Mechatronic system design · 2 Delft WB2414-Mechatronic System Design 2013-2014 3 University of...

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1 WB2414-Mechatronic System Design 2013-2014 1 Delft University of Technology Mechatronic system design Mechatronic system design wb24142013/2014 Course part 4 Prof.ir. R.H.Munnig Schmidt Mechatronic System Design Dynamics of motion systems WB2414-Mechatronic System Design 2013-2014 2 Delft University of Technology Contents Stiffness in Precision Engineering Passive and active stiffness Compliance of (a combination of) dynamic elements Dynamic modelling of damped massspring systems. Transmissibility Coupled massspring systems Eigenmodes, eigenfrequencies and modeshapes Standard mechanical frequency responses

Transcript of Mechatronic system design · 2 Delft WB2414-Mechatronic System Design 2013-2014 3 University of...

1

WB2414-Mechatronic System Design 2013-2014 1DelftUniversity ofTechnology

Mechatronic system design

Mechatronic system design wb2414‐20132014

Course part 4

Profir RHMunnig SchmidtMechatronic System Design

Dynamics of motion systems

WB2414-Mechatronic System Design 2013-2014 2DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

2

WB2414-Mechatronic System Design 2013-2014 3DelftUniversity ofTechnology

Well known objects

102 Nm Soft pillow

104 Nm Car suspension

Soft couch

105 Nm Table

Bicycle

107 Nm Office building

108 Nm Concrete pillar

109 Nm Steel train wheel on steel rail track

Stiffness of objects

WB2414-Mechatronic System Design 2013-2014 4DelftUniversity ofTechnology

What is stiffness

s

r

d

d

d

F k x

F F

xk

k

F

x

Hookersquos law for force from spring

Hooke‐Newton law for

external force

Where should you place the stiffness if possible

Take the shortest force loop

3

WB2414-Mechatronic System Design 2013-2014 5DelftUniversity ofTechnology

Natural frequency of the resonance of a mass-spring system

bull At resonance the forces are in

balancebull Deformation force (stiffness) plus acceleration force (mass) is zero

m

k

Stationary reference

x02 2

a d 2 2

d d0

d d

x xF F m kx m kx

t t

0

20 0 0

0

ˆ sin ( t)

ˆ ˆsin( ) sin( )

x x

mx t kx t

k

m

WB2414-Mechatronic System Design 2013-2014 6DelftUniversity ofTechnology

The first natural frequency determines the sensitivity to harmonic vibrations

bullThe maximum force needed to follow the acceleration

bullThe maximum error due to this force

bullThe natural frequency

bullWhich results in

20

k

m

20 0 f f

e f 020 e e

ˆ ˆˆ ˆ

ˆ ˆf x x

x x f ff x x

2f

ˆ ˆ ˆF ma mx

2f

e

ˆ ˆ ˆ

m xFx

k k

4

WB2414-Mechatronic System Design 2013-2014 7DelftUniversity ofTechnology

Active stiffness in a CD player bandwidth

bull200 μm radial vibrations at 25 Hz

bullMass lens 10 10‐3 kg

bullMax radial error 02 μm

6r

0 6r

r0

2r

2 50

ˆ 200 10 25 800

0 2 10

4 =25 Nm 1

middot102

xf f Hz

kf k mf

m

WB2414-Mechatronic System Design 2013-2014 8DelftUniversity ofTechnology

Virtual stiffness

bull Measure position

bull Actuate with force proportional and opposite to the deviation (feedback)

bull Gives virtual spring stiffness

m at rcr pF G G G G G

r tr

Fk G

5

WB2414-Mechatronic System Design 2013-2014 9DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 10DelftUniversity ofTechnology

10

Stiffness and compliance

bull Stiffness it the ability of a system to withstand a force by

minimising the resulting motiondeformation

bull Compliance is the opposite

bull Both can be real in phase with a periodic force or complex dynamic frequency dependent 90o out of phase with a periodic

force

bull A spring has a real stiffnesscompliance

s

1xC

F k

6

WB2414-Mechatronic System Design 2013-2014 11DelftUniversity ofTechnology

11

Compliance of (a combination of) dynamic elements

bull k = stiffness of the springbull c = damping coefficient of the damperbull m = mass of the body

m

x0k

Stationary reference

c F

x

s

1xC

F k

WB2414-Mechatronic System Design 2013-2014 12DelftUniversity ofTechnology

Stiffness and compliance of a damper

dd

d( ) ( )

d( )

( )

( )

1 1( )

( )

xF t c F s scx

tF jc x

xC

k F jc

F t

F t

m

x0k

Stationary reference

c F

x

7

WB2414-Mechatronic System Design 2013-2014 13DelftUniversity ofTechnology

Stiffness and compliance of a body

22

2

2

m 2m

( )d

( ) ( )d

( )

1 1( )

(

( )

)

xF t m F s ms x

t

F m x

xC

k F

F t

F t

m

m

x0k

Stationary reference

c F

x

WB2414-Mechatronic System Design 2013-2014 14DelftUniversity ofTechnology

Combined Compliance of body spring and damper

sts d m t

tt

s d m

d m

1 1 1( ) ( ) ( )

