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Ch. 3: Forced Vibration of 1-DOF System
3.0 Outline
Harmonic ExcitationFrequency Response FunctionApplicationsPeriodic ExcitationNon-periodic Excitation
3.0 Outline
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
Force input function of the harmonic excitation is theharmonic function, i.e. functions of sines and cosines. This type of excitation is common to many systeminvolving rotating and reciprocating motion. Moreover,many other forces can be represented as an infiniteseries of harmonic functions. By the principle ofsuperposition, the response is the sum of the individual harmonic response.
It is more convenient to use the frequency domaintechnique in solving the harmonic excitation problems.This is because the response to differentexcitation frequencies can be seen in one graph.
3.1 Harmonic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
( )( )
0
20 0 0
0
20
Let us focus on the particular solution ofcos
normalize the equation of motion2 cos , /
Re
solve for from 2
and the solution
n n
i t
i tn n
mx cx kx F t
x x x f t f F m
f t f e
z t z z z f e
ω
ω
ω
ζω ω ω
ζω ω
+ + =
+ + = =
⎡ ⎤= ⎣ ⎦∴ + + =
( ) ( ) ( )
( ) ( ) ( )( ) ( )
( )
2 20
is the real part of ; Re
Assume the solution to have the same form as the forcing function same frequency as the input w/ different mag. and phase
2
i t
i t i tn n
z t x t z t
z t Z i e
i Z i e f e
fZ i
ω
ω ω
ω
ω ζωω ω ω
ω
= ⎡ ⎤⎣ ⎦
=
− + + =
=( )
( )
20 0
22 2
02
/2 1 / 2 /
1 / 2 /
n
n n n n
n n
fi i
Fk i
ωω ω ζωω ω ω ζω ω
ω ω ζω ω
=− + − +
=⎡ ⎤− +⎣ ⎦
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
( ) ( )
( )
( ) ( )
( ) ( ) ( )
( )( ) ( )
002
02
2
0
2 22
12
1 2
Re , /1 2
1If is the frequency response1 2
cos
1where magnitude1 2
2tan phas1
i t i t
i tn
i
Fz t e H i F ek r i r
Fx t e rk r i r
H i H i ek r i r
x t F H i t
H ik r r
rr
ω ω
ω
θ
ωζ
ω ωζ
ω ωζ
ω ω θ
ωζ
ζθ −
= =⎡ ⎤− +⎣ ⎦
⎡ ⎤⎢ ⎥∴ = =
⎡ ⎤− +⎢ ⎥⎣ ⎦⎣ ⎦
= =⎡ ⎤− +⎣ ⎦
∴ = +
= =− +
−= =
−
( ) ( )
e
The system modulates the harmonic input by
the magnitude and phase H i H iω ω
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
( ) ( )( ) ( ) ( ) ( )( )
1 2
0
1
total response homogeneous soln. particular soln.Recall the homogeneous solution of the underdamped system
cos or sin cos
cos cos
or
n n
n
n
t th d h d d
td
t
x Ce t x e A t A t
x t Ce t F H i t
x t e A
ζω ζω
ζω
ζω
ω φ ω ω
ω φ ω ω θ
− −
−
−
= +
= − = +
∴ = − + +
= ( ) ( ) ( )2 0
1 2
sin cos cos
The initial conditions will be used to determine , or ,They will be different from those of free responsebecause the transient term now is partly due to the excitatio
d dt A t F H i t
C A A
ω ω ω ω θ
φ
+ + +
n force
and partly due to the initial conditions
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
Ex. 1 Compute and plot the response of a spring-masssystem to a force of magnitude 23 N, drivingfrequency of twice the natural frequency and i.c.given by x0 = 0 m and v0 = 0.2 m/s. The massof the system is 10 kg and the spring stiffnessis 1000 N/m.
