Speed control system for a vehicle

• US 4,843,553 A
• Filed: 06/21/1988
• Issued: 06/27/1989
• Est. Priority Date: 07/16/1987
• Status: Expired due to Term

• Current Assignee: Toyota Jidosha Kabushiki Kaisha (Toyota Motor Corporation)
• Original Assignee: Toyota Jidosha Kabushiki Kaisha (Toyota Motor Corporation)
• Inventors: Ohata, Akira
• Primary Examiner(s): Chin, Gary
• Application Number:
  US07/209,439
• Time in Patent Office: 371 Days
• Field of Search: 364/426.04, 364/431.07, 123/352, 180/176, 180/179
• US Class Current: 701/93
• CPC Class Codes: B60K 31/047 the memory being digital
• CPC Class Codes: B60W 2050/0011 Proportional Integral Differential [PID] controller
• CPC Class Codes: B60W 2050/0031 Mathematical model of the vehicle
• CPC Class Codes: B60W 2530/16 Driving resistance
• CPC Class Codes: B60W 2710/0644 Engine speed
• CPC Class Codes: B60W 2710/0666 Engine torque
• CPC Class Codes: B60W 2710/105 Output torque
• CPC Class Codes: F16H 2059/142 of driving resistance calculated from weight, slope, or the like
• CPC Class Codes: F16H 63/50 Signals to an engine or motor

Abstract

A vehicle speed control system is provided to maintain the vehicle speed at a target value. The control system includes a target vehicle speed determining section, a section for calculating a driving torque necessary to drive the vehicle at the target vehicle speed, a section for calculating a target engine rotational speed and an engine load torque and a section for calculating a control amount for controlling an opening of the throttle valve of the engine. The driving torque calculating section and the control amount calculating section are designed based on linear control theory on physical models describing the behavior of the vehicle and the engine, respectively, thereby improving the responsiveness of the control system compared to conventional PID control. The design of the control system is characterized by separate sections which reduces designing labor and which facilitate standardization of every section.

Claims

1. A speed control system for a vehicle having an internal combustion engine, an output power thereof is adjusted by a throttle valve and is transmitted via a transmission to a driving wheel in order to control a vehicle speed, the control system comprising:

target speed determination means for determining a target vehicle speed based on at least a command from a driver of the vehicle;

first calculation means responsive to an actual vehicle speed and the target vehicle speed for calculating a driving torque at an output side of the transmission necessary to bring the actual vehicle speed to the target vehicle speed utilizing predetermined first parameters, the first parameters being determined based on a first physical model describing the behavior of the vehicle utilizing the vehicle speed as a state variable;

second calculation means responsive to the driving torque, the target vehicle speed and a gear position of the transmission for calculating a target rotational speed and a load torque of the engine;

control amount calculation means responsive to the target rotational speed, the load torque, an actual rotational speed of the engine and an intake air pressure of the engine for calculating a control amount of the throttle valve necessary to bring the actual rotational speed of the engine to the target rotational speed utilizing predetermined second parameters, the second parameters being determined based on a second physical model describing the behavior of the engine utilizing said actual rotational speed of the engine and said intake air pressure of the engine as state variables; and

throttle driving means responsive to the control amount for driving the throttle valve of the internal combustion engine.

2. A speed control system according to claim 1, wherein the target speed determination means determines the target vehicle speed Vr based on an accelerator pedal displacement θ

and the gear position Is of the transmission.

3. A speed control system according to claim 1, wherein the first calculation means calculates the driving torque Td-Tb from the following equation:

space="preserve" listing-type="equation">Td-Tb=M·

(g1·

V+Σ

g2·

(V-Vr)+g3·

Vr) +(Ae·

Cd·

V.sup.2 +μ

·

M·

g),

where M is a mass of the vehicle, V is the actual vehicle speed, Vr is the target vehicle speed, Ae is a front projected area of the vehicle, Cd is a drag coefficient, μ

is a rolling resistance coefficient, g is the acceleration of gravity and g1, g2 and g3 are parameters determined from the first physical model.

4. A speed control system according to claim 1, wherein the second calculation means calculates the target rotational speed Nr and the load torque Tl of the engine from the folowing equations:

space="preserve" listing-type="equation">Nr=c·

Vr/(Rt·

Dt·

Dd) and

space="preserve" listing-type="equation">Tl=Td/(Ce·

Dt·

Dd),

where Vr is the target vehicle speed, Rt is an effective radius of the driving wheel, Dt is a reduction ratio of the transmission, Dd is a reduction ratio of a differential, Td is the driving torque calculated by the first calculation means, Ce is a transmission efficiency and c is a coefficient.

5. A speed control system according to claim 4, wherein the second calculation means determines the load torque Tl to be 0 and actuates a brake system of the vehicle when the driving torque calculated by the first calculation means is less than 0.

6. A speed control system according to claim 4, wherein the second calculation means determines the target rotational speed of the engine to be a predetermined idling speed of the engine and the load torque Tl to be 0 when the gear position of the transmission is in neutral.

7. A speed control system according to claim 4, wherein the second calculation means determines the load torque Tl to be 0 when a clutch of the vehicle is disengaged.

8. A speed control system according to claim 1, wherein the control amount calculation means calculates the control amount S from the following equation:

space="preserve" listing-type="equation">S=f1·

N+f2·

P+Σ

f3·

(N-Nr)+f4·

Nr +f5·

(Tl+α

.sup.n 4/α

.sup.n

     3)-(α

.sup.p 3/α

p2)·

P·

N

where N is the actual rotational speed of the engine, P is the intake air pressure of the engine, Nr is the target rotational speed of the engine, Tl is the load torque, and f1, f2, f3, f4, f5, α

ⁿ 4/α

ⁿ 3 and α

^p 3/α

^p 2 are parameters determined from the second physical model.