1( ) ( )

1 1 1

xF F x

C C C C

xC

FC

F

C C

F

8

WB2414-Mechatronic System Design 2013-2014 15DelftUniversity ofTechnology

Overview of the dynamic properties

WB2414-Mechatronic System Design 2013-2014 16DelftUniversity ofTechnology

The separate element responses in a bode plot

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

9

WB2414-Mechatronic System Design 2013-2014 17DelftUniversity ofTechnology

No dampingDue to energy conservation response becomes infinite(resonance)

Log |xF|

Log ωω0

Phase

180

0

WB2414-Mechatronic System Design 2013-2014 18DelftUniversity ofTechnology

Low damping

180

0

Log |xF|

Log ωω0

Phase

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

2

WB2414-Mechatronic System Design 2013-2014 3DelftUniversity ofTechnology

Well known objects

102 Nm Soft pillow

104 Nm Car suspension

Soft couch

105 Nm Table

Bicycle

107 Nm Office building

108 Nm Concrete pillar

109 Nm Steel train wheel on steel rail track

Stiffness of objects

WB2414-Mechatronic System Design 2013-2014 4DelftUniversity ofTechnology

What is stiffness

s

r

d

d

d

F k x

F F

xk

k

F

x

Hookersquos law for force from spring

Hooke‐Newton law for

external force

Where should you place the stiffness if possible

Take the shortest force loop

3

WB2414-Mechatronic System Design 2013-2014 5DelftUniversity ofTechnology

Natural frequency of the resonance of a mass-spring system

bull At resonance the forces are in

balancebull Deformation force (stiffness) plus acceleration force (mass) is zero

m

k

Stationary reference

x02 2

a d 2 2

d d0

d d

x xF F m kx m kx

t t

0

20 0 0

0

ˆ sin ( t)

ˆ ˆsin( ) sin( )

x x

mx t kx t

k

m

WB2414-Mechatronic System Design 2013-2014 6DelftUniversity ofTechnology

The first natural frequency determines the sensitivity to harmonic vibrations

bullThe maximum force needed to follow the acceleration

bullThe maximum error due to this force

bullThe natural frequency

bullWhich results in

20

k

m

20 0 f f

e f 020 e e

ˆ ˆˆ ˆ

ˆ ˆf x x

x x f ff x x

2f

ˆ ˆ ˆF ma mx

2f

e

ˆ ˆ ˆ

m xFx

k k

4

WB2414-Mechatronic System Design 2013-2014 7DelftUniversity ofTechnology

Active stiffness in a CD player bandwidth

bull200 μm radial vibrations at 25 Hz

bullMass lens 10 10‐3 kg

bullMax radial error 02 μm

6r

0 6r

r0

2r

2 50

ˆ 200 10 25 800

0 2 10

4 =25 Nm 1

middot102

xf f Hz

kf k mf

m

WB2414-Mechatronic System Design 2013-2014 8DelftUniversity ofTechnology

Virtual stiffness

bull Measure position

bull Actuate with force proportional and opposite to the deviation (feedback)

bull Gives virtual spring stiffness

m at rcr pF G G G G G

r tr

Fk G

5

WB2414-Mechatronic System Design 2013-2014 9DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 10DelftUniversity ofTechnology

10

Stiffness and compliance

bull Stiffness it the ability of a system to withstand a force by

minimising the resulting motiondeformation

bull Compliance is the opposite

bull Both can be real in phase with a periodic force or complex dynamic frequency dependent 90o out of phase with a periodic

force

bull A spring has a real stiffnesscompliance

s

1xC

F k

6

WB2414-Mechatronic System Design 2013-2014 11DelftUniversity ofTechnology

11

Compliance of (a combination of) dynamic elements

bull k = stiffness of the springbull c = damping coefficient of the damperbull m = mass of the body

m

x0k

Stationary reference

c F

x

s

1xC

F k

WB2414-Mechatronic System Design 2013-2014 12DelftUniversity ofTechnology

Stiffness and compliance of a damper

dd

d( ) ( )

d( )

( )

( )

1 1( )

( )

xF t c F s scx

tF jc x

xC

k F jc

F t

F t

m

x0k

Stationary reference

c F

x

7

WB2414-Mechatronic System Design 2013-2014 13DelftUniversity ofTechnology

Stiffness and compliance of a body

22

2

2

m 2m

( )d

( ) ( )d

( )

1 1( )

(

( )

)

xF t m F s ms x

t

F m x

xC

k F

F t

F t

m

m

x0k

Stationary reference

c F

x

WB2414-Mechatronic System Design 2013-2014 14DelftUniversity ofTechnology

Combined Compliance of body spring and damper

sts d m t

tt

s d m

d m

1 1 1( ) ( ) ( )

1( ) ( )

