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7/28/2019 4. Review of Classical Control
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1
Control of Smart Structures 4. Review of Classical Control 1
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
4. Review of Classical Controls
A Continuation of
Dynamics and Controls Related Knowledge
in Intelligent Structural Systems
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Control of Smart Structures 4. Review of Classical Control 2
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Classification of Control Systems
Type Based on their ability to follow step, ramp and parabolic inputs.
The magnitude of steady state errors due to these individual inputs are
indicative of the goodness of the system.
Consider the unity feedback system as shown
The Open Loop Transfer function is ( note the pole of Multiplicity
N or the N INTEGRATORS )
1 2
( 1)( 1)...( 1)( )
( 1)( 1)...( 1)
a b m
N
p
K T s T s T sG s
s T s T s T s
+ + +=
+ + +
G(s)R(s) C(s)
+-
E(s)
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Control of Smart Structures 4. Review of Classical Control 3
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
A system is called Type 0, Type 1, Type 2 if N=0, N=1,
N=2,
This is DIFFERENT from order of the system.
For the closed loop system shown in previous slide, the steady state
error is given by (if the system is stable)
Now, we will define various error constants. Names of the errors doesnot implies, position or velocity in literal terms. However, they imply
output, rate of change of output and so on.
Classification of Control Systems
0 0
( )lim ( ) lim ( ) lim
1 ( )ss
t s s
sR se e t sE s
G s = = =
+
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Control of Smart Structures 4. Review of Classical Control 4
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Static Position Error Constant Kp: The steady state error of the systems
for a unit STEP input is
is defined as
Thus the steady state error is
Steady State Errors
0
1 1lim1 ( ) 1 (0)
sss
seG s s G
= =+ +
pK
0
lim ( ) (0)ps
K G s G
= =
1
1ss pe K=
+
(if the system is stable)
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Control of Smart Structures 4. Review of Classical Control 5
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
For Type 0 system,
For Type 1 , system
Thus the steady state error is
Steady State Errors
00 01 2
( 1)( 1)...( 1)
lim ( ) lim ( 1)( 1)...( 1)
a b m
P s sp
K T s T s T s
G s Ks T s T s T s
+ + +
= = =+ + +
10 01 2
( 1)( 1)...( 1)lim ( ) lim 1( 1)( 1)...( 1)
a b mP
s sp
K T s T s T sK G s for Ns T s T s T s + + += = = + + +
10
1
0 1
ss
ss
e for TypeK
e for Type or higher systems
=+
=
(if the system is stable)
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Control of Smart Structures 4. Review of Classical Control 6
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Static Velocity Error Constant Kv: The steady state error of the
systems for a unit RAMP input is
is defined as
Thus the steady state error is
Steady State Errors
20 0
1 1lim lim1 ( ) ( )
sss s
seG s s sG s
= =+
vK
0
lim ( )vs
K sG s
=
1
ssve K
=
(if the system is stable)
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Control of Smart Structures 4. Review of Classical Control 7
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
For Type 0 system,
For Type 1 , system
For Type 2 or higher systems
Steady State Errors
00 0 1 2
( 1)( 1)...( 1)lim ( ) lim 0
( 1)( 1)...( 1)
a b mv
s s p
sK T s T s T sK sG s
s T s T s T s
+ + += = =
+ + +
10 01 2
( 1)( 1)...( 1)lim ( ) lim
( 1)( 1)...( 1)a b mv
s sp
s K T s T s T ss G s K
s T s T s T s
+ + += = =+ + +
20 01 2
( 1)( 1)...( 1)lim ( ) lim 2
( 1)( 1)...( 1)
a b mv
s sp
sK T s T s T sK sG s for N
s T s T s T s
+ + += = =
+ + +
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Control of Smart Structures 4. Review of Classical Control 8
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Thus the steady state error for unit ramp input is
Thus, Type 0, system cannot follow ramp input. Type 2 system can
follow ramp input with zero error.
