JPH03220055A - Hydraulic valve - Google Patents

Abstract

PURPOSE:To suppress the generation of an excessive reaction force and secure the smooth operation performance by installing a pressure absorbing means which absorbs the prescribed pressure variation of the reaction force chamber of a hydraulic valve equipped with an output port connected with a hydraulic operating device such as wheel brake. CONSTITUTION:In a brake hydraulic pressure controller, the output hydraulic pressure supplied from a hydraulic pressure feeding source 2 is controlled by a hydraulic valve 4 according to the hydraulic pressure outputted from a hydraulic pressure generating means 3 according to the stepping-on quantity for a brake pedal. The hydraulic control valve 4 is equipped with a spool 22 fitted in a housing 21, and a pressing piston 23, and a reaction force chamber 32 is installed on the front edge part side of the spool 22, and the first input action chamber 34 is installed between the second cylinder hole 26 and the pressing piston 23, and the second input action chamber 35 is installed between the rear edge part of the second cylinder hole 26 and a piston 36. In this case, a pressure absorbing means 24 including a damper piston 40 which is fitted in relatively slidable manner with the pressing piston 23 is installed, and the damper piston 40 is energized by a damper spring 41 interposed between the pressing piston 23 and the piston 40.

Description

Detailed Description of the Invention A5 Object of the Invention (1) Industrial Application Field The present invention provides an output port connected to a hydraulically operated device, an input port leading to a hydraulic pressure supply source, and a release port leading to a reservoir. a housing having a housing having a housing, and a rear position communicating between the input port and the release port, and a front position communicating between the manual port and the output port. a spool connected to the output port, a reaction force chamber formed within the housing to exert hydraulic pressure that biases the spool toward the rear, and a reaction force chamber that exerts hydraulic pressure that biases the spool toward the front. The present invention relates to a hydraulic control valve including an input pressure acting chamber formed in a housing.

(2) Conventional technology Conventionally, such a hydraulic @ control valve has been used, for example, in
It is publicly known from Publication No. 6346 and the like.

(3) Problems to be Solved by the Invention By the way, in the above conventional hydraulic pressure control valve, the output port is communicated with the reaction force chamber, and the spool is moved forward by applying hydraulic pressure to the input pressure action chamber. When the pressure is applied, the hydraulic pressure supply source communicates with the output port, the hydraulic pressure from the hydraulic pressure supply source acts on the reaction force chamber, and the hydraulic pressure in the reaction force chamber urges the spool to the rear side. ing. Therefore, when the reaction force chamber communicates with the output port, the spool operates in the direction of contracting the input pressure action chamber, and a reaction force acts on the operating member for applying hydraulic pressure to the input pressure action chamber. The operation of the operating member becomes jerky.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a hydraulic control valve that provides smooth operability.

B0 Structure of the Invention (1) Means for Solving the Problems The hydraulic control valve of the present invention for achieving the above object includes a pressure absorbing means for absorbing a predetermined pressure change in the reaction force chamber.

(2) Effect According to the above configuration, the pressure absorbing means absorbs a predetermined pressure change in the reaction force chamber, thereby avoiding generation of excessive reaction force.

(3) Real m! DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to a brake fluid pressure control device for a front engine/front drive vehicle will be described below with reference to the drawings.

First, in FIG. 1 showing the first embodiment of the present invention, a left front wheel brake device BFL and a right front wheel brake device B□ as hydraulically operated devices are respectively installed on the left front wheel and the right front wheel of a vehicle. A left rear wheel brake device BIIL and a right rear wheel brake device B□, which are hydraulically operated devices, are attached to the rear wheels and the right rear wheel, respectively. On the other hand, the brake pedal 1 is connected to a hydraulic pressure generating means 3 that outputs a hydraulic pressure according to the amount of depression of the brake pedal 1, and a hydraulic pressure supply source is connected to the brake pedal 1 in accordance with the hydraulic pressure output from the hydraulic pressure generating means 3. The output hydraulic pressure of No. 2 is controlled by a hydraulic pressure control valve 4. During normal braking, the hydraulic pressure corresponding to the output hydraulic pressure of the hydraulic pressure control valve 4 is applied to the left front wheel brake device BFL and the right rear wheel brake device W.
B m * and equally applied to the right front wheel brake device BFI and left rear wheel brake device BIL, and during anti-lock control or traction control, each brake device BFL, B□; BFl+ BI
It becomes possible to control L individually. Further, when the output hydraulic pressure of the hydraulic pressure supply source 2 is abnormally decreased, that is, when the output hydraulic pressure of the hydraulic pressure control valve 4 is abnormally decreased, hydraulic pressure corresponding to the amount of depression of the brake pedal l is applied from the hydraulic pressure generating means 3 to each brake device! Br
t.

B□; B□, given to F3wt.

The hydraulic pressure supply source 2 includes a hydraulic pump 5 that pumps hydraulic oil from the reservoir R, an accumulator 6 connected to the hydraulic pump 5, and a pressure switch 7 for controlling the operation of the hydraulic pump 5. Be prepared.

The hydraulic pressure generating means 3 is a so-called tandem mask cylinder, and includes a cylinder body 8 formed in a cylindrical shape with both ends closed. In the cylinder hole 9 provided in this cylinder body 8,
A first working piston 10 and a second working piston 11 disposed at a distance in front of the first working piston 10 are slidably fitted, and between the first working piston 10 and the second working piston 11. A first hydraulic chamber 12 is formed, and a second hydraulic chamber 13 is formed between the front end wall of the cylinder hole 9 and the second working piston 11. Further, a first return spring 14 that exerts a spring force that urges the first working piston 10 rearward is housed in the first hydraulic pressure chamber 12, and a first return spring 14 that exerts a spring force that urges the first working piston 10 backward is housed in the second hydraulic pressure chamber 13. Second return spring 1 that biases toward the side
5 is stored.

The first actuating piston 10 is integrally provided with a piston rod 10a that penetrates the rear end wall of the cylinder hole 9 in an oil-tight and movable manner and protrudes outward.
The front end of the pressing rod 16 connected to the piston rod 10a is brought into contact with the rear end of the piston rod 10a. Therefore, the first actuating piston 10 moves forward in the cylinder hole 9 in response to the braking operation of the brake pedal 1, and the hydraulic pressure generated in the first hydraulic pressure chamber 12 in response to the forward movement of the first actuating piston 10 causes the first actuating piston 10 to move forward in the cylinder hole 9. 2
The actuating piston 11 moves forward, and hydraulic pressure is generated in the second hydraulic chamber 13 accordingly.

Further, the cylinder body 8 is provided with a first output port 17 communicating with the first hydraulic pressure chamber 12 and a second output port communicating with the second hydraulic pressure chamber 13, and a first and second working piston. 10. Only when 11 returns to the backward limit, each hydraulic chamber 12
．． 13 to reservoir R) 19.20
is drilled.

