JP2632222B2 - Proportional pressure reducing valve - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Object of the Invention (1) Industrial Application Field The present invention relates to a housing having an input port and an output port, and a valve piston having one end disposed on a stopper side fixed to the housing. The one end face faces the output hydraulic chamber communicating with the output port, and the other end faces the input hydraulic chamber communicating with the input port. ,
A valve hole connecting the input hydraulic chamber and the output hydraulic chamber is formed at one end of the valve piston, and a valve element capable of closing the valve hole is housed in the input hydraulic chamber while being biased by a spring in a valve closing direction. A proportional pressure reducing valve.

(2) Prior Art Conventionally, such a proportional pressure reducing valve is known, for example, from Japanese Patent Publication No. 58-3851.

(3) Problems to be Solved by the Invention By the way, such a proportional pressure reducing valve is used, for example, in a brake hydraulic pressure control device for a vehicle. In some cases, a proportional pressure reducing valve is provided at a position where the pressure reducing valve is to be provided. In this case, an on-off valve is conventionally provided upstream or downstream of the proportional pressure reducing valve. Therefore, an on-off valve is required in addition to the proportional pressure reducing valve, and the number of parts has increased.

The present invention has been made in view of such circumstances,
It is an object of the present invention to provide a proportional pressure reducing valve which has not only a proportional pressure reducing function but also a fully closed state, thereby reducing the number of parts.

B. Configuration of the Invention (1) Means for Solving the Problems According to the present invention, the housing has one end face facing the pilot chamber and the other end face capable of contacting the stopper facing the output hydraulic chamber. The regulating piston is slidably fitted coaxially with the valve piston, and at least one of the regulating piston and the valve body has a protrusion that can abut the other of the regulating piston and the valve body. The protruding member has a length that sets the valve body to the valve opening position in a state where the valve body is at a predetermined proximity position.

(2) Operation According to the above configuration, the regulating piston is in contact with the stopper when high oil pressure is acting on the pilot chamber,
In this state, the valve piston contacts the stopper and the valve body opens the valve hole until the oil pressure in the output hydraulic chamber becomes a certain value or more, and the valve piston opens when the oil pressure in the output hydraulic chamber becomes a certain value or more. The valve body closes the valve hole in response to the spring coming away from the stopper against the spring force, and when the oil pressure in the input hydraulic chamber increases in the valve hole closed state, the valve piston moves to the stopper side and the valve hole is re-opened. Is released, and by repeating such an operation, the hydraulic pressure at the input port is reduced and output from the output port, and when the hydraulic pressure in the pilot chamber decreases, the regulating piston is moved by the hydraulic pressure in the output hydraulic chamber to the pilot chamber side. In this state, the valve hole remains closed by the valve body, and the input port and the output port are shut off.

(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.

First, in FIG. 1, a left front wheel brake device B _FL and a right front wheel brake device B are provided on the left front wheel and the right front wheel of the vehicle.
_FR is mounted, and a left rear wheel brake device B _RL and a right rear wheel brake device B _RR are mounted on the left rear wheel and the right rear wheel, respectively. On the other hand, an auxiliary hydraulic pressure generating means 3 for outputting a hydraulic pressure according to the amount of depression of the brake pedal 1 is connected to the brake pedal 1, and during normal braking, hydraulic pressure is supplied according to the hydraulic pressure output from the auxiliary hydraulic pressure generating means 3. The hydraulic pressure from the hydraulic supply source 2 controlled by the source hydraulic control means 4 is applied to each front wheel brake device B via hydraulic transmission means 5 _FL and 5 _FR.
FL, with given B _FR, hydraulic pressure from the hydraulic pressure supply source hydraulic pressure control means 4 is a hydraulic transmitting means 5 _R and proportional pressure reducing valves 6 B brake system for rear wheels through the _RL, given B _RR. Further, during a braking operation when the hydraulic pressure supply source 2 becomes malfunctioning, the hydraulic pressure generated by the auxiliary hydraulic pressure generating means 3 is applied to each brake device.
B _FL , B _FR , B _RL , and B _RR . In addition, each front wheel brake device B _FL, B _FR individually corresponding flow solenoid valve 7 provided _FL, 7 _FR and the outlet solenoid valves 8 _FL, 8 _FR and the rear wheels brake device B _RL, common to B _RR Inflow solenoid valve 7 _R provided in
And each braking device B _FL by outlet solenoid valve 8 _R, B _FR, B
_RL, held or reduced the braking oil B _RR can be performed antilock control, performing the brake device B _FL, increased by the traction control braking oil B _FR by the traction control changeover valve means 9 be able to.

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. In a first cylinder hole 15 provided in the first housing 14, a first working piston 16 is provided.
And a second working piston 17 disposed at an interval in front of the first working piston 16 are slidably fitted to each other, and a first hydraulic chamber is provided between the first working piston 16 and the second working piston 17. The front end wall of the first cylinder hole 15 and the second
A second hydraulic chamber 19 is formed between the working pistons 17.

The first working piston 16 has a piston rod 16 that movably penetrates a rear end wall of the first cylinder hole 15 and protrudes outward.
a is provided integrally, and the front end of the pressing rod 20 connected to the brake pedal 1 abuts on the piston rod 16a. Therefore, the first working piston 16 moves forward in the first cylinder hole 15 in response to the braking operation of the brake pedal 1.

On the inner surface of the first cylinder hole 15, a regulating flange 21 which abuts on the rear end of the second working piston 17 and regulates the retreat limit of the second working piston 17 is provided so as to protrude radially inward. A first return spring 22 for urging the first working piston 16 rearward is contracted between the regulating flange 21 and the first working piston 16. A second return spring 23 for urging the second working piston 17 rearward is contracted between the front end wall of the first cylinder hole 15 and the second working piston 17. This allows the first working piston
By generating the hydraulic pressure in the first hydraulic chamber 18 according to the forward operation of the
The second working piston 17 moves forward. However, the set load of the second return spring 23 is increased by the hydraulic pressure from the hydraulic pressure source hydraulic pressure control means 4 which operates in accordance with the hydraulic pressure of the first hydraulic chamber 18, after the on-off valves 104 _FL and 104 _FR described later are closed. 2-acting piston
It is set to the extent that 17 moves forward.

Also, the first housing 14 has a first hydraulic chamber 18 connected to the first hydraulic chamber 18.
Output port 24 and second output port leading to second hydraulic chamber 19
25, and each hydraulic chamber is set only when the first working piston 16 and the second working piston 17 return to the retreat limit.
Communication ports 26 and 27 are formed to communicate the ports 18 and 19 with the reservoir R.

