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© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Free Vibrations of Particles. Simple Harmonic Motion
19 - 2
• If a particle is displaced through a distance xm from its equilibrium position and released with no velocity, the particle will undergo simple harmonic motion,
( )0=+
−=+−==
kxxmkxxkWFma st
!!
δ
• General solution is the sum of two particular solutions,
( ) ( )tCtC
tmkCt
mkCx
nn ωω cossin
cossin
21
21
+=
⎟⎟⎠
⎞⎜⎜⎝
⎛+⎟⎟⎠
⎞⎜⎜⎝
⎛=
• x is a periodic function and ωn is the natural circular frequency of the motion.
• C1 and C2 are determined by the initial conditions:
( ) ( )tCtCx nn ωω cossin 21 += 02 xC =
nvC ω01 =( ) ( )tCtCxv nnnn ωωωω sincos 21 −== !
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Free Vibrations of Particles. Simple Harmonic Motion
19 - 3
( )φω += txx nm sin
==n
n ωπ
τ2 period
===πω
τ 21 n
nnf natural frequency
( ) =+= 20
20 xvx nm ω amplitude
( ) == −nxv ωφ 00
1tan phase angle
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Free Vibrations of Particles. Simple Harmonic Motion
19 - 4
( )φω += txx nm sin
• Velocity-time and acceleration-time curves can be represented by sine curves of the same period as the displacement-time curve but different phase angles.
( )( )2sin
cosπφωω
φωω
++=
+=
=
txtx
xv
nnm
nnm
!
( )
( )πφωω
φωω
++=
+−=
=
tx
tx
xa
nnm
nnm
sin
sin2
2
!!
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Simple Pendulum (Approximate Solution)
19 - 5
• Results obtained for the spring-mass system can be applied whenever the resultant force on a particle is proportional to the displacement and directed towards the equilibrium position.
for small angles,
( )
gl
tlg
nn
nm
πωπ
τ
φωθθ
θθ
22
sin
0
==
+=
=+!!
:tt maF =∑
• Consider tangential components of acceleration and force for a simple pendulum,
0sin
sin
=+
=−
θθ
θθ
lg
mlW
!!
!!
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Simple Pendulum (Exact Solution)
19 - 6
0sin =+ θθlg!! An exact solution for
leads to ( )
∫−
=2
022 sin2sin1
4π
φθ
φτ
mn
dgl
which requires numerical solution.
⎟⎟⎠
⎞⎜⎜⎝
⎛=
glK
n ππ
τ 22
(1)
, with K being integral in (1)
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Concept Question
19 - 7
The amplitude of a vibrating system is shown to the right. Which of the following statements is true (choose one)?
a) The amplitude of the acceleration equals the amplitude of the displacement
b) The amplitude of the velocity is always opposite (negative to) the amplitude of the displacement
c) The maximum displacement occurs when the acceleration amplitude is a minimum
d) The phase angle of the vibration shown is zero
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Sample Problem 19.1
19 - 8
A 50-kg block moves between vertical guides as shown. The block is pulled 40mm down from its equilibrium position and released.
For each spring arrangement, determine a) the period of the vibration, b) the maximum velocity of the block, and c) the maximum acceleration of the block.
SOLUTION:
• For each spring arrangement, determine the spring constant for a single equivalent spring.
• Apply the approximate relations for the harmonic motion of a spring-mass system.
