Chapter 4site.iugaza.edu.ps/mhaiba/files/2012/01/Ch-4-Deflection-and... · Chapter Outline Dr....

Chapter 4 Deflection and Stiffness

March 24, 2014

Dr. Mohammad Suliman Abuhaiba, PE 1

Chapter Outline

Dr. Mohammad Suliman Abuhaiba, PE

Spring Rates

Tension, Compression, and Torsion

Deflection Due to Bending

Beam Deflection Methods Beam Deflections by Superposition

Strain Energy

Castigliano’s Theorem

Deflection of Curved Members

Statically Indeterminate Problems

Compression Members—General Long Columns with Central Loading

Intermediate-Length Columns with Central Loading

Columns with Eccentric Loading

Struts or Short Compression Members

Suddenly Applied Loading

March 24, 2014 2

Force vs Deflection

Elasticity:property of a material that

enables it to regain its original configuration

after deformation

Spring: a mechanical element that exerts a force when deformed


March 24, 2014 3

Force vs Deflection


Linear spring Nonlinear

stiffening spring

Nonlinear

softening spring

Fig. 4–1

March 24, 2014 4

Spring Rate

Spring rate

For linear springs, k is constant, spring

constant


March 24, 2014 5

Axially-Loaded Stiffness

Total extension or contraction of a uniform

bar in tension or compression

Spring constant, with k = F/d


March 24, 2014 6

Torsionally-Loaded Stiffness

Angular deflection (radians) of a uniform

solid or hollow round bar subjected to a

twisting moment T

Torsional spring constant for round bar


March 24, 2014 7


Curvature of beam subjected to bending

moment M

Curvature of plane curve


March 24, 2014 8


Slope of beam at any point x along the

length

If slope is very small, denominator of Eq.

4.9 approaches unity:


March 24, 2014 9


Recall Eqs. 3-3 & 3-4


March 24, 2014 10

Example 4-1


Fig. 4–2

For the beam in Fig. 4–2, the bending moment equation,

for 0 ≤ x ≤ l, is

Using Eq. (4–12), determine the equations for slope &

deflection of the beam, slopes at ends, and max

deflection.

HW Assignment #4-1

Problem 4-1

Due Monday 17/3/2014

March 24, 2014


12

Beam Deflection Methods

1. Superposition

2. Moment-area method

3. Numerical integration

4. Castigliano energy method

5. Finite element software


March 24, 2014 13

Beam Deflection by Superposition

Table A-9

Roark’s Formulas for Stress & Strain


March 24, 2014 14

Example 4-2

Consider the uniformly loaded beam with a

concentrated force as shown in Fig. 4–3.

Using superposition, determine the reactions

and deflection as a function of x.


Fig. 4–3

Example 4-3

Consider the beam in Fig. 4–4a. Determine

the deflection equations using superposition.


Fig. 4–4

Example 4-4 Figure 4–5a shows a cantilever beam with an

end load. Normally we model this problem

by considering the left support as rigid. After

testing the rigidity of the wall it was found

that the translational stiffness of the wall was

kt force per unit vertical deflection, and the

rotational stiffness was kr moment per unit

angular (radian) deflection (see Fig. 4–5b).

Determine the deflection equation for the

beam under the load F.


Example 4-4


Fig. 4–5

HW Assignment #4-2

Problems: 4.10, 4.14, 4.41

Due Wednesday

19/3/2014

March 24, 2014


19

Strain Energy

External work done on elastic member

while deforming it is transformed into strain

energy, or potential energy.

Strain energy = average force × deflection


March 24, 2014 20

Axial loading, k = AE/l from Eq. (4-4),

Torsional loading, k = GJ/l from Eq. (4-7)

Some Common Strain

Energy Formulas


March 24, 2014 21

Some Common Strain

Energy Formulas

Direct shear loading,

Bending loading,


March 24, 2014 22

Some Common Strain

Energy Formulas

Transverse shear loading,

C = modifier dependent on x-sectional

shape


March 24, 2014 23

Some Common Strain

Energy Formulas

Table 4–1: Strain-Energy Correction Factors

for Transverse Shear


March 24, 2014 24

Example 4-8

A cantilever beam with a round cross

section has a concentrated load F at the

end, as shown in Fig. 4–9a. Find the strain

energy in the beam.


Fig. 4–9

Forces act on elastic systems subject to

small displacements

Displacement corresponding to any force

along its direction = partial derivative of

total strain energy wrt force

For rotational displacement, in radians,

Castigliano’s Theorem


March 24, 2014 26

Example 4-9 The cantilever of Ex. 4–8 is a carbon steel bar 10 in

long with a 1-in diameter and is loaded by a force F

= 100 lbf.

a. Find max deflection using Castigliano’s theorem,

including that due to shear.

b. What error is introduced if shear is neglected?


