JPH06344893A - Hydraulic control valve - Google Patents

Abstract

PURPOSE:To facilitate the regulation of reaction characteristic by providing such a constitution that a liquid pressure chamber can generate a liquid pressure controlled by the external forces acting on a reaction piston, a spring for energizing the reaction piston, and a second valve body, and the liquid pressure supplied to the liquid pressure chamber. CONSTITUTION:When a liquid pressure controlled by a liquid pressure chamber 27 is supplied to a booster 2 through a first passage 17 to a port (b), the passage in a hydraulic control valve is opened. The controlled liquid pressure is supplied to the liquid pressure chamber of the booster through a hydraulic control valve 4 to assist braking force, and a high liquid pressure is generated by a tandem master cylinder. Further, an electromagnetic piston 33 is operated, whereby the valve can be opened and closed. The reaction characteristic of the hydraulic control valve 4 can be easily regulated by changing the spring force FP of a third spring 26 and the spring force FV of a second spring 23.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic control valve, and more particularly, to a hydraulic booster that boosts pressure by using hydraulic pressure supplied from a hydraulic source, a vehicle brake control modulator, and the like. The present invention relates to a simple and inexpensive hydraulic control valve which can be applied and whose control characteristics can be easily changed.

[0002]

2. Description of the Related Art Conventionally, a hydraulic booster has been used for boosting an operating force in, for example, a hydraulic brake device of an automobile, but this type of hydraulic booster is generally operated by the hydraulic pressure of a power pressure chamber. Power piston, and an input piston that operates according to the operation of the operating member,
The control valve is provided between the power piston and the input piston, and is operated by relative movement of both pistons to control the hydraulic pressure of the power pressure chamber. Then, if the input piston moves forward according to the operation of the operating member, the control valve raises the hydraulic pressure of the power pressure chamber and the power piston moves forward.At this time, the hydraulic pressure of the power pressure chamber is also compared to the input piston. The reaction force proportional to the operating force of the power piston acts on the input piston by acting on a relatively small pressure receiving surface,
The operator can detect an increase in the output of the hydraulic booster.

An example of such a hydraulic booster for a vehicle is disclosed in Japanese Utility Model Publication No. 3-31653. This hydraulic booster will be described with reference to FIG. 8. In the figure, reference numeral 150 is a power piston, 151 is an input piston, and 152 is a control valve. The power piston 150 allows the power pressure chamber 153 and the constant pressure chamber 15 to move inside the housing.
It is divided into four. The control valve 152 is the power piston 1
It is provided between 50 and the input piston 151, and operates by relative movement of both pistons 150 and 151. The control valve 152 has a valve at each end,
These valves form the first opening / closing valve 155 and the second opening / closing valve 156 together with the valve seats formed on the power piston 150 and the input piston 151, respectively. The input piston 151 and the control valve have a flow path 151a,
152a is formed, and this flow path is opened and closed by the first opening / closing valve 155 and the second opening / closing valve 156.

Now, when the brake pedal is stepped on and an operating force is applied to the input piston 151 via the input rod, the input piston 151 moves forward and abuts against the control valve 152, and the input piston 151 further moves. When it moves forward together with 152, the first on-off valve 155 closes and the second on-off valve 1
56 is opened. As a result, the hydraulic oil from the hydraulic pressure source flows into the power pressure chamber 153 through the flow passage 157 → the flow passage 158 → the chamber 159 → the flow passage 152a → the flow passage 151a to raise the hydraulic pressure in the power pressure chamber 153. Let the power piston 150
To move forward and obtain auxiliary power. Also,
At this time, the oil pressure of the power pressure chamber 153 is changed to the input piston 151.
Also, the reaction force proportional to the operating force of the power piston is applied to the input piston 151 so that the operator can detect the increase in the output of the hydraulic booster. In addition to this, there is also known a brake fluid pressure control device having a booster function as disclosed in JP-A-1-301446.
This device is capable of performing antilock control and traction control while having the function of a hydraulic booster as in the above example, and is particularly required for performing antilock control and traction control. The hydraulic pressure from the hydraulic pressure source is prevented from being applied to the seal member or the like of each valve portion during non-control, thereby improving the deformation and deterioration of the seal member and the response delay of the valve.

