Feedback Control Systems (FCS)
Dr. Imtiaz Hussainemail: [email protected]
URL :http://imtiazhussainkalwar.weebly.com/
Lecture-22-23-24 Time Domain Analysis of 2nd Order Systems
Introduction• We have already discussed the affect of location of poles and zeros on
the transient response of 1st order systems.
• Compared to the simplicity of a first-order system, a second-order system exhibits a wide range of responses that must be analyzed and described.
• Varying a first-order system's parameter (T, K) simply changes the speed and offset of the response
• Whereas, changes in the parameters of a second-order system can change the form of the response.
• A second-order system can display characteristics much like a first-order system or, depending on component values, display damped or pure oscillations for its transient response.
Introduction• A general second-order system is characterized by
the following transfer function.
22
2
2 nn
n
sssRsC
)(
)(
Introduction
un-damped natural frequency of the second order system, which is the frequency of oscillation of the system without damping.
22
2
2 nn
n
sssRsC
)(
)(
n
damping ratio of the second order system, which is a measure of the degree of resistance to change in the system output.
Example#1
424
2
sssRsC)()(
• Determine the un-damped natural frequency and damping ratio of the following second order system.
42 n
22
2
2 nn
n
sssRsC
)(
)(
• Compare the numerator and denominator of the given transfer function with the general 2nd order transfer function.
sec/radn 2 ssn 22
422 222 ssss nn 50. 1 n
Introduction
• According the value of , a second-order system can be set into one of the four categories:
1
12
2
nn
nn
1. Overdamped - when the system has two real distinct poles ( >1).
-a-b-cδ
jω
Introduction
• According the value of , a second-order system can be set into one of the four categories:
1
12
2
nn
nn
2. Underdamped - when the system has two complex conjugate poles (0 < <1)
-a-b-cδ
jω
Introduction
• According the value of , a second-order system can be set into one of the four categories:
1
12
2
nn
nn
3. Undamped - when the system has two imaginary poles ( = 0).
-a-b-cδ
jω
Introduction
• According the value of , a second-order system can be set into one of the four categories:
1
12
2
nn
nn
4. Critically damped - when the system has two real but equal poles ( = 1).
-a-b-cδ
jω
Time-Domain Specification
11
For 0< <1 and ωn > 0, the 2nd order system’s response due to a unit step input looks like
Time-Domain Specification
12
• The delay (td) time is the time required for the response to reach half the final value the very first time.
Time-Domain Specification
13
• The rise time is the time required for the response to rise from 10% to 90%, 5% to 95%, or 0% to 100% of its final value.
• For underdamped second order systems, the 0% to 100% rise time is normally used. For overdamped systems, the 10% to 90% rise time is commonly used.
13
Time-Domain Specification
14
• The peak time is the time required for the response to reach the first peak of the overshoot.
1414
Time-Domain Specification
15
The maximum overshoot is the maximum peak value of the response curve measured from unity. If the final steady-state value of the response differs from unity, then it is common to use the maximum percent overshoot. It is defined by
The amount of the maximum (percent) overshoot directly indicates the relative stability of the system.
Time-Domain Specification
16
• The settling time is the time required for the response curve to reach and stay within a range about the final value of size specified by absolute percentage of the final value (usually 2% or 5%).
S-Plane
δ
jω
• Natural Undamped Frequency.
n
• Distance from the origin of s-plane to pole is natural undamped frequency in rad/sec.
S-Plane
δ
jω
• Let us draw a circle of radius 3 in s-plane.
3
-3
-3
3
• If a pole is located anywhere on the circumference of the circle the natural undamped frequency would be 3 rad/sec.
S-Plane
δ
jω
• Therefore the s-plane is divided into Constant Natural Undamped Frequency (ωn) Circles.
S-Plane
δ
jω
• Damping ratio.
• Cosine of the angle between vector connecting origin and pole and –ve real axis yields damping ratio.
cos
Example-2• Determine the natural frequency and damping ratio of the poles from the
following pz-map.
-4 -3.5 -3 -2.5 -2 -1.5 -1 -0.5 0-1.5
-1
-0.5
0
0.5
1
1.50.220.420.60.740.840.91
0.96
0.99
0.220.420.60.740.840.91
0.96
0.99
0.511.522.533.54
Pole-Zero Map
Real Axis (seconds-1)
Imag
inar
y Ax
is (s
econ
ds-1
)
Example-3
• Determine the natural frequency and damping ratio of the poles from the given pz-map.
• Also determine the transfer function of the system and state whether system is underdamped, overdamped, undamped or critically damped.