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Sample Problem 19.1
19 - 9
mkN6mkN4 21 == kk SOLUTION: • Springs in parallel:
- determine the spring constant for equivalent spring
mN10mkN10 4
21
21
==
+==
+=
kkPk
kkP
δ
δδ
- apply the approximate relations for the harmonic motion of a spring-mass system
nn
n mk
ωπ
τ
ω
2
srad14.14kg20N/m104
=
===
s 444.0=nτ
( )( )srad 4.141m 040.0=
= nmm xv ω
sm566.0=mv
2sm00.8=ma( )( )2
2
srad 4.141m 040.0=
= nmm axa
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Sample Problem 19.1
19 - 10
mkN6mkN4 21 == kk • Springs in series: - determine the spring constant for equivalent spring
- apply the approximate relations for the harmonic motion of a spring-mass system
nn
n mk
ωπ
τ
ω
2
srad93.6kg20
400N/m2
=
===
s 907.0=nτ
( )( )srad .936m 040.0=
= nmm xv ω
sm277.0=mv
2sm920.1=ma( )( )2
2
srad .936m 040.0=
= nmm axa1 2
1 2
1 2
1 2
1 2
1 2
( )
2.4kN m 2400 N m
P Pk k
k k Pk kk kPkk k
= + = +
+=
= = =+
d d d
d
d
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Free Vibrations of Rigid Bodies
19 - 11
• If an equation of motion takes the form 0or0 22 =+=+ θωθω nn xx !!!!
the corresponding motion may be considered as simple harmonic motion.
• Analysis objective is to determine ωn.
( ) ( )[ ] mgWmbbbmI ==+= ,22but 23222
121
053sin
53
=+≅+ θθθθbg
bg !!!!
gb
bg
nnn 3
522,53then π
ωπ
τω ===
• For an equivalent simple pendulum, 35bl =
• Consider the oscillations of a square plate ( ) ( ) θθθ !!!! ImbbW +=− sin
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Sample Problem 19.2
19 - 12
k
A cylinder of weight W is suspended as shown.
Determine the period and natural frequency of vibrations of the cylinder.
SOLUTION:
• From the kinematics of the system, relate the linear displacement and acceleration to the rotation of the cylinder.
• Based on a free-body-diagram equation for the equivalence of the external and effective forces, write the equation of motion.
• Substitute the kinematic relations to arrive at an equation involving only the angular displacement and acceleration.
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Sample Problem 19.2
19 - 13
SOLUTION: • From the kinematics of the system, relate the linear
displacement and acceleration to the rotation of the cylinder. θrx = θδ rx 22 ==
θα !!rra ==θα !!"= θ!!
"ra =
• Based on a free-body-diagram equation for the equivalence of the external and effective forces, write the equation of motion.
( ) :∑∑ = effAA MM ( ) αIramrTWr +=− 22( )θδ rkWkTT 2but 2
102 +=+=
• Substitute the kinematic relations to arrive at an equation involving only the angular displacement and acceleration.
( )( ) ( )
038
22 221
21
=+
+=+−
θθ
θθθ
mk
mrrrmrkrWWr
!!
!!
mk
n 38
=ωkm
nn 8
322π
ωπ
τ ==mkf n
n 38
21
2 ππω
==
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Sample Problem 19.3
19 - 14
n
10 kg1.13s
m ==t s93.1=nτ
The disk and gear undergo torsional vibration with the periods shown. Assume that the moment exerted by the wire is proportional to the twist angle.
Determine a) the wire torsional spring constant, b) the centroidal moment of inertia of the gear, and c) the maximum angular velocity of the gear if rotated through 90o and released.
SOLUTION:
• Using the free-body-diagram equation for the equivalence of the external and effective moments, write the equation of motion for the disk/gear and wire.
• With the natural frequency and moment of inertia for the disk known, calculate the torsional spring constant.
• With natural frequency and spring constant known, calculate the moment of inertia for the gear.
• Apply the relations for simple harmonic motion to calculate the maximum gear velocity.
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Sample Problem 19.3
19 - 15
s13.1lb20
n =
=
τ
Ws93.1=nτ
SOLUTION: • Using the free-body-diagram equation for the equivalence
of the external and effective moments, write the equation of motion for the disk/gear and wire.
( ) :∑∑ = effOO MM
0=+
−=+
θθ
θθ
IK
IK
!!
!!
KI
IK
nnn π
ωπ
τω 22===
• With the natural frequency and moment of inertia for the disk known, calculate the torsional spring constant.