However, in the hydraulic booster described in the first conventional example, the valve opening / closing portions of the first opening / closing valve 155 and the second opening / closing valve 156 are cantilevered (especially the first opening / closing valve 155). Section), the guide becomes incomplete, and hydraulic pressure leaks easily from this section.
The performance is also likely to be unstable. Further, in the second conventional example, since the structure of the valve device itself is complicated and high accuracy is required, it is difficult to manufacture at low cost. Further, each of them has a problem that it is troublesome to adjust the reaction force.

[0006]

SUMMARY OF THE INVENTION Therefore, the present invention provides a small hydraulic control valve having a small stroke, high performance, easy adjustment of reaction force characteristics, and a small number of parts. The proposal is to solve the above problems. Further, the present invention proposes a hydraulic control valve which has less noise during operation (fluid noise of hydraulic pressure) and can be simplified in its overall configuration.

[0007]

Therefore, according to the present invention, the flow path between the power hydraulic pressure source 5 and the hydraulic chamber of the hydraulic operating machine is opened in accordance with the hydraulic pressure or the load from the outside to open the hydraulic pressure. A hydraulic control valve (4) capable of supplying a controlled hydraulic pressure to a chamber, the hydraulic control valve (4) being arranged in a cylinder body and operated by hydraulic pressure,
31, a first valve body 12 that connects the power hydraulic pressure source to the hydraulic chamber of the hydraulic operating machine by the movement of the working piston, and a second valve body 20 that disconnects the communication between the reservoir and the hydraulic chamber. It has a reaction force piston 25 that transmits the load of the spring 23 to the second valve body 20, and a hydraulic pressure chamber 27 that generates a controlled hydraulic pressure. The hydraulic pressure chamber 27 includes the reaction force piston 25 and this reaction force piston. A hydraulic control valve configured to generate a hydraulic pressure controlled by a spring 23 for urging 25, an external force F acting on the second valve body, and a hydraulic pressure supplied to the hydraulic chamber. This is the means for solving the problem.

[0008]

When the brake pedal 1 is stepped on, the booster piston 2a provided on the booster 2 in FIG. 1 moves to the left in the figure, whereby an initial hydraulic pressure is generated in the tandem master cylinder 3. The hydraulic pressure generated in the tandem master cylinder 3 flows into the first working hydraulic chamber 34 and the second working hydraulic chamber 35 of the hydraulic control valve 4 from d and e, and by the action of the higher hydraulic pressure P among them. The first working piston 30 and the second working piston 31 are moved to the left in the figure by the force F.
When the force F at this time becomes larger than the difference (FP-FV) between the spring force FP of the third spring 26 and the spring force FV of the second spring 23, the second valve body 20 moves leftward together with the reaction force piston 25. Move, the second valve protrusion 21 and the first valve body 12
And abut each other, and disconnect the communication of the second valve constituted by them. After that, the second valve main body 20 is integrated with the first valve main body 12 and moves leftward in the drawing against the biasing force of the first spring 19 and the third spring 26.