The hydraulic supply source hydraulic control means 4 includes a second housing 30,
A spool 31, which is slidably fitted to the second housing 30,
A reaction force piston 32, a first pressing piston 33, and a second pressing piston 34 are provided.

The second housing 30 comprises an outer cylindrical portion 35 closed at both ends and an inner cylindrical portion 36 coaxially disposed in the outer cylindrical portion 35 and open at both ends, which are fixed to each other at an intermediate portion thereof. The outer cylinder 35 has an output port 37 and an input port 3 connected to the hydraulic pressure source 2.
8, and release ports 39 communicating with the reservoir R are provided at intervals in order from the front side to the rear side (from left to right in FIG. 1). The inner cylinder portion 38 is provided with a second cylinder hole 40, and the input port 38 is opened on the inner surface of the second cylinder hole 40. Moreover, an annular concave portion 41 is provided on the outer surface of the spool 31 slidably fitted in the second cylinder hole 40, and the axial length of the annular concave portion 41 is set when the spool 31 is at the rear position. It is set to communicate between the output port 37 and the release port 39 and to communicate between the output port 37 and the input port 38 when the spool 31 is at the front position.

At the rear end of the spool 31, there is a flange extending outward in the radial direction.
The flange 31a and the second housing 30 are provided.
A spring 42 is contracted between the spool 31 and the spool 31, and the spool 31 is biased rearward by the spring force of the spring 42.

The reaction force piston 32 is capable of contacting the front end of the spool 31 and is slidably fitted in the second cylinder hole 40 at a position in front of the spool 31. On the other hand, a cap-shaped member 43 is fitted to the front end of the inner cylinder portion 36, and the cap-shaped member 43 is moved rearward by a spring force of a spring 44 contracted between the inner cylinder portion 36 and the front end wall of the outer cylinder portion 35. It is urged toward the side. Thus, the cap-shaped member 43 and the reaction force piston
An output pressure action chamber 45 facing the front surface of the reaction force piston 32 is defined between the output pressure action chamber 32 and the output pressure action chamber 45 through a communication hole 46 formed in the cap-shaped member 43. Connects to output port 37.

A spring 47 is contracted between a step portion provided on the inner surface of the second cylinder hole 40 on the front side of the spool 31 and the reaction piston 32, and the reaction piston 32 is compressed by the spring force of the spring 47.
Is urged forward. Moreover, the set load of the spring 47 is set smaller than the set load of the spring 44, and in a state where no hydraulic pressure is acting on the output pressure action chamber 45,
The front end of the reaction force piston 32 is in contact with the cap-shaped member 43 which is urged by the spring 44 and is in contact with the front end of the inner cylinder portion 36.

The spool 31 has a communication passage communicating with the release port 39.
48 is bored in the front end surface of the spool 31 so as to open.
Therefore, no hydraulic pressure acts on the rear surface of the reaction force piston 32 and the front surface of the spoo 31.

The first pressing piston 33 is slidably fitted to a portion of the second housing 30 near the rear end of the outer cylindrical portion 35 on the rear side of the spool 31 so as to coaxially contact the rear end of the spool 31. You. In the outer cylindrical portion 35 of the second housing 30, behind the first pressing piston 33, a small-diameter portion having a closed rear end.
35a is protruded coaxially, and the second pressing piston 34 is
The small diameter portion is coaxially abutted on the rear end of the first pressing piston 33.
It is slidably fitted to 35a. Thus, a first input pressure action chamber 51 is defined between the first and second pressing pistons 33 and 34, and a second input pressure action chamber is provided between the rear end wall of the small diameter portion 35a and the second pressing piston 34. 52 is defined.

In this hydraulic supply source hydraulic control means 4, the output pressure action chamber 45
The hydraulic pressure toward the rear side acting on the reaction force piston 32 by the hydraulic pressure and the hydraulic pressure in the first input pressure acting chamber 51 or the second input pressure acting chamber 52 cause the first pressing piston 33 or the second pressing piston 34 to move. The spool 31 moves in the axial direction by the balance with the hydraulic pressure acting on the front side, and the pressure receiving area of the first pressing piston 33 facing the first input pressure action chamber 51 is the output of the reaction force piston 32. It is set larger than the pressure receiving area facing the pressure action chamber 45. Therefore, the spool 31 can be driven in the axial direction even if the hydraulic pressure introduced into the first input pressure action chamber 51 is relatively low.

By the way, an oil passage 53 leading to the first input pressure action chamber 51 of the hydraulic supply source oil pressure control means 4 is connected to the first output port 24 of the auxiliary oil pressure generation means 3 via a proportional pressure reducing valve 54 according to the present invention. A branch oil passage 53a branched from the oil passage 53 is connected to the accumulator 56. Moreover, the branch oil passage 53a is made of a high-pressure rubber hose.

The accumulator 56 includes an accumulator main body 57, an accumulator piston 59 that is slidably fitted to the accumulator main body 57 while defining an accumulator chamber 58 connected to the oil passage 53 therebetween, and the accumulator chamber 58. First and second accumulator springs 60, 61 interposed in series between the accumulator piston 59 and the accumulator body 57 to urge the accumulator piston 59 in the direction of contracting the volume of the accumulator piston 59.
And

The accumulator body 57 has a small-diameter hole with one end closed.
62 and a large-diameter hole 64, one end of which is coaxially connected to the other end of the small-diameter hole 62 via a step 63 and the other end of which is closed, is bored. An accumulator piston 59 slides into the small-diameter hole 62. It is movably fitted. Moreover, a pressure accumulating chamber 58 is defined between one end of the accumulator piston 59 and one closed end of the small-diameter hole 62. The large-diameter portion 64 accommodates a spring receiving member 65 that is in contact with the stepped portion 63 and is restricted from moving to the one end side so as to be movable in the axial direction. The first accumulator spring 60 includes an accumulator piston 59 and an accumulator piston 59. Contracted between the spring receiving members 65,
The second accumulator spring 61 includes a spring receiving member 65 and a large diameter portion 64.
Is closed between the other end and the closed end. In addition, the set load of the first accumulator spring 60 is
Is set smaller than the set load. Therefore, when the oil pressure is not acting on the pressure accumulating chamber 58, the spring receiving member 65 is in a position in contact with the step 63 by the spring force of the second accumulator spring 61.