Steady State Errors
10
1 11
1 0 2
ss
v
ss
v
ss
v
e for Type
K
e for TypeK K
e for Type or higher systemsK
= =
= =
= =
(if the system is stable)
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Control of Smart Structures 4. Review of Classical Control 10
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
For Type 0 system,
For Type 1 , system
For Type 2
For Type 3 or higher system
Steady State Errors
22
0
0 0 1 2
( 1)( 1)...( 1)lim ( ) lim 0
( 1)( 1)...( 1)
a b ma
s s p
s K T s T s T sK s G s
s T s T s T s
+ + += = =
+ + +2
2
10 01 2
( 1)( 1)...( 1)lim ( ) lim 0
( 1)( 1)...( 1)
a b ma
s sp
s K T s T s T sK s G s
s T s T s T s
+ + += = =
+ + +
22
20 01 2
( 1)( 1)...( 1)lim ( ) lim
( 1)( 1)...( 1)
a b ma
s sp
s K T s T s T ss G s K
s T s T s T s
+ + += = =
+ + +
22
20 01 2
( 1)( 1)...( 1)lim ( ) lim 3
( 1)( 1)...( 1)
a b ma
s sp
s K T s T s T sK s G s for N
s T s T s T s
+ + += = =
+ + +
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Control of Smart Structures 4. Review of Classical Control 11
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Thus the steady state error for unit Parabolic input is
Thus, Type 0 and Type 1, system cannot follow parabolic input. Type
2 system can follow ramp input with finite error. Type 3 and highersystem can follow a parabolic input with zero error.
Steady State Errors
10 1
1 12
1 0 3
ss
v
ss
a
ss
a
e for Type and Type
K
e for TypeK K
e for Type or higher systemsK
= =
= =
= =
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Control of Smart Structures 4. Review of Classical Control 12
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Unit Step Input Unit Ramp InputUnit Accleration
Input
Type 01
1 pK+
Type 1 0 1
vK
Type 2 0 0 1
a
Steady State Errors
Steady State Error in Terms of Error Constants
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Control of Smart Structures 4. Review of Classical Control 14
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Resonant Frequency and Resonant Peak Value
The magnitude of
This magnitude is maximum when the denominator is minimum. The
minimum of denominator occurs when
This is called the resonant frequency
2
2 22
2
1( )
1 2
1( )
1 2
n n
n n
G j
j j
is
G j
=
+ +
=
+
21 2 0 0.707r n for =
21 2n =
C l f S S 4 R i f Cl i l C l 15
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Control of Smart Structures 4. Review of Classical Control 15
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
For the resonant frequency is less than the damped
natural frequency which is exhibited in transient
response.
The magnitude of the resonant peak can be found as
As approaches zero approaches infinity. This means that for an
undamped system excited at its natural frequency the magnitude
becomes infinite.
Resonant Frequency and Resonant Peak Value
max 2
1( ) ( ) 0 0.707
2 1r rM G j G j for
= = =
r
0 0.707
21d n =
C t l f S t St t 4 R i f Cl i l C t l 16
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Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Relationship between System Type and Magnitude Curve
Consider a unity feedback control system.
The static position, velocity and acceleration constant describe the low
frequency behavior of the Type 0, Type 1 and Type 2 systems
respectively.
For a given system only one of the static error constant is finite and
significant. (refer table)
The larger the value of the finite static error constant, the higher theloop gain is as approaches zero.
The type of the system determines the slope of the log-magnitude
curve at low frequencies.
Thus information about the steady state error of a control system to a
given input can be determined from the low frequency region of the
log magnitude curve.
C t l f S t St t 4 R i f Cl i l C t l 17
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Control of Smart Structures 4. Review of Classical Control 17
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
For a unity feedback Open Loop Transfer Function is
For a Type 0 system (Magnitude plot
shown)
It follows that the low frequency asymptote is a horizontal line at
Relationship between System Type and Magnitude Curve
1 2
( 1)( 1)...( 1)( )
( 1)( 1)...( 1)
a b m
N
p
K T s T s T sG s
s T s T s T s
+ + +=
+ + +
0lim ( ) pG j K K
= =
20log .pK dB
Control of Smart Str ct res 4 Re ie of Classical Control 18
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Control of Smart Structures 4. Review of Classical Control 18
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
In a Type 1 system (Magnitude plot
shown)
The intersection of the initial -20
dB/decade segment or its extension with
the 0 dB line has a frequency numericallyequal to Kv.