-3 -2.5 -2 -1.5 -1 -0.5 0 0.5 1 1.5 2-3
-2
-1
0
1
2
3
0.420.560.7
0.82
0.91
0.975
0.5
1
1.5
2
2.5
3
0.5
1
1.5
2
2.5
3
0.140.280.420.560.7
0.82
0.91
0.975
0.140.28
Pole-Zero Map
Real Axis (seconds-1)
Imag
inar
y Ax
is (s
econ
ds-1
)
Example-4
• The natural frequency of closed loop poles of 2nd order system is 2 rad/sec and damping ratio is 0.5.
• Determine the location of closed loop poles so that the damping ratio remains same but the natural undamped frequency is doubled.
424
2 222
2
sssssRsC
nn
n
)()(
-2 -1.5 -1 -0.5 0 0.5 1-3
-2
-1
0
1
2
3
0.280.380.5
0.64
0.8
0.94
0.5
1
1.5
2
2.5
3
0.5
1
1.5
2
2.5
3
0.080.170.280.380.5
0.64
0.8
0.94
0.080.17
Pole-Zero Map
Real Axis
Imag
inar
y Ax
is
Example-4• Determine the location of closed loop poles so that the damping ratio remains same
but the natural undamped frequency is doubled.
-8 -6 -4 -2 0 2 4-5
-4
-3
-2
-1
0
1
2
3
4
5
0.5
0.5
24
Pole-Zero Map
Real Axis
Imag
inar
y Ax
is
Step Response of underdamped System
222222 221
nnnn
n
sss
ssC
)(
• The partial fraction expansion of above equation is given as
22 221
nn
n
sss
ssC
)(
22 ns
22 1 n
222 1
21
nn
n
s
ss
sC )(
22
2
2 nn
n
sssRsC
)(
)( 22
2
2 nn
n
ssssC
)(Step Response
Step Response of underdamped System
• Above equation can be written as
222 1
21
nn
n
s
ss
sC )(
2221
dn
n
s
ss
sC
)(
21 nd• Where , is the frequency of transient oscillations and is called damped natural frequency.
• The inverse Laplace transform of above equation can be obtained easily if C(s) is written in the following form:
22221
dn
n
dn
n
ss
ss
sC
)(
Step Response of underdamped System
22221
dn
n
dn
n
ss
ss
sC
)(
22
2
2
22
111
dn
n
dn
n
ss
ss
sC
)(
222221
1
dn
d
dn
n
ss
ss
sC
)(
tetetc dt
dt nn
sincos)(
211
Step Response of underdamped System
tetetc dt
dt nn
sincos)(
211
ttetc dd
tn
sincos)(21
1
n
nd
21
• When 0
ttc ncos)( 1
Step Response of underdamped System
ttetc dd
tn
sincos)(21
1
sec/. radn and if 310
0 2 4 6 8 100
0.2
0.4
0.6
0.8
1
1.2
1.4
1.6
1.8
Step Response of underdamped System
ttetc dd
tn
sincos)(21
1
sec/. radn and if 350
0 2 4 6 8 100
0.2
0.4
0.6
0.8
1
1.2
1.4
Step Response of underdamped System
ttetc dd
tn
sincos)(21
1
sec/. radn and if 390
0 2 4 6 8 100
0.2
0.4
0.6
0.8
1
1.2
1.4
Step Response of underdamped System
0 1 2 3 4 5 6 7 8 9 100
0.2
0.4
0.6
0.8
1
1.2
1.4
1.6
1.8
2
b=0b=0.2b=0.4b=0.6b=0.9
Step Response of underdamped System
0 1 2 3 4 5 6 7 8 9 100
0.2
0.4
0.6
0.8
1
1.2
1.4
wn=0.5wn=1wn=1.5wn=2wn=2.5
Time Domain Specifications (Rise Time)
ttetc dd
tn
sincos)(21
1
equation above in Put rtt
rdrdt
r ttetc rn
sincos)(21
1
1)c(tr Where
rdrdt tte rn
sincos21
0
0 rnte
rdrd tt
sincos21
0
Time Domain Specifications (Rise Time)
as writen-re be can equation above
01 2
rdrd tt
sincos
rdrd tt
cossin21
21
rd ttan
2
1 1tanrd t
Time Domain Specifications (Peak Time)
ttetc dd
tn
sincos)(21
1
• In order to find peak time let us differentiate above equation w.r.t t.