When the first valve body 12 is moved to the left, the first valve protrusion 14 formed on the outer periphery of the first valve body is brought into contact with the corner portion of the annular groove 13 formed on the inner peripheral surface of the cylinder body 10. The annular groove 13 and the spiral groove 15 communicate with each other. As a result, the hydraulic pressure of the accumulator 5 is changed from the port a to the annular groove 13 →
The pressure PK in the hydraulic pressure chamber 27 is increased by flowing into the hydraulic pressure chamber 27 through the spiral groove 15 → the first annular groove 16 → the first flow path 17. At this time, the pressure PK of the hydraulic chamber 27 causes the second valve body 20 to move.
A reaction force is generated, but at the same time, the load from the reaction force piston 25, which constitutes a part of the reaction force to the second valve body 20, is also reduced by the same amount, and the reaction force to the second valve body 20 is eventually reduced. The total force does not change until PK = FP / A2 (where A2 is the cross-sectional area of the reaction force piston 25). However, PK> FP / A
When it becomes 2, the reaction force piston 25 moves to the left side in the drawing by hydraulic pressure, and the second valve body 20 separates from the reaction force piston 25. Therefore, the hydraulic pressure PK acting on the second valve body 20 becomes the input F and the second. Balance with the resultant force of the spring force FV of the spring 23. That is P
K = (F / A1) + (FV / A1) (however, A
1 is the cross-sectional area of the second valve body 20, and this area A1 is configured to be substantially equal to the cross-sectional area A2 of the reaction force piston 25). As is clear from the above equation, in this embodiment, the hydraulic pressure PK in the hydraulic chamber 27 also increases as the input F increases.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a schematic view of a brake system to which a hydraulic control valve according to the first embodiment of the present invention is applied. In the figure, 1 is a brake pedal, 2 is a booster,
3 is a tandem master cylinder, 4 is a hydraulic control valve which is the main part of the present invention, 5 is an accumulator (power hydraulic pressure source), 6 is a reservoir, and the hydraulic control valve 4 is a hydraulic pressure from the tandem master cylinder 3 and a diagram. It is controlled by a signal from an electronic control unit (not shown), and realizes an operation mode of a brake (hydraulic pressure machine) described later.

In this brake system, for example, when the brake pedal 1 is depressed, an initial hydraulic pressure (operating hydraulic pressure) is generated in the tandem master cylinder 3 via the booster piston 2a, and this hydraulic pressure enters the hydraulic control valve 4. ,
As a result, as will be described later, the flow passage in the hydraulic control valve is opened, and the hydraulic pressure of the accumulator 5 is supplied to the hydraulic chamber of the booster 2 via the hydraulic control valve 4 to assist the braking force. Further, the hydraulic control valve is controlled by a signal from an electronic control unit (not shown), and anti-lock control, traction control, etc. are executed. In this system, the brake line is divided into two systems as a safety measure, and conventionally known members are used as members other than the hydraulic control valve. Therefore, detailed description of those configurations is omitted. The configuration of the first embodiment of the hydraulic control valve 4 will be described below with reference to the drawings.

[Hydraulic Control Valve 4] The hydraulic control valve 4 opens the flow passage in the valve by the hydraulic pressure from the tandem master cylinder 3 so that the hydraulic pressure from the accumulator 5 acts on the booster 2 and the hydraulic pressure by the electromagnetic force. The control valve 4 is configured to open and close the flow path in the control valve 4 to perform brake control. The hydraulic control valve 4 as the first embodiment has a valve chamber 11 in the cylinder body 10 as shown in FIG. 2, and slides in the valve chamber 11 while being guided by the valve chamber. A first valve body 12 is provided. On the outer periphery of the first valve body 12, an annular groove 1 formed on the inner peripheral surface of the cylinder body 10.
A first valve projection 14 that forms a first valve in cooperation with the third valve 3 is formed, and the annular groove 13 is connected to an accumulator 5 as a power hydraulic pressure source via a port a.
A spiral channel 15 and a first annular groove 16 communicating with the channel 15 are formed on the outer circumference of the first valve body 12, and the first annular groove 16 further includes a first channel 17 Is communicated with the inner hole 18 of the first valve body 12 via the port, and is communicated with the hydraulic operating machine via the port b. The first flow path 17
Are formed as radial passages. First valve body 12
Is urged to the right in the figure by the first spring 19 accommodated in the spring accommodating chamber 40, and in the state shown in the figure, the first valve protrusion 14 contacts the annular groove 13 to close the first valve. ing.

