NL2025573B1 - Method for controlling path tracking of an autonomous vehicle with input saturation - Google Patents
Method for controlling path tracking of an autonomous vehicle with input saturation Download PDFInfo
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- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D1/00—Control of position, course, altitude or attitude of land, water, air or space vehicles, e.g. using automatic pilots
- G05D1/02—Control of position or course in two dimensions
- G05D1/021—Control of position or course in two dimensions specially adapted to land vehicles
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- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
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- B60W30/18145—Cornering
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B60W30/10—Path keeping
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- B60—VEHICLES IN GENERAL
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- B60W50/00—Details of control systems for road vehicle drive control not related to the control of a particular sub-unit, e.g. process diagnostic or vehicle driver interfaces
- B60W50/06—Improving the dynamic response of the control system, e.g. improving the speed of regulation or avoiding hunting or overshoot
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- B60W60/00—Drive control systems specially adapted for autonomous road vehicles
- B60W60/001—Planning or execution of driving tasks
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W50/00—Details of control systems for road vehicle drive control not related to the control of a particular sub-unit, e.g. process diagnostic or vehicle driver interfaces
- B60W2050/0001—Details of the control system
- B60W2050/0019—Control system elements or transfer functions
- B60W2050/0028—Mathematical models, e.g. for simulation
- B60W2050/0031—Mathematical model of the vehicle
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W50/00—Details of control systems for road vehicle drive control not related to the control of a particular sub-unit, e.g. process diagnostic or vehicle driver interfaces
- B60W2050/0001—Details of the control system
- B60W2050/0019—Control system elements or transfer functions
- B60W2050/0028—Mathematical models, e.g. for simulation
- B60W2050/0031—Mathematical model of the vehicle
- B60W2050/0035—Multiple-track, 3D vehicle model, e.g. including roll and pitch conditions
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- B60W2520/00—Input parameters relating to overall vehicle dynamics
- B60W2520/10—Longitudinal speed
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2520/00—Input parameters relating to overall vehicle dynamics
- B60W2520/14—Yaw
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2530/00—Input parameters relating to vehicle conditions or values, not covered by groups B60W2510/00 or B60W2520/00
- B60W2530/20—Tyre data
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Abstract
A method for controlling path tracking of an autonomous vehicle with input saturation is provided. The robust Hoo path tracking controller is designed to solve the 5 problems such as network delays and input saturation during the control of path tracking of the autonomous vehicle and improve the path tracking performance of the vehicle under extreme driving conditions. The lateral velocity and the yaw rate of the vehicle are adjusted to improve the vehicle steerability and stability as well as achieve path tracking control of the autonomous vehicle. The robust Hoo path tracking control lO gain matrix for the autonomous vehicle can be obtained by solving the linear matrix inequality, which is easy to compute. The uncertainty of the vehicle dynamics model and effects of external disturbances are considered in this path tracking control design, which improves the robustness of the path tracking control algorithm. A static output feedback controller is designed to realize ideal path tracking control as well as 15 significantly cut down the cost of the control system.
Description
-1-
TECHNICAL FIELD The present disclosure relates to the technical field of autonomous vehicles, and more particularly, to a method for controlling vehicle tracking with input saturation.
BACKGROUND With the rapid development of the new generation of information technology and improvements in people's requirements for vehicle safety and comfort, the path tracking control of autonomous vehicles has been an area of concentration in recent years and is widely used in mobile robots and automatic parking systems. Autonomous vehicles contribute to reducing labor intensity, improving driving safety, mitigating the accident, and improving road traffic efficiency. According to statistics from the automobile industry, driven by the goal of relieving road congestion and traffic accidents, most automobiles would be unmanned in the future and expected to dominate road traffic. For autonomous vehicles, one of the basic problems to be solved is to realize the path tracking control of vehicles, and the control goal thereof is achieved by allowing vehicles to track the ideal path and maintaining the steady-state path tracking error (i.e., the lateral offset and heading error) zero.
