JPH06129562A - Liquid pressure control valve - Google Patents

Abstract

PURPOSE:To meet the requirements of increasing the attraction force of a solenoid and reducing the leak amount from around a spool by furnishing a minor diameter spool and a plunger having a greater diameter than the spool. CONSTITUTION:A valve spool 4 is provided separately from a plunger 54, wherein the former is formed with a smaller diameter than the latter 54. This enables suppressing the leak amount around the valve spool while a large attracting force is secured. An output port 11c opening at a throttle land 4c is given a greater diameter than the bore of a valve hole 11 and formed in the penetrative state in the direction perpendicularly intersecting the valve hole 11. Thereby the output liquid pressure is applied uniformly to the whole periphery of the valve spool to prevent generation of a lateral force acting on the valve spool, and poor operating performance as well as generation of hysteresis is precluded.

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 capable of controlling an output hydraulic pressure with respect to a supply hydraulic pressure.

[0002]

2. Description of the Related Art Conventionally, as a hydraulic pressure control valve, for example, one disclosed in Japanese Patent Laid-Open No. 3-121969 has been known.

This conventional hydraulic pressure control valve is incorporated in a brake hydraulic pressure control device for the purpose of controlling the hydraulic pressure supplied to the wheel cylinder with respect to the master cylinder pressure. As a result, a large-diameter spool that adjusts the output hydraulic pressure supplied to the wheel cylinder by sliding, a return spring that presses the spool in a direction to increase the output hydraulic pressure, and a plunger portion are integrally formed with the large-diameter spool. And a solenoid that pushes back the spool in the direction of reducing the output hydraulic pressure by the suction force.

[0004]

However, in such a conventional hydraulic control valve, as described above, since the spool and the plunger portion are integrally formed with the same diameter, There was a problem as described in.

That is, generally, in order to increase the suction force of the solenoid, it is necessary to increase the diameter of the plunger portion, but in order to reduce the amount of leakage around the spool, it is necessary to reduce the spool diameter. If the spool and the plunger portion have the same diameter integrated structure, both requirements cannot be satisfied at the same time.

Further, since the conventional hydraulic control valve does not have a hydraulic booster function, this hydraulic control valve is used as a hydraulic control valve for an anti-skid brake system (hereinafter sometimes abbreviated as ABS). When using it, it is necessary to incorporate a hydraulic booster mechanism that increases the master cylinder pressure into the system as a separate member, which increases the weight of the entire system and requires a large space as a whole. However, there is a problem that the vehicle mountability is deteriorated.

The present invention has been made by paying attention to the above-mentioned conventional problems, and is a hydraulic pressure capable of simultaneously satisfying both the requirements of increasing the solenoid attraction force and reducing the leak amount from around the spool. A first object is to provide a control valve, and a second object is to provide a hydraulic control valve capable of reducing the weight and size of the entire system and improving the vehicle mountability.

[0008]

In order to achieve the above-mentioned object, in the hydraulic pressure control valve of the present invention, a small diameter that regulates the output hydraulic pressure by sliding the hydraulic pressure from the hydraulic pressure source as the source. The spool, pressing means for pressing the spool in a direction to increase the output hydraulic pressure, and one end surface side of the spool, which is slidably provided on the shaft center part, and the protruding end surface of the spool contacts the stopper and the other end surface side When the output hydraulic pressure is received, the reaction force piston that pushes back the spool in the direction of reducing the output hydraulic pressure by the received pressure reaction force, and the plunger portion having a diameter larger than the spool at least abut on the other end face side of the spool. The means provided with the solenoid that is provided in this state and that pushes back the spool in the direction of reducing the output hydraulic pressure by the suction force.

Further, in the hydraulic control valve according to a second aspect of the present invention, the pressing means is constituted by a spring which constantly presses the spool in a direction to increase the output hydraulic pressure.

Further, in the hydraulic control valve according to a third aspect of the present invention, the pressing means is composed of a pilot piston that presses the spool in a direction to increase the output hydraulic pressure by receiving the hydraulic pressure on one end surface, The pressure receiving area of the pilot piston is made larger than the pressure receiving area of the reaction force piston at a predetermined magnification.

