JP3294350B2 - Vehicle drive system - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicular drive apparatus that drives by using a motor in addition to an engine.

[0002]

2. Description of the Related Art In recent vehicles, the number of four-wheel drive vehicles tends to increase. However, in order to reduce the weight and the like, main drive wheels for driving one of right and left front wheels and right and left rear wheels by an engine. In some cases, the other wheel is used as an auxiliary drive wheel driven by a motor. Japanese Patent Application Laid-Open No. Hei 2-12036 discloses a technique in which two motors having different driving forces are used to change the type and number of motors to be operated in accordance with the gear position of a transmission, that is, a motor. A method of changing the auxiliary driving force by a motor has been proposed.

Japanese Patent Laying-Open No. 57-74222 discloses that the distribution of hydraulic pressure to two right and left hydraulic motors (hydraulic cylinders) is automatically performed according to the road load applied to the left and right auxiliary drive wheels. In addition, a device having a function of a differential device has been proposed.

Japanese Unexamined Patent Publication (Kokai) No. 63-38031 discloses the use of two electric motors on the left and right sides. The higher the vehicle speed, the larger the generated voltage and the constant the generated torque of the motor. With the manual switch,
There has been proposed an apparatus which can switch between driving execution and driving stop by a motor.

[0005]

By the way, the conventional driving assist using a hydraulic motor is to convert a part of the torque generated by the engine into a form of hydraulic pressure and directly use it as it is. Therefore, the vehicle is not driven with a torque greater than the torque generated by the engine. That is, only the generated torque of the engine is distributed to the main drive wheels and the auxiliary drive wheels. Such a driving state is not particularly problematic when considered as a simple four-wheel drive vehicle that travels on a snowy road or the like for a long time.

On the other hand, recently, it has been considered to temporarily use an auxiliary drive wheel using a motor in order to enhance acceleration. In this case, a drive using a conventional hydraulic motor cannot obtain a drive torque higher than the torque generated by the engine, and thus cannot sufficiently satisfy the demand for improvement in acceleration and the like.

Accordingly, an object of the present invention is to provide a hydraulic motor
It is an object of the present invention to provide a vehicle drive device capable of temporarily driving a vehicle with a large torque equal to or larger than the torque generated by an engine on the premise of performing driving assistance using a motor.

[0008]

In order to achieve the above object, the present invention basically has the following configuration. That is, as described in claim 1 of the claims, one of the left and right front wheels and the left and right rear wheels is a main drive wheel driven by an engine via a transmission and a differential device. A vehicle in which the other wheel is an auxiliary driving wheel driven by a hydraulic motor, a reservoir tank for storing oil, an accumulator for accumulating hydraulic pressure, and the reservoir tank. A pump for pumping up the oil liquid inside and accumulating the pressure in the accumulator;
A supply circuit for supplying the hydraulic pressure accumulated in the accumulator to the motor; and a supply circuit for bypassing the supply circuit, wherein the motor is rotated by the auxiliary drive wheels. When the motor functions as the pump, the accumulator circuit for supplying the oil liquid in the reservoir tank to the accumulator, opening / closing means for opening / closing the accumulator circuit, and a predetermined accumulating condition. Pressure accumulating control means for causing the on-off valve to be opened, causing the motor to function as a pump, and accumulating pressure in the accumulator, wherein the motor has a left auxiliary drive wheel. , And a right motor for driving a right auxiliary driving wheel. The accumulator circuit has at least a portion between the motor and the accumulator in parallel with each other. Relationship In this way, the left and right motors are formed independently of each other, and the accumulator is set as a common one connected to the left and right pressure accumulator circuits. A check valve for preventing the flow of the oil liquid from the accumulator to the motor is connected between the motor and the motor.

[0009]

According to the present invention, the motor is driven by using the hydraulic pressure stored in the accumulator to drive the vehicle with a torque greater than the engine generated torque by the amount of the motor driving force. This is suitable for responding to a temporary drive force increase request. Further, while the large-sized accumulator is also used for the left and right motors, the accumulator can accumulate the pressure independently by the left and right motors, that is, the left and right auxiliary drive wheels.

[0010] Preferred embodiments of the invention are as set forth in the claims, the advantages of which will become apparent with reference to the following description of the embodiments.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hydraulic system, etc. (FIG. 1) In FIG. 1, 1FL is a left front wheel, 1FR is a right front wheel, 1R
L is a left rear wheel, and 1RR is a right rear wheel. An engine 2 is disposed in front of the vehicle body, and a driving force of the engine 2, that is, a generated torque is transmitted to a differential device 5 via a clutch 3, a manual transmission 4 having five forward speeds, and one reverse speed. Then, the left front wheel 1FL is output from the differential device 5 via the left drive shaft 6L.
The engine driving force is transmitted to the right front wheel 1FR via the right drive shaft 6R.