Path tracking control algorithms for autonomous vehicles include sliding mode control, adaptive control, robust Heo control, neural network control, model predictive control, linear matrix inequation (LMI) optimization control, and Lyapunov-function- based control. Most of these control methods only consider the vehicle steerability and stability. However, the problems of delays and data packet loss inevitably exist during the measurement of vehicle states and signal transmission. Moreover, in practical applications, there are physical limits to the actuator. For example, under extreme driving conditions, the tire force may reach saturation. When the system enters a
2- saturation state, the output of the controller and the input of the controlled object would not match, which greatly reduces the performance of the controller and even destabilizes the closed-loop system. Therefore, the method for realizing the path tracking control of autonomous vehicles with network delays and actuator saturation remains a challenging problem in the industrial and academic fields.
SUMMARY In order to overcome the shortcomings of the prior art, the present disclosure provides a method for controlling vehicle tracking with input saturation, which can realize excellent steering stability and path tracking performance of an autonomous vehicle under an extreme driving condition. The present disclosure adopts the following technical solutions to overcome the above-mentioned technical problems. A method for controlling path tracking of an autonomous vehicle with input saturation includes the following steps: a) establishing a vehicle dynamics model by formula (1): ! FE +F d Vv, = —( + Lv +d, (1) m ‚1 1 (1) j=—(I,F,—LF,)+—AM, +d)
LM I where, V, denotes the first derivative of V,, 7 denotes the first derivative of Y, V, denotes a longitudinal velocity of a center of mass CG of a vehicle, V, denotes a lateral velocity of the center of mass CG of the vehicle, } denotes a yaw rate of the vehicle, 77 denotes the mass of the vehicle, / - denotes a rotational inertia of the vehicle about the Z -axis, d, (£ ) and d 2 (¢ ) both denote unmodeled dynamics, Fy denotes a lateral force of a front tire of the vehicle, and F, denotes a lateral force of a rear tire of the vehicle; an external yaw moment AM ET calculated by formula (2) 2 4 v { . 0 i v AM, = YF [(=1)],c088, +1,sind,1+ > (DLE, 6 i=1 i=3 where, F, denotes a longitudinal force of the /" tire, l f denotes a distance from the center of mass CG of the vehicle to a front axle, / + denotes a distance from the center of mass CG of the vehicle to a rear axle, / + denotes a wheelbase, and 0 f denotes a steering angle of a front wheel, b) establishing a path tracking model by formula (3): & Ve) ¢ / 3) Ss where, l, denotes a horizontal distance between the center of mass CG of the vehicle and a sensor, Y e denotes a lateral offset [, distant from the center of mass CG of the vehicle, and Ó, denotes a heading error; an actual yaw angle @ of the vehicle is calculated by formula (4): $=9+%, (4) where, Ó, denotes a yaw angle of a tangent direction of a reference path relative to a global coordinate system, when the vehicle follows the reference path with a curvature of at the longitudinal velocity V,, 9, =V.0 ref , where Ó, denotes the first derivative of Ó, ; c) establishing a dynamic path tracking model by formula (5): x(t) = Ax(t)+ Bu(t) + d(t) (5)
4e where, X(Z) denotes the first derivative of X(£), X(#) denotes a state , variable, x(t ) = [v,., Vs 9. v,] ‚ 1" denotes a matrix transpose, u(t ) denotes ~ 7 an input variable, u(t) = [ò, AM, ] | and oo Tr d(t) = |, © d,() TV Pe AN ; the system matrix A and the system matrix B are calculated by formula (6); C +C Cl, -Cl | ! Sf Vv, 0 0 my, my, “1 “1 ~ 72 + 72 a= Cl, Cl, Cc A+ CL _ 0 1 0 0 1 [ v.
