METHOD FOR CONTROLLING A MOTOR VEHICLE IN EMERGENCY STEERING MODE BY MEANS OF FRONT WHEEL BRAKE-BASED TORQUE VECTORING

Abstract

A method can be used to control a steer-by-wire steering system in an emergency steering mode. The method comprises checking a steering system for the presence of a fault state and upon detection of a fault implementing the emergency steering mode, which involves determining a setpoint position of a steering tie rod using a setpoint wheel steering angle, determining a front wheel to be braked and a brake pressure to attain the setpoint position with a control unit, transmitting the front wheel to be braked and the brake pressure to a brake system, braking the front wheel to be braked, and increasing a torque provided by a wheel drive to compensate for a loss of speed of the motor vehicle caused by the braking of the front wheel to be braked.

Description

The present invention relates to a method for controlling a steer-by-wire steering system for a motor vehicle having the features of the preamble of claim 1, and to a motor vehicle that is designed to carry out this method.

In steer-by-wire steering systems, the position of the steered wheels is not directly linked to the steering wheel. There is a connection between the steering wheel and the steered wheels via electrical signals. The driver's steering demand is picked up by a steering angle sensor, and the position of the steered wheels is controlled by means of a steering actuator in a manner dependent on the driver's steering demand. No mechanical connection to the wheels is provided.

In the normal mode, the controller operates the steer-by-wire steering system and constantly checks that the system components of the steering system are functioning properly. If a fault occurs, the function of the steer-by-wire steering system is deactivated. A mechanical fallback level may be provided, which allows an emergency steering mode. However, such mechanical fallback levels are expensive.

It is an object of the present invention to specify a method for controlling a steer-by-wire steering system for a motor vehicle that allows an emergency steering mode without a mechanical fallback level.

This object is achieved by a method for controlling a steer-by-wire steering system having the features of claim 1, and by a steer-by-wire steering system that is configured to carry out such a method. Further advantageous embodiments of the invention can be found in the dependent claims.

Accordingly, a method for controlling a steer-by-wire steering system for a motor vehicle in an emergency steering mode is provided, wherein the motor vehicle comprises two axles each with two wheels, which are connected to one another via a steering tie rod of a steering system, wherein the front two wheels are steerable by means of a front-wheel steering system, and the motor vehicle comprises a single wheel drive which is assigned to one of the two axles and which drives the two wheels of the corresponding axle via a differential, wherein the wheel drive comprises a single actuator, and wherein the motor vehicle comprises a brake system, and the method comprises the following steps:

• • checking the steering system for the presence of a fault state,
  • implementing the emergency steering mode in the event that a fault state has been detected,
  • wherein the following steps are carried out in the emergency steering mode:
  • determining a setpoint position of the steering tie rod using a setpoint wheel steering angle,
  • determining a front wheel to be braked and a brake pressure to attain the setpoint position by means of a control unit,
  • transmitting the front wheel to be braked, and the brake pressure, to the brake system, and braking the front wheel to be braked,
  • increasing a torque provided by the wheel drive in order to compensate for a loss of speed of the motor vehicle caused by the braking of the front wheel to be braked.

The brake-based torque vectoring allows the motor vehicle to be steered even in a fault state, in particular in the event of failure of the steering system, without the need for a mechanical fallback level.

The differential is a controllable differential. It is in particular an open or partially open differential.

A setpoint wheel steering angle is preferably determined for each of the vehicle wheels; the setpoint wheel steering angle of the left-hand and right-hand vehicle wheels may be identical or may form different angles.

The control unit for determining the front wheel to be braked and the brake pressure preferably comprises software for arbitration.

It is preferable if the chassis geometry, the properties of the brake system and the sign of the setpoint toothed rack position are input into the software in order to determine the front wheel to be braked and the brake pressure.

In one embodiment, the wheel drive is a rear-wheel drive which, in the emergency steering mode, provides the same additional torque for both rear wheels, such that the sum of the two additional torques compensates for the loss of speed.

Provision may also be made for the wheel drive to be a front-wheel drive with an open differential which, in the emergency steering mode, drives the unbraked front wheel, specifically with the sum of the torques of the two front wheels and with the additional torque for compensating for the loss of speed. The following relationship preferably applies for a right-hand bend: T_FL+T_FR=2*T_FL+T_ped,br, where T_FL and T_FR are the torque of the left-hand and right-hand front wheels and T_ped,br is the braking torque introduced into the right-hand front wheel that is to be braked. The following relationship preferably applies for a left-hand bend: T_FL+T_FR=2*T_FR+T_ped,br, where T_ped,br is the braking torque introduced into the left-hand front wheel that is to be braked.

