Vehicle traction control apparatus

Abstract: A vehicle traction control apparatus for limiting the slip of a driven wheel (10,12) determines an excessive spinning condition of the wheel in response to an excess driving torque applied from the vehicle engine. If the vehicle speed is less than a predetermined value, a braking force is applied to the wheel that is a predetermined function of the spin ratio of the wheel and when the vehicle speed is greater than the predetermined value, a braking force is applied to the wheel that is a predetermined function of the difference between the driven wheel speed and the vehicle speed.

Description: This invention relates to a vehicle traction control apparatus and, more particularly to such an apparatus which responds rapidly to excessive wheel spin during vehicle launch and which tightly controls wheel spin at high vehicle speeds. It is a common experience with automotive vehicles for excessive wheel spin to occur during vehicle acceleration when the operator initiated engine torque delivered to the vehicle driven wheels are such that the frictional forces between the tyre and the road surface are overcome. While a small amount of spin between the tyre and road surface is necessary in order to achieve a driving force, excessive spin results in the reduction of effective driving force and in the deterioration in the lateral stability of the vehicle. Various methods have been proposed for preventing an excessive spinning condition of the driven wheels of a vehicle. These methods include the adjustment of engine torque and/or the application of the brakes of the driven wheels when an excessive spinning condition is detected. Whichever method is selected for controlling acceleration wheel spin, it is desirable (A) to quickly establish control of spin if excessive spin should occur during launch of the vehicle from a standstill position to prevent large excursions of wheel spin and to maximize vehicle acceleration and (B) to control the acceleration wheel spin so as to continuously maintain lateral stability of the vehicle. Various parameters have been proposed for controlling the engine torque output or the brakes of a spinning wheel in order to limit excessive spin. One such parameter is the difference between the speeds of the driven wheel and vehicle velocity as represented by the speed of an undriven wheel. However this speed difference may be very low at low vehicle speeds, such as during the launch phase of the vehicle, even though the driven wheel may be experiencing a very large spin ratio (the difference between the driven wheel speed and vehicle speed as represented by undriven wheel speeds, divided by the driven wheel speed). For example, at a vehicle speed of 4.83 km/h (3 miles per hour), a driven wheel may be traveling at a measured speed of 9.66 km/h (6 mph) resulting in a difference in velocity of 4.83 km/h (3 mph) but yet be experiencing a 50% spin ratio. The control of wheel spin in response to the difference between the driven wheel speed and vehicle speed at low vehicle speeds may result in slow response to an excessive spin condition resulting in a large excursion of spin of the driven wheels. On the other hand, at low vehicle speeds such as during the launch phase of the vehicle, control of wheel spin in response to the spin ratio would provide a rapid response to the excessive spin condition and provide improved vehicle acceleration while maintaining lateral stability. An example of the prior art can be found in US Patent No. 4,733,760. However, if control of acceleration wheel spin were based upon the spin ratio at high vehicle speeds, the lateral stability of the vehicle would decrease since large differences between the driven wheel speed and vehicle speed may result even at low values of the spin ratio. For example, at a low vehicle speed of 16.09 km/h (10 mph), a 20% spin ratio exists when the speed differential between the driven wheel and the vehicle is 4.02 km/h (2.5 mph). However, at a vehicle speed of 64.37 km/h (40 mph), a 20% spin ratio exists when the speed differential between the driven wheel and the vehicle is 16.09 km/h (10 mph). At high vehicle speeds, control of wheel spin based upon spin ratio (as is desirable at low vehicle speeds), would allow large differential velocities resulting in a deterioration in the lateral stability of the vehicle. It can be seen that at high vehicle speeds, it would be more desirable to utilize the difference in the driven wheel speed and vehicle speed for control of the acceleration wheel spin. Such control would provide a tight limit on the wheel spin having the effect of maintaining the lateral stability of the vehicle while maximizing vehicle acceleration. A vehicle traction control apparatus in accordance with