According to such an accumulator 56, with respect to the stroke change rate of the accumulator piston 59 until the hydraulic pressure acting on the pressure accumulating chamber 58 reaches a certain value, after the hydraulic pressure acting on the pressure accumulating chamber 58 reaches a certain value. Accumulator piston 59
The change rate of the stroke can be reduced to contribute to the miniaturization of the whole, and the stroke change rate can be smoothly changed by using the high pressure rubber hose for the branch oil passage 53a.

By the way, as long as the proportional pressure reducing valve 54 is not in the closed state, the first operating piston 16 corresponding to the depression operation of the brake pedal 1 is operated.
The hydraulic pressure generated in the first hydraulic chamber 18 by the forward operation is reduced by the proportional pressure reducing valve 54, and then accumulated in the accumulator 56 and acts on the first input pressure action chamber 51.
The operating pressure of the hydraulic supply hydraulic control unit 4 is set lower than the operating pressure of the accumulator 56 so that the hydraulic supply hydraulic control unit 4 starts operating before the accumulator 56 operates. That is, the pressure receiving area of the first pressing piston 33 facing the first input hydraulic chamber 51 in the hydraulic supply source hydraulic control means 4 is set to
S ₁ , the pressure receiving area of the accumulator piston 59 facing the pressure accumulating chamber 58 is S ₂ , the set load of the spring 42 in the hydraulic pressure control unit 4 is f _1, and the set load of the first accumulator spring 60 in the accumulator 56 is When f ₂ is set, the following equation (1) is established.

f ₁ / S ₁ <f ₂ / S ₂ (1) In FIG. 2, the proportional pressure reducing valve 54 is configured to close when the hydraulic pressure of the hydraulic pressure supply source 2 drops abnormally. An oil passage 53 communicating with the first input pressure action chamber 51 and an oil passage 66 communicating with the first output port 24 of the auxiliary hydraulic pressure generating means 3.
It is interposed between.

Thus, the proportional pressure reducing valve 54 has an input port 67, an output port
A third housing 70 as a housing having a 68 and a pilot port 69, a stopper 71 fixed to an intermediate portion in the third housing 70, and an output hydraulic chamber 72 communicating with the output port 68 with one end faced. A valve piston 73 slidably fitted to the third housing 70, and the valve piston 73 is contracted between the third housing 70 and the valve piston 73 while exerting a spring force in a direction in which the valve piston 73 comes into contact with the stopper 71. A spring 74 and an input hydraulic chamber 75 communicating with the input port 67 are defined between the other surface of the valve piston 73 so as to be relatively slidable while being fitted to the other end of the valve piston 73 and the stopper. Inner piston 76 whose movement limit on the side away from 71 is regulated by third housing 70
A valve hole 77 formed at one end of a valve piston 73 connecting the input hydraulic chamber 75 and the output hydraulic chamber 72, and a valve element housed in the input hydraulic chamber 75 so that the valve hole 77 can be closed. 78, a spring 79 contracted between the inner piston 76 and the valve body 78 to exert a spring force for urging the valve body 78 toward the closing side, and one end face on the side opposite to the valve piston 73 with respect to the stopper 71. A regulating piston 81 slidably fitted to the third housing 70 on the same axis as the valve piston 73 while facing the pilot chamber 80 and the other end face capable of contacting the stopper 71 toward the output hydraulic chamber 72. And a third housing 70 for exerting a spring force for urging the regulating piston 81 toward the stopper 71.
And a spring 82 contracted between the regulating pistons 81.

The third housing 70 has a bottomed cylinder fitted into the cylindrical body 83 with the stopper 71 side as an open end while a stopper 71 is interposed between the cylindrical body 83 and an intermediate step portion in the cylindrical body 83. Body 84, a cap 85 screwed to one end of the cylindrical body 83 to sandwich the stopper 71 and the bottomed cylindrical body 84 between the intermediate step portion, and a cap 85 to close the other end of the cylindrical body 83. And an end plate 86 fixed to the cylindrical body 83. Thus, the input port 67, the output port 68, and the pilot port 69 are formed in the cylindrical body 83.

The valve piston 73 is basically formed in a cylindrical shape with a bottom, and has one end, that is, a closed end, at the stopper 71.
And is slidably fitted to the cylindrical body 83. The spring 74 is contracted between the end plate 86 and the valve piston 73.
Further, the inner piston 76 is connected to the stopper 71 by the end plate 86.
The input hydraulic chamber 75 defined between the valve piston 73 and the inner piston 76 has a plurality of communication holes 87 formed in the side of the valve piston 73. Through the input port 67. In addition, an oil passage 66 communicating with the first output port 24 of the auxiliary hydraulic pressure generating means 3 is connected to the input port 67.

The stopper 71 has a plurality of through-holes 88 and is formed in a disk shape. The regulating piston 81 is slidably fitted to the bottomed cylindrical body 84 on the opposite side of the stopper 71 from the valve piston 73. Is done. Thus, a pilot chamber 80 is formed between the closed end of the bottomed cylindrical body 84 and one end face of the regulating piston 81. The pilot chamber 80 is formed by a plurality of communicating holes formed in the bottomed cylindrical body 84. The hole 89 communicates with the pilot port 69. Moreover, an oil passage 90 connected to the pilot port 69
Is connected to the hydraulic pressure source 2. The regulating piston 81 is urged by a spring 82 contracted between the closed end of the bottomed cylindrical body 84 and the regulating piston 81 in a direction in which the other end surface contacts the stopper 71.

The output hydraulic chamber 72 is formed between one end surface of the valve piston 73 and the other end surface of the regulating piston 81 with a stopper 71 having a plurality of through holes 88 interposed therebetween. Output port drilled into cylindrical body 83 for communication
The oil passage 53 is connected to 68.

The other end of the regulating piston 81 has a stopper at the other end.
In a state where the stopper 71 abuts, a protruding portion 81a is provided in which the front end surface is flush with the end surface of the stopper 71 on the valve piston 73 side.
The valve body 78 housed in the input hydraulic chamber 75 has a valve hole.
A shaft portion 78a that gently penetrates 77 is provided integrally, and the shaft portion 78a can contact the tip of the protruding portion 81a. When the regulating piston 81 is in contact with the stopper 71 and the valve piston 73 is at a position close to the regulating piston 81, the shaft portion 78a is pushed by the projecting portion 81a, so that the valve body 78 has a valve hole. It is in the position to open 77.