[0011]

Since the hydraulic control valve of the present invention is constructed as described above, the spool is pressed by the pressing means in the direction of increasing the output hydraulic pressure when the solenoid is not energized.

That is, when the pressing means is a spring as described in claim 2, the spool is always in a state of being pressed and slid in the direction in which the output hydraulic pressure is maximized.

Further, when the pressing means is a pilot piston as set forth in claim 3, the spool is pressed and slid in a direction in which the output hydraulic pressure is increased in proportion to the hydraulic pressure received by the pilot piston. . That is, the spool is arranged at a position where the pressing force of the pilot piston which receives the hydraulic pressure from the supply source and the pressure receiving reaction force of the reaction force piston which receives the output hydraulic pressure are balanced. In this case, since the pressure receiving area of the pilot piston is larger than that of the reaction force piston, the output hydraulic pressure with respect to the hydraulic pressure acting on the pilot piston is increased by a ratio according to the pressure receiving area ratio of both pistons. As a result, the hydraulic pressure control valve can exert a hydraulic pressure booster function that boosts the supplied hydraulic pressure.

Next, when the solenoid is energized, the spool is pushed back in the direction of reducing the output hydraulic pressure by the suction force of the plunger portion, that is, the output hydraulic pressure is reduced in inverse proportion to the value of the energized current. be able to.

Further, in the hydraulic control valve of the present invention, since the spool has a small diameter, the amount of leakage around the spool is small, and the diameter of the plunger portion is large, so that the suction force of the solenoid is large.

[0016]

Embodiments of the present invention will now be described in detail with reference to the drawings. (First Embodiment) First, the configuration of the first embodiment will be described. In this embodiment, the hydraulic pressure control valve of the present invention is shown in FIG.
A case where the present invention is applied to the ABS hydraulic pressure control valve 7 (7a, 7b) in the brake hydraulic pressure control system shown in FIG.

FIG. 1 shows a hydraulic pressure control valve 7 according to a first embodiment of the present invention.
2 is a cross-sectional view (cross-sectional view taken along line FF of FIG. 2), FIG.
1 is a view from the direction of arrow G in FIG. 1, and in both figures, 1 is a valve body, and a valve hole 11 is formed in this valve body 1. The valve hole 11 is formed with a hydraulic pressure supply port 11a and a drain port 11b, and an output port 11c is formed between the ports 11a and 11b.

As shown in the system diagram of FIG. 3, the hydraulic pressure supply port 11a is connected to the master cylinder 2 via the master cylinder pressure connection port 1d, and the drain port 11b is connected to the drain side connection port 1b. It is connected to the drain tank T via
The output port 11c is connected to the wheel cylinder 3 via the wheel side connection port 1c.

A valve spool 4 is slidably incorporated in the valve hole 11. The valve spool 4 has an annular communication groove 4a for communicating between the hydraulic pressure supply port 11a and the output port 11c, and the output port 1
An annular communication groove 4b for communicating between 1c and the drain port 11b is formed, and both annular communication grooves 4a, 4b are formed.
A diaphragm land 4c that overlaps the output port 11c is formed between them, and variable diaphragms s and t are formed between the diaphragm land 4c and the output port 11c.

That is, when the valve spool 4 slides to the left in FIG. 1, the variable throttle s is opened with the variable throttle s kept closed, whereby the master cylinder pressure is supplied to the output port 11c side and the wheel is rotated. When the fluid pressure of the cylinder 3 is changed to increase, while the valve spool 4 slides to the right in FIG. 1 contrary to the above, the variable throttle t is closed and the variable throttle s is opened, whereby When the supply of the master cylinder pressure is stopped and the liquid is discharged from the output port 11c side to the drain port 11b side, the hydraulic pressure of the wheel cylinder 3 is decreased.

