JPH11173451A - Solenoid valve device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To avoid an increase in size of a solenoid valve device and reduce flow resistance of a working fluid greatly so as to improve the control property by providing a passage communicating a valve hole with a control pressure space in a valve shaft and setting a pressure receive area facing a valve hole side of a valve element to be equal to a pressure receive are facing a control pressure chamber of the valve shaft. SOLUTION: A normally open solenoid valve 4 of a brake device for vehicle has a valve seat member 49 fixed in a valve housing 14 and a valve element 55 provided at one end of a valve shaft 54 supported on the valve housing 14 so as to slide freely in the axial direction. A movable core 39 to which the other end of the valve shaft 54 is fixed is stored in a control pressure chamber 38 that the other end of the valve shaft 54 faces, and it is driven by conducting electricity to a coil assembly body 43. In this case, the valve element 55 is formed integrally with the valve shaft 54, and a passage 57 communicating a valve hole 52 with the control pressure chamber 38 at all times is formed in the valve shaft 54. A pressure receive area facing the valve hole 52 of the valve element 55 is set to be equal to a pressure receive area facing the control pressure chamber 38 of the valve shaft 54 so as to increase the responsiveness at the time of valve opening and closing.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a solenoid valve device, and more particularly to a valve housing having an input port communicating with a fluid pressure generating source and an output port communicating with a fluid pressure actuator, and a valve hole communicating with the input port at a central portion. A valve seat member having a valve seat facing the inside and fixed to the valve housing, and formed in a cylindrical shape coaxial with the valve hole and supported by the valve housing so as to be capable of sliding in the axial direction. A valve shaft, a valve body provided at one end of the valve shaft so as to be able to be seated on the valve seat and shut off between the valve hole and the output port, and a control pressure chamber facing the other end of the valve shaft. A movable core connected to the other end of the valve shaft and accommodated so that the fluid pressure of the control pressure chamber acts on both ends in the axial direction, and preferably used for an antilock brake control device for a vehicle. Is It relates to an electromagnetic valve device.

[0002]

2. Description of the Related Art Conventionally, such an electromagnetic valve device is already well known, for example, from Japanese Patent Application Laid-Open No. Hei 9-118220.

[0003]

Problems to be Solved by the Invention
In the solenoid valve device disclosed in Japanese Patent Publication No. 220, the control pressure chamber is always communicated with the output port, and the hydraulic pressure from the input port is applied to one end to enable relative movement in the axial direction. The other end of the pin that fits tightly is
The pin is supported by an end of a guide cylinder that guides the movable core, and a cross-sectional area of the pin is set to be substantially the same as a seating seal area of a valve body provided at one end of a valve shaft to a valve seat.

According to the electromagnetic valve device having such a configuration, when the operation of the valve shaft and the valve element is started from the open state to the closed state, the same fluid pressure acts on both ends of the valve shaft. No large driving force is required to operate the valve shaft and the valve body in the valve closing direction, and the force for maintaining the valve closed state depends on the cross-sectional area of the pin and the seating seal area of the valve body on the valve seat. By being substantially the same, it can be small.
However, in order to reduce the flow resistance of the working fluid in the valve-open state, it is necessary to increase the flow area of the valve hole, that is, the sealing area of the valve body seated on the valve seat. When the sealing area is increased, the cross-sectional area of the pin must be increased, and the diameter of the valve shaft also increases. Therefore, it is difficult to significantly reduce the flow resistance while avoiding an increase in the size of the solenoid valve device. In addition, since the pin and the valve body are composed of separate parts, high machining accuracy is required to make the cross-sectional area of the pin equal to the sealing area of the valve body seated on the valve seat. It is penetrated by the core and is supported by the guide cylinder, and its configuration is hardly simple.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has a simple structure to relatively reduce the force required to operate from an open state to a closed state and maintain the closed state. It is a first object of the present invention to provide an electromagnetic valve device which enables a large reduction in flow resistance of a working fluid while avoiding an increase in size.

When such an electromagnetic valve device is provided between a wheel brake and a brake pressure generating source so as to enable anti-lock brake control of a wheel brake, the anti-lock brake control is performed during the anti-lock brake control. When the brake fluid pressure of the wheel brake is increased, the solenoid valve device is opened. When the high hydraulic pressure from the brake pressure source suddenly acts on the wheel brake due to the valve opening operation, the brake pressure is reduced. Pulsation may occur, which may cause discomfort to the vehicle driver. For this reason, it is desirable to gradually increase the output hydraulic pressure of the output port in the early stage of opening of the solenoid valve device. However, in the above-described conventional solenoid valve device, in order to perform the slow pressure increase, electrical chopping control is performed. It is necessary to perform

The present invention has been made in view of the above circumstances, and a second object of the present invention is to provide an electromagnetic valve device which does not require electrical control and enables a gradual increase in pressure at the beginning of valve opening. .

