JP2617353B2 - Braking hydraulic control device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Object of the Invention (1) Industrial application field The present invention relates to an auxiliary hydraulic pressure generating means capable of generating a hydraulic pressure according to a braking operation of a brake pedal, and a hydraulic pressure supply source. The present invention relates to a brake hydraulic control device that is controllable according to a braking operation of a brake pedal and includes a hydraulic supply source and a hydraulic supply source hydraulic control unit interposed between brake devices.

(2) Conventional technology Conventionally, such a braking hydraulic control device is disclosed in, for example,
It is known from, for example, Japanese Patent Application Laid-Open No. 187-187.

(3) Problems to be Solved by the Invention By the way, in the above-mentioned conventional one, the braking pressure of the brake device is controlled by the hydraulic supply source hydraulic pressure control means. When it becomes impossible to secure the supply source hydraulic pressure, it becomes difficult to apply sufficient braking pressure to the brake device.

The present invention has been made in view of such circumstances,
It is an object of the present invention to provide a brake hydraulic pressure control device capable of obtaining a sufficient braking pressure even when a sufficient hydraulic pressure is not obtained due to a malfunction of a hydraulic pressure source.

B. Configuration of the Invention (1) Means for Solving the Problems According to the present invention, the auxiliary hydraulic pressure generating means includes a plurality of operating pistons which are interlocked with each other to move forward in accordance with a braking operation of a brake pedal. The piston is slidably fitted in the first housing with the front face of the piston facing the hydraulic chamber, and the hydraulic supply hydraulic control means includes an output port, an input port communicating with the hydraulic supply source, and a release port communicating with the reservoir. A spool is slidably fitted in the second housing having the output port, the input port, and the release port so as to switch communication between the output port and the release port in accordance with the axial movement, and the output port communicates with the input port. The input pressure working chamber that exerts hydraulic pressure to urge the spool in the direction and the output port communicates with the output port to exert hydraulic pressure in the direction that causes the output port to communicate with the release port. An output pressure action chamber is provided in the second housing, and the output port faces the input hydraulic chamber that can communicate with the output port and the output hydraulic chamber that communicates with the brake device. The hydraulic pressure transmitting means is slidably fitted to the body and is connected to a brake device. One of the hydraulic chambers of the auxiliary hydraulic pressure generating means is connected to an input pressure action chamber of a hydraulic power supply hydraulic control means. The other hydraulic chamber of the auxiliary hydraulic pressure generating means is connected between the hydraulic transmission means and the brake device via an opening / closing valve which closes in accordance with an increase in the output hydraulic pressure of the hydraulic power supply hydraulic control means, and is used when a braking operation by the brake pedal is performed. Prior to the rise of the hydraulic pressure of the other hydraulic chamber, the on-off valve should be closed by the rise of the output hydraulic pressure of the hydraulic supply source hydraulic control means that operates in response to the hydraulic pressure of the one hydraulic chamber. It is set.

(2) Operation According to the above configuration, during normal braking in which the hydraulic pressure of the hydraulic supply source is normal, the hydraulic pressure is adjusted according to the hydraulic pressure output from one hydraulic chamber in the auxiliary hydraulic pressure generating means in accordance with the braking operation of the brake pedal. The hydraulic pressure is output from the supply-source hydraulic control means, and the on-off valve is closed accordingly, and the output hydraulic pressure of the hydraulic supply-source hydraulic control means is supplied to the brake device via the hydraulic transmission means, and the closing operation of the on-off valve is performed. Later, the hydraulic pressure is output from the other hydraulic chamber in the auxiliary hydraulic pressure generating means in response to the braking operation of the brake pedal, so that the hydraulic pressure output from the other hydraulic chamber does not act on the brake device. Also, when the hydraulic pressure of the hydraulic supply source drops abnormally, the on-off valve opens according to the decrease of the output hydraulic pressure of the hydraulic supply source hydraulic control means, and the brake operation amount of the brake pedal from the other hydraulic chamber in the auxiliary hydraulic pressure generation means is reduced. The hydraulic pressure output accordingly acts on the brake device to secure the braking pressure. In addition, when the on-off valve is opened, the hydraulic pressure of the brake device is prevented from escaping to the hydraulic supply source side by the hydraulic transmission means.

(3) Embodiment Hereinafter, an embodiment in which the present invention is applied to a braking hydraulic control device for a front engine / front drive vehicle will be described with reference to the drawings.

Brake device for front left wheel on front left and front right wheels of vehicle
B _FL and B _FR for the front right wheel are installed respectively, and B _RL for the rear left wheel and B _RL for the rear left and right wheels.
And a right rear wheel brake device B _RR are respectively mounted. On the other hand, the brake pedal 1
Auxiliary hydraulic pressure generating means 3 for outputting a hydraulic pressure according to the amount of depression of the vehicle
During normal braking, the hydraulic pressure from the hydraulic supply source 2 controlled by the hydraulic supply source hydraulic control means 4 according to the hydraulic pressure output from the auxiliary hydraulic pressure generation means 3 is transmitted by the hydraulic transmission means 5.
_The brake is supplied to each front wheel brake device B _FL , B _FR via _FL , 5 _FR, and the hydraulic pressure from the hydraulic supply source hydraulic control means 4 is supplied to each rear wheel brake via the hydraulic transmission means 5 _R and the proportional pressure reducing valve 6. It is given to the brake devices B _RL and B _RR . Hydraulic supply source 2
During the braking operation when the motor malfunctions, the hydraulic pressure generated by the auxiliary hydraulic pressure generating means 3 is applied to each of the brake devices B _FL , B _FR , B _RL , and B _RR.
Given to. Further, the inflow solenoid valves 7 _FL , 7 _FR and the outflow solenoid valves 8 _FL , 8 _FR provided respectively corresponding to the front wheel brake devices B _FL , B _FR and the brake devices B _RL , B for both rear wheels are provided.
Inflow solenoid valve 7 _R and outflow solenoid valve 8 _R commonly provided for _RR
The anti-lock control can be performed by holding or reducing the braking oil pressure of each of the brake devices B _FL , B _FR , B _RL , and B _RR , and the traction control switching control valve means 9 controls each of the brake devices B _FL , B _FR , B _RL , B _RR , and traction control can be performed by increasing the braking oil pressure.

The hydraulic supply source 2 includes a hydraulic pump 11 for pumping hydraulic oil from the reservoir R, an accumulator 12 connected to the hydraulic pump 11, and a pressure switch 13 for controlling the operation of the hydraulic pump 11.

