JP2000006786A - Brake hydraulic control device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the operating noise during ABS control, to reduce power consumption and to prevent the occurrence of a kickback by preventing reservoirs from being filled with a brake fluid, and continuing the ABS control over a long time. SOLUTION: In this brake hydraulic control device for a vehicle, the decompression, retention and boost of wheel brakes BFL, BFR are repeated during the ABS control of the wheel brake BFL for the left front wheel and the wheel brake BFR for the right front wheel. When the friction coefficient of the travel road surface is low during boost, the brake fluid in first and second reservoirs 7A, 7B is pumped up by first and second pumps 8A, 8B. Both reservoirs 7A, 7B are prevented from being filled with the brake fluid during a travel on the road surface having a low friction coefficient in particular, and the ABS control can be continued over a long time. ABS operating noise and power consumption are reduced, and the occurrence of a kickback can be prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a brake fluid pressure control device for a vehicle, and more particularly to a master cylinder, a reservoir for storing brake fluid, and a communication between the master cylinder and the wheel brake, but between the wheel brake and the reservoir. Control valve means capable of switching between a state of shutting off, a state of shutting off between the master cylinder and the wheel brake but communicating between the wheel brake and the reservoir, and a state of shutting off both the master cylinder and the reservoir and the wheel brake. The present invention relates to a vehicle brake fluid pressure control device provided.

[0002]

2. Description of the Related Art Conventionally, such an apparatus is disclosed in, for example,
These are already known from Japanese Patent Application Publication No. 254760 and Japanese Patent Application Laid-Open No. 9-216548.

[0003]

The vehicle brake fluid pressure control device disclosed in Japanese Patent Application Laid-Open No. 9-254760 is a so-called recirculation type antilock brake control device, in which a brake pumped from a reservoir is used. A pump is provided to recirculate the liquid between the master cylinder and the control valve means. Therefore, during anti-lock brake control (hereinafter referred to as ABS control), the operation of the pump is continued, the brake fluid in the reservoir is returned to the master cylinder side by the pump, and the pump is driven to the output hydraulic pressure of the master cylinder. It is necessary to discharge the brake fluid with the pressure to win. Therefore, the size of the pump and the size of the actuator for driving the pump are increased. In addition, since the pump continues to operate during the ABS control, the operation sound of the pump continues to be generated while the ABS continues, the power consumption increases, and the kickback to the brake pedal increases, which makes the driver feel uncomfortable. You may feel

The vehicle brake fluid pressure control device disclosed in Japanese Patent Application Laid-Open No. 9-216548 does not include a pump for returning to the master cylinder side.
The brake fluid is stored in the reservoir due to the pressure reduction of the wheel brake during the BS control. However, if the reservoir is filled with the brake fluid, the pressure reduction control of the wheel brake cannot be continued. Therefore, it is difficult to continue the ABS control for a long time even if it is necessary to continue the ABS control for a relatively long time when traveling on a road surface having a particularly low friction coefficient.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and enables the ABS control to be continued for a long time, to reduce the operation noise and the power consumption during the ABS control, and to prevent the occurrence of kickback. It is another object of the present invention to provide a brake fluid pressure control device for a vehicle in which a pump and an actuator for driving the pump can be miniaturized.

[0006]

In order to achieve the above object, the invention according to claim 1 comprises a master cylinder; a reservoir for storing brake fluid; and a communication between the master cylinder and the wheel brake. Control valve means capable of switching between a state in which the reservoir is shut off, a state in which the master cylinder and the wheel brake are disconnected but the wheel brake and the reservoir are in communication, and a state in which the master cylinder and the reservoir and the wheel brake are both shut off. A control unit for controlling the operation of the control valve means to control the brake hydraulic pressure of the wheel brakes. A control apparatus for a vehicle brake hydraulic pressure comprising: The discharge port of the pump that pumps up the stored brake fluid is Characterized in that it is connected for preventing the flow of the brake fluid to the.

According to such a configuration, at the time of normal brake operation, the control valve means communicates between the master cylinder and the wheel brake, but shuts off between the wheel brake and the reservoir and applies the brake pressure from the master cylinder to the wheel brake. When the ABS control is depressurized, the master valve and the wheel brake are shut off by the control valve means, but the brake pressure of the wheel brake is released to the reservoir by communicating between the wheel brake and the reservoir to release the brake fluid pressure of the wheel brake. When the brake pressure is reduced and the ABS control brake pressure is maintained, the master cylinder and the reservoir and the wheel brake are both shut off by the control valve means to maintain the wheel brake brake pressure.
By operating the pump in a state in which both the master cylinder and the reservoir and the wheel brake are shut off by the control valve means, the brake fluid pressure from the brake fluid pumped from the reservoir is applied to the wheel brake, and the brake fluid pressure of the wheel brake is reduced. Pressure can be increased. Further, at the time of rapid pressure increase in the ABS control, the control valve means communicates between the master cylinder and the wheel brake, but the wheel brake and the reservoir may be shut off to apply the brake pressure from the master cylinder to the wheel brake. In this case, by setting the discharge pressure of the pump to be lower than the output hydraulic pressure of the master cylinder, the discharge pressure of the pump does not act on the master cylinder side. Therefore, during ABS control, the pressure reduction, holding and pressure increase of the wheel brakes are repeated, so that the brake fluid in the reservoir is pumped up by the pump. Is not filled with the brake fluid, and the ABS control can be continued for a long time. Further, since the pump does not need to discharge a hydraulic pressure that overcomes the output hydraulic pressure of the master cylinder, the size and weight of the pump can be reduced, and the size and weight of the actuator for driving the pump can be reduced. . Further, the pump only needs to be operated when the brake fluid pressure of the wheel brake is increased, so that the ABS operation noise can be reduced and the power consumption can be reduced. Moreover, since the control valve means cuts off between the master cylinder and the wheel brakes when the pump is operating, the discharge pressure of the pump does not act on the master cylinder side, so that kickback does not occur,
The driver does not feel discomfort due to kickback.

[0008] The invention according to claim 2 provides the above-mentioned claim 1.
In addition to the configuration of the invention described, the control unit can determine the level of the friction coefficient of the road surface, and when the friction coefficient is low at the time of brake fluid pressure increase of the wheel brake in the anti-lock brake control state. When it is determined, the pump is operated to increase the pressure with the output pressure of the pump. When it is determined that the coefficient of friction is high, the operation of the pump is stopped and the pressure is increased by the output hydraulic pressure of the master cylinder. Controlling the operation of the means and the pump.

With this configuration, the ABS control can be continued for a long time while saving energy consumption. That is, in a state where the friction coefficient of the road surface is low and a state where the friction coefficient is high, the decompression time, the decompression amount,
The time until the end of the S control and the number of times of pressure reduction are different, and both are longer and more on a road surface having a lower friction coefficient. Therefore, when the pressure is increased in the ABS control on a road surface with a low friction coefficient, the pump is operated to return the brake fluid to the wheel brake side, so that the duration of the ABS control can be secured. Can be stopped to save energy consumption.