The hydraulic control valve 4 includes a housing 21 and a housing 21.
The spool 22 and the pressing piston 23 are slidably fitted into the spool 22 and the pressing piston 23, and a pressure absorbing means 24 is provided.

The housing 21 is basically formed in a cylindrical shape with both ends closed, and the housing 21 has first cylinder holes whose front ends are closed, sequentially from the front end (left end in FIG. 1). 25, and a second cylinder hole 26, which has a larger diameter than the first cylinder hole 25, is coaxially connected to the rear end of the first cylinder hole 25, and has a closed rear end.

Thus, a step 27 is provided between the first and second cylinder holes 25,26. In addition, the housing 21 has human power ports 2 which are opened in the inner surface of the first cylinder hole 25 from the front end to the rear end with spaces between them.
8, an output port 29 and a release port 30 are bored;
The input port 28 communicates with the hydraulic pressure source 2 and the release port 30 communicates with the reservoir R.

The spool 22 is slidably fitted into the first cylinder hole 25. Moreover, the output port 2 is provided on the outer surface of the spool 22.
9 is provided with an annular groove 31 that is in constant communication with the annular groove 31, and the axial length of the annular groove 31 is such that it extends between the output port 29 and the release port 30 when the spool 22 is in the rear position as shown in FIG. When the spool 22 is in the forward position, the output port 29 and the input port 28 are set to communicate with each other.

A reaction force chamber 32 is defined between the front end of the spool 22 and the front end wall of the first cylinder hole 225, and a return spring that urges the spool 22 rearward is provided in the reaction force chamber 32. 33 is stored.

The pressing piston 23 is slidably fitted into the second cylinder hole 26. Further, in the second cylinder hole 26, a first human pressure action chamber 34 is defined between the pressing piston 23 and a second human pressure action chamber 35 is defined between the second cylinder hole 26 and the rear end wall of the second cylinder hole 26. A piston 36 is slidably fitted thereto.

Moreover, the first human pressure working chamber 34 is connected to the first output port 17 of the hydraulic pressure generating means 3 via an oil passage 38 to which an accumulator 37 is connected in the intermediate part, and the second human pressure working chamber 35 is connected to the first output port 17 of the hydraulic pressure generating means 3. It is connected to the second output port 18 of the hydraulic pressure generating means 3 via a line 39 .

The pressure absorbing means 24 includes a pressing piston 23 and a spool 2.
2, and a damper spring 41 that is compressed between the damper piston 40 and the press piston 23. .

The pressing piston 23 is provided with a bottomed sliding hole 42 that opens toward the spool 22, and is integrally provided with a restriction #43 that extends radially inward from the open end of the sliding hole 42. At the rear end of the spool 22, there is a small-diameter abutting protrusion 22 that can penetrate the regulation *43 and enter the sliding hole 42.
a is coaxially and integrally protruded. The damper piston 40 is formed into a cylindrical shape with a bottom, and is slidably fitted into the slide hole 42 with its closed end abutting the abutting protrusion 42a. The damper piston 40 is slidable relative to the pressing piston 23 between the position where it contacts the closed end of the sliding hole 42 and the position where it contacts the regulating collar 43, and the set load of the damper spring 41 is set larger than the set load of the return spring 33. Further, a communication hole 44 is bored at the closed end of the damper piston 40 to avoid increasing or decreasing the hydraulic pressure between the damper piston 40 and the pressing piston 23. It is communicated with the release port 30 via the chamber between the pressure piston 23 and the pressure piston 23 .

Between the output port 29 and the reaction force chamber 32, the output port 29
via the first differential pressure valve 45 which opens only when the hydraulic pressure of the hydraulic fluid becomes greater than the hydraulic pressure of the reaction force chamber 32 by a predetermined value or more and allows the flow of hydraulic fluid from the output port 29 to the reaction force chamber 32. connected. A first one-way valve 46 that only allows flow from the reaction force chamber 32 toward the output port 29 side is connected in parallel to the first differential pressure valve 45, and the first one-way valve 46 is opened. The differential pressure is extremely small (set.

In this hydraulic pressure control valve 4, a rearward spring force by the return spring 33 and a rearward hydraulic pressure due to the hydraulic pressure in the reaction force chamber 32 act on the spool 22. On the other hand, the pressing piston 2 is
The liquid pressure toward the front side acting on the pressure absorbing means 2
4 on the spool 22, and the spool 22 moves in the axial direction due to the balance between the force toward the rear side and the hydraulic pressure toward the front side.

When the fluid pressure toward the front side exceeds the force toward the rear side and the spool 22 moves toward the front side, the output port 29 and the input port 28 are communicated with each other, and the force toward the rear side is reduced. exceeds the fluid pressure towards the front side and the spool 22 is moving towards the rear side, the output port 2
9 and the release port 30 are communicated with each other.

an output port 29 of the hydraulic pressure control valve 4 and a hydraulic pressure supply source 2;
Between the oil passage 48 and the oil passage 48, there is a traction control electromagnetic element that can be switched between a position where the output port 29 communicates with the oil passage 48 in a demagnetized state and a position where the hydraulic pressure supply source 2 communicates with the oil passage 48 in an energized state. A switching valve 49 is provided.

Each of the brake devices BFL, BFR, BRL, and BRR includes a cylinder body 51 and a brake piston 52 that is slidably fitted into the cylinder body 51, and is defined between the cylinder body 51 and the brake piston 52. Braking force is exerted by moving the brake piston 52 in accordance with the hydraulic pressure acting on the brake hydraulic pressure chamber 53.

Each of the above brake devices BFL, BFR, BRL, BRR
One-way hydraulic pressure transmission means 55F 55rs1. 55
mt.

551II are connected respectively. These one-way hydraulic pressure transmission means 55FL, 55Fm, 55mt,
55 m have basically the same configuration, so the configuration of the one-way hydraulic pressure transmission means 55FL will be described below as a representative.

The one-way hydraulic pressure transmission means 55FL has both ends facing the input hydraulic pressure chamber 56 and the output hydraulic pressure chamber 57, and the free piston 55
8 is slidably fitted into the cylinder body 59, and a spring 60 for biasing the free piston 58 toward the manual hydraulic pressure chamber 56 is housed in the output hydraulic pressure chamber 57.

Such a one-way hydraulic pressure transmission means 55. According to the configuration L, it is possible to output a hydraulic pressure corresponding to the hydraulic pressure acting on the input hydraulic pressure chamber 56 from the output hydraulic pressure chamber 57, and the hydraulic pressure of the output hydraulic pressure chamber 57 can be applied to the input hydraulic pressure chamber. 56 side, and the output hydraulic pressure chamber 57 is the brake hydraulic pressure chamber 5 of the brake device BFL.
3.

Each one-way hydraulic pressure transmission means 55FL, 55Fm.