1 1 1

xF F x

C C C C

xC

FC

F

C C

F

8

WB2414-Mechatronic System Design 2013-2014 15DelftUniversity ofTechnology

Overview of the dynamic properties

WB2414-Mechatronic System Design 2013-2014 16DelftUniversity ofTechnology

The separate element responses in a bode plot

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

9

WB2414-Mechatronic System Design 2013-2014 17DelftUniversity ofTechnology

No dampingDue to energy conservation response becomes infinite(resonance)

Log |xF|

Log ωω0

Phase

180

0

WB2414-Mechatronic System Design 2013-2014 18DelftUniversity ofTechnology

Low damping

180

0

Log |xF|

Log ωω0

Phase

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

3

WB2414-Mechatronic System Design 2013-2014 5DelftUniversity ofTechnology

Natural frequency of the resonance of a mass-spring system

bull At resonance the forces are in

balancebull Deformation force (stiffness) plus acceleration force (mass) is zero

m

k

Stationary reference

x02 2

a d 2 2

d d0

d d

x xF F m kx m kx

t t

0

20 0 0

0

ˆ sin ( t)

ˆ ˆsin( ) sin( )

x x

mx t kx t

k

m

WB2414-Mechatronic System Design 2013-2014 6DelftUniversity ofTechnology

The first natural frequency determines the sensitivity to harmonic vibrations

bullThe maximum force needed to follow the acceleration

bullThe maximum error due to this force

bullThe natural frequency

bullWhich results in

20

k

m

20 0 f f

e f 020 e e

ˆ ˆˆ ˆ

ˆ ˆf x x

x x f ff x x

2f

ˆ ˆ ˆF ma mx

2f

e

ˆ ˆ ˆ

m xFx

k k

4

WB2414-Mechatronic System Design 2013-2014 7DelftUniversity ofTechnology

Active stiffness in a CD player bandwidth

bull200 μm radial vibrations at 25 Hz

bullMass lens 10 10‐3 kg

bullMax radial error 02 μm

6r

0 6r

r0

2r

2 50

ˆ 200 10 25 800

0 2 10

4 =25 Nm 1

middot102

xf f Hz

kf k mf

m

WB2414-Mechatronic System Design 2013-2014 8DelftUniversity ofTechnology

Virtual stiffness

bull Measure position

bull Actuate with force proportional and opposite to the deviation (feedback)

bull Gives virtual spring stiffness

m at rcr pF G G G G G

r tr

Fk G

5

WB2414-Mechatronic System Design 2013-2014 9DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 10DelftUniversity ofTechnology

10

Stiffness and compliance

bull Stiffness it the ability of a system to withstand a force by

minimising the resulting motiondeformation

bull Compliance is the opposite

bull Both can be real in phase with a periodic force or complex dynamic frequency dependent 90o out of phase with a periodic

force

bull A spring has a real stiffnesscompliance

s

1xC

F k

6

WB2414-Mechatronic System Design 2013-2014 11DelftUniversity ofTechnology

11

Compliance of (a combination of) dynamic elements

bull k = stiffness of the springbull c = damping coefficient of the damperbull m = mass of the body

m

x0k

Stationary reference

c F

x

s

1xC

F k

WB2414-Mechatronic System Design 2013-2014 12DelftUniversity ofTechnology

Stiffness and compliance of a damper

dd

d( ) ( )

d( )

( )

( )

1 1( )

( )

xF t c F s scx

tF jc x

xC

k F jc

F t

F t

m

x0k

Stationary reference

c F

x

7

WB2414-Mechatronic System Design 2013-2014 13DelftUniversity ofTechnology

Stiffness and compliance of a body

22

2

2

m 2m

( )d

( ) ( )d

( )

1 1( )

(

( )

)

xF t m F s ms x

t

F m x

xC

k F

F t

F t

m

m

x0k

Stationary reference

c F

x

WB2414-Mechatronic System Design 2013-2014 14DelftUniversity ofTechnology

Combined Compliance of body spring and damper

sts d m t

tt

s d m

d m

1 1 1( ) ( ) ( )

1( ) ( )

1 1 1

xF F x

C C C C

xC

FC

F

C C

F

8

WB2414-Mechatronic System Design 2013-2014 15DelftUniversity ofTechnology

Overview of the dynamic properties

WB2414-Mechatronic System Design 2013-2014 16DelftUniversity ofTechnology

The separate element responses in a bode plot

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

9

WB2414-Mechatronic System Design 2013-2014 17DelftUniversity ofTechnology

No dampingDue to energy conservation response becomes infinite(resonance)

Log |xF|

Log ωω0

Phase

180

0

WB2414-Mechatronic System Design 2013-2014 18DelftUniversity ofTechnology

Low damping

180

0

Log |xF|

Log ωω0

Phase

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

4

WB2414-Mechatronic System Design 2013-2014 7DelftUniversity ofTechnology

Active stiffness in a CD player bandwidth

bull200 μm radial vibrations at 25 Hz

bullMass lens 10 10‐3 kg

bullMax radial error 02 μm

6r

0 6r

r0

2r

2 50

ˆ 200 10 25 800

0 2 10

4 =25 Nm 1

middot102

xf f Hz

kf k mf

m

WB2414-Mechatronic System Design 2013-2014 8DelftUniversity ofTechnology

Virtual stiffness

bull Measure position

bull Actuate with force proportional and opposite to the deviation (feedback)

bull Gives virtual spring stiffness

m at rcr pF G G G G G

r tr

Fk G

5

WB2414-Mechatronic System Design 2013-2014 9DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 10DelftUniversity ofTechnology

