10. Closed-Loop Dynamics
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Transcript of 10. Closed-Loop Dynamics
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Min-Sen Chiu
Department of Chemical and Biomolecular Engineering
National University of Singapore
CN3121 Process Dynamics and Control
10. Dynamic Behavior of Closed-loop Control System s
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Dynamic Behavior of Closed-Loop Control Systems
Learning Objectives
• Become familiar with the major elements in the feedback control system
• Evaluate the dynamic behavior of processes operated under feedback control
• Develop closed-loop transfer functions
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The combination of the process and the feedback controller is called the closed-loop system.
Variables of a closed-loop system:
1. Inputs – set-point and disturbance variables.
2. Output - controlled variable.
The analysis of closed-loop systems can be difficult due to the presence of feedback.
Two useful tools:
1. Block diagram
2. Closed-loop transfer function
Block diagrams can provide quantitative information if each block is represented by a transfer function.
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Return to the previous example of stirred tank blending process (see Chapters 2 and 4, SEM).
Development of a Block Diagram
Control objective: Regulate tank composition xManipulated variable: Flow rate of pure A, w2
Primary disturbance: Inlet composition x1
Assume w1 constant
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Derive transfer functions for each component in the closed-loop system.
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Process
Approximate dynamic model of the stirred-tank blending system is available (see eq. 4-69, SEM):
( ) ( ) ( )1 21 2 (11-1)
τ 1 τ 1
K KX s X s W s
s s ′ ′ ′= + + +
11 2
ρ 1, , and (11-2)
wV xK K
w w wτ −= = =where
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Composition Sensor
Assume a first-order transfer function:
( )( ) (11-3)
τ 1m m
m
X s K
X s s
′=
′ +
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Usually τm << τ.
Compared to the (slow) process dynamics, sensor dynamics is considered as negligible (fast) dynamics; thus its transfer function can be further simplified asa steady-state gain Km.
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Controller
Suppose that a proportional plus integral (PI) controller is used. The controller transfer function is
( )( )
11 (11-4)τc
I
P sK
E s s
′ = +
, E(s) - Laplace transforms of the controller output ˙and the error signal e(t)
( )P s′ ( )p t′
p′ and e - electrical signals (units of mA)
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Set point expressed as an electrical current signal
Set point expressed as the actual physical variable
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The error signal is )()(~)( '' txtxte msp −= (11-5)
Transform
)()(~
)( '' sXsXsE msp −= (11-6)
)('~ tx sp is internal set-point related to the actual composition set-point by sensor gain Km :)(' tx sp
)()(~ '' txKtx spmsp =
msp
sp KsX
sX=
)(
)(~
'
'
(11-7)
(11-8)
Eqs. 11-4, 11-6 and 11-8 are shown in the controller block diagram.
Transform
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Current-to-Pressure (I/P) Transducer
Usually has linear characteristics and negligible (fast) dynamics; thus assume that the transfer function merely consists of a steady-state gain KIP.
( )( ) (11-9)t
IPP s
KP s
′=
′
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( )( )
2 (11-10)τ 1
v
t v
W s K
P s s
′=
′ +
Assume that the valve can be modeled as
Control Valve
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[psi]
The valve dynamics is generally nonlinear => approximated by linear (1st order) model in the vicinity of the nominal operating condition
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Combining the block diagrams for the individual components, we get the composite block diagram of the control system:10
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Block Diagram Simplification
Basic elements in a block diagram:
Arrow indicates flow of information, e.g. p = Ge = G(r - c).
Circle represents algebraic relation of the input arrows, e.g. e = r – c.
Block represents the relevant dynamics (by transfer function model) between the input and output.
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Gr +
-
p
p
e
c
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Some basic rules
1. Y = A – B – C
2. Y = G1G2A G1 G2A Y
G2 G1A Y
G1G2A Y
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A +-
+-
B C
YA - B
B -
-
+
+
C A
Y- B - C
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3. Y = G1(A – B)
G1A
B
Y+
-G1
G1
YA
B
+
-
4. Y = (G1+G2)A
G1
G2
A Y+
+
G1+G2A Y
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G2 G1/G2A +
+Y
G2A G1A
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This is a general diagram that can be used to represent a wide variety of practical control problems.
Gp – Effect of manipulated variable on the controlled va riable
Gd – Effect of load variable on the controlled variable
Block Diagrams – General Treatment
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Standard symbols
G = transfer function
(subscripts c, v, p, d, m = controller, valve, process, disturbance, and measurement respectively)
Y - process output D - disturbance or load variable
Ym - measured output Ysp - set-point
Ỹsp - internal set-point E - error
P - controller output U - manipulated variable
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Note• Each variable in the figure is the Laplace transform of a deviation
variable.
• For simplicity, the primes and “s” have been omitted; thus Y means Y’(s).
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Closed-Loop Transfer Functions
The objective is to find the transfer functions between the inputs (Ysp and D) and the output (Y) of the closed-loop system.