A second valve body 20, which is biased leftward in the figure by a second spring 23, is slidably fitted in the inner hole 18 of the first valve body 12, and this second valve Body 20
A spiral flow path 22 and a second valve protrusion 21 are formed on the outer circumference of the. A liquid chamber 24 is formed between the second valve main body 20 and the cylinder main body 10, and the liquid chamber 24 and the spiral flow path 22 are the second valve protrusion 21 and the first valve. The second valve formed by the main body 12 and the main body 12 serves to cut off communication in a manner described later. The liquid chamber 24
Communicate with the reservoir 6 via the port c. A reaction force piston 25 is arranged in the inner hole 18 of the first valve body 12 so as to face the second valve body 20, and the reaction force piston 25 is provided in a spring accommodating chamber 40 with a third spring 26. Is urged to the right in the figure by the second valve body 20.
Is configured to abut. The reaction force piston 25 and the second valve main body 20 constitute a hydraulic pressure chamber 27, and the hydraulic pressure chamber 27 is connected to the port b formed in the cylinder main body 10 via the first flow passage 17 and the first annular groove 16. It is in communication.
The port b is connected to a booster 2 as a hydraulic working machine as shown in FIG. Further, the spring accommodating chamber 40 is connected to the reservoir 6 via the port c ′.

By the way, in the present hydraulic control valve, the spring 26 for urging the reaction force piston 25 to the right in the drawing is used.
Is set to be stronger than the spring force FV of the spring 23 that biases the second valve body 20 to the left in the figure, and the second valve body 20 is moved to the left in the figure. The spring force FV of the biasing spring 23 is the first spring 1
It is set to be stronger than the spring force FW of 9 (FP>FV>
FW). Then, in the state shown in FIG. 2, the second valve body 2
The second valve protrusion 21 of 0 is separated from the first valve body 12 and is in a state where the flow path is opened, and the annular groove 1 of the first valve body 12 is
3 contacts the first valve protrusion 14 to close the flow path. A first working piston 30 slidably arranged on the cylinder body 10 is in contact with the second valve body 20, and a second working piston 31 and a third working piston are arranged in series with the first working piston 30. 32 is arranged, and the electromagnetic piston 33 is in contact with the third working piston.
A first working hydraulic chamber 34 and a second working hydraulic chamber 35 are formed between the first working piston 30, the second working piston 31, and the third working piston 32, and the respective working hydraulic chambers 34,
35 is a tandem master cylinder 3 via ports d and e
Is in communication with. The electromagnetic piston 33 can move leftward in the drawing when a current flows from the electronic control unit (not shown) to the coil 36.

Therefore, when hydraulic pressure from the tandem master cylinder 3 acts on the first working hydraulic chamber 34 and the second working hydraulic chamber 35, the first working piston 30 and the second working piston 31 are moved to the left in the figure by F. The second valve main body 20 can be pressed to the left in the figure by the force of to move the first valve and the second valve as described later. Separately from this, when the coil 36 is energized, the electromagnetic piston 33 causes the pistons 31, 32, 33 to move.
The second valve body 20 can be pressed to the left in the figure via to open and close the first valve and the second valve in the same manner.

Next, the hydraulic control valve 4 having the above structure.
The operation will be described. When the brake pedal 1 is stepped on, the booster piston 2a provided on the booster 2 in FIG. 1 moves to the left in the figure, whereby an initial hydraulic pressure is generated in the tandem master cylinder 3. The hydraulic pressure generated in the tandem master cylinder 3 flows into the first working hydraulic chamber 34 and the second working hydraulic chamber 35 of the hydraulic control valve 4 from d and e, and by the action of the higher hydraulic pressure P among them. The first working piston 30 and the second working piston 31 are moved to the left in the figure by the force F. The force F at this time is the third spring 2
When it becomes larger than the difference (FP−FV) between the spring force FP of 6 and the spring force FV of the second spring 23, the second valve body 20
Moves leftward together with the reaction force piston 25, the second valve protrusion 21 and the first valve body 12 come into contact with each other, and the communication of the second valve constituted by them is cut off. After that, the second valve body 2
0 is integrated with the first valve body 12 to form the first spring 19
And, it moves to the left in the figure against the biasing force of the third spring 26.

