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MULTI DEGREE OFFREEDOM (M-DOF)
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Outline-Part 2
1 Using Newtons Second Law to derive
Equations of Motion
2 Influence Coefficients
3 Eigenvalue problem
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Using Newtons 2nd Law to deriveEquations of Motion
Step 1: Set up suitable coordinates to describe
positions of the various masses in the system.
Step 2: Measure displacements of the massesfrom their static equilibrium positions
Step 3: Draw free body diagram and indicateforces acting on each mass
Step 4: Apply Newtons 2nd
Law to each mass
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Example 1
Derive the equations of motion of the spring-
mass damper system shown below.
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Solution
Free-body diagram is as shown:
Applying Newtons 2nd Law gives:
Set i=1 with x0=0and i=nwith xn+1=0:
( ) ( ) ( ) ( ) 1,...,3,2,111111
=+++=++++
niFxxcxxcxxkxxkxm iiiiiiiiiiiiiii &&&&&&
( ) ( )
( ) ( ) nnnnnnnnnnnnn Fxkxkkxcxccxm
Fxkxkkxcxccxm
=++++
=++++
++ 1111
1221212212111
&&&&
&&&&
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Solution
Notes:
The equations of motion canbe expressed in matrix form:
[m] is the mass matrix
[c] is the damping matrix [k] is the stiffness matrix
[ ] [ ] [ ] Fxkxcxmrr&r&&r
=++
[ ]
=
nm
m
m
m
0...0
0
00
0...0
2
1
OM
M
[ ] [ ] ( )( )
( )
( )( )
( )
=
=
+
+
+
+
=
+
+
+
=
+
+
tF
tFtF
F
tx
txtx
x
kkk
kkkkkkk
kkk
k
ccc
cccc
ccc
c
nnn
nnn
3
2
1
3
2
1
1
433
3322
221
1
3322
221
,,
000
0
0000
00
,000
00
rr
OO
L
MM
M
M
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Influence Coefficients
One set of influence coefficients is
associated with each matrix involved in theequations of motion
Equation of Motion Influence coefficient
Stiffness matrix Stiffness influencecoefficient
Mass matrix Inertia influence coefficient
Inverse stiffnessmatrix
Flexibility influencecoefficient
Inverse mass matrix Inverse inertia coefficient
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Stiffness Influence Coefficient, kij
kij is the force at point idue to unit
displacement at pointjand zero displacementat all other points.
Total force at point i,
Matrix form:
=
==
n
j
jiji nixkF1
,...,2,1,
[ ] [ ]
==
nnnn
n
n
kkk
kkk
kkk
kxkF
...
...
...
where
21
22221
11211
MM
rr
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Stiffness Influence Coefficient, kij
Note:
kij= kji
kij for torsional systems is defined as thetorque at point idue to unit angular
displacement at pointjand zero angulardisplacements at all other points.
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Example 2
Find the stiffness influence coefficients of the
system shown below.
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Solution
Let x1, x2and x3be the displacements of m1, m2 and
m3 respectively.
Set x1=1 and x2=x3=0.
Horizontal equilibrium of forces:
Mass m1: k1= -k2+ k11 (E1)
Mass m2: k21= -k2 (E2)
Mass m3: k31 = 0 (E3)
Solving E1 to E3 gives k11=k1+k2
k21= -k2
k31
= 0
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Solution
Next set x2=1 and x1=x3=0.
Horizontal equilibrium of forces: Mass m1: k12 + k2 = 0 (E4)
Mass m2: k22 -k3 = k2 (E5)
Mass m3: k32 = -k3 (E6) Solving E4 to E6 gives
k22 = k2+k3
k12 = -k2k32 = -k3
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Solution
Finally set x3=1 and x1=x2=0.
Horizontal equilibrium of forces: Mass m1: k13 = 0 (E7)
Mass m2: k23 + k3 = 0 (E8)
Mass m3: k33 = k3 (E9)
Solving E7 to E9 givesk33 = k3k13 = 0
k23 = -k3
Thus the stiffness matrix is:[ ]
+
+
=
33
3322
221
0
0
kk
kkkk
kkk
k
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Flexibility Influence Coefficient,aij
Have to solve n sets of linear equations to
obtain all the kijs in an n DOF system
Generating aijs is simpler.
aij is defined as the deflection at point i due tounit load at pointj,
xij= aijFj, where xij is the displacement at
point i due to external force Fj
Matrix form:
==
===
n
j
jij
n
j
iji niFaxx11
,...,2,1,
[ ]Faxrr
=
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Flexibility Influence Coefficient,aij
Note:
Stiffness and flexibility matrices are theinverse of each other.
aij= aji
aijfor torsional systems is defined as theangular deflection of point idue to unit torque
at pointj.
[ ] [ ] [ ] [ ] 11, == kaak
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Example 3
Find the flexibility influence coefficients of the
system shown below.
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Solution
Let x1, x2and x3be the displacements of m1,
m2 and m3 respectively.
Set F1=1 and F2=F3=0.
Horizontal equilibrium of forces:
Mass m1: k1a11= k2(a21 a11) + 1 (E1)
Mass m2: k2(a21 a11) = k3(a31 a21) (E2) Mass m3: k3(a31 a21) = 0 (E3)
Solving E1 to E3 gives a11 = a21 = a31 = 1/k1
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Solution
Next set F2=1 and F1=F3=0.