Provision may very generally be made for the setpoint wheel steering angle to be determined using a steering torque that is introduced into a steering means by a driver, or to be specified by an autonomous or semi-autonomous driving mode.

The object is furthermore achieved by a motor vehicle that is configured to carry out the method described above. The motor vehicle preferably has a steering-head angle which is at a minimum and a scrub radius which at a maximum.

Preferred embodiments of the invention will be discussed in more detail below with reference to the drawing. Identical or functionally identical components are provided in this case with the same reference signs throughout the figures.

In the drawings:

FIG. 1 is a schematic illustration of a motor vehicle with front-wheel drive having a single drive motor,

FIG. 2 is a schematic illustration of a motor vehicle with front-wheel drive having two drive motors,

FIG. 3 is a schematic illustration of a motor vehicle with rear-wheel drive having one drive motor and front wheel brake-based torque vectoring,

FIG. 4 is a schematic illustration of a motor vehicle with front-wheel drive having one drive motor and front wheel brake-based torque vectoring, and

FIG. 5 shows a block diagram of a controller of the motor vehicle with front wheel brake-based torque vectoring.

FIG. 1 schematically illustrates a motor vehicle 1 with two axles 10, 20 and four wheels FL,FR,RL,RR, wherein only the front wheels FL,FR are drivable (front-wheel drive) and the drive 2 of the front wheels FL,FR is arranged on a front axle 10. The drive 2 is an electric motor. The front axle 10 comprises, in relation to a direction of travel, a left-hand steerable front wheel FL and a right-hand steerable front wheel FR that are connected to one another via a toothed rack 3 of a rack-and-pinion steering gear 4. When the toothed rack 3 is displaced to the right or left transversely with respect to the direction of travel, the wheels FL,FR are pivoted about a respective pivot point.

The driver introduces a steering torque T_sw into a steering means, in particular a steering wheel of a steer-by-wire steering system. A setpoint wheel steering angle of the steerable front wheels α_RW,ref and a setpoint toothed rack position S_R,ref are determined from this steering torque T_sw. The toothed rack 3 is thereupon moved by means of the rack-and-pinion steering gear 4 until it reaches an actual toothed rack position S_R and the wheels assume a wheel steering angle α_RW.

When driving through a right-hand bend, as illustrated in FIG. 1, the drive torque is distributed uniformly to both front wheels FL,FR by means of the front-wheel drive, that is to say the traction force is the same for both front wheels, F_FL=F_FR.

FIG. 2 likewise shows a front-wheel drive known from the prior art, which has two separate actuators 2,22. A left-hand wheel drive motor 220 is arranged on the left in the direction of travel, and a right-hand wheel drive motor 221 is arranged on the right in the direction of travel. The wheel drive motors 220,221 are each connected via drive shafts 5 to the steerable front wheels FL,FR. The wheel drive motors 220,221 are electric motors. The front wheels FL,FR of the front-wheel steering system are connected to one another via a toothed rack 3 of a rack-and-pinion steering gear 4. The rack-and-pinion steering gear 4 is controlled as in the case of the steer-by-wire steering system of FIG. 1, but the drive control is implemented such that a differential torque ΔT between the front wheels FL,FR is generated which is proportional to the setpoint wheel steering angle α_RW,ref of the steerable front wheels FL,FR or to the driver's steering demand. In other words, the setpoint wheel steering angle α_RW,ref of the steerable front wheels FL,FR is incorporated into the control of the front-wheel drive. When driving through a right-hand bend as illustrated in FIG. 2, the traction force for the left-hand front wheel is xN (for example 100N)+□ΔT/2 and the traction force for the right-hand front wheel is xN-ΔT/2. The differential torque leads to a displacement of the toothed rack and thus to a steering operation.

FIG. 3 shows an exemplary embodiment of the invention. The motor vehicle 1 has a front-wheel steering system and a rear-wheel drive. The front wheels FL,FR of the front-wheel steering system are connected to one another via a toothed rack 3 of a rack-and-pinion steering gear 4. The rear-wheel drive has a single actuator 2, in particular an electric motor, which drives the rear wheels via a differential. In the event that the steer-by-wire steering system fails, that is to say the front-wheel steering system is no longer available, the motor vehicle switches to an emergency steering mode. In this emergency steering mode, the steering torque is provided by braking one of the front wheels FL,FR. A setpoint toothed rack position S_R,ref is calculated in a manner dependent on the setpoint wheel steering angle α_RW,ref. The toothed rack position is controlled by means of a controller that comprises software for arbitration. The chassis geometry, the properties of the brake system and the sign of the setpoint toothed rack position S_R,ref are input into this software in order to determine a front wheel FR,FL to be braked and the brake pressure required for the braking operation. In order that the motor vehicle 1 does not lose speed as a result of the braking operation, the rear-wheel drive provides an additional torque at the rear wheels RR,RL, which additional torque corresponds to the traction force F_ped,br and compensates for the loss of speed. A position of an accelerator pedal of the motor vehicle, preferably an accelerator pedal angle, and a position of a brake pedal, preferably a brake pedal angle, are transmitted to the controller in order to detect acceleration or deceleration of the motor vehicle and, from this, to calculate the additionally required torque.

