Free Vibration -...
Transcript of Free Vibration -...
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Pertemuan – 6, 7
Multi Degree of Freedom System Free Vibration
Mata Kuliah : Dinamika Struktur & Pengantar Rekayasa Kegempaan
Kode : CIV – 308
SKS : 3 SKS
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TIU : Mahasiswa dapat menjelaskan tentang teori dinamika struktur.
Mahasiswa dapat membuat model matematik dari masalah teknis yang
ada serta mencari solusinya.
TIK : Mahasiswa mampu mendefinisikan derajat kebebasan, membangun
persamaan gerak sistem MDOF
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Sub Pokok Bahasan :
Penentuan derajat kebebasan
Properti matrik kekakuan, massa dan redaman
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Structures cannot always be described by a SDoF
model
In fact, structures are continuous systems and as such
possess an infinite number of DoF
There are analytical methods to describe the
dynamic behavior of continuous structures, which
are rather complex and require considerable
mathematical analysis.
For practical purposes to study Multi Degree of
Freedom System (MDoF), we shall consider the
multistory shear bulding model.
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A shear building may be defined as a structure in which there
is no rotation of a horizontal section at the level of the floors
Assumption for shear building
The total mass of the structure is concentrated at the
levels of the floors
The slabs/girders on the floors are infinitely rigid as
compared to the columns
The deformation of the structure is independent of the
axial forces present in the columns
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k1 k1
k2 k2
k3 k3
m2
m3
m1
u2
u3
u1
F1(t)
F2(t)
F3(t) F3(t)
k3(u3 u2)
m3ü3
F2(t)
k2(u2 u1)
m2ü2
k3(u3 u2)
F3(t)
k1u1
m1ü1
k2(u2 u1)
Shear Building w/ 3 DoF
Free Body Diagram
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By equating to zero the sum of the forces acting on each
mass :
Eq. (1) may conveniently be written in matrix notation as :
0
0
0
323333
223312222
11221111
tFuukum
tFuukuukum
tFuukukum
FuKuM (2)
(1)
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Where :
And :
3
2
1
00
00
00
m
m
m
M
33
3322
221
0
0
kk
kkkk
kkk
K
3
2
1
u
u
u
u
3
2
1
u
u
u
u
tF
tF
tF
F
3
2
1
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Natural Frequencies and Normal Modes EoM for MDoF system in free vibration is :
Solution of Eq. (3) is :
The substitution of Eq. (4) into Eq. (3) gives :
0 uKuM (3)
tsinBtcosAtqu nnnnnnn (4)
02 tqMK nnnn (5)
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The formulation of Eq (5) is known as an eigenvalue problem.
To indicate the formal solution to Eq. (5), it is rewritten as :
Eq (6) has non trivial solution if :
Eq.(7) gives a polynomial equation of degree n in n2, known
as characteristic equation of the system
02 nn MK (6)
A vibrating system with n DoF has n natural vibration frequencies n, arranged in
sequence from smallest to largest
0K2
Mn (7)
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The n roots of Eq. (7) determine the n natural frequencies n
of vibration.
These roots of the characteristic equation are also known as
eigenvalues
When a natural frequency n is known, Eq.(6) can be solved
for the corresponding vector n
There are n independent vectors , which are known as
natural modes of vibration, or natural mode shape of
vibration
These vectors are also known as eigenvector.
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Example 1
Determine :
1. The natural frequencies and
corresponding modal shapes
W1 = 11.600 kgf
4,5 m
W1
0x2
1
W2 = 24.000 kgf
u2
u1
3 m
W1
0x4
5
W1
0x2
1
W1
0x4
5
W10x21 I = 4,900 cm4
W10x45 I = 10,300 cm4
E = 2.106 kg/cm2
110385368090
2838 7610
2221
1211
21
,,
,,
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Tugas 6
Determine :
1. The natural frequencies and
corresponding modal shapes
W10x21 I = 4,900 cm4
W10x45 I = 10,300 cm4
E = 2.106 kg/cm2 W1 = 11.600 kgf
4,5 m
W1
0x2
1
W2 = 24.000 kgf
u2
u1
3 m
W1
0x4
5
W1
0x2
1
W1
0x4
5
W3 = 20.000 kgf
W1
0x2
1
W1
0x2
1 u3
3 m
11165742662085260
34315004155460
5339 6526 7,934
333231
232221
131211
321
,,,,,,
,,
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1
0,8526
0,5546
0 0
1
2
3
0 0,5 1 1,5
mode 1 1
-0,662
-1,004
0 0
1
2
3
-2 -1 0 1 2
mode 2 1
-2,6574
5,3431
0 0
1
2
3
-5 0 5 10
mode 3
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Modal & Spectral Matrices The N eigenvalues, N natural frequencies, and n natural
modes can be assembled compactly into matrices
nnnn
n
n
...............