The auxiliary hydraulic pressure generating means 3 includes a first housing 14 formed in a cylindrical shape with both ends closed. A first working piston 17 is provided in a first cylinder hole 15 provided in the first housing 14.
And a second working piston 18 arranged at a distance in front of the first working piston 17 and a third working piston 19 further arranged at a distance in front of the second working piston 18 can slide. A first hydraulic chamber 16 is formed between the first working piston 17 and the second working piston 18, and a first hydraulic chamber 16 is provided in front of the second working piston 18, that is, between the second working piston 18 and the third working piston 19. A second hydraulic chamber 20 is formed, and a third hydraulic chamber 21 is formed between the front end wall of the first cylinder hole 15 and the third working piston 19.

The first working piston 17 is integrally provided with a piston rod 17a which penetrates a rear end wall of the first cylinder hole 15 in an oil-tight and movably movable manner and protrudes outward, and is connected to the brake pedal 1. The front end of the pressing rod 22 is
It contacts the rear end of 17a. Therefore, brake pedal 1
The first working piston 17 moves forward in the first cylinder hole 15 in response to the braking operation.

On the inner surface of the first cylinder hole 15, a stopper 23 which abuts on the rear end of the second working piston 18 and regulates the retreat limit of the second working piston 18 projects radially inward and projects.
A first return spring 24 for urging the first working piston 17 rearward is contracted between the stopper 23 and the first working piston 17. A second working piston 18 and a third working piston
A second return spring 25 that urges the third operating piston 19 in the direction away from each other is housed in the second hydraulic chamber 20, and a third return spring 26 that urges the third working piston 19 rearward is provided in the first cylinder hole 15. Between the front end wall and the third working piston 19. As a result, the second and third working pistons 18, 19 move forward by the generation of oil pressure in the first hydraulic chamber 16 in accordance with the forward movement of the first working piston 17.

The first housing 14 has a first hydraulic chamber 16 connected to a first hydraulic chamber 16.
An output port 27 and a second output port communicating with the second hydraulic chamber 20
28 and a third output port 29 communicating with the third hydraulic chamber 21 are provided, and each hydraulic pressure is set only when the first working piston 17 and the second and third working pistons 18, 19 return to the retreat limit. Communication port for connecting chambers 16, 20, and 21 to reservoir R
30,31,32 are drilled.

The hydraulic supply source hydraulic control means 4 includes a second housing 33,
A spool 34 slidably fitted to the second housing 33,
A reaction piston 35 and a pressing piston 36 are provided.

The second housing 33 has an outer cylindrical portion 37 closed at both ends and an inner cylindrical portion 38 open at both ends coaxially arranged in the outer cylindrical portion 37 and fixed to each other at an intermediate portion thereof. The outer cylinder 37 has an output port 39 and an input port 4 connected to the hydraulic pressure source 2.
0, and release ports 41 communicating with the reservoir R are provided at intervals from the front to the rear (from left to right in FIG. 1). The inner cylinder 38 has a second cylinder hole.
The input port 40 is opened to the inner surface of the second cylinder hole 42. Moreover, an annular concave portion 46 is provided on the outer surface of the spool 34 slidably fitted in the second cylinder hole 42, and the axial length of the annular concave portion 46 is set when the spool 34 is at the rear position. The output port 39 and the release port 41 communicate with each other. When the spool 34 is at the front position, the output port
It is set to communicate between 39 and the input port 40.

At the rear end of the spool 34, a flange portion extending outward in the radial direction
The flange 34a and the second housing 33 are provided.
The control spring 48 is contracted between the control spring 48 and the spool 34, and the spool 34 is urged rearward by the spring force of the control spring 48.

The reaction force piston 35 can be brought into contact with the front end of the spool 34 and is slidably fitted in the second cylinder hole 42 at a position in front of the spool 34. On the other hand, a cap-shaped member 49 is fitted to the front end of the inner cylindrical portion 38, and the cap-shaped member 49 is moved rearward by the spring force of a spring 50 contracted between the inner cylindrical portion 38 and the front end wall of the outer cylindrical portion 37. It is urged toward the side. Thus, the cap-like member 49 and the reaction force piston
An output pressure action chamber 51 that faces the front face of the reaction force piston 35 is defined between the output pressure action chamber 35 and the output pressure action chamber 51 through a communication hole 52 formed in the cap-shaped member 49. Connects to output port 39.

A spring 54 is contracted between a step portion provided on the inner surface of the second cylinder hole 42 on the front side of the spool 34 and the reaction force piston 35, and the reaction force piston 35 is formed by the spring force of the spring 54.
Is urged forward. Moreover, the set load of the spring 54 is set smaller than the set load of the spring 50, and in a state where no hydraulic pressure is acting on the output pressure action chamber 51,
The front end of the reaction force piston 35 is in contact with the cap-shaped member 49 which is urged by the spring 50 and is in contact with the front end of the inner cylindrical portion 38.

The spool 34 has a communication passage communicating with the release port 41.
56 is bored in the front end face of the spool 34 so as to open.
Therefore, the hydraulic pressure does not act on the rear surface of the reaction force piston 35 and the front surface of the spool 34.

The pressing piston 36 is slidably fitted to an outer cylindrical portion 37 of the second housing 33 on the rear side of the spool 34 so as to abut on the rear end of the spool 34 coaxially.
The rear surface faces an input pressure action chamber 55 defined between the rear end wall and the outer cylinder portion 37.

In this hydraulic supply source hydraulic control means 4, the output pressure action chamber 51
The hydraulic pressure acting on the reaction force piston 35 by the hydraulic pressure toward the rear side and the hydraulic pressure in the input pressure action chamber 55
The spool 34 moves in the axial direction due to the balance with the hydraulic pressure acting on the front side acting on the 36, and the pressure receiving area facing the input pressure action chamber 55 of the pressing piston 36 is the reaction force piston.
The pressure receiving area is set to be larger than the pressure receiving area facing the 35 output pressure action chambers 51. Therefore, the spool 34 can be driven in the axial direction even if the hydraulic pressure introduced into the input pressure action chamber 55 is relatively low.

Further, the moving distance from the retreat limit position (the position shown) of the spool 34 to the communication of the input port 40 with the output port 39 is equal to the front end of the spool 34 in the retreat limit position and the output pressure action chamber.
The distance is set smaller than the distance between the rear end of the reaction force piston 35 located at the front position in a state where no oil pressure acts on 51.
Therefore, as shown in the drawing, in a state where the hydraulic pressure is not acting on the output pressure action chamber 51 and the input pressure action chamber 55, the input pressure action chamber 55
When the spool 34 is moved forward by the pressing piston 36 by applying hydraulic pressure, when the annular concave portion 46 communicates with the input port 40, the hydraulic pressure in the output pressure action chamber 51 increases and the reaction force piston 35 comes into contact with the spool 34. Until then, no reaction force acts on the pressing piston 36. As a result, the braking pressure can be rapidly increased at the beginning of the braking operation, and the initial braking operation can be smoothed.