the present invention is characterised over the prior art by the features specified in the characterising portion of Claim 1. This invention provides for control of acceleration wheel spin of a vehicle so as to provide rapid response to excessive wheel spin during the launch phase of the vehicle from a standstill while providing tight control on wheel spin during high vehicle speeds. In general, this is accomplished by controlling acceleration spin in response to spin ratio at low vehicle speeds and controlling acceleration spin in response to the difference in driven wheel speed and vehicle velocity (represented by the velocity of the undriven wheels) at high vehicle velocities. Specifically, in one embodiment of the invention, the brake of a spinning wheel is controlled to apply a pressure that is a function of the spin ratio at vehicle speeds less than a predetermined value. At vehicle speeds greater than the predetermined value, the brake pressure to the spinning wheel is controlled in response to the difference in velocity between the driven and undriven wheel speeds so as to provide a tight limit on wheel spin to maintain a lateral stability of the vehicle. In addition the brake pressure may be a function of parameters such as the acceleration of the spinning wheel. The present invention will now be described, by way of example, with reference to the following description of a preferred embodiment, and the accompanying drawings, in which:- Figure 1 is a schematic block diagram of a vehicle traction control apparatus; Figure 2 is a view of the brake pressure modulator for controlling wheel brake pressure for limiting wheel slip; Figure 3 is a diagram of the traction controller of Figure 1 for controlling spinning wheel brake pressure and the air flow into the intake of the vehicle engine for control of wheel spin; Figures 4-7 are flow diagrams illustrating the operation of the traction controller of Figure 1; and Figure 8 is a graph illustrating the control principles of this invention. A vehicle traction control apparatus for a front wheel drive vehicle is illustrated in Figure 1. The vehicle has two front (driven) wheels 10 and 12 and two rear (non-driven) wheels 14 and 16. The front wheels 10 and 12 have respective (hydraulic actuated) brakes 18 and 20 actuated by manual operation of a conventional master cylinder 22 through a pair of (traction control pressure) actuators 24 and 26. As will be described, when the actuators 24 and 26 are inactive, the hydraulic fluid from the master cylinder 22 passes through the actuators 24 and 26 to the brakes 18 and 20 of the front wheels 10 and 12. Thus, the actuators 24 and 26 are transparent to the braking apparatus during normal braking of the front wheels 10 and 12. Similarly, the rear wheels 14 and 16 include a pair of (hydraulic actuated) brakes 28 and 30 operated by hydraulic fluid under pressure from the master cylinder 22 in response to manual actuation of the brakes. The vehicle includes an internal combustion engine, not shown, having an air intake passage 32 with a (manually operable) primary throttle valve 34 therein for regulating engine air intake and therefore engine operation in the conventional manner. If the engine is operated so as to deliver excessive torque to the front driven wheels 10 and 12, they will experience excessive spin relative to the road surface thereby reducing the tractive force and lateral stability of the vehicle. In order to limit the acceleration spin of the front driven wheels 10 and 12 resulting from excess engine output torque, a traction controller 36 is provided which limits spin by operating the brakes of the front driven wheels 10 and 12 and by limiting the air intake through the air intake passage 32 via a (motor driven) auxiliary throttle valve 38. In regard to the operation of the brakes of the front wheels 10 and 12 to limit spin, the traction controller 36 monitors the wheel speeds of the left and right front driven wheels 10 and 12 via speed sensors 39 and 40 and the wheel speeds of the left and right rear undriven wheels 14 and 16 via speed sensors 41 and 42 to determine whether or not an excessive slipping wheel condition exists. If such a condition is detected, the actuators 24 and 26 are operated via actuator controllers 43 for braking the left, right or both of the front driven wheels 10 and 12 experiencing an excessive slipping condition. In order to prevent the potential for damage to the brakes 18 and 20 of the front driven wheels 10 and 12 when operated to limit wheel spin while engine torque is applied to the front wheels, the traction controller 36 provides for controlling engine torque by positioning the auxiliary throttle valve 38. This is accomplished via a throttle controller 44 which provides closed loop