The left and right front wheels 1FL and 1FR to be steered are linked by a steering link 7 such as a tie rod, and the steering link 7 and the handle 8 are linked by a rack and pinion mechanism 9.

The left and right rear wheels 1RL, 1RR are
Separately and independently, a pair of left and right hydraulic motors ML, MR
It is adapted to be driven by. That is, the left rear wheel 1RL is connected to the left motor M via the left drive shaft 11L.
L, and the right rear wheel 1RR is driven by the right drive shaft 11
Driven by the right motor MR via R. This motor ML, that is, the left drive shaft 11L
And the motor MR, that is, the right drive shaft 11R, are separated from each other so that the left and right can be driven independently. The left and right drive shafts 11L and 11R are
The hydraulic clutch 12 is capable of intermittent operation.

The motor ML (MR) is of a turbine type (impeller type) and has a first connection port La (Ra) and a second connection port Lb (Rb), and La (Ra). ) To Lb (Rb)
When the high-pressure oil liquid flows to the
When the high-pressure oil liquid flows in a direction opposite to this, the rotation is made in the backward direction. The motors ML and MR have the same specifications, and the total value of the maximum generated torque is about 1/3 to 1/2 of the maximum generated torque of the engine 2. In the embodiment, the rear wheel drive by the motors ML and MR is executed only under predetermined conditions described later. That is, the left and right front wheels 1FL,
Even when 1FR is driven, the left and right rear wheels 1RL, 1RL
RR may not be driven by the motors ML and MR.

P is a pump as a hydraulic pressure generating source. This pump P is of a variable displacement type, and has an output shaft 2 of the engine 2.
The drive pulley 13, the belt 14, and the driven pulley 15 drive the drive pulley 13a. The high-pressure oil pumped by the pump P from the reservoir tank 16 is discharged to a high-pressure line 18 to which a check valve 17 is connected. From this high-pressure line 18, first and second hydraulic pressure supply lines 31A and 31B connected to the check valve 10 or 32 are connected in parallel. A release line 23 extends from the reservoir tank 23.
Furthermore, each connection port La, Lb (R) of the motor ML (MR)
a, Rb), the parallel lines 20L, 21L
(20R, 21R) are derived.

Lines 20L and 21L of the left motor ML are provided with a switching valve VVA, mutually parallel lines 19 and 19L and lines 22 and 22L, and switching valves VVB · L and VVE ·.
L, the first supply line 31A and the release line 23
Can be selectively connected to. Similarly, lines 20R and 21R of the right motor MR are connected to the switching valves VVA,
Lines 19, 19R and lines 22, 22 parallel to each other
R, and switching valves VVB • R, VVE • R,
The first supply line 31A and the release line 23 can be selectively connected.

A switching valve VVI is connected to the second common supply line 31B on the downstream side of the check valve 32, and a flow dividing valve 34 is further connected on the downstream side. One branch supply line 33L branched into two by the branch valve VVI is connected to the line 19L, and the other branch supply line 33R is connected to the line 19R.

An accumulator 41 for storing high-pressure oil pressure is connected to the high-pressure line 18. For this high pressure line 18, a line 20L (20R)
Are connected by a passage 42L (42R). This passage 42L (42R) has a check valve 43L (43
R) and the switching valve VVF · L (VVF · R) are connected. The passages 43L and 43R are parallel to each other, and each of the valves VVA, VVB · L (VVB · R), VVE · L (V
VE · R), VVI, the flow dividing valve 34 and the like are bypassed.

The line 20L (20R) and the line 21
L (21R) is communicated with a communication path 51L (51R), and a variable orifice VVC · L (VVC · R) is connected to the communication path 51L (51R).

An actuator for engaging and disengaging the clutch 12 is indicated by reference numeral 61. This actuator 61
Supply line 62 for high pressure line 18 and discharge line 63 for release line 23, switching valve VVJ
And the two lines 62 and 63 can be shut off by the switching valve VVJ.

The left and right motors ML and MR are connected to each other by a communication passage 71.
VD is connected. The release line 23 is connected to the high pressure line 18 on the upstream side (pump P side) of the check valve 17 via a load / unload valve VVH and on the downstream side of the check valve 17. Are connected via a safety valve VVG.

Description of Control Modes (Table 1) This embodiment has a total of eight types of control modes, as will be described later, and controls each of the above-described valves when each mode is executed. The operating conditions are summarized in Table 1 below. In this table, symbols “L” and “R” for identifying left and right are omitted. The load / unload valve VVH not shown in Table 1 is controlled to open and close so that the pressure in the high pressure line 18 falls within a predetermined pressure range between a lower limit and an upper limit.