According to a third aspect of the present invention, in addition to the configuration of the first or second aspect, the reservoir and the pump are provided for each of a plurality of different combinations of the wheel brake and the control valve means. According to this configuration, each pump can operate independently of each other. According to such a configuration, the operation and operation of each pump are controlled according to the brake fluid pressure control state of the wheel brakes corresponding to each pump. By controlling the stop individually, or by varying the drive time of each pump, more precise brake pressure control can be performed, and energy consumption can be reduced and pump operation noise can be reduced.

According to a fourth aspect of the present invention, in addition to the configuration of the first aspect of the present invention, one wheel brake for a front wheel and one wheel brake for a rear wheel respectively mounted on a pair of front and rear wheels are provided. The reservoir includes the reservoir and the pump, and the discharge port of the pump is any one of between a wheel brake for a front wheel and the control valve means for a front wheel and between the wheel brake for a rear wheel and the control valve means for a rear wheel. According to this configuration, the pressure is increased by the discharge pressure of the pump during the ABS control on the wheel brake side to which the pump is connected, and the master cylinder is increased during the ABS control on the wheel brake side to which the pump is not connected. By increasing the pressure by the output hydraulic pressure, the size and weight of the pump and the actuator can be further reduced.

According to a fifth aspect of the present invention, in addition to the configuration of the fourth aspect of the present invention, a discharge port of the pump is connected between a wheel brake for a front wheel and the control valve means for a front wheel. According to such a configuration, according to this configuration, the brake fluid pressure of the rear wheel brake, which is the side where the amount of liquid consumption is small, is increased by the output hydraulic pressure of the master cylinder, and the pressure for the front wheel which is the side where the amount of liquid consumption is large is increased. By increasing the brake fluid pressure of the wheel brake by the discharge pressure of the pump, the efficiency of the ABS control can be increased.

According to a sixth aspect of the present invention, in addition to the configuration of the fourth or fifth aspect, a discharge port of the pump is a wheel brake for a wheel which is a driving wheel among a front wheel and a rear wheel; The control valve means, which is connected between the control valve means corresponding to the drive wheel and the front wheel and the rear wheel, and which corresponds to a driven wheel, comprises a master cylinder and a reservoir and a wheel brake for the driven wheel. It is characterized in that it is configured to be able to communicate between them.

According to such a configuration, when the brake is not operated, the pump is operated in a state in which both the master cylinder and the reservoir and the wheel brakes of the drive wheels are shut off by the control valve means for the drive wheels. By applying the brake fluid pressure by the pumped brake fluid to the wheel brakes for the drive wheels, the wheel brakes of the drive wheels are operated, and traction control can be performed by reducing the drive force of the drive wheels. At this time, by controlling the master cylinder and the reservoir together with the wheel brake for the driven wheel by the control valve means for the driven wheel,
The suction port of the pump is communicated with the master cylinder, and the brake fluid from the inactive master cylinder can be sucked by the pump and supplied to the wheel brakes for the drive wheels, and the brake fluid is constantly stored in the reservoir. You don't have to. In addition, traction control can be executed only by changing the control of the pump and the control valve means from the time of the ABS control, without the necessity of providing means dedicated to traction control.

According to a seventh aspect of the present invention, in addition to the configuration of the first aspect of the present invention, in the pump, a plunger having one end facing the pump chamber is slidable in the pump housing. The reciprocating actuator is coaxially connected to the plunger. According to this configuration, the connection structure between the pump and the actuator is simplified, and the operation efficiency of the pump and the actuator is improved. be able to.

According to an eighth aspect of the present invention, in addition to the configuration of the seventh aspect, the actuator is coaxially connected to the fixed core and the plunger so as to be able to approach and separate from the fixed core. It is characterized by being a solenoid having a movable core, and according to such a configuration,
The actuator can have a simpler configuration and cost can be reduced.

[0017]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiments of the present invention will be described below based on one embodiment of the present invention shown in the accompanying drawings.

1 to 8 show one embodiment of the present invention. FIG. 1 is a hydraulic circuit diagram of a vehicle brake hydraulic pressure control device, FIG. 2 is a vertical sectional view of a pump and an actuator, and FIG. FIG. 4 is a block diagram showing a control system of each control valve means and each pump, FIG. 4 is a flowchart showing a control procedure at the time of pressure increase in the ABS control state, and FIG. 5 corresponds to FIG. 1 showing a pressure decrease state in the ABS control. Hydraulic circuit diagram, Fig. 6 is AB
FIG. 7 shows a hydraulic circuit diagram corresponding to FIG. 1 showing a hydraulic pressure holding state in S control, FIG. 7 shows a hydraulic circuit diagram corresponding to FIG. 1 showing a pressure increasing state in ABS control, and FIG. 8 shows a traction control state. FIG.
FIG. 3 is a hydraulic circuit diagram corresponding to FIG.

Referring first to FIG. 1, the brake fluid pressure control device is mounted on a front-wheel drive four-wheel vehicle.
A master cylinder M having a reservoir R and configured in a tandem type, and wheel brakes B _FL and B _FR for left and right front wheels mounted on left and right front wheels as drive wheels, respectively.
And left and right rear wheel brakes B _RL , B _RR mounted respectively on the left rear wheel and the right rear wheel that are driven wheels, and a proportional pressure reducing valve 1 for the left rear wheel brake B _{RL. L} is connected, and a proportional pressure reducing valve 1 _R is connected to the wheel brake B _RR for the right rear wheel.
Is connected.

The master cylinder M is provided with a pair of output ports 4A and 4B for outputting a brake fluid pressure corresponding to the depression of the brake pedal 3, and the first and second output fluid passages 5A and 5A are connected to both output ports 4A and 4B. 5B are individually connected. Thus, the first output hydraulic pressure path 5A corresponds to the wheel brakes B _FL and B _RR for the left front wheel and the right rear wheel which are respectively mounted on the front and rear left and right rear wheels, respectively. Yes,
The second output hydraulic pressure passage 5B corresponds to wheel brakes B _FR and B _RL for the right front wheel and the left rear wheel, which are respectively mounted on a pair of front right and left rear wheels.

The first output hydraulic line 5A is connected to the first output hydraulic line 5A.
First check valve 1 that permits the flow of brake fluid to A side
First reservoir 7A for storing brake fluid via 0A
The second output hydraulic passage 5B is connected to a second reservoir 7B that stores the brake fluid via a second check valve 10B that allows the brake fluid to flow to the second output hydraulic passage 5B. Connected to.