Relationship between System Type and Magnitude Curve
( ) 1vK
G j for w
j
=
1
1
1
2
1 2 3
( ) 1v
v
KG j
jK
= =
=
=
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Control of Smart Structures 4. Review of Classical Control 19
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Relationship between System Type and Magnitude Curve
In a Type 2 system (Magnitude plot
shown)
The intersection of the initial -40
dB/decade segment or its extension with
the 0 dB line has a frequency numericallyequal to the square root of Ka.
( )
2( ) 1v
KG j for w
j
=
( )220log 20log1 0a
a
a a
K
j
K
= =
=
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Control of Smart Structures 4. Review of Classical Control 20
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Gain and Phase Margin
Phase Margin: The phase margin is that amount of additional phase lag
at the gain cross over frequency required to bring the system to the
verge of instability.
The gain cross over frequency is the frequency at which the magnitude
of the open loop transfer function is unity.
The phase margin is plus the phase angle of the open loop
transfer function at the gain cross over frequency or,
180
180 = +
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Control of Smart Structures 4. Review of Classical Control 21
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Gain Margin: The gain margin is the reciprocal of the magnitude at the
frequency at which the phase angle is .
Defining the phase cross over frequency to be the frequency at
which the phase angle of the open loop transfer function equals
gives the gain margin
In term of dB
Gain and Phase Margin
180
180
1
gK
1
( )gK
G j=
120log 20log ( )g gK dB K G j= =
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Control of Smart Structures 4. Review of Classical Control 22
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Gain and Phase Margin
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Control of Smart Structures 4. Review of Classical Control 23
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
The values of and are almost the same for small values of . Thus for small values of , the value of is indicative of the speed
of transient response of the system.
Correlation between Step Transient and
Frequency response for second order system The phase margin and damping ratio are directly related. Figure shows
a plot of the phase margin as a function of the damping ratio .
For a second order system the phase margin and damping ratio are
related by a straight line for as follows
0 0.6
100
=
rr
d
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Control of Smart Structures 4. Review of Classical Control 24
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Summary: Frequency Response
Information Obtained from Open Loop Frequency Response
- The low frequency region (far below cross over frequency) of the
locus indicates the steady state behaviorof the closed loop system.
- The medium frequency region indicates the relative stability
- The high frequency region (far above cross over frequency) of the
locus indicates the complexity of the closed loop system.
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Control of Smart Structures 4. Review of Classical Control 25
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Nyquist Plots: Stability and Relative Stability
Nyquist plot is the locus of vectors as is varied fromzero to infinity.
Nyquist stability criterion determines the stability of a closed loop
system from its open loop frequency response. ( Remember RootLocus also gives stability of closed loop system from open looptransfer function root locus plot)
The Nyquist stability criterion relates the open loop frequency
response to the number of zeros and poles of thecharacteristic equations that lie in the right halfs-plane.
Absolute stability of the closed loop system can be determined fromgraphically from the open loop frequency response and thus there is no
need for actually determining closed loop poles. This is important because in practical systems mathematical
expressions are often not available, only the frequency response data isavailable.
( ) ( )G j H j 1 ( ) ( )G s H s+
( ) ( )G j G j
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Control of Smart Structures 4. Review of Classical Control
Department of Mechanical Engineering
Dr. G. Song, Associate Professor
TASK:
Self Study: Plotting of Nyquist Plots, Mapping Theorem (s-plane to
F(s)plane whereF(s)=1+G(s)H(s) )
Self study: Nyquist Stability Analysis and Relative Stability Analysis.