In such a proportional pressure reducing valve 54, when normal high oil pressure is acting on the pilot chamber 80 from the oil pressure supply source 2, the restricting piston 81 is in contact with the stopper 71. In this state, the valve piston 73 contacts the stopper 71 until the hydraulic pressure in the output hydraulic chamber 72 becomes higher than the hydraulic pressure determined by the spring 74, and the valve element 78
Has opened the valve hole 77, and the hydraulic pressure of the input port 67 is output from the output port 68 as it is. As a result, the hydraulic pressure in the output hydraulic chamber 72 increases, and the valve piston resists the spring force of the spring 74.
As the 73 moves away from the stopper 71, the valve 78
When the oil pressure in the input hydraulic chamber 75 increases while the valve hole 77 is closed, the valve piston 73 moves to the stopper 71 side, and the valve hole 77 is opened again. The oil pressure of 67 is reduced and the output port 68
Will be output. Further, when the operation of the hydraulic pressure supply source 2 becomes abnormal and the oil pressure in the pilot chamber 80 drops abnormally, the regulating piston 81 is moved by the oil pressure in the output oil pressure chamber 72 to the spring 82.
Moves to the side of reducing the volume of the pilot chamber 80 against the spring force of the
77 remains closed by the valve element 78 and the input port 67
And between the output ports 68. In addition, since the regulating piston 81 is pressed toward the stopper 71 by the spring 82, air can be released from the line from the oil passage 66 to the oil passage 53 even when the hydraulic pressure is not acting on the pilot chamber 80.

The hydraulic transmission means 5 _FL , 5 _FR , and 5 _R are connected to the output port 37 of the hydraulic supply source hydraulic control means 4 and the brake devices B _FL , B _FR , B _RL , and B _RR.
And the hydraulic transmission means 5 _FL , 5 _FR
Is a normally open solenoid valve of the traction control switching control valve means 9 connected to the output port 37 of the hydraulic supply source hydraulic control means 4.
9a and the brake device B _FL , B _FR, and the hydraulic transmission means
5 _R is provided between the proportional pressure reducing valve 6 connected the normally open solenoid valve 9a and the brake device B _RL, the B _RR. These hydraulic transmission means 5 _FL , 5 _FR , 5 _R transmit the hydraulic pressure from the hydraulic supply source hydraulic control means 4 when the hydraulic pressure from the hydraulic supply source 2 is normal, to the respective brake devices B _FL , B _FR , B _RL , The hydraulic fluid is transmitted to the _BRR , but when the hydraulic pressure of the hydraulic supply source 2 drops abnormally, it is possible to prevent the hydraulic oil from flowing back from the brake devices _BFL , _BFR , _BRL , and _BRR to the hydraulic supply source 2 side. Since they have functions and basically have the same configuration, the configuration of the hydraulic pressure transmission means _5FL will be representatively described below.

The hydraulic transmission means _5FL includes a spring 95 that slidably fits the free piston 93 to the cylinder body 94 with both ends facing the input chamber 91 and the output chamber 92, and biases the free piston 93 toward the input chamber 91. Are housed and arranged in the output chamber 82.

According to such a configuration of the hydraulic transmission means 5 _FL , the input chamber 9
It is possible to output a hydraulic pressure according to the hydraulic pressure acting on 1 from the output chamber 92, and the hydraulic pressure in the output chamber 92 does not flow to the input chamber 91 side, and the output chamber 92 is connected to the brake device _BFL .

That is, the brake devices B _FL , B _FR , B _RL , and B _{RR each} include a cylinder body 96 and a brake piston 97 slidably fitted in the cylinder body 96. The output of the output chamber 92 is communicated with the brake hydraulic chamber 98 by the movement of the brake piston 97 in accordance with the hydraulic pressure acting on the brake hydraulic chamber 98 defined in FIG.

Hydraulic transmission means for front wheel brake devices B _FL and B _FR
To 5 _FL, 5 _FR input chamber 91, 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 the input chamber 91 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 input chamber 91 and the reservoir R of the hydraulic transmitting means _{5 FL, 5 FR, 5 R} . The inlet solenoid valves 7 _FL, 7 _FR, 7 _R is interposed between the hydraulic transmitting means 5 _FL, 5 _FR, 5 _R input chamber 91 and output oil passage 99. Furthermore, each inlet solenoid valves 7 _FL, 7 _FR, 7 in parallel with _R the hydraulic pressure releasing one-way valves 100 _FL, 100 _FR, 100 _R are connected, these one-way valves 100 _FL, 100 _FR, 100 _R Is the input room 91
This permits only the flow of hydraulic oil from the oil passage to the output oil passage 99 side.

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 a control means 101, 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 , Inflow solenoid valves 7 _FL , 7 _FR , 7 _R
A pressure holding state in which demagnetization outflow solenoid valve 8 _FL, 8 _FR, 8 _R with exciting the inflow solenoid valve 7 _FL, 7 _FR, 7 _R and outlet solenoid valves 8 _FL, the 8 _FR, 8 _R were both degaussing The pressure increase control state can be switched.

The traction control switching control valve means 9 includes a normally open solenoid valve 9a interposed between the output port 37 and the output oil passage 99 of the hydraulic supply source oil pressure control means 4, and the hydraulic control source 2 and the output oil passage 99. And a normally-closed solenoid valve 9b interposed therebetween. Excitation and demagnetization of these solenoid valves 9a and 9b are also controlled by the control means 101, and the control means 101 demagnetizes and opens the solenoid valve 9a and demagnetizes the solenoid valve 9b in a normal state. Close the solenoid valve and set the solenoid valve 9a during traction control.
And the solenoid valve 9b is excited to open. Further, the control means 101, 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 to the hydraulic pressure source 2 via a constant differential pressure reducing valve 102. For this reason, when the solenoid valve 9b is opened, the hydraulic oil from the hydraulic pressure source 2 is reduced in pressure by the pressure reducing valve 102, and the output oil path 9
9 will be supplied.

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 82 at a certain value or more B
_RL, the function of exerting on the brake hydraulic pressure chamber 88 of the B _RR to.

The first output port 24 of the auxiliary hydraulic pressure generating means 3 is connected to the first input pressure action chamber 51 of the hydraulic power supply hydraulic pressure control means 4 via a proportional pressure reducing valve 54, and the second output port 25 is connected to the hydraulic power supply hydraulic pressure. It is connected to the second input pressure action chamber 52 of the control means 4. Accordingly, the hydraulic pressure of the second hydraulic chamber 19 is directly input to the second input pressure operating chamber 52, whereas the hydraulic pressure of the first hydraulic chamber 18 is reduced to the first input pressure operating chamber 51. Will be. Therefore, if the pressure receiving area S ₃ of the second pressing piston 34 facing the second input pressure action chamber 52 is set to be equal to or larger than the pressure receiving area S ₁ of the first pressing piston 33 facing the first input pressure action chamber 51, the proportional pressure reducing valve the effect of reduced pressure at 54 are those disappears, the pressure receiving area S ₃ of the second pressure piston 34, a first pressure piston 33 to the extent that does not negate the action of vacuum by the proportional pressure reducing valve 54 the pressure receiving area S ₁
It is set smaller than.