For the process input,
)()~
( YGYKGGYYGGEGGPGU mspmcvmspcvcvv −=−===
Process output is obtained as
DGUGY dp +=
From the above two equations,
DGYGYKGGGY dmspmcvp +−= )(
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Rearranging,
DGGGG
GY
GGGG
KGGGY
mcvp
dsp
mcvp
mcvp
++
+=
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Effect of Ysp on Y Effect of D on Y
(11-30)
Eq. 11-30 illustrates the important role of Laplace Transform in analysis of feedback control system
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Two Types of Control Problem
1. Servo problem (set-point change)
Assume Ysp ≠ 0 and D = 0 (set-point change while disturbance change is zero). From the last equation,
mcvp
mcvp
sp GGGG
KGGG
Y
Y
+=
1(11-26)
(closed-loop transfer function for set point change)
2. Regulator problem (disturbance change)
mcvp
d
GGGG
G
D
Y
+=
1(11-29)
Assume D ≠ 0 and Ysp = 0 (constant set-point)
(closed-loop transfer function for load change)
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Remarks
1. Closed-loop transfer functions (eqs. 11-26 and 1 1-29) depend on dynamics of process, measurement device, controller and control valve.
3. Overall transfer function = (product of transfer functions in the forward path)/(1 + product of all transfer func tions in the loop).
4. (1+ GpGvGcGm) is often written as ( 1+ GOL) where GOL= GpGvGcGm is the open-loop transfer function. G OL relates Ym to ˙̇̇̇Ỹsp if the feedback loop is opened just before the comparator .
2. Denominator for both transfer functions, eqs. 11 -26 and 11-29, is the same => (1 + product of all the transfer functions in the loop), i.e. (1+GpGvGcGm).
5. For simultaneous changes in disturbance and set- point (i.e., ˙̇̇̇D ≠≠≠≠ 0 and Y sp ≠≠≠≠ 0), eq 11-30 holds => overall response is the ˙̇̇̇sum of the individual responses .
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1c v p m
sp c v p m
G G G KY
Y G G G G=
+
Negative feedback
1d
c v p m
GY
D G G G G=
+
Forward path from Y sp to Y
Forward path from D to Y
Product of all transfer functions in the loop
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Remark 3
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1c v p m
sp c v p m
G G G KY
Y G G G G=
+
Negative feedback
1p
c v p m
GY
D G G G G=
+
Forward path from Y sp to Y
Forward path from D to Y
Product of all transfer functions in the loop
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Consider this feedback system,
+
-Gc
Gm
Y+ Gp
D
+Gv
Ysp Km
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Feedback system – equivalent diagrams
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+
-Gc
Gm
Y+ Gp
D
+Gv
Ysp Km
spY~
Gc
+Y
D
+
Gp
Gv Gp
Gm
+
-Ysp Km
spY~
Ysp Y+
Gp
1+GcGvGpGmD
+GcGvGpKm
1+GcGvGpGm
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Analysis and Design Problems
Analysis Given particular Gp, Gv, Gc, Gm, ˙
- Is the closed-loop system stable? - Speed of response? Damping? …
Design Given particular Gp, Gv, Gm, and Gd, “design”Gc so that
- The closed-loop dynamics are stable- Y/Ysp has a gain of ?? and Y/D has a gain of ??
- The dynamics are sufficiently fast and smooth ˙ (without excessive oscillations)
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Effect of Proportional Control on Closed-Loop Response
Consider 1st-order process and P-controller.
Then 1+
=s
KG p
p τ 1+=
s
KG d
d τcc KG =
For simplicity, let and vv KG = mm KG =
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From eq. 11-30,
DKKKKs
KY
KKKKs
KKKKY
mpvc
dsp
mpvc
mpvc
+++
++=
11 ττ
Ds
KY
s
Ksp 11 1
2
1
1
++
+=
ττ
mpvc KKKK+=
11
ττ
mpvc
mpvc
KKKK
KKKKK
+=
11
mpvc
d
KKKK
KK
+=
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Decreases with increasing K cAlways < ττττ, i.e., CL response is faster than OL response
≠≠≠≠ 1 unless K c = ∞∞∞∞Always < 1
≠0 unless K c = ∞∞∞∞Always < Kd
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Note: CL system is 1 st order with time const τ1. For both TFs, τ is the same, but gain is different
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Servo problem
Step change of magnitude M in set-point, i.e., Ysp = M/s and D = 0.
Then from the last eq. s
M
s
KY
11
1
+=
τInverting, )1()( 1/
1τteMKty −−=
mpvc KKKK
M
+=
1
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Less than the desired value M.
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Offset = current set-point – (final value of the response)
mpvcmpvc
mpvc
KKKK
M
KKKK
KKKMKMMKM
+=
+−=−
111=
As t →∞, output response never reaches new set-point. The discrepancy is called (steady-state) offset.
Offset decreases with increasing Kc. This is the characteristic of P-control.