10

Stiffness and compliance

bull Stiffness it the ability of a system to withstand a force by

minimising the resulting motiondeformation

bull Compliance is the opposite

bull Both can be real in phase with a periodic force or complex dynamic frequency dependent 90o out of phase with a periodic

force

bull A spring has a real stiffnesscompliance

s

1xC

F k

6

WB2414-Mechatronic System Design 2013-2014 11DelftUniversity ofTechnology

11

Compliance of (a combination of) dynamic elements

bull k = stiffness of the springbull c = damping coefficient of the damperbull m = mass of the body

m

x0k

Stationary reference

c F

x

s

1xC

F k

WB2414-Mechatronic System Design 2013-2014 12DelftUniversity ofTechnology

Stiffness and compliance of a damper

dd

d( ) ( )

d( )

( )

( )

1 1( )

( )

xF t c F s scx

tF jc x

xC

k F jc

F t

F t

m

x0k

Stationary reference

c F

x

7

WB2414-Mechatronic System Design 2013-2014 13DelftUniversity ofTechnology

Stiffness and compliance of a body

22

2

2

m 2m

( )d

( ) ( )d

( )

1 1( )

(

( )

)

xF t m F s ms x

t

F m x

xC

k F

F t

F t

m

m

x0k

Stationary reference

c F

x

WB2414-Mechatronic System Design 2013-2014 14DelftUniversity ofTechnology

Combined Compliance of body spring and damper

sts d m t

tt

s d m

d m

1 1 1( ) ( ) ( )

1( ) ( )

1 1 1

xF F x

C C C C

xC

FC

F

C C

F

8

WB2414-Mechatronic System Design 2013-2014 15DelftUniversity ofTechnology

Overview of the dynamic properties

WB2414-Mechatronic System Design 2013-2014 16DelftUniversity ofTechnology

The separate element responses in a bode plot

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

9

WB2414-Mechatronic System Design 2013-2014 17DelftUniversity ofTechnology

No dampingDue to energy conservation response becomes infinite(resonance)

Log |xF|

Log ωω0

Phase

180

0

WB2414-Mechatronic System Design 2013-2014 18DelftUniversity ofTechnology

Low damping

180

0

Log |xF|

Log ωω0

Phase

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

5

WB2414-Mechatronic System Design 2013-2014 9DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 10DelftUniversity ofTechnology

10

Stiffness and compliance

bull Stiffness it the ability of a system to withstand a force by

minimising the resulting motiondeformation

bull Compliance is the opposite

bull Both can be real in phase with a periodic force or complex dynamic frequency dependent 90o out of phase with a periodic

force

bull A spring has a real stiffnesscompliance

s

1xC

F k

6

WB2414-Mechatronic System Design 2013-2014 11DelftUniversity ofTechnology

11

Compliance of (a combination of) dynamic elements

bull k = stiffness of the springbull c = damping coefficient of the damperbull m = mass of the body

m

x0k

Stationary reference

c F

x

s

1xC

F k

WB2414-Mechatronic System Design 2013-2014 12DelftUniversity ofTechnology

Stiffness and compliance of a damper

dd

d( ) ( )

d( )

( )

( )

1 1( )

( )

xF t c F s scx

tF jc x

xC

k F jc

F t

F t

m

x0k

Stationary reference

c F

x

7

WB2414-Mechatronic System Design 2013-2014 13DelftUniversity ofTechnology

Stiffness and compliance of a body

22

2

2

m 2m

( )d

( ) ( )d

( )

1 1( )

(

( )

)

xF t m F s ms x

t

F m x

xC

k F

F t

F t

m

m

x0k

Stationary reference

c F

x

WB2414-Mechatronic System Design 2013-2014 14DelftUniversity ofTechnology

Combined Compliance of body spring and damper

sts d m t

tt

s d m

d m

1 1 1( ) ( ) ( )

1( ) ( )

1 1 1

xF F x

C C C C

xC

FC

F

C C

F

8

WB2414-Mechatronic System Design 2013-2014 15DelftUniversity ofTechnology

Overview of the dynamic properties

WB2414-Mechatronic System Design 2013-2014 16DelftUniversity ofTechnology

The separate element responses in a bode plot

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

9

WB2414-Mechatronic System Design 2013-2014 17DelftUniversity ofTechnology

No dampingDue to energy conservation response becomes infinite(resonance)

Log |xF|

Log ωω0

Phase

180

0

WB2414-Mechatronic System Design 2013-2014 18DelftUniversity ofTechnology

Low damping

180

0

Log |xF|

Log ωω0

Phase

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

6

WB2414-Mechatronic System Design 2013-2014 11DelftUniversity ofTechnology

11

Compliance of (a combination of) dynamic elements

bull k = stiffness of the springbull c = damping coefficient of the damperbull m = mass of the body

m

x0k

Stationary reference

c F

x

s

1xC

F k

WB2414-Mechatronic System Design 2013-2014 12DelftUniversity ofTechnology

Stiffness and compliance of a damper

dd

d( ) ( )

d( )