FIG. 3 shows driving through a right-hand bend. The setpoint toothed rack position S_R,ref and the setpoint wheel steering angle α_Rw,ref are also incorporated into the calculation of the braking torque T_ped,br provided by the right-hand front wheel. A drive controller of the rear-wheel drive drives the right-hand rear wheel RR and left-hand rear wheel RL correspondingly, each of which imparts a traction force of xN (for example 100N)+F_ped,br/2, where F_ped,br is the force that compensates for the braking torque T_ped,br.

In the emergency steering mode, the motor vehicle can be steered by way of front wheel brake-based torque vectoring, without drive-based torque vectoring, despite the fact that the drive comprises only a single electric motor. An additional mechanical fallback level can thus be omitted, whereby costs and weight can be saved.

FIG. 4 illustrates a motor vehicle 1 with front-wheel drive and front-wheel steering system. The front wheels FL,FR of the front-wheel steering system are connected to one another via a toothed rack 3 of a rack-and-pinion steering gear 4. The front-wheel drive has a single actuator 2, in particular an electric motor, which drives the front wheels FL,FR via an open differential (without locking device) or a partially open differential. In the event that the steering system fails, that is to say the front-wheel steering system is no longer available, the motor vehicle 1 switches to an emergency steering mode. In this emergency steering mode, the steering torque is provided by braking one of the front wheels FL,FR. A setpoint toothed rack position S_R,ref is calculated in a manner dependent on the setpoint wheel steering angle α_RW,ref. The toothed rack position is controlled by means of a controller that comprises software for arbitration. The chassis geometry, the properties of the brake system and the sign of the setpoint toothed rack position S_R,ref are input into this software in order to determine a front wheel to be braked and the brake pressure. In order that the motor vehicle 1 does not lose speed as a result of the braking operation, the actuator 2 of the front-wheel drive provides an additional torque that compensates for the loss of speed. A position of an accelerator pedal of the motor vehicle, preferably an accelerator pedal angle α, and a position of a brake pedal, preferably a brake pedal angle, are transmitted to the controller in order to detect acceleration or braking of the motor vehicle in order to calculate the additional torque.

The following relationship applies to the right-hand bend illustrated in FIG. 4:

T_FL+T_FR=2*T_FL+T_ped,br, where T_FL and T_FR are the torque of the left-hand and right-hand front wheels and T_ped,br is the braking torque introduced into the front wheel FR to be braked.

In this case, the brake-based torque vectoring constitutes a particularly favorable and simple emergency steering mode, which allows the motor vehicle 1 to be steered after a failure of the steering system, without the need for a mechanical fallback level.

All embodiments preferably have in common the fact that a steering-head angle is at a minimum and a scrub radius is at a maximum, in order that a steering operation or a translation of the toothed rack can already be brought about by a small amount of brake pressure on the front wheel FL,FR to be braked.

A steering operation and/or emergency steering operation can be initiated both by a driver by turning a steering wheel, or moving some other steering means, and by a controller of an autonomous or semi-autonomous motor vehicle.

FIG. 5 illustrates a block diagram of a controller of the motor vehicle with brake-based torque vectoring. In a first unit 6, the steering torque T_sw introduced into a steering wheel by the driver, or a setpoint torque T_reg demanded by an autonomous driving mode, are converted into a setpoint wheel steering angle α_{RW, ref} of the steerable front wheels FL,FR. A second unit 7 determines a setpoint toothed rack position S_R,ref from the setpoint wheel steering angle α_RW,ref. The actual toothed rack position S_R and the toothed rack force F_Rack are determined in a third unit 8 from the setpoint toothed rack position S_R,ref and the braking torque T_ped,br and the acceleration torque T_{ped, acc} of the driven wheels. In a fourth unit 9, it is then determined from this how the motor vehicle and the vehicle wheels behave in the case of a constant speed and a cornering maneuver, acceleration and a cornering maneuver and during a braking operation in a cornering maneuver, with subsequent implementation for the respective vehicle state.