First output hydraulic path 5A and first reservoir 7
A control valve means 6 _FL is provided between A and the left front wheel brake B _FL, and is provided between the first output hydraulic pressure path 5A and the first reservoir 7A and the right rear wheel brake B _RR. Is provided with control valve means 6 _RR . The control valve means 6 _FR is provided between the second output hydraulic pressure line 5B and the second wheel brake B _FR for reservoir 7B and right front wheel, the second output hydraulic pressure line 5B and the second reservoir 7B and left Control valve means 6 _RL is provided between the rear wheel brake B _RL .

The discharge port 18 (see FIG. 2) of the first pump 8A, to which the suction port 20 (see FIG. 2) is connected to the first reservoir 7A, is connected between the wheel brake B _FL for the left front wheel and the control valve means 6 _FL. The discharge port of the second pump 8B, which is connected to the left front wheel brake _BFL side by blocking the flow of brake fluid from the side to the first pump 8A side, and the suction port of which is connected to the second reservoir 7B, The brake fluid is connected between the right front wheel brake _BFR and the second pump 8B side between the right front wheel brake _BFR and the control valve means _6FR .

The first and second pumps 8A and 8B have the first
And the second actuators 9A and 9B are individually connected, and both pumps 8A and 8B can operate independently of each other.

The control valve means 6 _FL corresponding to the wheel brake B _FL for the front left wheel is a normally open solenoid valve 11 provided between the first output hydraulic pressure path 5A and the wheel brake B _FL for the front left wheel.
_FL , a wheel brake B _FL for the front left wheel, and a normally closed solenoid valve 13 _FL provided between the first reservoir 7A.

The control valve means 6 _FL comprises a normally open solenoid valve 11
Demagnetized _FL, demagnetize the normally closed electromagnetic valve 13 _FL with opened, the wheel brake B wheel is communicated between the _FL brake B _FL and the first valve closing to the master cylinder M and left front wheel
The state in which the reservoir 7A is shut off and the normally open solenoid valve 11 _FL
Is excited and closed, and the normally closed solenoid valve 13 _FL is excited.
And state, but blocking between the wheel brake B _FL for the master cylinder M and left front wheel which communicates between the wheel brake B _FL and the first reservoir 7A for the left front wheel and open, energizing the normally open electromagnetic valve 11 _FL , The normally closed solenoid valve 13 _FL is demagnetized and closed, and the master cylinder M and the first reservoir 7 are closed.
Control is performed so as to switch between a state in which both A and the wheel brake B _FL for the left front wheel are shut off.

The control valve means 6 _FR corresponding to the wheel brake B _FR for the front right wheel includes a normally open solenoid valve 11 provided between the second output hydraulic pressure path 5 B and the wheel brake B _FR for the front right wheel.
_FR , a normally closed solenoid valve 13 _FR provided between the right front wheel brake B _FR and the second reservoir 7B,
And a state communicating between the wheel brake B _FR for the master cylinder M and right front wheel but to block the inter-wheel brake B _FR and second reservoir 7B for the right front wheel, between the wheel brake B _FR for the master cylinder M and right front wheel To be switched between a state in which communication between the right front wheel brake _BFR and the reservoir 7B is communicated and a state in which both the master cylinder M and the reservoir 7B and the right front wheel brake _BFR are both disconnected. Controlled.

The control valve means 6 _RR corresponding to the wheel brake B _RR for the right rear wheel is a normally open electromagnetic type with a throttle provided between the first output hydraulic path 5A and the wheel brake B _RR for the right rear wheel. A valve 11 _RR , a one-way valve 12 _RR connected in parallel with the normally-open solenoid valve 11 _RR , and a normally-closed solenoid valve 13 provided between a wheel brake B _RR for the right rear wheel and the first reservoir 7A. _The one-way valve 12 _RR is connected to the master cylinder M side from the wheel brake B _RR for the right rear wheel when the brake operation is stopped in the open state of the normally open solenoid valve 11 _RR provided with a throttle. It works to quickly return the brake fluid.

The control valve means 6 _RR includes a normally open solenoid valve 11.
Demagnetized _RR, normally closed solenoid valve 13 deenergized _RR, but communicates between the wheel brake B _RR for the master cylinder M and the right rear wheel and closed wheel brake B _RR and the first as well as opening
The state in which the reservoir 7A is shut off and the normally open solenoid valve 11 _RR
Is excited and closed, and the normally closed solenoid valve 13 _RR is excited.
A state in which the valve is opened to shut off the connection between the master cylinder M and the wheel brake B _RR for the right rear wheel, but the communication between the wheel brake B _RR for the right rear wheel and the first reservoir 7A, and the normally open solenoid valve 11 _RR And the normally closed solenoid valve 13 _RR is demagnetized and closed to release the master cylinder M and the first reservoir 7.
A state in which both A and the wheel brake B _RR for the right rear wheel are shut off, the normally open solenoid valve 11 _RR is demagnetized and opened, and the normally closed solenoid valve 13 _RR is excited and opened to open the master. Cylinder M, first reservoir 7A and wheel brake B for right rear wheel
Control is performed to switch between a state of communicating with the _RR .

Further, a wheel brake B for the left rear wheel_RLCompatible with
Control valve means 6_RLIs the second output hydraulic path 5B and the rear left
Wheel brake B for wheels_RLNormally open solenoid valve 1 provided between
1_RLAnd the normally open solenoid valve 11_RLWhile connected in parallel to
Valve 12_RLAnd the wheel brake B for the left rear wheel_RLAnd the second
Normally closed solenoid valve 13 provided between reservoirs 7B_RLComposed with
And a wheel brake for the master cylinder M and the left rear wheel.
Key B_RLBut the wheel brake B_RLAnd the second lisa
Between the master cylinder M and the master cylinder M
Wheel brake B for left rear wheel_RLShut off between the left rear wheel
Wheel brake B _RLAnd the second reservoir 7B.
State, master cylinder M and second reservoir 7B and left
Wheel brake B for rear wheel_RLA state that shuts off between
, Master cylinder M, second reservoir 7B and left rear wheel
Wheel brake B for_RLTo communicate with
It is controlled to switch.

Next, referring to FIG. 2, the first pump 8A
The configuration of the first and second pumps 8A and 8B is the same, and therefore the description of the configuration of the second pump 8B is omitted, and the first and second actuators 9A and 9B are omitted. Since the configuration of 9B is the same, the description of the configuration of the second actuator 9B will be omitted.

The first pump 8A has a bottomed cylindrical pump housing 16 having an end wall 15 at one end, and a rod-shaped plunger 17 slidably fitted to the pump housing 16.
And

A discharge port 18 is provided at the center of the end wall 15, and a pump chamber 19 is formed between one end of the plunger 17 and the end wall 15. The other end of the plunger 17 projects from the other end of the pump housing 16.
7 is provided with a suction port 20 extending along one diameter line and having both ends opened to the outer surface of the plunger 17. Further, a communication path 21 is formed coaxially with the plunger 17 so as to face one end opening to a tapered valve seat 23 provided at the center of one end of the plunger 17, and the other end of the communication path 21 communicates with the suction port 20.