( ) ( )21 2 22
1 10 kg 0.2 m 0.2 kg m2
I mr= = = ◊
0.21.13 2K
= p 6.18N m radK = ◊
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Sample Problem 19.3
19 - 16
s13.1lb20
n =
=
τ
Ws93.1=nτ
K = 6.18 N ⋅m rad
KI
IK
nnn π
ωπ
τω 22===
• With natural frequency and spring constant known, calculate the moment of inertia for the gear.
1.93 26.183I= p Igear = 0.583 kg ⋅m2
• Apply the relations for simple harmonic motion to calculate the maximum gear velocity.
nmmnnmnm tt ωθωωωθωωθθ === sinsin
rad 571.190 =°=mθ
( ) ⎟⎠⎞
⎜⎝⎛=⎟⎟
⎠
⎞⎜⎜⎝
⎛=
s 93.12rad 571.12 π
τπ
θωn
mm
srad11.5=mω
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Group Problem Solving
19 - 17
A uniform disk of radius 250 mm is attached at A to a 650-mm rod AB of negligible mass which can rotate freely in a vertical plane about B. If the rod is displaced 2°from the position shown and released, determine the period of the resulting oscillation.
SOLUTION:
• Using the free-body and kinetic diagrams, write the equation of motion for the pendulum.
• Determine the natural frequency and moment of inertia for the disk (use the small angle approximation).
• Calculate the period.
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Group Problem Solving
19 - 18
Draw the FBD and KD of the pendulum (mbar ~ 0).
Bn Bt
man mat
Iαmg
Determine the equation of motion.
B BM I αΣ =
( )2sinmgl I mlθ α− = + sin tmgl I lmaθ α− = +
*Note that you could also do this by using the “moment” from at, and that at = lα
θ l r
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Group Problem Solving
19 - 19
Find I, set up equation of motion using small angle approximation
Determine the natural frequency
( )2sinmgl I mlθ α− = +
21 , sin2
I mr θ θ= ≈
12mr2 +ml2
!
"#
$
%& θ +mglθ = 0
( )2
22
2
2 212
(9.81)(0.650)(0.250) (0.650)
14.0533.7487 rad/s
n r
n
gll
ω
ω
=+
=+
=
=
Calculate the period
2 1.676 snn
πτ
ω= =
1.676 snτ =
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Damped Free Vibrations
19 - 20
• With viscous damping due to fluid friction, :maF =∑ ( )
0=++
=−+−
kxxcxmxmxcxkW st
!!!
!!!δ
• Substituting x = eλt and dividing through by eλt yields the characteristic equation,
mk
mc
mckcm −⎟
⎠⎞
⎜⎝⎛±−==++
22
220 λλλ
• Define the critical damping coefficient such that
ncc m
mkmc
mk
mc
ω2202
2===−⎟
⎠
⎞⎜⎝
⎛
• All vibrations are damped to some degree by forces due to dry friction, fluid friction, or internal friction.
© 2013 The McGraw-Hill Companies, Inc. All rights reserved.
Vector Mechanics for Engineers: Dynamics
Tenth Edition
Damped Free Vibrations
19 - 21
• Characteristic equation,
mk
mc
mckcm −⎟
⎠⎞
⎜⎝⎛±−==++
22
220 λλλ
== nc mc ω2 critical damping coefficient
• Heavy damping: c > cc tt eCeCx 21 21
λλ += - negative roots - nonvibratory motion
• Critical damping: c = cc ( ) tnetCCx ω−+= 21 - double roots
- nonvibratory motion
• Light damping: c < cc ( ) ( )tCtCex dd
tmc ωω cossin 212 += −
=⎟⎟⎠
⎞⎜⎜⎝
⎛−=
21
cnd c
cωω damped frequency
Free Vibra)ons
Free Vibra)ons Solu)on
Damped vibra)ons
Damped vibra)ons solu)on
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