iver2 auv control design thesis defense
DESCRIPTION
This is the slideshow that I used while doing my thesis defense for "Analysis, Redesign and Verification of the Iver2 Autonomous Underwater Vehicle Motion Controller."TRANSCRIPT
Analysis, Redesign and Verification of the Iver2 Autonomous Underwater Vehicle Motion Controller
A Thesis inElectrical Engineering
by Eric A. Leveille
Submitted in Partial Fulfillment of theRequirements for the Degree of
Master of Science
July, 2007
Committee Members
• Professor Steven Nardone: Co-advisor
• Professor Gilbert Fain: Co-advisor
• Associate Professor Howard Michel: Committee Member
• Jon Crowell - Director of Engineering, OceanServer Technology: Committee Member
Presentation Overview
• Introduction
• Modeling the Iver2 AUV
• Linear Control Design
• Controller Nonlinearities
• Field-testing the Depth Controller
• Conclusion
Motivation for Research
• Typical AUV applications [1] : – surveillance– reconnaissance– mine countermeasures– tactical oceanography– communications– navigation– anti-submarine warfare
• Control system failures may lead to a failed mission or loss of vehicle
The Iver2 AUV
• Dimensions: 4 foot long by 6 inch diameter
• Weight: 46 pounds• Cost: $50k• Nearest competitor’s
cost: $500k
Original Motion Controller Design
• Proportional gains control pitch, depth, heading and roll.
• Trial and error design technique is used.
• An analytical approach may improve the overall system response. 550 560 570 580 590 600 610
3
4
5
6
7
8
9
X: 589.9Y: 7.61
Time (s)
Dep
th F
rom
Sur
face
(ft
) X: 592.4Y: 6.64
DepthGoal Depth
Iver2 Model Development
• Vehicle model needed for analytical controller redesign.
• Modeling process relies heavily on Verification of a Six-Degree of Freedom Simulation Model for the REMUS Autonomous Underwater Vehicle [2].
Controller Design and Implementation
• Controller designs based upon linear transfer function models
• Root locus, frequency domain, and time plots are used to design each controller.
• Field tests performed to verify the designed depth controller
Vehicle Coordinate Systems
Vehicle Kinematics
• Kinematic equations [3] convert body-fixed velocities and rotation rates to changes in inertial position or attitude.
• Integrating the kinematic equations provides the solution for new position and attitude.
r
q
p
w
v
u
z
y
x
cos/coscos/sin0000
sincos0000
tancostansin1000
000coscossincossin
000cossinsinsincossinsinsincoscoscoscos
000sincoscossinsinsinsincoscossincoscos
Control Coordinate System
• Center of buoyancy is the point to be controlled.• Center of gravity is typically located directly
below the center of buoyancy for improved stability.
Rigid Body Dynamics
• Dynamic equations are given by Standard Equations of Motion for Submarine Simulation [4,5].
Xqprzrqxwqvrum GG 22
Yrqpxpqrzurwpvm GG
Zqrpxqpzvpuqwm GG 22
KurwpvzmqrIIpI Gyzx
MvpuqwxwqvruzmrpIIqI GGzxy
NurwpvxmpqIIrI Gxyz
.
External Forces and Moments
• Each component of the sum of external forces is calculated based on current states and vehicle coefficients.
• Vehicle coefficients, such as the axial drag coefficient, are found based on measured vehicle parameters and the hull shape.
CONTROLMASSADDEDDRAGLIFTCHYDROSTATIEXT FFFFFF
uuACF fdDRAGAXIAL )2
1(
6-DOF Nonlinear Model
• Combines equations for kinematics, dynamics, and external forces and moments.
• Simulates how control and hydrodynamic forces affect both the body-fixed velocities and overall change in position and attitude.
),( iii uxfx
Ti zyxrqpwvux
Linear Depth Plane Model
GӨ
δs(t) Ө(t)GZ
z(t)
qYqY
q
qY
s
MIM
sMI
Ms
MI
M
s
ssG
s
2)(
)()(
5203.0007.1
147.12
ss
s
U
s
szsGZ
)(
)()(
s
1
Depth Plane Control Structure
• Two available measurements: depth and pitch• Cascade control structure is used for increased
disturbance rejection.
KDEPTH KPITCH GӨ GZ
- -
+ + δs(t) Ө(t) Z(t)Depth Reference
(m)
Inner Pitch Loop (Fast)
Outer Depth Loop (Slow)
Depth Sensor Feedback
Pitch Sensor Feedback
Inner Pitch Loop Design
• Main goal is disturbance rejection.
• A proportional-derivative (PD) controller is chosen to meet requirements.