[0008]

SUMMARY OF THE INVENTION To achieve the first object, the invention as defined in claim 1 comprises a valve housing having an input port leading to a fluid pressure source and an output port leading to a fluid pressure actuator; A valve seat member having a valve seat with a valve hole facing the center facing the input port and fixed in the valve housing; and a cylindrical member coaxial with the valve hole and having an axial sliding operation. A valve shaft provided at one end of the valve shaft for allowing movement and supported on a valve housing, seating on the valve seat to shut off between the valve hole and the output port, and the valve; A solenoid valve device comprising: a movable core connected to the other end of the valve shaft and housed in a control pressure chamber facing the other end of the shaft so that the fluid pressure of the control pressure chamber acts on both ends in the axial direction. In the above valve Is formed in a ring shape and is formed coaxially and integrally with one end of the valve shaft, and the valve shaft is provided with a passage for constantly communicating between the valve hole and the control pressure chamber, and is seated on the valve seat. The pressure receiving area facing the valve hole side of the valve body is set to be equal to the pressure receiving area facing the control pressure chamber of the valve shaft.

According to the first aspect of the present invention, when the valve body is in the open state in which the valve body is separated from the valve seat, the same fluid pressure acts on both ends of the valve shaft, and the valve is closed. No large driving force is required to operate the valve stem and the valve body in the valve closing direction to seat the body on the valve seat, and the force for maintaining the valve closed state in which the valve body is seated on the valve seat is: Since the pressure receiving area facing the valve hole side of the valve element seated on the valve seat is equal to the pressure receiving area facing the control pressure chamber of the valve shaft, it is possible to reduce the pressure receiving area. Therefore, it is possible to reduce the flow resistance of the working fluid by setting the diameter of the valve hole relatively large, while avoiding an increase in the diameter of the valve shaft, that is, an increase in the size of the solenoid valve device. In addition, the valve element is formed simply and coaxially at one end of the cylindrical valve axis, so that the valve axis and the valve element can be easily processed without requiring strict processing accuracy. Can be.

According to another aspect of the present invention, there is provided a valve housing having an input port leading to a fluid pressure generating source and an output port leading to a fluid pressure actuator, and communicating with the input port. A valve seat member having a valve seat with a valve hole facing the center and fixed in the valve housing; and a valve formed in a cylindrical shape coaxial with the valve hole and capable of sliding in the axial direction. A valve shaft supported by a housing, a valve body provided at one end of the valve shaft to be able to be seated on the valve seat and shut off the valve hole and the output port, and the other end of the valve shaft. A movable core connected to the other end of the valve shaft and accommodated in the control pressure chamber to be exposed so that the fluid pressure of the control pressure chamber acts on both ends in the axial direction. And control pressure A passage for constantly communicating between the chambers is provided in the valve shaft, receives fluid pressures of the output chamber and the control pressure chamber communicating with the output port at both ends, and is urged by the spring toward the control pressure chamber to slide on the valve housing. The valve shaft is coaxially fitted to the movably fitted cylindrical body so as to allow relative sliding in the axial direction, and between the control pressure chamber and the output chamber, between the valve shaft and the cylindrical body. Seal means for preventing the flow of working fluid between the valve housing and the cylindrical body is provided, and an annular path communicating with a valve hole when the valve body is separated from the valve seat is provided between the valve body and the valve body. And an orifice valve seat member fixed to the valve housing and fixed to the valve housing, and an orifice valve body provided at an end of the cylindrical body on the output chamber side to enable seating on the orifice valve seat member. To control pressure chamber The annular passage communicates with the output chamber when moving, but when the orifice valve body is seated on the orifice valve seat member accompanying the movement of the cylindrical body toward the output chamber, the flow of fluid between the annular passage and the output chamber is controlled. A throttle orifice valve is configured.

According to the configuration of the second aspect of the present invention, when the valve body is in a closed state in which the valve body is seated on the valve seat, the valve hole communicating with the input port is controlled by the control pressure through the passage of the valve shaft. Since the working fluid is communicated with the chamber and the working fluid is prevented from flowing from the control pressure chamber to the output chamber side through the valve shaft and the cylindrical body and between the valve housing and the cylindrical body by the sealing means, When the fluid pressure at the input port is greater than the fluid pressure at the output port, the pressure difference between the control pressure chamber and the output chamber causes the cylinder to move to a position where the orifice valve at one end is seated on the orifice valve seat member. Will be. For this reason, in the initial stage when the valve shaft at the valve closing position is operated in the valve opening direction, the flow of the working fluid from the annular passage leading to the valve hole to the output chamber, that is, the output port, is restricted by the orifice valve. The output fluid pressure of the port will gradually increase. Moreover, since the cylinder is spring-biased toward the control pressure chamber, when the fluid pressure in the output chamber is gradually increased to a certain value, the cylinder moves the orifice valve body away from the orifice valve seat member. The fluid moves to the control pressure chamber side, and the working fluid in the annular passage communicating with the input port via the valve hole flows to the output chamber, that is, the output port side without restricting the circulation.
Therefore, it is possible to gradually increase the pressure in the early stage of valve opening, and to increase the brake pressure when increasing the brake fluid pressure of the wheel brake during anti-lock brake control when an electromagnetic valve device is provided between the wheel brake and the brake pressure generation source. Since it is possible to prevent the occurrence of operating noise by preventing the pulsation of the pressure, it is possible to improve the riding feeling, and it is possible to gradually increase the pressure without the need for electrical control. , Excellent reliability can be obtained.

According to a third aspect of the present invention, in addition to the configuration of the second aspect of the present invention, the valve shaft is provided with an orifice interposed in the middle of the passage. According to this configuration, when the valve is opened in a state where there is no fluid pressure difference between the input port and the output port, it is necessary to rapidly increase the fluid pressure of the fluid pressure actuator. When a high-pressure fluid pressure acts suddenly, it is possible to prevent a relatively high fluid pressure from directly acting on the control pressure chamber by restricting the orifice. Therefore, even if the pressure difference between the input port and the output chamber temporarily increases due to the sudden action of the fluid pressure on the input port, the cylinder is pushed toward the output chamber by the fluid pressure in the control pressure chamber. Thus, a relatively high fluid pressure can be quickly applied to the fluid pressure actuator from the output port.

According to a fourth aspect of the present invention, in addition to the configuration of the second or third aspect, the sealing means faces the end face of the cylindrical body on the side opposite to the orifice valve and controls the control pressure. An annular seal member is provided between the valve housing and the valve shaft so as to be able to slide in the direction of pushing the cylindrical body under the pressure of the chamber.

According to the configuration of the invention described in claim 4, the sealing member interposed only between the valve housing and the valve shaft allows the valve body to be positioned between the valve shaft and the cylindrical body when the valve body is seated on the valve seat. It is possible to prevent the flow of the working fluid from the control pressure chamber to the output chamber through the space between the valve housing and the cylindrical body, and the seal member functions as a piston for pushing the cylindrical body. A single component can perform multiple functions.

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiments of the present invention will be described below based on one embodiment of the present invention shown in the accompanying drawings.

FIGS. 1 to 5 show an embodiment in which the present invention is applied to a normally-open solenoid valve of a vehicle brake device. FIG. 1 is a system diagram of a vehicle brake device, and FIG. FIG. 3 is a longitudinal sectional view of a normally-open solenoid valve in an open state, FIG. 3 is an enlarged view of a main part of FIG. 2, FIG. 4 is a longitudinal sectional view of a normally-open solenoid valve in a closed state, and FIG. FIG. 3 is a longitudinal sectional view of the normally-open solenoid valve of FIG.

First, in FIG. 1, a master cylinder M as a fluid pressure generating source is provided with an output port 2 for outputting a brake fluid pressure according to a depression operation of a brake pedal 1,
An antilock brake control device 3 is provided between the output port 2 and a wheel brake B as a fluid pressure actuator.

This anti-lock brake control device 3
Output port 2 of master cylinder M and wheel brake B
A normally-open electromagnetic valve 4 as an electromagnetic valve device provided therebetween,
A one-way valve 5 connected in parallel to a normally-open solenoid valve 4 by allowing the brake fluid to flow from the wheel brake B to the output port 2 side, a reservoir 6, and between the reservoir 6 and the wheel brake B A return pump 10 having a suction port connected to the reservoir 6 via a suction valve 8 and a discharge port connected to the output port 2 via a discharge valve 9; A damper 11 is connected between the output port 2 and the discharge valve 9, and a throttle 12 is provided between the damper 11 and the output port 2.