( )

( )

1 1( )

( )

xF t c F s scx

tF jc x

xC

k F jc

F t

F t

m

x0k

Stationary reference

c F

x

7

WB2414-Mechatronic System Design 2013-2014 13DelftUniversity ofTechnology

Stiffness and compliance of a body

22

2

2

m 2m

( )d

( ) ( )d

( )

1 1( )

(

( )

)

xF t m F s ms x

t

F m x

xC

k F

F t

F t

m

m

x0k

Stationary reference

c F

x

WB2414-Mechatronic System Design 2013-2014 14DelftUniversity ofTechnology

Combined Compliance of body spring and damper

sts d m t

tt

s d m

d m

1 1 1( ) ( ) ( )

1( ) ( )

1 1 1

xF F x

C C C C

xC

FC

F

C C

F

8

WB2414-Mechatronic System Design 2013-2014 15DelftUniversity ofTechnology

Overview of the dynamic properties

WB2414-Mechatronic System Design 2013-2014 16DelftUniversity ofTechnology

The separate element responses in a bode plot

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

9

WB2414-Mechatronic System Design 2013-2014 17DelftUniversity ofTechnology

No dampingDue to energy conservation response becomes infinite(resonance)

Log |xF|

Log ωω0

Phase

180

0

WB2414-Mechatronic System Design 2013-2014 18DelftUniversity ofTechnology

Low damping

180

0

Log |xF|

Log ωω0

Phase

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

7

WB2414-Mechatronic System Design 2013-2014 13DelftUniversity ofTechnology

Stiffness and compliance of a body

22

2

2

m 2m

( )d

( ) ( )d

( )

1 1( )

(

( )

)

xF t m F s ms x

t

F m x

xC

k F

F t

F t

m

m

x0k

Stationary reference

c F

x

WB2414-Mechatronic System Design 2013-2014 14DelftUniversity ofTechnology

Combined Compliance of body spring and damper

sts d m t

tt

s d m

d m

1 1 1( ) ( ) ( )

1( ) ( )

1 1 1

xF F x

C C C C

xC

FC

F

C C

F

8

WB2414-Mechatronic System Design 2013-2014 15DelftUniversity ofTechnology

Overview of the dynamic properties

WB2414-Mechatronic System Design 2013-2014 16DelftUniversity ofTechnology

The separate element responses in a bode plot

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

9

WB2414-Mechatronic System Design 2013-2014 17DelftUniversity ofTechnology

No dampingDue to energy conservation response becomes infinite(resonance)

Log |xF|

Log ωω0

Phase

180

0

WB2414-Mechatronic System Design 2013-2014 18DelftUniversity ofTechnology

Low damping

180

0

Log |xF|

Log ωω0

Phase

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

8

WB2414-Mechatronic System Design 2013-2014 15DelftUniversity ofTechnology

Overview of the dynamic properties

WB2414-Mechatronic System Design 2013-2014 16DelftUniversity ofTechnology

The separate element responses in a bode plot

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

9

WB2414-Mechatronic System Design 2013-2014 17DelftUniversity ofTechnology

No dampingDue to energy conservation response becomes infinite(resonance)

Log |xF|

Log ωω0

Phase

180

0

WB2414-Mechatronic System Design 2013-2014 18DelftUniversity ofTechnology

Low damping

180

0

Log |xF|

Log ωω0

Phase

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

9

WB2414-Mechatronic System Design 2013-2014 17DelftUniversity ofTechnology

No dampingDue to energy conservation response becomes infinite(resonance)

Log |xF|

Log ωω0

Phase

180

0

WB2414-Mechatronic System Design 2013-2014 18DelftUniversity ofTechnology

Low damping

180

0

Log |xF|

Log ωω0

Phase

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

10

WB2414-Mechatronic System Design 2013-2014 19DelftUniversity ofTechnology

High damping

180

0

Log |xF|

Log ωω0

Phase

WB2414-Mechatronic System Design 2013-2014 20DelftUniversity ofTechnology

Extreme damping two first order systems

180

0

Log |xF|

Log ωω0

Phase

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

11

WB2414-Mechatronic System Design 2013-2014 21DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 22DelftUniversity ofTechnology

Start with second law of NewtonF=ma

2

2

d d( ) )

d d

x xF t m c kx

t t

2 ( )( ) ( )F s x m ct s sF k

t 2

20 0

( )( ) ( )2 1

sCxC F

s sFt

1sC

k 0

k

m

2

c

km

t 22

11

( ) ( )1

mx kC s sm csF ms cs k sk k

FRF

With only positive imaginary terms (Fourier)

m

x0k

Stationary reference

c F

x

Laplace gives

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

12

WB2414-Mechatronic System Design 2013-2014 23DelftUniversity ofTechnology

The magnitude and the phase

Start with s=jω

2 22

20 0

( )