551L and 55111 transmit the hydraulic pressure from the hydraulic pressure control valve 4 to each brake equipment fBrt, B□, BIL, and 8 ports when the output hydraulic pressure of the hydraulic pressure supply source 2 is normal, and also It has a function that can prevent hydraulic fluid from flowing backward from each brake device Brt, B□*BILI Bml to the hydraulic pressure supply source 2 side when the hydraulic pressure of the hydraulic pressure supply source 2 drops abnormally.

One-way hydraulic pressure transmission means 5 corresponding to the left and right front wheel brake devices BFL and B□ mounted on the left and right front wheels that are drive wheels.
The input hydraulic chamber 56 of 5FL and 55Fl has an inflow valve 62□
, 62Fl and outflow valves 63FL, 631 are connected in parallel, respectively, and a brake device for front and rear wheels BIL+Bl
An inflow valve 62 and an outflow valve 63m are connected in parallel to the input hydraulic pressure chambers 56 of the one-way hydraulic pressure transmission means 55*t and 55□ corresponding to 1, respectively.

Inflow valve 62FL, 62F1. 621 is a normally open solenoid valve that closes when energized, and outflow valves 63F163□,
63 is a normally closed solenoid valve that opens when excited. Therefore, the outflow valves 63rt, 63F1. 631 is interposed between the input hydraulic pressure chamber 56 and the reservoir R of the one-way hydraulic pressure transmission means 55FL, 55□, 55mL, and 55I, respectively. Further, the inflow valves 62FL and 62Fll are respectively interposed between the input hydraulic pressure chamber 56 and the oil passage 64 of the one-way hydraulic pressure transmission means 55FL and 55□, and the inflow valve 62 is connected to the one-way hydraulic pressure transmission means 55*t and 55++t. is interposed between the input hydraulic pressure chamber 56 and the oil passage 65.

The oil passage 64 is connected to the oil passage 48 through a parallel circuit consisting of a second differential pressure valve 66 and a second one-way valve 67 that is parallel to the second differential pressure valve 66. Therefore, the second differential pressure valve 66 is connected to the oil passage 4.
The valve opens when the hydraulic pressure in the second oil passage 48 becomes greater than the hydraulic pressure in the oil passage 64 by a predetermined value or more, and only the hydraulic oil is allowed to flow from the oil passage 48 to the oil passage 64. Directional valve 67
allows the hydraulic oil to flow only from the oil passage 64 to the oil passage 48, and the valve differential pressure is set extremely small during this period. Further, the oil passage 65 is connected to the reaction force chamber 32 of the hydraulic pressure control valve 4, and the first differential pressure valve 45 and the first
It is connected to the output port 29 of the hydraulic control valve 4 via a parallel circuit consisting of a one-way valve 46 .

Each brake device BFL, BP, BIL+ Bl
m, one set of left and right wheel brake devices, that is, the left front wheel brake device BFL and the right rear wheel brake device BIL, are connected via the first separation valve 681, and the other set of left and right wheel brake devices, that is, The right front wheel brake device B□ and the left rear wheel brake device BIL are connected via a second separation valve 68□. These isolation valves 6B+, 6
8z has basically the same configuration, so
As a representative example, the configuration of the first isolation valve 6 will be described below.

The first separation valve 681 is bored in one end wall of the separation valve body 69 while communicating with the cylindrical separation valve body 69 whose both ends are closed and the output hydraulic pressure chamber 57 of the one-way hydraulic pressure transmission means 551°. a valve hole 70 and a valve body portion 71a that can close the valve hole 70;
A separation piston 71 is slidably fitted into the separation valve body 69 with the other end facing a pilot chamber 72 defined between the separation valve body 69 and the other end wall of the separation valve body 69.
and a spring 73 interposed between the separation valve body 69 and the separation piston 71 to urge the separation piston 71 toward the pilot chamber 72 side.

A valve chamber 74 that can communicate with the valve hole 70 is defined between one end wall of the separation valve main body 69 and the separation piston 71.
A spring 73 is housed in 4. The separation valve body 69 also has a one-way hydraulic pressure transmission means 55FL that communicates with the valve chamber 74.
An inlet port 75 communicating with the output hydraulic pressure chamber 57 is bored.

According to the first separation valve 6B, when the hydraulic pressure in the pilot chamber 72 is lower than a certain value, the valve body portion 71a closes to the valve hole 7.
The separation piston 71 moves toward the pilot chamber 72 until it opens the valve, and the one-way hydraulic pressure transmission means 55F
Between the output hydraulic pressure chamber 57 of L, 55+=a, that is, the left front wheel brake device BFL and the right rear wheel brake device B□
The braking hydraulic pressure chambers 53 are in communication with each other. Also, the pilot room 72
When the hydraulic pressure becomes equal to or higher than the above-mentioned fixed value, the separation piston 71 moves to close the valve hole 70 with the valve body portion 71a, and the first
Separation valve 68. is closed, and the one-way hydraulic pressure transmission means 55FL.

The output hydraulic pressure chambers 57 of the 55 m distance, that is, the braking hydraulic pressure chambers 53 of the left front wheel brake device BFL and the right rear wheel brake device B1m are cut off.

The pilot chamber 72 of each separation valve 6B+, 68z is an oil passage 76
are commonly connected. The oil passage 76 is connected to the normally closed solenoid valve 7.
The normally closed electromagnetic valve 77 is connected to the oil passage 48 via the oil passage 7, and a third one-way valve 78 that only allows flow from the oil passage 76 to the oil passage 48 side is connected in parallel. Therefore, when the normally closed solenoid valve 77 is closed, both the heat valves 6B+ and 6
The valve 8g is in an open state, and the front left wheel brake device BFL and the right rear wheel brake device BIN are in communication with each other, and the right front wheel brake device B□ and the left rear wheel brake device B are in communication with each other. In addition, the normally closed solenoid valve 77
When the valves are energized and opened, both the heat distribution valves 6B, 68□ are closed, and the valves are closed between the left front wheel brake device BFL and the right rear wheel brake device Ba11, as well as between the right front wheel brake device BFI and the left rear wheel. The brake devices BIL are in a mutually disconnected state.

In the hydraulic pressure control valve 4, the first manual pressure action chamber 34 connected to the first output port 17 of the hydraulic pressure generating means 3 is connected to the hydraulic pressure regulating means 8.
01 and the opening/closing valve 811 to the left front wheel brake device BFL, and the second human pressure application chamber 35 is connected to the second output port 18 of the hydraulic pressure generating means 3 in the hydraulic pressure control valve 4.
is connected to the right front wheel brake device BFI via the hydraulic pressure regulating means 802 and the on-off valve 81z.

Both on-off valves 8L and 81g have basically the same configuration, and only the structure of on-off valve 811 will be described below.