The output port 11c opening in the throttle land 4c is formed to have a diameter larger than that of the valve hole 11, and is formed so as to penetrate the valve hole 11 in a direction orthogonal to the valve spool. The output hydraulic pressure is evenly applied to the entire outer circumference of the valve 4, so that generation of lateral force on the valve spool 4 can be prevented. This is aimed at this improvement because it becomes difficult to insert a tool into the valve hole shaft to machine the land when the valve hole diameter becomes smaller. The hydraulic pressure supply port 11a and the drain port 11b are connected to the valve hole 1
Although the diameter is smaller than 1, it is formed in an abutting state, but since it opens in the annular communication grooves 4a, 4b formed in the valve spool 4, the hydraulic pressure acts evenly on the entire outer circumference of the valve spool 4. Therefore, the lateral force does not act on the valve spool 4.

One end surface of the valve spool 4 (see FIG.
At the outer peripheral position of the right end face), an ABS solenoid 5 for sliding the valve spool 4 by the suction force generated by energization is provided. When the solenoid 5 is energized, the valve spool 4 moves to the right in FIG. Slide in the direction to push back to output port 11c (wheel cylinder 3 side)
Reduce the output hydraulic pressure of.

The solenoid 5 includes a solenoid body portion B, a coil portion K, and a plunger portion 54.

The solenoid body portion B has a base 51 fixed to the end surface of the valve body 1 with a bolt 60, an intermediate cylinder 56 fitted and fixed to the base 51, and a suction fitted to the intermediate cylinder 56. And the member 58.

The coil portion K comprises a coil 53 for generating a magnetic field, a hobbin 55 made of a non-magnetic material around which the coil 53 is wound, and a coil casing 52 covering the outer periphery of the hobbin 55. .

The valve hole 1 is provided at the center of the base 51.
Through hole 57 forming a plunger chamber 62 having a diameter larger than 1
The plunger portion 54 is slidably provided in the through hole 57 via a bush 100.

The attraction member 58, the coil casing 52, the base 51, the bush 100, and the plunger portion 54 are each made of a magnetic material, and these members form a magnetic loop. It has become. A magnetic leakage portion 61 having a triangular cross section for generating a force for attracting the plunger portion 54 is formed on the inner peripheral end surface of the attraction member 58, and the attraction member 5 is formed.
A back chamber 16b is formed between the inner inner peripheral end surface of 8 and the end surface of the plunger portion 54, and the back chamber 16b and the plunger chamber 62 communicate with each other formed at the axial center portion of the plunger portion 54. The holes 54a are in communication with each other.

A return spring 4d as a pressing member is interposed between the suction member 58 and the plunger portion 54 in a compressed state, and the repulsive force presses the valve spool 4 leftward in FIG. I am energetic. Therefore, when the solenoid 5 is not energized, the valve spool 4 is pressed to the left in FIG. 1, and the output hydraulic pressure of the output port 11c (wheel cylinder 3) is the same as the master cylinder hydraulic pressure. Has become.

On the end surface (left end surface in FIG. 1) of the valve body 1 opposite to the side where the solenoid 5 is provided, a back chamber cover 17 forming a back chamber 16a communicating with the valve hole 11 is bolted. The stopper portion 17a is attached and fixed at 60, and a stopper portion 17a is provided at the axial center portion of the inner end surface of the back chamber cover 17 so as to project toward the end surface direction of the valve spool 4, while facing the stopper portion 17a. A piston sliding hole 63 communicating with the output port 11c is formed at the axial center of the end face of the valve spool 4, and a cylindrical reaction force piston 64 is slidably provided in the piston sliding hole 63. There is.

The back chamber 16a is communicated with the drain port 11b and the plunger chamber 62 through the damping prevention orifice 12 of the valve spool 4, so that the movement of the valve spool 4 is damped. There is.

Next, the operation of the embodiment will be described.

(B) When the solenoid is not energized When the energization current to the solenoid 5 is 0, the hydraulic pressure control valve 7 pushes the valve spool 4 to the left in FIG. 1 by the set force of the return spring 4d. The variable throttle s between the output port 11c and the drain port 11b is fully closed and the variable throttle t between the output port 11c and the hydraulic pressure supply port 11a is fully open. The master cylinder 2 is in a state where the increased master cylinder pressure is directly supplied to each wheel cylinder 3.