In the pump chamber 19, a suction valve 22 capable of closing one end opening of the communication passage 21 is accommodated. The suction valve 22 can be seated on the valve seat 23 and the valve seat 23. There is provided a spherical valve element 24 and a spring 25 provided between the end wall 15 of the pump housing 16 and the valve element 24 and exerting a spring force for urging the valve element 24 in a direction of seating on the valve seat 23.

The suction valve 22 opens when the pressure in the pump chamber 19 is reduced as the plunger 17 moves in the direction of increasing the volume of the pump chamber 19 (to the right in FIG. 2). Then, the brake fluid is sucked into the pump chamber 19 from the suction port 20 through the communication passage 21, but the pressure in the pump chamber 19 increases as the plunger 17 moves in the direction of reducing the volume of the pump chamber 19. The valve is closed in response to the pressure being applied, and functions to prevent the flow of the brake fluid from the communication passage 21 into the pump chamber 19.

The control valve means 6 _FL , 6 _RR ,
6 _FR , 6 _RL , both reservoirs 7A, 7B, both check valves 10
A and 10B are commonly mounted on the base 26, and the first pump 8A is also mounted on the base 26.

The base 26 is provided with a bottomed first fitting hole 27 for fitting and fixing the pump housing 16 of the first pump 8A. Between the closed end of the fitting hole 27 and the discharge liquid chamber 28
Is fitted in the first fitting hole 27 so as to form
An annular seal member 29 that resiliently contacts the inner peripheral surface of the first fitting hole 27 is mounted on the outer periphery of the pump housing 16.

The pump housing 1 in the discharge liquid chamber 28
6 is equipped with a discharge valve 30, and the discharge valve 30 is
A tapered valve seat 31 provided on the surface of the end wall 15 on the side of the discharge chamber 28 with the discharge port 18 communicating with the pump chamber 19 facing the center, and a spherical valve element 32 that can be seated on the valve seat 31. When,
Retainer 34 attached to one end of pump housing 16
And a spring 33 which is provided between the valve bodies 32 and exerts a spring force for urging the valve body 32 in the seating direction of the valve seat 31. A discharge liquid chamber 28 is provided at the center of the retainer 34 by the retainer 34. A communication hole 35 for preventing the inside from being partitioned is provided.

The discharge valve 30 is provided with the plunger 17
The valve is closed in response to the pressure of the pump chamber 19 being reduced in accordance with the movement of the pump chamber 19 in the direction of increasing the volume of the pump chamber 19, and the pump chamber 19 is discharged from the discharge liquid chamber 28 through the discharge port 18.
To prevent the brake fluid from flowing into the
The valve opens when the pressure of the pump chamber 19 is increased in accordance with the movement of the pump chamber 19 in the direction of reducing the volume of the pump chamber 19. 28
It works to discharge the brake fluid.

[0040] substrate 26 is a discharge passage 36 having one end communicating is provided in the discharge liquid chamber 28, the other end of said discharge exit passage 36, the wheel brake B _FL and the control valve means for the left front wheel 6
Connected between _FL . That is, the discharge port 1 of the first pump 8A
8 is the first pump 8 from the left front wheel brake _BFL side.
So as to block the flow of the brake fluid to the A side by the discharge valve 30, it is to be connected between the wheel brake B _FL and the control valve means 6 _FL for the left front wheel.

The first actuator 9A includes a fixed core 38
And a movable core 39 coaxially connected to the plunger 17 of the first pump 8A so as to be able to approach and separate from the fixed core 38.

The fixed core 38 is made of a magnetic metal and has a cylindrical shape. The distal end of a connection cylinder 40 having a base end coaxially and integrally connected to one end of the fixed core 38 is formed as follows. The first pump 8A is coupled to the other end of the pump housing 16 by caulking or the like. In addition, a flange portion 41 extending radially outward from a continuous portion of the fixed core 38 and the connection tube portion 40 is provided integrally with the fixed core 38 and the connection tube portion 40.

Further, the other end of the plunger 17 of the first pump 8A protrudes from the other end of the pump housing 16 and is slidably fitted in the connection cylinder 40. Is mounted with an annular seal member 42 which resiliently slides on the outer surface of the other end of the plunger 17.

The base 26 has a second fitting hole 43 having a diameter larger than that of the first fitting hole 27 in which the pump housing 16 is fitted. It is provided coaxially with the first fitting hole 27 so as to form the part 44, and the outer end of the second fitting hole 43 is opened on the outer surface of the base 26. Thus, the connection tube portion 40 is fitted into the second fitting hole 43 so that the flange portion 41 is fastened to the outer surface of the base 26, and the distal end portion of the connection tube portion 40 and the other end portion of the pump housing 16 are provided. And an annular chamber 45 is formed between the inner peripheral surface of the second fitting hole 43 and the step portion 44,
An annular seal member 46 that resiliently contacts the inner surface of the second fitting hole 43 is mounted on the outer surface near the flange 41.

A guide member 47 formed of a magnetic material into a cylindrical shape is fitted into the fixed core 38 and the connection cylinder portion 40, and the inner end is inserted into an annular groove 48 provided on the outer periphery of the guide member 47. A pin 49 that is fitted to determine the axial position of the guide member 47 is fitted to the fixed core 38 with an axis along the radial direction of the guide member 47. Thus, the plunger 1 is provided between one end of the guide member 47 whose axial position within the fixed core 38 and the connection cylinder 40 is determined, and the other end of the plunger 17 and the tip of the connection cylinder 40.
A suction liquid chamber 50 is formed to communicate with the suction port 20 provided in the nozzle 7, and the other end of the guide member 47 is arranged so as not to protrude from the fixed core 38 toward the movable core 39. Further, the outer end of the pin 49 does not protrude from the outer surface of the fixed core 38 when the pin 49 is fitted to the fixed core 38.

A plurality of communication passages 51 are provided in the connecting cylinder portion 40 to communicate the annular chamber 45 with the suction liquid chamber 50, and a suction passage 52 is formed in the base 26 through one end of the annular chamber 45.
And the other end of the suction passage 52 is connected to a first reservoir 7A.
Connected to. That is, the suction port 20 of the first pump 7A communicates with the first reservoir 7A.

The fixed core 38 is pressed into the guide cylinder 53. The guide cylinder 53 includes a cylindrical portion 53a on one end side of which the fixed core 38 is fitted, and a bottomed cylindrical portion 53b coaxially connected to the other end of the cylindrical portion 53a.
Although the thickness of the bottomed cylindrical portion 53b is formed to be thinner than the thickness of the cylindrical portion 53a, the cylindrical portion 53a and the bottomed cylindrical portion 53b are formed.
Are integrally connected so as to connect the inner surfaces flush. In addition, an annular seal member 54 that resiliently contacts the inner surface of the cylindrical portion 53a of the guide cylinder 53 is mounted on the outer periphery of the fixed core 38.

