multiple degree of freedom (mdof) systems
TRANSCRIPT
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Mohammad Tawfik
Multiple Degree of Freedom
Systems
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Multiple Degrees of Freedom
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Objectives
• What is a multiple degree of freedom system?
• Obtaining the natural frequencies of a multiple
degree of freedom system
• Interpreting the meaning of the eigenvectors of a
multiple degree of freedom system
• Understanding the mechanism of a vibration
absorber
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Two Degrees of Freedom
Systems
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Two Degrees of Freedom Systems
• When the dynamics of the system can be
described by only two independent
variables, the system is called a two
degree of freedom system
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Two Degrees of Freedom
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Free-Body Diagram
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Equations of Motion
)()()(
)()()()(
12222
1221111
txtxktxm
txtxktxktxm
0)()()(
0)()()()(
221222
2212111
txktxktxm
txktxkktxm
Rearranging:
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Initial Conditions
• Two coupled, second -order, ordinary
differential equations with constant
coefficients
• Needs 4 constants of integration to
solve
• Thus 4 initial conditions on positions
and velocities
202202101101 )0(,)0(,)0(,)0( xxxxxxxx
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In Matrix Form
)()(
)(,)()(
)(,)()(
)(2
1
2
1
2
1
txtx
ttxtx
ttxtx
t
xxx
22
221
2
1 ,0
0kkkkk
Km
mM
0xx KMWhere:
With initial conditions:
20
10
20
10 )0( ,)0(xx
xx
xx
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Recall: For SDOF
• The ODE is
• The proposed
solution:
• Into the ODE you get
the characteristic
equation:
• Giving:
0)()( tkxtxmtaetx )(
02 tt aemk
ae
mk
2mk
j
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Solving the system
• The ODE is
• The proposed
solution:
• Into the ODE you get
the characteristic
equation:
• Giving:
tjet ax )(
02 tjtj ee KaMa
0xx KM
02 tje aKM
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Giving:
02
1
aa
aEither:
Trivial solution;
No motion!
02 KMOR:
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Giving:
022
22
22112
kmk
kkkm
0)( 212
2212214
21 kkkmkmkmmm
Which can be solved as a quadratic equation in 2.
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NOTE!
• For spring mass systems, the resulting
roots are always positive, real, and distinct
• Which give two couples of distinct roots.
224,3
212,1 &
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Example
• m1=9 kg,m2=1kg,
k1=24 N/m and k2=3
N/m
• In Matrix form:
033327
1009
xx
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Example (cont’d)
• The proposed solution:
• Into the ODE you get the characteristic equation:
4-62+8=(2-2)(2-4)=0
• Giving:
2 =2 and 2 =4
tjet ax )(
Each value of 2 yields an expression for a:
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Calculating the corresponding
vectors a1 and a2
0a
0a
222
121
)(
)(
KM
KM
A vector equation for each square frequency
And:
4 equations in the 4 unknowns (each
vector has 2 components, but...
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Computing the vectors a
let 2,=For 12
111
21
aa
a
2 equations, 2 unknowns but DEPENDENT!
03 and 039
00
)2(333)2(927
)(-
12111211
12
11
21
aaaa
aa
KM 0a
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0a0a
a0a
u
1211
21
1121
1
21
121112
11
)()(
:arbitrary , does so ,)(
satisfies Suppose arbitrary. is magnitude The
.0 :because is This
!determined becan magnitude not the direction, only the
:equationsboth from 31
31
cKMcKM
ccKM
KM
aaaa
continued
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For the second value of 2:
31
aor 039
00
)4(333)4(927
)(-
have then welet 4,=For
22212221
22
21
21
22
212
22
aaa
aa
KM
aa
0a
a
Note that the other equation is the same
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What to do about the
magnitude!
11
11
31
222
31
112
a
a
a
a
Several possibilities, here we just fix one element:
Choose:
Choose:
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Thus the solution to the
algebraic matrix equation is:
1 ,2
1 ,2
31
24,2
31
13,1
a
a
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Return now to the time
response:
nintegratio of constants are and ,,, where
)sin()sin(
)(
)(
,,,)(
2121
22221111
21
2211
2211
2211
2211
2211
AA
tAtA
decebeaet
edecebeat
eeeet
tjtjtjtj
tjtjtjtj
tjtjtjtj
aa
aax
aaaax
aaaax
We have four solutions:
Since linear we can combine as:
determined by initial conditions
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Physical interpretation of all that
math! • Each of the TWO masses is oscillating at
TWO natural frequencies 1 and 2
• The relative magnitude of each sine term,
and hence of the magnitude of oscillation
of m1 and m2 is determined by the value of
A1a1 and A2a2
• The vectors a1 and a2 are called
mode shapes
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What is a mode shape?