By the way, the input pressure action chamber of the hydraulic supply source hydraulic control means 4
An oil passage 76 communicating with 55 is connected to a first output port 27 of the auxiliary hydraulic pressure generating means 3 via a proportional pressure reducing valve 77. The proportional pressure-reducing valve 77 reduces the oil pressure from the first output port 27 proportionally after the oil pressure reaches a certain value, and acts on the input pressure action chamber 55, and has a conventionally well-known structure. Things. From the proportional pressure reducing valve 77 Thus, the hydraulic pressure P ₁₆ of the first hydraulic chamber 16 in the auxiliary hydraulic pressure generating means 3 is output is reduced for example, as shown in Figure 2. That is, the first hydraulic chamber 1
Until pressure P ₁₆ of 6 reaches a constant pressure p is the proportional pressure reducing valve 77 is output as the pressure P _16, the constant pressure of greater than from p angle θ a tilt proportionally reduced pressure While outputting.

An accumulator 78 is connected to the oil passage 76 between the proportional pressure reducing valve 77 and the input pressure action chamber 55. This accumulator 78
The accumulator body 90 and an accumulator piston 92 slidably fitted to the accumulator body 90 while defining an accumulator chamber 91 communicating with the oil passage 76 therebetween, and reduce the volume of the accumulator chamber 91. First and second accumulator springs 93 and 94 are provided in series between the accumulator piston 92 and the accumulator main body 90 to bias the accumulator piston 92 in the direction.

The accumulator body 90 has a small-diameter hole with one end closed.
A small-diameter hole 95 is provided with a large-diameter hole 97, one end of which is coaxially connected to the other end of the small-diameter hole 95 via a step 96, and the other end of which is closed. The accumulator piston 92 slides into the small-diameter hole 95. It is movably fitted. In addition, a pressure accumulation chamber 91 is defined between one end of the accumulator piston 92 and one closed end of the small-diameter hole 95. In the large-diameter hole 97, a spring receiving member 98 that is in contact with the stepped portion 96 and is restricted from moving toward the one end side is accommodated so as to be movable in the axial direction. The first accumulator spring 93 includes the accumulator piston 92 and the accumulator piston 92. Contracted between the spring receiving members 98,
The second accumulator spring 94 includes a spring receiving member 98 and a large-diameter hole 97.
Is closed between the other end and the closed end. In addition, the set load of the first accumulator spring 93 is increased by the second accumulator spring 94
Is set smaller than the set load. Therefore, when the oil pressure is not acting on the pressure accumulating chamber 91, the spring receiving member 98 is in a position in contact with the step portion 96 by the spring force of the second accumulator spring 94.

By the way, the hydraulic pressure generated in the first hydraulic chamber 16 by the forward operation of the first operating piston 17 in accordance with the depression operation of the brake pedal 1 is reduced by the proportional pressure reducing valve 77, then accumulated in the accumulator 78 and the input pressure is applied. The input hydraulic pressure set to start the operation of the hydraulic pressure control unit 4 so that the hydraulic pressure control unit 4 starts operating before the accumulator 78 operates, although it operates on the chamber 55. The oil pressure in the chamber 55 is set lower than the pressure at which the accumulator 78 starts accumulating pressure. That pressure receiving area facing the input hydraulic pressure chamber 55 of the pressure piston 36 and S ₁ in the hydraulic pressure supply source hydraulic pressure control means 4, the accumulation chamber of the accumulator piston 92 91
The pressure receiving area and S ₂ facing the, the set load of the control spring 48 of the hydraulic supply source hydraulic pressure control means 4 and f _1, the set load of the first accumulator spring 93 in the accumulator 78
When f ₂ is set, the following equation (1) is established.

f ₁ / S ₁ <f ₂ / S ₂ (1) The hydraulic transmission means 5 _FL , 5 _FR , and 5 _R are the output port 39 of the hydraulic supply source hydraulic control means 4 and the brake devices B _FL , B _FR , and B _RL. , B _RR
And the hydraulic transmission means 5 _FL , 5 _FR
Is a traction control switching control valve means 9 connected to the output port 39 of the hydraulic pressure control means 4 and a brake device.
Between B _FL and B _FR, and hydraulic transmission means 5 _R
It is interposed between 39 and the proportional pressure reducing valve 6 connected to the brake devices B _RL and B _RR . These hydraulic transmission means 5 _FL , 5 _FR , 5 _R
When the hydraulic pressure from the hydraulic supply source 2 is normal, the hydraulic pressure from the hydraulic supply
B _FL , B _FR , B _RL , and B _RR are transmitted to each of the brake devices B _FL , B _FR , and B _FL when the hydraulic pressure of the hydraulic pressure supply source 2 abnormally decreases.
_RL, has a function that can prevent the hydraulic oil from the B _RR to the hydraulic supply source 2 side flows backward, so are basically having the same structure, representatively hydraulic transmission means 5 _FL
The configuration will be described below.

The hydraulic transmission means 5 _FL is connected to the input hydraulic chamber 58 and the output hydraulic chamber 5.
Free piston 60 moves to cylinder body 6 with both ends facing 9
A spring 62 that is slidably fitted to 1 and biases the free piston 60 toward the input hydraulic chamber 58 is housed and arranged in the output hydraulic chamber 59.

According to such a configuration of the hydraulic pressure transmission means _5FL , it is possible to output a hydraulic pressure according to the hydraulic pressure acting on the input hydraulic chamber 58 from the output hydraulic chamber 59, and to output the hydraulic pressure of the output hydraulic chamber 59 to the input hydraulic chamber 59. It does not flow to the side 58, and the output hydraulic chamber 59 is connected to the brake device _BFL .

That is, each of the brake devices B _FL , B _FR , B _RL , and B _RR includes a cylinder body 63 and a brake piston 64 slidably fitted in the cylinder body 63. The output hydraulic chamber 59 is communicated with the brake hydraulic chamber 65 by moving the brake piston 64 in accordance with the hydraulic pressure acting on the brake hydraulic chamber 65 defined in FIG.

Hydraulic transmission means for front wheel brake devices B _FL and B _FR
To 5 _FL, 5 _FR input hydraulic pressure chamber 58, inlet solenoid valves 7 _FL, 7 _FR and the outlet solenoid valves 8 _FL, 8 _FR are respectively connected in parallel, the rear wheel brake device B _RL, corresponding to B _RR to the input hydraulic pressure chamber 58 of the hydraulic transmission means 5 _R inflow solenoid valve 7 _R and outlet solenoid valve 8 _R are connected in parallel.