The first output port 24 is connected to a first
While being connected to the input pressure action chamber 51,
3, the rear wheel brake device via an on-off valve 104 _R and the proportional pressure reducing valve 6 is opened in accordance with the output oil pressure of the output port 37
Connected to B _RL and B _RR . The second output port 25 is
It is connected to the input pressure application chamber 52, the on-off valve 94 _FL, 94 left and right front wheel brake via the _FR apparatus B _FL to be opened in accordance with the output oil pressure of the output port 37 is connected to the B _FR.

Hydraulic regulating means 103, only the flow of hydraulic fluid to the on-off valve 104 _R side from the first hydraulic chamber 18 output oil pressure of the first hydraulic chamber 18 in the auxiliary hydraulic pressure generating means 3 in response to exceeding the set pressure P ₁ a first one-way valve 105 which permits, from said on-off valve 104 _R-side first
A second one-way valve 106 connected in parallel to the first one-way valve 105 while allowing only the flow of hydraulic oil to the hydraulic chamber 18 side. The hydraulic regulating unit 93 and the on-off valve 104 _R between is connected to the reservoir R via the third one-way valve 107, hydraulic oil in the third one-way valve 107 from the reservoir R to the on-off valve 104 _R side Is allowed only for distribution.

The first one-way valve 105 adjusts the hydraulic pressure of the first hydraulic chamber 18 to a set pressure P _1.
When the pressure exceeds the set pressure P ₁ , only the flow of hydraulic oil from the first hydraulic chamber 18 to the on-off valve 104 _R side is permitted.
A first hydraulic pressure or more input pressure working chamber 51 necessary to the hydraulic supply source hydraulic pressure control means 4 to be closed off valve 104 _R at the output oil pressure of the output port 37 in the hydraulic pressure supply source hydraulic pressure control means 4 is operated Is set to the value of

The second one-way valve 106 returns the first working piston 16 of the auxiliary hydraulic pressure generating means 13 to the retreat limit position with the end of the braking operation,
The first hydraulic chamber 18 is communicated with the rear wheel brake device in a state of communicating with the reservoir R via port 26 B _RL, the hydraulic pressure of the braking hydraulic pressure chambers 98 in the B _RR proportional pressure reducing valve 6, opening and closing valves 104 _R, and the first hydraulic is intended to serve to escape to the reservoir R via the chamber 18, it is set to open at a set pressure P _2. Thus to set pressure P ₂ is set so that The set pressure P ₂ to the corresponding hydraulic brake system even acting on the braking oil pressure chamber 98 B _RL, off at B _RR rubbing does not occur.

The third one-way valve 107 causes the first working piston 16 of the auxiliary hydraulic pressure generating means 3 to return to the retreat limit position with the end of the braking operation,
When the first hydraulic chamber 18 is in communication with the reservoir R via the communication port 26, the braking hydraulic chamber 98 in the rear wheel brake devices B _RL and B _RR can breathe due to a temperature change or the like. The flow of hydraulic oil from the first hydraulic valve to the brake hydraulic chamber 98 is allowed. The set pressure P ₃ set by the third one-way valve 107 prevents the brake hydraulic chamber 98 from being in a negative pressure state. It is set to the extent that it is obtained.

Off valves 104 _FL, 104 _FR, 104 _R are those having the same configuration, it will be described only to the following configuration of the on-off valve 104 _FL.

The on-off valve 104 _FL has a cylindrical on-off valve main body 114 having both ends closed, a valve hole 115 formed in one end wall of the on-off valve main body 114 while communicating with the output chamber 92 of the hydraulic transmission means 5 _FL , The valve hole
An opening / closing piston 118 slidably fitted to the opening / closing valve body 114 while having a valve body 116 at one end that can close the 115 and the other end facing the pilot chamber 117, and the opening / closing piston 118 is connected to the pilot chamber. On-off valve body 114 to urge to 117 side
And a spring 119 interposed between the opening and closing pistons 118.

A valve chamber 120 that can communicate with a valve hole 115 is defined between one end wall of the on-off valve main body 114 and the on-off piston 118.
The spring 119 is housed in the housing. Further, the valve chamber 120 is connected to the second output port 25 of the auxiliary hydraulic pressure generating means 3.

According to the opening / closing valve _104FL , when the oil pressure in the pilot chamber 117 is lower than a certain value, the opening / closing piston 118 moves to the pilot chamber 117 side to the position where the valve element 116 opens the valve hole 115 and opens. When the oil pressure in the pilot chamber 117 becomes equal to or higher than the predetermined value, the opening / closing piston 118
Move 115 to close and close the valve.

A branch oil passage 121 _FL branched from the output oil passage 99 is communicated with the pilot chamber 117. Thus the hydraulic pressure is high state of branch oil passage 121 _FL That pilot chamber 117 on-off valve 104 _FL is between the second output port 25 and the brake device B _FL is shut off by closing the hydraulic pressure of the branched oil passage 121 _FL is lowered On-off valve 104
_FL opens and the second output port 25 and brake device B _FL
Communication is established between them.

The on-off valve 104 _FR closes when the oil pressure in the branch oil passage 121 _FR branched from the output oil passage 99 is high, and the second output port 25
And blocked between brake device B _FR, communicates between the second output port 25 and the brake device B _FR and opened when the branch oil passage 121 _FR pressure is low. Further off valve 104 _R is closed by the hydraulic high state of branch oil passages 121 _R branched from the output oil passage 99, whereby the hydraulic pressure regulating means 103 and the braking device
B _RL, is interrupted between B _RR, the branch oil passage 121 _R hydraulic pressure decreases and the on-off valve 104 _R is opened hydraulic regulating unit 103 and the brake device B _RL, between B _RR is communicated.

In the output oil passage 99, the branch oil passage 121 _FL, 121 _FR, 121 hydraulic transmitting means 5 _FL of the branch portion of the _R, 5 _FR, 5 _R is the side fourth one-way valve 122 is interposed. The fourth one-way valve 122 opens according to a differential pressure equal to or higher than a preset pressure and opens the output port.
Only the flow of hydraulic oil from the 37 side to the hydraulic transmission means 5 _FL , 5 _FR , 5 _R side is permitted.