Nyquist Plots: Stability and Relative Stability
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27Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Characteristics of Lead, Lag and Lag-Lead Compensators
Lead Compensatoressentially yields an appreciable improvement in
transient response and a small change in steady state accuracy. This
implies it can be used for vibration suppression.
Lag Compensatoryields an appreciable improvement in steady state
accuracy at the expense of increasing the transient response time.
Lag-Lead Compensatorcombines both the characteristics of Lead and
Lag compensators.
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28Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Lead Control Design
Two approaches can be used for Lead Controller Design
1. Root Locus Approach
2. Bode Plot (Frequency Response Approach)
We will deal with both the approaches.
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29Department of Mechanical Engineering
Dr. G. Song, Associate Professor
+_
Lead comp. plant
PZT
sensor
C(s)
Gc(s) G(s)
R(s)
command
1. Phase-lead compensator
)10(1
1
1
1
)(
1
1
2
1
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30Department of Mechanical Engineering
Dr. G. Song, Associate Professor
System
5.0,2
31:..
424
)()(
1 2
==
=
++=
+=
n
jspolesLC
sssRsC
GGCL
)2(
4)(
+=
sssG
Close-loop uncompensated
5.0,4: == nObjectiveDesign
Steps: 1) Determine the desired location for the dominant C.L. poles(new) from
performance spaces.
jjs nn
n
o
3221
4
605.0cos
2
2,1 ==
=
===
Lead compensator (Root Locus)
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31Department of Mechanical Engineering
Dr. G. Song, Associate Professor
2) Draw the root-locus plot of the uncompensated system, see if gain adjustment alonecan achieve the desired C.L. poles. If not (this case), calculate the angle deficiency ,
which will be contributed by the lead compensator.(we need to modify a little to satisfy
the angle condition)
new
4j
3j
2j
j120
old
60
60
r = 4
=+=+
=+
=
=
18030210)2(
4
210)2(
4
1
1
ss
ss
ssGc
ss
Lead compensator (Root Locus)
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32Department of Mechanical Engineering
Dr. G. Song, Associate Professor
The lead compensator will have a phase lead of 30.
)10(1
1
1
1
)(
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33Department of Mechanical Engineering
Dr. G. Song, Associate Professor
68.4
1
)2(
4
4.5
9.2
1
4.59.2)(
537.0
345.04.5
1
9.21
1
=
=
++
+
=
++=
=
==
=
=
c
ss
c
c
cc
K
sss
sK
GGNow
ssKsG
T
T
T
15o
Design finished, verify the result
Lead compensator (Root Locus)
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34Department of Mechanical Engineering
Dr. G. Song, Associate Professor
m
mm
mzpm
pz
p
zc
ccc
TT
TTs
s
K
Ts
Ts
KTs
TsKsG
sin1
sin1
1
1sin
11
)1
,1
(
1
1
)10(1
1
1
1)(
2
+
=
+
=
===
==+
+=
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36Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Lead compensator (Frequency Response)
Design example and procedures
Gc+- 1010.24ss
5.122 ++
Design requirement:
Kp (WHY Kp ? ) to be 10 times of the original one
phase margin at least 33
gain margin at least 10 dB
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37Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Procedures:
1. Determine gainKto satisfy the requirement on the given static error constant
12
0
1 12.5 1( ) * ( )1 0.24 101 1
lim ( )
10*101/12.5 80.8
c
p cs
Ts TsG G s K G sTs s s Ts
K G G s
K
+ += =+ + + +
=
= =
2. Draw bode diagram of
G1 : gain adjusted O.L. transfer function (not include the compensator, but
include the compensators gain)
Evaluate the phase margin from bode plot
1( ) ( )G s KG s=
Lead compensator (Frequency Response)
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38Department of Mechanical Engineering
Dr. G. Song, Associate Professor
3. Determine the necessary phaselead angle to be added to thesystem, allowing for a smallamount of angle addition to
compensate for the shift in gaincross over frequency.