O i © Cr Cy 0 0 m a B= : 1 0 — 0 0 7 z d) a change in the longitudinal velocity V, of the vehicle is expressed by the formula 1/ Vv, = (1+ A) / Vv. , where A, denotes a time-varying parameter and | A IS 1, V. denotes a nominal value of V, | the system matrix A is expressed as A=A,+AA, where AA=EMF, M =A, and F denotes an identity matrix; A, is calculated by formula (7), and £ is calculated by formula (8);
C,+C, GN Lr ILO 00 MV.
MV, | A, =| — C, 1, ' Cr _ C, 1; Mead 0 0 IV, Iv, (7) 0 1 0 0 1 I Vv, 0 C,+C CI, CI AL rn tt ry v. 0 0 my.
MV, 1 Y TY 2 1 2 rol C ir Cl.
Cl +C I 0 0 Lv, Ly, (8) 0 0 0 0 0 0 Vv. 0 e) establishing a vehicle path tracking control system by formula (9): X(1) = (4, + ADx(1) + Bo(u(®)) + d(1) 9 z(t) = C.x(1) ©) 5 where, C, denotes a fourth-order identity matrix, u(t ) eR” where R” denotes an n-dimensional real space, out) =[o(u (1), o(u,(2)),---, ou, (6))] , U ars it u, (¢) > U max 0 (u, (0) 7 u, (£), if == U arr = u, (f) < Une i=1 2 Rh TU max? if U, (7) < “Ua where, Wimax denotes a maximum value of u, (¢ ) , and U, (¢ ) denotes the i element of U(?) : f) establishing a state feedback path tracking controller by formula (10): u(t) = Kx(t—7(1)) (10) where, T(t ) denotes a delay, T(t ) 7 +7,, T, denotes a transmission
-6- delay of a control signal from the sensor to the controller, 7, denotes a delay of a control signal from the controller to an actuator, and K denotes a control gain matrix to be designed, g) establishing a closed-loop system for controlling the path tracking of the autonomous vehicle by formula (11): (1) = (4, +AA)x(E) + Bo(Kx(t — (1) + d(t)
11 =(£) = Cx(1) (1h) wherein when d(#)=0 | the closed-loop system for controlling the path tracking of the autonomous vehicle established by formula (11) 1s asymptotically stable; when d(t) #0 the robust H „ disturbance suppression performance index }7 is calculated by formula (12); Lr 2f gr | 27 (Dz(Ddt Sy | d" (t)d(t)dt 12) h) calculating positive definite matrices X >0 and Q > 0, general matrices Y, , Y, , and N ; , and the quantity O > 0 to satisfy the linear matrix inequality shown in formula (13), where i =1,2,3;
7e — — — 5 ) ï ~T An En EB, { N, oF XI AC, + =, 2, 0 NM 0 0 0 * tE.
I N, OF 0 0 xk * * vl] 0 0 0 0 Q,= nev <0 * * * * TO 0 0 0 (13) * * * * * 9/7 0 0 x x * ze x * —0f 0 sk sk xk sk % xk % JI u? y _ N ae } . . ma IW <0, i=1,2,...,0 Vai —p X where, * in formula (13) denotes the transposition of the symmetric elements of the matrix, and V 1 denotes a performance index. =, = A,X +XA +N, +N], — : 17 UT 2, =BS(v, YY) N,+N,, _ T TT Sp 7 XA, + N, > _ 7 UT Ep = NN, _ ’ TT Soy = [BS (4, Y,,Y,)] —N;, =,=70-2X ViVi t+ (1 u VO Sk, ,)= : Vin + (1 = V, Vi HY += Hi) Su, Y, > Y, )] = . Hoy Vin + (1 = H, Von where, Vri denotes the i" line of Y. where i=12,..., n.
Vhi denotes the /" line of Y, , where I= L, 2, on: Vi denotes the i element of V ,
-8- where I =1,2,....1 : H, denotes the i™ element of MH ‚ where i=L2,....n.
T denotes an upper bound of delay T(t ) ‚ Pand Una both denote a positive constant, vel, uel’, V = {w eR" :w =lor 0} 1) calculating a gain matrix of the vehicle state feedback controller by formula (14):
_ ~1 K=Yx" 14 and solving the convex optimization problem in formula (15) to obtain the optimal robust H state feedback path tracking controller: min y, st.