The movable core 39 is slidably fitted in the guide cylinder 53 so as to face the fixed core 38. One end of the movable core 39 is provided with the plunger 1 in the first pump 8A.
The other end of a rod 55 made of a non-magnetic material whose one end abuts coaxially with the other end of the rod 7 is slidably fitted on the guide member 47. In addition, in the suction liquid chamber 50, between the plunger 17 and the connection cylinder 40,
A spring 56 is provided which exerts a spring force in a direction in which the plunger 17 is brought into contact with the rod 55. The spring force of the spring 56 acts on the movable core 39 via the rod 55, and the spring force of the spring 56 The movable core 39 is urged in a direction away from the fixed core 38. The spring force of the spring 25 in the suction valve 22 also acts on the plunger 17 in a direction in which it comes into contact with the rod 55. The spring load of the spring 25 is set smaller than the spring load of the spring 56.

Between the movable core 39 and the fixed core 38,
A washer 59 made of a non-magnetic material is used to prevent the movable core 39 from moving away from the fixed core 38 due to residual magnetism when the movable core 39 comes into direct contact with the fixed core 38. The movable core 39 separated from the core 38 is interposed so as to have a sufficient space.

The cylindrical portion 53a of the guide cylinder 53 is coaxially surrounded by a bobbin 57 made of synthetic resin.
Is wound around the coil 58.

Further, the bobbin 57 and the coil 58 and the protruding portion of the guide cylinder 53 from the bobbin 57 are covered with a yoke 60 made of a magnetic metal, and the yoke 60 is connected to the flange portion 41.

The yoke 60 is formed, for example, in a cylindrical shape with a step and a bottom, and has a first cylindrical portion 60 a having one end facing the outer surface of the base 26 and fitting the flange portion 41, and a flange portion. 41, a first annular step portion 60b projecting radially inward from the other end of the first cylindrical portion 60a so as to come into contact with the outer peripheral edge portion, a bobbin 57 and a coil 58.
A second cylindrical portion 60c coaxially surrounding the first cylindrical step portion 60b and having one end coaxially connected to the inner peripheral portion of the first annular step portion 60b;
A second annular stepped portion 60 d extending inward in the radial direction from the other end of the second portion and sandwiching the bobbin 57 with the flange portion 41;
A third cylindrical portion 60e coaxially surrounding a protruding portion of the guide cylinder 53 from the bobbin 57 by coaxially connecting one end to the inner peripheral portion of the annular step portion 60d, and closing the other end of the third cylindrical portion 60e. An end plate portion 60f is provided, and the first cylindrical portion 60a and the flange portion 41 are mutually connected by caulking connection or the like.

In such a first actuator 9A,
When the coil 58 is in the demagnetized state, the movable core 39 is at a position (the position in FIG. 2) separated from the fixed core 38 by the spring force of the spring 56, and the plunger 17 of the first pump 8A reduces the volume of the pump chamber 19. Moving to increasing position. When the coil 58 is excited, the movable core 39 is
Moves in a direction approaching the fixed core 38 against the spring force of the first pump 8A, and the plunger 17 of the first pump 8A is pressed and driven to reduce the volume of the pump chamber 19. That is, coil 5
By switching between demagnetization and excitation of 8, the movable core 39 reciprocates in the axial direction, the plunger 17 is reciprocally driven in the axial direction accordingly, and the first pump 8A operates.

Incidentally, the movable core 39 and the fixed core 3
8 and the space between the closed end of the guide cylinder 53 and the movable core 39 are each in a sealed state, the space is increased or reduced according to the reciprocating movement of the movable core 39, and the movable core 39 The smooth reciprocating operation will be hindered. Therefore, on the outer surface of the movable core 39, a communication groove 61 connecting the two spaces is provided over the entire length in the axial direction. On one end surface of the rod 55 facing the suction liquid chamber 50, a groove 62 is provided along one diameter line of the rod 55, and the movable core 39
A groove 63 is provided on the other end surface of the rod 55 in contact with the rod 55 along one diameter line of the rod 55.
A communication hole 64 connecting between the two 63 is provided coaxially. That is, the suction liquid chamber 50 includes the groove 62, the communication hole 64, and the groove 63.
The space between the movable core 39 and the fixed core 38 communicates with the space between the closed end of the guide cylinder 53 and the space between the movable core 39 via the communication groove 61. are doing.

In FIG. 3, each control valve means 6 _FL , 6 _FR ,
6 _RL , 6 _RR normally open solenoid valves 11 _FL , 11 _FR , 11 _RL , 1
1 _RR and normally closed solenoid valve 13 _FL , 13 _FR , 13 _RL , 13
_RR and the first driving the first and second pumps 8A and 8B.
And the second actuators 9A and 9B are controlled by the control unit 65.
Reference numeral 5 denotes wheel speed detectors 66 _FL , 66 _FR , and 6 for individually detecting the wheel speeds of the left and right front wheels and the left and right rear wheels, respectively.
6 _RL , 66 _RR , based on the detected values, the ABS control for controlling the brake fluid pressure of each wheel brake B _FL , B _FR , B _RL , B _RR during the brake operation, and the left, Traction control for controlling the brake pressures of the left and right front wheel brakes B _FL and B _FR mounted on the right front wheel can be executed.

Wheel brake B for left and right front wheels_FL,
B_FRWhen the pressure is increased in the ABS control state, the control unit 65
Are the wheel brakes B according to the control procedure shown in FIG._FL,
B_FRThe pressure increase control is executed for each
The operation and operation of each of the pumps 8A and 8B depend on the high and low friction coefficient.
And deactivation are defined. That is, the control unit 65
Are each wheel speed detector 66_FL, 66_FR, 66_RL, 66_RRof
It is possible to judge the level of friction coefficient of the road surface based on the detected value
And the vehicle for the left and right front wheels in the ABS control state
Wheel brake B_FL, B_FRWhen the brake fluid pressure is increased,
When it is determined that the friction coefficient is low, the pumps 8A and 8B are turned off.
Activate and increase the pressure by the output pressure of the pumps 8A and 8B
However, when it is determined that the coefficient of friction is high,
The operation of the pumps 8A and 8B is stopped and the master cylinder M
The control valve means 6 increases the pressure by the hydraulic pressure._FL, 6_FRNormally open
Type solenoid valve 11_FL, 11_FRAnd normally closed solenoid valve 13_FL, 1
3 _FRAnd the pumps 8A and 8B, that is, the actuator 9
A, 9B.

In the pressure increase control in the ABS control, the friction coefficient of the traveling road surface may be determined for each of the left and right front wheels, or the friction coefficient of the traveling road surface may be determined for the entire vehicle. .