33 - 0.195 = 32.805
32.80 + 5.20 = 38
Addition of a lead compensatormodifies the magnitude curveand shifts the gain cross overfrequency to the right. To
offset the increase phase lag ofdue to the
increase in the gain cross overfrequency, we provide someadditional angle, as above.
Lead compensator (Frequency Response)
Bode Plot of Gain adjusted Open Loop system
KGjG =)(1
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Control of Smart Structures 4. Review of Classical Control 40
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40Department of Mechanical Engineering
Dr. G. Song, Associate Professor
6. Determine the corner frequency of the lead compensator
7. Determine Kc
1
122.87
1 122.87 95.32
0.24
m
m
p
T
T
T
=
= =
= = =
Zero:
Pole:
Lead compensator (Frequency Response)
c
c
K K/ 80.8/0.24 336.66
s 22.87G 336.66s 95.32
= = =
+= +
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41Department of Mechanical Engineering
Dr. G. Song, Associate Professor
8. Check the gain margin and phase margin of the Open Loop compensated system
Lead compensator (Frequency Response)
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42Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Check the transient response
Lead compensator (Frequency Response)
High Overshoots:
Characteristics oflead compensators.
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43Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Basics: Zero is always located to the left of pole in s-plane for lag compensator. It
reduces steady state error at the expense of increasing the transient
response time. Given by:
Lag compensator
11 ( ) ( 1)
11c c c
sTs TG s K K Ts
TsT
++
= = >+ +
Figure shows a typical lag compensator.
Magnitude of the lag compensator (for this
case only) is 40 dB for low frequencies and
20 dB at high frequencies. Thus, the lag
compensator is essentially a low pass filter
-1/T -1/(T)
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44Department of Mechanical Engineering
Dr. G. Song, Associate Professor
In Lag compensators, pole and zero are chosen very
close to each other. By the use of lag compensator we
are intending to reduce the steady state error. To do
so, we do not want to alter the transient response
much. However, the addition of poles and zeros
change the root locus. To avoid major changes in the
root locus, the poles and zeros are chosen very close
to each other as well as very close to the origin.
The design will be dealt in detail, when we design a
lag lead compensator.
If we use large , Gc(s) will change the root loci of the system, therefore we hope to
use large to increase the steady state error Kp & KvcK
-1/T -1/(T)
s
Lag compensator
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45Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Basics: Used to improve both transient response and steady state
response. The lag-lead compensator is given by
Lag-Lead Compensator (Root-Locus)
( )1 2
1 2
1 1
( ) ( ) ( ) 1, 11c c
s sT T
G s K
s sT T
+ +
= > >+ +
Lead Network Lag Network
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46Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Problem
Problem Statement: For the Block diagram shown below design acompensator such that the dominant closed loop poles are located at
and the static velocity error constant is 50 sec-1.
Q. What kind of Compensator ?
A. Lag-Lead, because we need to reshape the root-locus and decrease the steadystate error by increasing .
Q. Which Compensator will be designed first?A. Lead, because lead compensator will change the root locus. After reshaping theroot locus, we can design lag . Lag compensator do not appreciably change theroot locus.
js 3222,1 =
vK
Gc+
-
10
s(s 2)(s 5)+ +
v
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47Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Step1: Find angle deficiency, which will be compensated by the lead portion.
1 1 1
10100.89
( 2)( 5)s s s
=
+ +
Assume is not equal to for design simplicity
1 = 120
2 = 90
3 = 50
123
O.L.poles0-2-5
s1
Lag-Lead Compensator (Root Locus)
180 100.89 79.11angle deficiency = =
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48Department of Mechanical Engineering
Dr. G. Song, Associate Professor
Not to increase the system order, we choose 1/T1 =2, then (s+ 1/T1 ) will cancel the plant
pole at (s+2)
1
( 2) 101 33.6
( 20) ( 2)( 5)c c
s s
sK K
s s s s=
+= =
+ + +
Use Magnitude Condition
-21.6 -2
79.11
s1
1
1
20.00, 1/ 2 0.5, 10.0T
T
= = = =
01
1
5&11
1
2
1
2
1
2
1
2
1