ttette
dttdc
dd
ddt
ddt
nnn
cossinsincos)(22 11
tttte d
dddd
ndn
tn
cossinsincos
22
2
110
tttte d
nddd
ndn
tn
cossinsincos
2
2
2
2
1
1
10
Time Domain Specifications (Peak Time)
tttte d
nddd
ndn
tn
cossinsincos
2
2
2
2
1
1
10
01 2
2
tte dddntn
sinsin
0 tne 01 2
2
tt ddd
n
sinsin
01 2
2
d
nd t
sin
Time Domain Specifications (Peak Time)
01 2
2
d
nd t
sin
01 2
2
d
n
0tdsin
01sintd
dt
,,, 20
• Since for underdamped stable systems first peak is maximum peak therefore,
dpt
Time Domain Specifications (Maximum Overshoot)
pdpdt
p ttetc pn
sincos)(21
1
1)(c
10011
12
pdpdt
p tteM pn
sincos
equation above in Putd
pt
1001 2
dd
ddp
dn
eM
sincos
Time Domain Specifications (Maximum Overshoot)
1001 2
dd
ddp
dn
eM
sincos
1001 2
1 2
sincosnn
eM p
1000121
eM p
10021
eM p
equation above in Put 21-ζωω nd
Time Domain Specifications (Settling Time)
ttetc dd
tn
sincos)(21
1
12 nn
nT
1
Real Part Imaginary Part
Time Domain Specifications (Settling Time)
nT
1
• Settling time (2%) criterion• Time consumed in exponential decay up to 98% of the input.
ns Tt
44
• Settling time (5%) criterion• Time consumed in exponential decay up to 95% of the input.
ns Tt
33
Summary of Time Domain Specifications
ns Tt
44
ns Tt
33 100
21
eM p
21
ndpt
21
ndrt
Rise Time Peak Time
Settling Time (2%)
Settling Time (4%)
Maximum Overshoot
Example#5• Consider the system shown in following figure, where
damping ratio is 0.6 and natural undamped frequency is 5 rad/sec. Obtain the rise time tr, peak time tp, maximum overshoot Mp, and settling time 2% and 5% criterion ts when the system is subjected to a unit-step input.
Example#5
ns Tt
44
10021
eM p
dpt
drt
Rise Time Peak Time
Settling Time (2%) Maximum Overshoot
ns Tt
33
Settling Time (4%)
Example#5
nst
4
dpt
Peak Time Settling Time (2%)
nst
3
Settling Time (4%)
st p 785041413 ..
sts 331
5604 ..
sts 1560
3
.
Example#5Step Response
Time (sec)
Ampl
itude
0 0.2 0.4 0.6 0.8 1 1.2 1.4 1.60
0.2
0.4
0.6
0.8
1
1.2
1.4
Mp
Rise Time
Example#6• For the system shown in Figure-(a), determine the values of gain K
and velocity-feedback constant Kh so that the maximum overshoot in the unit-step response is 0.2 and the peak time is 1 sec. With these values of K and Kh, obtain the rise time and settling time. Assume that J=1 kg-m2 and B=1 N-m/rad/sec.
Example#6
Nm/rad/sec and Since 11 2 BkgmJ
KsKKsK
sRsC
h
)()()(
12
22
2
2 nn
n
sssRsC
)(
)(
• Comparing above T.F with general 2nd order T.F
Kn KKKh21 )(
Example#6
• Maximum overshoot is 0.2.
Kn KKKh21 )(
2021 .ln)ln(
e
• The peak time is 1 sec
dpt
245601
1413
..
n
21
14131
n
.
533.n
Example#7When the system shown in Figure(a) is subjected to a unit-step input, the system output responds as shown in Figure(b). Determine the values of a and c from the response curve.
)( 1cssa
Example#8Figure (a) shows a mechanical vibratory system. When 2 lb of force (step input) is applied to the system, the mass oscillates, as shown in Figure (b). Determine m, b, and k of the system from this response curve.
Example#9Given the system shown in following figure, find J and D to yield 20% overshoot and a settling time of 2 seconds for a step input of torque T(t).
Step Response of critically damped System ( )
• The partial fraction expansion of above equation is given as
22
n
n
ssRsC
)(
)( 2
2
n
n
sssC
)(Step Response
22
2
nnn
n
sC
sB
sA
ss
211
n
n
n ssssC
)(
teetc tn
t nn 1)(
tetc ntn 11)(
1
72
Example 10: Describe the nature of the second-order system response via the value of the damping ratio for the systems with transfer function
Second – Order System
12812)(.1 2
ss
sG
16816)(.2 2
ss
sG
20820)(.3 2
ss
sG
Do them as your own revision
END OF LECTURES-22-23-24
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