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
( )
( ) ( )( )( )
( )
32 2
31 2
31 2
2
/ 1000 /10 10 rad/s/ 2 0
2 10 20 rad/s1 1 0.333 10
1 2 1000 1 2
sin cos 23 0.333 10 cos
cos sin 23 0.333 10 sin
i.c. 0 0 23 0.333 10
n
n
n n
n n n n
k mc m
H ik r i r
x t A t A t t
x t A t A t t
x A
ωζ ωω
ωζ
ω ω ω
ω ω ω ω ω ω
−
−
−
= = =
= =
= × =
= = = − ×⎡ ⎤− + × −⎣ ⎦
= + − × ×
= − + × × ×
= = − × ×
( )( ) ( )
3 32
1 1
3
, 7.667 10
0 0.2 10 , 0.02
0.02sin10 7.667 10 cos10 cos 20 m
A
x A A
x t t t t
− −
−
= ×
= = × =
∴ = + × −
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
Ex. 2 Find the total response of a SDOF system withm = 10 kg, c = 20 Ns/m, k = 4000 N/m, x0 = 0.01 m,v0 = 0 m/s under an external force F(t) = 100cos10t.
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
( )
( ) ( )( ) ( ) ( ) ( )
( ) ( )( )
2 2
0
21 2
1
/ 20 rad/s/ 2 0.05/ 0.5
1 1 332.6 6 0.06661 2 4000 1 0.5 2 0.05 0.5
cos 33.26 3cos 10 0.0666
sin cos , 1 19.975 rad/s
s
n
n
n
n
n
p
th d d d n
t
k mc m
r
H i Ek r i r i
x t F H i t E t
x t e A t A t
x t e A
ζω
ζω
ωζ ω
ω ω
ωζ
ω ω θ
ω ω ω ω ζ−
−
= =
= =
= =
= = = − −⎡ ⎤− + × − + × ×⎣ ⎦
= + = − −
= + = − =
= ( ) ( ) ( )( ) ( ) ( )
( ) ( )
2 0
1 2 1 2
0
in cos cos
sin cos cos sin
sin
n n
d d
t tn d d d d d d
t A t F H i t
x t e A t A t e A t A t
F H i t
ζω ζω
ω ω ω ω θ
ζω ω ω ω ω ω ω
ω ω ω θ
− −
+ + +
= − + + −
− +
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
ωresponse finally becomes ω, and in phase
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
ωresponse finally becomes ω, and out of phase
Ch. 3: Forced Vibration of 1-DOF System
3.1 Harmonic Excitation
F0ωnt/(2k)
( ) ( )
( ) 0
In case of 0 and , the guess solution of the form
cos sin is invalid. This is becauseit has the same form as the homogeneous solution.
The correct particular solution is
ni t
np
x t X i e A t B t
Fx t
ω
ζ ω ω
ω ω ω
ω
= =
= = +
= sin .2 n
t tk
ω
Ch. 3: Forced Vibration of 1-DOF System
Beat when the driving frequency is close to natural freq.
3.1 Harmonic Excitation
( ) ( )0 00 2 2
2 2 20 0 1 0 0
2 20
The total solution can be arranged in the form
sin cos cos cos
2 sin tan sin sin2 2
If the system is at rest in
n n nn n
n n n nn
n n
v fx t t x t t t
x v x ft t tv
ω ω ω ωω ω ω
ω ω ω ω ω ωωω ω ω
−
= + + −−
+ ⎛ ⎞ − +⎛ ⎞ ⎛ ⎞= + +⎜ ⎟ ⎜ ⎟ ⎜ ⎟− ⎝ ⎠ ⎝ ⎠⎝ ⎠
( ) 02 2
02 2
the beginning,2 sin sin
2 2
The response oscillates with frequency inside2
2the slowly oscillated envelope sin2
The beat frequency is
n n
n
n
n
n
n
fx t t t
f t
ω ω ω ωω ω
ω ω
ω ωω ω
ω ω
− +⎛ ⎞ ⎛ ⎞= ⎜ ⎟ ⎜ ⎟− ⎝ ⎠ ⎝ ⎠+
−⎛ ⎞⎜ ⎟− ⎝ ⎠
∴ −
Ch. 3: Forced Vibration of 1-DOF System
Beat when the driving frequency is close to natural freq.
3.1 Harmonic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.2 Frequency Response Function
3.2 Frequency Response Function
( ) ( )2
The core of the particular solution to the harmonic function is1 ; frequency response function
1 2
It specifies how the system responds to harmonic excitation.As a standard, we normalize the
H ik r i r
ωζ
=− +
( ) 2
frequency response function1 and then study how it varies as the
1 2excitation frequency and system parameters , vary.It is indeed more convenient since we already normalized the frequen
n
G ir i r
ωζω ζ ω
=− +
( )( )
cy;/ . So we can now study its variation to and .