At this time, the reaction force piston 64 receives the output hydraulic pressure on the output port 11c side and is pressed and slid to the left in FIG. 1, and when the sliding is restricted by the stopper portion 17a, The pressure receiving reaction force pushes and slides the valve spool 4 to the right in FIG. 1, whereby the end surface of the valve spool 4 can be brought into contact with the end surface of the plunger portion 54. Since the urging force of the return spring 4d is set to a value larger than the pressure reaction force from the master cylinder 2 with respect to the maximum master cylinder pressure, the movement of the valve spool 4 is fixed even if the supply fluid pressure changes. Thus, the master cylinder pressure from the master cylinder 2 is supplied to the wheel cylinder 3 side as it is.

(B) When energizing the solenoid When the solenoid 5 is energized, a magnetic loop is formed by the adsorbing member 58, the coil casing 52, the base 51, the bush 100, and the plunger portion 54, and the inside of the adsorbing member 58 is formed. An attractive force is generated in the magnetic leakage portion 61 having a triangular cross section formed on the end face, and this attractive force causes the plunger portion 54 to move.
Is pressed rightward in FIG. 1 against the urging force of the return spring 4d.

The return current is small because the energizing current is small and the force obtained by adding the suction force to the pressure-receiving reaction force.
While the plunger portion 54 and the valve spool 4 do not slide while the force is smaller than the urging force, the output hydraulic pressure is kept in the same state as the supply hydraulic pressure as shown in FIG. As it is raised, the force obtained by adding the suction force to the pressure receiving reaction force becomes larger than the urging force of the return spring 4d, and the valve spool 4 is slid to the right in FIG.
The opening of the variable throttle t between the output port 11c and the hydraulic pressure supply port 11a is reduced to reduce the hydraulic pressure supply to the output port 11c, and the variable throttle s between the output port 11c and the drain port 11b is reduced. Since the discharge amount in the drain port 11b direction gradually increases due to the change to the opening direction, the output hydraulic pressure of the output port 11c decreases in inverse proportion to the increase of the energization current to the solenoid 5, as shown in b of FIG. .

That is, the valve spool 4 is arranged at a position where the pressure receiving reaction force of the reaction force piston 64 + the suction force and the setting force of the return spring 4d are in equilibrium, that is, the valve spool 4 corresponds to the suction force in FIG. It is pushed back to the right and the output hydraulic pressure decreases.

Next, the system (brake hydraulic pressure control system) diagram of FIG. 3 to which the hydraulic pressure control valve of this embodiment is applied will be described.

That is, this brake fluid pressure control system is
In addition to the front side hydraulic pressure control valves 7a, 7a and the rear side hydraulic pressure control valves 7b, 7b, a hydraulic pressure booster 2b is provided to increase the master cylinder pressure in accordance with the operation amount of the brake pedal 2a. And a wheel cylinder 3, which is provided in the brake device for each wheel.
3, 3, 3 and a reservoir tank 20 for temporarily storing the brake fluid returning from the wheel cylinder 3 when depressurizing,
A pump 21 that returns the brake fluid stored in the reservoir tank to the master cylinder 2 by depressurization, an accumulator 22 that prevents the fluid pressure generated from the pump 21 from directly applying to the master cylinder 2, and a brake fluid pressure when the pump 21 discharges the fluid. The inlet valve 23 that prevents the return to the reservoir tank 20 side, the outlet valve 24 that prevents the brake fluid discharged from the pump 21 from returning to the pump 21 again, and the hydraulic control valve 7 are bypassed at the time of depressurizing the wheel cylinder fluid. A bypass check valve 25 for returning the pressure to the master cylinder 2; and a feeling valve 26 for preventing the high hydraulic pressure generated from the pump 21 from being directly applied to the master cylinder 2 and for preventing residual pressure from remaining when the brake operation is released. , Disconnect the brake system on the rear side from the hydraulic pressure of the master cylinder 2. The TCS first switching valve 27 that is released, the TCS second switching valve 28 that generates braking force by supplying the hydraulic pressure from the hydraulic booster 2b to the rear wheel cylinder 3, the brake controller 13, and the vehicle speed. It has a sensor 18 and a wheel rotation sensor 19.