Next, the operation of this embodiment will be described.
And normal brake operation by depressing the brake pedal 3
During operation, each control valve means 6_FL~ 6_RRThen, normally open solenoid valve
11_FL~ 14_RRIs demagnetized and the valve is open
Normally closed solenoid valve 13_FL~ 13_RRBecomes demagnetized and valve closed
The hydraulic pressure output from the master cylinder M is
Brake B for vehicle and right rear wheel_FL, B_FRAct on
With proportional pressure reducing valve 1 _R, 1_LDepressurized for the right rear wheel
And wheel brake B for left rear wheel_RR, B_RLAct on.
At this time, both actuators for driving both pumps 8A and 8B are used.
Data 9A and 9B remain stopped.

When the wheels are about to enter the locked state during such a brake operation, each of the control valve means 6 _FL-
Of the 6 _RRs , the ABS control is performed by switching the pressure reduction, holding and pressure increase of the brake fluid pressure by the control valve means corresponding to the wheel that is about to enter the locked state.
The following, as shown in FIG. 5, the ABS control of the wheel brake B _FL for the left front wheel of when the left front wheel is likely to become locked
This will be described with reference to FIG.

At the time of the ABS control when the front left wheel is about to enter the locked state, first, the wheel brake B for the front left wheel is used.
Are those pressure reduction control of the _FL is executed, at the time of this pressure reduction control, as shown in Figure 5, the normally open electromagnetic valve 11 _FL of the control valve means 6 _FL excitation, with closing the normally closed solenoid valve 13 _{The FL} is excited and opened to cut off the connection between the master cylinder M and the wheel brake B _FL for the front left wheel, but to communicate between the wheel brake B _FL for the front left wheel and the first reservoir 7A. As a result, the brake fluid of the wheel brake B _FL for the left front wheel becomes the first fluid.
Escaped to reservoir 7A, left front wheel brake _BFL
Brake fluid pressure is reduced. At this time, the first pump 8A
The first actuator 9A for driving is stopped.

At the time of maintaining the hydraulic pressure following the pressure reduction control, FIG.
As shown in FIG._FLNormally open solenoid valve 1
1_FLThe solenoid valve 13 is energized and closed, and the normally closed solenoid valve 13 is closed._FLTurn off
Magnetic, valve closed, master cylinder M and first reservoir 7A
And wheel brake B for left front wheel _FLCut off between
You. Thereby, the wheel brake B for the left front wheel_FLBrake
The hydraulic pressure is maintained, but also at this time, the first pump 8A is driven.
The moving first actuator 9A remains stopped.

Further, at the time of pressure increase following the hydraulic pressure holding,
When the control unit 65 determines that the friction coefficient of the surface is low
The control unit 65 includes a control valve as shown in FIG.
Step 6 _FLNormally open solenoid valve 11_FLExcitation and valve closing
Both normally closed solenoid valves 13_FLBy demagnetizing and closing the valve
For the master cylinder M, the first reservoir 7A and the left front wheel.
Wheel brake B_FLWith both of them shut off,
The first pump 8A is operated by the actuator 9A.
You. Then, from the first reservoir 7A to the first pump 8A
The brake fluid pressure by the pumped brake fluid is the front left wheel
Wheel brake B for_FLWheel breaker for the left front wheel
Key B_FLWill be increased.

[0063] In addition to the surge pressure time in a state a low friction coefficient of the running road surface, the control valve means normally open electromagnetic valve 11 demagnetize _FL of 6 _FL, demagnetize the normally closed electromagnetic valve 13 _FL with the open state, In the closed state, the master cylinder M and the front left wheel brake _BFL communicate with each other, but the left front wheel brake _BFL and the first reservoir 7A are shut off to apply the brake pressure from the master cylinder M to the front left wheel. Wheel brake B for
_In this case, the discharge pressure of the first pump 8A is set to be lower than the output hydraulic pressure of the master cylinder M, so that the discharge pressure of the first pump 8A is Does not work.

Further, when the friction coefficient of the traveling road surface is high, A
The pressure increase at the BS control, while stopping the operation of the first actuator 9A or first pump 8A, similarly to the normal brake operation shown in FIG. 1, normally open electromagnetic valve of the control valve means 6 _FL 11 _FL is demagnetized and opened, and the normally closed solenoid valve 13 _FL is demagnetized and closed, and the hydraulic pressure output from the master cylinder M acts on the wheel brake B _FL for the front left wheel. Te, the brake pressure of the wheel brake B _FL is boosted.

[0065] For the ABS control of the wheel brake B _FR for the right front wheel, AB of the wheel brake B _FL for the left front wheel of the above-mentioned
S control and is controlled similarly controlled valve means 6 _FR, second actuator 9B for driving the second pump 8B, the brake fluid in the wheel brake B _FR for the right front wheel in a state a low friction coefficient of the running road surface -pressure Only works when pressure is applied.

[0066] In this way, the wheel brakes B _FL and the wheel brake B _FR of the time ABS control the wheel brakes B _FL for the right front wheel for the left front wheel, decompression of B _FR, holding and pressure increase are repeated, road surface When the pressure is increased in a state where the friction coefficient is low, the brake fluid in the first and second reservoirs 7A and 7B is pumped up by the first and second pumps 8A and 8B, and the vehicle travels on a road surface having a particularly low friction coefficient. Even at times, the inside of both reservoirs 7A and 7B is not filled with the brake fluid, and the ABS control can be continued for a long time.

Since it is not necessary for both pumps 8A and 8B to discharge a hydraulic pressure that overcomes the output hydraulic pressure of master cylinder M,
The first and second pumps 8A, 8B can be reduced in size and weight, and the first pumps 8A, 8B can be driven respectively.
In addition, the size and weight of the second actuators 9A and 9B can be reduced.

Further, both pumps 8A and 8B need only be operated when the brake fluid pressure of the left and right front wheel brakes B _FL and B _FR is increased in a state where the friction coefficient of the running road surface is low. The power consumption can be reduced as well as the power consumption. Moreover, both pumps 8A, 8
Control valve means 6 _FL during operation of B, 6 _FR by the master cylinder M and the wheel brakes B _FL, since between B _FR is interrupted, that each pump 8A, the discharge pressure of the 8B is applied to the master cylinder M side Therefore, kickback can be prevented from occurring, and the driver does not feel discomfort due to kickback. In addition, the energy consumption can be reduced by stopping the operation of the pumps 8A and 8B on a road surface having a high friction coefficient.