control of the auxiliary throttle valve 38 via a motor 45 and a throttle position sensor 46 monitoring the actual position of the auxiliary throttle valve 38 to a position commanded by the traction controller 36. Additional signal inputs used for controlling acceleration spin include a throttle position signal provided by a position sensor 48 monitoring the position of the primary throttle valve 34, a speed signal RPM representing the speed of the engine such as provided by an ignition control circuit of the engine, a brake condition signal provided by a brake switch 50 closed upon actuation of the brakes of the vehicle by the conventional brake pedal 52 and a signal provided by a (manually operable) disable switch 54 closed to disable traction control at the option of the vehicle operator. Referring to Figure 2, there is illustrated a braking apparatus for one of the front driven wheels 10 or 12 including the actuator 24,26 controlled by the traction controller 36 for limiting slip of the driven wheel. In general, the braking apparatus is composed of a hydraulic boost unit 56 and brake lines 58 providing fluid communication with the brake 18,20. The brake 18,20 is illustrated as a disc brake system that includes a caliper 60 located at a rotor 62 of the vehicle wheel. A wheel speed sensing assembly at each wheel is generally comprised of an exciter ring 64 which is rotated with the wheel and an electromagnetic sensor 66 which monitors the rotation of the exciter ring to provide a signal having a frequency proportional to wheel speed. The wheel speed signals are provided to the traction controller 36 to be used to determine the wheel speed. The actuator 24,26 is illustrated in the inactive position wherein it is transparent to the braking apparatus. This is the actuator 24,26 condition during normal vehicle braking. Each actuator 24,26 in the preferred embodiment includes a DC torque motor 68 whose output shaft drives a gear train 70 whose output turns a ball screw actuator 72 comprised of a linear ball screw 74 and nut 76. As the linear ball screw 74 rotates, the nut 76 is either extended or retracted thereby positioning a piston 78 which forms a part of the nut 76. Each actuator 24,26 includes a housing 80 in which a cylinder 82 is formed. The piston 78 is reciprocally received in the cylinder 82 and defines therewith a chamber 84. The cylinder 82 has an inlet which is connected to the master cylinder 22 and an outlet which is coupled to the caliper 60 of the brake. A valve member 86 is carried by and extends from the end of the piston 78. This valve member 86 is spring biased within the piston 78 to an extended position as shown by a spring 88. When the piston 78 is in the retracted position illustrated, the fluid path between the master cylinder 22 and the brake 18 is open. When, however, the linear ball screw 74 is rotated by the DC torque motor 68 to extend the nut 76 and therefore the piston 78, the valve member 86 is seated against the opening at the inlet to the chamber 84 from the master cylinder 22 to isolate the chamber 84 and the brake 18,20 from the master cylinder 22. Once the valve member 86 is seated, further extension of the piston 78 by rotation of the DC torque motor 68 then functions to pressurize the fluid at the brake 18 to apply braking forces to the wheel. The power consumed by the DC torque motor 68 while controlling pressure is directly proportional to the rotational torque exerted by the DC torque motor on the gear train 70. The rotational torque is translated through the linear ball screw and nut 74 and 76 to the piston 78. The pressure present at the piston head is proportional to the wheel brake pressure. Therefore, the value of the current through the DC torque motor 68 is proportional to the wheel brake pressure and can be considered a measure thereof. The ball screw actuator 72 is a high efficiency actuator so that the linear ball screw 74, gear train 70 and the motor output shaft are reverse driven by the hydraulic pressure acting on the piston 78 when it is greater than the torque output of the DC torque motor 68 until the hydraulic pressure is reduced to a level where it is overcome or offset by the torque output of the DC torque motor 68. The traction controller 36 of Figure 1 takes the form of a conventional general purpose digital computer programmed to control the slip of the front driven wheels 10 and 12 in accordance with the principles of this invention. As illustrated in Figure 3, the traction controller 36 consists of a common digital computer composed of a read-only memory (ROM), a random access memory (RAM), an analogue-to-digital converter (A/D), a power supply device (PSD), a central processing unit (CPU) and an input/output section (I/O) which interfaces to a wheel speed buffer