• First note that A1,A2, 1 and 2 are
determined by the initial conditions
• Choose them so that A2 = 1 = 2 =0
• Then:
• Thus each mass oscillates at (one)
frequency 1 with magnitudes proportional
to a1 the1st mode shape
taa
Atxtx
t 112
111
2
1 sin)()(
)(
x
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Multiple Degrees of Freedom
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Things to note
• Two degrees of freedom implies two
natural frequencies
• Each mass oscillates at these two
frequencies present in the response
• Frequencies are not those of two
component systems
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Eigenvalues and Eigenvectors
• Can connect the vibration problem with the
algebraic eigenvalue problem
• This will give us some powerful
computational skills
• And some powerful theory
• All the codes have eigensolvers so these
painful calculations can be automated
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Compound Pendulum
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Pendulum Video
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Frequency Response
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Frequency Response
• Similar to SDOF systems, the frequency
response of a MDOF system is obtained by
assuming harmonic excitation.
• An analytical relation between all the possible
input forces and output displacements may be
obtained, called transfer function
• For our course, we will pay more attention to the
plot of the relation.
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Dynamic Stiffness
• The system of equations we obtain for an undamped vibrating system is always in the form
fKxxM • For harmonic excitation harmonic
response, we may write
fxKM 2fxKD
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Dynamic Stiffness
• Now, we have a system of algebraic
equations that may be solved for the
amplitude of vibration of each DOF as a
response to given harmonic excitation at a
certain frequency!
fKx D1
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Example
• For the three DOF system given in the
sketch, consider all stiffness values to be 2
and m1=2, m2=1, m3=3
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Example
• The equations of motion may be written in
the form:
3
2
1
3
2
1
3
2
1
420242
024
300010002
fff
xxx
xxx
FKxxM
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Example
• Getting the eigenvalues, and frequencies
796.0295.1241.2
,633.0000677.1000023.5
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Getting the Frequency Response
300010002
420242
0242DK
010
3
2
1
fff
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Notes:
• For all degrees of freedom, as the frequency reaches one of the natural frequencies, the amplitudes grows too much
• For some frequencies, and some degrees of freedom, the response becomes VERY small. If the system is designed to tune those frequencies to a certain value, vibration is absorbed: “Vibration absorber”
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Vibration Absorber
The first passive damping
technique we will learn!
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For a 2-DOF System
• For the shown 2-DOF
system, the equations
of motion may be
written as:
• Where:
fxx KM
2
1
ff
f
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For Harmonic Excitation
• We may write the
equation for each of
the excitation
frequency in the form
of:
• Then we may add
both solutions!
0
11 tCosfKM
xx
tCosf
KM22
0
xx
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Consider the first force
• We may write the
equation in the form:
• And the solution in
the form:
• Which will give:
tCosfKM 101
xx
tCosxx
2
1x
xx 2
2
12
tCosxx
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The equation of motion becomes
• Get x1() and find out when does it equal
to zero!
000 1
2
1
22
221
22
12 f
xx
kkkkk
mm
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Using the Dynamic Stiffness
Matrix • Writing down the dynamic stiffness matrix:
Getting the inverse:
01
2
1
222
2
22112 f
xx
KmKKKKm
01
2222
2211
2211
22
2222
2
1 f
KKmKKm
KKmKKKm
xx
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Obtaining the Solution
• Multiply the inverse by the right-hand-side
• For the first degree of freedom:
12
1222
212
212124
212
1 1fK
fKmKKKmKKmmmx
x
0
212
212124
21
1222
1
KKKmKKmmmfKm
x
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Vibration Absorber
• For the first degree of freedom to be
stationary, i.e. x1=0
• The excitation frequency have to satisfy:
• Note that this frequency is equal to the
natural frequency of the auxiliary spring-
mass system alone
2
2
mK
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Vibration absorber
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Vibration absorber
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Homework #2
• Repeat the example of this lecture using
f2=f3=0 and f1=1 AND f1=f2=0 and f3=1
• Plot the response of each mass for each
of the excitation functions
• Comment on the results in the lights of
your understanding of the concept of
vibration absorber
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Homework #2 (cont’d)
• Use modal decomposition
(diagonalization) to obtain the same
results.