Next, the operation of the system (brake hydraulic pressure control system) of FIG. 3 to which the hydraulic pressure control valve 7 of the embodiment is applied will be described. (A) At the time of normal braking The current supplied to the solenoid 5 is zero. In the above, in each hydraulic control valve 7, the master cylinder pressure increased from the master cylinder 2 is directly supplied to each wheel cylinder 3 side.

Therefore, when the brake pedal 2a is depressed in this state, a braking force boosted according to the depression force is generated.

(C) During ABS operation During sudden braking or braking on a low μ road such as a snowy road, the frictional resistance of the tire against the road surface is smaller than the braking frictional resistance of the wheel by the braking device, and the tire slips. Then, the wheels are locked.

Therefore, AB of the brake controller 13
In the S control unit, when the slip state of the tire is detected from the vehicle speed detected by the vehicle speed sensor 18 and the wheel rotation speed detected by the wheel rotation sensor 19, the hydraulic pressure control valve 7 is detected according to the slip amount. The ABS solenoid 5 is energized.

As described above, when the ABS solenoid 5 is energized, the output hydraulic pressure of the output port 11c decreases in inverse proportion to the increase of the energized current. As a result, each hydraulic control valve 7 Output hydraulic pressure (wheel cylinder 3
(Supplied hydraulic pressure to the wheel) decreases and the braking force of the wheel decreases, so that the slip amount of the wheel decreases.

AB of the brake controller 13
In the S control unit, the detected slip amount and the preset proper slip amount (braking force) are constantly compared, and the energization current value for the ABS solenoid 5 is adjusted so that the detected slip amount becomes the proper slip amount. The increase / decrease change control is performed.

As described above, the hydraulic pressure control valve of the first embodiment has the following effects.

The valve spool 4 and the plunger portion 54
Is a separate body, and for the large-diameter plunger part 54,
By forming the valve spool 4 with a small diameter, it is possible to suppress a leak amount around the valve spool 4 while securing a large suction force.

The output port 11c opening in the throttle land 4c is formed to have a diameter larger than the diameter of the valve hole 11, and the valve hole 11 is formed in a penetrating state in a direction orthogonal to the outer circumference of the valve spool 4. The output hydraulic pressure is made to act evenly on the whole, and thereby, it is possible to prevent the generation of lateral force on the valve spool 4 and prevent malfunction or hysteresis. Further, even if the valve hole diameter becomes small, the valve groove structure can be easily formed.

Next, a modification of the first embodiment shown in FIG. 5 will be described.

That is, in this modification, the valve spool 4
Insert the end of the into the hole in the axial center of the plunger 54,
Both are connected and integrated by a knock pin 29,
Therefore, the communication hole 54a is formed in the outer peripheral portion other than the axial center portion.

(Second Embodiment) Next, the hydraulic control valve of the second embodiment of the present invention shown in FIG. 6 will be described. In this embodiment, the same components as those of the first embodiment are designated by the same reference numerals, the description thereof will be omitted, and only different points will be described.

First, in this embodiment, the return spring 4d has the back chamber cover 1 in the direction opposite to that of the first embodiment.
7 and the end surface of the valve spool 4.

Further, in this embodiment, a pilot chamber 66 in which a cylindrical pilot piston 65 (pressing member) is slidably inserted is provided in the axial center portion of the suction member 58 facing the inner side of the plunger portion 54. A master cylinder pressure connection port 1d is formed on the outer end surface of the suction member 58 and communicates with the pilot chamber 66 through an orifice 68 that prevents damping of the pilot piston 65. And this master cylinder pressure connection port 1
d is the master cylinder pressure fluid passage 15b as shown in FIG.
Is connected to the master cylinder 2 via.

On the other hand, the hydraulic pressure supply port 11a is connected to the external hydraulic pressure supply source 6 via the external hydraulic pressure connection port 1a and the hydraulic pressure supply liquid passage 14 as shown in the system diagram of FIG.