In such an anti-lock brake control device 3, during normal braking, the normally-open solenoid valve 4 and the normally-closed solenoid valve 7 are in a demagnetized state, and the output hydraulic pressure of the master cylinder M is reduced. Wheel brake B via valve 4
Act on. When the wheel provided with the wheel brake B is about to fall into a locked state, the demagnetization / excitation of the normally-open solenoid valve 4 and the normally-closed solenoid valve 7 is switched and the return pump 10 is operated. When the brake fluid pressure of the wheel brake B is reduced, the normally open solenoid valve 4 is closed and the normally closed solenoid valve 7 is opened. When the brake fluid pressure of the wheel brake B is maintained, the normally open solenoid valve 4 is opened. And the normally closed solenoid valve 7 are both closed, and the wheel brake B
When the brake fluid pressure is increased, the normally open solenoid valve 4 is opened and the normally closed solenoid valve 7 is closed.

The normally-open solenoid valve 4 is configured as the solenoid valve device of the present invention. Hereinafter, the structure of the normally-open solenoid valve 4 will be described in detail.

In FIG. 2, a valve housing 14 of the normally open solenoid valve 4 includes a housing main body 15 made of a magnetic metal,
A ring-shaped lid member 16 constituting a part of a filter 50 for filtering the brake fluid flowing into the normally-open solenoid valve 4. The valve housing 14 is fitted and fixed to a base 17. . That is, the base 17 has its one surface 17
a, a bottomed fitting recess 18 having one end opening is formed with a step, and the opening end of the fitting recess 18 is formed on the outer periphery of the other end of the valve housing 14 fitted into the fitting recess 18. The retaining ring 20 attached to the inner surface is engaged.

The housing main body 15 has a tapered first mounting hole 21 having a smaller diameter toward one end in the axial direction in order from one end in the axial direction (lower end in FIG. 2).
A second mounting hole 22 having a smaller diameter than the large-diameter end of the mounting hole 21;
A first sliding hole 23 smaller in diameter than the second mounting hole 22 and a second sliding hole 24 smaller in diameter than the first sliding hole 23 are coaxially provided, and the outer periphery is formed in a tapered shape. The lid member 16 is joined to the housing main body 15 by being pressed into the first mounting hole 21.

At the other end of the housing body 15, a cylindrical fixed core 26 extending in a direction protruding from one surface 17a of the base 17 is integrally provided.
The second sliding hole 24 is formed so as to extend into the fixed core 26.
The third sliding hole 25 having a smaller diameter than the second sliding hole 24
It is provided so as to be coaxial with the sliding hole 24.

An input port 27 is provided at the center of the lid member 16 in the valve housing 14, and a base 17 is provided.
Is provided with an input hydraulic pressure passage 28 communicating with the master cylinder M. The input hydraulic pressure passage 28 is coaxially opened to the input port 27 at the inner end of the fitting recess 18.

A lip seal 30 and an O-ring 31 that resiliently come into contact with the inner surface of the fitting concave portion 18 are mounted on the outer surface of the housing main body 15 at positions spaced apart in the axial direction. An annular chamber 32 is formed between the outer surface and the inner surface of the fitting recess 18. Both ends in the axial direction are sealed by a lip seal 30 and an O-ring 31.
7 is provided with an output hydraulic pressure passage 33 that connects the annular chamber 32 to the wheel brake B.

The lip seal 30 and the O-ring 31
An annular groove 34 is provided on the outer surface of the housing main body 15 therebetween, and a filter 35 housed in the annular chamber 32 is mounted on the housing main body 15 so as to cover the annular groove 34. In addition, the housing main body 15 is provided with an output port 36 having an inner end opened in the first sliding hole 23 and an outer end opened in the annular groove 34 so as to extend along one radial direction of the housing main body 15.

An open end of a guide cylinder 37 that is formed in a thin cylindrical shape with a nonmagnetic material and that extends coaxially with the valve housing 14 is fitted into and fixed to the fixed core 26. The guide cylinder 37 and the fixed core 2
A control pressure chamber 38 is formed between the six pressure chambers. This guide tube 3
7 guides the axial movement of the movable core 39 which can be moved toward and away from the fixed core 26.
9 is provided on the outer surface of the movable core 39 between both ends in the axial direction of the movable core 39. That is, the movable core 39 is housed in the control pressure chamber 38 so that the hydraulic pressure of the control pressure chamber 38 acts on both ends in the axial direction.

The guide cylinder 37 has a coil 42
Are wound coaxially by a coil assembly 43 in which a guide cylinder 37 is inserted through a center hole 44 provided in the bobbin 41.

One end of the coil assembly 43 is fixed core 26.
A magnetic path forming frame 45 made of magnetic metal is magnetically coupled to the movable core 39 via the guide cylinder 37 whose other end is thin and along the axial direction of the guide cylinder 37. It is held so that it can move freely.

The magnetic path forming frame 45 includes a cylindrical portion 45a coaxially surrounding the coil assembly 43, a first flat plate portion 45b extending radially inward from one end of the cylindrical portion 45a, and a first flat plate portion 45b. A first fitting cylinder portion 45c extending from the inner periphery to one end in the axial direction, a second flat plate portion 45d extending radially inward from the other end of the cylindrical portion 45a, and a shaft extending from the inner periphery of the second flat plate portion 45d. And a second fitting cylinder portion 45e extending toward one end in the direction. Thus, the cylindrical portion 45a, the first flat plate portion 45b, and the first fitting cylindrical portion 45c are formed integrally by press-forming a magnetic metal plate, and the second flat plate portion 45d and the second fitting cylindrical portion 45e are also magnetic. The second flat plate portion 45d is integrally formed by press molding of a metal plate, and is connected to the other end of the cylindrical portion 45a by press-fitting or caulking.

The first fitting cylindrical portion 45c of the magnetic path forming frame 45 is fitted and fixed to the fixed core 26. Also the second
The fitting cylinder portion 45e is connected to the bobbin 4 in the coil assembly 43.
1 and the guide cylinder 37 are fitted. Moreover, a spring 46 is provided between the first flat plate portion 45b and the coil assembly 43, and the coil assembly 43 is movable in the axial direction of the guide cylinder 37 so as to expand and contract the spring 46.

Referring also to FIG. 3, the valve housing 14
In the second mounting hole 22 of the housing main body 15 at
A spacer 48 formed in a cylindrical shape having a flange portion 48a projecting inward in the radial direction at one end so that the other end abuts on a step between the second mounting hole 22 and the first sliding hole 23. The valve seat member 49 is fitted into the second mounting hole 22 so as to be received at one end of the spacer 48.

The valve seat member 49 is made of rubber, for example, and is sandwiched between a spacer 50 and a filter 50 which is connected to one end of the housing main body 15 by press fitting or the like. That is, the valve housing 14 is
The cover member 16 is a part of the filter 50, and the filter 50 is attached to one end of the housing main body 15 by press-fitting the cover member 16 into the first mounting hole 21, and the valve seat The member 49 is the valve housing 1
4 will be fixed.

The valve seat member 49 is provided with a valve hole 52 coaxial with the axis of the valve housing 14. On the opposite side of the filter 50, the valve seat member 49 is tapered so that the valve hole 52 faces the center. A valve seat 53 is provided.

A cylindrical valve shaft 54 coaxial with the valve hole 52 is slidably fitted in the third sliding hole 25 of the fixed core 26 integral with the valve housing 14.
A ring-shaped valve body 55 that can be seated on the valve seat 53 of the valve seat member 49 is formed coaxially and integrally at one end of the valve seat member 49. The other end of the valve shaft 54 faces the control pressure chamber 38, and the movable core 39 is coaxially abutted on the other end of the valve shaft 54. A coil-shaped return spring 56 is provided between one end of the valve shaft 54 and the filter 50 so as to penetrate the valve seat member 49 coaxially.
4 is urged in a direction to bring the other end into contact with the movable core 39, and the valve shaft 54 and the valve body 55
Moves in the axial direction following the operation in the axial direction.

The valve shaft 54 has the same outer diameter over the entire length in the axial direction, and the valve body 55 formed to have the same outer diameter as the outer diameter of the valve shaft 54 on the valve seat member 49 side. Is seated on the valve seat 53. Therefore, the pressure receiving area facing the valve hole 52 of the valve body 55 seated on the valve seat 53 is set equal to the pressure receiving area facing the control pressure chamber 38 of the valve shaft 54.

The valve shaft 54 is coaxially provided with a passage 57 extending between both ends in the axial direction, and an orifice 58 interposed in the passage 57, for example, at an end on the valve body 55 side.
Is provided. Moreover, the other end surface of the valve shaft 54 has a passage 57.
The movable passage 39 for communicating the pressure to the control pressure chamber 38
And a groove 59 extending in the radial direction of the valve shaft 54 to be formed therebetween. Therefore, the valve hole 52 always communicates with the control pressure chamber 38 via the orifice 58.

First and second valve housings 14
A cylindrical body 61 is slidably fitted in the sliding holes 23 and 24 such that movement toward the control pressure chamber 38 is restricted at the step between the sliding holes 23 and 24. , The cylindrical body 6
An annular output chamber 62 that is always in communication with the output port 36 is formed between the outer surface on one end side of the valve 1 and the valve housing 14.
Thus, between the control pressure chamber 38 and the output chamber 62, the valve shaft 5
4 and a seal means for preventing the flow of brake fluid between the valve body 14 and the cylinder body 61 and between the valve housing 14 and the cylinder body 61. The seal means is provided at the other end of the valve shaft 54. An annular seal member such as an O-ring 60 interposed between the outer surface and the inner surface of the second sliding hole 24 in the fixed core 26 integral with the valve housing 14 so as to be able to slide in the axial direction; O-ring 60
Is disposed so as to face the other end surface of the cylindrical body 61.

When the hydraulic pressure in the control pressure chamber 38 is higher than the hydraulic pressure in the output chamber 62, the O-ring 60
8 also acts as a piston that presses the cylindrical body 61 toward the output chamber 62 in response to the hydraulic pressure of the output chamber 8. When the hydraulic pressure of the control pressure chamber 38 is lower than the hydraulic pressure of the output chamber 62,
Receiving from the cylinder 61, the control pressure chamber 38
Side, but comes into contact with a step formed between the second and third sliding holes 24 and 25 to thereby control the control pressure chamber 3.
Movement to the 8 side is regulated.

A portion of the output chamber 62 on the valve seat member 49 side is formed in a cylindrical shape having one end close to and opposed to the valve seat member 49 and protrudes radially outward so as to be received by the flange 48 a of the spacer 48. A synthetic resin orifice valve seat member 64 having a flange 64a on the other end side is inserted,
A spring 63 is provided between the orifice valve seat member 64 and the cylindrical body 61. The spring force exerted by the spring 63 urges the cylindrical body 61 toward the control pressure chamber 38, and the orifice valve seat member 64 is substantially fixed to the valve housing 14.

The inner diameter of the orifice valve seat member 64 is
5, the annular path 65 is formed between the orifice valve seat member 64 and the valve element 55. Thus, the annular passage 65 is connected to the valve seat 5 of the valve body 55.
At the time of separation from the valve 3, the valve hole 52 is communicated.

At one end of the cylindrical body 61, that is, at the end on the output chamber 62 side, an orifice valve body 66 formed in a ring shape so as to be able to be seated on the orifice valve seat member 64 is formed coaxially and integrally. And this orifice valve element 66
And the orifice valve seat member 64 constitute an orifice valve 67. That is, in the orifice valve seat member 64, a groove 68 extending in the radial direction of the orifice valve seat member 64 through the inner end of the annular passage 65 is formed at one end of the cylindrical body 61, that is, the end face facing the orifice valve body 66.
Is provided so that its outer end is located at least outside the portion corresponding to the outer periphery of the orifice valve body 66. When the orifice valve body 66 is seated on the orifice valve seat member 64, the annular passage 65 and The flow of the brake fluid between the output chambers 62 becomes possible only through the grooves 68, and the flow of the brake fluid between the annular passage 65 and the output chamber 62 is reduced. The cylindrical body 61 is the control pressure chamber 3
When the orifice valve body 66 moves to the side 8 and separates from the orifice valve seat member 64, the annular passage 65 and the output chamber 62 communicate with each other without restricting the flow of the brake fluid.

Next, the operation of this embodiment will be described. In the normally open solenoid valve 4, when the coil 42 is in the demagnetized state, the movable core 39 is pressed by the spring force of the return spring 56 from the valve shaft 54. Is separated from the fixed core 26, and in this state, the valve body 55 is in an open state in which the valve body 55 is separated from the valve seat 53 as shown in FIGS.
In this valve open state, the control pressure chamber 38 is connected to the valve hole 5 through the passage 57 and the groove 59 with the orifice 58 interposed therebetween.
2 and the same hydraulic pressure acts on both ends of the valve shaft 54. Therefore, when the coil 42 is excited and the valve body 55 is seated on the valve seat 53 in order to execute the anti-lock brake control for reducing the brake fluid pressure of the wheel brake B, the valve shaft 54 and the valve body 55 are closed. The electromagnetic force required to operate in the direction is relatively small. As shown in FIG. 4, when the valve body 55 is seated on the valve seat 53 and the valve is closed, the valve body 55 and the valve shaft 54 are provided with the hydraulic pressure generated by the hydraulic pressure on the valve hole 52 side and the spring of the return spring 56. The sum of the forces acts in the valve opening direction, and the fluid pressure due to the fluid pressure in the control pressure chamber 38 acts in the valve closing direction. However, the pressure received by the valve body 55 seated on the valve seat 53 faces the valve hole 52 side. Since the area is equal to the pressure receiving area facing the control pressure chamber 38 of the valve shaft 54 and the hydraulic pressure of the valve hole 52 and the hydraulic pressure of the control pressure chamber 38 are equal, the valve body 55 is seated on the valve seat 53 in a closed state. Is only required to overcome the spring force of the return spring 56, and the electromagnetic force can be relatively small.

The valve body 55 is formed coaxially and integrally with one end of the cylindrical valve shaft 54, and the valve hole 52 and the control pressure chamber 38 are always in communication with each other through a passage 57 provided in the valve shaft 54. The pressure receiving area facing the valve hole 52 side of the valve body 55 seated on the valve seat 53 is the control pressure chamber 38 of the valve shaft 54.
With the simple configuration that is set to be equal to the pressure receiving area facing the valve, the force required to operate the valve shaft 54 and the valve body 55 to the closed state and to maintain the valve closed state can be made relatively small. Becomes Moreover, even if the diameter of the valve hole 52 is set to be relatively large, it is possible to prevent the diameter of the valve shaft 54 from increasing. That is, it is possible to set the diameter of the valve hole 52 to be relatively large while preventing the valve housing 14 from increasing in size, thereby making it possible to reduce the flow resistance of the brake fluid. Moreover, the valve body 55 is simply formed integrally and coaxially at one end of the cylindrical valve shaft 54, so that the valve shaft 54 and the valve body 55 can be easily processed without requiring strict processing accuracy. Can be.

When the normally open solenoid valve 4 is closed as described above to reduce the brake fluid pressure of the wheel brake B, the valve hole 52 communicating with the input port 27 is provided in the control pressure chamber 3.
Since the output hydraulic pressure of the master cylinder M acting on the input port 27 is higher than the brake hydraulic pressure of the wheel brake B, that is, the hydraulic pressure of the output chamber 62, the O-ring 60 The cylinder 61 slides so as to push toward the output chamber 62 side, and has been operated to a position where the orifice valve body 66 at one end thereof is seated on the orifice valve seat member 64.

From the state in which the normally-open solenoid valve 4 is closed as described above, at the initial stage when the normally-open solenoid valve 4 is opened in order to increase the brake fluid pressure of the wheel brake B, FIG. As shown, the orifice valve 67 has the orifice valve element 66 seated on the orifice valve seat member 64, and the output chamber 62, that is, the output port 3 from the annular passage 65 communicating with the valve hole 52.
The orifice valve 67 restricts the flow of the brake fluid to 6. As a result, the output hydraulic pressure of the output port 36, that is, the brake hydraulic pressure of the wheel brake B gradually increases. Moreover, since the cylinder 61 is biased toward the control pressure chamber 38 by a spring, when the hydraulic pressure in the output chamber 62 is gradually increased to a certain value, the cylinder 61 moves the orifice valve body 66 to the orifice valve seat member 64. The brake fluid in the annular passage 65 that communicates with the input port 27 through the valve hole 52 does not flow through the output chamber 62, that is, the output port 62. 3
It will be distributed to the 6 side.

Thus, the normally-open solenoid valve 4 which has been closed to reduce the brake fluid pressure of the wheel brake B
It is possible to gradually increase the brake fluid pressure of the wheel brake B in the early stage of opening the valve, thereby preventing pulsation of the brake pressure and suppressing the generation of operation noise, and improving the riding feeling. It is possible to improve the pressure, and it is possible to gradually increase the pressure without the need for electrical control.
Excellent reliability can be obtained.

In the closed state in which the valve body 55 is seated on the valve seat 53, the control pressure is applied between the valve shaft 54 and the cylindrical body 61 fitted to each other and between the cylindrical body 61 and the valve housing 14. If the brake fluid leaks from the chamber 38 to the output chamber 62 side, the throttle function of the orifice valve 67 at the initial stage of valve opening from the closed state cannot be performed.
O-ring 60 provides a seal between control pressure chamber 38 and output chamber 62. That is, the O-ring 60 is opposed to the end face of the cylindrical body 61 on the side opposite to the orifice valve 67, and is slidable in the direction of pushing the cylindrical body 61 under the pressure of the control pressure chamber 38. The valve is interposed between the valve shafts 54, and the control chamber 38 and the output chamber 62 are closed when the valve is closed with a minimum number of parts that are interposed only between the valve housing 14 and the valve shaft 54.
To the brake fluid. Moreover, the O-ring 60 also functions as a piston that pushes the cylindrical body 61 to operate the orifice valve 67.
A single component can perform multiple functions.