[0023]

[Table 1]

In each control mode shown in Table 1, the operating state of the valve which plays a major role will be specifically described.
It is as follows. (1) Integrated mode In the integrated mode, as will be described in detail later, the drive control of the motors ML and MR is performed so that the left and right rear wheels 1RL and 1RR have the same rotation speed. There are two types, drive (drive assist) and reverse drive (braking). In this integration mode,
The clutch 12 is engaged (the switching valve VVJ opens the line 62 and closes the line 63), and the switching valve VVB · L (V
VB · R), VVE · L (VVE · R) and VVI are in the state shown in FIG. In this state, the switching valve VVA is controlled to switch the hydraulic pressure supply direction according to the forward drive or the reverse drive (setting the forward and reverse directions of the motors ML and MR) and to control the motors ML and MR. The supply flow rate is controlled (hydraulic supply using the first supply line 31A).
In the reverse drive, a larger deceleration is obtained than in the hydraulic lock mode described later. However, it is natural that the rear wheels 1RL and 1RR rotate in a direction opposite to the traveling direction of the vehicle. It does not provide any driving force.

(2) Independent mode As described later in detail, the independent mode is such that the left and right rear wheels 1RL and 1RR have respective target rotational speeds set independently of each other. , MR drive control, and there are two types of forward drive and reverse drive as in the case of the integrated mode. In this independent mode, the clutch 12 is released (the switching valve VVJ closes the line 62 and opens the line 63). Switching valve VVE-L (VVE-R)
Is operated as shown in FIG. 1, but the switching valve VVA
Is set to the center switching position and the first supply line 31A is shut off. The switching valve VVI is set to the open position, and the hydraulic pressure is supplied using the second supply line 31B. In this state,
By controlling the switching valve VVB · L (VVB · R), switching of the hydraulic pressure supply direction according to forward drive or reverse drive (motor M
L, MR forward and reverse directions) and motors ML, M
The supply flow rate for R is controlled.

(3) LSD mode The LSD mode obtains an operation limiting function.
VB · L and VVB · R are connected to lines 20L and 21L (2
0R, 21R) are both closed to completely shut off the supply and discharge of hydraulic pressure to the motors ML, MR. And
The on-off valve VVD is opened, and the closed left and right hydraulic paths of the motors ML and MR communicate with each other to form the left and right motors.
This prevents a large rotation difference between the data ML and MR. In this LSD mode, the variable orifice VV
C · L (VVC · R) is fully closed

(4) Hydraulic lock mode The hydraulic lock mode has a passage resistance, that is, a variable orifice V
A deceleration force using the throttle resistance of VC · L (VVC · R) is obtained. In this hydraulic lock mode, the switching valve V
VB · L and VVB · R are in the center switching position, the lines 20L, 21L, 20R and 21R are shut off, and the on-off valve VVD is closed. And the variable orifice V
VC · L and VVC · R are opened. In this state, the oil liquid is circulated through the closed hydraulic circuit including the variable orifice VVC · L (VVC · R) according to the rotation of the motor ML (MR). Is a variable orifice VVC · L (VVC · R) through which the oil liquid passes during circulation.
The throttle resistance gives a deceleration force to the vehicle. The degree of opening of the variable orifices VVC · L and VVC · R is controlled to decrease as the deceleration of the vehicle increases (variable orifices VVC · L, V corresponding to the deceleration).
The setting of the VC / R opening is exemplified in step E37 in FIG. 4). Note that the clutch 12 may be in either the engaged state or the released state.

(5) Accumulation mode The accumulation mode is used when the vehicle, that is, the rear wheels 1RL, 1R
The motors ML and MR driven by R function as pumps to accumulate pressure in the accumulator 41. In this pressure accumulation mode, the line 21L (21R) communicates with the reservoir tank 16 while the on-off valve VVF · L
When (VVF.R) is opened, the oil liquid in the reservoir tank 16 is pumped up by the motor ML (MR) and accumulated in the accumulator 41.

The pump P driven by the engine 2 has:
When the accumulator 41 is in the above-mentioned predetermined pressure range, its discharge capacity is zero or extremely small, and its driving resistance is extremely small. In addition to this, if the accumulator 41 is sufficiently accumulated,
As the de-unload valve VVH is opened, the drive resistance is reduced to a virtually nonexistent level. In other words,
In a time range in which the motors ML and MR are temporarily driven during acceleration or the like, the motor is driven only by using the hydraulic pressure accumulated in the accumulator 41, and the torque generated by the engine 2 is obtained. Are all front wheels 1FL, 1
Used for driving the FR (a driving state in which the motor driving force is added to the torque generated by the engine 2). When the vehicle travels on a snowy road or the like for a long time using the motor drive, the motor drive uses the hydraulic pressure from the pump P driven by the engine 2 (the torque generated by the engine is reduced by 4).
Driving state distributed to the two wheels 1FL to 1RR).