For the fixed damping ratio, we plot with varies.
has both magnitude and phase magnitude and phase plot.
Then we repeatedly evaluate
nr rG i r
G i
G i
ω ω ζω
ω
=
⇒
( ) by varying .ω ζ
Ch. 3: Forced Vibration of 1-DOF System
3.2 Frequency Response Function
Frequency response plot(Bode diagram)
( )( ) ( )2 22
1
1 2H i
r rω
ζ=
− +
12
2tan1
rrζθ − −⎛ ⎞= ⎜ ⎟−⎝ ⎠
Ch. 3: Forced Vibration of 1-DOF System
Resonance is defined to be the vibration response atω=ωn, regardless whether the damping ratio is zero.At this point, the phase shift of the response is –π/2.
The resonant frequency will give the peak amplitude for the response only when ζ=0. For ,the peak amplitude will be at , slightly before ωn.For , there is no peak but the max. value of theoutput is equal to the input for the dc signal (of course, for this normalized transfer function).
3.2 Frequency Response Function
21 2nω ω ζ= −0 1/ 2ζ< <
1/ 2ζ ≥
Ch. 3: Forced Vibration of 1-DOF System
3.2 Frequency Response Function
Ex. 3 Consider the pivoted mechanism with k=4x103 N/m,l1=0.05 m, l2=0.07 m, l=0.10 m, and m=40 kg.The mass of the beam is 40kg which is pivotedat point O and assumed to be rigid. Calculate cso that the damping ratio of the system is 0.2.Also determine the amplitude of vibration of thesteady-state response if a 10 N force is appliedto the mass at a frequency of 10 rad/s.
Ch. 3: Forced Vibration of 1-DOF System
( ) ( )
( )
12 2 1 1
2 212 1
2
12 2
0.1 10cos10 0.5 0.0049 59.050.004915.37, 0.2 , 627.3 Ns/m
2 0.5
O O
nn
l lM I Fl mgl Mg c l l k l l
l l l lml M M
t cc c
θ θ θ θ θ
θ
θ θ θ
ω ζω
ω
−⎛ ⎞⎡ ⎤= − − − −⎜ ⎟⎣ ⎦ ⎝ ⎠⎡ ⎤+ −⎛ ⎞= + +⎢ ⎥⎜ ⎟
⎝ ⎠⎢ ⎥⎣ ⎦× = + +
= = = =× ×
=
∑
( ) ( )( )
10, 0.65061 0.02677 24.268
59.05 0.5767 0.26
0.02677 cos 10 0.424ss
r
H ii
t
ω
θ
=
= = − °+
= −
3.2 Frequency Response Function
Ch. 3: Forced Vibration of 1-DOF System
Ex. 4 A foot pedal for a musical instrument is modeledas in the figure. With k=2000 kg/s2, c=25 kg/s,m=25 kg, and F(t)=50cos2πt N, compute thesteady-state response assuming the system startsfrom rest. Use the small angle approximation.
3.2 Frequency Response Function
Ch. 3: Forced Vibration of 1-DOF System
( ) ( )
( ) ( )
2
2
0.15 0.05 0.05 0.05 0.1 0.15
5 1003.75 50cos 2 , positive CW6 3
Find the parameters2.98, 0.0373, 2 , 2.108
1 0.0087 177.41 2
since 0, the transie
O O
n
M I F k c m
t
r
H ik r i r
θ θ θ θ
θ θ θ π
ω ζ ω π
ωζ
ζ
⎡ ⎤= × − × − × = ×⎣ ⎦
+ + =
= = = =
= = − °− +
≠
∑
( ) ( ) ( )0
nt response will die out
cos 0.435cos 2 3.096ss F H i t tθ ω ω θ π= + = −
3.2 Frequency Response Function
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
Ch. 3: Forced Vibration of 1-DOF System
3.3 Applications
( ) ( )
( ) ( )
2
2 22
2 22
2
2
2
measured acc. 10 1actual acc. 9.81 1 2
1 2 0.962
From the problem statement, 628 rad/s, 1 628 rad/s
11
758 rad/s , 0.5621
5745.6 N/m, 8.49 Ns/
n
d n
d
dn
n
zy r r
r r
r
k cm m
k c
ω
ζ
ζ
ω ω ω ζωω ζ
ωω ζωζ
= = =− +
− + =
= = − =
= =−
= = = = =−
= = m
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
A periodic function is any function that repeats itself in time, called period T.