Q, <0, X > 0, O0 >0, u (15) YY, Ni=12,3,ò>0 Further, in step a), the lateral force F yr of the front tire of the vehicle and the lateral force F w of the rear tire of the vehicle are calculated by the formulas Fy =2C f a, > Fy = -2C., , where C, denotes a cornering stiffness of the front wheel, C, denotes a cornering stiffness of the rear wheel, a, denotes a cornering angle of the front wheel, CX. denotes a cornering angle of the rear wheel, — 0. — Lr — Yy = Lr — Vy and Fr = 9 » Oy = : Vv, Vv, Vv, Vv Preferably, the curvature fs in step b) is obtained by a global positioning system (GPS) combined with a geographic information system (GIS). Further, after step g), the method further includes the following steps:
29. 7 ‚ 2 C X= } . h2) selecting an output vector J 2 7. 9. > el ‚ and calculating the positive definite matrices X, >0, X,>0, Q>0, general matrices Ve, +, ‚ and N i , and quantity 0>0 to satisfy the linear matrix inequality shown in formula (16), where 1 =1,2.3 Z, 8, Es I No XF' XC! + 5,082, 0 NM 0 0 0 + + 2. I NO 0 0 2 * * * vl 0 0 0 0 y 1 ml < 0 xk * % xk —7 . TO 0 0 0 16)
+k +k +k +k sk —0f 0 0
+k +k +k +k sk +k —0f 0 xk +k x +k xk x +k —7 u? 7 ma hi . a "<0, i=12,..,n Nui -p X where, * in formula (16) denotes the transposition of the symmetric elements of the matrix, and y | denotes the performance index;
-10- =, =A4,X+X4 +N, +N/, S BSV FT) NNT =p = BSV, YY) N, +N,, S= VAT NT =13 = XA, + N, 2 r— A7 AT Ey =—N,—N,, = vv UT ArT ZE, =[BS(4, 1 Y,)] — Ny, E,,=70-2X, X = NX NG +GX GG , U T v _ T Y,=YG JY, =YG ? ViVi + (1 VOY Sw, Yr) = , Vo Vi + (1 V, VV in hy, +1=p)y, S(p,Y, Y= : Ho Vin + (1 H, Vn where, Vi denotes the i" line of Y, where i=12,....n : Vhi denotes the i line of XY, , where i=1L2,...n : V, denotes the i element of V , where i=12,....n : H, denotes the i" element of H ‚ where i=12,....n : where, T denotes the upper bound of delay T({ ) , Pand Umar both denote a positive constant, vel, uel, V = fw eR":w =lor 0} . 12) calculating the gain matrix of the vehicle output feedback controller by formula (17): vv -1 K=rX (17) wherein the column of N, is a basis of a null space of the output matrix €, and
-11- the matrix G is calculated by formula (18): G=Cl+N,L L=NIXCT(C XC (1%) where, Cl = C, | (C,C, | 17! denotes the Moore-Penrose generalized inverse matrix of the matrix C,, and N J denotes the Moore-Penrose generalized inverse matrix of the matrix N,,.
The advantages of the present disclosure are as follows. The robust Hoo path tracking controller is designed to solve the problems such as network delays and input saturation during the control of path tracking of the autonomous vehicle and improve the path tracking performance of the vehicle under extreme driving conditions. The lateral velocity and the yaw rate of the vehicle are adjusted to improve the vehicle steerability and stability as well as achieve path tracking control of the autonomous vehicle. The robust Hoo path tracking control gain matrix for the autonomous vehicle can be obtained by solving the linear matrix inequality, which is easy to compute. The uncertainty of the vehicle dynamics model and effects of external disturbances are considered in this path tracking control design, which improves the robustness of the path tracking control algorithm. A static output feedback controller is designed to realize ideal path tracking control as well as significantly cut down the cost of the control system.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic diagram showing the vehicle dynamics model of the present disclosure; and FIG. 2 1s a schematic diagram showing the vehicle path tracking of the present disclosure.