When the first valve body 12 is moved to the left, the first valve protrusion 14 formed on the outer periphery of the first valve body is brought into contact with the corner portion of the annular groove 13 formed on the inner peripheral surface of the cylinder body 10. The annular groove 13 and the spiral groove 15 communicate with each other. As a result, the hydraulic pressure of the accumulator 5 is changed from the port a to the annular groove 13 →
The pressure PK in the hydraulic pressure chamber 27 is increased by flowing into the hydraulic pressure chamber 27 through the spiral groove 15 → the first annular groove 16 → the first flow path 17. At this time, the pressure PK of the hydraulic chamber 27 causes the second valve body 20 to move.
A reaction force is generated, but at the same time, the load from the reaction force piston 25, which constitutes a part of the reaction force to the second valve body 20, is also reduced by the same amount, and the reaction force to the second valve body 20 is eventually reduced. The total force does not change until PK = FP / A2 (where A2 is the cross-sectional area of the reaction force piston 25). However, PK> FP / A
When it becomes 2, the reaction force piston 25 moves to the left side in the drawing by hydraulic pressure, and the second valve body 20 separates from the reaction force piston 25. Therefore, the hydraulic pressure PK acting on the second valve body 20 becomes the input F and the second. Balance with the resultant force of the spring force FV of the spring 23. That is P
K = (F / A1) + (FV / A1) (however, A
1 is a cross-sectional area of the second valve body 20, and this area A1 is configured to be substantially equal to the cross-sectional area A2 of the reaction force piston 25.
The force FW of the spring 19 is neglected because the load is small). As is clear from the above equation, in this embodiment, the hydraulic pressure PK in the hydraulic chamber 27 also increases as the input F increases.

A characteristic diagram of this hydraulic control valve is shown in FIG. As is clear from this figure, the output PK is
It is constant until the input F becomes larger than the difference between the spring force FP of the third spring 26 and the spring force FV of the second spring 23, and then starts to rise as indicated by a in the figure. From this, the pressure PK generated in the hydraulic chamber 27
It can be understood that (characteristics of the hydraulic control valve) can be easily changed by setting the FP and FV. In addition, b in the figure shows the case where the reaction force control by the spring force is not performed. By the way, looking at the relationship between the input pressure P acting on the hydraulic control valve and the output pressure PK,
When the cross-sectional area of the first working piston 30 and the second working piston 31 is A3 and the cross-sectional area of the second valve body is A1, P × A3
= PK × A1, that is, the output pressure PK = P × A3 / A1, and the output eventually becomes the ratio A3 / A1 of the sectional area of the working piston and the second valve body. Therefore, in this embodiment, A
Since 3 <A1, the output is to be reduced from the input.

When the hydraulic pressure controlled in the hydraulic pressure chamber 27 as described above is supplied to the booster 2 via the first flow passage 17 → port b, the flow passage in the hydraulic control valve is opened and controlled as described above. The hydraulic pressure thus generated is supplied to the hydraulic chamber of the booster via the hydraulic control valve 4, and the brake force is assisted to generate a high hydraulic pressure by the tandem master cylinder. In addition to this, in this embodiment, the valve can be opened and closed by operating the electromagnetic piston 33. As described above, this hydraulic control valve 4
Is the spring force FP of the third spring 26 and the second spring 2
It is possible to easily adjust the reaction force characteristics by changing the spring force FV of No. 3, and further, as the flow path, the spiral flow path 1
Since 5 and 22 are used, noise during operation (fluid noise of hydraulic pressure) is small, and the entire configuration can be simplified.

Next, a second embodiment according to the present invention will be described. As shown in FIG. 4, the hydraulic control valve 40 includes the first valve body 4 inside the cylinder body 10 as in the first embodiment.
1 and the second valve main body 42 and the reaction force piston 43 independent of the second valve main body in the second valve main body. The first spring 44 is provided between the first valve main body 41 and the cylinder main body 10.
(Spring force FW) is equal to the second valve body 42 and the reaction force piston 43.
The third spring 46 (spring force FQ) between the second valve body 42 and the cylinder body 10.
5 (spring force FP) is arranged so as to have the same valve function as that of the first embodiment. Further, in this example, the reaction force piston 43 is configured to be operable independently of the second valve body 42. In this example, the reaction force piston 43 receives the hydraulic pressure in the hydraulic chamber 47 and controls the hydraulic pressure in the control chamber 47 as described later. Also, the reaction force piston 4
3 is biased in the direction away from the contact surface of the cylinder body 10 by the third spring 46 provided inside the second valve body when not in operation, and the gap S between that surface and the valve seat of the second valve is formed. The relationship of the gap L is set to L> S.