It is more general than the harmonic function. Here, wewill find the response to the input that is a periodic function. The idea is to decompose that periodic inputinto the sum of many harmonics. The response, by thesuperposition principle of linear system, is then the sum of the responses of individual harmonic. The response of a harmonic function was studied in section 3.1
3.4 Periodic Excitation
( ) ( )f t f t T= +
Ch. 3: Forced Vibration of 1-DOF System
Fourier found the way to decompose the periodicfunction into sum of harmonic functions (sine & cosine)whose frequencies are multiples of the fundamental frequency. The fundamental frequency is the frequency of the periodic function.
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
Fourier series
3.4 Periodic Excitation
( ) ( )
( )
( )
( ) 0
00 0 0
1
00
00
Fourier series in real form:2cos sin ,
2Fourier coefficients:
2 cos , 0,1, 2,
2 sin , 1, 2,3,
Fourier series in complex form:
n nn
T
n
T
n
in tn
n
af t a n t b n tT
a f t n t dt nT
b f t n t dt nT
f t C e ω
πω ω ω
ω
ω
∞
=
∞
=−∞
= + + =
= =
= =
=
∑
∫
∫
…
…
( ) 0
0
0
2,
Fourier cofficients (complex):
1 , , 2, 1,0,1, 2,T
in tn
T
C f t e dt nT
ω
πω
−
=
= = − −
∑
∫ … …
Ch. 3: Forced Vibration of 1-DOF System
Some properties of Fourier series
3.4 Periodic Excitation
) ( )) ( )
) ( )
) ( ) ( ) 0
0
01
1 If is an even function, 0.
2 If is an odd function, 0.
3 is the average value of over one period.2
4 If is real, 2Re
n
n
in tk k n
n
f t b
f t aa f t
f t C C f t C C e ω∞
−=
=
=
⎛ ⎞= ⇒ = + ⎜ ⎟⎝ ⎠∑
Ch. 3: Forced Vibration of 1-DOF System
Frequency spectrum tells how much each harmoniccontributes to the periodic function .
Plot of the amplitude of each harmonic vs. its frequencyis the (discrete) frequency spectrum.
3.4 Periodic Excitation
( )f t
( )
2 20
0
In real form, the harmonic at has the amplitude
In complex form, the harmonic at has the amplitude 2 Re n n
n
n a b
n C
ω
ω
+
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
Superposition principle of linear system
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
Response to harmonic excitation
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
( )( )
( )
( )
( )
0
0
0
0
0
0 2
0 0
01
00
1
From section 3.1, 1where
1 2
2 Re
by superposition, 2Re
in tn
in tss n
n n
in tn
n
in tss n
n
mx cx kx F t C e
x C H in e
H inn nk i
mx cx kx F t C C e
Cx C H in ek
ω
ω
ω
ω
ω
ωω ωζω ω
ω
∞
=
∞
=
+ + = =
=
=⎛ ⎞⎛ ⎞ ⎛ ⎞⎜ ⎟− +⎜ ⎟ ⎜ ⎟⎜ ⎟⎝ ⎠ ⎝ ⎠⎝ ⎠
⎛ ⎞+ + = = + ⎜ ⎟⎝ ⎠⎛= +⎝
∑
∑ ⎞⎜ ⎟
⎠
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
response frequency spectrumexcitation frequency spectrum
system frequency response
Ch. 3: Forced Vibration of 1-DOF System
Ex. Calculate the response of a damped system tothe periodic excitation f(t) depicted in the figureby means of the exponential form of the Fourierseries. The system damping ratio is 0.1 and thedriving frequency is ¼ of the system natural freq.