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DETAILED DESCRIPTION OF THE EMBODIMENTS The present disclosure will be further described hereinafter with reference to FIG. 1 and FIG. 2. A method for controlling path tracking of an autonomous vehicle with input saturation includes the following steps: a) A vehicle dynamics model is established by formula (1), as shown in FIG. 1. 1 al = (FE) vd m . 1 1 1) y=(LF LF, )+—AM_+d,(1) LN: "IJ where, v, denotes the first derivative of Vv, , y denotes the first derrvative of Y, V. denotes a longitudinal velocity of a center of mass CG of a vehicle, V, denotes a lateral velocity of the center of mass CG of the vehicle, 2 denotes a yaw rate of the vehicle, 77? denotes the mass of the vehicle, 1 z denotes a rotational inertia of the vehicle about the Z -axis, d 1 (£ ) and d 2 (1 ) both denote unmodeled dynamics, F yr denotes a lateral force of a front tire of the vehicle, and FE, denotes a lateral force of a rear tire of the vehicle; an external yaw moment AM z IS calculated by formula (2); 2 | 4 : { . o i : AM, => Fl, cosó +1 sing 1+) CDF, 6) i=1 i=3 where, F, denotes a longitudinal force of the /" tire, l f denotes a distance from the center of mass CG of the vehicle to a front axle, / + denotes a distance from the center of mass CG of the vehicle to a rear axle, / + denotes a wheelbase, and 0 f denotes a steering angle of a front wheel; b) A path tracking model is established by formula (3), as shown in FIG. 2.
-13- ¢ Ve) e 0] (8) $ where, [ s denotes a horizontal distance between the center of mass CG of the vehicle and a sensor, y e denotes a lateral offset , distant from the center of mass CG of the vehicle, and 9, denotes a heading error.
An actual yaw angle @ of the vehicle is calculated by formula (4): ¢ = Ó, + Ó, (4) where, ¢, denotes a yaw angle of a tangent direction of a reference path relative to a global coordinate system, when the vehicle follows the reference path with a curvature of Pref at the longitudinal velocity V, , Ó, = vp ref , where Ó, denotes the first derivative of Ó, c) A dynamic path tracking model is established by formula (5).
X(t) = Ax(£) + Bu(t) + d(¢) (5) where, X(#) denotes the first derivative of X(£), X(f) denotes a state 7 variable, X(f)= [v,, V,9,, 3,1 | T denotes a matrix transpose, (1) denotes 7 an input variable, u(t) = [ò, AM] ‚ and 7 d(t) = [a © d,(t) VP AL oop | ‚the system matrix A and the system matrix B are calculated by formula (6),
-14- Cc, +C Cd, Cl dn ALE v‚ 0 0 my, my, } “1 1 ~ 72 -~v 72 gl Cd, Ct, 5 C+ 00 Iv, Iv, 0 1 0 O 1 [ v. 0 | . © m I B= : 1 0 — 0 0 I,
d) A change in the longitudinal velocity V, of the vehicle changes is expressed by the formula 1/ Vv. = (1+ A, )/ V_, where A, denotes a time-varying parameter and | A, |< 1, V. denotes a nominal value of V, ‚the system matrix A is expressedasd =A, + A4, where Ad=EMF, M =A, and F denotes an identity matrix; A, is calculated by formula (7), and £ is calculated by formula (8); CC +C.
CA Cl ee tt Oy, 0 0 MV, MV, . Cl, -Cl, C+, 4, = 44 rr 44 er 0 0 Iv, Iv, (7) 0 1 0 0 1 I Vv, 0 Cc, +C cl, Cl LA L450 0 my, MV, 1 7 p2 + 2 rol Cd, Cl.
Cl +C I 0 0 0 0 0 0 0 0 Vv. 0
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e) In order to complete the task of controlling the path tracking of the autonomous vehicle, the lateral offset y, and the heading error ¢_ of the vehicle should be as small as possible.
Moreover, the lateral stability of the vehicle can be improved by adjusting the lateral velocity and yaw angle.
Further, in consideration of saturation characteristics of the actuator, a vehicle path tracking control system is established by formula (9):
x(t) = (A, + Ax (1) + Bo (u(t) + d(t)
9
=(t) = C,x(1) (9)
where, C, denotes a fourth-order identity matrix, % ({ ) e R" , where R” denotes an n-dimensional real space,
| 7 o(u(t)) = [o(%, (¢ )), o(u, (1)), tS o(u, (¢ ))] > Ua» if u, (1) > U nar o(u,®)=3u), if-u,, <u()<u,, [0 on TU ax > if ú, (7) < “Ux where, Umax denotes a maximum value of U, (¢ ) , and u, (¢ ) denotes the i element of 24(Z)
f) A state feedback path tracking controller is established by formula (10):
u(t) = Kx(t—7(t)) (10) where, T(t ) denotes a delay, in the vehicle path tracking control system based on network control, the vehicle status and control signals generally have varying degrees of delay and packet loss during the transmission process, and T(t ) —=7, +7,, where 7; denotes a transmission delay of a control signal from the sensor to the controller, 7, denotes a delay of a control signal from the controller to the actuator, and K denotes a control gain matrix to be designed.
-16- g) A closed-loop system for controlling the path tracking of the autonomous vehicle is established by formula (11). X(1)=(A4, + AA)x(1) + Bo(Kx(t —7(1))) + d(¢) 11 =(1) = Caf) (1) The goal of controlling the path tracking of the autonomous vehicle is achieved by designing the robust H state/output feedback controller.
When d()=0 the closed-loop system (11) is asymptotically stable.
When d(t) #0 the robust H oo disturbance suppression performance index 1 is calculated by formula (12). 2 (0z()de <7 [dT (Dd(Dd 2 (0)z(0)de < yd" (Wd (dt a h) The robust H state feedback controller and the static output feedback controller are designed to solve the problems of network delay and input saturation during the control of the path tracking of the autonomous vehicle.
When d(t)=0 | the closed-loop system is asymptotically stable and satisfies the given HA disturbance suppression performance index, and the control gain matrix can be obtained by solving the corresponding linear matrix inequality, which is easy to compute.
The positive definite matrices X >0 and Q > 0, general matrices Ye , Y, , and N, , and the quantity Ô> 0 are calculated to satisfy the linear matrix inequality shown in formula (13), where i =1,2.3;
-17- = = = NT \ r ~T An En EB, { N, oF XI AC, + =, 2, 0 NM 0 0 0 * tE.
I N, off 0 0 * * Sy 0 0 0 0 Q,= nev <0 * x x x TO 0 0 0 (13) * * * * *% 9/7 0 0 +k * + * * + 0/7 0 * * xk x* * xk * JI u? y ~ Himax hi . ; 1150, i=L2,...n Voi p X where, * in formula (13) denotes the transposition of the symmetric elements of the matrix, and V 1 denotes a performance index. _ TT 77 Zi =A4A,X+X4, +N, +N, _ 17: IT =p = BS(v.Y,.Y,)-N, +N, 5 =, =XA +N! _ x7 FT 92 = —N, 7 N, > _ T x37 Zs =[BS (1, Ys Yl — N; > ZE =70-2X Viva TU=v)y, Sv.
YY) = : V, J kn + (1 = V, )y hn Het A= U) Vi SY, Y= : Ho Yim + (1 == U ) Vu where, Vri denotes the i* line of Y, where i=12,..., n.: Vhi denotes
-18- the i® line of Y, ‚ where I= 1, 2, on: V, denotes the i element of V , where i=12,...n : LU, denotes the i™ element of ye , where i=12,....n : T denotes the upper bound of delay T(t ) ‚ Pand U,,,. both denote a positive constant, vel, uel’, V = {w eR" :w =lor 0} 1) The gain matrix of the vehicle state feedback controller is calculated by formula (14): _ ~1 K=YX (14) The convex optimization problem in formula (15) is solved to obtain the optimal robust 7 state feedback path tracking controller. min jy, st.
Q,<0,X>0,0>0, (15) 7 . _ X YY, N.,i=123,0>0 Embodiment 1: Preferably, in step a), the lateral force Fy of the front tire of the vehicle and the lateral force EF, of the rear tire of the vehicle are calculated by the formulas by = 2C, a 1 Lk, = -2C.a, , where C, denotes a cornering stiffness of the front wheel, C, denotes a cornering stiffness of the rear wheel, a denotes a cornering angle of the front wheel, CX, denotes a cornering angle of the rear wheel, and JS J > Mp Embodiment 2: the curvature ef in step b) is obtained by a global positioning system (GPS)
-19- combined with a geographic information system (GIS). Embodiment 3: The robust A state feedback controller and the static output feedback controller are designed to solve the problems of network delay and input saturation during the control of the path tracking of the autonomous vehicle.
When d(1)=0 | the closed- loop system is asymptotically stable and satisfies the given H, disturbance suppression performance index, and the control gain matrix can be obtained by solving the corresponding linear matrix inequality, which is easy to compute.
Therefore, after step g), the method further includes the following steps: h2) Since it is difficult to measure the lateral velocity v, of the vehicle by low- cost sensors, in order to diminish the cost of the control system, an output vector 7 =(C,x = : : : y 2 7. 9. ‚Jy A is selected, the static output feedback path tracking controller is designed, and the positive definite matrices X, >0, X,>0, 0>0, general matrices Y. +, , and N i , and quantity 0> 0 are calculated to satisfy the linear matrix inequality shown in formula (16), where i=1,2,3 ; ~ = = Yi . 7 7 HZ, EZ, 1 N, oF XF XC, + 2 E, 0 NM 0 0 0 + + =. I NE 0 0 2 xk xk * vl 0 0 0 0 y 1 mi < 0 * +k +k * T 70 0 0 0 (16) % +k +k +k +k —0f 0 0 +k +k +k +k +k +k —of 0 + xk x xk xk x xk —7
-20- u? y imax hi . 7 A7 <0, i=l2,...n Yi —pP where, * 1n formula (16) denotes the transposition of the symmetric elements of the matrix, and y | denotes the performance index;
= U TU AT A7 vz
HE, =A4,X+X4, +N, +N, ,
= _ CT UN AN WT
—12 = BS(v.Y..Y,)-N, +N, ’
= VAT A7
Ez = AA, +N,
= _ ONT ArT
—22 = —N 2 N 20
= TTT WT
3 = [BS(4, YY, )] —N, >
HE, =TO-24X,
X= Ny X (Ny + GX,G',
U T v _ T
Y, = VG ‚TY, = TG >
Via + (1 u VO) Vi S(11.7,.7,) = Va Ven + (1 = V, Von LV += HM) Vn Su, 1, ,Y,)]= : Hy Vi + (1 H, Von where, Vri denotes the f! line of Y, , where i=l2,...n : Vhi denotes the i line of T, , where i=12,...n : V; denotes the i" element of V ‚ where i=12,...,n : U, denotes the 7! element of H ‚ where i=12,....n ;
where, T denotes the upper bound of delay T(t ) ‚ Pand Umar both denote a positive constant, vel”, uel’, V = fw eR" :w =1lor 0}
21-
12) The gain matrix of the vehicle output feedback controller is calculated by formula (17): 1-1 K=} A (17) The column of N, is a basis of a null space of the output matrix C,, and the matrix G is calculated by formula (18): G=C,+N,L _ NT 7 yl (18) L=N!xclc,xclhy C=C (CC) ized where, Ly 1, ( 2% ) denotes the Moore-Penrose generalized inverse matrix of the matrix C,, and N 0 denotes the Moore-Penrose generalized inverse matrix of the matrix N,.
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