The on-off valve 81+ includes a cylindrical on-off valve body 82 with both ends closed, and a one-way hydraulic pressure transmission means 55. L output hydraulic pressure chamber 57
A valve hole 83 is formed in one end wall of the on-off valve body 82 while communicating with the on-off valve body 82, and has a valve body portion 84a that can close the valve hole 83 at one end, and the other end wall of the on-off valve body 82. an opening/closing piston 84 that is slidably fitted into the opening/closing valve body 82 with its other end facing the defined pilot chamber 85;
A spring 86 is provided between the on-off valve body 82 and the on-off piston 84 to urge the on-off piston 84 toward the pilot chamber 85 side.

A valve chamber 87 that can communicate with the valve hole 83 is defined between one end wall of the on-off valve main body 82 and the on-off piston 84.
A spring 86 is housed in 7. Further, an artificial port 88 is provided in the opening/closing valve body 82 and communicates with the valve chamber 87 and is connected to the hydraulic pressure regulating means 81+.

According to the on-off valve 81+, when the hydraulic pressure in the pilot chamber 85 is lower than a certain value, the on-off piston 84 moves to the position where the valve body 84a opens the valve hole 83.
When the hydraulic pressure in the pilot chamber 85 exceeds the predetermined value, the opening/closing piston 84 moves to close the valve hole 83 with the valve body portion 84a and closes the valve.

Further, the pilot chamber 85 communicates with the oil passage 48 .

Therefore, when the hydraulic pressure in the oil passage 48, that is, the biloft chamber 85 is high, the on-off valve 81+ closes and the hydraulic pressure regulating means 8
0+ and the left front wheel brake device BFL are cut off,
When the hydraulic pressure in the oil passage 48 becomes low, the on-off valve 811 opens and the hydraulic pressure regulating means 80t and the left front wheel brake device BFL are communicated with each other.

Further, the on-off valve 81□ closes when the hydraulic pressure in the oil passage 48 is high, thereby cutting off between the hydraulic pressure regulating means 80 and the right front wheel brake device B□, and the hydraulic pressure in the oil passage 48 is reduced. When the pressure becomes low, the on-off valve 818 opens and the fluid pressure regulating means 80□ and the right front wheel brake device B□ are communicated with each other.

Also, the hydraulic pressure regulating means 80. ．． 80. have basically the same configuration, and one hydraulic pressure regulating means 80. Only the configuration of 1 will be explained, and the explanation of the configuration of the other hydraulic pressure regulating means 80□ will be omitted.

The hydraulic pressure regulating means 801 controls the output hydraulic pressure of the first output port 17 in the hydraulic pressure generating means 3, that is, the first human pressure action chamber 34.
a fourth one-way valve 90 that only allows flow of hydraulic fluid from the first manual pressure working chamber 34 to the on-off valve 811 side in response to the hydraulic pressure exceeding the set pressure P; A fifth one-way valve 91 is connected in parallel to the fourth one-way valve 90 while only allowing the flow of hydraulic oil to the one-man pressure working chamber 34 side.

The set pressure P of the fourth one-way valve 90 is the first input necessary for the hydraulic pressure control valve 4 to operate until the on-off valve 811 can be closed by the output hydraulic pressure of the output port 29 in the hydraulic pressure control valve 4. The pressure is set to a value greater than or equal to the hydraulic pressure in the pressure chamber 34. Further, the fifth one-way valve 91 causes the first and second actuating pistons 10.11 of the hydraulic pressure generating means 3 to return to the backward limit position upon completion of the braking operation.
With the first hydraulic pressure chamber 12 communicating with the reservoir R via the communication port 19, the hydraulic pressure in the brake hydraulic pressure chamber 53 in the left front wheel brake system f B F t and the right rear wheel brake system WBo is transferred to the reservoir R. It functions as a relief valve, and is set to open at a set pressure Pt.

Therefore, even if the hydraulic pressure corresponding to the set pressure P2 is acting on the brake hydraulic pressure chamber 53, the set pressure P2 is set in the brake device BFL,
B□ is set to such an extent that no dragging occurs.

Also, both hydraulic pressure regulating means 801.80□ and an on-off valve 811.
81□ is connected to the reservoir R via a sixth one-way valve 921°92. These sixth one-way valves 92+, 92g are operated by the hydraulic pressure generating means 3 upon completion of the braking operation.
The re-operation piston l0911 returns to the retraction limit position, and the first and second hydraulic chambers 12, 13 are connected to the communication port 19.20.
In order to enable the brake hydraulic pressure chambers 53 in each brake device BFL+BFI+BIL+BIN to breathe due to temperature changes, etc., the operation is performed from the reservoir R to each brake hydraulic pressure chamber 53 while communicating with the reservoir R via the reservoir R. These sixth one-way valves 92 only allow the flow of oil.
．． ．． The set pressure P set in 92□ is for each brake hydraulic pressure chamber 5.
3 is set to such an extent that it is possible to avoid a negative pressure state.

Next, the operation of this first embodiment will be explained.

First, assuming a normal braking operation with the hydraulic pressure supply source 2 operating normally, the inflow valve 62FL.

62Fm, 62. and outflow valves 63FL, 63Fm
, 63Il is demagnetized JI! (It is in the state 1 shown in the first figure, and the traction control electromagnetic switching valve 49 and the normally closed solenoid valve 77 are also in the demagnetized state 1! (in the state I shown in the first figure.

Therefore, the output port 29 of the hydraulic pressure control valve 4
, second differential pressure valve 66, oil passage 64 and inflow valve 62FL, 6
The one-way hydraulic pressure transmission means 55FL and 55□ are in communication with the input hydraulic pressure chamber 56 through the 2□, and the one-way hydraulic pressure is transmitted through the first differential pressure valve 45, the oil passage 65, and the inflow valve 62m. Means 55.

It is in a state of communicating with an input hydraulic pressure chamber 56 of 55□.

Also, both parts hot valve 68. , 68□ are open, and the brake device BFL for the left front wheel and the brake device B, l for the right rear wheel are open.
The brake hydraulic pressure chambers 53 of the right front wheel brake device B□ and the left rear wheel brake device BIL are in communication with each other.

When the brake pedal 1 is depressed in this state, the first and second actuating pistons 10 and 11 of the hydraulic pressure generating means 3 move forward, and the hydraulic pressure generated in the first hydraulic chamber 12 is accumulated in the accumulator 37. At the same time, the hydraulic pressure generated in the first manual pressure application chamber 34 of the hydraulic pressure control valve 4 is applied, and the hydraulic pressure generated in the second hydraulic pressure chamber 13 is applied to the second manual pressure application chamber 35 of the hydraulic pressure control valve 4. As a result, in the hydraulic control valve 4, the press piston 23 advances, the spool 22 is driven forward, and the communication state between the release port 3o and the output port 29 is released, and the output port 29
communicates with the input port 28, and hydraulic pressure is output from the output port 29. Furthermore, the first differential pressure valve 45 remains closed until the output hydraulic pressure of the output port 29 becomes greater than the hydraulic pressure of the reaction force chamber 32 by a predetermined value or more.