In this hydraulic valve, when the brake pedal is depressed and an initial hydraulic pressure is generated in the tandem master cylinder, the hydraulic pressure is changed from d and e to the first hydraulic pressure chamber 34 and the second hydraulic pressure of the hydraulic control valve 4. The first working piston 30 and the second working piston 31 are moved to the left side in the figure by the force F due to the action of the higher hydraulic pressure P of the fluid flowing into the chamber 35. When the force F at this time becomes larger than the spring force FP of the second spring 45, the second valve main body 42 moves to the left and blocks the communication of the second valve. After that, the second valve main body 42 moves integrally with the first valve main body 41 to the left in the figure against the biasing force of the first spring 44 and the second spring 45.

When the first valve body 41 moves to the left, the first valve opens and the hydraulic pressure of the accumulator 5 flows into the hydraulic chamber 47. At this time, the reaction force is constant until the pressure PK in the hydraulic chamber 47 reaches a pressure that moves the reaction force piston 43 to the left in the figure against the biasing force of the third spring 46, but the pressure is When it becomes higher and PK> FQ / A1, the reaction force piston 43 moves leftward in the figure and the reaction force piston 43 abuts against the wall of the cylinder body, which causes a reaction force (however, FQ Is the spring force of the third spring 46, A
1 is the cross-sectional area of the reaction force piston 43). When the input F is further increased, the pressure in the hydraulic chamber 47 rises and the reaction force also increases. In this way, the pressure PK (characteristic of the hydraulic pressure control valve) generated in the hydraulic chamber 47 can be easily changed by setting FQ. Further, in the case of this embodiment, the output is the ratio (A of the sectional areas of the reaction force piston 43 and the working piston 30).
3 / A1) times and the output is increased more than the input.

Next, a third embodiment according to the present invention will be described with reference to FIG. This example is different in that an elastic body 56 made of rubber or the like is used in place of the third spring in the second embodiment, and that a voice coil motor 51 is used in place of the electromagnetic piston. In this hydraulic control valve, when the brake pedal is depressed and an initial hydraulic pressure is generated in the tandem master cylinder, this hydraulic pressure flows into the hydraulic control valve 4 from d and e, and by the action of the higher hydraulic pressure P among them. The second valve body 52 is moved to the left in the figure. Alternatively, separately from this, the voice coil motor 51
Operates to move the second valve body 52 to the left in the figure. As a result, the communication of the second valve 58 is cut off, and then the second valve main body 52 is integrated with the first valve main body 51 to resist the urging force of the first spring 54 and the second spring 55 and left in the figure. Move towards.

By moving the first valve body 51 to the left, the first valve 59 is opened and the hydraulic pressure of the accumulator 5 flows into the hydraulic chamber 57. At this time, the pressure PK in the hydraulic chamber 57 changes the elastic body 5
The reaction force is constant until it becomes higher than the spring force of 6, but when the pressure becomes higher, the elastic body 56 deforms, the reaction force piston 53 moves to the left in the figure, and the reaction force piston 53 moves. It abuts against the wall of, and a reaction force is generated by this. Thus, the pressure PK generated in the hydraulic chamber 57
(The characteristic of the hydraulic control valve) can be easily changed by setting the spring force of the elastic body. The voice coil motor 51 can also control the hydraulic control valve. Further, since the elastic body that also serves as the hydraulic seal is used, the configuration of the hydraulic control valve can be further simplified.