circuit 90 which functions to condition the speed signal outputs of the wheel speed sensors 39-42, the actuator controllers 43, the throttle controller 44, the brake switch 50, the disable switch 54 and the speed signal RPM. The actuator controllers 43 take the form of two conventional independent closed loop motor current controllers each of which establishes the current through the DC torque motor 68 of a respective one of the actuators 24 or 26 at a level commanded by the traction controller 36. The ROM of the digital computer of Figure 3 contains the instructions necessary to implement the control algorithm as diagrammed in the Figures 4-7. In describing the functions of the algorithm encoded in the ROM, reference to the tasks which have been detailed as flow diagram function blocks will be designated by <mm>, wherein mm is the diagram reference number and < > indicates that the concept described by the particular flow diagram function block text is being referenced. The text in the flow diagram function block describes the general task or process being executed by the traction controller 36 at that point. The specific programming of the ROM for carrying out the functions depicted in the flow diagrams of Figures 4-7 may be accomplished by standard skill in the art using conventional information processing languages. While the digital computer of Figure 3 may take any conventional form, one such form may be the single chip Motorola microcomputer MC-68HC11. Referring to Figure 4, a control cycle interrupt routine for limiting the acceleration spin of the front driven wheels 10 and 12 is illustrated. This routine is executed by the traction controller 36 at constant interrupt intervals established by an internal timing circuit. For example, the interrupt routine of Figure 4 may be executed at 10 millisecond intervals. Upon receipt of a control cycle interrupt, the traction controller 36 reads the various system inputs including wheel speeds V 1f , V rf , V 1r and V rr , engine speed, the positions of the auxiliary throttle valve 38 and the primary throttle valve 34 provided by the position sensors 46 and 48 and the discrete signal states including the open or closed state of the brake switch 50 and the disable switch 54 <91> and then determines various wheel state variables <92>. The wheel state variables include filtered values of wheel velocity and acceleration for each of the vehicle wheels 10-16. The filtering may be provided by use of a standard first order lag equation. Based upon the determined velocity and acceleration values, the spin ratio of the left front driven wheel 10 is determined by the expression (V 1f - V 1r )/V 1f where V 1f and V 1r are the determined wheel velocities of the left side wheels 10 and 14 respectively, and the spin ratio of the front driven wheel 12 is determined by the expression (V rf - V rr )/V rf where V rf and V rr are the determined wheel velocities of the right side wheels 12 and 16, respectively. In other words, spin is based upon the driven and undriven wheels on the same side of the vehicle. In addition, the difference in velocity (delta velocity) of the driven and undriven wheels on the same side of the vehicle is determined by the expressions V 1f - V 1r for the left side wheels 10 and 14 and V rf - V rr for the right side wheels 12 and 16. The final wheel state variables determined are the difference in acceleration (delta acceleration) of the driven and undriven wheels and 'energy' terms related to the difference between the squared velocities of the driven and undriven wheels on each side of the vehicle. Once the wheel state variables have been determined, the program determines the proper mode of operation of the brake actuators <93> and performs the necessary I/O with the brake <94> and throttle <95> actuators to control wheel spin to appropriate values. At this point, it should be noted that unless a program function specifically relates to both wheels, the control cycle interrupt routine is selectively conditioned for performing steps associated with one or the other left or right front driven wheel 10 or 12. Accordingly, parameters associated with one of the front driven wheels are selected depending upon which wheel the routine is conditioned for. It will be assumed that the routine is first conditioned for the left front driven wheel 10 <96>. In the Brake Mode Determination routine (Figure 5), the program evaluates the status of the brake switch 50 <97> and the status of the manually operated disable switch 54 <98>. The sensed closure of either one of these switches represents a condition not requiring acceleration slip control and the program exits the routine. However, if neither of the brake and disable switches 50 and 54 is closed, the program continues to