1 2

st

CC

And phase angle φ is ndash arctan (imaginaryreal of the denominator)

WB2414-Mechatronic System Design 2013-2014 24DelftUniversity ofTechnology

Compliance Bode plot with damping

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

13

WB2414-Mechatronic System Design 2013-2014 25DelftUniversity ofTechnology

The damping ratio is related to the pole location in the Laplace plane

s j Poles are those values of s where denominator of Ct is zero

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

0s

t 1 02

2

If 0 then 0 no damping

and and 1

c

CC p j p j

ms

k

Re

Im

WB2414-Mechatronic System Design 2013-2014 26DelftUniversity ofTechnology

Critical damping ratio

Re

Im

= 1

lt 1

lt 1

gt 1

gt 1

1

2t

s2

20 0

1

1 2 1

Cx kCm cs s sF sk k

1 2 and d dp j p j

s

2

s s2 2t

2

If 2 then 1 and

1

11 2 1 1

c km

C C CkCm cs m m sms s s sk k k k k

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

14

WB2414-Mechatronic System Design 2013-2014 27DelftUniversity ofTechnology

Above critical damping the mass-spring system reduces to two first order systems

Log |xF|

Log ω

Spring line

Mass line (‐2)

Damper line (‐1)Spring line

Damper line

180 Mass line

1s

s

xC

F k

2

1m

m

xC

F m

1d

d

xC

F c

Phase

90

0

180

0

ω0

020

1 1

k

k m m

WB2414-Mechatronic System Design 2013-2014 28DelftUniversity ofTechnology

Effect of the damping ratio on the stepresponse

At ζ = 1 no overshootCritical dampingtime domain related term

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

15

WB2414-Mechatronic System Design 2013-2014 29DelftUniversity ofTechnology

Energy at natural Frequency

Energy will be ldquotrappedrdquo in the systemWhen excited in this frequency the amplitude will continue to rise

For electrical engineering (frequency domain) the quality factor Q is defined for this property as resonators are also useful But in mechanical engineering the time domain related term ldquodamping ratiordquo is more commonly used

Letrsquos bridge the gap

WB2414-Mechatronic System Design 2013-2014 30DelftUniversity ofTechnology

Q=100 means peak level at 100 times spring-line level

bull k = 104 Nm

bull m = 025 kg

m

x0k

Stationary reference

c F

x

At Q = 1 no resonance peakfrequency domain related term

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

16

WB2414-Mechatronic System Design 2013-2014 31DelftUniversity ofTechnology

Relation Q and

1 1

2 2Q

Q

1 1

2 2EE ME

ME EE

Electrical vs mechanical Time vs frequency domain

WB2414-Mechatronic System Design 2013-2014 32DelftUniversity ofTechnology

Velocity response kinetic energy

2

20 0

dd

2 1

s

xv sxtF F F

s C

s s

m

x0k

Stationary reference

c F

x

bull k = 104 Nm

bull m = 025 kg

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

17

WB2414-Mechatronic System Design 2013-2014 33DelftUniversity ofTechnology

Resonance is energy storage damping is velocity related

bull Driving force is in phase with velocity at resonance

bull Power is Force times speed

bull Max energy transfer at resonance

bull Damper is just the opposite

bull Q tells something about the height of the resonance peak

Maximum energy stored2

Energy lost per cycleQ

WB2414-Mechatronic System Design 2013-2014 34DelftUniversity ofTechnology

Q and energy

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

18

WB2414-Mechatronic System Design 2013-2014 35DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 36DelftUniversity ofTechnology

Transmissibility transfer of motion through the support of a dynamic system

2m f m

tm f m2

d d( )( ) ( )

d d

x x xF t m c k x x

t t

02

20 0

2 1

2 1

m

f

sx

s sx

0

k

m

2

c

km

22

1

1

m

f

csx cs k k

m csx ms cs k sk k

With

The force acting on the body equals

m xm

kxfTable

c

Stationary reference

2m f( ) ( )x ms cs k x cs k

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

19

WB2414-Mechatronic System Design 2013-2014 37DelftUniversity ofTechnology

Bode plot of transmissibility

WB2414-Mechatronic System Design 2013-2014 38DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

20

WB2414-Mechatronic System Design 2013-2014 39DelftUniversity ofTechnology

Coupled mass-spring systems

m1

x1

km2

x2

F

Stationary reference

Elastically coupled Multi-body or finite-element non-rigid body dynamics

WB2414-Mechatronic System Design 2013-2014 40DelftUniversity ofTechnology

Which statement is true There is a frequency where

m1

x1

km2

x2

F

Stationary reference

1 Only m1 will resonate with k

2 Only m2 will resonate with k

3 Only m1 will stop moving

4 Only m2 will stop moving

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

21

WB2414-Mechatronic System Design 2013-2014 41DelftUniversity ofTechnology

Equations of Motion

bull First body

bull Second body

m1

x1

km2

x2

F

Stationary reference

21

1 1 22

21 1 1 2

22

2 1 22

22 2 1 2

d ( )( ) ( )