Fig. 4–9

Utilizing a Fictitious Force

Apply a fictitious force Q at the point, and

in the direction, of the desired deflection.

Set up the equation for total strain energy

including energy due to Q.

Take derivative of total strain energy wrt Q

Set Q to zero


March 24, 2014 28

Finding Deflection Without

Finding Energy Partial derivative is moved inside the integral.

For example, for bending,


March 24, 2014 29

Common Deflection Equations


Example 4-10 Using Castigliano’s method, determine the

deflections of points A and B due to the force F

applied at the end of the step shaft shown in Fig. 4–

10. The second area moments for sections AB and

BC are I1 and 2I1, respectively.


Fig. 4–10

Example 4-11

For the wire form of diameter d shown in Fig. 4–11a,

determine the deflection of point B in the direction

of the applied force F (neglect the effect of

transverse shear).


Fig. 4–11

Example 4-11


HW Assignment #4-3

Problems: 4.67, 4.70

Due Saturday 22/3/2014

March 24, 2014


34

Deflection of Curved Members Four strain energy terms due to:

1. Bending moment M

2. Axial force Fq

3. Bending moment due to Fq

4. Transverse shear Fr


March 24, 2014 35

Strain energy due to bending moment M


rn = radius of neutral axis

March 24, 2014 36


Strain energy due to axial force Fq


March 24, 2014 37


Strain energy due to bending moment from Fq


March 24, 2014 38


Strain energy due to transverse shear Fr


March 24, 2014 39


Combining four energy terms

Deflection by Castigliano’s method


March 24, 2014 40



March 24, 2014 41



March 24, 2014 42


Deflection of Thin Curved

Members R/h > 10, eccentricity is small

Strain energies approximated with regular

energy equations: Rdq ≈ dx

As R increases, bending component

dominates all other terms


March 24, 2014 43

Example 4-12

The cantilevered hook shown in Fig. 4–13a is formed

from a round steel wire with a diameter of 2 mm.

The hook dimensions are l = 40 & R = 50 mm. A force

P of 1 N is applied at point C. Use Castigliano’s

theorem to estimate deflection at point D at the tip.


Fig. 4–13

HW Assignment #4-4

Problems: 4.78

Due Monday 24/3/2014

March 24, 2014


45

Statically Indeterminate

Problems

Redundant supports: extra constraint

supports

A deflection equation is required for each

redundant support.


March 24, 2014 46

Procedure 1 for Statically

Indeterminate Problems 1. Choose redundant reactions

2. Write equations of static equilibrium for

remaining reactions in terms of applied

loads & redundant reactions.

3. Write deflection equations for points at

locations of redundant reactions in terms

of applied loads and redundant

reactions.

4. Solve equilibrium & deflection equations Dr. Mohammad Suliman Abuhaiba, PE

March 24, 2014 47

Example 4-14

The indeterminate beam 11 of Appendix

Table A–9 is reproduced in Fig. 4–16.

Determine the reactions using procedure 1.


Fig. 4–16

Procedure 2 for Statically

Indeterminate Problems 1. Write equations of static equilibrium in

terms of applied loads & unknown

restraint reactions.

2. Write deflection equation in terms of

applied loads and unknown restraint

reactions.

3. Apply boundary conditions to deflection

equation consistent with restraints.

4. Solve the set of equations. Dr. Mohammad Suliman Abuhaiba, PE

March 24, 2014 49

Example 4-15

The rods AD & CE shown in Fig. 4–17a each

have a diameter of 10 mm. The second area

moment of beam ABC is I = 62.5(103) mm4.

The modulus of elasticity of the material used

for the rods and beam is E = 200 GPa. The

threads at the ends of the rods are single-

threaded with a pitch of 1.5 mm. The nuts

are first snugly fit with bar ABC horizontal.

Next the nut at A is tightened one full turn.

Determine the resulting tension in each rod

and the deflections of points A and C. Dr. Mohammad Suliman Abuhaiba, PE

Example 4-15


Fig. 4–17

HW Assignment #4-5

Problems: 4.95, 4.97

Due Wednesday

26/3/2014

March 24, 2014


52

Compression Members

Column:

A member loaded in compression

either its length or eccentric loading

causes it to experience more than

pure compression


March 24, 2014 53

Compression Members

Four categories of columns

1. Long columns with central loading

2. Intermediate-length columns with

central loading

3. Columns with eccentric loading

4. Struts or short columns with eccentric

loading


March 24, 2014 54

Long Columns with Central

Loading

When P reaches

critical load,

column becomes

unstable &

bending

develops rapidly


March 24, 2014 55

Euler Column Formula Pin-ended

column,

Other end conditions: apply

a constant C for each end

condition


March 24, 2014 56

Recommended Values for

End Condition Constant

Table 4-2: End-Condition Constants for Euler

Columns [to Be Used with Eq. (4–43)]


March 24, 2014 57


Loading I = Ak2, Euler column formula becomes

l/k = slenderness ratio, to classify columns according to length categories.