evaluate the wheel variables to determine if brake actuation is required. The initial step in this process is to determine the brake motor current correction factor. As previously discussed, during the launch phase of the vehicle during which vehicle speeds are low, it is desirable to respond quickly to an excessive acceleration slip condition of the front wheel 10,12 to prevent a large wheel slip excursion with the resulting loss of traction and lateral stability. This is accomplished by controlling the brake pressure applied to the brake 18,20 of the front wheel 10,12 in response to the spin ratio of the front wheel (the ratio of the difference between the speeds of the slipping front wheel and a rear undriven wheel to the speed of the slipping front wheel) which can be large even though the velocity difference between the slipping front wheel and the rear undriven wheel may be small. Accordingly, if the vehicle speed (which may be taken as the average speeds of the rear undriven wheels 14 and 16) is determined to be less than a calibration value V <100>, a motor current correction factor is determined from a memory lookup table storing values of the correction factor at memory locations addressed by the values of spin ratio and acceleration difference between the front driven and rear undriven wheels <102>. The stored value of the correction factor may represent positive values for increasing brake pressure at the spinning front wheel 10,12, may represent a zero correction factor to hold the brake pressure or may represent a negative value for releasing the brake pressure. At higher vehicle speeds, the difference between the speeds of the front driven and rear undriven wheels may be large even though the spin ratio is small. To control spin to maintain vehicle stability at these higher speeds, it is desirable to tightly control wheel slip in order to maintain lateral stability. This is accomplished by controlling the brake 18,20 of a front wheel 10,12 having excess spin in response to the velocity difference between the front driven and rear undriven wheels even though the spin ratio may be small. Accordingly, if the vehicle speed is determined to be greater than the calibration value V <100>, a motor current correction factor is determined from a lookup table storing values of the correction factor at memory locations addressed by the values of the velocity difference between the front driven and rear undriven wheels and the acceleration difference between the front driven and rear undriven wheels <104>. In one embodiment, the same lookup table may be utilized in each of the steps <102> and <104> by scaling the table axis in accordance with spin ratio at vehicle velocities less than the threshold V and in accordance with velocity difference when the vehicle speed is equal to or greater than V. The brake pressure control of this invention is further demonstrated in Figure 8 where the solid lines represent lines of constant lookup table motor current correction values for a constant acceleration difference between the driven and undriven wheels. In the graph illustrated, the motor current correction factor is based on spin ratio below a vehicle speed of 20.12 kph (12.5 mph) and on velocity difference at higher vehicle speeds. Referring again to Figure 5, the determined motor current correction factor is modified as a function of the jerk of the wheel <106>. Generally, the jerk (either positive or negative) is scaled and summed with the correction factor to provide jerk compensation. This then provides an increasing correction factor for higher jerk values and decreasing correction factors for negative jerk values. The final correction factor is compared to an apply threshold <108>. If the final correction factor is greater than the apply threshold, and a Traction Control Active (TCA) flag is not already set <110> then a series of conditions are examined to determine if traction control should be requested. Traction control is requested <111> by setting the TCA flag if the difference between the velocities of the front driven and rear undriven wheels is greater than a specified amount <112>, if the energy term is larger than a predetermined amount <114>, or if the delta velocity and delta acceleration are both greater than specified thresholds <116,118>. (The threshold in step <112> is larger than the threshold in step <118>). If the TCA flag is already set <110> or has just been set <111>, the program advances to the right wheel or next routine, as appropriate <119,120>. If the final correction factor is less than the apply threshold <108>, and the TCA flag is not set <122>, the program also advances to the right wheel or next routine <119,120>. If the final correction factor is less than the apply threshold, and the TCA flag is set, the program checks whether the TCA flag should be cleared. When wheel spin has been less than a release threshold for a specified amount of time represented by N interrupt intervals <124,126,128,130>, the TCA flag is cleared <132> after which the program will then again advance to the next wheel or next routine <120,121>. If the specified amount of time has not lapsed, the program advances to the next wheel or next routine <120,121>. Upon completion of the mode determination routine, the brake control routine is entered (Figure 6). The brake control routine first checks for brake pedal application <136>, a disable condition <138>, or a lack of either wheel's TCA flag being set <140>. If any of the above conditions are satisfied, brake pressure from both actuators 24,26 will be released. This is done by applying reverse current to both DC torque motors 68 for a set period of time represented by T interrupt intervals <142,144,145>. All flags used in brake control are also cleared <147>. The reverse current on the DC torque motors 68 returns the pistons 78 in the actuators 24,26 to their home positions and opens valve members 86, allowing normal braking function. If the brake pedal 52 is not actuated <136>, the disable switch 54 is open <138> or if either TCA flag is set <140>, the program checks for completion of an initiation sequence <146>. In the initiation sequence <148> a predetermined motor current command for each of the DC torque motors 68 of the actuators 24 and 26 is established for a predetermined amount of time. This is done to remove the brake apparatus compliance and to ready the actuators 24 and 26 for control of the brake pressure to the brakes 18 and 20. During initiation, the shutdown counter used to time the complete release of traction brake pressure <142,144,145> is also cleared <149>. If initiation is complete, brake actuator currents are then determined for each actuator before the routine is completed. As with other routines, when the brake control initiation is complete <146>, control parameters are first determined for the left front wheel 10, followed by the right front wheel 12. Actuator motor currents are determined in one of three ways. If the TCA flag is not set for a particular wheel <152>, the current is set to a minimum value <154> to ensure that the brake compliance removed in the initiation sequence <148> does not return. If the TCA flag is set, the program checks for completion of an initial 'ramp' of brake integral terms <156>. The initial ramp control 158 occurs immediately after the actuator initiation sequence <148> is complete. It allows the brake control integral terms to increase at a rate based primarily on engine torque as represented, for example, by the position of the primary throttle valve 34, which, being nearly constant during this short period, causes the integral term to ramp up to some value. The value is determined (the ramp ends) when the acceleration of the spinning front wheel is found to be below a set threshold at the same time that the jerk for that front wheel is negative. This ramp control allows for a rapid estimation of the integral portion of the brake control parameters, in absence of specific information about the vehicle tyre/road interface. For instance, higher brake pressure (a faster ramp) will be necessary when a high engine torque acceleration is attempted on an icy surface than when a lower torque manoeuvre is attempted. On a higher coefficient surface, a shorter ramp is calculated as less brake pressure is needed to slow down the acceleration of the spinning front wheel. During the ramp, proportional terms are also based on engine torque, but are modified by other vehicle parameters. After the initial ramp is complete, brake control integral and proportional terms are then derived from the modified correction factor determined at step <106> in the brake mode determination routine of Figure 5 to determine the current command to the DC torque motor 68 and therefore brake pressure to the brake 18,20 <160>. In one embodiment, integral and proportional correction values are obtained by multiplying the correction factor by predetermined constants. In another embodiment, the factors may be complex terms that are variable as a function of predetermined vehicle parameters such as spin, delta velocity, engine torque and vehicle speed. The proportional correction value comprises the brake control proportional term and the sum of the prior integral term and the integral correction value comprises the brake control integral term. After the proportional and integral values are determined, total motor current is determined by adding together the proportional and integral terms <162>. Assuming a jolt current is not required <164> the determined motor current is outputted to the appropriate actuator controller 43 <166>. Although the control interrupt cycle may be initiated every 10 msec, total motor current may not be changed every cycle. In the current embodiment, new commands are established by step <160> in varying periods of 10 to 30 msec, depending on the changing state of wheel spin and acceleration. The jolt current is periodically outputted to the DC torque motors 68 <164,168> to help overcome seal friction in the actuators 24 and 26, ensuring the desired linear relationship between brake actuator current and brake pressure. A jolt current is considered required if the determined motor current remains in any state (increasing, decreasing or constant) for three interrupt intervals or if there has been a change from one of the states to another. The routine next points to the right front wheel 12 and returns to step <152> <170,172> or when the brake control routine is completed for the right front wheel <170>, a throttle control routine illustrated in Figure 7 is executed. In summary of the brake control routine of Figure 6, the brake 18,20 of each of the front driven wheels 10 and 12 are controlled to establish a pressure that is adjusted as a function of its spin ratio at low vehicle speeds so as to quickly take control of an excessive spin condition and as a function of the differential velocity value at higher vehicle speeds so as to provide tight control of front wheel spin and maintain vehicle stability. In some vehicle applications, wheel brake control alone may be used for acceleration slip control. However, in other vehicle applications, it may be desirable to also use control of engine torque to assist the brakes 18,20 in controlling acceleration slip. The throttle control routine for assisting the brakes is illustrated in Figure 7. The throttle control routine generally monitors the control of the brakes by the brake control routine and provides for a transfer of control of acceleration spin to the engine by reducing the engine torque output. This allows the brake control routine to decrease the brake pressure applied to the brakes 18,20. The throttle control routine first determines a value T b related to the engine torque that is being absorbed by the brakes 18 and 20 of both front wheels 10,12 <174>. This is accomplished by scaling each of the motor current commands to the actuators 24 and 26 and summing the scaled values to achieve a value representing the total engine torque being absorbed. The routine also determines engine torque by use of a table relating engine output torque with engine speed and throttle position <176>. At this point, if neither actuator 24,26 is active, and a Torque Control Active (TQCA) flag is not set <178,180> the routine is exited. If either actuator 24,26 is active, and the TQCA flag has not been previously set, a throttle initiation sequence <184,186> is entered. This sequence sets an initial value of torque desired from the engine to be the current engine torque minus an amount related to spin, vehicle acceleration and engine torque <184>. This sequence puts an upper limit on engine output torque until the controlled brake pressure is low enough to justify return of engine power. During initiation the TQCA flag is set <180>. If either actuator 24,26 is active, and the TQCA flag was previously set <178,182> then a value of engine torque increase or reduction from the present engine torque value is calculated as a function of engine torque and the total engine torque T b being absorbed by the brakes 18,20 <188>. A torque reduction value is calculated in this embodiment by multiplying the total engine torque T b being absorbed by the two brakes 18,20 above a predetermined value by a constant that has one value if one wheel is spinning and a second value if both wheels 10,12 are spinning. A torque increase is provided having a value increasing as a predetermined function of the amount that the total engine torque T b being absorbed by the two brakes 18,20 is below the predetermined value referred to above and as a function of the time that the spin of both front driven wheels 10,12 is below a predetermined threshold. A new value of torque desired is then determined by using the torque desired of the previous cycle adjusted by the above determined torque reduction or torque increase value <190>. Having arrived at a desired torque value, a position of the auxiliary throttle valve 38 is determined that will cause the engine torque to achieve the desired value <192>. This may be done by using a series of look up tables relating throttle position, engine speed and desired torque or by other means. If in the process of throttle control the auxiliary throttle valve position reaches a fully open position while a torque increase is being requested <194>, the TQCA flag is cleared <196> and motor current set to zero <197>. (This condition may not occur until after both actuators 24,26 have been released). Otherwise, the routine outputs the determined auxiliary throttle valve position <198>. After the throttle position is commanded, the routine is exited. In summary, the throttle control routine responds to the application of brake pressure via the actuators 24 and 26 and adjusts the torque output of the engine by control of the auxiliary throttle valve 38 in direction to reduce the engine torque and therefore the required application of brake pressure to the brakes 18 and 20 to achieve control of acceleration spin. Upon repeated executions of the control cycle routine including the brake control routine of Figure 6 and the throttle control routine of Figure 7, the brake pressure applied to the brakes 18 and 20 to control acceleration spin will be reduced in response to the wheel state variable response to the reduction in engine torque output as the engine torque is progressively decreased to limit acceleration spin. As excessive spin of a front driven wheel 10,12 is brought under control, the brake control routine begins to decrease the commanded current value to the DC torque motor 68 of the respective actuator 24 or 26 to release the brake pressure, which brings about an increase in engine torque requested, and an eventual full release of the auxiliary throttle valve 38. After the end of the throttle control routine, the current interrupt cycle is ended. Whilst the above embodiment has been described in relation to driven front wheels and undriven rear wheels, the present invention equally applies to vehicles having undriven front wheels and driven rear wheels. Attention is drawn to our corresponding patent applications EP-A-0397330 and EP-A-0397328, filed the same day as the present application.

Claims: A vehicle traction control apparatus for a vehicle having an engine for applying a driving torque to a vehicle driven wheel (10,12), the apparatus comprising a wheel speed sensor (39,40) for measuring a speed of the driven wheel; and a vehicle speed sensor (36,41,42,100) for measuring a speed of the vehicle; characterised by means (36,91,92) for determining a spin ratio of the driven wheel (10,12); means (36,112,114,116,118) for determining an excessive spinning condition of the driven wheel in response to an excessive driving torque applied thereto from the engine; and means (36,100,102,104,24,26,156-168) responsive to a determined excessive spinning condition for applying a braking force to the driven wheel having a value (A) that is a predetermined function of the spin ratio of the driven wheel when the vehicle speed is less than a predetermined value and (B) that is a predetermined function of the difference between the driven wheel speed and the vehicle speed when the vehicle speed is greater than the predetermined value. A vehicle traction control apparatus for a vehicle having an engine for applying a driving torque to a vehicle driven wheel (10,12), the apparatus comprising a wheel speed sensor (39,40) for measuring driven wheel speed; a vehicle speed sensor (36,41,42,100) for measuring vehicle speed; means responsive to the measured driven wheel speed for determining driven wheel acceleration; and means responsive to the measured vehicle speed for determining vehicle acceleration; characterised by means (36,91,92) for determining a spin ratio of the driven wheel (10,12); means (36,112,114,116,118) for determining an excessive spinning condition of the driven wheel in response to an excessive driving torque applied thereto from the engine; and means (36,100,102,104,24,26,156-168) responsive to a determined excessive spinning condition for applying a braking force to the driven wheel having a value (A) that is a predetermined function of the difference between (1) the driven wheel acceleration and the vehicle acceleration and (2) the spin ratio of the driven wheel when the vehicle speed is less than a predetermined value and (B) that is a predetermined function of the difference between (1) the driven wheel acceleration and the vehicle acceleration and (2) the difference between the driven wheel speed and the vehicle speed when the vehicle speed is greater than the predetermined value. A vehicle traction control apparatus as claimed in claim 2, wherein the spin ratio of the driven wheel (10,12) is determined in accordance with the expression (V f -V r )/V f , where V f is the driven wheel speed and V r is the measured vehicle speed.

Inventors: THATCHER DAVID ALAN, TIERNEY GORDON LEO, THATCHER, DAVID ALAN, TIERNEY, GORDON LEO
Applicants: GEN MOTORS CORP, GENERAL MOTORS CORPORATION
Application year: 1990
Main classification: B60T8
IPC codes: B60T8