Further, the coil portion K of this embodiment is detachably mounted on the outer circumference of the solenoid body portion B and can be replaced by a fastening nut 59 screwed onto the outer circumference of the end portion of the suction member 58. It is installed.

Next, the system (brake hydraulic pressure control system) diagram of FIG. 7 to which the hydraulic pressure control valve 7 of this embodiment is applied will be described.

That is, this brake fluid pressure control system
In addition to the front-side hydraulic pressure control valves 7a, 7a and the rear-side hydraulic pressure control valves 7b, 7b, a master cylinder 2 for generating a master cylinder pressure according to an operation amount of a brake pedal 2a, and a brake for each wheel. Wheel cylinders 3, 3, 3, 3 provided in the device, an external hydraulic pressure supply source 6, fail-safe valves 10a, 10b, and a brake controller 1
3 and 3.

The external hydraulic pressure supply source 6 is a hydraulic pump 6a.
And a check valve 6b for preventing backflow, an accumulator 6c for storing high-pressure liquid, and a relief valve 6e, which are interposed in the hydraulic pressure supply liquid passage 14 of the hydraulic pump 6a. Further, in the middle of both master cylinder pressure fluid passages 15a and 15b which are output from the master cylinder 2 by two systems for driving wheels and driven wheels, a hydraulic damper for eliminating a feeling of stone depression when the brake pedal 2a is operated. Da and Db are interposed.

The hydraulic pressure supply port 11a is connected to the hydraulic pressure supply liquid passage 14 of the external hydraulic pressure supply source 6 via the external hydraulic pressure connection port 1a, and the drain port 11b is connected to the drain side connection port 1b. The output port 11c is connected to the wheel cylinder 3 via the wheel side connection port 1c.

The fail-safe valves 10a and 10b are
When the hydraulic pressure supplied from the external hydraulic pressure supply source 6 is interrupted due to a failure of the hydraulic pressure pump 6a or the like, the master cylinder pressure is directly switched to the hydraulic pressure supply port 11a to switch the brake operation. It serves to secure the

As shown in FIG. 7, the brake controller 13 has an ABS control section for controlling the drive of the ABS solenoid 5 based on the input signals from the vehicle speed sensor 18 and the wheel rotation sensor 19.

Next, the operation of the embodiment will be described.

(A) During non-braking Since the master cylinder pressure of the master cylinder 2 of each wheel is 0 when the brake pedal 2a is not depressed, the set force of the return spring 4d is set in each hydraulic pressure control valve 7a, 7b. The valve spool 4 is pushed and slid to the right as shown in FIG.
The output hydraulic pressure of c is O.

Therefore, the hydraulic pressure supplied to each wheel cylinder 3 is also O, and the brake device is inoperative.

(B) During normal braking When the brake pedal 2a is depressed, the master cylinder pressure of the master cylinder 2 rises according to the pedaling force, and the hydraulic pressure control valves 7a and 7b change this hydraulic pressure to the master cylinder pressure. The pilot piston 65 receives pressure via the connection port 1d and the orifice 68, and pushes and slides the pilot piston 65 leftward in FIG. 6, so that this pressing force resists the setting force of the return spring 4d. Plunger part 5
6 and the valve spool 4 are slid to the left in FIG. 6, whereby the output hydraulic pressure of the output port 11c is increased and the hydraulic pressure supplied to each wheel cylinder 3 is increased.

On the other hand, the output hydraulic pressure of the output port 11c is received by the reaction force piston 64, and the reaction force piston 64
6 is slid to the left in FIG. 6, and when the sliding of the reaction force piston 64 is restricted by the stopper 17a,
The pressure receiving reaction force of the reaction force piston 64 acts on the valve spool 4 as a feedback force, whereby the valve spool 4 is pushed back to the right in FIG.