Pcr/A = critical unit load necessary to place

the column in a condition of unstable

equilibrium Dr. Mohammad Suliman Abuhaiba, PE

March 24, 2014 58

Euler Curve

Pcr/A vs l/k, with C = 1 gives curve PQR


Fig. 4–19

March 24, 2014 59


Loading

Vulnerability to failure near point Q

Buckling is sudden & catastrophic, a

conservative approach near Q is desired

T is defined such that Pcr/A = Sy/2, giving


March 24, 2014 60

Condition for Use of Euler

Equation

(l/k) > (l/k)1, use Euler

equation

(l/k) ≤ (l/k)1, use a parabolic

curve between Sy & T


March 24, 2014 61

Intermediate-Length Columns

with Central Loading

Intermediate-length columns, (l/k) ≤ (l/k)1,

use a parabolic curve between Sy and T

General form of parabola


March 24, 2014 62

If parabola starts at Sy, then a = Sy

Intermediate-Length Columns

with Central Loading


March 24, 2014 63


M = -P(e+y)

d2y/dx2=M/EI


Fig. 4–20

March 24, 2014 64


Boundary conditions:

y = 0 at x = 0 and at x = l


March 24, 2014 65

At midspan where x = l/2


March 24, 2014 66


Max compressive stress:

Substituting Mmax from Eq. (4-48)


March 24, 2014 67


Using Syc as the maximum value of sc, and solving for P/A, we obtain the secant

column formula


March 24, 2014 68


Secant Column Formula

ec/k2 = eccentricity ratio


Fig. 4–21

March 24, 2014 69

Example 4-16

Develop specific Euler equations for the

sizes of columns having

a. Round cross sections

b. Rectangular cross sections


Example 4-17

Specify the diameter of a round column 1.5

m long that is to carry a maximum load

estimated to be 22 kN. Use a design factor

nd = 4 and consider the ends as pinned

(rounded). The column material selected

has a minimum yield strength of 500 MPa

and a modulus of elasticity of 207 GPa.


Example 4-18

Repeat Ex. 4–16 for J. B. Johnson columns.

(a) For round columns, Eq. (4–46) yields

(b) For round columns, Eq. (4–46) yields


Example 4-19

Choose a set of dimensions for a rectangular

link that is to carry a maximum compressive

load of 5000 lbf. The material selected has a

minimum yield strength of 75 kpsi and a

modulus of elasticity E = 30 Mpsi. Use a

design factor of 4 and an end condition

constant C = 1 for buckling in the weakest

direction, and design for

a. a length of 15 in

b. a length of 8 in with a minimum thickness

of 0.5 in. Dr. Mohammad Suliman Abuhaiba, PE

Struts or Short Compression

Members Strut: short member loaded in

compression

If eccentricity exists, max stress

is at B with axial compression

and bending.


March 24, 2014 74

Struts or Short Compression

Members Differs from secant equation in that it

assumes small effect of bending deflection

If bending deflection is limited to 1% of e,

then from Eq. 4-44, the limiting slenderness

ratio for strut is


March 24, 2014 75

Example 4-20

Figure 4–23a shows a workpiece clamped to

a milling machine table by a bolt tightened

to a tension of 2000 lbf. The clamp contact is

offset from the centroidal axis of the strut by

a distance e = 0.10 in, as shown in part b of

the figure. The strut, or block, is steel, 1 in

square and 4 in long, as shown. Determine

the maximum compressive stress in the

block.


Example 4-20


Fig. 4–23

HW Assignment #4-6

Problems: 4.107, 4.111

Due Saturday 29/3/2014

March 24, 2014


78


Weight falls from distance h and suddenly

applies a load to a cantilever beam

Find deflection and force applied to

beam due to impact


March 24, 2014 79


Abstract model considering

beam as simple spring

Table A-9: beam 1,

k= F/y =3EI/l3

Assume beam to be massless, so

no momentum transfer, just

energy transfer

Loss of potential energy from

change of elevation is

W(h + d) Dr. Mohammad Suliman Abuhaiba, PE

March 24, 2014 80


Increase in potential energy

from compressing spring is

kd 2/2

Conservation of energy

W(h + d) = kd 2/2


March 24, 2014 81

Maximum deflection

Maximum force


March 24, 2014 82


Chapter 4site.iugaza.edu.ps/mhaiba/files/2012/01/Ch-4-Deflection-and... · Chapter Outline Dr....

Documents

Transcript of Chapter 4site.iugaza.edu.ps/mhaiba/files/2012/01/Ch-4-Deflection-and... · Chapter Outline Dr....