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
( )
( )
( )
( )
( )
0
0 0 0
0
/2
00 0 /2
odd
Expand as sum of harmonic series
1 1 2 ,
0, even1 1 2 , odd
2 2
in tn
n
T T Tin t in t in t
nT
nn
i nin t
n
f t
f t C e
C f t e dt Ae dt Ae dtT T T
niAC i An n
n
i A Af t e en n
ω
ω ω ω
ωω
πω
ππ
π π
∞
=−∞
− − −
=
=
⎡ ⎤= = + − =⎢ ⎥
⎣ ⎦=⎧
⎪⎡ ⎤= − − = ⎨⎣ ⎦ − =⎪⎩
∴ = − × = ×
∑
∫ ∫ ∫
∑
( )
( )( )
( ) ( ) ( )
( ) ( )
0 20odd
1,3,
02
2
1222 2
01,3,
4 1 sin
1 , 0.1, 1 2 4
11 / 4 0.05
1 0.05, tan1 0.251 0.25 0.05
4 1 sin
t
nn
nn n
n
n n
ss n nn
A n tn
n nG i rr i r
G in i n
nG Gnn n
Ax t G n t Gn
π
ωπ
ωωω ζζ ω ω
ω
ωπ
⎛ ⎞ ∞−⎜ ⎟⎝ ⎠
==
−
∞
=
=
= = = = =− +
=− +
−= =
−⎡ ⎤− +⎣ ⎦
∴ = +
∑ ∑
∑
…
…
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
Ex. The cam and follower impart a displacement y(t)in the form of a periodic sawtooth function to thelower end of the system. Derive an expressionfor the response x(t) by means of Fourier analysis.
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
( )
( )
( )
( ) ( )
( )
0
0
2 1
1 21 2 2
0
0
FBD and assume
, , 2
Write in the Fourier series expansion
2, , , 0
1 1
x x
nn
in tn
n
Tin t
n
y x
F ma mx k y x k x cx
k k cmx cx k k x k ym m
y t
Ay t C e y t B t t TT T
C y t e dt BeT T
ω
ω
ω ζω
πω∞
=−∞
− −
>
⎡ ⎤= = − − −⎣ ⎦
++ + + = = =
= = = + ≤ ≤
= =
∑
∑
∫
( )
0 0
0 0
2
2 2
22
00
0
1
Integration formula: and 1
2 1 , 02 22
2
T Tin t in t
ax axax ax
TT
in t in tT T
n
Adt te dtT T
e ee dx c xe dx ax ca a
B e A e iAC in t nT T T nin inT T
AC B
ω ω
π π
ππ ππ
−
− −
+
= + = − +
⎡ ⎤⎡ ⎤ ⎢ ⎥⎢ ⎥ ⎛ ⎞⎢ ⎥= + − − = ≠⎢ ⎥ ⎜ ⎟⎢ ⎥⎝ ⎠⎛ ⎞⎢ ⎥− −⎢ ⎥⎜ ⎟⎣ ⎦ ⎝ ⎠⎣ ⎦
= +
∫ ∫
∫ ∫
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
( ) ( )
( )
( )( )
( )( )
( )
0 01
01
21 2
2
0 01 2
22
0 01 2
2 Re cos sin2 2
1 sin2
1Frequency response 1 2
1
1 2
1
1 2
n
n
n
n
n n
n
n n
A iAy t B n t i n tn
A Ay t B n tn
H ik k r i r
H in nk k i
Hn nk k
ω ωπ
ωπ
ωζ
ωω ωζω ω
ω ωζω ω
∞
=
∞
=
⎡ ⎤∴ = + + +⎢ ⎥⎣ ⎦
= + −
=⎡ ⎤+ − +⎣ ⎦
=⎡ ⎤⎛ ⎞ ⎛ ⎞⎢ ⎥+ − +⎜ ⎟ ⎜ ⎟⎢ ⎥⎝ ⎠ ⎝ ⎠⎣ ⎦
=⎛ ⎞⎛ ⎞⎜ ⎟+ − +⎜ ⎟⎜ ⎟⎝ ⎠⎝ ⎠
∑
∑
( ) ( )
0
12
20
2 20
11 2
2, tan
1
1 sin2
nn
n
ss n nn
n
Hn
k k AAx t B H n t Hk k n
ωζω
ωω
ωπ
−
∞
=
⎛ ⎞− ⎜ ⎟
⎝ ⎠=⎛ ⎞⎛ ⎞⎛ ⎞ − ⎜ ⎟⎜ ⎟⎜ ⎟ ⎝ ⎠⎝ ⎠⎝ ⎠
⎛ ⎞= + − +⎜ ⎟+ ⎝ ⎠∑
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.4 Periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
Harmonic and steady-state excitation and response are conveniently described in the frequency domain. Fordeterministic non-periodic excitation and response, timedomain technique is more suitable.
We cannot find the repeated pattern that lasts forever (both in the past & future) for the non-periodic excitation.
System response to the unit impulse, called the impulse response, will be first studied. Then, this fundamentalresponse will be used to synthesize the response of theLTI system to arbitrary excitation.
3.5 Non-periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
Impulse
The unit impulse, or Dirac delta function, is defined as
This means that the unit impulse is zero everywhereexcept in the neighborhood of t=a. Since the areaunder the graph δ-t is 1, the value of is very large in the vicinity of t=a.The impulse of magnitude , which may represent alarge force acting over a short period, can be written as
3.5 Non-periodic Excitation
( )
( )
0 for
1
t a t a
t a dt
δ
δ∞
−∞
− = ≠
− =∫
( )t aδ −
F̂
( ) ( )ˆF t F t aδ= −
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
The unit impulse has a useful property called the“sampling property”. Multiplying a continuous function
by , and integrating w.r.t. time:
which is just the value of f(t) at t=a. This is a way inevaluating integrals involving with impulse.
3.5 Non-periodic Excitation
( )f t ( )t aδ −
( ) ( ) ( ) ( ) ( )f t t a dt f a t a dt f aδ δ∞ ∞
−∞ −∞
− = − =∫ ∫
Ch. 3: Forced Vibration of 1-DOF System
Impulse response
The impulse response, h(t), is the response to the unitimpulse, δ(t), applied at t=0 with zero initial conditions.The impulse response is very important since it contains all the system characteristics and can be used to findthe response to arbitrary excitation of LTI system via the convolution integral theorem.
The impulse response of a 1 DOF MBK system mustsatisfy
subject to i.c.
3.5 Non-periodic Excitation
( ) ( ) ( ) ( )mh t ch t kh t tδ+ + =
( ) ( )0 0, 0 0h h= =
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
( )
( ) ( )0 0
0
Get rid of the impulse function byintegrating over the duration 0, of the impulse
1
Take limit as 0 and apply the i.c.to evaluate the integral on the left hand side:
lim
mh ch kh dt t dt
m
ε ε
ε
ε
δ
ε
→
+ + = =
→
∫ ∫
( ) ( ) ( ) ( )
( ) ( ) ( ) ( )
( ) ( ) ( )
( )
000
00 00
00 00
lim 0 0, assuming is not continuous
lim lim 0 0, assuming is continuous
lim lim 0 0, assuming is continuous
0 1
h t dt mh t mh h t
ch t dt ch t ch h t
kh t dt gh t h t
mh
εε
ε
εε
ε ε
εε
ε ε
+
→
+
→ →
→ →
+
= = ≠
= = =
= =
∴ =
∫
∫
∫
Ch. 3: Forced Vibration of 1-DOF System
Therefore, the effect of a unit impulse at t=0 is toproduce equivalent initial velocity (impulse-momentum)
Now, we are ready to find the impulse response. Theequivalent system is a homogeneous system with i.c.
If the system is underdamped, the impulse response is
Note that the above i.c. is not the actual i.c.