Therefore, as shown in FIG. 2, when the hydraulic pressure Pw of the first and second human pressure working chambers 34,35 reaches the value PH1 and the input port 2 communicates with the output port 29, the output from the output port 29 is The hydraulic pressure PM suddenly increases, and each on-off valve 8
1. , 81□ operates to close the valve, and each brake device B
The play in each part up to FL+ BFIll+ BIL+B□ is removed by supplying relatively high hydraulic pressure, and each brake device BFL, B□.

The initial operation of the braking piston 52 in the Bat 8 mouth becomes smooth.

At this time, the hydraulic pressure generated in the first and second hydraulic chambers 12.13 in the hydraulic pressure generating means 3 in response to the depression operation of the brake pedal 1 is controlled by the fourth one-way valve in the hydraulic pressure regulating means 801.80□. 90, the on-off valve 81. ．． 81. Each brake device BFL+Br*, until the valve closes.
B IL+ It has no effect on B□.

When the differential pressure ΔP between the output hydraulic pressure P from the output port 29 and the hydraulic pressure Pc in the reaction force chamber 32 reaches a value, the first differential pressure valve 4
When the valve 5 is opened, the hydraulic pressure of the output port 29 acts on the reaction force chamber 32. Therefore, the increased hydraulic pressure of the reaction force chamber 32 acts rearward on the spool 22, causing the spool 22 to retreat and the output port 29 to be cut off from the input port 2.

Further, as the brake pedal 1 is depressed and the hydraulic pressures in the first and second hydraulic pressure chambers 12 and 13 increase, the spool 22 moves forward again, and the output port 29 communicates with the input port 28. In this way, in response to the braking operation of the brake pedal 1, the spool 22 reciprocates between the front position where the output port 29 is communicated with the input port 28 and the rear position where the output port 29 is communicated with the release port 30. , whereby the hydraulic pressure of the hydraulic pressure supply source 2 is applied to the brake pedal 1.
It is controlled in accordance with the amount of braking operation and is output from the output port 29.

Moreover, as mentioned above, the output hydraulic pressure P from the output port 29 at the initial stage of braking. If the hydraulic pressure in the reaction force chamber 32 suddenly increases due to a sudden increase in When the force is applied, the damper piston 40 of the pressure absorbing means 24 moves in the direction away from the regulating collar 43 while contracting the damper spring 41, thereby causing the pressure piston 23 to move as shown by the solid line in FIG. It is possible to reduce the reaction force exerted on the brake pedal l, and it is possible to obtain a smooth pedal feeling.

When the first differential pressure valve 45 described above is opened, the second differential pressure valve 66 is also opened, and the on-off valve 81. ．． After the valve 812 is closed, as the first and second differential pressure valves 45.66 open,
The hydraulic pressure from the output port 29 is transferred to the oil line 48 and the second differential pressure valve 6G.
,oil! 64 and inflow valves 62FL, 62□, it acts on the input hydraulic pressure chamber 56 of the one-way hydraulic pressure transmission means 55FL, 55□, and thereby the left and right front wheel brake device BFL+B
Braking pressure can be obtained by the FI, and the hydraulic pressure from the output port 29 is controlled by the first differential pressure valve 45, the oil passage 65, and the inflow valve 62.
One-way hydraulic pressure transmission means 5511t, 55 via 1I
It acts on the input hydraulic pressure chamber 56 of mm, thereby making it possible to obtain braking pressure with the left and right rear wheel brake devices BIL+Bll. Moreover, since both the function valves 6L and 68g are open, the brake device BFL for the left front wheel and the brake device B for the right rear wheel. The braking pressures of the right front wheel brake device BFI and the left rear wheel brake devices B and L are equal. Therefore, it is possible to avoid an imbalance between the left and right braking forces.

Also, each separation valve 68. , 6B, is the one-way hydraulic pressure transmission means 5
5FL and 55□ and between the output hydraulic pressure chambers 57 of the one-way hydraulic pressure transmission means 55F11.551L, the left front wheel brake device B
When either the FL or the right rear wheel brake device B□ breaks down and the braking pressure decreases, the left front wheel brake device BF
A one-way hydraulic pressure transmission means 55Fm that equally lowers the braking pressure of the L and right rear wheel brake devices Bljl, but corresponds to the right front wheel brake device B□ and the left rear wheel brake device BIL.

Due to the hydraulic pressure from the hydraulic pressure control valve 4 acting on the input hydraulic pressure chamber 56 of 551L, the braking pressure of the right front wheel brake device B□ and the left rear wheel brake device B□ decreases. can be avoided.

In this way, the hydraulic pressure from the hydraulic pressure supply source 2 is controlled according to the amount of braking operation, and each brake device Byt,, B□,
BIL, B□ can be given to one-way hydraulic pressure transmission means 55FL, 55Fl, 5511L
, 55 mm, each brake device BFL+B□, BIL+Blm is isolated from the hydraulic circuit from the input hydraulic pressure chamber 56 to the hydraulic pressure supply source 2 by the free piston 58, so that the hydraulic oil is not supplied to the hydraulic pressure supply source 2. Gas that may get mixed into each brake device BFL, B□+BIItt
There is no negative effect on Btu.

Furthermore, by accumulating the hydraulic pressure from the first hydraulic chamber 12 of the hydraulic pressure generating means 3 in the accumulator 37, the pedal stroke of the brake pedal 1 can be ensured. There is no need for a configuration for ensuring this, and it is possible to downsize the hydraulic control valve 4.

Moreover, when a sudden reaction force acts, the accumulator 37
Due to the damper action, it is possible to avoid a sudden reaction force directly acting on the brake pedal 1.

During such braking, when the pedal force applied to the brake pedal 1 becomes excessive and the wheels are about to lock, the normally closed solenoid valve 77 is energized and opened, and the two-way heating valve 68. , 6B□, the left front wheel brake device 13rt and the right rear wheel brake device B□ are isolated, and the right front wheel brake device B□ and the left rear wheel brake device B
Isolate IL. At the same time, inflow valves 62FL, 62□, 621 corresponding to wheels that are about to lock
Energize and close the valve. That is, when the left front wheel is about to lock up, the inflow valve 62. L is closed and the one-way hydraulic pressure transmission means 55. When the front right wheel is about to lock, the inflow valve 62□ is closed to shut off the one-way hydraulic pressure transmission means 55□ and the oil passage 64, and both rear wheels are blocked. When it is about to lock, the inflow valve 628 is closed and the one-way hydraulic pressure transmission means 551L,
5511 and the oil passage 65. This suppresses an increase in braking force to prevent the wheels from becoming locked. If the wheels are still likely to enter the locked state, the corresponding outflow valve 63. L, 63Fm,
631 is excited and the one-way hydraulic pressure transmission means 55FL, 55
The tendency of the wheels to lock can be eliminated by communicating the manual hydraulic pressure chamber 56 of Fm, 551L, 55-1 with the reservoir R and reducing the braking pressure. That is, separation valve 68. ．． Close valve 6B□ and inflow valve 62yL.