• Use of derivative action frequently leads to problems with high frequency signals.
Type A PD Controller [6]
KP GӨ
-
+ δs(t)
Ө(t)
Pitch Sensor Feedback
Pitch ReferenceFrom Outer Control Loop
(radians)
d/dt
+
KD
+
Inner Pitch Loop (Fast)
GsKK
sKKS
DP
DPI )(1
• Amplifies high-frequency noise on the feedback path and on the time-varying pitch reference.
Type B PD Controller
KP GӨ
-
+ δs(t)
Ө(t)
Pitch Sensor Feedback
Pitch ReferenceFrom Outer Control Loop
(radians)
d/dt
-+
KD
Inner Pitch Loop (Fast)
• Avoids the differentiation of the time-varying pitch reference, which reduces fin flutter.
GsKK
KS
DP
PI )(1
Pitch Controller Step Response
• Type B PD controller designed using Root Locus techniques.
• Rise Time: 2 sec• Critically damped
for a quick rise time with no overshoot.
• Steady-state error is allowable.
0 0.5 1 1.5 2 2.5 3 3.5 4 4.5 50
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9Step Response of Pitch Controller
Time (sec)
Pitc
h (
deg
)
Outer Depth Loop Controller
• Outer depth loop must be slower than the inner pitch loop for the cascade structure to work correctly.
• P and PI depth controllers are designed.
KP GZ
-
+ Ө(t) Z(t)Depth Reference
(m)
Depth Sensor Feedback
TP
Closed-Loop TF forInner Pitch Loop
Effective Depth Plant
KI
+
+
dt
P Controller Depth Response
• Slower depth loop has a rise time of 8 seconds, which is 4x faster than the inner pitch loop.
• Overshoot should be kept less than 20%.
0 5 10 150
0.2
0.4
0.6
0.8
1
System: TzTime (sec): 8.15Amplitude: 0.907
Step Response of Depth Loop with P Controller
Time (sec)
Dep
th (
m)
PI Controller Depth Response
• Integral action added to offset effects of tow-float.
• Integral action has a destabilizing effect due to phase lag introduced.
0 10 20 30 40 50 60 70 80 90 1000
0.2
0.4
0.6
0.8
1
System: Tz2Time (sec): 7.31Amplitude: 0.917
1m Depth Change with PI Control using Linear Model
Time (sec)
Dep
th (
m)
Nonlinear Depth Plane Simulation
• 6-DOF model used to verify the results of the designed PI controller.
• Nonlinear model simulation produces similar results to the linear simulations.
0 20 40 60 80 1000
0.2
0.4
0.6
0.8
1
X: 8.233Y: 0.8952
Time (s)
Dep
th (
m)
1m Depth Change with PI Depth Control using 6-DOF Model
Linear Control Signals
• Linear control signals travel to extreme values.
• Limiting their values will change the designed response.
0 20 40 60 80 100-100
-50
0
50
100
150
200
250Commanded Pitch and Stern Fin Angle During 5m Depth Change
Time (s)
Ang
le (
de
g)
Reference PitchStern Control Fin
Saturating Nonlinearities
• Designs so far assumed linear controllers.• Control fin angles and commanded pitch angle
are both limited in practice.
KDEPTH KPITCH GӨ GZ
--
+ + δs(t) Ө(t)
Z(t)
Depth Reference
(m)
Inner Pitch Loop (Fast)
Outer Depth Loop (Slow)
Depth Sensor Feedback
Pitch Sensor Feedback
LP Lδs
n
n
+
+ +
+
Linear and Saturated Responses
• Saturation in the controller slows the rise time and increases overshoot.
• Rise time varies due to pitch limiting.
• Increased overshoot is unacceptable.
0 50 100 1509
10
11
12
13
14
15
16
17
Time (s)
Dep
th (
m)
Saturated and Linear 5m Depth Changes with 6-DOF Model
LinearSaturated
Integrator Windup
KP GZ
-
+ Ө(t)Z(t)
Depth Reference
(m)
Depth Sensor Feedback
TP
Closed-Loop TF forInner Pitch Loop
Effective Depth Plant
dt KI
+
+
Pnom Psat
e
• Integrator continues to “wind up” the depth error when the reference pitch is saturated.
• Integrator windup can lead to an undesired response and even instability.
Preventing Integrator Windup [7]
1. Integrator Limiting
2. Conditional Freeze
3. Freeze
4. Preloading
5. Anti-windup Bumpless-transfer
6. Variable-structure PID Control
Simulated Anti-windup Techniques
• Conditional Freeze and Freeze methods present the best results for the Iver2 application.