Inlet solenoid valve 7 _FL, 7 _FR, 7 _R is a solenoid valve interrupting during excitation, also spill solenoid valve 8 _FL, 8 _FR, 8 _R is an electromagnetic valve which communicates at excitation. Thus to outlet solenoid valve 8 _FL, 8 _FR, 8 _R is respectively interposed between the hydraulic transmitting means 5 _FL, 5 _FR, 5 input hydraulic pressure chamber 58 and reservoir _R R. The inlet solenoid valves 7 _FL, 7 _FR is interposed between the hydraulic transmitting means 5 _FL, 5 _FR input hydraulic pressure chamber 58 and the output oil passage 66 of the _F, inlet solenoid valve 7 _R hydraulic transmitting means 5 _R input hydraulic pressure chamber It is interposed between the 58 and the output oil passage 66 _R. Further, a one-way hydraulic pressure release valve 8 is arranged in parallel with each of the inflow solenoid valves 7 _FL , 7 _FR , 7 _R.
1 _FL , 81 _FR , 81 _R are connected.
_FL , 81 _FR , and 81 _R allow only the flow of hydraulic oil from the input hydraulic chamber 58 to the output oil passages 66 _F and 66 _R.

Such inflow solenoid valves _7FL , _7FR , _7R and outflow solenoid valves
Excitation and demagnetization of 8 _FL , 8 _FR , and 8 _R are controlled by control means 80, which controls the inflow solenoid valves 7 _FL , 7 _FR , 7 _R and the outflow solenoid valve 8 _FL during normal braking. , 8 _FR, although remain degauss 8 _R, at the time of anti-lock control, the inlet solenoid valve 7 _FL, 7 _FR, a 7 _R and outlet solenoid valves 8 _FL, 8 _FR, 8 _R were both excited vacuum control state , The inflow solenoid valves 7 _FL , 7 _FR , 7 _R are energized and the outflow solenoid valves 8 _FL , 8 _FR , 8 _R are demagnetized while the inflow solenoid valves 7 _FL , 7 _FR , 7 _R and the outflow solenoid valves are demagnetized.
It is possible to switch between the pressure increase control state in which 8 _FL , 8 _FR and 8 _R are all demagnetized.

Output oil passage 66 _F is the hydraulic pressure supply source hydraulic pressure control means 4 through a normally open electromagnetic valve 9a of the traction control changeover valve means 9
Is the connection to the output port 39, an output oil passage 66 _R is connected directly to the output port 39 of the hydraulic supply source hydraulic pressure control means 4.

Traction control changeover valve means 9, the normally open solenoid valve 9a which is interposed between the output port 39 and the output oil passage 66 _F hydraulic supply source hydraulic pressure control means 4, the hydraulic pressure supply source 2 and the output oil passage 66 _And a normally closed solenoid valve 9b interposed between _F. Excitation and demagnetization of these solenoid valves 9a and 9 are also controlled by the control means 80, and the control means 80 demagnetizes and opens the solenoid valve 9a and demagnetizes the solenoid valve 9b in a normal state. The valve is closed, and during traction control in the non-braking state, the solenoid valve 9a is excited to close and the solenoid valve 9b is excited to open. Further, the control means 80, the excitation of the solenoid valve 9a pressure boosting i.e. inlet solenoid valve 7 _FL in anti-lock control state, 7 _FR, 7 _R and outlet solenoid valves 8 _FL, the 8 _FR, 8 _R are both state of demagnetization -Switching control of demagnetization is also possible.

The solenoid valve 9b of the traction control switching control valve means 9 is connected between the input port 40 of the hydraulic pressure source hydraulic pressure control means 4 and the hydraulic pressure source 2 via a constant differential pressure reducing valve 83. Therefore so that hydraulic oil from the hydraulic supply source 2 during the opening of the solenoid valve 9b is supplied to the decompressed output oil passage 66 _F by the pressure reducing valve 83.

Proportional pressure reducing valve 6, which has a well-known structure, the hydraulic transmitting means 5 _R of proportionally reduced pressure to the rear wheel brake device the hydraulic pressure output from the output hydraulic pressure chamber 59 at a certain value or more B
_It functions to act on the brake hydraulic chamber 65 of _RL and B _RR .

The second output port 28 of the auxiliary hydraulic pressure generating means 3
The third output port 29 of the auxiliary hydraulic pressure generating means 3 is connected between the proportional pressure reducing valve 6 and the hydraulic pressure transmitting means 5 _R via _R ,
It is connected between the left front wheel brake device B _FL and the hydraulic transmission means 5 _FL via the 67 _FL , and connected between the right rear wheel brake device B _FR and the hydraulic transmission means 5 _FR via the open / close valve 67 _FR. You. Off valves 67 _FL, 67 _FR, 67 _R are those having the same configuration, will be described only to the following configuration of the on-off valve 67 _FL.

On-off valve 67 _FL is a cylindrical on-off valve body with both ends closed
A valve hole 69 formed in one end wall of the on-off valve body 68 while communicating with the output hydraulic chamber 59 of the hydraulic transmission means 5 _FL ;
An opening / closing piston 72 which has a valve body 70 at one end capable of closing the 69 and is slidably fitted to the opening / closing valve body 68 with the other end facing the pilot chamber 71, and the opening / closing piston 72 is connected to the pilot chamber. A spring 73 is provided between the opening / closing valve body 68 and the opening / closing piston 72 so as to urge it toward the 71 side.

A valve chamber 74 that can communicate with the valve hole 69 is defined between the one end wall of the opening / closing valve body 68 and the opening / closing piston 72, and a spring is formed in the valve chamber 74.
73 is stored. The opening / closing valve body 68 is provided with an inlet port 75 communicating with the valve chamber 74 and communicating with the third output port 29.

According to the opening / closing valve _67FL , when the oil pressure in the pilot chamber 71 is lower than a predetermined value, the opening / closing piston 72 moves to the pilot chamber 71 side until the valve body 70 opens the valve hole 69 and opens. When the oil pressure in the pilot chamber 71 becomes equal to or higher than the predetermined value, the opening / closing piston 72 moves so as to close the valve hole 69 with the valve body 70 and closes the valve.

Branched from the output oil passage 66 _F branch oil passage 84 _FL is communicated to the pilot chamber 71. Therefore, when the oil pressure in the branch oil passage _84FL, that is, the pilot chamber 71 is high, the on-off valve _67FL closes to shut off the connection between the third output port 29 and the brake device _BFL , and the oil pressure in the branch oil passage _84FL decreases. The on-off valve _67FL is opened to allow _{communication} between the third output port 29 and the brake device BFL.

The on-off valve 67 _FR closes when the oil pressure of the branch oil passage 84 _FR branched from the output oil passage 66 _F is high, shuts off the third output port 29 and the brake device B _FR , and the branch oil passage 84 _FR When the hydraulic pressure is low, the valve is opened to communicate between the third output port 29 and the brake device _BFR . Further, the on-off valve 67 _R is connected to the output oil passage 66.
_The valve closes when the oil pressure in the branch oil passage 84 _R branched from _R is high,
As a result, the connection between the second output port 28 of the auxiliary hydraulic pressure generation means 3 and the brake devices B _FL and B _RR is cut off, and the branch oil passage 84 _R
The second output port 28 and the brake device B _RL, between B _RR is communicated with the valve opening pressure is lowered and opening and closing valve 67 _R is.