By individually controlling 62□, 621 and the outflow valves 63FL, 63□, 63 kick, the left front wheel brake device B
The braking pressure of the FL and right front wheel brake devices BFI can be controlled independently, and the braking pressure of the left and right rear wheel brake devices BIL, B□ can be controlled independently of these front wheel brake devices BFL+ BFI. be able to.

During the above-mentioned braking, the hydraulic pressure supply tz due to a failure of the hydraulic pump 5, etc.
Assume that a high hydraulic pressure cannot be obtained from The braking hydraulic pressure generated in the first and second hydraulic pressure chambers 12 and 13 of the generating means 3 is applied to each brake device BFL-B**
The braking force acts directly on each side, ensuring equal braking force on the left and right sides. At this time, the one-way hydraulic pressure transmission means 55FL to 551111 are connected to each brake device Brt,
- B, 11 and the hydraulic pressure control valve 4, so that the braking pressure of each brake device BFL to B□ is the hydraulic pressure control valve 40! There is no running away.

When the brake is not applied after the braking operation is completed, the on-off valves 81+ and 81□ are opened due to a decrease in the hydraulic pressure in the oil passage 48, and the sixth one-way valve is connected to the output hydraulic pressure chamber 57 of each one-way hydraulic pressure transmission means 551L to 55111. 92. ．． Hydraulic oil can be supplied from reservoir R via 92□. In addition, the inflow valves 62FL, 62□, and the second
One-way hydraulic pressure transmission means 55FL via one-way valve 67, traction control electromagnetic switching valve 49, and hydraulic pressure control valve 4,
The input hydraulic pressure chamber 56 in 55Fl can be communicated with the reservoir R, and the one-way hydraulic pressure transmission means 551L, 551 . The input hydraulic pressure chamber 56 can be communicated with the reservoir R. Therefore, the free piston 58 in each one-way hydraulic pressure transmission means 552L to 55tm
However, it quickly moves to the manual hydraulic pressure chamber 56 side without creating a negative pressure in the output hydraulic pressure chamber 57, and therefore there is no need to provide a special reservoir. Moreover, the first one-way valve 4
6 also functions to release the hydraulic pressure in the reaction force chamber 32 in the hydraulic pressure control valve 4 to the reservoir R. Further, when the normally closed solenoid valve 77, which had been in the open state until then, is demagnetized and closed during non-braking after the end of the braking operation, each separation valve 68. , 68□ in the pilot chamber 72 is controlled by the third one-way valve 78 and the hydraulic pressure control valve 4.
is released to the reservoir R side via.

By the way, when not braking, each one-way hydraulic pressure transmission means 55FL~
55. It is also conceivable that the hydraulic pressure in the manual hydraulic pressure chamber 56 will increase due to a rise in temperature, and in that case, braking pressure will be applied if the hydraulic pressure cannot be released. However, since the set valve opening pressures of the first and second one-way valves 46, 67 are set small, they open in response to an increase in the hydraulic pressure in the input hydraulic pressure chamber 56, allowing hydraulic oil corresponding to the increased hydraulic pressure to escape. be able to.

Further, when the driving force of the engine becomes excessive and the driving wheels, that is, the left and right front wheels are about to experience excessive slip, the traction control electromagnetic switching valve 49 is energized. As a result, high hydraulic pressure from the hydraulic pressure supply source 2 is transferred to the one-way hydraulic pressure transmission means 5rt,
Acting on the input hydraulic pressure chamber 56 of 5□, braking force is generated in the brake devices B2 and B□ of the left and right front wheels, which are driving wheels, and the occurrence of excessive slip is avoided. After this, the inflow valve 62. The braking force can be controlled by controlling the excitation and demagnetization of L, 62□ and the outflow valves 63, 163Fl+.

In such a vehicle brake fluid pressure control device, a left front wheel brake device B FL and a right rear wheel brake device Ba
11, as well as between the right front wheel brake device B■ and the left rear wheel brake device BIL, are connected via separation valves ss+ and ssz, and by controlling the opening and closing of each separation valve 6L and 68g, Front wheel brake system BFL and right rear wheel brake system W B * *, and right front wheel brake system [BFL and left rear wheel brake system B
It is possible to switch between communication and disconnection between ILs. Therefore, it is possible to easily switch between a state in which the left and right braking forces are applied equally and a state in which the left and right braking forces are individually controlled, making it possible to support anti-lock control and traction control.

In the first embodiment, the first separation valve 68. of,
In addition, a second separation valve 68: was interposed between the right front wheel brake device B□ and the left rear wheel brake device BIL, but the left front wheel brake device BFL and the right front wheel brake device B□
In between, there is a first separation valve 681, and a brake device B for the left rear wheel.
A second separation valve 68□ may be interposed between the IL and the right rear wheel brake device Bl1.

In addition, the brake system for the left and right front wheels WBrL, the hydraulic system from Br* to the hydraulic pressure control valve 4, and the brake system BI for the left and right rear wheels.
The hydraulic system from L+ B1111 to hydraulic pressure control valve 4 may be different, and the entire brake system BWL+ BFL+
The hydraulic system from BIL+ Bll to the hydraulic pressure control valve 4 may be shared.

FIG. 4 shows a second embodiment of the present invention, and parts corresponding to those in the first embodiment are given the same reference numerals.

The hydraulic pressure control valve 4' includes a housing 101 and a housing 1.
01, a spool 102 and a pressing piston 103, and a pressure absorbing means 104.

The housing 101 is basically formed in a cylindrical shape with both ends closed, and the housing 101 has first holes 107 whose front ends are closed, sequentially from the front end (left end in FIG. 4). , a second hole 10B having a smaller diameter than the first hole 107 and coaxially connected to the rear end of the first hole 107, and a second hole 10B having a larger diameter than the second hole 108 and coaxially connected to the rear end of the second hole 108 and the rear end thereof. A third hole 109 with a closed end is drilled. A stepped portion 110 is provided between the first hole 107 and the second hole 108, and a stepped portion 110 is provided between the first hole 107 and the second hole 108.
A step portion 111 is provided between the holes 9 and 9, and an annular recess 112 is provided on the inner surface of the second hole 108 near the third hole 109. Moreover, the housing 101 has a release port 113 that opens into the annular recess 112 and communicates with the reservoir R.
is drilled. Further, an input port 114 that opens on the inner surface of the middle part of the second hole 108 is bored in the housing 101, and a second
An output port 115 that opens into the inner surface of the hole 108 is bored in the housing 101 . The input port 114 is connected to the hydraulic pressure supply source 2, and the output port 115 is connected to a hydraulically operated device, ie, a brake device BWL+BF, via a hydraulic circuit similar to that shown in FIG.