A fifth one-way valve 123 is connected in parallel to the fourth one-way valve 122. The fifth one-way valve 123 opens in response to a differential pressure equal to or higher than a preset pressure to open the hydraulic transmission means.
Only the flow of hydraulic oil from the 5 _FL , 5 _FR , 5 _R side to the output port 37 side is allowed, and the set pressure of the fifth one-way valve 123 is set to open the fourth one-way valve 122. It is set smaller than the pressure.

Next, the operation of this embodiment will be described. Referring first hydraulic supply source 2 is assumed during normal braking operation in a state where operating normally, the inflow solenoid valve 7 _FL, 7 _FR, 7 _R and outlet solenoid valves 8 _FL, 8 _FR, 8 _R is demagnetized (The state shown in FIG. 1),
Also, both solenoid valves 9 of the traction control switching control valve means 9
The a and 9b are also in the demagnetized state (the state shown in FIG. 1), and the proportional pressure reducing valve 54 is in a state where the pressure can be reduced in accordance with the hydraulic pressure of the hydraulic pressure supply source 2 acting on the pilot chamber 80. Therefore, the output port 37 of the hydraulic supply source hydraulic control means 4 communicates with the output oil passage 99, and the output oil passage 99 is connected to the inflow solenoid valves _7FL , _7FR ,
The first output port of the auxiliary hydraulic pressure generating means 3 is in a state of being in communication with the input chamber 91 of the hydraulic pressure transmitting means 5 _FL , 5 _FR , 5 _R via 7 _R.
24 is in communication with the first input pressure action chamber 51 and the accumulator 56 of the oil pressure control means 4 via the proportional pressure reducing valve 54, and the second output port 25 is in communication with the second input pressure action chamber 52. In state.

When the brake pedal 1 is depressed in this state, the first operating piston 16 of the auxiliary hydraulic pressure generating means 3 moves forward, and the hydraulic pressure generated in the first hydraulic chamber 18 is reduced by the proportional pressure reducing valve 54 to control the hydraulic supply source hydraulic pressure. It acts on the first input pressure action chamber 51 of the means 4 and on the accumulator chamber 58 of the accumulator 56. At this time, the hydraulic pressure control unit 4 is set to start operating earlier than the accumulator 54. That is,
First pressing piston 33 in hydraulic supply source hydraulic control means 4
, The pressure receiving area S ₁ facing the input hydraulic chamber 51, the pressure receiving area S ₂ facing the accumulator chamber 58 of the accumulator piston 59, the set load f ₁ of the spring 42 in the hydraulic pressure control unit 4, and the first accumulator spring in the accumulator 56. set load f ₂ of 60 is set as the inequality shown in the equation (1) described above is satisfied.

As a result, in the hydraulic pressure control unit 4, the first pressing piston 33 moves forward before the accumulator 56 performs the pressure accumulation operation, and the spool 31 whose rear end is in contact with the pressing piston 33 is driven to move forward. . As described above, prior to the pressure accumulation operation of the accumulator 56, the hydraulic supply
By starting the operation of (1), the generation of useless reaction force during the braking operation can be avoided, the loss of the pedaling force of the brake pedal 1 can be prevented, and the response can be improved.

In the hydraulic supply source hydraulic control means 4, the first pressing piston 33
The output port 37 communicates with the input port 38 when the spool 31 moves forward by a certain distance in accordance with the forward movement of the hydraulic pressure source 2, and the output oil pressure from the output port 37 which communicates with the hydraulic pressure source 2 increases rapidly. Thus, before the differential pressure across the fourth one-way valve 122 in the output oil passage 89 reaches the set valve opening pressure, the branch oil passages 121 _FL and 121 _FL
FR, 121 in response to the hydraulic pressure increases in _R-off valves 104 _FL, 104 _FR, 104 _R
First, the fourth one-way valve 122 is opened in response to the differential pressure being equal to or higher than the set valve opening pressure. As a result, the oil pressure from the output port 37 is changed to the output oil passage 99 and the inflow solenoid valve.
_{Acting on} the input chamber 91 of the hydraulic transmission means 5 _FL , 5 _FR , 5 _R via 7 _FL , 7 _FR , 7 _R , the braking pressure can be obtained by the brake devices B _FL , B _FR and the hydraulic transmission means 5 _R hydraulic pressure is reduced by a proportional pressure reducing valve 6 rear wheel brake device to be outputted from the output chamber 92 of the B _RL, given B _RR. Therefore, when braking
Before the operation of the hydraulic transmission means 5 _FL , 5 _FR , 5 _R , the on-off valve 104
_FL , 104 _FR , 104 _R are reliably closed, and the hydraulic transmission means 5 _FL , 104 _R
5 enhances the operation simultaneously with the braking pressures of _FR, 5 _R can be improved responsiveness.

In addition, since the output oil pressure from the output port 37 increases rapidly, 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. _{B FL, B FR, B RL} , the initial operation of the brake piston 97 in the B _RR becomes smooth.

By the way, each on-off valve 104 _FL , 104 _FR , 104 _R is an output port
At the time of the closed hydraulic from 37, hydraulic regulating means 103 in the first one-way valve 105 is pressure from the first hydraulic chamber 18 of the auxiliary and opening hydraulic pressure generating means 3 to the inlet side of the opening and closing valve 104 _R When the forward operation of the second operating piston 17 of the auxiliary hydraulic pressure generating means 3 starts, the hydraulic pressure generated in the second hydraulic chamber 19
4 _FL , 104 _{Acts on} the inlet side of _FR . However, each on-off valve 10
4 _FL, 104 _FR, 104 since _R is already closed, the hydraulic braking device B _FL of the first and second hydraulic chambers 18, 19, B _FR, B _RL,
It has no effect on _BRR .

Due to the communication of the output port 37 with the input port 38, the hydraulic pressure of the output pressure working chamber 45 also increases, and the reaction force piston 32 is driven rearward to abut the front end of the spool 31, whereby the spool 31 retreats. The output port 37 is cut off from the input port 38. Further, when the brake pedal 1 is depressed, the hydraulic pressure in the first hydraulic chamber 18 increases.
31 advances again, and the output port 37 communicates with the input port 38. In this way, in response to the braking operation of the brake pedal 1, the spool 31 reciprocates between the front position where the output port 37 communicates with the input port 38 and the rear position where the output port 37 is disconnected from the input port 38. 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 37.