In the first state, the motor vehicle is driving at a constant speed v and along a bend or curved path. During the cornering maneuver, the setpoint toothed rack position S_R,ref must, as a result of a steering wheel being turned or as a result of the front vehicle wheels being turned, assume a non-zero value because the toothed rack position changes or must change in the process. The braking force of the respective front vehicle wheels corresponds to the function of the setpoint toothed rack position F_FL,F_FR.=f(S_R,ref). In this case, for the rear vehicle wheels, this means that the traction torque of the rear vehicle wheels T_FL,T_FR is a function of the setpoint toothed rack position S_R,ref and the acceleration torque T_ped,acc(T_FL,T_FR.=f(S_R,ref, T_ped,acc)) in order to maintain the vehicle speed.

In the second state, that is to say in the case of a tangential vehicle acceleration v>0 and during a cornering maneuver S_R,ref≠0, the relationships relating to the braking force and the traction torque correspond to the 1st state: F_FL,F_FR.=f(S_R,ref) and T_ped,acc (T_FL,T_FR.=f(S_R,ref, T_ped,acc)).

In the third state, which corresponds to a braking operation, that is to say when the vehicle speed is being reduced (v<0) and the vehicle is performing a cornering maneuver or driving on a curved path S_R,ref≠0, the braking force of the front vehicle wheels is correspondingly a function of the setpoint toothed rack position and the braking torque T_ped,br F_FL,F_FR.=f(S_R,ref; T_ped,br)) The traction torque at the rear vehicle wheels is not present, and is therefore zero (T_FL,T_FR.=0).

Claims

1.-10. (canceled)

11. A method for controlling a steer-by-wire steering system for a motor vehicle in an emergency steering mode, wherein the motor vehicle comprises two axles each with two wheels, wherein the two front wheels are steerable with a front-wheel steering system and are connected to one another via a steering tie rod of a steering system of the front-wheel steering system, wherein the motor vehicle comprises a single wheel drive that is assigned to one of the two axles and that drive the two wheels of the one axle via a differential, wherein the single wheel drive comprises a single actuator, wherein the motor vehicle comprises a brake system, the method comprising: checking the steering system for the presence of a fault state; andimplementing an emergency steering mode upon detection of a fault state, wherein the following steps are performed in the emergency steering mode: determining a setpoint position of the steering tie rod using a setpoint wheel steering angle,determining a front wheel to be braked and a brake pressure to attain the setpoint position with a control unit,transmitting the front wheel to be braked and the brake pressure to the brake system,braking the front wheel to be braked, andincreasing a torque provided by the single wheel drive to compensate for a loss of speed of the motor vehicle caused by the braking of the front wheel to be braked.

12. The method of claim 11 comprising performing arbitration with software of the control unit.

13. The method of claim 11 wherein the control unit comprises software for arbitration.

14. The method of claim 13 wherein to determine the front wheel to be braked and the brake pressure, the method comprises incorporating into a calculation a chassis geometry, properties of the brake system, and a sign of the setpoint position.

15. The method of claim 11 wherein the single wheel drive is a rear-wheel drive, wherein the method comprises in the emergency steering mode providing with the rear-wheel drive a same additional torque to both of the rear wheels such that a sum of the additional torques compensates for the loss of speed of the motor vehicle.

16. The method of claim 11 wherein the single wheel drive is a front-wheel drive with an open differential, wherein the method comprises in the emergency steering mode driving with the front-wheel drive a non-braked front wheel such that a sum of torques of the two front wheels and the increased torque compensating for the loss of speed of the motor vehicle.

17. The method of claim 16 wherein the following applies while the motor vehicle travels through a right-hand bend: TFL+TFR=2*TFL+Tped,br,wherein TFL is a torque of a left-hand front wheel,wherein TFR is a torque of a right-hand front wheel,wherein Tped,br is a braking torque introduced into the front wheel to be braked.

18. The method of claim 11 comprising determining the setpoint wheel steering angle based on a steering torque that is introduced into a steering means by a driver.

19. The method of claim 18 comprising specifying the setpoint wheel steering angle by an autonomous or semi-autonomous driving mode.

20. The method of claim 11 comprising specifying the setpoint wheel steering angle by an autonomous or semi-autonomous driving mode.

21. A motor vehicle that is configured to perform the method of claim 11.

22. The motor vehicle of claim 21 wherein a steering-head angle is at a minimum and a scrub radius is at a maximum.