In the output oil passage 66 _F, the hydraulic transmitting means 5 _FL, 5 _FR side of the branching portion of the branched oil passage 84 _FL, 84 _FR is interposed the first directional valve 85 _F, branched oil at the output oil passage 66 _R a first one-way valve 85 _R is interposed in the hydraulic transmitting means 5 _R side from the branching portion of the road 84 _R. These first one-way valves 85 _F and 85 _R open according to a differential pressure equal to or higher than a preset _first valve opening pressure ΔP ₁ and output ports.
Only the flow of hydraulic oil from the 39 side to the hydraulic transmission means 5 _FL , 5 _FR , 5 _R side is permitted.

Also the the first one-way valve 85 _F, 85 _R second one-way valve 8
6 _F and 86 _R are connected in parallel. These second one-way valves 8
6 _F and 86 _R are opened according to a differential pressure equal to or greater than a preset _second valve opening pressure ΔP _2, and hydraulic oil is transmitted from the hydraulic transmission means 5 _FL , 5 _FR , 5 _R side to the output port 39 side. The second valve opening pressure ΔP ₂ is smaller than the first valve opening pressure ΔP ₁ (Δ
P ₂ <ΔP ₁ ) is set.

By the way, at the time of the braking operation by the brake pedal 1 when the hydraulic pressure supply source 2 is operating normally, prior to the hydraulic pressure rise of the second and third hydraulic chambers 20 and 21 in the auxiliary hydraulic pressure generating means 3, the first hydraulic chamber off valve 67 _FL by 16 the oil pressure of the operation of the hydraulic supply source hydraulic pressure control means 4, 67 _FR, 67 _R are intended to be set so as to valve closing, are set each section as described below.

That is, the input F of the pressing rod 22 by the braking operation of the brake pedal 1 is applied to the first hydraulic chamber 16 of the first working piston 17.
Assuming that the pressure receiving area facing SP is SP ₁₇ and the load of the first return spring 24 is F ₂₄ , it is expressed by the following equation (2).

F = P ₁₆ × SP ₁₇ + F ₂₄ (2) Also, the hydraulic pressure P ₁₆ of the first hydraulic chamber ₁₆ and the hydraulic pressure P ₅₅ of the input pressure action chamber 55 in the hydraulic supply source hydraulic control means 4, that is, the proportionality shown in FIG. relationship between the output pressure of the pressure reducing valve 77, P ₅₅ = P ₁₆ ... when P ₁₆ ≦ p (3) _{becomes, P 16> P 55 = p} + (P 16 -p) when p × θ ... (4) Becomes

In the hydraulic supply source hydraulic control means 4, the pressing piston 36
There hydraulic P ₅₅ output hydraulic chamber 55 to drive the position where the output port 39 to communicate with the input port 40 the spool 34 starts to move against the force F ₄₈ of the control spring 48, the pressure piston 36 the pressure receiving area facing the output hydraulic pressure chamber 55 is expressed by the equation (5) follows upon the SP _36.

P ₅₅ = F ₄₈ / SP ₃₆ … (5) Also, the reaction force piston 35 starts to move against the load F _{54 of the} spring 54 and drives the spool 34 to a position where the output port 39 communicates with the release port 41. hydraulic P _J of the hydraulic or output port 39 of the output pressure application chamber 51 when is expressed by the following equation (6) when the pressure receiving area facing the output pressure application chamber 51 of the reaction piston 35 and the SP ₃₅ You.

_{P J = F 54 / SP 35} ... (6) further output hydraulic pressure P _C from the output port 39 after the hydraulic P _J occurs, satisfies the following first (7) of the relationship.

P _C × SP ₃₅ = P ₅₅ × SP ₃₆ … (7) From such expressions (5) to (7), the input pressure working chamber is obtained.
When showing the relationship between the hydraulic pressure P ₅₅ of 55 and the output hydraulic pressure P _C of the output port 39, so that the third view.

That is, when P ₅₅ ≦ F ₄₈ / SP ₃₆ , the output oil pressure P _C =
Is 0, P _55> F ₄₈ / the SP ₃₆ output hydraulic pressure P _C is represented by the equation (8).

By substituting equation (8) into equations (3) and (4), the following equations (9) and (10) are obtained. That is, the hydraulic pressure P of the first hydraulic chamber 16 in the auxiliary hydraulic pressure generation means 3
_{When 16} is less than or equal to p (P ₁₆ ≦ p), And when P ₁₆ > p, Becomes

By the way, in the on-off valves 67 _FL , 67 _FR , and 67 _R , the on-off pistons 72 are operated by the hydraulic pressure of the valve chamber 74, that is, the hydraulic pressures P ₂₀ and P ₂₁ of the second and third hydraulic chambers 20 and 21 in the auxiliary hydraulic pressure generating means 3.
The hydraulic pressure P ₇₁ of the pilot chamber 71 required to perform the valve closing operation when is 0 is SP ₇₂ when the pressure receiving area of the opening / closing piston 72 facing the pilot chamber 71 is F ₇₂ and the load of the spring 73 is F ₇₃ . It is necessary to satisfy the expression (11).

P ₇₁ > F ₇₃ / SP ₇₂ … (11) The hydraulic pressure P ₁₆ in the first hydraulic chamber 16 in the auxiliary hydraulic pressure generation means 3
The hydraulic pressures P ₂₀ and P ₂₁ generated in the second and third hydraulic chambers 20 and 21 as a result of the occurrence of
When the pressure receiving areas SP ₁₈ and SP ₁₉ at both ends of the 9 are the same (SP ₁₈ = SP ₁₉ ) and the loads of the second and third return springs 25 and 26 are F ₂₅ and F ₂₆ , the following (12) ) And (13).

_{P 20 = (P 16 × SP} 18 -F 25) / SP 18 ... (12) P 21 = (P 16 × SP 18 -F 26) / SP 18 ... (13) where the second and third hydraulic chambers 20 , before pressure P _20, P ₂₁ of 21 for boosting the pressure required to output hydraulic pressure P _C of the output port 39 in the hydraulic pressure supply source hydraulic pressure control means 4 to close the opening and closing valve 67 _FL, 67 _FR, 67 _R to boost up _{the, P 20 = P 21 = 0} ... (14) P C> P 71MIN ... (15) must satisfy the relational expression becomes. However, the (15)
_P71MIN in the equation is the minimum hydraulic pressure in the pilot chamber 71 that satisfies the equation (11).