(6) Stopping mode In the stopping mode, the motors ML and MR stop the vehicle when the parking brake is not operating.
(The driving of the motors ML and MR is controlled so that the vehicle speed becomes the target vehicle speed 0). In this case, the hydraulic pressure supply line uses the second supply line 31B, and the supply / discharge control of the hydraulic pressure is performed by the switching valve VVB · L (VVB · L).
R).

(7) Parking Mode The parking mode enhances the operation of maintaining the parking state when the parking brake is activated. That is, in the parking mode, the switching valve VVB · L
(VVB · R) is set to the closed position of the center switching position, the hydraulic supply / discharge line is cut off, and the clutch 12 is engaged.

(8) F / S mode The F / S mode is a fail-safe mode. When there is any abnormality, for example, when the high-pressure line becomes abnormally high, the mode is changed. -When the valves ML and MR are not driven normally, when a certain valve is stuck, or when the oil temperature becomes higher than a predetermined temperature, and the like, the safety valve VVG is opened, The oil pressure in the high pressure line 18 is released.

Description of Control System (FIG. 2) FIG. 2 shows a control system in the present invention. In the figure, U1, U2 and U3 are control units each constructed using a microcomputer.
Is a main control unit that controls the above-described valves VVA and the like. The control unit U2 is for ABS control (anti-lock brake control), and the control unit U3
Is for traction control. Also, S1 to S14 are
Each is a sensor or a switch.

The sensors S1 to S4 are provided for each wheel 1FL to 1R.
The rotation speed of R, that is, the wheel speed is detected independently, and the wheel speed detected by each of the sensors S1 to S4 is transmitted from the control unit U2 to the control units U1 and U3. The sensor S5 detects the vehicle speed. In the embodiment, the sensor S5 detects the ground vehicle speed (detection of the absolute vehicle speed). The sensor S6 detects a shift position of the transmission 4, that is, a gear position. The sensor S7 detects the engine speed. The sensor S8 detects the steering angle of the steering wheel. The sensor S9 detects the accelerator opening. The sensor S10 detects the depression amount of the brake pedal. The switch S11 is an ignition switch. The switch S12 detects whether the parking brake has been activated.

The sensor S13 detects a rough road (uneven road). The rough road is detected, for example, assuming that the sensor S13 detects a vertical stroke of the suspension.
The control unit U1 determines that a stroke that is equal to or greater than a predetermined amount occurs a predetermined number of times or more within a predetermined time as a bad road. Further, the sensor S14 detects the vertical G (acceleration) acting on the vehicle body, and the control unit U determines that the road is rough when the vertical S occurs more than a predetermined number of times within a predetermined time.
1 may be determined. It should be noted that the determination of the degree of the rough road may be made by changing one or more of the thresholds for the above-described rough road determination.

The signals from the sensors or the switches S5 to S14 are input to the control unit U1, and the control unit U1 controls the above-described valves VVA to VVJ. Of course, the control unit U2 is for preventing the wheels from locking during braking, and the control unit U2 provides a brake hydraulic pressure for independently adjusting the braking of each wheel. The adjusting unit 81 is controlled. Further, the control unit U3 includes left and right front wheels 1F which are always driven when acceleration or the like.
When the slip on the road surface of L, 1FR becomes excessive, at least the engine output (torque generated by the engine 2) is reduced. For example, the opening degree of the throttle valve of the engine 2, the ignition timing, the fuel injection amount, etc. The adjusting torque adjusting means 82 is controlled.

From the control unit U2 to the control unit U1, in addition to the wheel speed signals detected by the sensors S1 to S4, A
An ABS signal indicating that the BS control is being executed and a μ signal indicating the road μ (friction coefficient) are transmitted. Further, a wheel speed signal is transmitted from the control unit U2 to the control unit U3. Further, the control unit U3 sends to the control unit U1 a T indicating that the traction control is being executed.
In addition to the RC signal, a torque reduction signal indicating the amount of reduction in engine torque performed by the traction control and a road surface μ signal are transmitted. The detection of the road surface μ can also be performed by the control unit U1, and the sensors S1 to S1
Each wheel speed detected in S4 may be directly input to the control unit U1.

Description of the flowchart (FIG. 3) Next, the control contents of the control unit U1 will be described with reference to the flowcharts of FIG. In the following description, D, E, W, and Z indicate steps, respectively. First, in the main flowchart of FIG. 3, after a signal from each sensor or the like is input at D0, it is determined at D1 whether or not the ignition switch is OFF. If the determination in D1 is NO, in D2, it is determined whether or not the ignition switch is ON. If the determination in D2 is NO, D3
In, the safety valve VVG is opened, and the pressure in the high-pressure line 18 is released. Also, in the determination of D2, Y
In the case of ES, at D4, the safety valve VVG is closed, and the high-pressure oil is supplied to the high-pressure line 18.

