System for determining skew stiffness

• US 5,931,880 A
• Filed: 10/30/1996
• Issued: 08/03/1999
• Est. Priority Date: 11/30/1995
• Status: Expired due to Fees

• Current Assignee: Robert Bosch GmbH
• Original Assignee: Robert Bosch GmbH
• Inventors: Brachert, Jost
• Primary Examiner(s): NGUYEN, TAN QUANG
• Application Number:
  US08/739,547
• Time in Patent Office: 1,007 Days
• Field of Search: 701/38, 701/41, 701/42, 701/72, 701/82, 701/83, 701/90, 701/91, 180/197, 180/422, 303/140, 303/146
• US Class Current: 701/38
• CPC Class Codes: G05D 1/0891 specially adapted for land vehicles

Abstract

The yawing motion, the float angle, the longitudinal velocity of the vehicle, the front wheel steering angle, and optionally the rear wheel steering angle are determined. When certain driving conditions are present, at least the variable representing the front skew stiffness is determined as a function of the determined variables. In an alternative embodiment of the invention, the detection of the float angle is omitted. The variable representing the front skew stiffness is then calculated as a function of the detected yawing motion and the detected longitudinal velocity of the vehicle and as a function of a fixed, predefined value representing the rear skew stiffness. This calculation, too, occurs only when certain driving conditions are present.

Claims

1. Method for controlling the actual motion of a vehicle, said method comprising determining input variables comprising yaw velocity φ

, float angle β

, longitudinal vehicle velocity v, front wheel steering angle δ

_v, and optionally a rear wheel steering angle δ

_h,

determining when the vehicle is undergoing steady state travel around a curve,

determining a front skew stiffness c_v and optionally a rear skew stiffness c_h based on said input variables which are determined when said vehicle is undergoing steady state travel around a curve,

calculating a desired vehicle motion based on said front skew stiffness c_v and optionally said rear skew stiffness c_h, and

controlling said vehicle so that the actual vehicle motion conforms to the desired vehicle motion.

2. Method as in claim 1 wherein said step of determining when said vehicle is undergoing steady state travel around a curve comprises

determining a yaw acceleration φ

" based on said yaw velocity φ

'"'"', and

comparing the absolute value |φ

"| of said yaw acceleration with a threshold S1, and

determining that steady state travel around a curve is present when |φ

"| falls below S1 for a predetermined period of time t_abgl.

3. Method as in claim 2 wherein said step of determining when said vehicle is undergoing steady state travel around a curve comprises

determining a float angle velocity β

'"'"' based on said float angle β

,

comparing the absolute value β

'"'"'| of said float angle velocity with a threshold S2, and

determining that steady state travel around a curve is present when |φ

"| falls below said threshold S1 and |β

'"'"'|

falls below said threshold S2 for a predetermined period of time t_abgl.

4. Method as in claim 1 further comprising filtering said determined front skew stiffness c_v and optionally said determined rear skew stiffness c_h in a low pass filter prior to calculating said desired vehicle motion.

5. Method as in claim 1 wherein said front skew stiffness c_v and optionally said rear skew stiffness c_h is stored in a non-volatile memory cell and subsequently used for either open loop control or closed loop control of the actual vehicle motion.

6. Method as in claim 1 further comprising

determining rational speeds of the non-driven vehicle wheels,

determining said yaw velocity φ

'"'"' based on said longitudinal vehicle velocity v and said rotational speeds of said non-driven wheels.

7. System according to claim 1, characterized in that the determination of the variable (c_v) representing the front skew stiffness is determined according to the equation:

##EQU8## where;

φ

'"'"'=the detected yaw rate;

β

=the detected float angle;

v=the detected longitudinal velocity of the vehicle;

δ

_v =the detected front wheel steering angle;

l_v =the distance of the center of gravity from the front;

l_h =the distance of the center of gravity from the rear;

m_g =the total weight of the vehicle; and

l_g =l_v +l_h.

8. Method for controlling the actual motion of a vehicle, said method comprising

determining input variables comprising yaw velocity φ

'"'"', longitudinal vehicle velocity v, front wheel steering angle δ

_v, and rear wheel steering angle δ

_h,

determining when the vehicle is undergoing steady state travel around a curve,

determining a front skew stiffness c_v based on said input variable, which are determined when said vehicle is undergoing steady state travel around a curve, and a predetermined value c_h for the rear skew stiffness,

calculating a desired vehicle motion based on said front skew stiffness c_v, and

controlling said vehicle so that the actual vehicle motion conforms to said desired vehicle motion.

9. Method as in claim 8 wherein said step of determining when said vehicle is undergoing steady state travel around a curve comprises

determining a yaw acceleration φ

" based on said yaw velocity φ

'"'"', and

comparing the absolute value |φ

"| of said yaw acceleration with a threshold S1, and

determining that steady state travel around a curve is present when |φ

"| falls bellow S1 for a predetermined period of time t_abgl.

10. Method as in claim 8 further comprising filtering said determined front skew stiffness c_v in a low pass filter prior to calculating said desired vehicle motion.

11. Method as in claim 8 wherein said front skew stiffness is stored in a non-volatile memory cell and subsequently used for either open loop control or closed loop control of the actual vehicle motion.

12. Method as in claim 8 further comprising

determining rational speeds of the non-driven vehicle wheels,

determining said yaw velocity φ

'"'"' based on said longitudinal vehicle velocity v and said rotational speeds of said non-driven wheels.

13. System according to claim 8, characterized in that the determination of the variable (c_v) representing the front skew stiffness is determined according to the equation:

##EQU9## where;

φ

'"'"'=the detected yaw rate;

v=the detected longitudinal velocity of the vehicle;

δ

_v =the detected front wheel steering angle;

δ

_h =the detected rear wheel steering angle;

l_v =the distance of the center of gravity from the front;

l_h =the distance of the center of gravity from the rear;

m_g =the total weight of the vehicle;

c_h =the value predefined for the rear skew stiffness; and

l_g =l_v +l_h.

14. System according to claim 13, characterized in that the determination of the variable (c_h) representing the rear skew stiffness is determined according to the equation:

##EQU10## where;

φ

'"'"'=the detected yaw rate;

β

=the detected float angle;

v=the detected longitudinal velocity of the vehicle;

δ

_v =the detected front wheel steering angle;

δ

_h =the detected rear wheel steering angle;

l_v =the distance of the center of gravity from the front;

l_h =the distance of the center of gravity from the rear;

m_g =the total weight of the vehicle;

c_v =the determined value representing the front skew stiffness; and

l_g =l_v +l_h.