Thus to P _71MIN is a low pressure, the P ₁₆ at the time of P _71MIN occurs A
When A <p, the hydraulic pressure of the pilot chamber 71 becomes P
_When it is set to be _{71 MIN} , the following expression (9), expression (11), expression (12), expression (13), expression (14), and expression (15) Equations (16), (17) and (18) are derived.

A × SP ₁₈ ≦ F ₂₅ … (16) A × SP ₁₈ ≦ F ₂₆ … (17) Here, F ₄₈ / SP ₃₆ <A.

In this way, by setting so that the above-mentioned expressions (16), (17) and (18) are satisfied, the second and the third hydraulic pressure generating means 3 at the time of the braking operation by the brake pedal 1 are operated. Prior to the rise of the hydraulic pressure in the three hydraulic chambers 20, 21, the operation of the hydraulic supply source hydraulic control means 4 is started by the hydraulic pressure in the first hydraulic chamber 16 in the auxiliary hydraulic pressure generating means 3, and the on-off valves _67FL , _67FR , 67 _R will close. However,
In deriving the above equations, the sliding resistance of each piston, the spring constant of each spring, and the change in spring load when each valve is opened and closed are not taken into account. Must be set.

Next, the operation of this embodiment will be described. First, assuming a normal control operation in a state where the hydraulic supply source 2 is operating normally, the inflow solenoid valves 7 _FL , 7 _FR , 7 _R and the outflow solenoid valves 8 _FL , 8 _FR , 8 _R are in a demagnetized state. (Shown), and both solenoid valves 9a, 9b of the traction control switching control valve means 9.
Are also in the demagnetized state (the state shown). Therefore, the output port 39 of the hydraulic supply source hydraulic control means 4 communicates with the output oil passages 66 _F and 66 _R , and one output oil passage 66 _F is connected to the hydraulic transmission means 5 _FL via the inflow solenoid valves 7 _FL and 7 _FR. , in a state in communication with the input hydraulic pressure chamber 58 of 5 _FR, the other output oil passage 66 _R is in a state of communication with the input hydraulic pressure chamber 58 of the hydraulic transmission means 5 _R through the inlet solenoid valve 7 _R.

When the brake pedal 1 is depressed in such a state, the first operating piston 17 of the auxiliary hydraulic pressure generating means 3 operates forward, and the hydraulic pressure generated in the first hydraulic chamber 16 is reduced by the proportional pressure reducing valve 77 to control the hydraulic supply source hydraulic pressure. It acts on the input pressure action chamber 55 of the means 4 and on the accumulator chamber 91 of the accumulator 78. At this time, the hydraulic pressure control unit 4 is set to start operating earlier than the accumulator 78. That is, the pressure-receiving area S ₁ facing the input hydraulic pressure chamber 55 of the pressure piston 36 in the hydraulic supply source hydraulic pressure control means 4, the pressure receiving area S ₂ which faces the accumulator chamber 91 of the accumulator piston 92, the hydraulic pressure supply source hydraulic pressure control means 4
The set load f ₁ of the control spring 48 and the set load f ₂ of the first accumulator spring 93 in the accumulator 78 are set so that the above inequality expression (1) is satisfied.

As a result, in the hydraulic supply source hydraulic control means 4, the pressing piston 36 moves forward before the accumulator 78 performs the pressure accumulation operation,
The spool 34 whose rear end is in contact with the pressing piston 36 is driven forward. Accumulator like this
By starting the operation of the hydraulic pressure control means 4 prior to the pressure accumulating operation of 78, it is possible to avoid the generation of useless reaction force during the braking operation, to prevent the loss of the pedaling force of the brake pedal 1, and to improve the responsiveness. Can be.

The output port 39 communicates with the input port 40 when the spool 34 moves forward by a certain distance in accordance with the advance of the pressing piston 36, and the output hydraulic pressure from the output port 39 which communicates with the hydraulic pressure supply source 2 increases rapidly. . Thus was first one-way valve 85 at the output oil passage 66 _F, 66 _R are _F, 85 _R of the differential pressure across the first valve opening pressure [Delta] P ₁
Branch oil passage 84 before the reaching _FL, 84 _FR, 84 off valves 67 _FL, 67 _FR, 67 _R are first closed in response to the oil pressure increase in _R, then the differential pressure is first valve opening pressure [Delta] P ₁ or more in response to a first one-way valve 85 _F, 85 _R is opened. Thereby, _F hydraulic pressure output oil passage 66 from the output port 39 and the inlet solenoid valve 7 _FL, 7 hydraulic transmission means via the _FR 5 _FL, 5 and acts on the input hydraulic pressure chamber 58 of the _FR brake device B _FL, B _FR in can be obtained braking pressure, also oil pressure from the output port 39 output oil passage 66 _R and the inlet solenoid valve 7
Through _R acts on the input hydraulic pressure chamber 58 of the hydraulic transmission means 5 _R, the hydraulic transmission means 5 _R output hydraulic chamber 59 pressure is depressurized by the rear wheel brake device by a proportional pressure reducing valve 6 B outputted from the _RL , B _RR . Therefore, during braking, the hydraulic transmission means
5 _FL, 5 _FR, 5 _R off valve before the operation of the 67 _FL, 67 _FR, 67 _R
, The braking pressure is increased at the same time as the operation of the hydraulic transmission means 5 _FL , 5 _FR , 5 _R to improve the responsiveness.

Moreover, at the time of the braking operation, the hydraulic supply source hydraulic control means 4 by the hydraulic pressure of the first hydraulic chamber 16 is operated prior to the rise of the hydraulic pressure of the second and third hydraulic chambers 20 and 21 in the auxiliary hydraulic pressure generating means 3 to open and close. because it is set the valve 67 _FL, 67 _FR, 67 _R so as to close the second and third hydraulic chambers 20, 21
It is possible to prevent the braking feeling from being deteriorated due to the action of the hydraulic pressure on the brake devices B _FL , B _FR , B _RL , and B _RR .

Further, as the output oil pressure from the output port 39 rapidly increases, the play gaps of the respective brake devices B _FL , B _FR , B _RL , and B _RR are removed by supplying a relatively high oil pressure, and the respective brake devices are removed. _BFL , _BFR , _BRL , _BRR braking piston 64
Initial operation becomes smooth.

Due to the communication of the output port 39 with the input port 40, the hydraulic pressure of the output pressure working chamber 51 also increases, and the reaction force piston 35 is driven rearward to abut the front end of the spool 34, whereby the spool 38 retreats. The output port 39 is cut off from the input port 40. Further, as the hydraulic pressure in the first hydraulic chamber 16 increases by depressing the brake pedal 1, the spool
34 advances again, and the output port 39 communicates with the input port 40. In this way, in response to the braking operation of the brake pedal 1, the spool 34 reciprocates between the front position where the output port 39 communicates with the input port 40 and the rear position where the output port 39 is disconnected from the input port 40. Accordingly, the hydraulic pressure of the hydraulic pressure supply source 2 is controlled according to the braking operation amount of the brake pedal 1 and output from the output port 39.