At D5, it is determined whether or not the vehicle speed (ground vehicle speed) is substantially zero. If the determination in D5 is YES, it is determined in D6 whether the gear position of the transmission 4 is neutral. YE in D6 discrimination
In the case of S, it is determined in D7 whether or not the packing brake is activated. If the determination in D7 is YES, in D8, the control of the parking mode is executed. If the determination in D7 is NO, in D9, the control of the stop mode is executed.

If the determination in D5 is NO and the determination in D6 is NO, the transmission 4
It is determined whether or not the gear position is the reverse position. D1
If the determination of 0 is NO, in D11, it is determined whether or not the vehicle is currently in the stack. The determination as to whether or not the vehicle is a stack is made, for example, when the accelerator is depressed, the vehicle speed is almost 0, and the rotational speeds of the left and right front wheels 1FL and 1FR are sufficiently higher than the vehicle speed. Can be determined. If the determination in D11 is NO, in D12, it is determined whether or not to execute a control mode other than the parking mode and the stop mode, as described later.

If the determination in D10 is YES, D
At 15, driving assistance using the motors ML and MR is executed. In this case, normal driving is performed in the independent mode (the rear wheels 1 RL and 1 RR are driven in the reverse direction). If the determination in D11 is YES, in D14,
Driving assistance using the motors ML and MR is executed.
In this case, a forward drive is performed in an independent mode described later in which the target vehicle speed is set to a low vehicle speed (for example, about 10 km / h, which is a stack release condition).

If the determination in D1 is YES, D16
After the clutch 16 has been engaged in D1, the clutch engagement is maintained in D17 (the switching valve VVL is
2 and 63 are both closed.) Then, at D18,
The safety valve VVG is opened.

Description of the flowchart (FIGS. 4 to 9) Details of D12 in FIG. 3 are shown in the flowcharts of FIGS. First, at E23 in FIG.
It is determined whether the traction control is being performed by the control unit U3. When the determination in E23 is NO,
At E24, it is determined whether the vehicle is currently traveling on a rough road. If the determination in E24 is NO, it is determined in E25 whether or not the road surface is low μ. If the determination in E25 is NO, it is determined in E26 whether the vehicle is currently traveling straight. In this embodiment, whether or not the vehicle is going straight is determined based on the steering angle and the vehicle speed.
Is calculated, and when the lateral G is equal to or less than a predetermined value, it is determined that the vehicle is traveling straight.

If the determination in E26 is YES, E27-
The processing of E39 is performed.
It is assumed that the vehicle is traveling on a road and going straight. Finally, the forward drive (E28) and the reverse drive (E28) in the integrated mode
35) It is determined whether control conditions for performing the pressure accumulation mode (E33, E39) or the hydraulic lock mode (E31, E37) are satisfied.

The degree of acceleration and the degree of deceleration can be determined by various known methods. For example, the degree of acceleration
It can be known from any one or a combination of any two or more of the accelerator pedal depression speed, the accelerator pedal depression amount increase amount, and the vehicle body acceleration obtained by differentiating the vehicle speed. The degree of deceleration is, for example, any one of a magnitude of an accelerator release speed, a magnitude of a brake depression speed, an increase in a brake depression amount, a vehicle deceleration obtained by differentiating a vehicle speed, and the like. Alternatively, it can be known by arbitrary plural combinations. However, in the embodiment, at least when the accelerator return speed is high (when the accelerator release speed is high), it is determined that the deceleration is equal to or more than the slow deceleration for setting the hydraulic lock mode.

If the determination at E26 in FIG. 4 is NO,
FIG. 5 is based on the assumption that the vehicle is turning on a good road and a high μ road. Finally, it is determined whether the control conditions for performing the forward drive (E42) and the reverse drive (E44) or the LSD mode (E45) in the independent mode are satisfied.

When the determination at E25 in FIG. 3 is YES, the processing shown in FIG. 6 is performed. In FIG. 6, first, E
At 51, it is determined whether or not the vehicle is traveling straight. If the determination in E51 is YES, the processing of E52 to E59 is performed, but this processing is performed on the assumption that the vehicle is traveling on a good road, a low μ road, and straight ahead. Finally, it is determined whether or not the control conditions for performing the forward drive (E55) and the reverse drive (E57), the hydraulic lock mode (E54), and the LSD mode (E59) in the independent mode are satisfied. Is determined.

If the determination at E51 in FIG. 6 is NO, the processing shown in FIG. 7 is performed, but this processing is performed on a good road, a low μ road, and when turning. Finally, it is determined whether the control conditions for performing the normal drive (E62), the hydraulic lock mode (E65), and the LSD mode (E66) in the independent mode are satisfied.