That is, in the valve spool 4, the pressing force of the pilot piston 65 and the reaction force of the reaction force piston 64 +
The return spring 4d is arranged at a position balanced with the setting force of the return spring 4d. In this case, since the pressure receiving area of the pilot piston 65 is larger than that of the reaction force piston 64,
As shown in the boosting function characteristic of FIG. 8, the output hydraulic pressure (W / CYL pressure) with respect to the master cylinder pressure (M / CYL pressure) is increased by the pressure receiving area ratio of the pistons 65 and 64. As a result, the master cylinder pressure is supplied to the wheel cylinders 3 in a state in which the master cylinder pressure is increased at a predetermined magnification (about 9 times in the embodiment), that is, a boosting function for boosting the pedal effort of the brake pedal 2a ( The hydraulic booster function) is exerted and a strong braking force can be obtained.

(C) ABS operation At the time of sudden braking or braking on a low μ road such as a snowy road, the frictional resistance of the tire against the road surface is smaller than the braking frictional resistance of the wheel by the braking device and the tire slips. Then, the wheels are locked.

Therefore, AB of the brake controller 13
In the S control unit, when the slip state of the tire is detected from the vehicle speed detected by the vehicle speed sensor 18 and the wheel rotation speed detected by the wheel rotation sensor 19, each hydraulic pressure control valve is detected according to the slip amount. The ABS solenoids 5 of 7a and 7b are energized.

In this way, when the ABS solenoid 5 is energized, the attracting member 58, the coil casing 52,
A magnetic loop is formed by the base 51, the bush 100, and the plunger portion 54, and the plunger portion 54 is slid to the right in FIG. 6 on the magnetic leakage portion 61 having a triangular cross section formed on the inner end surface of the attraction member 58. A suction force for moving is generated, and this suction force pushes the valve spool 4 back to the right in FIG.

That is, the pressing force of the pilot piston 65 generated by the brake operation, the pressure receiving reaction force of the reaction force piston 64 + the setting force of the return spring 4d + the suction force,
The valve spool 4 is arranged in a position where the two balance with each other, that is, the valve spool 4 is pushed back by the amount of the suction force in the right direction in FIG. 6, whereby the output hydraulic pressure (the hydraulic pressure supplied to the wheel cylinder 3) is reduced. However, since the braking force of the wheel is reduced, the slip amount of the wheel is reduced.

AB of the brake controller 13
In the S control unit, the detected slip amount and the preset proper slip amount (braking force) are constantly compared, and the current value applied to the ABS solenoid 5 is adjusted so that the detected slip amount becomes the proper slip amount. The increase / decrease change control is performed. That is, within the range of the ABS function shown in FIG. 8, the output hydraulic pressure (W / CYL) with respect to the master cylinder pressure (M / CYL pressure)
Pressure) characteristics can be changed.

As described above, in this embodiment, in addition to the effects of the first embodiment, the following effects can be obtained.

That is, since the hydraulic pressure booster mechanism for exerting a boosting function is compactly incorporated in the hydraulic pressure control valve 7, compared with the case where the hydraulic pressure booster mechanism is incorporated in the system as a separate member, the entire system is It can be made lighter and more compact, and can be installed more easily in vehicles.

(Third Embodiment) Next, the hydraulic control valve of the third embodiment of the present invention shown in FIG. 9 will be described. In this embodiment, the same components as those of the second embodiment are designated by the same reference numerals, and the description thereof will be omitted, and only different points will be described.

In this embodiment, contrary to the cases of the first and second embodiments, the hydraulic pressure supply port 11a and the drain port 11b are formed with a diameter larger than the diameter of the valve hole 11, and While the valve hole 11 is formed in a penetrating state in a direction orthogonal to the valve hole 11, the output port 11c is formed in an abutting state with a diameter smaller than that of the valve hole 11, and the valve spool at the opening position of the output port 11c. 4, an annular communication groove 4e for communicating the output port 11c with either the hydraulic pressure supply port 11a or the drain port 11b is formed on the outer periphery of the No.

In this embodiment, the annular communication groove 4e is formed.
And drain port 11b or hydraulic pressure supply port 11a
And the variable diaphragms s and t are formed between them.

That is, even in the case of the configuration of this embodiment, it is possible to prevent the lateral force from being exerted on the valve spool 4.