...
...
21
22221
11211
2
22
21
2
n
Mode 1 2 n
DoF 1 2 ….. n
Modal matrix
Spectral matrix
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Orthogonality of Modes The natural modes corresponding to different natural
frequencies can be shown to satisfy the following
orthogonality conditions :
0
0
rT
n
rT
n
M
K
When n ≠ r
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Free Vibration Response : Undamped System
EoM for MDoF Undamped Free Vibration is :
The differential equation (8) to be solved had led to the
matrix eigenvalue problem of Eq.(6).
The general solution of Eq. (8) is given by a superposition of
the response in individual modes given by Eq. (4).
Or
0 uKuM (8)
nn q...qqqu 332211
qu
(9)
(10)
N
nnn
qu1
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Premultiply Eq. (10) with {n}T[M] :
Regarding the orthogonality conditions :
From which :
also
nT
nT
n qMuM (11)
nn
T
n
T
nqMuM
NN
T
n
T
n
T
n
qM
....qMqM
2211
n
T
n
T
n
nM
uMq
n
T
n
T
n
nM
uMq
(11)
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If Eq. (8) is premultiplied by the transpose of the nth mode-
shape vector {n}T, and using Eq.(10) with its second
derivative it becomes :
Eq.(11) is an EoM from SDoF Undamped System for mode n,
which has solution :
0nn
T
nnn
T
nqKqM
Mn Kn
(11)
Generalized mass Generalized stiffness
tsinq
tcosqtqn
n
n
nnn
00
(12)
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Solution for Eq. (8) becomes :
The procedure described above can be used to obtain an
independent SDoF equation for each mode of vibration of
the undamped structure.
This procedure is called the mode-superposition method
N
nn
n
n
nnntsin
qtcosqu
1
00
(13)
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Gaya pegas tiap lantai dari masing-masing
mode dapat dicari dengan persamaan :
uMuKf ns
2
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Example 2
Based on data from Example 1, and the
following initial condition, for each DoF plot
the time history of displacement, regarding
the 1st, and 2nd mode contribution.
mu t
3
3
0 108
106
m/s0,20
00
tu
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Tugas 7
Based on data from Assignment 6, and the
following initial condition, for each DoF
plot the time history of displacement,
regarding the 1st, 2nd , and 3rd mode
contribution.
Also plot the time history of spring
force
W1 = 11.600 kgf
4,5 m
W1
0x2
1
W2 = 24.000 kgf
u2
u1
3 m
W1
0x4
5
W1
0x2
1
W1
0x4
5
W10x21 I = 4,900 cm4
W10x45 I = 10,300 cm4
E = 2.106 kg/cm2
W3 = 20.000 kgf
W1
0x2
1
W1
0x2
1 u3
3 m
cm,,,
u t
018060
0 cm/s0200
0
tu
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Free Vibration Response : Damped System
EoM for MDoF Damped Free Vibration is :
Using Eq. (10) and its derivative :
Premultiply Eq. (15) with {}T :
0 uKuCuM (14)
(15)
(16)
0 qKqCqM
0 qKqCqMTTT
Mn Cn Kn
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Eq.(16) is an EoM from SDoF Damped System for mode n,
which has solution :
The displacement response of the system is then obtained by
substituting Eq. (17) in Eq. (10)
tsin
qqtcosqetq
nD
nD
nnnn
nDn
t
n
nn
00
0
(17)
tsinqq
tcosqetunD
nD
nnnn
nDn
tN
nn
nn
00
01
(18)