JPH1086813A - Fluid pressure control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To facilitate machining of respective ports so as to reduce a production cost in a fluid pressure control valve of a brake fluid pressure controller. SOLUTION: A stepped main sleeve 18 is inserted into a stepped valve hole 17 in a fluid pressure control valve main body 16, while an input port 39, an output path 41, and a discharge port 42 are connected to an input path 32, an output path 33, and the second drain path 31b, and they are connected to a fluid pressure supply source, a wheel cylinder and a reservoir. A spool 20 is fitted inside the main sleeve 18, while a proportional solenoid 21 is installed in the valve hole 17. A fluid pressure to the wheel cylinder is regulated by moving the spool 20, and a braking force is controlled. Fluid pressures of the input path 32 and the output path 33 work on a stepped part of the main sleeve 18, so that the main sleeve 18 is brought into contact with the proportional solenoid 21 so as to be positioned. As respective ports can be arranged while using one end part of the cylindrical main sleeve 18 as a reference, machining can be facilitated and required precision can be accomplished.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic pressure control valve used for a brake hydraulic pressure control device of a vehicle such as an automobile.

[0002]

2. Description of the Related Art In a hydraulic braking apparatus for a vehicle such as an automobile, the hydraulic pressure supplied to a wheel cylinder is electrically controlled based on the hydraulic pressure of a master cylinder generated by a driver's braking operation, thereby doubling the hydraulic pressure. There is a brake fluid pressure control device that enables force control, antilock control, traction control, and the like.

This type of brake fluid pressure control device supplies, for example, a master cylinder that generates a fluid pressure by a driver's brake operation, a wheel cylinder that activates a brake device of each wheel by the fluid pressure, and a wheel cylinder. A hydraulic pressure supply source including a hydraulic pressure pump and an accumulator for generating hydraulic pressure, a hydraulic pressure control valve for controlling supply and discharge of a brake fluid between the hydraulic pressure supply source and the reservoir and the wheel cylinder, and a hydraulic pressure control valve for the master cylinder. And an electronic control unit that controls the hydraulic control valve based on the pressure.

[0004] With this configuration, normally, the electronic control unit controls the hydraulic pressure control valve based on the hydraulic pressure of the master cylinder due to the brake operation of the driver, and provides a predetermined boosting ratio from the hydraulic pressure supply source. The hydraulic pressure is supplied to the wheel cylinder to generate a braking force. Also, anti-lock control and traction control are performed by judging the slip state of the wheel based on the rotational speed information of the wheel and controlling the hydraulic pressure control valve based on this to appropriately adjust the braking force on the wheel. be able to.

In general, a hydraulic pressure control valve used in this type of brake hydraulic pressure control device will be described with reference to FIG. As shown in FIG. 6, the hydraulic control valve 1 is a spool valve, and a spool 4 is slidably fitted in a guide hole 3 of a hydraulic control valve body 2. The hydraulic pressure control valve body 2 is provided with an input port 5, an output port 6, and a discharge port 7 that communicate with the guide hole 3, and these are connected to a hydraulic pressure supply source, a wheel cylinder, and a reservoir, respectively. . A variable throttle S is formed between the input port 5 and the output port 6 by the spool 4, and a variable throttle T is formed between the output port 6 and the discharge port 7. The variable aperture S is opened and the variable aperture T is closed when it is moved to. The variable aperture S is closed and the variable aperture T is opened when it is moved rightward in the figure.

At one end of the hydraulic pressure control valve body 2, a proportional solenoid 8 is mounted, and its operating rod 9 is attached to the spool 4
And presses the spool 4 to the left in the figure with a thrust proportional to the current supplied from the electronic control unit. At the other end of the hydraulic pressure control valve body 2,
A control port 10 is provided, and a control pin 11 is connected to the other end of the spool 4. The control pin 11 is slidably inserted into the guide member 12, and receives the hydraulic pressure of the control port 10 to press the spool 4 rightward in the figure. The spool 4 is urged rightward in the figure by a return spring 13. Control port 10 is connected to output port 6 by line 14.

Normally, due to the spring force of the return spring 13, the spool 4 is located on the right side in the figure, the variable throttle S is closed, and the variable throttle T is open, so that the hydraulic pressure acts on the output port 6. No, the wheel cylinder does not work. When the proportional solenoid 8 is energized by the electronic control unit, the operating rod 9 moves the spool 4 to the left in the figure according to the energized current, and the variable throttle S opens and the variable port T closes. Hydraulic pressure is supplied from the inlet port 5 to the output port 6 to operate the wheel cylinder to generate a braking force. At this time, the hydraulic pressure of the output port 6 is transmitted to the control port 10 via the pipe line 14, and the control pin 11 presses the spool 4 rightward in the drawing, so that the thrust of the proportional solenoid 8 and the control port 10 ( The hydraulic pressure at the output port 6 increases until the hydraulic pressure at the output port 6) and the spring force of the return spring 13 are balanced and the spool 4 stops at the position where the variable throttles S and T are closed. As a result, the hydraulic pressure at the output port 6 can be directly controlled according to the current supplied to the proportional solenoid 8, and the braking force can be controlled.

[0008]

When the hydraulic pressure control valve 1 shown in FIG. 6 is manufactured, the input ports 5 and the discharge ports 7 constituting the variable throttles S and T must be accurately arranged. In addition, high machining accuracy is required for the machining. However, the hydraulic pressure control valve body 2 has strength,
The input port 5 and the discharge port 7 are not necessarily formed in such a shape that the processing accuracy can be easily obtained because of the mounting space, formability and the like. Therefore, generally, the input port 5
It is often difficult to machine the discharge port 7 with a desired accuracy. Also, high machining accuracy is required for obtaining the coaxiality of the spool 4, the control pin 11, and the guide member 12. As described above, the difficulty of machining causes an increase in manufacturing cost.

The present invention has been made in view of the above points, and an object of the present invention is to provide a hydraulic control valve in which each port can be easily provided with a desired accuracy and the manufacturing cost can be reduced. Aim.

[0010]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the invention according to claim 1 is connected to an input passage connected to a hydraulic pressure supply source, an output passage connected to a wheel cylinder, and a reservoir. A spool is housed in a hydraulic pressure control valve body having a drain passage, and the spool is moved based on a hydraulic pressure generated by a master cylinder to flow between the input passage and the drain passage and the output passage. A hydraulic pressure control valve configured to control a hydraulic pressure supplied to the wheel cylinder by adjusting an area, wherein the hydraulic pressure control valve body communicates with the input passage, the output passage, and the drain passage, An inner peripheral portion is provided with a stepped valve hole having a larger diameter in order from the bottom side. In the valve hole, an outer peripheral portion has a larger diameter in order from one end side, and the side wall communicates with the input passage, the output passage and the drain passage respectively. Do A stepped cylindrical main sleeve having a force port, an output port, and a discharge port is slidably fitted therein, and the spool is slidably fitted in the main sleeve. The input passage, the output passage, and the drain passage are arranged so that the end surface of the main sleeve becomes a pressure receiving surface, and the main sleeve is pressed against one side of the hydraulic pressure control valve body by the hydraulic pressure of the passage so as to be positioned. It is characterized by having done.

With this configuration, the main sleeve is pressed against one side of the hydraulic pressure control valve main body to be positioned by receiving the hydraulic pressure in the input passage, the output passage, and the drain passage of the hydraulic pressure control valve main body. Therefore, the input port, the output port, and the discharge port can be arranged with reference to one end of the cylindrical main sleeve.

According to a second aspect of the present invention, in addition to the configuration of the first aspect, a sub-sleeve abutting on the main sleeve is slidably fitted in a valve hole of the hydraulic control valve body. A control chamber is formed at the bottom of the valve hole, one end of a control pin slidably inserted into the sub-sleeve is brought into contact with the spool, and further, the control chamber is communicated with an output passage, and The hydraulic pressure in the passage presses the control pin against the spool to control the movement of the spool, and the sub-sleeve presses the main sleeve toward one side of the control valve body. I do.

[0013] With this configuration, the control pin and the spool are separated from each other, so that coaxiality between the sub-sleeve, the control pin and the spool is not required.

According to a third aspect of the present invention, there is provided a hydraulic pressure control valve according to the first or second aspect, wherein an annular groove is provided in an outer peripheral portion of a land of the spool opposed to the input port, and the input port is provided in a main sleeve. And a balance port for constantly communicating with the annular groove.

With this configuration, the hydraulic pressure at the input port is constantly transmitted through the balance port into the annular groove, so that the hydraulic pressure always uniformly acts on the entire circumference of the spool, and the spool is moved to the main sleeve. Held in the center of

[0016]

Embodiments of the present invention will be described below in detail with reference to the drawings.

The hydraulic pressure control valve according to the first embodiment will be described with reference to FIGS. As shown in FIG. 1, a hydraulic pressure control valve 15 according to the first embodiment is a spool valve, and a cylindrical main sleeve 18 and a sub-hole are provided in a valve hole 17 provided in a hydraulic pressure control valve body 16. Sleeve 19 is inserted,
Further, a spool is provided in the guide hole 18a of the main sleeve 18.
20 is inserted, and a proportional solenoid 21 is attached to the opening of the valve hole 17.

In the valve hole 17 of the hydraulic pressure control valve body 16, in order from the bottom side, the smallest-diameter small-diameter fitting portion 22, the guide portion 23 having a slightly larger diameter than the small-diameter fitting portion 22, and slightly larger than the guide portion 23. Larger first inner diameter portion 24, second inner diameter portion 25 slightly larger than first inner diameter portion 24, third inner diameter portion 26 slightly larger than second inner diameter portion 25, and third inner diameter portion 26
A fourth inner diameter portion 27 having a slightly larger diameter, a seal portion 28 having a larger diameter than the fourth inner diameter portion 27, and a large-diameter fitting portion 29 having a larger diameter than the seal portion 28 are formed. In addition, the hydraulic pressure control valve body 16 includes:
The control passage 30, which communicates with the guide portion 23 of the valve hole 17, the first inner diameter portion 24
, An input passage 32 communicating with the second inner diameter portion 25, an output passage communicating with the third inner diameter portion 26, and a second drain passage 31b communicating with the fourth inner diameter portion 27. .

As shown in FIG. 2, on the outer peripheral portion of the main sleeve 18, the smallest diameter portion 33A having the smallest diameter and the first diameter portion 24 of the valve hole 17 having a slightly larger diameter than the small diameter portion 33A are arranged in order from one end side. A first outer diameter portion 34 movably fitted, a second outer diameter portion 35 slidably fitted to the second inner diameter portion 25, and a third outer diameter slidably fitted to the third inner diameter portion 26. A part 36 is formed. A first drain port 37 communicating with the guide hole 18a is provided on a side wall of the small diameter portion 33A.
However, the outer peripheral groove 38 and the outer peripheral groove
An input port 39 for communicating the guide hole 38 with the guide hole 18a is provided.
The third outer diameter portion 36 is provided with a discharge port 42 and a second drain port 43 which communicate with the guide hole 18a. The first drain port 37 and the second drain port 43 are each 180 ° along the circumferential direction.
Two ports are arranged at intervals, and the input port 39, the output port 41, and the discharge port 42 are respectively arranged along the circumferential direction.
Four are arranged at 90 ° intervals.

The outer peripheral portions of the first, second and third outer diameter portions 34, 35 and 36 are provided with annular seal grooves 44, 45 and 46, respectively. , Each O-ring 4
7, 48 and 49 are fitted. And the main sleeve 1
8 is inserted into the valve hole 17, the first, second, and third outer diameter portions 34, 35, 36 and the first, second,
Sealing between the third inner diameter portions 24, 25, 26, the first drain port 37 is in the first drain passage 31a, the input port 39 (outer peripheral groove 38) is in the input passage 32, and the output port 41 (outer peripheral groove). 40) is connected to the output passage 33, and the discharge port 42 and the second drain port are connected to the second drain passage 31b.

In the guide hole 18a of the main sleeve 18,
A spool 20 is slidably fitted. Spool 20
In the figure, an annular valve groove 50 is provided on the outer periphery of the central portion and always communicates with the output port 41, and lands 51 and 52 are formed on both sides thereof. The land 51 forms a variable throttle S between the input port 39 and the output port 41, and the land 52 forms a variable throttle T between the output port 41 and the discharge port 42. Moving to the middle left opens the variable aperture S and closes the variable aperture T, and moving to the right in the figure closes the variable aperture S and opens the variable aperture T.

A substantially cylindrical bottomed sub-sleeve 19 is slidably fitted in the guide portion 23 of the valve hole 17 such that the bottom side of the sub-sleeve 19 is in contact with one end of the main sleeve 18. .
An annular seal groove 53 is provided on the outer peripheral portion at the bottom of the sub-sleeve 19.
And an O-ring 54 is fitted in the seal groove 53. The O-ring 54 seals between the outer peripheral portion of the sub-sleeve 19 and the guide portion 23, and a control chamber 55 is defined at the bottom of the valve hole 17.

A guide bore 56 extends through the bottom of the sub-sleeve 19 along its axis. A control pin 57 is slidably and liquid-tightly inserted into the guide bore 56. One end of the control pin 57 is in contact with the end of the spool 20, and a spring receiver 58 is attached to the other end. The control pin 57 is pressed against the spool 20 by a compression spring 60 interposed between the spring receiving member 59 and the spring receiver 58 fitted in the small diameter fitting portion 22 of the valve hole 17. Sub sleeve
An outer peripheral groove 61 communicating with the control passage 30 of the hydraulic pressure control valve body 16 and a control port 62 for communicating the outer peripheral groove 61 with the control chamber 55 are provided on a side wall of the hydraulic pressure control valve body 16.

The proportional solenoid 21 has a cylindrical fitting portion 64 formed concentrically around an operating rod 63, an outer peripheral portion of which is fitted into the seal portion 28 of the valve hole 17, and a large-diameter flange portion. 65 is fitted to the large-diameter fitting portion 29, and the control valve main body 16
The retainer 66 is fixed to the end of the flange 65 by a connecting means such as a bolt (not shown). The space between the outer peripheral portion of the fitting portion 64 and the seal portion 28 is sealed by an O-ring 67. Also,
A third outer diameter portion of the main sleeve 18 is provided on an inner peripheral portion of the fitting portion 64.
The ends of 36 are loosely fitted. The main sleeve 18 performs axial positioning by bringing the end face 36a of the third outer diameter portion 36 into contact with the bottom portion 64a of the fitting portion 64 of the proportional solenoid 21 disposed at one end of the valve hole 17. And the first drain port 37 and the input port based on the end face 36a.
39, an output port 41, a discharge port 42 and a second drain port 43 are arranged.

The proportional solenoid 21 has an end portion of the operating rod 63 in contact with an end portion of the spool 20.
Irrespective of the displacement, the spool 20 is pressed to the left in the figure with a constant thrust proportional to the current supplied to the coil 68 (see FIG. 4).

Next, a brake fluid pressure control device provided with the fluid pressure control valve 15 will be described with reference to FIG.

As shown in FIG. 4, a brake fluid pressure control device
Reference numeral 69 denotes a hydraulic pressure supply source 71 connected to an input passage 32 of the hydraulic pressure control valve 15 via an electromagnetic on-off valve 70, and a hydraulic pressure amplification device 72 and a fail-safe valve 73 (pilot-type switching valve) to an output passage 33.
A wheel cylinder 74 is connected to the first and second drain passages 31a and 31b through the reservoir 75 of the hydraulic pressure supply source 71.
Are connected, and the output passage 33 and the control passage 30 are connected to each other by a conduit 76A. Wheel cylinder 74
Is connected to a master cylinder 76 via a fail-safe valve 73, and the master cylinder 76 is connected to an accumulator 78 via a pilot-type on-off valve 77.

The brake fluid pressure control device 69 includes a fluid pressure sensor 80 for detecting the fluid pressure of the wheel cylinder 74, the master cylinder 76, and the fluid pressure of the accumulator 79 of the fluid pressure supply source 71, respectively.
81 and 82, and a speed sensor 83 for detecting the rotation speed of the wheels are provided. Based on these output signals, the electromagnetic on-off valve 70, the motor 84 of the hydraulic pressure supply source 71 and the hydraulic pressure control valve 15 are provided.
An electronic control unit 85 for controlling the proportional solenoid 21 is provided.

The hydraulic pressure supply source 71 accumulates the hydraulic pressure generated by driving the hydraulic pump 86 by the motor 84 in the accumulator 79 and supplies a predetermined hydraulic pressure to the hydraulic pressure control valve 15. ing. Hydraulic pressure sensor by electronic control unit 85
By controlling the motor 84 based on the output signal of the motor 82, the hydraulic pressure of the accumulator 79 is adjusted. Reference numeral 87 in the figure denotes a pressure regulating valve that releases a predetermined or more hydraulic pressure of the accumulator 79 to the reservoir 75.

The hydraulic pressure amplifying device 72 amplifies the hydraulic pressure from the output passage 33 of the hydraulic pressure control valve 15 at a predetermined ratio and transmits the amplified hydraulic pressure to the wheel cylinder 74 due to the pressure receiving area difference of the stepped piston 88. I have.

The operation of the brake fluid pressure control device 69 equipped with the fluid pressure control valve 15 configured as described above will now be described.

When the hydraulic pressure is generated from the master cylinder 76 by operating the brake pedal 89, the hydraulic pressure is applied to the hydraulic pressure sensor 81.
Detects and outputs a hydraulic pressure signal. Electronic control unit 85
Receives the hydraulic pressure signal from the hydraulic pressure sensor 81 and receives the electromagnetic switching valve
Open 70, and from the hydraulic pressure supply source 71 to the inlet passage of the hydraulic pressure control valve 15
Connect the flow path to 32. The electronic control unit 85
The master cylinder 76 is connected to the coil 68 of the proportional solenoid 21 of the hydraulic pressure control valve 15 based on the hydraulic pressure signal from the hydraulic pressure sensor 81.
A current corresponding to the fluid pressure is supplied.

In the hydraulic pressure control valve 15, the operating rod 63 moves the spool 20 to the left in the drawing against the elastic force of the return spring 60 by the current flowing through the coil 68. By this movement, the variable throttle T is closed, the communication between the output port 41 and the discharge port 45 is interrupted, and when the spool 50 moves to the left, the variable throttle S is opened, and the input port is set in accordance with the opening.
32 and the output port 41 are communicated. Thus, the hydraulic pressure supply source 71 connected to the inlet passage 32 and the wheel cylinder 74 connected to the outlet passage 33 communicate with each other via the variable throttle S, and the hydraulic pressure from the hydraulic pressure supply source 71 is amplified by the hydraulic pressure. The signal is amplified at a predetermined ratio by the device 72 and supplied to the wheel cylinder 74 to generate a braking force.

At this time, the hydraulic pressure in the output passage 33 is increased by the line 76A,
The control signal is transmitted to the control chamber 55 via the control passage 30 and the control port 62, and the control pin 57 presses the spool 20 rightward in the drawing, so that the thrust of the proportional solenoid 21 and the control chamber 55 (that is, the output port 41) The hydraulic pressure at the output port 41 increases until the hydraulic pressure and the spring force of the return spring 60 balance and the spool 20 stops at the position where the variable throttles S and T are closed. Accordingly, the hydraulic pressure of the output port 41, that is, the output passage 33 can be controlled in accordance with the current supplied to the coil 68 of the proportional solenoid 21, and the hydraulic pressure supplied to the wheel cylinder 74 can be controlled. The braking force can be controlled according to the operation force of the brake pedal 89.

The output port 41 (output passage 33) of the hydraulic pressure control valve 15 is connected to a wheel cylinder via a hydraulic pressure amplifying device 72.
In the state where the hydraulic pressure is normally supplied to the 74, the fail-safe valve 73 and the pilot-type on-off valve 77 are switched to positions different from the positions shown in the drawing, using the hydraulic pressure as the pilot pressure. Is connected to the wheel cylinder 74, while the master cylinder 76 is disconnected from the wheel cylinder 74 and connected to the accumulator 78. Thus, the hydraulic pressure generated by the master cylinder 76 is accumulated in the accumulator 78, so that the stroke of the brake pedal 89 can be secured and an appropriate operation feeling can be obtained.

Then, from the braking state, the brake pedal
When the operation of 89 is released and the hydraulic pressure of the master cylinder 76 is reduced, the hydraulic pressure sensor 81 outputs a hydraulic pressure signal in accordance with the reduction of the hydraulic pressure. The electronic control unit 85 reduces the current supplied to the coil 68 of the proportional solenoid 21 based on the hydraulic pressure signal from the hydraulic pressure sensor 81.

In the hydraulic pressure control valve 15, the spool 20 moves rightward in the drawing due to a decrease in the current supplied to the coil 68, the variable throttle S closes, and the communication between the input port 32 and the output port 41 is cut off. . Further, when the spool 20 is moved rightward in the drawing, the variable throttle T is opened, and the output port 41 and the discharge port 42 are communicated with each other.
The brake fluid is returned to the reservoir 75 via b, and the braking is released. When the release of the hydraulic pressure of the master cylinder 74 is detected by the hydraulic pressure sensor 81, the electronic control unit 85 closes the electromagnetic on-off valve 70, and the hydraulic pressure supply valve 71
The flow path to the 15 inlet passages 32 is shut off.

The electronic control unit 85 determines the slip state of the wheel based on the output signal of the speed sensor 83, and controls the current supplied to the coil 68 of the hydraulic pressure control valve 15 based on the slip state based on the slip state. The antilock control and the traction control can be performed by increasing or decreasing the braking force.

According to the brake fluid pressure control device 69, when the fluid pressure from the output passage 33 of the fluid pressure control valve 15 to the wheel cylinder 74 does not increase during the braking operation, the fail-safe valve 73 and the pilot-type on-off valve 77 returns to the position shown in the figure to enter the fail-safe operation state. In this state, while the wheel cylinder 74 is cut off from the hydraulic pressure amplifying device 72 and is directly connected to the master cylinder 76, the master cylinder 76 is cut off from the accumulator 78, so that the hydraulic pressure generated by the master cylinder 76 is directly reduced. Wheel cylinder 74
And the braking force can be secured.

The hydraulic control valve 15 is slidably fitted with a stepped main sleeve 18 having a larger diameter from one end side into a stepped valve hole 17 having a larger diameter from the bottom side. The input passage 32, the output passage 33, and the first drain passage 31a are arranged so that the end surface of the step portion of the main sleeve 18 becomes a pressure receiving surface. The hydraulic pressure in the 1 drain passage 31a causes the main sleeve 18
Is pressed to the right in the figure, and its end surface 36a is proportional solenoid.
It is pressed against the bottom part 64a of the fitting part 64 of FIG. Further, the sub-sleeve 19 is urged rightward in the figure by the hydraulic pressure introduced into the control chamber 55 from the control passage 30 and the control port 62, and presses the main sleeve 18 against the proportional solenoid 21. Here, since the first drain port 37, the input port 39, the output port 41, the discharge port 42, and the second drain port 43 are arranged on the main sleeve 18 with reference to the end face 36a, each port is accurately positioned. You.

When the brake is released, the pressure in the input passage 32, the output passage 33, and the first drain passage 31a is reduced, but the friction between the O-rings 47, 48, 49, 54 and the inner peripheral surface of the valve hole 17 causes the pressure to be reduced. Since the main sleeve 18 and the sub sleeve 19 do not move, the main sleeve 18 and the sub sleeve 19
Does not move to cause a response delay.

Then, the first drain port 37, the input port
39, output port 41, discharge port 42, second drain port 43
Is positioned on the side wall of the cylindrical main sleeve 18 with reference to the one end surface 36a thereof, so that it can be easily positioned, and can be easily provided with desired accuracy by machining or the like. Since the step portion of the main sleeve 18, that is, the small-diameter portion 33A, the first outer-diameter portion 34, the second outer-diameter portion 35, and the third outer-diameter portion 36 are coaxially arranged, they are fixed to a certain machining axis. It can be easily formed by machining or the like. Similarly, the stepped valve hole 17 can be easily formed by machining or the like along a certain processing axis.

The control passage 30, the first drain passage 31a, the input passage 32, and the output passage second drain passage 31b of the hydraulic pressure control valve body 16 only communicate with the ports of the main sleeve 18 and the sub-sleeve 19. Since the arrangement does not require high precision, it can be easily provided by machining or the like. .

Further, since the control pin 57 is provided separately from the spool 20, a guide bore 56 for the spool 20 and the sub sleeve is provided.
Since the coaxiality between the control pin and the control pin 57 is not required, these can be easily manufactured.

Further, since the main sleeve 18 and the sub-sleeve 19 are not provided integrally with the threaded portion, they do not need to be rotated along the threaded portion when assembling, so that the O-ring 47, 48, 49, 54 can be prevented from being damaged.

Next, a hydraulic control valve according to a second embodiment of the present invention will be described with reference to FIG. The hydraulic pressure control valve according to the second embodiment has substantially the same structure as that of the first embodiment except that a part of the spool and a part of the main sleeve are different. The same parts as in the embodiment are denoted by the same reference numerals, and only different parts will be described in detail.

As shown in FIG. 5, in the hydraulic pressure control valve 90 according to the second embodiment, an annular groove 91 is formed on the outer periphery of the central portion of one land 51 of the spool 20 facing the input port 39 of the main sleeve 18. Have been. Also, the first of the main sleeve 18
A balance port 92 is provided on the side wall of the outer diameter portion 34 so as to face the annular groove 91. Four balance ports 92 are provided at 90 ° intervals or two at 180 ° intervals along the circumferential direction. The input ports 32 (input ports 39) are provided through the first inner diameter portion 24 of the valve hole 17. Is communicated to. Further, the balance port 92 is arranged at a position that always communicates with the annular groove 91 regardless of the axial position of the spool 20.

With this configuration, the hydraulic pressure at the input port 39 is constantly transmitted into the annular groove 91 via the balance port 92, so that the hydraulic pressure constantly and uniformly acts on the entire circumference of the spool 20. By this hydraulic pressure, the spool 20 is held at the center in the guide hole 18a of the main sleeve 18, so that the sliding resistance due to the bias of the spool 20 can be reduced,
The movement of the spool 20 can be smoothly performed, and stable hydraulic pressure control can be performed. Since the annular groove 91 is disposed in the center of the land 51, the first drain port 37
Also, the leakage of the liquid into the valve groove 50 of the spool 20 is very small and does not affect the hydraulic control.

[0049]

As described above in detail, according to the hydraulic control valve of the first aspect, the main sleeve receives the hydraulic pressure of the input passage, the output passage and the drain passage of the hydraulic control valve body, and the hydraulic pressure of the main sleeve increases. Since it is positioned by being pressed against one side of the control valve body, the input port, the output port and the discharge port can be arranged with reference to one end of the cylindrical main sleeve. As a result, each port can be easily provided with desired accuracy by machining or the like, and the manufacturing cost can be reduced.

According to the second aspect of the present invention, since the control pin and the spool are provided separately, the sub-sleeve, the control pin and the spool do not need to be coaxial, and can be easily manufactured. be able to.

According to the third aspect of the present invention, since the hydraulic pressure at the input port is constantly transmitted through the balance port into the annular groove, the hydraulic pressure constantly acts on the entire circumference of the spool. As a result, the spool is held at the center in the main sleeve, the sliding resistance due to the bias of the spool can be reduced, and the movement of the spool can be made smooth and stable hydraulic pressure control can be performed.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a main part of a hydraulic pressure control valve according to a first embodiment of the present invention.

FIG. 2 is a longitudinal sectional view of a main sleeve of the hydraulic control valve of FIG.

FIG. 3 is a longitudinal sectional view of a sub-sleeve of the hydraulic control valve of FIG.

FIG. 4 is a circuit diagram of a brake fluid pressure control device equipped with the fluid pressure control valve of FIG. 1;

FIG. 5 is a longitudinal sectional view of a main part of a hydraulic pressure control valve according to a second embodiment of the present invention.

FIG. 6 is a schematic view of a conventional hydraulic pressure control valve.

[Explanation of symbols]

 15 Hydraulic control valve 16 Hydraulic control valve body 17 Valve hole 18 Main sleeve 19 Sub-sleeve 20 Spool 31a First drain passage 31b Second drain passage 32 Input passage 33 Output passage 39 Input port 41 Output port 42 Drain port 51 Land 55 Control room 57 Control pin 71 Hydraulic pressure supply source 74 Wheel cylinder 75 Reservoir 76 Master cylinder 90 Hydraulic pressure control valve 91 Annular groove 92 Balance port

Claims (3)

[Claims] A spool is housed in a hydraulic control valve body having an input passage connected to a hydraulic pressure supply source, an output passage connected to a wheel cylinder, and a drain passage connected to a reservoir, and a master cylinder is provided. Based on the generated hydraulic pressure,
A hydraulic pressure control valve configured to control a hydraulic pressure supplied to the wheel cylinder by adjusting a flow passage area between the input passage and the drain passage and the output passage by moving the spool. The hydraulic control valve body,
The input passage, the output passage and the drain passage, provided with a stepped valve hole in which the inner peripheral portion has a larger diameter in order from the bottom side, in the valve hole, the outer peripheral portion has a larger diameter in order from one end side, the side wall A stepped cylindrical main sleeve having an input port, an output port, and a discharge port communicating with the input passage, the output passage, and the drain passage, respectively, is slidably fitted, and further, the spool is inserted into the main sleeve. The input passage, the output passage, and the drain passage are arranged so that the end surface of the step portion of the main sleeve becomes a pressure receiving surface, and the main sleeve is hydraulically moved by the hydraulic pressure of the passage. A hydraulic pressure control valve characterized in that it is positioned by pressing against one side of a control valve body. 2. A control sleeve is formed at the bottom of the valve hole by slidably fitting a sub-sleeve in contact with the main sleeve in a valve hole of the hydraulic pressure control valve body, and slides on the sub-sleeve. One end of the control pin, which is inserted as possible, is brought into contact with the spool, and further, the control chamber is communicated with an output passage, and the control pin is pressed against the spool by the hydraulic pressure of the output passage so that the spool is pressed. 2. The hydraulic pressure control valve according to claim 1, wherein the sub-sleeve presses the main sleeve toward one side of the control valve body while controlling the movement of the hydraulic pressure control valve. 3. An annular groove is provided on an outer peripheral portion of a land of a spool facing an input port, and a balance port is provided on a main sleeve for constantly communicating the input port with the annular groove. Or the hydraulic pressure control valve according to 2.