If NO in the determination of E24 in FIG.
In E71, it is determined whether or not the road is extremely bad.
If the determination in E71 is NO, E72 to E8
6 is performed, which is performed by the control mode on a rough road.
C. If the determination in E71 is YES, the processing after E91 in FIG. 9 is performed, but this is the determination of the control mode on an extremely rough road.

Description of the flowchart (FIG. 10) FIG. 10 shows details of the positive drive control in the independent mode. The positive drive control in the integrated mode is different only in that the same target vehicle speed is given to the left and right rear wheels.
This is performed in substantially the same manner as the normal drive control in the mode. First, after data is input at Z1, a target vehicle speed VTR is set at Z2 using the accelerator opening and the shift position of the transmission 4 as parameters.

Next, at Z3, it is determined whether or not a value obtained by subtracting the actual wheel speed VBL of the left rear wheel 1RL from the target vehicle speed VTR is higher than a predetermined speed V1. When the determination in Z3 is NO, it is determined that the drive assist by the forward drive is not necessary, and the forward drive of the left rear wheel is stopped in Z13. The processing of Z3 and Z13 is performed for the right rear wheel 1RR independently of the left rear wheel 1RL. The predetermined speed V1 is set to a speed indicating a slip amount sufficient for acceleration, but may be a constant value or a variable value that increases as the vehicle speed VA increases. If the determination in Z3 is YES, it is determined whether or not the accelerator is fully closed in Z4. If the determination in Z4 is YES, the motor M
It is determined that driving assistance using L and MR is not necessary, and the process proceeds to Z13 (in this case, the left and right rear wheels 1R
L and 1RR are stopped at the same time.

If the determination in Z4 is NO, in Z5, the lateral G acting on the vehicle body is calculated based on the vehicle speed VA and the steering angle. Thereafter, in Z6, the correction coefficients k1 and k2 are set. Then, in Z7, it is determined whether or not the vehicle is turning right. If the determination in Z7 is YES, in Z9, the left rear wheel 1RL
Is the target vehicle speed VTR determined by Z2.
TR is calculated by multiplying TR by a correction coefficient k1, and similarly, target wheel speed VTRR of right rear wheel 1RR is calculated by multiplying target vehicle speed VTR by correction coefficient k2.

If NO in Z7, the target wheel speeds of the left and right rear wheels 1RL and 1RR are calculated in Z8. In short, the processing of Z6 to Z9 corresponds to the processing of increasing the target wheel speed on the turning outer wheel side and decreasing the target wheel speed on the turning inner wheel side. However, when the vehicle is going straight, the determination of Z7 is NO and the process proceeds to Z8. At this time, since the correction coefficient is 1, the horizontal G is 0 or almost 0.
), The target wheel speeds of the left and right rear wheels 1RL, 1RR are equal to each other).

After Z8 or Z9, at Z10, the target wheel speed VTRL (VTRR) is changed from the rear wheel 1RL.
(1RR) The amount of oil liquid Q supplied to the motor ML (MR) according to the value obtained by subtracting the actual wheel speed VBL (VBR).
Is determined. This oil liquid amount Q is determined by the left and right motors ML, M
R is determined independently of each other. Then, in Z11, the switching valves VVB · L and VVB · R are individually controlled so as to realize the determined oil liquid amount Q.

At Z12, it is determined whether or not a value obtained by subtracting the actual wheel speed VBL of the left rear wheel 1RL from the vehicle speed VA is smaller than a predetermined speed "-V2". This Z
In the end, the determination of 12 is to determine whether or not the actual wheel speed VBL of the left rear wheel 1RL is too high compared to the vehicle speed VA. If the determination of Z12 is YES, Z1
In 3, so that the rear wheel maintains a predetermined slip value,
Correction for reducing the supply flow rate Q is performed. Note that Z1
2, the processing of Z13 is similarly performed for the right rear wheel 1RR. If the determination in Z12 is NO, Z13
Is returned without going through.

In the positive drive control in the integrated mode, Z
5 to Z9 become unnecessary, and the target vehicle speed VTR determined in Z2 becomes the target wheel speed VT of the left and right rear wheels 1RL, 1RR.
RL and VTRR. In addition, a switching valve VVA is used to realize the flow rate Q at Z11.

Description of the flowchart (FIG. 11) FIG. 11 shows details of the reverse drive in the independent mode. In addition,
The positive drive control in the integrated mode is the same as the positive drive control in the independent mode except that the switching valve used for flow rate adjustment is different from the switching valve used in the independent mode. Done. First, after data is input at Z21, it is determined at Z22 whether or not the reverse drive flag is 1. When the determination of Z22 is NO,
In Z30, the steering angle and the vehicle speed VA are parameters.
A confirmation is made as to where the current state is in the area set as the data. Thereafter, in Z31, it is determined whether or not the current state is in the hatched C area in the area shown in Z30. If the determination in Z31 is YES, the reverse drive flag is set to 1 in Z32, and the process returns to Z21. If the determination in Z31 is NO, Z
Return to Z21 without going through 32.