In this manner, the hydraulic pressure from the hydraulic supply source 2 can be controlled by the hydraulic supply source hydraulic control means 4 according to the braking operation amount and applied to each of the brake devices B _FL , B _FR , B _RL , and B _RR . In the hydraulic transmission means 5 _FL , 5 _FR , 5 _R , the free piston 60
Since each of the brake devices B _FL , B _FR , B _RL , and B _RR is isolated from the hydraulic circuit from the input hydraulic chamber 58 to the hydraulic supply 2, there is a possibility that the hydraulic supply 2 mixes with the hydraulic oil. The gas does not adversely affect each of the brake devices _BFL , _BFR , _BRL , and _BRR .

At this time, when the hydraulic pressure in the first hydraulic chamber 16 in the auxiliary hydraulic pressure generating means 3 increases in response to the depression operation of the brake pedal 1 and the hydraulic pressure in the second and third hydraulic chambers 20 and 21 increases due to volume contraction, the second and third hydraulic chambers increase. While hydraulic pressure is outputted from the third output port 28 and 29, on-off valve 67 _FL, 67 _FR, 67 since _R is closed, hydraulic pressure is the brake device B _FL of the hydraulic chambers 20 and 21,
B _FR, B _RL, not to act on B _RR.

At the time of this braking, the braking force of the left and right rear wheels needs to be lower than that of the left and right front wheels, and the braking force of the left and right rear wheels is reduced by reducing the hydraulic pressure from the hydraulic pressure supply source hydraulic control means 4 by the proportional pressure reducing valve 6. It is lower at a fixed ratio than the left and right front wheels.

Further, since the oil pressure in the first oil pressure chamber 16 acts on the input pressure action chamber 55 via the proportional pressure reducing valve 77, the oil pressure acting on the input pressure action chamber 55 and the accumulator 78 is kept low, and the oil pressure supply source oil pressure control means 4 This can contribute to reducing the load on the accumulator 78. In addition, when the brake pedal 1 is idled several times, the hydraulic pressure in the first hydraulic chamber 16 is reduced by the proportional pressure reducing valve 77 and applied to the input pressure action chamber 55,
The frequency of hydraulic pressure increase after the hydraulic pressure control unit 4 can be reduced, the amount of hydraulic oil circulated can be reduced to reduce wasteful consumption of hydraulic oil, and the free piston 60 in the hydraulic transmission units 5 _{FL to} 5 _R can be controlled. The operation frequency can be suppressed to contribute to the improvement of durability.

Further, by accumulating the hydraulic pressure from the first hydraulic chamber 16 with the accumulator 78, the pedal stroke of the brake pedal 1 can be ensured, so that the hydraulic supply source hydraulic control means 4 has a configuration for ensuring the pedal stroke. This is unnecessary, and the hydraulic supply hydraulic pressure control means 4 can be reduced in size. In addition, it is possible to prevent the sudden reaction force from directly acting on the brake pedal 1 due to the damper action by the accumulator 78 when the sudden reaction force acts.

At the time of such braking, when the pedaling force of the brake pedal 1 becomes excessive and the wheels are about to be locked, the inflow solenoid valves 7 _FL and 7 _FL corresponding to the wheels that are about to be locked
7 _FR and 7 _R are excited, and the output oil passage 66 _F and the hydraulic transmission means 5
_{Between FL} and 5 _FR , output oil passage 66 _R and hydraulic transmission means 5 _R
Cut off between. This suppresses an increase in the braking force to avoid the wheels from being locked. This while still wheel is likely to enter the locked state, the input hydraulic pressure chamber 58 of the corresponding outlet solenoid valve 8 _FL, 8 _FR, 8 hydraulic transmission means by energizing the _R 5 _FL to 5 _R communicates with the reservoir R, By lowering the braking pressure, the tendency to lock the wheels can be eliminated.

After the lock tendency is eliminated, the inflow solenoid valves 7 _FL , 7 _FR ,
Demagnetize 7 _R and demagnetize outflow solenoid valves 8 _FL , 8 _FR and 8 _R. Thus, the output port of the hydraulic pressure control unit 4
The hydraulic pressure from 39 is applied again to the hydraulic pressure transmission means 5 _FL , 5 _FR , 5 _R to increase the braking pressure.

By controlling the operation of the solenoid valve 9a in the traction control switching valve means 9 at the time of pressure increase in such an anti-lock control state, the anti-lock control of both front wheels can be performed more precisely. That is, by intermittently closing the solenoid valve 9a, it is possible to prevent the oil pressure from the output port 39 from acting on each of the inflow solenoid valves _7FL and _7FR abruptly, and to moderate the increase in oil pressure. Also, when anti-lock control is performed on the front wheels that are in contact with the road surface with a low friction coefficient while the friction coefficients of the ground road surfaces of the left and right front wheels are different, braking with the front wheels that are in contact with the road surface with a high friction coefficient It is also possible to suppress the rise in pressure by the intermittent closing operation of the solenoid valve 9a, and to gently suppress the generation of the yaw moment of the vehicle body.

It is assumed that a high hydraulic pressure cannot be obtained from the hydraulic pressure supply source 2 due to a failure of the hydraulic pump 11 or the like during the braking. In this case, the branch oil passage 84 in accordance with the oil pressure from the output port 39 of the hydraulic supply source hydraulic pressure control means 4 _FL, 84 _FR, 84 on-off valve 67 by the hydraulic pressure drop in _{R FL,} 67 _FR, 67 _R is opened I do. Therefore, the braking hydraulic pressure generated in the second and third hydraulic chambers 20 and 21 of the auxiliary hydraulic pressure generating means 3 directly acts on each of the brake devices B _{FL to} B _RR , and the braking force can be secured. .

At this time, the hydraulic transmission means 5 _{FL to} 5 _R are connected to the respective brake devices B _FL to
The brake pressure of each of the brake devices B _{FL to} B _RR does not escape to the hydraulic pressure control unit 4 side because it is interposed between the B _RR and the hydraulic pressure control unit 4.

During non-braking after braking operation ends, the branch oil passage 84 _FL in accordance with the output oil pressure of the output port 39, 84 _FR, 84 first closing valve 67 _FL by oil pressure of the _R, 67 _FR, 67 _R is opened. Then, the second one-way valve 86 _F, 86 _R of the differential pressure across the second valve opening pressure level [Delta] P ₂
As a result, the second one-way valves 86 _F and 86 _R open,
The input hydraulic chamber 58 in each of the hydraulic transmission means 5 _{FL to} 5 _R communicates with the reservoir R via the hydraulic supply source hydraulic control means 4. Therefore, the free piston 6 in the hydraulic transmission means 5 _{FL to} 5 _R
The output hydraulic chamber 59 can be breathed according to the movement of the input hydraulic chamber 58 to zero. In addition, the hydraulic pressure in the input hydraulic chamber 58 in each of the hydraulic transmission means 5 _{FL to} 5 _R is controlled by the hydraulic release one-way valve 81 _FL , 8
It is possible to escape to 1 _FR, 81 via the _R output oil passage 66 _F, 66 _R, the hydraulic pressure releasing of the inlet solenoid valve 7 _FL, 7 _FR, 7 the even flow resistance is large at the _R input hydraulic pressure chamber 58 And the free piston 60 can be quickly returned to the original position.