0 50 100 1508
10
12
14
16
18
20
22
24
Time (s)
Dep
th (
m)
Comparison of Anti-Windup Methods during 10m Depth Change
CI-ILIMCI-CFRZCI-FRZAWBTVSPIDNo Anti-windup
Dive Video
Implemented Depth Controller
• PI Outer Depth Loop Control• Integrator Freeze Antiwindup Method• Type A PD Inner Pitch Loop Control
KP
-
+ δs(t)
Pitch Sensor Feedback
Commanded Pitch
d/dt
+
KD
+
KP
-
+
Depth Sensor Feedback
KI
+
+
To ControlFin Motors
Goal Depth
dt
Integrator Freeze Antiwindup
Old vs New Depth Responses
550 560 570 580 590 600 6103
4
5
6
7
8
9
X: 589.9Y: 7.61
Time (s)
Dep
th F
rom
Sur
face
(ft
) X: 592.4Y: 6.64
DepthGoal Depth
Old Controller New Controller
• New controller removes steady-state error, decreases overshoot, and removes the steady-state oscillations.
45 50 55 60 65 70 75 80 85 90 952
3
4
5
6
7
8
Time (s)
Dep
th F
rom
Sur
face
(ft
)
Goal DepthActual Depth
Old vs New Pitch Responses
550 560 570 580 590 600 610-20
-15
-10
-5
0
5
10
15
20
Time (s)
Ang
le (
de
g)
PitchGoal Pitch
Old Controller New Controller
• New controller removes the steady-state oscillations and is more-capable of tracking the goal pitch.
45 50 55 60 65 70 75 80 85 90 95-20
-15
-10
-5
0
5
10
15
20
Time (s)
Ang
le (
de
g)
Goal PitchPitch
Old vs New Control Fin AnglesOld Controller New Controller
• New controller slightly increases fin flutter due to the use of derivative action in the inner pitch loop.
550 560 570 580 590 600 610-30
-20
-10
0
10
20
30
Time (s)
Ang
le (
de
g)
45 50 55 60 65 70 75 80 85 90 95-30
-20
-10
0
10
20
30
Time (s)
Fin
Ang
le (
de
g)
Future Improvements
• Reprogram the controller to fit the Type B structure.
• Introduce a lowpass filter in the derivative path of the pitch controller.
• Investigate online-tuning procedures for the cascade control structure to automatically tune the depth controller.
Conclusion
• Nonlinear and linear models were developed for the Iver2 AUV.
• Analytical redesign of the depth plane controller reduced overshoot, removed steady-state error and removed steady-state oscillations, and is a good addition to the Iver2 platform.
• Room for further improvement remains.
References• [1] Robert L. Wernli. Low-Cost UUV’s for Military Applications: Is the Technology
Ready? Space and Naval Warfare Systems Center San Diego. 2001 • [2] Timothy Prestero. Verification of a Six-Degree of Freedom Simulation Model for
the REMUS Autonomous Underwater Vehicle. M.S. Thesis, 2001• [3] Thor I. Fossen. Guidance and Control of Ocean Vehicles. John Wiley & Sons Ltd.
1994.• [4] Morton Gertier and Grant R. Hagen. Standard Equations of Motion for Submarine
Simulation. Naval Ship Research and Development Center. June, 1967.• [5] J. Feldman. DTNSRDC Revised Standard Submarine Equations of Motion. David
W. Taylor Naval Ship Research and Development Center. June, 1979.• [6] Yun Li, Kiam Heong Ang, Gregory C.Y. Chong. PID Control System Analysis and
Design: Problems, Remedies and Future Directions. IEEE Control Systems Magazine. February, 2006.
• [7]A. Scottedward Hodel, Charles E. Hall. Variable-Structure PID Conrol to Prevent Integrator Windup. IEEE Transactions on Industrial Electronics, Vol. 48, No. 2, April 2001.
Thank You!
QUESTIONS?
Simulink Model
[u v w p q r]
2
[u v w p q r]
1
[x y z phi theta psi]
Body -f ixed State
Inertial State
Rudder Fin Angle (rad)
Stern Fin Angle (rad)
Sum of Forces
Sum of Forces Vector
U( : )
Reshape3
U( : )
Reshape2
Reshape
Reshape1
MatrixMultiply
Matrix Multiply
Matrix
Mass Matrix1s
Integrator1
1s
Integrator
Inertial StateRotation Matrix
Body to Inertial Rotation Matrix
MatrixMultiply
Body to Inertial
GeneralInverse
(LU)
LU Inverse
2
Stern FinAngle (rad)
1
Rudder FinAngle (rad)