Next, a fourth embodiment according to the present invention will be described with reference to FIG. This embodiment is characterized in that the hydraulic chambers (reaction chambers) 47 and 53 of the second and third embodiments are arranged outside the valve body. In FIG. 6, reference numeral 60 denotes a cylinder main body, and in this cylinder main body 60, a first valve main body 61 and a second valve main body 62 are arranged in the same manner as in the previous embodiment. 64 is formed. Further, the spring accommodating chamber 65 and the liquid chamber 66 are communicated with each other by a flow passage 67 formed in the second valve body 62. Also,
In the cylinder body 60, there is a hydraulic chamber 68 communicating with the port b.
The reaction force piston 69 disposed in the hydraulic chamber 68 is disposed so as to face the second valve body 62. The reaction piston 69 is biased to the left in the figure by a spring 70.

Therefore, in this hydraulic valve, when the brake pedal is depressed and the initial hydraulic pressure is generated in the tandem master cylinder, the hydraulic pressure is changed from d and e to the first hydraulic pressure chamber 71 and the second hydraulic pressure of the hydraulic control valve. Flow into chamber 72,
Of these, the action of the higher hydraulic pressure P causes the first working piston 7
3. The second working piston 74 is moved to the left in the figure by the force F. The force F at this time is the spring force F of the third spring 26.
When it becomes larger than P, the second valve body 62 moves to the left and blocks the communication of the second valve 64. After that, the second valve body 62 is integrated with the first valve body 61, and the first spring 1
9. It moves to the left in the figure against the urging force of the second spring 26.

When the first valve body 61 moves to the left, the first valve 63 opens and the hydraulic pressure of the accumulator flows into the hydraulic chamber 70 through the port b. At this time, the pressure PK in the hydraulic chamber 70 resists the urging force of the spring 70 and the reaction force piston 6
The reaction force is constant until the pressure for moving 9 to the right in the figure is reached, but when the pressure becomes higher and PK> FQ / A1, the reaction force piston 69 moves to the right in the figure and the reaction force piston 69 contacts the second valve body 62, and a reaction force is thereby generated (where FQ is the spring force of the spring 68 and A1 is the cross-sectional area of the reaction force piston 69). Thus, also in this embodiment, the hydraulic pressure in the hydraulic chamber 70 is controlled by the relationship between the cross-sectional area of the reaction force piston 69 and the spring force of the spring 68 for the above-mentioned reason. Further, since the hydraulic chamber (reaction chamber) 70 is arranged outside the valve body, the structure of the hydraulic control valve is simplified and the manufacturing cost can be reduced.

Further, a fifth embodiment according to the present invention will be described with reference to FIG. In this embodiment, the hydraulic control valve of the first embodiment is integrally incorporated in the booster piston. In FIG. 7, a booster piston 2a is arranged in the tandem master cylinder 3,
In this booster piston 2a, a hydraulic control valve having the same structure and function as in the first embodiment described above is incorporated. In the figure, 12 'is the first valve body, 17' is the first flow passage, 20 'is the second valve body, 25' is the reaction force piston,
a is a port that communicates with the accumulator, b is a port that communicates with a hydraulic chamber 80 as a hydraulic operating machine (booster), and the second valve body 20 ′ has an input piston 151.
Is in contact with.

Therefore, in this hydraulic control valve, when the brake pedal 1 is stepped on, the input piston 151 in FIG. 7 moves to the left in the figure, and the second valve body 20 ',
The first valve body 12 'is moved leftward in the drawing against the biasing force of the spring. As a result, the port a becomes the first channel 17 '
Fluid chamber 80 because it also communicates with port b
The hydraulic pressure is supplied from the accumulator to the left side of the booster piston to assist the braking force. The hydraulic pressure control in the hydraulic chamber 80 at this time is performed in the hydraulic control valve as in the first embodiment. In this embodiment, since the hydraulic control valve is incorporated in the booster piston, the entire structure of the device can be downsized and the manufacturing cost can be reduced.

[0030]

According to this embodiment having the above-described structure, the valve element has a small stroke but high performance,
Further, it is possible to configure a small hydraulic control valve in which the reaction force characteristics can be easily adjusted and the number of parts is small. Further, it is possible to provide a hydraulic control valve that produces less noise (fluid noise of hydraulic pressure) at the time of operation, and so on.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram of a brake control device as a first embodiment according to the present invention.

FIG. 2 is a detailed view of a hydraulic control valve as a first embodiment in FIG.

FIG. 3 is a characteristic diagram of a hydraulic control valve.

FIG. 4 is a detailed view of a hydraulic control valve as a second embodiment according to the present invention.

FIG. 5 is a detailed view of a hydraulic control valve as a third embodiment according to the present invention.

FIG. 6 is a detailed view of a hydraulic control valve as a fourth embodiment according to the present invention.

FIG. 7 is a detailed view of a hydraulic control valve as a fifth embodiment according to the present invention.

FIG. 8 is a detailed view of a conventional booster.

[Explanation of symbols]

 1 Brake Pedal 2 Booster 3 Tandem Master Cylinder 4 Hydraulic Control Valve 12 First Valve Body 20 Second Valve Body 25 Reaction Force Piston 19 First Spring 26 Second Spring 23 Third Spring

Claims (6)

[Claims] 1. A controlled hydraulic pressure can be supplied to the hydraulic chamber by opening a flow path between the power hydraulic pressure source 5 and the hydraulic chamber of the hydraulic operating machine according to the hydraulic pressure or a load from the outside. A hydraulic control valve 4, the hydraulic control valve 4
Is a working piston 30, 31 arranged in the cylinder body and actuated by working fluid pressure; and a first valve body 12 for communicating a power hydraulic pressure source and a hydraulic chamber of a hydraulic working machine by the movement of the working piston. , The second valve body 20 for disconnecting the communication between the reservoir and the hydraulic chamber, and the load of the spring 23 on the second valve body 20.
Has a reaction force piston 25 for transmitting to the reaction force and a hydraulic pressure chamber 27 for generating a controlled hydraulic pressure. The hydraulic pressure chamber 27 includes the reaction force piston 25 and a spring 23 for urging the reaction force piston 25.
And a hydraulic control valve configured to generate a hydraulic pressure controlled by an external force F acting on the second valve body and a hydraulic pressure supplied to the hydraulic chamber. 2. The cylinder body of the hydraulic control valve 4 is configured as a booster piston, and the hydraulic pressure controlled by the hydraulic control valve 4 is configured to act on the booster piston which also serves as the cylinder body. The hydraulic control valve according to claim 1, wherein: 3. The fluid pressure chamber 27 includes the first valve body 12,
The hydraulic control valve according to any one of claims 1 and 2, which is configured by the second valve body 20 and the reaction force piston 25. 4. The fluid pressure chamber 27 is provided in the first valve body 12,
The hydraulic control valve according to claim 1, wherein the hydraulic control valve is separated from the second valve body 20 and arranged at another position in the cylinder body. 5. A hydraulic control capable of opening a flow path between the power hydraulic pressure source 5 and a hydraulic chamber of a hydraulic operating machine according to the operating hydraulic pressure or a load from the outside to supply a controlled hydraulic pressure to the hydraulic chamber. The hydraulic control valve 4 is a valve 4, which is disposed in the cylinder body and is operated by a hydraulic pressure. The hydraulic piston is a hydraulic power source and a hydraulic chamber of a hydraulic operating machine. A fluid pressure chamber 27 that communicates with the fluid pressure chamber 27 and generates a controlled fluid pressure;
Second valve body 20 and reaction force piston 2 for controlling the hydraulic pressure of the
5, the hydraulic chamber 27 is provided with a second spring 23 for urging the second valve body 20 and a third spring 26 for urging the reaction force piston 25. The load of each spring is set to the second spring 23. <Hydraulic control valve characterized by being the third spring 26. 6. The hydraulic control valve 4 is configured to be operated by a mechanical input, and at the same time, a first valve and a second valve in the hydraulic control valve can be opened and closed by a signal from an electronic control unit. The hydraulic control valve according to any one of claims 1 to 5.