BIL+ Connected to Blm.

The spool 102 is slidably fitted into the second hole 108 with its outer surface in direct sliding contact with the inner surface of the second hole 10B. Moreover, the output port 11 is provided on the outer surface of the spool 102.
5 is provided with an annular groove 116 that is in continuous communication with the output port 115 and the annular recess 112, that is, the axial length of the annular groove 116 is such that when the spool 102 is in the rear position as shown in FIG. When the spool 102 is in the forward position, the output port 11 is in communication with the port 113.
5 and the input port 114 are set to communicate with each other.

The rear end of the spool 102 protrudes from the second hole 10 to the third hole 109 side, and the flange 102a and the step 111 are provided at the rear end of the spool 102 and protrude outward in the radial direction. A spring 117 is compressed between the two, and the spring force of the spring 117 biases the spool 102 toward the rear side.

The pressing piston 103 defines an input pressure acting chamber 118 between the rear end wall of the housing 101 and the third hole 1 .
The front end of the pressing piston 103 is brought into contact with the rear end of the spool 102, which is slidably fitted into the spool 102 and biased rearward by a spring 117. Therefore, the input pressure action chamber 118
A first hydraulic pressure chamber 12 of a hydraulic pressure generating means 3 that outputs hydraulic pressure in response to depression of the brake pedal 1 is connected to the first hydraulic pressure chamber 12 of the hydraulic pressure generating means 3.

The pressure absorbing means 104 includes a damper piston 120 that is slidably fitted into the front end of the second hole 108 while defining a reaction force chamber 119 between the damper piston 120 and the front end of the spool 102 . In other words, it consists of a damper spring 121 that is compressed between the front end wall of the housing 101 and the damper piston 120 to urge it toward the reaction force chamber 119, and the damper piston 120 is provided with a retracting limit when it comes into contact with the stepped portion 110. A regulating collar 120 that extends outward in the radial direction to regulate
A is provided protrudingly. Further, the housing 101 is provided with a communication port 122 that communicates a chamber defined between the front end wall of the housing 101 and the damper piston 120 with the reservoir R.

A spool 102 is provided between the reaction force chamber 119 and the reservoir R.
A shutoff valve 1°5 is provided which closes in response to the forward movement of the valve. This cutoff valve 105 communicates with the reservoir R and has a second
It is composed of a valve hole 123 that opens into the hole 108 and is bored in the housing 101, and the front end of the spool 102. When the spool 102 is in the rear position, it is in an open state, and when the spool 102 moves forward, the spool 102
is set to be closed at the front end of the

The spool 102 is provided with a differential pressure valve 106 that opens when the hydraulic pressure in the output port 115, that is, the annular groove 116 becomes greater than the hydraulic pressure in the reaction force chamber 119 by a predetermined value or more. This differential pressure valve 106 has a valve hole 124 bored in the spool 102 and communicating with the annular groove 116, and a reaction force chamber 1.
19 and provided in the spool 102
A spherical valve body 126 is housed in the valve hole 124 to open and close the valve hole 124, and a valve chamber 12 is housed in the valve chamber 12 to bias the valve body 126 in the valve closing direction.
5 and a valve spring 127 housed within the valve spring 127.

A valve hole 124 whose one end communicates with the annular groove 116
is opened into the valve chamber 125, and the valve body 126 is accommodated in the valve chamber 125 so as to be seated at the opening end of the valve hole 124 to the valve chamber 126.

In this hydraulic pressure control valve 4', a rearward spring force by the spring 117 and a rearward hydraulic pressure due to the hydraulic pressure in the reaction force chamber 119 act on the spool 102. On the other hand, hydraulic pressure in the input pressure action chamber 118 acts on the pressing piston 103 toward the front side, and the balance between the force toward the rear side and the hydraulic pressure toward the front side causes the spool 102 to moves in the axial direction.

Therefore, the hydraulic pressure toward the front side due to the hydraulic pressure in the input pressure action chamber 118 exceeds the force toward the rear side of the spool 102.
When the spool 102 moves to the front side, communication is established between the output port 115 and the input port 114, and the force toward the rear side exceeds the hydraulic pressure toward the front side due to the hydraulic pressure in the input pressure action chamber 118, and the spool 102 moves rearward. In the state of moving to the side, the output port 115 and the release port 113 are communicated with each other.

Moreover, the distance traveled by the spool 102 from its backward limit position (the position shown in the fourth figure) until it communicates the input port 114 with the output port 115! 1, and the distance j2. that the spool 102 in the retraction limit position moves until the shutoff valve 105 is shut off. and the front end of the damper piston 120 and the housing 10 when the spool 102 is at the retraction limit position.
Distance between the front end walls of 1! , the following relationship holds true.

p3>ffi, -42z Next, the operation of this second embodiment will be explained.

In the hydraulic pressure control valve 4', the press piston 103 moves forward in response to the hydraulic pressure applied to the input pressure chamber 118, and the spool 10 is in a state where its rear end is in contact with the press piston 103.
2 is driven forward. As a result, the spool 102 is
At the time of forward movement by j21, the communication state between the release port 113 and the output port 115 is released, and the output port 115 communicates with the input port 114. At that time, the cutoff valve 105 has already been cut off, and the reaction force chamber 119 is isolated from the reservoir R. As a result, the hydraulic pressure in the reaction force chamber 119 increases in accordance with the forward movement of the spool 102, but a portion of this increase in hydraulic pressure is absorbed by the forward movement of the damper piston 120, and the output liquid pressure at the output port 115 increases. The differential pressure valve 1
05 remains closed.

Therefore, as shown in FIG. 2, when the hydraulic pressure PH in the input pressure action chamber 118 reaches the value P)II and the input port 114 communicates with the output port 115, the output hydraulic pressure Pt1 from the output port 115 suddenly increases. It will increase to .

Output hydraulic pressure Pw from the output port 115 and reaction force chamber 11
When the differential pressure ΔP with the hydraulic pressure Pc of 9 reaches a value, the differential pressure valve 1
05 opens, and the hydraulic pressure in the output port 115 reaches the reaction force chamber 119.
It acts on For this reason, the spool 102 has a reaction force chamber 11
The increased hydraulic pressure of 9 acts rearward, causing the spool 102 to retreat and the output port 115 to be cut off from the input port 114. As the amount of braking operation further increases, the spool 102 moves forward again, and the output port 1
15 communicates with the input port 114. In this way, depending on the amount of braking operation, the spool 102 is moved between the forward position where the output port 115 is connected to the input port 114 and the forward position where the output port 115 is communicated with the input port 114.
is reciprocated between a position on the rear side communicating with the release port 113, and thereby the hydraulic pressure of the hydraulic pressure supply source 2 is controlled according to the amount of braking operation and is output from the output port 115.