Wheel brake B for right rear wheel_RRAnd left rear wheel
Wheel brake B for_RLPressure reduction in ABS control and
Regarding the holding control, the left front wheel and the right front wheel
Wheel brake B_FL, B_FRControl in the same way as during
Control means 6_RR, 6_RLIs controlled. However, the car for the right rear wheel
Wheel brake B_RRAnd wheel brake B for left rear wheel_RLA
During the pressure increase control in the BS control, the control valve means 6_RR, 6
_RLNormally open solenoid valve 11 _RR, 11_RLIs demagnetized and opened
Both normally closed solenoid valves 13_RR, 13_RLIs demagnetized and closed
You. That is, the wheel brake B for the right rear wheel_RRAnd left rear wheel
Wheel brake B for_RLIs a normally open solenoid valve 11_RR, 11_RL
Output fluid of the master cylinder M
The pressure is increased by the pressure, and the discharge of each pump 8A, 8B
Pressure for the left front wheel when the coefficient of friction on the road surface is low.
Brake B for right and front right wheels_FL, B _FRFor use only when increasing pressure
Each pump 8A, 8B and each actuator
Data 9A and 9B can be further reduced in size and weight.
it can.

Further, the first and second pumps 8A and 8B can operate independently of each other, and can be operated in accordance with the brake fluid pressure control states of the wheel brakes B _FL and B _FR corresponding to the respective pumps 8A and 8B. The operation and stop of each of the pumps 8A and 8B can be individually controlled, and the driving times of the pumps 8A and 8B can be made different, so that the brake pressure control can be performed more precisely. In addition, it is possible to save energy consumption and reduce pump operation noise.

Further, the left and right front wheel brakes B _FL ,
B _FR consumes more liquid than the left and right rear wheel brakes B _RL and B _RR , and the left and right front wheel brakes B _FL and B _FR which consume more liquid. Is increased by the discharge pressure of each of the pumps 8A and 8B, so that the efficiency of the ABS control can be increased.

Further, the discharge port 1 of each of the pumps 8A and 8B
.. _{Are connected} between wheel brakes B _FL , B _FR for the left and right front wheels, which are drive wheels, and control valve means 6 _FL , 6 _FR corresponding to the wheel brakes B _FL , B _FR , respectively. Thus, during non-braking operation without operating the brake pedal 3, traction control can be performed to reduce the driving force of the left and right front wheels.

That is, when executing the traction control for reducing the driving force of the left front wheel, as shown in FIG. 8, the normally open solenoid valve _11FL of the control valve means _6FL is excited and closed, and the normally closed solenoid valve 11FL is closed. The valve 13 _FL is demagnetized and closed, and the first pump 8 A is operated by the first actuator 9 A in a state in which both the master cylinder M and the first reservoir 7 A and the wheel brake B _FL for the left front wheel are shut off, actuated wheel brake B _FL for the left front wheel caused to act on the brake fluid pressure by the brake fluid pumped from the first reservoir 7A to the wheel brake B _FL for the left front wheel, to perform a traction control by the left front wheel of the driving force reduction Can be.

[0074] At this time, the control valve means 6 _RR corresponding to the wheel brake B _RR for the right rear wheel is a driven wheel in which the first reservoir 7A in common with the wheel brake B _FL for the left front wheel, the normally open electromagnetic The valve 11 _RR is demagnetized and opened, and the normally closed solenoid valve 13 _RR is energized and opened. As a result, the master cylinder M and the first reservoir 7A and the right rear wheel brake _BRR are both in communication with each other, and the first pump 8A
Is connected to the master cylinder M, and the brake fluid from the inactive master cylinder M can be sucked by the first pump 8A and supplied to the left front wheel brake _BFL. It is not necessary to always store the brake fluid in the first reservoir 7A. In addition, it is not necessary to provide a means dedicated to traction control, and traction control can be executed only by changing the control of the first pump 8A and the control valve means _6FL , _{6RR from} the time of ABS control.

[0075] For even the wheel brake B _FR for the right front wheel, which is another drive wheel, like the wheel brakes B _FL for the left front wheel described above, by controlling the control valve means 6 _FR, 6 _RL,
Traction control for reducing the driving force of the right front wheel can be executed.

Further, each of the pumps 8A and 8B is
9, a plunger 17 having one end facing the pump housing 16 is slidably fitted to the pump housing 16, and each reciprocating actuator 9A, 9B is coaxially connected to the plunger 17 ... The connection structure between the pumps 8A and 8B and the actuators 9A and 9B can be simplified, and the operation efficiency of the pumps 8A and 8B and the actuators 9A and 9B can be improved.

Each of the actuators 9A and 9B is a solenoid having a fixed core 38 and a movable core 39 coaxially connected to the plunger 17 so as to be able to approach and separate from the fixed core 38. By making the actuators 9A and 9B simpler, the cost can be reduced.

In the above embodiment, the actuators 9A, 9
Although a solenoid was used as B, actuators 9A,
Since 9B may be small, a step motor, a linear motor, and a piezoelectric element can be used as an actuator.

In the above embodiment, the brake fluid pressure control device for a four-wheeled vehicle has been described. However, the present invention can be applied to a brake fluid pressure control device for a motorcycle.

Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the appended claims. It is possible to do.

[0081]

As described above, according to the first aspect of the present invention, the ABS is prevented from being filled with the brake fluid even when traveling on a road surface having a particularly low friction coefficient. The control can be continued for a long time, the size of the pump and the actuator can be reduced and the weight can be reduced, and the ABS operation noise and the power consumption can be reduced. Moreover, kickback can be prevented from occurring, and the driver does not feel uncomfortable due to kickback.

According to the second aspect of the present invention, when the pressure is increased by the ABS control on a road surface having a low friction coefficient, the pump is operated to return the brake fluid to the wheel brake side.
The duration of the ABS control is ensured, and the operation of the pump is stopped on a road surface having a high friction coefficient, so that the ABS control can be continued for a long time while saving energy consumption.

According to the third aspect of the present invention, the operation / stop of each pump is individually controlled according to the brake fluid pressure control state of the wheel brake corresponding to each pump, and the driving time of each pump is controlled. , The more precise brake pressure control becomes possible, the energy consumption can be reduced, and the pump operation noise can be reduced.

According to the fourth aspect of the present invention, the pressure on the wheel brake side to which the pump is connected is increased by the discharge pressure of the pump during the ABS control, and the output of the master cylinder during the ABS control on the wheel brake side to which the pump is not connected. By increasing the pressure by the hydraulic pressure, the size and weight of the pump and the actuator can be further reduced.

According to the fifth aspect of the present invention, the brake fluid pressure of the rear wheel brake, which is the side where the amount of liquid consumption is small, is increased by the output hydraulic pressure of the master cylinder, and the pressure is increased on the side where the amount of liquid consumption is large. By increasing the brake fluid pressure of a wheel brake for a front wheel by the discharge pressure of the pump, the efficiency of the ABS control can be increased.

According to the sixth aspect of the invention, the brake fluid pressure from the brake fluid pumped from the reservoir is applied to the wheel brakes for the drive wheels during the non-braking operation, so that the wheel brakes for the drive wheels are actuated. Traction control by driving force reduction can be performed. On this occasion,
The suction port of the pump is connected to the master cylinder, and the brake fluid from the inactive master cylinder can be sucked by the pump and supplied to the wheel brakes for the drive wheels, and the brake fluid is constantly stored in the reservoir. You don't have to. In addition, traction control can be executed only by changing the control of the pump and the control valve means from the time of the ABS control, without the necessity of providing means dedicated to traction control.