3.5 Non-periodic Excitation
( )0 1/h m+ =
( ) ( )0 0, 0 1/h h m= =
( )1 sin , 0
0, 0
ntd
d
e t tmh t
t
ζω ωω
−⎧ ≥⎪= ⎨⎪ <⎩
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
Impulse response of underdamped system
Ch. 3: Forced Vibration of 1-DOF System
( )x t
Linear Time Invariant (LTI) system has the characteristic that the shape of the response will not be influenced bythe time the input is applied to the system. That is
3.5 Non-periodic Excitation
LTI system( )f t
LTI system( )f t a− ( )x t a−
Hence if the impulse is applied at t=to, the response is
( )( ) ( )0
0 0
0
1 sin ,
0,
n t td
d
e t t t tmh t
t t
ζω ωω
− −⎧ − ≥⎪= ⎨⎪ <⎩
Ch. 3: Forced Vibration of 1-DOF System
Total response of underdamped MBK with i.c. x(a)=x0and v(a)=v0 subject to the impulse force
3.5 Non-periodic Excitation
( )F̂ t aδ −
( )( ) ( ) ( )( ) ( ) ( )
( ) ( ) ( )
( ) ( ) ( ) ( )
1 2
1 2
1 2
ˆ sin cos sin
ˆ sin cos ,
ˆsin cos
n n
n
n
h p
t a t ad d d
d
t ad d
d
t an d d
d
x t x x
Fe A t a A t a e t am
Fe A t a A t a t am
Fx t e A t a A t am
ζω ζω
ζω
ζω
ω ω ωω
ω ωω
ζω ω ωω
− − − −
− −
− −
= +
= − + − + −
⎧ ⎫⎛ ⎞⎪ ⎪= + − + − ≥⎜ ⎟⎨ ⎬⎪ ⎪⎝ ⎠⎩ ⎭
⎧ ⎫⎛ ⎞⎪ ⎪= − + − + −⎜ ⎟⎨ ⎬⎪ ⎪⎝ ⎠⎩ ⎭
+ ( ) ( ) ( )1 2
ˆcos sinn t a
d d d dd
Fe A t a A t am
ζω ω ω ω ωω
− − ⎧ ⎫⎛ ⎞⎪ ⎪+ − − −⎜ ⎟⎨ ⎬⎪ ⎪⎝ ⎠⎩ ⎭
Ch. 3: Forced Vibration of 1-DOF System
Total response of underdamped MBK with i.c. x(a)=x0and v(a)=v0 subject to the impulse force
3.5 Non-periodic Excitation
( )F̂ t aδ −
( ) ( )
( ) ( ) ( ) ( ) ( )
0 0 1 2
0 2
0 2 1
2 0 1 0 0
0 0 0
Apply i.c. and to solve for and :
ˆ
ˆ1 and
1 sin cos , n
n dd
nd
t an d d
d
x a x x a v A Ax A
Fv A Am
FA x A x vm
x t e x v t a x t a t aζω
ζω ωω
ζωω
ζω ω ωω
− −
= =
=
⎛ ⎞= − + +⎜ ⎟
⎝ ⎠⎛ ⎞
∴ = = + −⎜ ⎟⎝ ⎠
⎧ ⎫∴ = + − + − ≥⎨ ⎬
⎩ ⎭
Ch. 3: Forced Vibration of 1-DOF System
Arbitrary Excitation
Ideally, arbitrary excitation can be expressed as linearcombinations of simpler excitations. The simplerexcitations are simple enough that the responseis readily available. This concept is exactly used byFourier.
Now, the idea is to regard the arbitrary excitation as asuperposition of impulses of varying magnitude andapplied at different times. It is used when the excitationcan be easily described in time domain.
3.5 Non-periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
Consider the excitation F(t). We can imagine that it is constructed from infinite impulses at different times.
3.5 Non-periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
Convolution integral theorm
3.5 Non-periodic Excitation
( )( ) ( )
( )
Focus on the time interval , at whichthe impulse of magnitude is acting. This
shifted impulse can be written as .The response of the LTI system to this particularimpulse is
,
tF
F t
x t F
τ τ ττ τ
τ τδ τ
τ
< < + Δ
Δ
Δ −
Δ = ( ) ( )( ) ( ) ( )
( )( ) ( ) ( )
( ) ( ) ( )0
Since by sampling property ,
and the system is linear, the response to is
In the limit as 0, .t
h t
F t F t
F t
x t F h t
x t F h t d
τ
τ
τ τ τ
τ τδ τ
τ τ τ
τ τ τ τ
Δ −
= Δ −
= Δ −
Δ → = −
∑
∑
∫
Ch. 3: Forced Vibration of 1-DOF System
Convolution integral theormThe response of the arbitrary excitation is thesuperposition of shifted impulse responses.
3.5 Non-periodic Excitation
Interpretationfor the wholerange of time; t
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
( ) ( )To obtain from , we need to carry outtwo operation; shifting and folding. This is another interpretationfor the specific time t. The figures show the steps in evaluating the convolution.