Moreover, as described above, the output hydraulic pressure P from the output port 115 at the initial stage of braking. When rapidly increasing the reaction force chamber 119
Even if the hydraulic pressure suddenly occurs, as shown by the broken line in FIG.
The reaction force acting on the pressing piston 103, that is, the brake pedal 1, gradually increases, and the pedal feeling can be improved.

By the way, in this second embodiment, the first differential pressure valve 45 is
The one-way hydraulic pressure transmitting means 551L transmits the hydraulic pressure from the hydraulic pressure control valve 4 until the on-off valves 811 and 812 are closed.

5511.

As a modification of the second embodiment, the spring 117 in the hydraulic control valve 4' is omitted, and a protrusion protruding rearward from the rear end of the damper piston 120 is brought into contact with the front end of the spool 102. In this case, the distance between the front end of the damper piston 120 and one end wall of the housing 101! , are set larger than the moving distance of the spool 102.

FIG. 5 shows a third embodiment of the present invention, and parts corresponding to each of the above embodiments are given the same reference numerals.

The hydraulic pressure control valve 4' has a spool 102 connected to an input port 114.
and a function as a cutoff valve that cuts off the reaction force chamber 119 and the reservoir R when the output port 115 is in the forward position communicating with each other, and the output hydraulic pressure of the output port 115 is lower than the hydraulic pressure of the reaction force chamber 119 by a predetermined value. A control mechanism 130 is provided which functions as a differential pressure valve that opens the hydraulic pressure of the output port 115 and guides the hydraulic pressure of the output port 115 to the reaction force chamber 119 when the hydraulic pressure exceeds a value.

This control mechanism 130 includes a valve hole 131 bored in the spool 102 with one end communicating with the output port 115, and an opening end of the valve hole 131 to the reaction force chamber 119 which can be opened and closed. The valve body 132 to be accommodated and the damper piston 12 to bias the valve body 132 in the direction of closing the valve hole 131.
0 and the valve body 132, and an engagement member 134 provided between the damper piston 120 and the valve body 132 to regulate the amount of movement of the valve body 132.
Equipped with. One end of the retaining member 134 is engaged with a locking portion 120b protruding from the rear end of the damper piston 120 to enable relative axial movement within a regulated range.
The other end is fixed to the valve body 132.

In this control mechanism 130, when the spool 102 is in the rear position communicating between the input port 114 and the release port 113 as shown in FIG. The spool 102 is located at the position where the valve hole 131 is opened, and the spool 102 is located at the position where the valve hole 131 is opened.
4 and the output port 115, the valve body 132 is set to be in a position that allows movement in the valve opening direction and closes the valve hole 131. Therefore, when the spool 102 is in the rear position, the reaction force chamber 119 is connected to the valve hole 131 and the release port 11.
The spool 10 is connected to the reservoir R via the spool 10.
2 moves forward to the forward position, the reaction force chamber 119 is isolated from the reservoir R, and the output hydraulic pressure of the output port 115 becomes larger than the hydraulic pressure of the reaction force chamber 119 by a predetermined value or more. @The valve opening operation of the control mechanism 130 establishes communication between the output port 115 and the reaction force chamber 119.

This third embodiment can also provide the same effects as the above embodiments.

As another embodiment of the present invention, the chamber between the damper piston 120 and the housing 101 may be opened to the atmosphere instead of being communicated with the reservoir R, and the chamber between the damper piston 120 and the housing 101 may be opened to the atmosphere as a pressure absorbing means. The housing may be provided with a metal diaphragm, rubber, or the like.

In each of the embodiments described above, the present invention is applied to a brake hydraulic pressure control device, but the present invention can also be applied to a booster for a hydraulic clutch.

C8 Effects of the Invention As described above, the hydraulic control valve of the present invention is equipped with a pressure absorption means that absorbs a predetermined pressure change in the reaction force chamber, so that the pressure absorption means absorbs a predetermined pressure change in the reaction force chamber. This prevents generation of excessive reaction force and provides smooth operability.

[Brief explanation of drawings]

Fig. 1 is an overall hydraulic circuit diagram of the first embodiment of the present invention;
The figure is an output hydraulic pressure characteristic diagram of the hydraulic pressure control valve, Figure 3 is a reaction force characteristic diagram applied to the pressing piston in the hydraulic pressure control valve, and Figures 4 and 5 are the second and third embodiments of the present invention. FIG. 3 is an example overall hydraulic circuit diagram. 2... Hydraulic pressure supply source, 3... Hydraulic pressure generating means, 4, 4'
4'...Liquid pressure control valve, 21.101...Housing, 22.102...Spool, 24,104...Pressure absorption means, 28.114...Input port, 29,1
15...Output port, 30,113...Release port, 32.119...Reaction force chamber, 34.35.118...
・Input pressure action chamber, BFLI B□. ILL B□... Brake device as a hydraulically actuated device Patent applicant: Honda Motor Co., Ltd. Agent: Ken Raku, car engineer Akira Niki Figure 3 Time 2nd factor

Claims (1)

[Claims] [1] Hydraulic operated equipment (B_F_L, B_F_R, B_R
Output ports (29, 1
15), an input port (28,
114), as well as a housing (21, 101) having a release port (30, 113) leading to the reservoir (R)
and input ports (28, 114) and release ports (3
0, 113) and the input port (28, 114) and output port (29, 115).
), the spool (22, 102) is slidably fitted into the housing (21, 101) and allows axial movement between positions on the front side communicating with the output port (29).
, 115) while being connected to the spools (22, 10).
2) reaction force chambers (32, 119) formed within the housing (21, 101) to exert hydraulic pressure that urges the
), and an input pressure acting chamber (34, 35; 118) formed within the housing (21, 101) to exert a hydraulic pressure that urges the spool (22, 102) forward. In the control valve, the reaction force chamber (32, 119)
pressure absorption means (24, 10) for absorbing a predetermined pressure change of
4) A hydraulic control valve comprising: [2] The pressure absorbing means (104) has one end connected to a reaction force chamber (
A damper piston (120) that faces the housing (119) and is slidably fitted into the housing (101), and a reaction force chamber (119).
9) comprises a damper spring (121) interposed between the housing (101) and the damper piston (120) to urge the damper piston (120) to the side that contracts the volume of the damper piston (120). A hydraulic control valve according to claim [1]. [3] The pressure absorbing means (24) includes a pressing piston (36) that is slidably fitted into the housing (21) with one end facing the input pressure action chamber (34), and the pressing piston (36).
A damper piston (40) is fitted to allow relative sliding within a limited range, and a damper spring (36) is interposed between the damper piston (40) and the pressing piston (34).
41) Claim No. [1]
] Hydraulic pressure control valve described in section.