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 93
Since each of the brake devices B _FL , B _FR , B _RL , and B _RR is isolated from the hydraulic circuit from the input chamber 91 to the hydraulic supply 2, the gas that may be mixed into the hydraulic oil at the hydraulic supply 2 _Does not adversely affect the brake devices _BFL , _BFR , _BRL , and _BRR .

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.

In addition, the hydraulic pressure in the first hydraulic chamber 18
Since it acts on the input pressure action chamber 51, the hydraulic pressure acting on the first input pressure action chamber 51 and the accumulator 56 is kept low in a high pressure region after the braking force is sufficiently exerted, and the hydraulic pressure supply source hydraulic control means 4 and the accumulator 56 Can be reduced. In addition, when the brake pedal 1 is depressed several times, the hydraulic pressure in the first hydraulic chamber 18 is reduced by the proportional pressure reducing valve 54 and applied to the first input pressure action chamber 51. The frequency of hydraulic pressure rise is reduced to a small extent, and the amount of hydraulic oil circulation is reduced to reduce wasteful consumption of hydraulic oil. The frequency of operation of the free piston 93 in the hydraulic transmission means 5 _{FL to} 5 _R is also reduced to improve durability. Can be contributed to.

Further, by accumulating the hydraulic pressure from the first hydraulic chamber 18 with the accumulator 56, the pedal stroke of the brake pedal 1 can be ensured, whereby a configuration for ensuring the pedal stroke in the hydraulic supply source hydraulic control means 4 is provided. 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 effect of the accumulator 56 when a sudden reaction force is applied.

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
_Energize 7 _FR and 7 _R to output oil passage 99 and hydraulic transmission means
_Cut off between 5 _FL , 5 _FR and 5 _R. This suppresses an increase in the braking force to avoid the wheels from being locked.
If the wheel is still going to lock up,
By exciting the corresponding outlet solenoid valve 8 _FL, 8 _FR, 8 _R communicates the input chamber 91 of the hydraulic transmission means 5 _FL to 5 _R a reservoir R, to eliminate the locking tendency of the wheels by lowering the brake pressure be able to.

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 37 is applied again to the hydraulic 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 avoids act rapidly on the hydraulic each inlet solenoid valves 7 _FL, 7 _FR, 7 _R from the output port 37 by intermittently closing the solenoid valve 9a, be gentle hydraulic increased Can. 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 121 in accordance with the oil pressure from the output port 37 of the hydraulic supply source hydraulic pressure control means 4 _FL, 121 _FR, 121-off valve by the hydraulic pressure drop in _{R 104 FL, 104 FR, 104} R is opened I do. Therefore, the first and second hydraulic chambers 18, 1 of the auxiliary hydraulic pressure generating means 3
The braking oil pressure generated in 9 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.

Moreover, in response to the abnormal decrease in the hydraulic pressure of the hydraulic pressure supply source 2, in the proportional pressure reducing valve 54, the hydraulic pressure in the pilot chamber 80 decreases, whereby the regulating piston 81 moves in a direction away from the stopper 71, and the valve body 78 77 is closed to shut off the connection between the input port 67 and the output port 68, that is, between the oil passages 66 and 53. Therefore, unnecessary reaction force of the accumulator 56 is prevented from acting on the brake pedal 1. By providing such a shutoff function in the proportional pressure reducing valve 54, the hydraulic pressure from the hydraulic pressure supply source 2 becomes abnormal. The number of parts is reduced as compared with the case where the on-off valve that closes as the pressure decreases is provided either before or after the proportional pressure reducing valve.

During non-braking after braking operation completed, the oil pressure of the output hydraulic pressure branch oil passage 121 in accordance with the reduction _FL, 121 _FR, 121 _R of the output port 37, first on-off valve 104 _FL, 104 _FR, 104 _R is opened .
Next, as the differential pressure across the fifth one-way valve 123 becomes greater than or equal to the set valve opening pressure, the fifth one-way valve 123 opens, and the input chamber 91 in each of the hydraulic pressure transmission means 5 _{FL to} 5 _R receives hydraulic pressure. It communicates with the reservoir R via the supply oil pressure control means 4. Therefore, the input chamber 91 of the free piston 93 in the hydraulic transmission means 5 _{FL to} 5 _R
According to the movement to the side, the output chamber 92 can breathe. Moreover, the hydraulic pressure of the input chamber 91 in each of the hydraulic transmission means 5 _{FL to} 5 _R can be released to the output oil passage 99 via the one-way valve 100 _FL , 100 _FR , 100 _R , so that the inflow solenoid valves 7 _FL , 7 _FR , 7 be larger flow resistance of at _R can be returned quickly original position free piston 93 is performed promptly the pressure release of the input chamber 91.

By the way, it is conceivable that the hydraulic pressure in the input chamber 91 increases due to the temperature increase in each of the hydraulic pressure transmission means 5 _FL , 5 _FR , 5 _R during non-braking. In this case, if the hydraulic pressure cannot be released, the braking pressure is applied. Become. However, the fifth one-way valve 123
Is smaller than the set valve opening pressure of the fourth one-way valve 122, and is set to a relatively small value. Hydraulic oil can escape.

Further, when the driving force of the engine becomes excessive and the driving wheels are likely to slip excessively, both the solenoid valves 9a and 9b of the traction control switching control valve means 9 are excited by the control means 101. As a result, the hydraulic pressure from the hydraulic supply source 2 acts on the input chamber 91 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, thereby causing excessive slip. Occurrence 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.
Since the pressure is reduced to the hydraulic pressure adapted to the control by 2, the traction control is not performed by the excessive hydraulic pressure. Therefore, control responsiveness does not decrease or become smooth.

In such a braking hydraulic pressure control device, the hydraulic pressure generated in the first hydraulic pressure chamber 18 of the auxiliary hydraulic pressure generating means 3 is reduced by the proportional pressure reducing valve 54 and is transmitted to the first input pressure action chamber 51 of the hydraulic pressure source hydraulic pressure control means 4. The brake device is input via the on-off valve 104 _R and the proportional pressure reducing valve 6 when the hydraulic pressure source 2 is malfunctioning.
The hydraulic pressure applied to B _RL and B _RR and generated in the second hydraulic chamber 19 is input to the second input pressure action chamber 52 of the hydraulic power supply hydraulic pressure control means 4, and the on-off valve 104 when the hydraulic power supply 2 is out of order. _FL , 1
It is given to the brake devices B _FL and B _FR via 04 _FR . Therefore, the first and second hydraulic chambers 18, 1 of the auxiliary hydraulic pressure generating means 3
9 have two functions, respectively, and can contribute to downsizing of the auxiliary hydraulic pressure generating means 3.