Theoretically, offset → 0 when Kc→ ∞.
But, does it happen? If not, why?
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Regulator problem
In this case, D = M/s Ysp = 0 and Ds
KY
11
2
+=
τInverting, )1()( 1/
2τteMKty −−=
0
M D(t)
y(t)
no control (K c=0)KdM
Time0
K2M with controloffset
Offset = current set-point – (final value of the response)
mpvc
d
KKKK
MKMK
+−=−=
10 2
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Kc offset
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Proportional-Integral Control for Disturbance Change
In this case, )1
1(s
KGI
cc τ+=
)1()1()
11(
11
1+++
=+
++
+=sKKKKss
sK
ss
KKKKs
K
D
Y
ImpvcI
Id
I
mpvc
d
ττττ
ττ
τ
Rearrange
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3
3
++=
ss
sK
D
Y
τζτwhere
ττζττττ I
mpvc
mpvc
mpvc
I
mpvc
Id
KKKK
KKKK
KKKKKKKK
KK
)1(
2
1,, 333
+===
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Gain = ?
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For a unit step change in load, D = 1/s and hence
12)(
3322
3
3
++=
ss
KsY
τζτ
The output response for ζ3 < 1 is
−
−= −
3
23
/
233
3 1sin1
11)( 33
τζ
ζττζ t
eKty t
For this specific case, the responses for different Kc
and τI are given in the next slide.
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Remarks
1. Integral action eliminates offset, ysp(∞) – y(∞) = 0
ττττ = 1, Kp = 1, Kv = 1
τI = 0.25 Kc = 3.5y(t) y(t)
2. For Kc↑ or τI↓ � response speeds up
3. For Kc↓ � response more oscillatory (unexpected)
5. Note In general, closed loop response becomes more oscillatory as Kc↑. The anomalous result above is due to neglected valve and measurement dynamics. When these are included, the TF is no longer 2nd-order.
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4. For τI↓ � response more oscillatory (expected)
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Proportional-Integral Control for Set Point Change
)1/()/11(1
)1/()/11(
+++++
=ssKK
ssKK
Y
Y
Ipc
Ipc
sp ττττ
For this case,
Standard form
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1
3322
3 +++=
ss
s
Y
Y I
sp τζττ
τ3, ζζζζ3 – as defined earlier
Introduce unit step change in Ysp and inverse
3
2/
23
1sin1
)( 3
τζ
ζττ τζ t
ety tI −−
= −
−+−
−−+ −−
ζζ
τζ
ζτζ
21
3
2/
2
1tan1sin
1
11 3
te t
Gain = 1 always! No offset 2nd order dynamics
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y(t)Kc = 1, Kp = 1 ττττI = 1, ττττ = 1
Again, zero offset
Offset = ysp(∞) – y(∞) = 1 – 1 = 0
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Effect of Measurement Lag
As before let
1+=
s
KG p
p τ 1+=
s
KG d
d τ cc KG = 1== vv KG,,,
Assume significant measurement lag:1
1
+=
sG
mm τ
Resulting control system is
1+=
s
KG d
d τ
Kc 1+=
s
KG p
p τ
1
1
+=
sG
mm τ
+ ++
-
YspY
D
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Ym
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Consider set point change,
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)1(
)1)(1(1
1
5522
5
5
+++=
+++
+=ss
sK
ss
KKs
KK
Y
Y m
m
pc
pc
sp τζττ
ττ
τ
,15
cp
c
KK
KK
+= ,
15cp
m
KK+= τττ
cpm
m
KK++=
1
1
25 ττ
ττζ
where and
Produces 2nd-order system even for P-control. Response may be oscillatory depending on the choice of τ, τm, Kp
and Kc. One possibility is as follows:
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▪ Measurement lag produces poorer transients
Remarks
▪ Offset results from the use of P controller
Kp = 1
ττττ =1Kc = 8 Ysp = 1/s
y(t)
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Control of Pure Capacity (or integrating) Process
h controlled by manipulating q1.
Mass balance (in terms of deviation variables):
1qdt
dhA =
As
qh 1=or
(const)
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Let Gc = Kc, Gv = Gm = 1.
Kc 1/Ashspq1 h
spc
hKAs
h1)/(
1
+=
For set-point change hsp = 1/s, 1 1
( / ) 1c
hAs K s
= ⋅+
h(t→∞) = lim [s h(s)] = 1s→0000
Therefore offset = hsp – h (t→∞) = 1 – 1 = 0
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Alternatively, ..…
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When we place chemical process in a closed-loop wit h sensors, transducers, valves and controllers, we ha ve a more complicated system than the original process. Neve rtheless, our analysis shows that a closed-loop system can be written as one single transfer function.
Thus we recognize that a block diagram provides a convenient representation for analyzing control sys tems.
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Summary
We understand the key features of P and PI control using simple first-order processes.
We notice that measurement dynamics can cause deterioration in the control system performance.
Further reading: Chapter 11.1 and 11.3, SEM