d

( ) ( )

d ( )( )

d

( ) ( )

x tm F t k x x

t

m s x s F k x x

x tm k x x

t

m s x s k x x

note The domain (s or t) is only mentioned once

WB2414-Mechatronic System Design 2013-2014 42DelftUniversity ofTechnology

Resulting equations in the Laplace domain

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

Low values of s at low frequencies

1 2

21 2

1( ) ( )

x xs s

F F m m s

High values of s at high frequencies

1 22 4

1 1 2

1( ) ( )

x x ks s

F m s F m m s

Fourth order system

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

22

WB2414-Mechatronic System Design 2013-2014 43DelftUniversity ofTechnology

At mid frequency the driven body shows a strange effect

Combination of poles and zeros

21 2

4 21 2 1 2

24 2

1 2 1 2

2 2

2

1

( )

w

then the compliance of shows a dip

hen

k

m

x m s k

F m m s k m m s

x ks

F m m s k m

s

x

m s

WB2414-Mechatronic System Design 2013-2014 44DelftUniversity ofTechnology

m1 = 01 m2 an actuated large mass by a lighter actuator

1

2

4

3

3

25 10 kg

25 10

1

kg

Nm0

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

1 2

21 2

1LF ( ) ( )

x x

s sF F m m s

1 22 4

1 1 2

1HF ( ) ( )

x x ks s

F m s F m m s

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

23

WB2414-Mechatronic System Design 2013-2014 45DelftUniversity ofTechnology

m1 = m2 motor mass is optimisedto the driven mass

31

32

4

25 10 kg

25 10

10

kg

Nm

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

WB2414-Mechatronic System Design 2013-2014 46DelftUniversity ofTechnology

m1 = 10 m2 parasitic resonances

1

2

4

3

025 kg

25 10 kg

1 m0 N

m

m

k

21 2

4 21 2 1 2

24 2

1 2 1 2

( )

( )

x m s ks

F m m s k m m s

x ks

F m m s k m m s

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

24

WB2414-Mechatronic System Design 2013-2014 47DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass spring systems

bull Transmissibility

bull Coupled mass spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

WB2414-Mechatronic System Design 2013-2014 48DelftUniversity ofTechnology

Eigenmodes

When excited non‐rigid bodies and complex mass‐spring systems

vibrate in different eigenmodes with two main properties

bull Eigenfrequency the related natural (resonance) frequency

bull Mode‐shape the deformation that corresponds with the eigenmode described in a multiple degree of freedom ldquoshape‐

function rdquo

Modelling is done by discretisation of the system in multiple mass‐

spring systems

bull The shape function reduces to an eigenvector with one value for

each body for the relative motion magnitude and direction (sign)

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

25

WB2414-Mechatronic System Design 2013-2014 49DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 50DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

26

WB2414-Mechatronic System Design 2013-2014 51DelftUniversity ofTechnology

Eigen modes of coupled bodies

1

1

1

2

1

1

WB2414-Mechatronic System Design 2013-2014 52DelftUniversity ofTechnology

Multiplicative expression shows two resonating eigenfrequencies

c

c

2122 2

1 2

1 2

1 2

22 2

1 2 c

1 1

with

1

xm s k

F m m s m s k

m mm

m m

x k

F m m s m s k

2

1 2 24 2 4 2

1 2 1 2 1 2 1 2

x m s k x k

F m m s k m m s F m m s k m m s

Starting with

11 2

2

00

m m

k

M

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

27

WB2414-Mechatronic System Design 2013-2014 53DelftUniversity ofTechnology

Additive expression

bull Can be written as a combination of two eigenmodes with modal

mass and stiffness using eigenvector

21 1 222 2

1 2 1c

c 2

22 2

1 2 c

1 1 with

1

x m mm s k m

F m m s m s k m m

x k

F m m s m s k

2 22 2

2 2

c 1 1

1 2 1 212 2 2 2

1 2

1 2 1 222 2 2 2

1 2

2 2

1 2 1 22 2

c 1 1 2 2

1 1=

( )

1 1=

( )

m m

m m m mx

F m m s m s k s s

m m

m m m mx

F m m s m s k s s

m m

1

1

1

2

1

1

i i i

WB2414-Mechatronic System Design 2013-2014 54DelftUniversity ofTechnology

Modes 1 and 2 combined

1 212 2

1 222

22

2

1 1 2 2

1 22

1 12

2 2

1

1

m

m mx

F s s

m

m mx

F s s

m

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

28

WB2414-Mechatronic System Design 2013-2014 55DelftUniversity ofTechnology

i

Theory on modal decompositionbull General equation of motion (vectormatrix) of finite element system

bull General transfer function

bull In absence of external force

bull Decoupled by eigenvalue problem where is the eigenvector

2

2

20

( ) ( ) ( )

( ) ( ) ( )

( ) ( ) 0

0i i

Mx t Kx t F t

Ms x s Kx s F s

Ms x s Kx s

K M

WB2414-Mechatronic System Design 2013-2014 56DelftUniversity ofTechnology

Modal mass and stiffness orthogonality of eigenmodes

bull Modal mass

bull Modal Stiffness

20

0 ( )