According to the seventh aspect of the invention, the connection structure between the pump and the actuator can be simplified, and the operation efficiency of the pump and the actuator can be improved.

Further, according to the invention of claim 8, it is possible to reduce the cost by making the actuator simpler.

[Brief description of the drawings]

FIG. 1 is a hydraulic circuit diagram of a vehicle brake hydraulic pressure control device.

FIG. 2 is a vertical sectional view of a pump and an actuator.

FIG. 3 is a block diagram showing a control system of each control valve means and each pump.

FIG. 4 is a flowchart showing a control procedure at the time of pressure increase in an ABS control state.

FIG. 5 is a hydraulic circuit diagram corresponding to FIG. 1 and showing a reduced pressure state in ABS control.

FIG. 6 is a hydraulic circuit diagram corresponding to FIG. 1 and showing a hydraulic pressure holding state in ABS control.

FIG. 7 is a hydraulic circuit diagram corresponding to FIG. 1 and illustrating a pressure increasing state in ABS control.

FIG. 8 is a hydraulic circuit diagram corresponding to FIG. 1 and showing a traction control state.

[Explanation of symbols]

6 _FL , 6 _FR , 6 _RL , 6 _RR Control valve means 7A, 7B Reservoir 8A, 8B Pump 9A, 9B Actuator 16 Pump housing 17 Plunger 18 ... discharge port 19 ... pump chamber 20 ... suction port 38 ... fixed core 39 ... movable core 65 ... control unit _BFL , _BFR ... wheel brake for front wheels _BRL , B _RR : Wheel brake for rear wheel M: Master cylinder

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Motoyasu Nakamura, 840 Kokubu, Ueda-shi, Nagano Prefecture Nissin Kogyo Co., Ltd. (72) Inventor Masashi Kobayashi 840 Kokubu, Ueda-shi, Nagano Prefecture Nissin Kogyo Co., Ltd. (72) Inventor Hiroo Kawakami 1-4-1 Chuo, Wako-shi, Saitama F-term in Honda R & D Co., Ltd. Reference) 3D046 BB05 BB07 BB28 CC02 DD04 EE01 FF09 HH46 LL23 LL37 LL43 LL47 LL50

Claims (8)

[Claims] 1. A master cylinder (M); reservoir (7A, 7B) for reserving the brake fluid and; master cylinder (M) and the wheel brake (B _FL, B _FR) communicating between but the wheel brake (B _FL , B _FR ) and reservoir (7A,
7B), a state in which the master cylinder (M) and the wheel brakes (B _FL , B _FR ) are cut off, but a communication between the wheel brakes (B _FL , B _FR ) and the reservoirs (7A, 7B) is established. Control valve means ( _6FL , _6FR ) capable of switching a state in which both the master cylinder (M) and the reservoirs (7A, 7B) and the wheel brakes ( _BFL , _BFR ) are shut off; The control valve means ( _6FL , _BFR ) controls the brake fluid pressure of ( _BFL , _BFR ).
A control unit for controlling the (65) the operation of the 6 _FR); In the vehicle brake hydraulic pressure control apparatus comprising, said control valve means (6 _FL, 6 _FR) and the wheel brake (B _FL, B _FR)
In the meantime, a discharge port (18) of a pump (8A, 8B) that pumps up brake fluid stored in the reservoir (7A, 7B)
From the wheel brake (B _FL , B _FR ) side to the pump (8
A, 8B) A brake fluid pressure control device for a vehicle, wherein the brake fluid pressure control device is connected so as to block the flow of brake fluid to the side. 2. The control unit (65) according to claim 1, further comprising:
High and low friction coefficient can be determined and anti-lock
The wheel brake (B) in the brake control state _FL, B_FR)
When the brake fluid pressure is increased, it is determined that the friction coefficient is low.
The pumps (8A, 8B) are activated when
The pressure is increased by the output pressure of the pumps (8A, 8B).
When it is determined that the number is high, the pump (8A, 8B)
Is stopped and the output hydraulic pressure of the master cylinder (M) is stopped.
The control valve means (6_FL, 6_FR)and
The operation of the pumps (8A, 8B) is controlled.
The vehicle brake fluid pressure control device according to claim 1, wherein 3. The wheel brake (B)_FL, B_FR)and
The control valve means (6 _FL, 6_FR) Mutually different pairs
For each combination, the reservoir (7A, 7B) and the
Each pump has a combination of pumps (8A, 8B)
(8A, 8B) can operate independently of each other
The vehicle brake fluid pressure according to claim 1 or 2,
Control device. 4. A front wheel brake and a rear wheel brake (B _FL , B _RR ; B _FR , B _FR , B _FR) mounted on a pair of front and rear wheels, respectively.
B _RL ), one for each of the reservoirs (7A, 7B)
And the pumps (8A, 8B), and the discharge ports (18) of the pumps (8A, 8B) are provided with front wheel brakes (B _FL , B _FR ) and front valve control valve means (6).
_FL , 6 _FR ) and wheel brakes for rear wheels (B _RL , B
_The brake fluid pressure control device for a vehicle according to claim 1, wherein the brake fluid pressure control device for a vehicle is connected to any one of the control valve means ( _6RL , _6RR ) for the rear wheel. 5. A discharge port (1) of the pump (8A, 8B).
5. The vehicle brake fluid pressure according to claim 4, wherein the brake valve is connected between the front wheel brake ( _BFL , _BFR ) and the front valve control valve means ( _6FL , _6FR ). Control device. 6. A discharge port (1) of the pump (8A, 8B).
8) is connected between a wheel brake (B _FL , B _FR ) for a wheel which is a driving wheel among the front wheels and the rear wheels, and the control valve means (6 _FL , 6 _FR ) corresponding to the driving wheel. The control valve means (6 _RL , 6 _RR ) corresponding to the driven wheel of the front wheel and the rear wheel is provided with the master cylinder (M) and the reservoirs (7A, 7B) and the wheel brake (B) for the driven wheel. _FL, B _FR) and the brake fluid pressure control apparatus according to claim 4 or 5, wherein it is configured as allowing both communicating between. 7. The pump (8A, 8B) is configured such that a plunger (17) having one end facing a pump chamber (19) is slidably fitted in a pump housing (16), and an actuator that reciprocates. The vehicle brake fluid pressure control device according to any one of claims 1 to 6, wherein (9A, 9B) is coaxially connected to the plunger (17). 8. The actuator (9A, 9B)
A solenoid comprising a fixed core (38) and a movable core (39) coaxially connected to said plunger (17) so as to be able to approach and separate from said fixed core (38). The brake fluid pressure control device for a vehicle according to any one of the preceding claims.