After passing through Z32, the determination of Z22 is YE
At this time, it is determined in Z23 whether or not the ABS control is currently being performed. In the determination of Z23, N
In the case of O, it is determined in Z24 whether or not the brake depression amount is large. NO in this determination of Z25
, The vehicle speed VA is increased to a predetermined value V at Z25.
It is determined whether or not the vehicle speed is 3 or less.

If the determination in Z25 is NO, Z2
At 6, the supply flow rate Q to the motors ML and MR is determined using the vehicle speed VA and the shift position of the transmission 4 as parameters. Thereafter, in Z27, the switching valves VVB · L and VVB · R are controlled such that the flow rate Q determined in Z26 is supplied to the left and right motors ML and MR. Z2
After step 7, the processing of Z28 and Z29 is performed. This processing corresponds to the processing of Z12 and Z13 in FIG. 9 and is a processing for correcting that the reverse driving force becomes too large.

If the determination in any of Z23, Z24 and Z25 is YES, the reverse drive control is stopped in Z33, and then the reverse drive flag is reset to 0 in Z34. The reverse drive control in the integrated mode is based on Z26.
VVA is used as a switching valve for realizing the flow rate Q determined in the above.

FIG. 12 is a flow chart of the operation performed when the traction control is being performed by the control unit U3. This is control of drive assistance (right and left independent positive drive) using MR.
First, after data is input in Z41, the amount of decrease in the torque applied to the front wheels 1FL and 1FR caused by the traction control of the control unit U3, that is, the amount TF of decrease in the torque generated in the engine 2 is controlled in Z42. It is read based on a signal from the unit U3. After this, Z4
In 3, the vehicle speed reduction amount VC according to the torque reduction amount TF is determined.

In Z44, the supply flow rate Q to be supplied to the motors ML and MR is determined according to the vehicle speed reduction amount VC.
The supply flow rate Q is determined so that the total generated torque of the motors ML and MR is equal to the generated torque reduction amount of the engine 2. Thereafter, in Z45, it is determined whether or not the traction control has been stopped. If the determination in Z45 is NO, the processing in Z46 to Z52 is performed. The processing of Z46 to Z52 is performed by correcting the correction coefficients F1 and F2.
, The supply flow rate QTRL, QTR for the left and right rear wheels
R, that is, the torque distribution ratio is determined. More specifically, during turning, the torque distribution amount to the turning outer wheel side is made larger than the torque distribution amount to the turning inner wheel side (Z49,
Z51), the torque distribution ratio to the left and right rear wheels is made equal when traveling straight (Z52).

In FIG. 49, after Z51 or Z52,
The processing after Z53 is performed, but since this processing corresponds to Z11 to Z13 in FIG. 9, the duplicated description is omitted.

Description of the flowchart (FIG. 13) FIG. 13 shows the control contents of the stop mode in D9 of FIG. First, after data is input at Z61, it is determined at Z62 whether or not the accelerator is depressed. When the determination of Z62 is NO, Z
At 63, after the target vehicle speed VTR is set to 0,
In Z64, the supply flow rates to the motors ML and MR are adjusted so that the actual wheel speed VBL or VBR of the left and right rear wheels 1RL and 1RR becomes the target vehicle speed VTR, respectively.
It is controlled back (left and right independent control).

When the transmission 4 is an automatic transmission (in this case, the clutch 3 is a torque converter), even if the accelerator is not depressed, as is called a creep. Traveling at extremely low speeds is performed. To obtain this creep, the target vehicle speed V
If TR is set to, for example, 5 km / h, the creep speed can always be kept constant irrespective of the inclination of the road surface during stopping. The target vehicle speed VTR can be selected continuously or continuously in a range of 0 to 15 km / h, for example, manually (no creep when the target vehicle speed is 0).

Although the embodiment has been described above, the present invention is not limited to this, and includes, for example, the following case. (1) A manual switch may be provided to select whether or not to execute rear wheel drive assist (forward drive, reverse drive) using a motor. The accumulator 41
Alternatively, only the temporary motor drive using only the accumulated pressure may be selected. (2) When only a temporary motor drive using only the accumulated pressure of the accumulator 41 is performed, the pump P driven by the engine 2 may be unnecessary (in this case, the motor is used). An accumulator circuit using ML and MR as accumulator pumps is necessary). (3) It is not necessary to separately provide a pressure accumulating circuit constituted by the pressure accumulating lines 42L and 42R (in this case, a pump P driven by the engine 2 is required). (4) The left and right rear wheels 1RL and 1RR may be driven by the engine 2, and the left and right front wheels 1FL and 1FR may be driven by the motors ML and MR. (5) The motors may not be provided independently for the left and right, but may be provided for only one common to the left and right (a differential device is provided for performing auxiliary driving by the motor during turning). (6) For example, in order to sufficiently satisfy the acceleration performance using the motor drive while performing the motor drive for a long time in the steady running on the low μ road, the accumulator 41 always has the acceleration hydraulic pressure left. The drive of the pump P may be performed while the pump P is being driven. Particularly, the drive of the pump P is stopped during acceleration (opening of the valve VVF, drastic reduction of the discharge capacity of the pump P, and further between the engine 2 and the pump P) Disconnection of the electromagnetic clutch).