Although the embodiment of the present invention has been described in detail above with reference to the drawings, the specific structure is not limited to this embodiment, and the present invention can be applied even if there are design changes and the like within the scope not departing from the gist of the present invention. Included in the invention.

[0079]

As described above, in the hydraulic control valve of the present invention, as described above, the spool having the small diameter,
Since the structure has the plunger portion having a diameter larger than that of the spool, it is possible to simultaneously satisfy both the requirements of increasing the solenoid attraction force and reducing the leak amount around the spool.

Further, in the hydraulic pressure control valve according to the third aspect, the output hydraulic pressure can be increased by pressing the spool in the direction of increasing the output hydraulic pressure by receiving the hydraulic pressure on one end surface. By constructing a pilot piston that presses the spool in the direction of increasing pressure, and forming the pressure receiving area of the pilot piston larger than the pressure receiving area of the reaction force piston by a predetermined ratio, the output for the hydraulic pressure acting on the pilot piston It is possible to increase the hydraulic pressure by a ratio according to the pressure receiving area ratio of both pistons, which allows the hydraulic pressure control valve to exert a hydraulic booster function that boosts the supplied hydraulic pressure. Compared to the case where the booster mechanism is incorporated into the system as a separate member, the overall system can be made lighter and more compact, and the vehicle mountability will be improved. Cormorants effect can be obtained.

[Brief description of drawings]

FIG. 1 is an F of FIG. 2 showing a hydraulic control valve according to a first embodiment of the present invention.
It is a -F sectional view.

FIG. 2 is a view from the direction of arrow G in FIG. 1 showing the hydraulic pressure control valve of the first embodiment.

FIG. 3 is a system diagram of a brake fluid pressure control device showing an application example of the fluid pressure control valve of the first embodiment.

FIG. 4 is an output hydraulic pressure characteristic diagram of the hydraulic control valve of the first embodiment.

FIG. 5 is a cross-sectional view of essential parts showing a modified example of the hydraulic control valve of the first embodiment.

FIG. 6 is a sectional view showing a fluid pressure control valve according to a second embodiment of the present invention.

FIG. 7 is a system diagram of a brake fluid pressure control device showing an application example of a fluid pressure control valve according to a second embodiment.

FIG. 8 is a wheel cylinder hydraulic pressure characteristic diagram for the master cylinder pressure of the hydraulic pressure control valve of the second embodiment.

FIG. 9 is a sectional view showing a hydraulic control valve according to a third embodiment of the present invention.

[Explanation of symbols]

 2 master cylinder (hydraulic pressure supply source) 4 valve spool 4d return spring (pressing means) 5 solenoid for ABS 6 external hydraulic pressure supply source (hydraulic pressure supply source) 17a stopper part (stopper) 7 hydraulic pressure control valve 54 plunger part 64 Reaction force piston 65 Pilot piston

Claims (3)

[Claims] 1. A small-diameter spool for adjusting an output hydraulic pressure by sliding the hydraulic pressure from a hydraulic pressure supply source as a supply source, a pressing means for pressing the spool in a direction to increase the output hydraulic pressure, and a spool. The end face of the side end face is slidably mounted, the end face of the protruding side abuts the stopper, and the output liquid pressure is received on the other end face side, so that the output liquid pressure is reduced by the pressure receiving reaction force. A reaction force piston for pushing back the spool and a plunger portion having a diameter larger than that of the spool are provided in a state of at least abutting on the other end face side of the spool, and the solenoid for pushing back the spool in a direction to reduce the output hydraulic pressure by its suction force. And a hydraulic pressure control valve. 2. The hydraulic control valve according to claim 1, wherein the pressing means is a spring that constantly presses the spool in a direction to increase the output hydraulic pressure. 3. The pressing means is composed of a pilot piston that presses the spool in a direction in which the output hydraulic pressure is increased by receiving hydraulic pressure on one end surface, and the pressure receiving area of the pilot piston is the same as that of the reaction piston. The hydraulic control valve according to claim 1, wherein the hydraulic control valve is formed to be larger than the pressure receiving area at a predetermined magnification.