If we
h t hτ τ−
( ) ( ) ( )( ) ( ) ( )
( ) ( )
0
0
define a new variable , then and . With the change of the integration limits,
That is the convolution is symmetric in and .
To decide which formula to u
t
t
t td d
x t F t h d F t h d
F t h t
λ τ τ λτ λ
λ λ λ τ τ τ
= − = −= −
= − − = −∫ ∫
( ) ( )
( ) ( )
se depends on the nature of and .
It is obvious that if the excitation or the impulse response is too complicated, we may be unable to evaluate the closed formsolution of the convolution inte
F t h t
F t h t
gral. The excitation may not at allbe written as functions of time. In these cases, the integration mustbe carried out numerically.
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
Interpretation for the specific time; t
Ch. 3: Forced Vibration of 1-DOF System
Ex. Determine the response of the underdamped MBKto the unit step input.
3.5 Non-periodic Excitation
u(t)1
0 t
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
( ) ( ) ( )
( ) ( ) ( )
( ) ( )( ) ( ) ( )
( )
( ) ( )
0
0
and is the system impulse responseshifted by and mirrored about the vertical axis.If 0, 0 because of no overlap
If 0,
0, 0
, 0
Let
t
t
x t F h t d
F u h tt
t F h t
t F h t h t
x t t
x t h t d t
t
τ τ τ
τ τ τ
τ τ
τ τ τ
τ τ
= −
= −
< − =
> − = −
∴ = <
∴ = − >
−
∫
∫
( ) ( )
( )
0 0
. Hence
1 sin
Substitute sin and use 2
1 1 cos sin , 0
n
d d
n
t t
dd
i i axax
d
t nd d
d
d d
x t h d e dm
e e ee dx ci a
x t e t t tk
ζω λ
ω λ ω λ
ζω
τ λ τ λ
λ λ ω λ λω
ω λ
ζωω ωω
−
−
−
= = −
∴ = =
−= = +
⎡ ⎤⎛ ⎞∴ = − + >⎢ ⎥⎜ ⎟
⎝ ⎠⎣ ⎦
∫ ∫
∫
Ch. 3: Forced Vibration of 1-DOF System
Ex. Find the undamped response for the sinusoidalpulse force shown using zero i.c.
3.5 Non-periodic Excitation
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
( ) ( ) ( )
( )
( )
( )
( ) ( )( )
0
0 00 0
2sin sin2
1 sin
is the system impulse response shifted by and mirrored about the vertical axis.If 0, 0 because of no overlap
0, 0
t
nn
x t F h t d
F F FT T
hm
h t t
t F h t
x t t
τ τ τ
π πτ τ τ
τ ω τω
τ
τ τ
= −
⎛ ⎞ ⎛ ⎞= =⎜ ⎟ ⎜ ⎟
⎝ ⎠ ⎝ ⎠
=
−
< − =
∴ = <
∫
Ch. 3: Forced Vibration of 1-DOF System
3.5 Non-periodic Excitation
( ) ( ) ( )
( ) ( ) ( ) ( )
( ) ( )
( ) ( ) ( )
0 00
0
00 0
002
1If 0 , sin sin
sin sin
1using the relation sin sin cos cos and some arrangements2
sin sin , 0 where1
nn
t t
nn
n
t T F h t F tT m
Fx t F h t d t dm T
Fx t t r t t Tk r
πτ τ τ ω τω
πτ τ τ τ ω τ τω
α β α β α β
ω ω
⎛ ⎞< < − = × −⎜ ⎟
⎝ ⎠⎛ ⎞
= − = −⎜ ⎟⎝ ⎠
= − − +⎡ ⎤⎣ ⎦
∴ = − < <−
∫ ∫
( ) ( ) ( ) ( ) ( ) ( ) ( )
( ) ( ) [ ] ( ) ( ){ }
0
0
2
0
00 0
00 0 02
, ,
If ,
sin sin sin sin , 1
superposition of the out-of-phase shifted sine trains
nn
Tt t
t T
n n
r k mT
t T x t F h t d F h t d F t h d
Fx t t r t t T r t T t Tk r
π ωω ωω
τ τ τ τ τ τ τ τ τ
ω ω ω ω
−
= = =
> = − = − = −
∴ = − − − − − >⎡ ⎤⎣ ⎦−
∫ ∫ ∫