[Brief description of the drawings]

FIG. 1 is a diagram showing an example of a hydraulic system used in the present invention.

FIG. 2 is a diagram illustrating an example of a control system.

FIG. 3 is a flowchart showing a control example of the present invention.

FIG. 4 is a flowchart showing a control example of the present invention.

FIG. 5 is a flowchart showing a control example of the present invention.

FIG. 6 is a flowchart showing a control example of the present invention.

FIG. 7 is a flowchart showing a control example of the present invention.

FIG. 8 is a flowchart showing a control example of the present invention.

FIG. 9 is a flowchart showing a control example of the present invention.

FIG. 10 is a flowchart showing a control example of the present invention.

FIG. 11 is a flowchart showing a control example of the present invention.

FIG. 12 is a flowchart showing a control example of the present invention.

FIG. 13 is a flowchart showing a control example of the present invention.

[Explanation of symbols]

 U1: Control unit (for motor control) U2: Control unit (for ABS control) U3: Control unit (for traction control) P: Pump ML, MR: Motor 1FL, 1FR: Front wheel 1RL, 1RR: Rear wheel 2: Engine 4: Transmission 5: Differential device 19, 32: Hydraulic supply line 42L, 42R: Accumulation line 43L, 43R: Check valve VVF (L, R): Open / close valve (for opening / closing the accumulation line)

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-2-12036 (JP, A) JP-A 63-147321 (JP, U) JP-A 63-145720 (JP, U) JP-A 63-147720 35621 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) B60K 17/28-17/36 B60K 25/00 B60K 25/04 F16H 61/40

Claims (7)

(57) [Claims] 1. One of right and left front wheels and right and left rear wheels is a main drive wheel driven by an engine via a transmission and a differential device, and the other wheel is a hydraulic motor. In a vehicle which is driven as an auxiliary driving wheel, a reservoir tank for storing oil, an accumulator for accumulating hydraulic pressure, and an accumulator which pumps up the oil in the reservoir tank A pump for accumulating pressure in the accumulator, a supply circuit for supplying hydraulic pressure accumulated in the accumulator to the motor, and a supply circuit for bypassing the supply circuit.
When the motor is rotated by the auxiliary drive wheels,
The reservoir tank by causing the reservoir to function as the pump.
Pressure accumulator for supplying the oil liquid in the accumulator
A passage, an opening / closing means for opening / closing the pressure accumulation circuit, and opening / closing the opening / closing valve when predetermined pressure accumulation conditions are satisfied.
Then, the motor is made to function as a pump to
Pressure accumulation control means for causing the motor to accumulate pressure , the motor comprising: a left motor for driving a left auxiliary drive wheel;
And a right motor for driving the right auxiliary drive wheel.
Wherein the pressure accumulating circuit is configured so that at least
So that there is a parallel relationship between them
The left and right motors are formed independently of each other,
The accumulator is connected to both the left and right accumulator circuits.
And the accumulator and the motor of the left and right accumulator circuits.
Between the accumulator and the motor
A drive device for a vehicle , further comprising a check valve connected to prevent the occurrence of the vehicle. 2. The method of claim 1, as the pump comprises a pump driven by the engine, that drives the vehicle to feature a. 3. The vehicle drive device according to claim 1, wherein the predetermined pressure accumulation condition is set as a time of deceleration of the vehicle . 4. The method of claim 1 or claim 2, wherein the predetermined accumulator condition has been steady operation sometimes setting of the vehicle, the driving apparatus for a vehicle, characterized in that. 5. A method according to claim 1 or claim 2, wherein the predetermined pressure accumulation condition is fast sometimes set the vehicle,
During low speed vehicle accumulator is inhibited, characterized in that
Vehicle drive device . 6. The method according to claim 1 or claim 2, wherein the predetermined pressure accumulation condition is sudden deceleration sometimes setting of the vehicle, during slow deceleration of the vehicle accumulator is inhibited, characterized in that
Vehicle drive device . 7. The method of claim 1 or claim 2, wherein the predetermined pressure accumulation condition is straight sometimes set the vehicle,
It is prohibited when turning the vehicle.
Drive .