By the way, it is conceivable that the hydraulic pressure in the input hydraulic chamber 58 increases due to the temperature rise in each of the hydraulic transmission means 5 _FL , 5 _FR , 5 _R during non-braking, and in this case, if the hydraulic pressure cannot be released, the braking pressure is applied. become. However, the second one-way valve
86 _F, 86 second valve opening pressure [Delta] P ₂ of the _R first smaller than the valve opening pressure [Delta] P ₁ of the first one-way valve 85 _F, 85 _R, since it is set to a relatively small value, the input hydraulic The valve is opened according to the increase in the oil pressure of the chamber 58, and the hydraulic oil corresponding to the increase in the oil pressure can be released.

Further, when the driving force of the engine becomes excessive and the driving wheels are likely to slip excessively, both solenoid valves 9a and 9b of the traction control switching control valve means 9 are excited by the control means 80. As a result, the hydraulic pressure from the hydraulic pressure supply source 2 acts on the input hydraulic chamber 58 of the hydraulic transmission means 5 _FL , 5 _FR , and braking force is generated by the brake devices B _FL , B _FR of the left and right front wheels, which are drive wheels, resulting in excessive slip. Is avoided. Thereafter, as in the case of anti-lock control described above, the excitation and demagnetization control of the inlet solenoid valve 7 _FL, 7 _FR and the outlet solenoid valves 8 _FL, 8 _FR, can control the braking force.

Moreover, the output oil pressure of the hydraulic supply source 2 is set to be considerably large.
Thus, the traction control is not performed by an excessive oil pressure.
Therefore, control responsiveness does not decrease or become smooth.

In the above embodiment, the first housing 14 of the auxiliary hydraulic pressure generating means 3 and the second housing 33 of the hydraulic pressure
And are configured separately, but may be configured integrally.

C. Effects of the Invention As described above, according to the present invention, during normal braking in which the hydraulic pressure of the hydraulic supply source is normal, the hydraulic supply source hydraulic control unit uses the hydraulic pressure from the auxiliary hydraulic pressure generation unit that operates according to the braking operation. Is started to close the on-off valve first to obtain the braking force by the hydraulic pressure from the hydraulic supply source hydraulic control means. Therefore, the hydraulic pressure from the auxiliary hydraulic pressure generating means acts on the brake device to provide a braking feeling. Can be prevented from becoming worse. Also, when the hydraulic pressure of the hydraulic supply source drops abnormally, by opening the on-off valve, the hydraulic pressure from the auxiliary hydraulic pressure generating means can be applied to the brake device to obtain a braking force. The oil pressure of the device can be prevented from escaping to the oil pressure supply side by the oil pressure transmission means.

[Brief description of the drawings]

The drawings show an embodiment of the present invention. FIG. 1 is a hydraulic circuit diagram, FIG. 2 is a pressure reducing characteristic diagram of a proportional pressure reducing valve, and FIG. 3 is an output hydraulic pressure characteristic diagram of a hydraulic supply hydraulic pressure control means. is there. 1 ... brake pedal, 2 ... hydraulic supply source, 3 ... auxiliary hydraulic pressure generation means, 4 ... hydraulic supply source hydraulic control means, 5 _FL , 5
_FR , 5 _R …… Hydraulic transmission means, 14 …… First housing, 16,2
0,21 ... Hydraulic chamber, 17,18,19 ... Working piston, 33 ... Second housing, 34 ... Spool, 39 ... Output port, 40
…… Input port, 41 …… Release port, 48 …… Control spring,
51 …… Output pressure action chamber, 55 …… Input pressure action chamber, 58 …… Input hydraulic chamber, 59 …… Output hydraulic chamber, 60 …… Free piston, 61
…… Cylinder body, 67 _FL , 67 _FR , 67 _R …… On-off valve, B _FL , B
_FR , B _RL , B _RR ...... Brake device, R ...... Reservoir

 ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Kazutoshi Tajima 1-4-1 Chuo, Wako-shi, Saitama In-house Honda R & D Co., Ltd. (56) References JP-A-61-102360 (JP, A) Showa 55-63944 (JP, A) JP-A-2-306855 (JP, A) U.S. Pat. No. 3,827,759 (US, A)

Claims (1)

(57) [Claims] An auxiliary hydraulic pressure generating means capable of generating a hydraulic pressure according to a brake operation of a brake pedal, and an oil pressure from a hydraulic pressure supply source being controllable according to a brake operation of a brake pedal, between an oil pressure supply source and a brake device. And a hydraulic supply source hydraulic control means interposed in the brake hydraulic control apparatus, wherein the auxiliary hydraulic pressure generating means includes a plurality of operating pistons interlocked with each other to move forward in accordance with a braking operation of a brake pedal. Are slidably fitted to the first housing with the front faces of the hydraulic chambers facing each other, and the hydraulic supply hydraulic control means has an output port, an input port leading to the hydraulic supply source, and a release port leading to the reservoir. The spool is slidable in the second housing to switch the communication between the output port, the input port, and the release port according to the axial movement. The output port is adapted to exert a hydraulic pressure in a direction in which the input pressure working chamber and the output port communicate with the release port, the hydraulic pressure urging the spool in a direction in which the output port communicates with the input port. And an output pressure action chamber communicating with the free piston is provided in the second housing, and the output port faces the input hydraulic chamber which can communicate with the output port and the output hydraulic chamber which communicates with the brake device with both end faces facing each other. Is connected to a brake device via hydraulic transmission means slidably fitted to a cylinder body, and one hydraulic chamber of the auxiliary hydraulic pressure generation means is connected to an input pressure action chamber of a hydraulic supply source hydraulic control means. The other hydraulic chamber of the auxiliary hydraulic pressure generating means is connected between the hydraulic pressure transmitting means and the brake device via an open / close valve which closes in response to an increase in the output hydraulic pressure of the hydraulic pressure source hydraulic control means. The opening / closing valve is closed by the output hydraulic pressure rise of the hydraulic supply source hydraulic control means that receives and operates the hydraulic pressure of the one hydraulic chamber before the hydraulic pressure of the other hydraulic chamber rises during the braking operation by the brake pedal. A brake hydraulic control device set to operate a valve.