By the way, the hydraulic supply source hydraulic control means 4 includes a spool.
First and second input pressure action chambers 51 and 52 for exerting hydraulic pressure for driving the 31 are provided, and the spool 31 is driven regardless of which input pressure action chamber 51 or 52 receives a hydraulic pressure. It is possible. Therefore, even if a hydraulic pressure failure occurs between the first hydraulic chamber 18 and the first input pressure acting chamber 51 and between the second hydraulic chamber 19 and the second output pressure acting chamber 52 in the auxiliary hydraulic pressure generating means 3, Hydraulic supply source hydraulic control means 4
It is possible to supply the braking pressure by driving the respective brake device B _FL .about.B _RL a.

In such a vehicle brake hydraulic pressure control device, the connection relationship between the first hydraulic chamber 18 and the second hydraulic chamber 19 of the auxiliary hydraulic pressure generating means 3 may be reversed, in which case the spring 22 operates in the first and second actuations. The spring 22 is provided between the pistons 16 and 17, and the spring force of the spring 22 is set to be larger than the spring force of the spring 23. Further, the first housing 14 of the auxiliary hydraulic pressure generation means 3 and the second housing 30 of the hydraulic pressure supply source hydraulic pressure control means 4 may be separate bodies,
You may make it unify.

The second working piston 17 in the auxiliary hydraulic pressure generating means 3
Is larger than the pressure receiving area facing the first hydraulic chamber 18 in the second hydraulic chamber.
A stepped shape may be adopted so that the pressure receiving area facing 19 becomes small, so that when the output oil pressure of the oil pressure supply source 2 abnormally decreases, the left and right front wheel brake devices _BFL and _BFR provide higher braking. Pressure can be applied. In that case, the second pressing piston 34 in the hydraulic pressure supply source hydraulic control means 4 has a stepped shape in which the pressure receiving area facing the second input pressure action chamber 52 is smaller than the pressure receiving area facing the first input pressure action chamber 51. As a result, when the hydraulic supply source 2 operates normally, the second working piston 17 is a stepped piston.
It is possible to prevent the operation of the spool 31 from being affected even if the pressure in the input pressure action chamber 52 increases.

Further, the hydraulic pressure from the output port 37 of the hydraulic supply source hydraulic control means 4 may be applied to the pilot chamber 80 of the proportional pressure reducing valve 54, and the output hydraulic pressure of the output port 37 may be such that the hydraulic pressure of the hydraulic supply source 2 is abnormal. Since it decreases as the pressure decreases, the proportional pressure reducing valve is the same as that connected to the hydraulic pressure source 2.
54 can be operated. In addition, when the output port 37 is connected to the pilot chamber 80 in this manner, the spring 82 of the proportional pressure reducing valve 54 covers the delay in the rise of the hydraulic pressure in the pilot chamber 80 and pushes the regulating piston 81 against the stopper 71. It is possible to prevent the valve hole 77 from being closed by the valve body 78 by contact.

As another embodiment of the present invention, both the regulating piston 81 and the valve body 78 may be provided with a protruding portion that can abut against each other, and the protruding portion may be provided only on the valve body 78 side. Is also good.

The above embodiment is a case where the proportional pressure reducing valve of the present invention is applied to the vehicle brake hydraulic pressure control device. However, the proportional pressure reducing valve of the present invention is related to a proportional pressure reducing valve which needs to maintain a shut-off state when necessary. Widely applicable.

C. Effects of the Invention As described above, according to the present invention, a regulating piston having one end face facing the pilot chamber and the other end face capable of contacting the stopper facing the output hydraulic chamber is provided in the housing. The regulating piston and the valve body are slidably fitted coaxially with each other, and at least one of the regulating piston and the valve body has a protruding portion that can contact the other of the regulating piston and the valve body. A proportional pressure reducing function that applies high oil pressure to the pilot chamber to reduce the oil pressure at the input port from the output port and output the same, and A function of closing the valve hole with the valve body in a state where the hydraulic pressure of the chamber is lowered to cut off between the input port and the output port,
This can be achieved while reducing the number of parts by eliminating the need for an on-off valve.

[Brief description of the drawings]

The drawings show an embodiment of the present invention. FIG. 1 is a hydraulic circuit diagram of a vehicle brake hydraulic control device, and FIG. 2 is an enlarged vertical sectional view of a proportional pressure reducing valve. 54… Proportional pressure reducing valve, 67… Input port, 68… Output port, 70
... the third housing as a housing, 71 ... stopper,
72: output hydraulic chamber, 73: valve piston, 75: input hydraulic chamber, 77: valve hole, 78: valve body, 80: pilot chamber, 81: regulating piston, 81a: protrusion

Continuing from the front page (72) Inventor Kazutoshi Tajima 1-4-1 Chuo, Wako-shi, Saitama Prefecture Inside Honda R & D Co., Ltd. (72) Inventor Takeshi Kojima 1-4-1 Chuo, Wako-shi, Saitama Honda Co., Ltd. Inside the Technical Research Institute (72) Inventor Yoshinobu Mizusaki Ueda City, Nagano Prefecture

Claims (1)

(57) [Claims] 1. An input port (67) and an output port (68).
A valve piston (73) having one end arranged on the side of a stopper (71) fixed to the housing (70) is connected to an output hydraulic chamber (72) communicating with the output port (68). The input hydraulic chamber (75) communicating with the input port (67) is spring-biased in the direction in which it comes into contact with the stopper (71) while facing the other surface, with the end face facing the input port (67). A valve hole (77) connecting the input hydraulic chamber (75) and the output hydraulic chamber (72) is formed at one end of the valve piston (73), and the valve hole (7) is formed in the input hydraulic chamber (75).
In the proportional pressure reducing valve in which the valve body (78) capable of closing the valve (7) is housed while being biased by a spring in the valve closing direction, the housing (7)
0) is a regulating piston (81) having one end face facing the pilot chamber (80) and the other end face capable of contacting the stopper (71) facing the output hydraulic chamber (72). (73) is slidably fitted coaxially with at least one of the restricting piston (81) and the valve body (78), a protruding part that can abut the other of the restricting piston (81) and the valve body (78). The part (81a) is characterized in that it is protruded to have a length that allows the valve body (78) to be in the valve-open position in a state where the valve piston (73) and the regulating piston (81) are at predetermined close positions. And a proportional pressure reducing valve.