Horizontal equilibrium of forces:
Mass m1: k1a12 = k2(a22 a12) (E4) Mass m2: k2(a22 a12) = k3(a32 a22) +1 (E5)
Mass m3: k3(a32 a22) = 0 (E6)
Solving E4 to E6 gives a12 = 1/k1
a22 = a32 = 1/k1 + 1/k2
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Solution
Next set F3=1 and F1=F2=0.
Horizontal equilibrium of forces:
Mass m1: k1a13 = k2(a23 a13) (E7) Mass m2: k2(a23 a13) = k3(a33 a23) (E8)
Mass m3: k3(a33 a23) = 1 (E9)
Solving E7 to E9 gives a13 = 1/k1
a23 = 1/k1 + 1/k2
a33 = 1/k1 + 1/k2 + 1/k3
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Eigenvalue Problem
(Eigenvalue problem)
For a non-trivial solution, determinant ofthe coefficient matrix must be zero.
i.e. = |kij-2mij| = |[k]- 2[m]| =0(Characteristic equation)
2 is the eigenvalue
[ ] [ ][ ] 02rr
= Xmk
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Solution of the Eigenvalue Problem
Eigenvalue problem:
Multiplying by [k]-1:
[I] is identity matrix [D]=[k]-1[m] is dynamical matrix.
For a non-trivial solution of
characteristic determinant =|[I]-[D]|=0
Use numerical methods to solve if DOF ofsystem is large
[ ] [ ][ ]2
10
== whereXmkrr
[ ] [ ][ ] [ ] [ ]XDXXDIrrrr
== Ior0
,Xr
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Example 4
Find the natural frequencies and mode
shapes of the system shown below fork1=k2=k3=k and m1=m2=m3=m
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Solution
Dynamical matrix [D]=[k]-1[m] [a][m]
Flexibility matrix
Mass matrix
Thus
[ ]
=
321
221
1111
ka
[ ]
=
100
010
001
mm
[ ]
=
321
221111
k
mD
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Solution
Frequency equation:
=|[I]-[D]|=
Dividing throughout by ,
2
1where0
321
221
111
00
00
00
==
k
m
km
km
2
23 where0165
31
2
2
21
1
===+=
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Solution
Once the natural freq are known, the
eigenvectors can be calculated using
m
k
k
m8025.1,2490.3 3
2
33 ===
m
k
k
m2471.1,5553.1 2
2
22 ===
m
k
k
m44504.0,19806.0 1
2
11 ===
[ ] [ ][ ] ( ) ( )
( )
( )
( )
(E1)where3,2,1,0
3
2
1
===
i
i
i
ii
i
X
X
X
XiXDIrrr
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Solution
1st mode: Substitute 1=5.0489 into (E1):
3 unknowns X1(1),X2(1), X3(1) in 3 equations
Can express any 2 unknowns in terms of the
remaining one.
( )
( )
( )
=
0
00
321
221111
100
010001
0489.51
3
1
2
1
1
X
XX
k
m
k
m
k
m
( )
( )
( )
=
0
0
0
0489.221
20489.31
110489.4
..1
3
1
2
11
X
X
X
ei
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Solution
X2(1) + X3(1) = 4.0489 X1(1)
3.0489X2(1) 2X3(1) = X1(1)
Solving the above, we get
X2(1)
=1.8019X1(1)
and X3(1)
=2.2470X1(1)
Thus first mode shape
where X1(1) can be chosen arbitrarily.
( ) ( )
=
2470.2
8019.1
11
1
1XX
r
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Solution
2nd mode: Substitute 2=0.6430 into (E1):
3 unknowns X1(2),X2(2), X3(2) in 3 equations
Can express any 2 unknowns in terms ofthe remaining one.
k
m
( )
( )
( )
=
0
0
0
321
221
111
100
010
001
6430.02
3
22
2
1
X
X
X
km
km
( )
( )
( )
=
0
0
0
3570.221
23570.11
113570.0
..2
3
22
2
1
X
X
X
ei
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Solution
X2(2) X3(2) = 0.3570X1(2)
-1.3570X2(2) 2X3(2) = X1(2)
Solving the above, we get
X2(2)
=0.4450X1(2)
and X3(2)
=-0.8020X1(2)
Thus 2nd mode shape
where X1(2) can be chosen arbitrarily.
( ) ( )
=
8020.0
4450.0
12
1
2XX
r
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Solution
3rd mode: Substitute 3=0.3078 into (E1):
3 unknowns X1(3),X2(3), X3(3) in 3 equations
Can express any 2 unknowns in terms of the
remaining one.
( )
( )
( )
=
0
0
0
321
221
111
100
010
001
3780.03
3
3
2
3
1
X
X
X
k
m
k
m
( )
( )
( )
=
0
0
0
6922.221
26922.11
116922.0
..3
3
3
2
3
1
X
X
X
ei
k
m
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Solution
-X2(3) - X3(3) = 0.6922X1(3)
-1.6922X2(3) 2X3(3) = X1(3)
Solving the above, we get
X2(3)
=-1.2468X1(3)
and X3(3)
=0.5544X1(3)
Thus 3rd mode shape
where X1(3) can be chosen arbitrarily.
( ) ( )
=
5544.0
2468.1
13
1
3XX
r
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Solution
When X1(1) = X1(2) =
X1(3) =1, the modeshapes are as follows: