JP4310658B2 - Vehicle driving force control device - Google Patents

Description

  The present invention relates to a vehicle driving force control device, and more particularly to a driving force control device that controls the driving force of a vehicle by controlling the throttle opening of an engine and controlling the ignition timing.

In a vehicle such as an automobile equipped with a spark ignition engine, as one of the driving force control devices for controlling the driving force of the vehicle by controlling the throttle opening of the engine and controlling the ignition timing, the driving slip of the driving wheel When the engine speed increases, the engine output is reduced by the throttle valve fully closed control and the ignition timing retard control to reduce the driving force of the vehicle. When the drive slip of the drive wheels decreases, the ignition timing retard control is first performed. A driving force control apparatus configured to end and then end the throttle valve fully-closed control is already known, and is described, for example, in Patent Document 1 below.
Japanese Patent Publication No. 7-84850 JP-A-10-264801

  In the control of a spark ignition engine, by retarding the ignition timing, the engine output can be reduced with good responsiveness, so that the driving force of the vehicle can be reduced with good responsiveness, and the ignition By limiting the time for retarding the timing, it is possible to suppress the increase in the temperature of the exhaust gas of the engine accompanying the retard of the ignition timing and the deterioration of the exhaust gas purification catalyst due to this.

  However, if the engine output is reduced by retarding the ignition timing, the engine output will be drastically reduced as compared to the case of reducing the throttle valve opening, and this is transmitted from the engine to the drive wheels via the drive system. Therefore, depending on the traveling state of the vehicle, rotational vibration is generated in the driving wheel or the rotational vibration state of the driving wheel is deteriorated.

  However, in the driving force control apparatus described in Patent Document 1, not only the execution time of the ignition timing retardation control is not considered, but also when the engine output is reduced by the ignition timing retardation, The fact that the rotational vibration state of the drive wheels may be deteriorated is not taken into account, and depending on the running condition of the vehicle, the rotational vibration state of the drive wheels is deteriorated due to a decrease in engine output due to the retard of the ignition timing. There is a problem that.

  In the driving force control device described in Patent Document 2, the execution time of the ignition timing retarding control is limited. However, even in this driving force control device, the ignition timing retarding control is performed. When the output of the engine is reduced, it is not considered that the rotational vibration state of the driving wheel may be deteriorated depending on the traveling state of the vehicle. In the case of the driving force control device described in Patent Document 1, There is a similar problem.

  Also, by reducing the amount of fuel supplied to the engine, the engine output can be reduced more responsively than the throttle opening reduction control as in the case of the ignition timing retard control, In the case of reducing the fuel supply amount, the temperature of the engine exhaust gas is likely to rise and the exhaust gas purification catalyst is deteriorated due to this, as in the case of the retard timing control of the ignition timing. This deteriorates the rotational vibration state of the drive wheels.

  The present invention solves the above-described problem in the case where the driving force of the vehicle is reduced by reducing the engine output by retarding the ignition timing or reducing the fuel supply amount in addition to reducing the throttle opening of the engine. The main object of the present invention is to determine the possibility that the rotational vibration state of the drive wheels will deteriorate when the driving force of the vehicle is reduced by retarding the ignition timing or reducing the fuel supply amount. By doing so, the driving force of the vehicle is effectively reduced while preventing deterioration of the rotational vibration state of the drive wheels.

[Means for Solving the Problems and Effects of the Invention]
According to the present invention, the main problem described above is the configuration of claim 1, that is, throttle opening control means for controlling the throttle opening of the engine based on at least the driving operation amount of the driver, and ignition of the engine The engine output reduction means for reducing the output of the engine by retarding the timing or reducing the amount of fuel supplied to the engine, and determining the degree of necessity for reducing the driving force of the vehicle based on the running state of the vehicle, A driving force reduction control means for reducing the output of the engine by controlling at least the throttle opening control means when the degree is high, and the driving force reduction control means has a degree of necessity equal to or greater than a first reference value. When the throttle opening degree is controlled by the throttle opening degree control means, the second degree is greater than the first reference value. A vehicle driving force control device configured to reduce the output of the engine by the engine output reduction means in addition to the reduction of the throttle opening degree controlled by the throttle opening control means when it is equal to or greater than a quasi-value. The driving force reduction control means includes a rotational vibration state determination means for determining a possibility of deteriorating the rotational vibration state of the driving wheel by reducing the engine output by the engine output reduction means, and the degree of necessity is the second level. Prohibition of prohibiting reduction of engine output by engine output reduction means when it is determined that there is a possibility that the rotational vibration state of the drive wheels is likely to be worsened by the rotational vibration state determination means even if it is greater than a reference value And a driving force control device for a vehicle.

  According to the first aspect of the present invention, the degree of necessity for reducing the driving force of the vehicle is determined based on the running state of the vehicle, and the throttle controlled by the throttle control means when the degree of necessity is equal to or greater than the first reference value. When the opening is reduced and the required degree is equal to or greater than the second reference value which is larger than the first reference value, the engine output reducing means controls the engine in addition to the throttle opening reduction controlled by the throttle opening control means. Since the output is reduced, the engine output can be reduced by the engine output reduction means only in a very high situation where the necessity of reducing the driving force of the vehicle is equal to or higher than the second reference value.

  According to the configuration of claim 1, when it is determined that the rotational vibration state of the driving wheel may be deteriorated by the rotational vibration state determination means even if the necessary degree is equal to or greater than the second reference value. Since reduction of engine output by the engine output reduction means is prohibited, reduction of engine output by the engine output reduction means when there is a possibility of deteriorating the rotational vibration state of the drive wheels due to reduction of engine output by the engine output reduction means. Can be reliably prevented.

  Therefore, when the degree of necessity for reducing the driving force of the vehicle is not less than the first reference value but less than the second reference value, the engine output is prevented from being reduced by the engine output reduction means, and the exhaust gas of the engine is reduced. It is possible to prevent the exhaust gas purifying catalyst from deteriorating due to temperature rise, and the throttle opening degree in a very high situation where the necessity of reducing the driving force of the vehicle is more than the second reference value. By reducing the engine output by the engine output reduction means in addition to the reduction in the engine output, the engine output can be reliably and effectively reduced, and thereby the vehicle driving force can be reliably and effectively reduced. Furthermore, it is possible to reliably prevent the rotational vibration state of the drive wheels from being deteriorated due to the reduction of the engine output by the engine output reduction means.

  When the degree of necessity for reducing the driving force of the vehicle is greater than or equal to the second reference value, the engine output is reduced by both the reduction of the throttle opening and the reduction of the engine output by the engine output reducing means, thereby driving the vehicle. Since the power is efficiently reduced, the degree of necessity for reducing the driving force is quickly reduced, so that the time during which the engine output is reduced by the engine output reducing means is not excessively long.

  According to the present invention, in order to effectively achieve the main problem described above, in the configuration of claim 1, the rotational vibration state determining means includes means for detecting rotational vibration of the drive wheel, When the degree of rotational vibration of the driving wheel is greater than or equal to a reference value for rotational vibration determination, it is determined that there is a possibility of deteriorating the rotational vibration state of the driving wheel (configuration of claim 2).

  According to the present invention, in order to effectively achieve the main problems described above, the rotational vibration state determination means detects the friction coefficient of the road surface corresponding to the left and right drive wheels. And determining that there is a possibility of deteriorating the rotational vibration state of the drive wheels when the difference in friction coefficient between the road surfaces corresponding to the left and right drive wheels is equal to or greater than a reference value for cross-over determination. (Structure of claim 3).

  When the engine output is reduced by the engine output reduction means, the rotational vibration state of the drive wheels deteriorates when the drive wheels already have some rotational vibration or the friction coefficient of the road surface corresponding to the left and right wheels. The difference between the two is significant, so it is determined whether a certain amount of rotational vibration has already occurred on the drive wheels, and whether the difference in friction coefficient between the road surfaces corresponding to the left and right wheels is large. Thus, it can be determined whether or not there is a possibility of deteriorating the rotational vibration state of the drive wheel.

  According to the configuration of the second aspect, it is determined that the rotational vibration state of the driving wheel may be deteriorated when the degree of rotational vibration of the driving wheel is equal to or higher than a reference value for rotational vibration determination. According to this configuration, when it is determined that there is a possibility of deteriorating the rotational vibration state of the driving wheel when the difference in friction coefficient between the road surfaces corresponding to the left and right driving wheels is equal to or greater than the reference value for the crossing road determination. It is possible to reliably determine whether or not the rotational vibration state of the drive wheels is deteriorated by reducing the engine output by the engine output reduction means.

  According to the present invention, in order to effectively achieve the main problems described above, in the configuration according to any one of the first to third aspects, the driving force control device is configured such that the driving operation amount of the driver and the vehicle And a means for calculating a target driving force of the vehicle based on a running state, wherein the driving force reduction control means is based on two target driving forces calculated before and after the degree of necessity becomes equal to or greater than the first reference value. Thus, the target driving force under the control of the throttle opening control means that changes more gently than the change between the two target driving forces, and the change that decreases more gently than the change between the two target driving forces. Calculating the target driving force by the control of the throttle opening control means and the engine output reduction means, which changes and decreases more rapidly than the change in the target driving force by the control of the throttle opening control means, The deviation between the target driving force controlled by the throttle opening control means and the target driving force controlled by the throttle opening control means and the engine output reduction means is a deviation criterion. The engine output reducing means is configured to reduce the engine output when the value is greater than or equal to a value, and the prohibiting means has the degree of necessity equal to or greater than the second reference value and the throttle opening control means. Even if the deviation between the target driving force by control of the throttle and the target driving force by control of the throttle opening control means and the engine output reduction means is equal to or greater than the deviation determination reference value, the rotational vibration state determination means causes the drive wheel to When it is determined that there is a risk of worsening the rotational vibration state of the engine, the engine output reduction means reduces the engine output. Configured to stop (the fourth aspect).

  According to the configuration of the above-described fourth aspect, the change of the driving force of the vehicle changes more gently than the change of the two target driving forces calculated before and after the degree of necessity of reducing the driving force becomes equal to or higher than the first reference value. The target driving force under the control of the throttle opening control means and a lower change more gently than the lower change between the two target driving forces, and more quickly than the lower change in the target driving force under the control of the throttle opening control means The target driving force by the control of the changing throttle opening control means and the engine output reduction means is calculated, the required degree is equal to or greater than the second reference value, and the target driving force and the throttle opening by the control of the throttle opening control means are calculated. When the deviation from the target driving force by the control of the degree control means and the engine output reduction means is equal to or greater than the deviation determination reference value, the engine output is reduced by the engine output reduction means. .

  Therefore, when the amount of reduction in the target driving force of the vehicle is large, the necessary degree is equal to or greater than the second reference value, and the deviation between the two target driving forces is equal to or greater than the deviation determination reference value, the throttle opening reduction and engine output are reduced. By reducing the engine output by the reduction means, the engine output can be reliably and effectively reduced, and the necessary degree is equal to or greater than the second reference value, but the deviation between the two target driving forces is the deviation determination reference value. If it is less than the engine output, the engine output reduction means prevents the engine output from being reduced, and only the engine output is reduced by reducing the throttle opening, thereby causing the engine output reduction means to reduce the engine output. It is possible to reliably prevent the exhaust gas temperature rise of the engine and the deterioration of the exhaust gas purification catalyst due to this.

  According to the fourth aspect of the present invention, the required degree is not less than the second reference value and the target driving force is controlled by the throttle opening control means and the target driving is controlled by the throttle opening control means and the engine output reduction means. Even if the deviation from the force is equal to or greater than the deviation determination reference value, the engine output reduction means reduces the engine output when it is determined by the rotational vibration state judgment means that the rotational vibration state of the drive wheels may be deteriorated. Therefore, even if it is necessary to reduce the engine output by the engine output reduction means, the engine output reduction means reduces the engine output when there is a risk of deteriorating the rotational vibration state of the drive wheels. This can reliably prevent the rotational vibration state of the drive wheels from deteriorating.

  According to the present invention, in order to effectively achieve the main problem described above, in the configuration of claim 4, the deviation determination reference value is determined so that the engine speed is low when the engine speed is low. It is configured to be variably set according to the engine speed so as to be smaller than when it is high (configuration of claim 5).

  When the engine speed is low, the flow rate of air, mixed gas, etc. in the engine is lower than when the engine speed is high, and the engine output due to the throttle opening being reduced due to this. Therefore, in order to effectively reduce the engine output, it is necessary to reduce the engine output by the engine output reducing means when the engine speed is low compared to when the engine speed is high. Is expensive.

  According to the configuration of the fifth aspect, the deviation determination reference value is variably set according to the engine speed so as to be smaller when the engine speed is low than when the engine speed is high. When the engine speed is low, it can be easily determined that the deviation between the two target driving forces is greater than the deviation criterion value compared to when the engine speed is high. The engine output can be easily reduced.

  According to the present invention, in order to effectively achieve the above main problem, in the configuration of claim 4, the gradient of the decrease in the target driving force by the control of the throttle opening control means is the engine. When the engine speed is low, the engine speed is variably set according to the engine speed so as to be smaller than when the engine speed is high (structure of claim 6).

  According to the configuration of the sixth aspect, the gradient of the decrease in the target driving force under the control of the throttle opening control means is smaller when the engine speed is low than when the engine speed is high. Therefore, when the engine speed is low, the deviation between the two target driving forces is increased as compared with when the engine speed is high. Can easily be greater than or equal to the deviation determination reference value, thereby making it easier to reduce the engine output by the engine output reduction means.

  Further, according to the present invention, in order to effectively achieve the main problem described above, in the configuration according to any one of claims 4 to 6, when the necessary degree is equal to or more than the first reference value, The throttle opening control means is configured to control the throttle opening based on a target driving force controlled by the throttle opening control means.

  According to the configuration of the seventh aspect, since the throttle opening is controlled based on the target driving force controlled by the throttle opening control means, it corresponds to a decrease in the target driving force controlled by the throttle opening control means. Thus, the throttle opening can be controlled to be reduced.

  Further, according to the present invention, in order to effectively achieve the main problem described above, in the configuration according to any one of claims 2 to 7, when the necessary degree is equal to or more than the second reference value, The engine output reducing means reduces the engine output based on a deviation between a target driving force controlled by the throttle opening control means and a target driving force controlled by the throttle opening control means and the engine output reducing means. (Structure of claim 8).

  According to the above configuration, the engine output is reduced based on the deviation between the target driving force controlled by the throttle opening control means and the target driving force controlled by the throttle opening control means and the engine output reduction means. Therefore, the throttle opening degree can be reduced and controlled so as to correspond to the decrease change of the target driving force due to the control of the throttle control means, and the engine output to correspond to the decrease change of the target driving force due to the control of the engine output reduction means. The engine output can be reduced by the reduction means.

  According to the present invention, in order to effectively achieve the above main problem, in the configuration according to any one of claims 1 to 3, the driving force reduction control means has the second degree of necessity. The engine output reduction means is configured to reduce the engine output when the engine speed is equal to or greater than a reference value and the engine speed is equal to or less than an engine speed determination reference value. Even if the engine speed is equal to or greater than the second reference value and the engine speed is equal to or less than the engine speed determination reference value, the rotational vibration state determination means may deteriorate the rotational vibration state of the drive wheels. When it is determined that the engine output is present, the engine output reduction means is configured to prohibit the reduction of the engine output (structure of claim 9).

  As described above, when the engine speed is low, the flow velocity of air, mixed gas, etc. in the engine is lower than when the engine speed is high, and as a result, the throttle opening is reduced. Therefore, in order to effectively reduce the engine output, it is preferable that the engine output is reliably reduced by the engine output reduction means when the engine speed is low. When there is a risk of deteriorating the rotational vibration state of the drive wheels, it is preferable that the engine output reduction means not reduce the engine output regardless of the engine speed.

  According to the configuration of claim 9, when the degree of necessity is equal to or greater than the second reference value and the engine speed is equal to or less than the engine speed determination reference value, the engine output is reduced by the engine output reduction means. Therefore, when the engine speed is low, the engine output can be reliably reduced by the engine output reduction means. In the situation where the necessary degree is equal to or higher than the second reference value, if the engine speed is equal to or lower than the engine speed determination reference value, the engine output reduction means immediately starts to reduce the engine output. The engine output reduction by the engine output reduction means can be started earlier than in the case of the configurations of the fourth to eighth aspects of the invention, whereby the driving force of the vehicle can be reduced early.

  According to the configuration of the ninth aspect, even if the degree of necessity is equal to or greater than the second reference value and the engine speed is equal to or less than the engine speed determination reference value, the rotational vibration state of the drive wheels may be deteriorated. Since it is prohibited to reduce the engine output by the engine output reduction means when it is determined that the engine output is present, the engine output reduction means must be reduced by the engine output reduction means as in the case of the configuration of claim 4 described above. However, when there is a possibility of deteriorating the rotational vibration state of the drive wheel, it is ensured that the engine output is reduced by the engine output reduction means and that the rotational vibration state of the drive wheel is deteriorated due to this. Can be prevented.

  According to the present invention, in order to effectively achieve the main problem described above, in the configuration of claim 9, the driving force control device is based on the driving operation amount of the driver and the traveling state of the vehicle. Means for calculating a target driving force of the vehicle, wherein the driving force reduction control means calculates a difference between the two target driving forces calculated before and after the degree of necessity becomes equal to or greater than the first reference value. As a difference, the engine speed determination reference value is variably set in accordance with the reference target driving force difference so that it is larger when the reference target driving force difference is larger than when the reference target driving force difference is small. (Structure of claim 10).

  When the reference target driving force difference is large, the amount of reduction in the vehicle driving force that must be actually reduced is larger than when the reference target driving force difference is small. When the reference target driving force difference is large, it is more necessary to reduce the engine output by the engine output reducing means than when the reference target driving force difference is small.

  According to the configuration of the above tenth aspect, the engine speed determination reference value is variable according to the reference target driving force difference so that the reference value becomes larger when the reference target driving force difference is large than when the reference target driving force difference is small. Therefore, when the reference target driving force difference is large, the engine speed can be easily lower than the engine speed determination reference value compared to when the reference target driving force difference is small, thereby reducing engine output. The engine output can be easily reduced by the means.

  According to the present invention, in order to effectively achieve the main problems described above, in the configuration according to any one of claims 1 to 10, the second reference value is the frictional property of the road surface, the side of the vehicle. It is configured to be variably set based on at least one of acceleration and vehicle speed (configuration of claim 11).

  According to the configuration of claim 11, the second reference value is variably set based on at least one of the road surface frictional property, the vehicle lateral acceleration, and the vehicle speed, so that the second reference value is constant. As compared with this, the engine output due to the retard of the ignition timing can be accurately reduced in accordance with the traveling state of the vehicle.

  According to the present invention, in order to effectively achieve the main problem described above, in the configuration according to any one of claims 1 to 11, the second reference value is set when the engine speed is low. The engine is variably set according to the engine speed so as to be smaller than that when the engine speed is high (structure of claim 12).

  According to the configuration of the twelfth aspect, the second reference value is variably set according to the engine speed so that it is smaller when the engine speed is low than when the engine speed is high. When the engine speed is low, it is possible to easily determine that the required degree is equal to or higher than the second reference value compared to when the engine speed is high. Reduction can be facilitated.

  Further, according to the present invention, in order to effectively achieve the main problems described above, in the structure according to any one of claims 1 to 12, the driving force reduction control means is a vehicle based on a running motion state of the vehicle. The degree of necessity is determined based on at least one of the required reduction amount of the target driving force, the degree of driving slip of the driving wheel, and the friction coefficient of the road surface (configuration of claim 13).

  According to the configuration of claim 13, the driving force of the vehicle based on at least one of the required reduction amount of the target driving force of the vehicle based on the running motion state of the vehicle, the degree of driving slip of the driving wheel, and the friction coefficient of the road surface. Therefore, it is possible to reduce the target driving force of the vehicle without excess or deficiency so that the reduction of the driving slip of the driving wheels and the securing of the stable running motion of the vehicle are properly achieved.

[Preferred embodiment of problem solving means]
According to one preferable aspect of the present invention, in the configuration according to any one of the first to thirteenth aspects, the prohibiting means is at least any one by the rotational vibration state determining means even if the necessary degree is not less than the second reference value. When it is determined that there is a possibility of deteriorating the rotational vibration state of the drive wheels, the engine output reduction means is configured to prohibit the reduction of the engine output (preferred aspect 1).

  According to another preferred aspect of the present invention, in the configuration according to any one of claims 2 or 4 to 13 or preferred aspect 1, the means for detecting the rotational vibration of the drive wheel is the wheel speed of the drive wheel. And detecting the rotational vibration of the drive wheel based on the periodic fluctuation of the wheel speed of the drive wheel (preferred aspect 2).

  According to another preferred aspect of the present invention, in the structure according to any one of claims 3 to 13, the reference value for the straddle determination is the lower of the friction coefficients of the road surface corresponding to the left and right drive wheels. The lower friction coefficient is configured to be variably set according to the lower friction coefficient so that the lower friction coefficient is smaller than when the lower friction coefficient is high (preferred aspect 3).

  According to another preferred aspect of the present invention, in the configuration according to any one of claims 4 to 8, the driving force reduction control means is calculated before and after the degree of necessity becomes equal to or higher than the first reference value. The target driving force calculated by the control of the throttle control means is calculated by calculating the filter processing with the first time constant for the decrease in the target driving force between the two target driving forces. The target by the control of the throttle control means and the engine output reduction means by calculating the filter process with the second time constant larger than the first time constant with respect to the change in the target driving force during the driving force. It is comprised so that a driving force may be calculated (Preferred aspect 4).

  According to another preferred aspect of the present invention, in the configuration of claim 9 or 10, the driving force control device determines the target driving force of the vehicle based on the driving operation amount of the driver and the running state of the vehicle. The driving force reduction control means has a means for calculating, based on the two target driving forces calculated before and after the degree of necessity becomes equal to or greater than the first reference value, rather than a decrease change between the two target driving forces. The target driving force under the control of the throttle control means that gently changes, and the lower change between the two target driving forces, and the lower the change in the target driving force under the control of the throttle control means. When the target driving force by the control of the throttle control means and the engine output reduction means that are decreasing is calculated, and the degree of necessity is equal to or greater than the first reference value, the throttle opening control means Configured to control the throttle opening based on the target driving force by the control stage (preferred embodiment 5).

  According to another preferred aspect of the present invention, in the configuration of the preferred aspect 5 described above, when the necessary degree is equal to or greater than the second reference value, the ignition timing control means is a target driving force controlled by the throttle control means. The engine output is reduced on the basis of a deviation from the target driving force controlled by the throttle control means and the engine output reduction means (preferred aspect 6).

  According to another preferred aspect of the present invention, in any one of the above-described claims 4 to 8 or the preferred aspect 5 or 6, the engine output reduction means is an ignition timing control means, and the driving force reduction. The control means is based on the two target driving forces calculated before and after the degree of necessity becomes equal to or greater than the first reference value, and the throttle opening that changes more gently than the lower change between the two target driving forces. The target driving force under the control of the control means and the lower change between the two target driving forces are more moderately lower and change more rapidly than the target driving force with the throttle opening control means. The target driving force calculated by the throttle opening control means and the ignition timing control means is calculated, and the required degree is equal to or greater than the second reference value and the target driving force is controlled by the throttle opening control means. When the deviation from the target driving force by the control of the throttle opening control means and the ignition timing control means is equal to or larger than the deviation determination reference value, the ignition timing controlled by the ignition timing control means is retarded (preferably Aspect 7).

  According to another preferred aspect of the present invention, in the configuration of the preferred aspect 7, when the necessary degree is equal to or greater than the second reference value, the ignition timing control means is controlled by the throttle opening degree control means. The ignition timing is retarded based on the deviation between the target driving force and the target driving force controlled by the throttle opening control means and the ignition timing control means (preferred aspect 8).

  According to another preferred embodiment of the present invention, in any one of the above-described claims 4 to 8 or the preferred embodiment 5 or 6, the engine output reducing means is a fuel supply amount reducing means, and the driving force Based on the two target driving forces calculated before and after the degree of necessity becomes equal to or greater than the first reference value, the reduction control means performs throttle opening that changes more gently than the lower change between the two target driving forces. The target driving force under the control of the degree control means and the lowering change more gently than the lowering change between the two target driving forces, and the lowering change more quickly than the lowering of the target driving force under the control of the throttle opening control means And the target driving force by the control of the throttle opening control means and the fuel supply amount reduction means to calculate, the target degree is equal to or greater than the second reference value, and the target drive by the control of the throttle opening control means is calculated. The fuel supply amount reduction means reduces the fuel supply amount to the engine when the deviation between the force and the target driving force controlled by the throttle opening control means and the fuel supply amount reduction means is equal to or greater than the deviation determination reference value. (Preferred embodiment 9).

  According to another preferred aspect of the present invention, in the configuration of the preferred aspect 9 described above, when the required degree is equal to or greater than the second reference value, the fuel supply amount reducing means controls the throttle opening degree control means. The fuel supply amount to the engine is reduced based on the deviation between the target drive force by the target drive force by the control of the throttle opening degree control means and the fuel supply amount reduction means (preferred aspect 10).

  According to another preferred embodiment of the present invention, in the structure according to any one of claims 11 to 13 or preferred embodiments 1 to 10, the second reference value is the road surface when the road surface friction coefficient is low. It is configured to be variably set according to the friction coefficient of the road surface so as to be smaller than when the friction coefficient is high (preferred aspect 11).

  According to another preferred aspect of the present invention, in the structure according to any one of claims 11 to 13 or preferred aspects 1 to 11, the second reference value is a large lateral acceleration of the vehicle. It is configured to be variably set according to the magnitude of the lateral acceleration of the vehicle so as to be smaller than when the magnitude of the lateral acceleration of the vehicle is small (preferred aspect 12).

  According to another preferred embodiment of the present invention, in the structure according to any one of claims 11 to 13 or preferred embodiments 1 to 12, the second reference value is set when the vehicle speed is low when the vehicle speed is high. It is configured to be variably set according to the vehicle speed so as to be smaller (preferred aspect 13).

  According to another preferred aspect of the present invention, in the configuration of the above-described claim 13 or any of the preferred aspects 1 to 13, the vehicle moves the vehicle by controlling the braking / driving force of the vehicle or the wheels. It has a running motion control device that stabilizes and determines the degree of necessity for reducing the driving force of the vehicle based on the required amount of reduction of the target driving force of the vehicle accompanying the control of the braking / driving force of the vehicle or wheels by the running motion control device (Preferred embodiment 14).

The present invention will now be described in detail with reference to a few preferred embodiments with reference to the accompanying drawings.
[First embodiment]

  FIG. 1 is a schematic configuration diagram (A) and a control system block diagram (B) showing a first embodiment of a vehicle driving force control apparatus according to the present invention applied to a rear wheel drive vehicle.

  In FIG. 1, a driving force control device 10 is mounted on a vehicle 12, and a braking / driving force control device 14 that controls traveling motion of the vehicle by controlling braking / driving force of the vehicle and wheels, and a spark ignition engine 16. And an engine control device 18 for controlling the engine. The driving force of the engine 16 is transmitted to the propeller shaft 26 via an automatic transmission 24 including a torque converter 20 and a transmission 22. The driving force of the propeller shaft 26 is transmitted to the left rear wheel axle 30L and the right rear wheel axle 30R by the differential 28, whereby the left and right rear wheels 32RL and 32RR which are driving wheels are rotationally driven.

  On the other hand, the left and right front wheels 32FL and 32FR are driven wheels and steered wheels, which are not shown in FIG. 1, but are driven in response to a steering wheel steering operation by a driver. The steering device is steered in a known manner via a tie rod.

  The intake air amount of the engine 16 is controlled by a throttle valve 36 provided in the intake passage 34, and the throttle valve 36 is driven by a throttle actuator 38 including an electric motor. The opening degree of the throttle valve 36, that is, the throttle opening degree is controlled by the engine control device 18 via the throttle actuator 38 in accordance with the depression amount of the accelerator pedal 42 detected by the accelerator position sensor 40. In addition, an injector 44 for injecting fuel such as gasoline is provided at the supply port of each cylinder of the intake passage 34 of the engine 16. The fuel injection amount by the injector 44, that is, the fuel supply amount to the engine 16 is shown in FIG. 1. Is controlled by the engine control device 18 in accordance with the intake air amount Ra detected by an air flow meter not shown, whereby the output of the engine is controlled to increase or decrease.

  As is well known, the fuel injected by the injector 44 is mixed with the intake air, and the air-fuel mixture is combusted by being ignited by a spark plug not shown in FIG. 1, thereby generating the driving force of the engine 16. Is done. Exhaust gas generated by the combustion of the air-fuel mixture is discharged from an exhaust manifold (not shown in FIG. 1) to an exhaust pipe 46 and purified by an exhaust gas purification catalyst 48 provided in the exhaust pipe 46. It is released into the atmosphere via a muffler not shown.

  The engine control device 18 has a signal indicating the depression amount (accelerator opening Ap) of the accelerator pedal 42 from the accelerator position sensor (AP sensor) 40, and a signal indicating the opening φ of the throttle valve 36 from the throttle position sensor (TP sensor) 50. A signal indicating the engine speed Ne is input from the engine speed sensor (Ne sensor) 52, and a signal indicating other information necessary for controlling the engine is input from other sensors not shown in the figure. .

  The braking forces of the left and right front wheels 32FL, 32FR and the left and right rear wheels 32RL, 32RR are controlled by controlling the braking pressures of the corresponding wheel cylinders 58FL, 58FR, 58RL, 58RR by the hydraulic circuit 56 of the braking device 54. Although not shown in the drawing, the hydraulic circuit 56 includes a reservoir, an oil pump, various valve devices, and the like, and the pressure in each wheel cylinder, that is, the braking pressure of each wheel, is normally depressed by the driver. The pressure is controlled by the pressure in the master cylinder 62 driven according to the operation, and the pressure is controlled to be higher than the pressure in the master cylinder 62 by controlling the hydraulic circuit 56 as necessary.

  As shown in FIG. 1B, the braking / driving force control device 14 includes a signal indicating the lateral acceleration Gy of the vehicle from the lateral acceleration sensor 64, friction coefficient sensors 66A provided corresponding to the left and right wheels, and A signal indicating friction coefficient μA and μB of the road surface from 66B, wheel speed Vwi (i = FL, FR, RL, left and right rear wheels) from wheel speed sensor 68i (i = FL, FR, RL, RR) RR) is input. Further, a shift control device 70 that controls the shift speed of the braking / driving force control device 14, the engine control device 18, and the automatic transmission 24 exchanges necessary signals with each other as necessary.

  The braking / driving force control device 14, the engine control device 18, and the transmission control device 70 actually include a CPU, a ROM, a RAM, an input / output port device, etc., which are connected to each other via a bidirectional common bus. It may include a microcomputer and a drive circuit having the configuration described above. The lateral acceleration sensor 64 detects the lateral acceleration Gy of the vehicle with the vehicle turning left as positive.

  The engine control unit 18 calculates the basic target driving force Fxta of the vehicle based on the accelerator opening Ap and the like in a manner known in the art, and generates a signal indicating the basic target driving force Fxta of the vehicle. 14 to output. The braking / driving force control device 14 reduces the driving force of the vehicle in order to make the vehicle run stably based on the running state of the vehicle, in particular, the friction coefficient of the road surface, the driving slip state of the driving wheels, and the running motion state of the vehicle. When it is determined whether or not it is necessary to reduce the driving force of the vehicle, it is possible to stabilize the vehicle based on the friction coefficient of the road surface, the driving slip state of the driving wheels, and the traveling motion state of the vehicle. The vehicle's target driving force Fxt for driving the vehicle is calculated, and a signal indicating the vehicle's target driving force Fxt is output to the engine control device 18. On the other hand, when the braking / driving force control device 14 determines that there is no need to reduce the driving force of the vehicle, it sets the target driving force Fxt of the vehicle to the basic target driving force Fxta and a signal indicating the target driving force Fxt of the vehicle. Is output to the engine control device 18.

  The engine control device 18 calculates the target gear stage St and the target throttle opening φt of the automatic transmission 24 based on the target driving force Fxt of the vehicle, and outputs a signal indicating the target gear stage St to the transmission control device 70. The shift control device 70 controls the automatic transmission 24 so that the shift stage of the automatic transmission 24 becomes the target shift stage St. Further, the engine control device 18 calculates a target advance angle θt of the ignition timing based on the intake air amount Ra and the engine speed Ne detected by an air flow meter not shown in FIG.

  In particular, in the first embodiment shown in the drawing, the braking / driving force control device 14 determines the vehicle body speed (in the manner known in the art based on the wheel speed Vwi of each wheel detected by the wheel speed sensor 68i. (Vehicle speed) Vb is calculated, and the left and right rear wheel drive slip amounts SArl and SArr are calculated based on the wheel speeds of the left and right rear wheels and the vehicle body speed Vb. The average value SAa of the left and right rear wheel drive slip amounts SArl and SArr is calculated. This is calculated as an index value indicating the degree of necessity for reducing the driving force of the vehicle.

  Then, the braking / driving force control device 14 determines whether or not the index value SAa is greater than or equal to the first reference value SAa1 (positive constant), and when the index value SAa is less than the first reference value SAa1, The opening degree reduction request flag Fth is set to 0, and a signal indicating that the throttle opening degree reduction request flag Fth is 0 is output to the engine control device 18.

  Further, when the index value SAa becomes equal to or higher than the first reference value SAa1 from less than the first reference value SAa1, the braking / driving force control device 14 decreases the target driving force Fxt as shown in FIG. That is, the vehicle value calculated immediately after the index value SAa becomes equal to or greater than the first reference value SAa1 based on the vehicle target driving force Fxt (Fxta) calculated immediately before the index value SAa becomes equal to or greater than the first reference value SAa1. For example, the target driving force Fxt1 by the throttle opening reduction control is calculated by the filter processing calculation of the target driving force Fxt as the value that changes more gently than the decreasing change to the target driving force Fxt (Fxtb), and the target driving force For example, the throttle opening reduction control and the ignition timing retardation control are performed by filtering the target driving force Fxt as values that change more gently than the lowering change of Fxt and more rapidly than the target driving force Fxt1. It calculates a target driving force Fxt2 with.

  In this case, the time constant of the filter processing when calculating the target driving force Fxt1 by the throttle opening reduction control is set according to the responsiveness of the decrease in the driving force of the vehicle due to the reduction of the opening of the throttle valve 36, Thus, the target driving force Fxt1 by the throttle opening reduction control is achieved by reducing the opening of the throttle valve 36 when the change in the engine speed Ne is a general value when the vehicle is running. Calculation is performed to correspond to a decrease in driving force. Similarly, the time constant of the filter processing when calculating the target driving force Fxt2 by the throttle opening reduction control and the ignition timing retard control is the vehicle driving force by the throttle opening reduction control and the ignition timing retard control. Accordingly, the target driving force Fxt2 based on the throttle opening reduction control and the ignition timing retarding control is set according to the responsiveness of the lowering change of the engine. The value is calculated so as to correspond to a decrease in driving force of the vehicle achieved by the throttle opening reduction control and the ignition timing retardation control.

  Further, when the index value SAa is equal to or greater than the first reference value SAa1, the braking / driving force control device 14 calculates the target throttle opening φtb based on the target driving force Fxt1 based on the throttle opening control, and the throttle opening. The reduction request flag Fth is set to 1, and a signal indicating that the target throttle opening φtb and the throttle opening reduction request flag Fth are 1 is output to the engine control device 18.

  When the engine control device 18 receives a signal indicating that the throttle opening reduction request flag Fth is 0 from the braking / driving force control device 14, the opening of the throttle valve 36 becomes the target throttle opening φt. The throttle actuator 38 is controlled. In contrast, when the engine control device 18 receives a signal indicating the target throttle opening φtb and a signal indicating that the throttle opening reduction request flag Fth is 1 from the braking / driving force control device 14, the throttle valve 36. The throttle actuator 38 is controlled so that the opening of the engine becomes the target throttle opening φtb, thereby reducing the output of the engine 16.

  Further, when the index value SAa is equal to or larger than the second reference value SAa2 (positive value) larger than the first reference value SAa1, the braking / driving force control device 14 determines the target driving force Fxt1 by the throttle opening reduction control and It is determined whether or not the deviation ΔFxt (= Fxt1−Fxt2) from the target driving force Fxt2 by the throttle opening reduction control and the ignition timing retardation control is equal to or larger than the deviation determination reference value Fxt3 (positive constant).

  When the braking / driving force control device 14 determines that the deviation ΔFxt of the target driving force is greater than or equal to the deviation determination reference value Fxt3, the left and right rear wheels are based on the wheel speeds VwRL and VwRR of the left and right rear wheels that are driving wheels. The amplitudes AwRL and AwRR of the rotational vibrations 32RL and 32RR are calculated, and it is determined whether or not the amplitudes AwRL and AwRR are greater than or equal to a reference value Awo (positive constant) for rotational vibration determination.

  When the braking / driving force control device 14 determines that both the amplitudes AwRL and AwRR are less than the reference value Awo for rotational vibration determination, it calculates the difference Δμ between the friction coefficients μA and μB of the road surface and calculates the absolute value of the difference Δμ. Is equal to or greater than a reference value Δμo (positive constant) for crossing road determination.

  The braking / driving force control device 14 has a target driving force deviation ΔFxt that is greater than or equal to the deviation determination reference value Fxt3, and that both the left and right rear wheel rotational vibration amplitudes AwRL and AwRR are less than the rotational vibration determination reference value Awo and When the absolute value of the difference Δμ between the friction coefficients μA and μB of the road surface is equal to or less than the reference value Δμo for crossing road determination, the ignition timing retard correction amount θtb is calculated based on the target driving force deviation ΔFxt, and the ignition timing Is set to 1, and a signal indicating that the ignition timing retardation correction amount θtb and the ignition timing retardation request flag Fig is 1 is output to the engine control device 18.

  On the other hand, in the braking / driving force control device 14, when the index value SAa is not less than the first reference value SAa1 but less than the second reference value SAa2, the index value SAa is not less than the second reference value SAa2. When the target driving force deviation ΔFxt is less than the deviation determination reference value Fxt3, the index value SAa is greater than or equal to the second reference value SAa2 and the target driving force deviation ΔFxt is greater than or equal to the deviation determination reference value Fxt3. When either of the rotational vibration amplitudes AwRL and AwRR of the wheel is greater than or equal to the reference value Awo of the rotational vibration determination, or the absolute value of the difference Δμ between the friction coefficients μA and μB of the road surface is larger than the reference value Δμo of the straddle road determination The ignition timing retardation correction amount θtb is reset to 0, the ignition timing retardation request flag FIG. Is reset to 0, and a signal indicating that the ignition timing retardation request flag FIG. 18 is output.

  The engine control device 18 controls the distributor 72 based on the target advance angle θt before correction when receiving a signal from the braking / driving force control device 14 indicating that the ignition timing retardation request flag FIG. As a result, the ignition timing, that is, the output timing of the ignition current to the spark plug of each cylinder not shown in FIG. On the other hand, when the engine control device 18 receives a signal indicating that the ignition timing retard request flag Fig is 1 from the braking / driving force control device 14, the engine control device 18 retards the target advance angle θt of the ignition timing by the retard correction. The output is corrected by the amount θtb to the retard side, and the distributor 72 is controlled based on the target advance angle θta (= θt−θtb) after the retardation correction, thereby reducing the output of the engine 16 by retarding the ignition timing. .

  Next, a vehicle target driving force calculation routine achieved by the braking / driving force control device 14 in the first embodiment will be described with reference to a flowchart shown in FIG. The control according to the flowchart shown in FIG. 2 is started by closing an ignition switch not shown in the figure, and is repeatedly executed at predetermined time intervals. This also applies to control according to flowcharts shown in FIGS. 3 and 4 described later.

  First, in step 210, a signal indicating the wheel speed Vwi detected by the wheel speed sensor 68i is read, and in step 220, the running behavior of the vehicle is determined as known in the art. It is determined whether or not the vehicle is deteriorating as in a spin state or a drift-out state. If a negative determination is made, the process proceeds to step 250. If an affirmative determination is made, the traveling behavior of the vehicle is stabilized in step 220. The target driving force Fxt of the vehicle necessary for making it become is calculated in a manner known in the art.

  In step 225, the left and right rear wheel drive slip amounts SArl and SArr are calculated based on the left and right rear wheel speeds VwRL and VwRR and the vehicle body speed Vb, and the left and right rear wheel drive slip amounts SArl and SArr are averaged. The value is calculated as an index value SAa indicating the degree of necessity for reducing the driving force of the vehicle.

  In step 230, it is determined whether or not the index value SAa is greater than or equal to the first reference value SAa1, that is, whether or not reduction control of the output torque of the engine 16 by controlling the throttle opening is necessary. If a negative determination is made, the process proceeds to step 240. If an affirmative determination is made, the target drive of the vehicle necessary for reducing the drive slip of the left and right rear wheels based on the index value SAa is determined in step 235. The force Fxt is calculated as known in the art.

  In step 240, it is determined whether or not the road surface friction coefficient μ detected by the friction coefficient sensor 66 is equal to or less than a reference value μo (positive constant), that is, the drive slip of the left and right rear wheels may be excessive. If a negative determination is made, the process proceeds to step 250. If an affirmative determination is made, the drive slip of the left and right rear wheels is determined based on the friction coefficient μ of the road surface in step 245. The vehicle target driving force Fxt required to reduce the possibility of becoming excessive is calculated in a manner known in the art.

  In step 250, the vehicle target driving force Fxt is set to the vehicle basic target driving force Fxta. In step 255, the vehicle target driving force Fxt calculated in step 220, 235, 245, or 250 is calculated. Fxt is output to the engine control device 18.

  Next, a vehicle target driving force and ignition timing correction control routine achieved by the braking / driving force control device 14 in the first embodiment will be described with reference to the flowchart shown in FIG.

  First, in step 310, a signal indicating the index value SAa calculated in the vehicle target driving force calculation routine shown in FIG. 2 is read, and in step 315, the index value SAa is read as the first value. When it is determined whether or not it is greater than one reference value SAa1, that is, whether or not the output torque of the engine 16 needs to be reduced by controlling the throttle opening, and if an affirmative determination is made, a step is performed. If the determination is negative, the throttle opening reduction request flag Fth is reset to 0 in step 320, and then the process proceeds to step 380.

  In step 325, the index value SAa is calculated immediately after the index value SAa becomes equal to or greater than the first reference value SAa1 based on the vehicle target driving force Fxt calculated immediately before the index value SAa becomes equal to or greater than the first reference value SAa1. For example, the target driving force Fxt1 by the throttle opening reduction control is calculated by a filter processing calculation of the target driving force Fxt as a value that changes more gently than the lowering of the target driving force Fxt of the vehicle up to the target driving force Fxt of the vehicle. In addition, as a value that changes more gently than the target drive force Fxt and changes more quickly than the target drive force Fxt1, for example, the target drive force by retarding control of the ignition timing by the filter processing calculation of the target drive force Fxt Fxt2 is calculated.

  In step 335, the throttle opening reduction request flag Fth is set to 1, and the target driving force Fxt1 by the throttle opening reduction control and the shift stage information of the automatic transmission 24 input from the shift control device 70 are displayed. The target throttle opening .phi.tb for setting the vehicle driving force to the target driving force Fxt1 is calculated based on the above. In step 340, the vehicle speed Vb, the vehicle lateral acceleration Gy, the road friction coefficient .mu., The engine speed Ne. The second reference value SAa2 related to the index value SAa is calculated from the map shown in FIG. In this case, as shown in FIG. 6, the second reference value SAa2 decreases as the vehicle speed Vb increases, decreases as the absolute value of the vehicle lateral acceleration Gy increases, and decreases as the road surface friction coefficient μ decreases. The calculation is performed such that the lower the rotation speed Ne, the smaller the rotation speed Ne.

  In step 345, it is determined whether or not the index value SAa is greater than or equal to the second reference value SAa2, that is, whether or not the output torque reduction control of the engine 16 by the ignition timing retardation control is necessary. If a negative determination is made, the process proceeds to step 380. If an affirmative determination is made, the process proceeds to step 350.

  In step 350, the deviation determination reference value Fxt3 is calculated from the map shown in FIG. 7 based on the engine speed Ne so that the deviation determination reference value Fxt3 becomes smaller as the engine speed Ne becomes lower.

  In step 355, it is determined whether or not the deviation ΔFxt between the target driving force Fxt1 by controlling the throttle opening and the target driving force Fxt2 by retarding the ignition timing is equal to or greater than the deviation determination reference value Fxt3. It is determined whether or not the output torque reduction control of the engine 16 by the retard angle control is permitted. If a negative determination is made, the process proceeds to step 380. If an affirmative determination is made, the process proceeds to step 370. Proceed to

  In step 370, the rotational vibration amplitudes AwRL and AwRR of the left and right rear wheels 32RL and 32RR are calculated based on the wheel speeds VwRL and VwRR of the left and right rear wheels, and at least one of the amplitudes AwRL and AwRR is rotational vibration. If it is determined whether or not the reference value Awo is greater than or equal to the determination reference value Awo, that is, whether or not rotational vibration has occurred in at least one of the left and right rear wheels that are drive wheels, a positive determination is made. Proceed to 380, and if a negative determination is made, proceed to step 375.

  In this case, the amplitudes AwRL and AwRR of the rotational vibration may be obtained in any manner known in the art. For example, the bandpass filter processing is performed on the wheel speeds VwRL and VwRR of the left and right rear wheels. Thus, the vibration components of the wheel speeds VwRL and VwRR may be extracted, and the difference between the maximum value and the minimum value of the wheel speed may be calculated for the vibration waveform corresponding to a half cycle of the vibration components.

  In step 375, the difference Δμ between the friction coefficients μA and μB of the road surface is calculated, and it is determined whether or not the absolute value of the difference Δμ is equal to or greater than the reference value Δμo for the crossing road determination, that is, to the left and right driving land. When the difference in the friction coefficient of the corresponding road surface is large, it is determined whether or not the traveling road is a so-called straddle road. If a negative determination is made, the process proceeds to step 385, and if an affirmative determination is made, the process proceeds to step 380. At this time, the ignition timing retardation request flag FIG. Is reset to OFF, and the ignition timing retardation correction amount θtb is set to 0. Thereafter, the routine proceeds to step 390.

  In step 385, the ignition timing retard request flag Fig is set to 1, and the ignition timing retard correction amount θt increases as the target driving force Fxt2 by the ignition timing retard control decreases. Based on the target driving force Fxt2 by the timing delay control, the ignition timing retard correction amount θt is calculated. In step 390, the throttle opening reduction request flag Fth, the target throttle opening φstb, the ignition timing retard A signal indicating the request flag FIG. And the ignition timing retardation correction amount θt is output to the engine control device 18, and then the process returns to step 310.

  Next, the control routine for the throttle opening and ignition timing achieved by the engine control device 18 in the first embodiment will be described with reference to the flowchart shown in FIG.

  First, at step 410, a signal indicating the target driving force Fxt of the vehicle is read, and at step 415, the automatic transmission is performed based on the target driving force Fxt in a manner known in the art. 24 target shift speeds St are calculated, and a signal indicating the target shift speed St is output to the shift control device 70.

  In step 420, the target throttle opening φt is calculated based on the target driving force Fxt in a manner known in the art, and in step 425, the intake air amount Ra detected by the air flow meter and Based on the engine speed Ne, the target advance angle θt of the ignition timing is calculated.

  In step 430, it is determined whether or not the throttle opening reduction request flag Fth is 1, that is, whether or not the throttle opening is to be reduced, and a negative determination is made. Sometimes, at step 435, the throttle actuator 38 is controlled so that the opening degree of the throttle valve 36 becomes the target throttle opening degree φt. When an affirmative determination is made, the opening degree of the throttle valve 36 is reduced at step 440. The throttle actuator 38 is controlled to achieve the target throttle opening φtb.

  In step 445, it is determined whether or not the ignition timing retard request flag Fig is 1, that is, whether or not the ignition timing is to be retarded, and a negative determination is made. In step 445, the distributor 72 is controlled based on the target advance angle θt before correction, and when an affirmative determination is made, in step 450, the target advance angle θta (= θt−θtb) after retard correction is set. Based on this, the distributor 72 is controlled.

  Thus, according to the first embodiment shown in the drawing, in the vehicle target driving force calculation routine shown in FIG. 2, the vehicle is based on the friction coefficient of the road surface, the driving slip state of the driving wheel, and the running motion state of the vehicle. When it is determined that it is not necessary to reduce the driving force of the vehicle in order to drive the vehicle stably, the target driving force Fxt of the vehicle is set to the basic target driving force Fxta calculated based on the accelerator opening Ap, When it is determined that it is necessary to reduce the driving force of the vehicle in order to stably drive the vehicle based on the friction coefficient of the road surface, the driving slip state of the driving wheels, and the traveling motion state of the vehicle, the target driving of the vehicle Based on the friction coefficient of the road surface, the driving slip state of the driving wheels, and the traveling motion state of the vehicle, the force Fxt is calculated as the vehicle target driving force Fxt for causing the vehicle to travel stably.

  In step 315 of the vehicle target driving force and ignition timing correction control routine shown in FIG. 3, an index value SAa indicating the degree of necessity for reducing the driving force of the vehicle, that is, the driving slip amount SArl of the left and right rear wheels, By determining whether or not the average value of SArr is equal to or greater than the first reference value SAa1, it is determined whether or not reduction control of the output torque of the engine 16 by controlling the throttle opening is necessary.

  When an affirmative determination is made in step 315, in step 330 it is gentler than the change in decrease in the target drive force Fxt so as to correspond to the responsiveness of the decrease in the drive force of the vehicle due to the actual throttle opening reduction control. The target driving force Fxt1 by the throttle opening reduction control is calculated as a value that changes to a lower value, and the vehicle driving force reduction response by the actual throttle opening reduction control and the actual ignition timing retardation control is calculated. The target driving force Fxt2 by the throttle opening reduction control and the ignition timing retarding control as a value that gently changes below the target driving force Fxt and changes more rapidly than the target driving force Fxt1. Is calculated.

  In step 345, whether or not the index value SAa is equal to or greater than the second reference value SAa2 determines whether or not reduction control of the output torque of the engine 16 by ignition timing retard control is necessary. In step 355, it is determined whether or not the deviation ΔFxt between the target driving force Fxt1 by controlling the throttle opening and the target driving force Fxt2 by retarding the ignition timing is equal to or greater than the deviation determination reference value Fxt3. As a result, it is determined whether or not the engine 16 output torque reduction control by the ignition timing retardation control is permitted.

  Further, in step 370, it is determined whether or not rotational vibration has occurred in at least one of the left and right rear wheels on the basis of the wheel speeds VwRL and VwRR of the left and right rear wheels. Situation where it is prohibited to reduce the output torque of the engine 16 by retarding the ignition timing in order to prevent deterioration of the rotational vibration state of the left and right rear wheels by determining whether or not the road is a so-called crossing road It is determined whether or not.

  If an affirmative determination is made in steps 330, 345, and 355 and a negative determination is made in steps 370 and 375, the throttle opening and ignition timing shown in steps 335 and 385 and FIG. In steps 440 and 450 of the control routine, the engine 16 output torque reduction control by the throttle opening reduction control and the engine 16 output torque reduction control by the ignition timing retardation control are executed.

  On the other hand, even if an affirmative determination is made in step 330, a negative determination is made in step 345 or 355, or even if an affirmative determination is made in steps 330, 345, and 355, step 370 or If an affirmative determination is made at 375, the output torque of the engine 16 is controlled by controlling the throttle opening in step 380 and steps 440 and 455 of the throttle opening and ignition timing control routine shown in FIG. Only the reduction control is executed, and the ignition timing is controlled as usual without being retarded.

  Therefore, according to the first embodiment, the index value SAa is large, the degree of necessity for reducing the output torque of the engine 16 is very high, and the output torque of the engine 16 is reduced by retarding the ignition timing. However, only in a situation where there is no risk of deterioration of the rotational vibration state of the left and right rear wheels, in addition to the reduction control of the output torque of the engine 16 by the throttle opening reduction control, the engine 16 by the retard control of the ignition timing is used. The engine can be controlled to reduce the output torque, and therefore, in a situation where the driving force of the vehicle is required but the degree of necessity is not very high, the ignition timing is prevented from being retarded. The temperature of the exhaust gas and the deterioration of the exhaust gas purification catalyst 48 due to this can be prevented, and the throttle opening is reduced in a situation where the necessity of reducing the driving force of the vehicle is very high. By reducing the ignition timing and retarding the ignition timing, the output of the engine can be reliably and effectively reduced, and the driving force of the vehicle can be reliably and effectively reduced.

  Even if the degree of necessity for reducing the output torque of the engine 16 is very high, if the output torque of the engine 16 is reduced by retarding the ignition timing, the rotational vibration state of the left and right rear wheels may be deteriorated. Sometimes, it is possible to prevent the ignition timing from being retarded, thereby reliably preventing the rotational vibration state of the left and right rear wheels from being deteriorated by the reduction of the output torque of the engine 16 by retarding the ignition timing. it can.

  For example, when the index value SAa increases or decreases, as shown in FIG. 8, the determination in step 315 becomes a positive determination at time t1, the negative determination at time t10, and the determination in step 345 occurs. Assume that an affirmative determination is made at time t2 after t1, and a negative determination is made at time t6 before time t10. The determination in step 355 is affirmative determination at time t3 after time t2, negative determination and positive determination at times t4 and t5 prior to time t6, and after time t6. Assume that a negative determination is made at time t7, and an affirmative determination and a negative determination are made at times t8 and t9 before time t10, respectively.

  In this situation, the throttle opening reduction request flag Fth becomes 1 from time t1 to time t10 unless the retard of ignition timing is prohibited by making a positive determination in step 370 or 375. The ignition timing retard flag Flag is set to 1 from t3 to time t4 and from time t5 to time t6. Therefore, the throttle opening is reduced from time t1 to time t10, but the ignition timing is delayed from time t3 to time t4 and from time t5 to time t6.

  In general, when the engine speed Ne is low, the flow velocity of air, mixed gas, or the like in the engine 16 is lower than when the engine speed Ne is high, thereby reducing the throttle opening. Therefore, in order to effectively reduce the engine output, the ignition timing needs to be retarded when the engine speed Ne is low compared to when the engine speed Ne is high. High nature.

In particular, according to the first embodiment shown in the figure, in step 350, the deviation determination reference value Fxt3 is reduced as the engine speed Ne is lower based on the map shown in FIG. Since the deviation determination reference value Fxt3 is variably set, it is easy to determine that the deviation ΔFxt of the target driving force is greater than or equal to the deviation determination reference value Fxt3 when the engine speed Ne is low compared to when the engine speed Ne is high. Therefore, even in a situation where the engine speed Ne is low and the speed of the engine output decrease due to the throttle opening being reduced, the engine output is effectively reduced by retarding the ignition timing, Thereby, the driving force of the vehicle can be effectively reduced.
[Second Example]

  FIG. 9 is a flow chart showing a vehicle target driving force and ignition timing correction control routine achieved by the braking / driving force control device 14 in the second embodiment of the vehicle driving force control device according to the present invention. In FIG. 9, the same steps as those shown in FIG. 3 are assigned the same step numbers as those shown in FIG.

  In this embodiment, the steps of the vehicle target driving force calculation routine and the throttle opening and ignition timing control routine are executed in the same manner as in the first embodiment. In addition, steps 310 to 320, steps 335 to 345, and steps 355 to 390 of the vehicle target driving force and ignition timing correction control routine of this embodiment are executed in the same manner as in the first embodiment described above. Steps corresponding to step 350 in the first embodiment described above are omitted.

  As shown in FIG. 9, when an affirmative determination is made in step 315, the target driving force Fxt1 by the throttle opening reduction control is determined in step 330 as in the case of the first embodiment described above. Although the target driving force Fxt2 by the ignition timing retarding control is calculated, as shown in FIG. 10, the lower gradient of the target driving force Fxt1 by the throttle opening reduction control becomes smaller as the engine speed Ne becomes lower. As described above, the decreasing gradient of the target driving force Fxt1 by the throttle opening reduction control is variably set according to the engine speed Ne when the index value SAa becomes equal to or higher than the first reference value SAa1. This variable setting corresponds to the fact that the lower gradient of the driving force of the vehicle due to the throttle opening reduction control becomes smaller as the engine speed Ne becomes lower.

  Thus, according to the second embodiment shown in the figure, as in the case of the first embodiment described above, the index value SAa is large, the degree of necessity for reducing the output torque of the engine 16 is very high, and the ignition timing is retarded. Even if the output torque of the engine 16 is reduced by the control, the output torque reduction control of the engine 16 by the throttle opening reduction control is performed only in a situation where there is no risk of deterioration of the rotational vibration state of the left and right rear wheels. In addition, it is possible to control the reduction of the output torque of the engine 16 by retarding the ignition timing, and therefore it is necessary to reduce the driving force of the vehicle, but in a situation where the degree of necessity is not very high. It is possible to prevent the ignition timing from being retarded to prevent the temperature of the exhaust gas of the engine from rising and the deterioration of the exhaust gas purification catalyst due to this, and the necessity of reducing the driving force of the vehicle is very high. In high situations, the throttle opening can be reduced and the ignition timing can be retarded to reliably and effectively lower the engine output, thereby reducing the driving force of the vehicle reliably and effectively. Furthermore, it is possible to reliably prevent the rotational vibration state of the left and right rear wheels from being deteriorated by reducing the output torque of the engine 16 by retarding the ignition timing.

Further, according to the second embodiment, the index value SAa becomes equal to or higher than the first reference value SAa1 so that the decreasing gradient of the target driving force Fxt1 by the throttle opening reduction control becomes smaller as the engine speed Ne becomes lower. The decreasing gradient of the target driving force Fxt1 by the throttle opening reduction control is variably set according to the engine rotational speed Ne at that time. Therefore, the lower the engine speed Ne, the larger the target driving force deviation ΔFxt. As a result, it becomes easier to make an affirmative determination in step 355. Therefore, as in the case of the first embodiment, the engine speed Ne. The engine output is effectively reduced by retarding the ignition timing, and the driving force of the vehicle is effectively reduced even in situations where the engine output is reduced at a low speed due to low throttle opening. Can be reduced.
[Third embodiment]

  FIG. 11 is a flow chart showing a vehicle target driving force and ignition timing correction control routine achieved by the braking / driving force control device 14 in the third embodiment of the vehicle driving force control device according to the present invention. In FIG. 11, the same steps as those shown in FIG. 3 are assigned the same step numbers as those shown in FIG.

  Also in this embodiment, the steps of the vehicle target driving force calculation routine and the throttle opening and ignition timing control routine are executed in the same manner as in the first embodiment. Further, Steps 310 to 345 and Steps 370 to 390 of the vehicle target driving force and ignition timing correction control routine of this embodiment are executed in the same manner as in the case of the first embodiment described above. Instead of steps 350 and 355 in the embodiment, steps 360 and 365 are executed, respectively.

  Step 360 is executed when an affirmative determination is made in Step 345. In Step 360, the vehicle target driving force Fxt (calculated immediately before the index value SAa becomes equal to or greater than the first reference value SAa1). Fxta) and a deviation ΔFxt between the vehicle target driving force Fxt (Fxtb) calculated immediately after the index value SAa becomes equal to or greater than the first reference value SAa1, and based on the target driving force deviation ΔFxt. A reference value Ne3 related to the engine speed Ne is calculated from the map shown in FIG. In this case, as shown in FIG. 12, the reference value Ne3 is calculated so as to increase as the target driving force deviation ΔFxt increases.

  In step 365, it is determined whether or not the engine speed Ne is less than or equal to the reference value Ne3, that is, whether or not the output torque reduction control of the engine 16 by the ignition timing retardation control is permitted. When a determination is made and an affirmative determination is made, the process proceeds to step 370. When a negative determination is made, the process proceeds to step 380.

  Thus, according to the third embodiment shown in the figure, as in the case of the first and second embodiments described above, the index value SAa is large, the degree of necessity for reducing the output torque of the engine 16 is very high, and the ignition timing Even if the output torque of the engine 16 is reduced by the retard angle control, the output torque of the engine 16 by the throttle opening reduction control is only in a situation where there is no possibility that the rotational vibration state of the left and right rear wheels will deteriorate. In addition to this reduction control, it is possible to perform reduction control of the output torque of the engine 16 by retarding the ignition timing.

  Further, according to the third embodiment shown in the figure, the lower the engine speed Ne and the lower the engine output decrease rate due to the reduced throttle opening, the lower the engine 16 output torque by the ignition timing retard control. Since the reduction can be easily performed, the ignition timing is reduced even in a situation where the decrease rate of the engine output due to the reduction of the throttle opening is low, as in the case of the first and second embodiments described above. The engine output can be effectively reduced by this retardation, and thereby the driving force of the vehicle can be effectively reduced.

  Further, according to the third embodiment shown in the figure, in a situation where the index value SAa is equal to or greater than the second reference value SAa2 and the positive determination is made in steps 315 and 345, the engine speed Ne is set to the reference value Ne3. Since the ignition timing is retarded if it is below, the ignition timing is retarded earlier than in the case of the first and second embodiments, so that the engine output is reduced and the vehicle is driven accordingly. Power reduction can be achieved early.

  For example, FIG. 13 shows an example of changes in the flags Fth and Fig when the index value SAa changes in the same manner as in FIG. 8 in a situation where the engine speed Ne is equal to or less than the reference value Ne3. As shown in FIG. 13, in the case of the third embodiment, the determination in step 365 is affirmative at time t2, and the positive determination is performed in step 370 or 375, so that ignition is performed. As long as the retard of the timing is not prohibited, the flag FIG. Becomes 1 at the time t2, so that the ignition is performed earlier than in the first and second embodiments in which the flag FIG. 1 becomes 1 at the time t3. The timing delay can be started. Although the end of the ignition timing retardation is not shown in FIG. 13, when the index value SAa is less than the second reference value SAa2 or the engine speed Ne is greater than the reference value Ne3. In this case, the flag Fig becomes 0, and the ignition timing retardation is completed.

  In particular, according to the third embodiment shown in the figure, the reference value Ne3 related to the engine speed Ne is calculated so as to increase as the target driving force deviation ΔFxt increases, as shown in FIG. As the force deviation ΔFxt is larger and the required reduction amount of the driving force of the vehicle is larger, the output torque of the engine 16 can be more easily reduced by the retard control of the ignition timing, and the reference value Ne3 is a constant value. Compared to the case, it is possible to appropriately determine whether or not it is necessary to execute the retard control of the ignition timing according to the necessary reduction amount of the driving force of the vehicle.

  According to each of the above-described embodiments, in step 370, it is determined whether or not rotational vibration has occurred in at least one of the left and right rear wheels based on the wheel speeds VwRL and VwRR of the left and right rear wheels. In step 375, since it is determined whether or not the traveling road is a so-called straddle road, it is determined whether or not the rotational vibration state of the left and right rear wheels may be deteriorated. Compared with the case where only one of the determinations in step 370 or 375 is performed, it is more reliable and effective that the rotational vibration state of the left and right rear wheels is deteriorated by the reduction of the output torque of the engine 16 by the retard control of the ignition timing. Can be prevented.

  Further, according to each of the above-described embodiments, the output torque reduction control of the engine 16 by the ignition timing retardation control is limited at the start of the vehicle driving force reduction control, or the execution time thereof is reduced. Since it is not limited to a certain time after the start of the control, the driving slip of the driving wheel is again performed after the output torque reduction control of the engine 16 is performed by the throttle opening degree control and the ignition timing retardation control. Even if it becomes excessive, the output torque of the engine 16 can be reliably and effectively reduced by controlling the throttle opening and retarding the ignition timing, and the drive slip of the drive wheels can be reliably and effectively reduced. it can.

  In each of the above-described embodiments, when the index value SAa is equal to or greater than the second reference value SAa2, the engine output is reduced by both the reduction of the throttle opening and the retard of the ignition timing, thereby driving the vehicle. Since the force is efficiently reduced, the index value SAa quickly decreases, and therefore, the retard of the ignition timing is not continued excessively long.

  Further, according to the above-described embodiments, in step 340, the second reference value SAa2 is smaller as the vehicle speed Vb is higher, and smaller as the absolute value of the lateral acceleration Gy of the vehicle is larger, as shown in FIG. When the second reference value SAa2 is a constant value, it is variably set according to the vehicle speed Vb, the lateral acceleration Gy of the vehicle, and the friction coefficient μ of the road surface so as to decrease as the friction coefficient μ of the road surface decreases. On the other hand, according to the vehicle speed Vb, the lateral acceleration Gy of the vehicle, and the friction coefficient μ of the road surface, in other words, according to the possibility of destabilization of the traveling motion of the vehicle due to the excessive driving force of the vehicle. Thus, it is possible to appropriately determine whether or not the ignition timing retardation control is necessary.

  Further, according to the above-described embodiments, in step 340, the second reference value SAa2 is variably set in accordance with the engine speed Ne so that the second reference value SAa2 becomes smaller as the engine speed Ne becomes lower, as shown in FIG. Therefore, compared with the case where the second reference value SAa2 is a constant value regardless of whether the engine speed Ne is high or low, the engine output Ne is low and the engine output is quickly reduced by reducing the throttle opening. Even in situations where it is impossible to do so, the engine output can be reduced quickly and reliably, and conversely, the engine output can be reduced relatively quickly even when the engine speed Ne is relatively high and the throttle opening is reduced. In the situation, it is possible to prevent the ignition timing from being retarded unnecessarily, thereby increasing the temperature of the exhaust gas and causing the deterioration of the exhaust gas purification catalyst. It is possible to reliably reduce the possibility.

  Further, according to the above-described embodiments, in step 325 or 330, the target driving force Fxt1 by the throttle opening reduction control and the target driving force Fxt2 by the ignition timing retardation control are calculated, and the throttle opening is reduced. In step 440, since the opening of the throttle valve 36 is controlled so as to become the target throttle opening φtb corresponding to the target driving force Fxt1, the opening of the throttle valve 36 is reduced or reduced too quickly. Can be reliably prevented from becoming too slow.

  Similarly, when the ignition timing is retarded, in step 450, the target driving force Fxt1 based on throttle opening reduction control and the target driving force Fxt2 based on throttle opening reduction control and ignition timing retardation control are compared. Since the ignition timing is controlled so that the ignition timing is retarded with the retardation correction amount corresponding to the deviation ΔFxt, it is ensured that the ignition timing is retarded too early or too late. Can be prevented.

  Although the present invention has been described in detail with reference to specific embodiments, the present invention is not limited to the above-described embodiments, and various other embodiments are possible within the scope of the present invention. It will be apparent to those skilled in the art.

  For example, in each of the embodiments described above, the engine output reduction means for reducing the engine output by reducing the fuel supply amount to the engine reduces the engine output by retarding the ignition timing of the engine. However, the engine output reduction means may reduce the engine output by reducing the fuel supply amount to the engine, and may reduce the engine output by both retarding the ignition timing and reducing the fuel supply amount. It may be reduced.

  In particular, when the engine output reduction means reduces the engine output by reducing the amount of fuel supplied to the engine, the target driving force Fxt2 in each of the above embodiments is the throttle opening reduction control and the fuel supply. The amount of fuel supply is calculated according to the deviation ΔFxt between the target drive force Fxt1 and the target drive force Fxt2.

  Similarly, when the engine output reduction means reduces the engine output by retarding the ignition timing and reducing the fuel supply amount, the target driving force Fxt2 in each of the above embodiments is equal to the throttle opening degree. It is calculated as a target driving force by reduction control, ignition timing retardation control, and fuel supply amount reduction control, and the ignition timing retardation correction amount and fuel supply amount reduction amount are the difference between the target driving force Fxt1 and the target driving force Fxt2. It is controlled according to the deviation ΔFxt.

  In each of the above-described embodiments, it is determined in step 370 whether or not rotational vibration has occurred in at least one of the left and right rear wheels based on the wheel speeds VwRL and VwRR of the left and right rear wheels. In step 375, it is determined whether or not the traveling road is a so-called straddle road, but the determination in either step 370 or 375 may be omitted.

  In each of the above-described embodiments, the determination reference value Awo in step 370 and the determination reference value Δμo in step 375 are constants. For example, the lower the road friction coefficient, the slower the ignition timing. Since the rotational vibration of the driving wheel is easily generated by reducing the engine output due to the corner, the reference value Awo is set to the friction coefficient of the road surface so that it becomes smaller when the friction coefficient of the road surface is low than when the friction coefficient of the road surface is high. The reference value Δμo may be modified so as to be variably set accordingly, so that when the lower value of the friction coefficient μA and μB of the road surface is low, the reference value Δμo is smaller than when the lower value is high. It may be modified so as to be variably set according to the lower value of the friction coefficient μA and μB of the road surface.

  Further, in each of the above-described embodiments, when the determination of steps 215, 230, and 240 is performed and the running behavior of the vehicle is deteriorated, the road surface when the index value SAa is equal to or greater than the first reference value SAa1. When the friction coefficient μ is equal to or less than the reference value μo, the vehicle target driving force Fxt necessary to reduce the possibility of excessive driving slip of the left and right rear wheels is calculated. The determination of any of steps 215, 230, and 240 may be omitted, and the determination of whether or not it is necessary to reduce the driving force of the vehicle is modified to be determined based on the travel information of other vehicles. May be.

  In each of the above-described embodiments, the determination reference value SAa1 in step 230 is the same as the determination reference value SAa1 in step 315, but these determination reference values may be different from each other. Further, the reference value SAa1 for determination in steps 230 and 315 is a constant, but at least one of the reference values for determination in steps 230 and 315 is variably set in accordance with the engine speed Ne so that it becomes smaller as the engine speed Ne is lower. It may be modified so that.

  In the above-described embodiments, the target driving force Fxt of the vehicle is calculated by the driving force control device 14 separately from the basic target driving force Fxt calculated by the engine control device 18, and based on the target driving force Fxt. The target gear stage St and the target throttle opening degree φt of the automatic transmission 24 are calculated. When it is not necessary to reduce the driving force of the vehicle, the accelerator opening degree is the same as in the case of a general vehicle. The throttle opening φ may be controlled based on Ap or the like, and the gear position of the automatic transmission 24 may be controlled based on the throttle opening φ and the vehicle speed.

  In each of the above-described embodiments, when the index value SAa is equal to or greater than the first reference value SAa1, the target driving force Fxt1 by the throttle opening reduction control is calculated, and the target throttle is based on the target driving force Fxt1. The opening degree φtb is calculated, and the throttle opening degree φ is controlled based on the target throttle opening degree φtb. However, the throttle opening degree φ is corrected so as to be reduced and corrected based on the index value SAa, for example. Also good.

  Similarly, when the index value SAa is equal to or greater than the second reference value SAa2, the target driving force Fxt2 by the throttle opening reduction control and the ignition timing retardation control is also calculated, and the target driving force Fxt1 and the target driving force Fxt2 are calculated. The ignition timing retardation correction amount θtb is calculated based on the deviation ΔFxt of the ignition timing, and the ignition timing is retarded based on the ignition timing retardation correction amount θtb. May be modified to be retarded based on

  Further, in each of the above-described embodiments, the determination of step 355 or 365 is performed in addition to the determination of step 345, and when these determination results are affirmative determination, the ignition timing is retarded. However, the determination in step 355 or 365 may be omitted, and if an affirmative determination is made in step 345, the ignition timing may be delayed.

  In each of the above-described embodiments, the second reference value related to the index value SAa from the map shown in FIG. 6 based on the vehicle speed Vb, the vehicle lateral acceleration Gy, and the road friction coefficient μ in step 340. SAa2 is calculated, but any parameter of the vehicle speed Vb, the lateral acceleration Gy of the vehicle, and the friction coefficient μ of the road surface may be omitted, and the second reference value SAa2 is set to a constant value. It may be set.

  In the first embodiment described above, the deviation determination reference value Fxt3 is variably set according to the engine speed Ne so that the deviation determination reference value Fxt3 becomes smaller as the engine speed Ne becomes lower in step 350. However, step 350 may be omitted and the deviation determination reference value Fxt3 may be set to a constant value.

  Similarly, in the third embodiment described above, in step 360, the reference value Ne3 is set in accordance with the target driving force deviation ΔFxt so that the reference value Ne3 increases as the target driving force deviation ΔFxt increases. Although it is variably set, step 360 may be omitted and the reference value Ne3 may be set to a constant value.

  Further, in each of the above-described embodiments, the vehicle is a rear wheel drive vehicle, but the vehicle to which the present invention is applied may be a front wheel drive vehicle or a four wheel drive vehicle, and the automatic transmission 24 may have a torque. Although the multistage automatic transmission including the converter 20 is used, the transmission of the vehicle to which the present invention is applied may be a continuously variable transmission.

FIG. 1 is a schematic configuration diagram (A) and a block diagram (B) of a control system showing a first embodiment of a vehicle driving force control device according to the present invention applied to a rear wheel drive vehicle. It is a flowchart which shows the target driving force calculation routine of the vehicle achieved by the braking / driving force control apparatus in a 1st Example. 3 is a flowchart showing a correction control routine for a target driving force and ignition timing of a vehicle achieved by the braking / driving force control device in the first embodiment. It is a flowchart which shows the control routine of the throttle opening degree and ignition timing which are achieved by the engine control apparatus in the first embodiment. An example of the change in the target driving force Fxt, the target driving force Fxt1 by the throttle opening reduction control, and the target driving force Fxt2 by the throttle opening reduction control and the ignition timing retardation control in the first embodiment is shown. It is a graph. It is a figure which shows the map for 2nd reference value SAa2 calculation based on the vehicle speed Vb, the absolute value of the lateral acceleration Gy of a vehicle, and the friction coefficient μ of a road surface. It is a figure which shows the map for deviation determination reference value Fxt3 calculation based on the engine speed Ne. FIG. 4 is a time chart showing an example of determinations in steps 315, 345, and 355 of FIG. 3 and changes in a throttle opening reduction request flag Fth and ignition timing retard request flag FIG. It is a flowchart which shows the correction control routine of the target drive force and ignition timing of the vehicle which are achieved by the braking / driving force control device in the second embodiment. An example of the change in the target driving force Fxt, the target driving force Fxt1 by the throttle opening reduction control, and the target driving force Fxt2 by the throttle opening reduction control and the ignition timing retardation control in the second embodiment is shown. It is a graph. It is a flowchart which shows the correction | amendment control routine of the target drive force and ignition timing of a vehicle which are achieved by the braking / driving force control apparatus in a 3rd Example. It is a figure which shows the map for the reference value Ne3 calculation based on deviation (DELTA) Fxt of target drive force. FIG. 12 is a time chart showing an example of discrimination, throttle opening reduction request flag Fth, and change in ignition timing retard request flag FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Driving force control apparatus, 14 ... Braking / driving force control apparatus, 18 ... Engine control apparatus, 16 ... Engine, 24 ... Automatic transmission, 36 ... Throttle valve, 42 ... Accelerator pedal, 52 ... Engine speed sensor, 54 ... Brake device, 64 ... lateral acceleration sensor, 66A, 66B ... friction coefficient sensor, 68i ... wheel speed sensor, 70 ... transmission control device,

Claims (13)

  Throttle opening control means for controlling the throttle opening of the engine based on at least the driving operation amount of the driver; and the output of the engine by retarding the ignition timing of the engine or reducing the fuel supply amount to the engine. The engine output reducing means for reducing and the degree of necessity for reducing the driving force of the vehicle based on the running state of the vehicle are determined, and when the degree of necessity is high, the engine output is controlled by controlling at least the throttle opening degree control means. Driving force reduction control means for reducing the throttle force, the driving force reduction control means reduces the throttle opening degree controlled by the throttle opening degree control means when the degree of necessity is greater than or equal to a first reference value, When the required degree is equal to or greater than a second reference value larger than the first reference value, the throttle opening control means A driving force control apparatus for a vehicle configured to reduce the engine output by the engine output reduction means in addition to the reduction of the throttle opening to be controlled, wherein the driving force reduction control means is the engine output reduction means Rotational vibration state determining means for determining the possibility of deteriorating the rotational vibration state of the drive wheels by reducing the engine output by the engine, and the rotational vibration state determining means even if the necessary degree is equal to or greater than the second reference value And a prohibiting means for prohibiting reduction of the engine output by the engine output reducing means when it is determined that there is a risk of deteriorating the rotational vibration state of the drive wheels. Control device.   The rotational vibration state determining means includes means for detecting rotational vibration of the driving wheel, and worsens the rotational vibration state of the driving wheel when the degree of rotational vibration of the driving wheel is equal to or higher than a reference value for rotational vibration determination. The vehicle driving force control apparatus according to claim 1, wherein it is determined that there is a fear.   The rotational vibration state determining means includes means for detecting a friction coefficient of the road surface corresponding to the left and right drive wheels, and a difference in the friction coefficient of the road surface corresponding to the left and right drive wheels is equal to or greater than a reference value for straddle road determination. The vehicle driving force control apparatus according to claim 1, wherein it is determined that the rotational vibration state of the driving wheel is likely to deteriorate.   The driving force control device has means for calculating a target driving force of the vehicle based on a driving operation amount of the driver and a running state of the vehicle, and the driving force reduction control means has the degree of necessity of the first reference value. Based on the two target driving forces calculated before and after the above, the target driving force by the control of the throttle opening control means that changes more gently than the lower change between the two target driving forces, The throttle opening control means and the engine output that change more gently than the change between the two target driving forces and change more rapidly than the change in the target driving force under the control of the throttle opening control means. The target driving force by the control of the reducing means is calculated, the required degree is not less than the second reference value, and the target driving force by the control of the throttle opening control means and the throttle The engine output reduction means reduces the engine output when the deviation from the target driving force by the control of the degree control means and the engine output reduction means is equal to or greater than a deviation determination reference value. The means is a deviation between the target driving force controlled by the throttle opening control means and the target driving force controlled by the throttle opening control means and the engine output reduction means when the necessary degree is equal to or greater than the second reference value. Even when the deviation determination reference value is equal to or greater than the deviation determination reference value, when it is determined that the rotational vibration state of the driving wheel is likely to be deteriorated by the rotational vibration state determination unit, the output of the engine by the engine output reduction unit is determined. 4. The driving force control apparatus for a vehicle according to claim 1, wherein the reduction is prohibited.   5. The deviation determination reference value is variably set according to the engine speed so that the deviation determination reference value is smaller when the engine speed is low than when the engine speed is high. The driving force control device for a vehicle according to claim 1.   According to the engine speed, the gradient of the decrease in the target driving force under the control of the throttle opening control means is smaller when the engine speed is low than when the engine speed is high. The vehicle driving force control device according to claim 4, wherein the vehicle driving force control device is variably set.   The vehicle driving force control device according to any one of claims 4 to 6, wherein the throttle opening control means controls the throttle opening based on a target driving force controlled by the throttle opening control means. .   The engine output reducing means reduces the engine output based on a deviation between a target driving force controlled by the throttle opening control means and a target driving force controlled by the throttle opening control means and the engine output reducing means. The vehicle driving force control apparatus according to any one of claims 4 to 7.   The driving force reduction control means outputs the engine output by the engine output reduction means when the degree of necessity is not less than the second reference value and the engine speed is not more than an engine speed judgment reference value. The prohibiting means determines the rotational vibration state even if the degree of necessity is equal to or greater than the second reference value and the engine speed is equal to or less than the engine speed determination reference value. 4. The engine output reduction means prohibits reduction of the engine output when it is determined by the means that there is a risk of deteriorating the rotational vibration state of the drive wheel. 5. The driving force control device for a vehicle according to claim 1.   The driving force control device has means for calculating a target driving force of the vehicle based on a driving operation amount of the driver and a running state of the vehicle, and is calculated before and after the degree of necessity becomes the first reference value or more. With the difference between the two target driving forces as a reference target driving force difference, the engine speed determination reference value is larger when the reference target driving force difference is larger than when the reference target driving force difference is small. The vehicle driving force control device according to claim 9, wherein the vehicle driving force control device is variably set according to the reference target driving force difference.   The vehicle driving force control according to any one of claims 1 to 10, wherein the second reference value is variably set based on at least one of a frictional property of a road surface, a lateral acceleration of the vehicle, and a vehicle speed. apparatus.   The second reference value is variably set according to the engine speed so that the second reference value is smaller when the engine speed is low than when the engine speed is high. The vehicle driving force control apparatus according to any one of 1 to 11. The driving force reduction control means determines the degree of necessity based on at least one of a required amount of reduction of the target driving force of the vehicle based on a running motion state of the vehicle, a degree of driving slip of the driving wheel, and a friction coefficient of the road surface. The driving force control apparatus for a vehicle according to any one of claims 1 to 12.

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