0 ( )

i j

i i i

i j

i i i i i

M i j

M

K i j

K

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

29

WB2414-Mechatronic System Design 2013-2014 57DelftUniversity ofTechnology

Scaling

bull Length of eigenvector is not defined (only the direction)

bull Three scaling methods are often applied

1 1

2 max 1

3 1

i i i

i

i

i

M

WB2414-Mechatronic System Design 2013-2014 58DelftUniversity ofTechnology

Modal coordinates

bull When qiequals the motion of eigenmode i then the total displacement vector x(t) will be

where qi is called the modal coordinate

bull This gives the following displacement for DOF xk(t)

1 1 2 2 n n

1 1 2 2 n

( ) ( ) ( ) ( )

( ) ( ) ( ) ( )k k k n k

x t q t q t q t

x t q t q t q t

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

30

WB2414-Mechatronic System Design 2013-2014 59DelftUniversity ofTechnology

Full set of uncoupled equations

1

1 2 n

n

2

( ) ( )

( )

with and ( ) ( )

( )

applied to ( ) ( ) ( )

gives with pre-multiplication with

( ) ( ) ( )

i

x t q t

q t

q t q t

q t

Ms x s Kx s F s

M q t K q t F t

WB2414-Mechatronic System Design 2013-2014 60DelftUniversity ofTechnology

This can be transformed into a combined transfer function

bull The response of DOF by

eigenmode i on force equals

bull The total response equals

2

i

n n 2

1 1

( )

( )

i k i

k i i

i k i

i ik k i ii

xs

F s

x xs

F F s

xkF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

31

WB2414-Mechatronic System Design 2013-2014 61DelftUniversity ofTechnology

Graphical representation

bull The modal coordinate is

represented by the angle of the lever or the displacement at distance 1

bull Modal mass and stiffness are connected to the modal

coordinate

bull The eigenvectors determine the

ratio of ldquocontrollabilityrdquo of actuator and ldquoobservabilityrdquo of sensor

2

i

( ) i k i

k i i

xs

F s

WB2414-Mechatronic System Design 2013-2014 62DelftUniversity ofTechnology

Effective modal values

As perceived at the actuator

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

32

WB2414-Mechatronic System Design 2013-2014 63DelftUniversity ofTechnology

Mass on leafspring two eigenmodes

F

x

F

x

y

x

a Mode shape 1 b Mode shape 2

Stationary reference Stationary reference

WB2414-Mechatronic System Design 2013-2014 64DelftUniversity ofTechnology

Modes 1 and 2 combined by measuring non co-local with the force

‐2 slope with ‐360o

phase is non‐minimum phase system

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

33

WB2414-Mechatronic System Design 2013-2014 65DelftUniversity ofTechnology

Non-minimum phase step response

WB2414-Mechatronic System Design 2013-2014 66DelftUniversity ofTechnology

Summary of termsbull Eigenvector

bull Vector with terms that represent the relative motion amplitude of each element in the

discretised structure It is the discretised ldquoshape functionrdquo

bull Scaling is at will as long as the scaling is equal for all properties of that eigenmode

bull Modal mass and stiffnessbull relate to the mass and stiffness matrix by double multiplication with the eigenvector

bull Scaling of the eigenvector also scales the modal mass and stiffness (squared)

bull Modal coordinatesbull Represent the motion of the eigenmode at the location of the modal mass and

stiffness

bull It is used to determine the motion of all elements with the eigenvector and as such it

also depends on the chosen scaling

bull Effective modal mass and stiffness

bull Is the modal mass and stiffness as perceived at the actuator position It is calculated

from the modal mass and stiffness by dividing by the corresponding eigenvector term

squared hence the chosen scaling no longer plays a role

i i i i i iM K

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

34

WB2414-Mechatronic System Design 2013-2014 67DelftUniversity ofTechnology

Mode-shape of complex non-rigid body

WB2414-Mechatronic System Design 2013-2014 68DelftUniversity ofTechnology

Contents

bull Stiffness in Precision Engineering

bull Passive and active stiffness

bull Compliance of (a combination of) dynamic elements

bull Dynamic modelling of damped mass‐spring systems

bull Transmissibility

bull Coupled mass‐spring systems

bull Eigenmodes eigenfrequencies and modeshapes

bull Standard mechanical frequency responses

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

35

WB2414-Mechatronic System Design 2013-2014 69DelftUniversity ofTechnology

Typical combination of two eigenmodes one rigid and one non-rigid

bullActuated at xa

bullSensed at different locations

WB2414-Mechatronic System Design 2013-2014 70DelftUniversity ofTechnology

Different combinations of two eigenmodes

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF

36

WB2414-Mechatronic System Design 2013-2014 71DelftUniversity ofTechnology

4 types of responses result

WB2414-Mechatronic System Design 2013-2014 72DelftUniversity ofTechnology

Eigenfrequencies of multiple eigenmodes in 6-DOF