When the brake is operated in the non-antilock brake control state, that is, when the normally-open solenoid valve 4 is opened and the normally-closed solenoid valve 7 is closed, the output hydraulic pressure of the master cylinder M is applied to the wheel brake B. When there is almost no hydraulic pressure difference between the input port 27 and the output port 36, it is necessary to increase the brake hydraulic pressure of the wheel brake B promptly. When the high-pressure brake fluid pressure is suddenly applied, the relatively high brake fluid pressure does not directly act on the control pressure chamber 38 because the orifice 58 is provided in the passage 57 of the valve shaft 54. Therefore, even if the pressure difference between the input port 27 and the output chamber 62 temporarily increases due to the sudden action of the brake hydraulic pressure on the input port 27, the cylinder 61 is moved by the hydraulic pressure in the control pressure chamber 38. Without being pushed to the 62 side,
Since the hydraulic pressure is not restricted between the annular passage 65 and the output chamber 62 by the orifice valve 67, a relatively high brake hydraulic pressure can be quickly applied to the wheel brake B from the output port 36.

Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the appended claims. It is possible to do.

For example, in the above embodiment, the case where the present invention is applied to a normally-open solenoid valve has been described. However, the present invention can be applied to a normally-closed solenoid valve, and the solenoid valve device of the present invention can be applied. Can be widely implemented as an electromagnetic valve device for controlling a fluid pressure applied from a fluid pressure generation source to a fluid pressure actuator as well as a device for an antilock brake control device for a vehicle.

[0052]

As described above, according to the first aspect of the present invention, the force for operating the valve shaft and the valve body in the valve closing direction so that the valve body is seated on the valve seat, and the valve body is provided with the valve seat. It is possible to reduce the force for maintaining the valve-closed state in which the solenoid valve device is seated, and to reduce the flow resistance of the working fluid while avoiding an increase in the size of the electromagnetic valve device. In addition, with a simple configuration in which the valve element is formed integrally and coaxially at one end of the cylindrical valve axis, the valve axis and the valve element can be easily processed without requiring strict processing accuracy. it can.

According to the second aspect of the invention, in the initial stage when the valve shaft at the valve closing position is operated in the valve opening direction, the flow of the working fluid from the valve hole to the output port is reduced by the orifice valve. Accordingly, the output fluid pressure at the output port can be gradually increased, and the pressure can be slowly increased without the need for electrical control, so that excellent reliability can be obtained.

According to the third aspect of the invention, when the valve is opened in a state where there is no fluid pressure difference between the input port and the output port, a relatively high fluid pressure suddenly acts on the input port from the fluid pressure generating source. At this time, it is possible to prevent the orifice valve according to the second aspect from operating in the valve closing direction, and quickly apply a relatively high fluid pressure to the fluid pressure actuator from the output port.

Further, according to the fourth aspect of the present invention, the sealing function interposed only between the valve housing and the valve shaft provides a sealing function between the control pressure chamber and the output chamber when the valve body is seated on the valve seat. , Can act as a piston that pushes the cylinder, and can perform multiple functions with a single minimal piece.

[Brief description of the drawings]

FIG. 1 is a system diagram of a vehicle brake device.

FIG. 2 is a vertical sectional view of a normally-open solenoid valve in an open state.

FIG. 3 is an enlarged view of a main part of FIG. 2;

FIG. 4 is a longitudinal sectional view of the normally-open solenoid valve in a closed state.

FIG. 5 is a longitudinal sectional view of the normally-open solenoid valve immediately after opening.

[Explanation of symbols]

 4 Normally open solenoid valve as electromagnetic valve device 14 Valve housing 27 Input port 36 Output port 38 Control pressure chamber 39 Movable core 49 Valve Seat member 52 ... valve hole 53 ... valve seat 54 ... valve shaft 55 ... valve body 57 ... passage 58 ... orifice 60 ... O-ring as a seal member 61 ... Cylindrical body 62 ... Output chamber 64 ... Orifice valve seat member 65 ... Annular path 66 ... Orifice valve body 67 ... Orifice valve B ... Wheel brake as fluid pressure actuator M ... Master cylinder as fluid pressure source

Claims (4)

[Claims] 1. A valve housing (14) having an input port (27) leading to a hydraulic pressure source (M) and an output port (36) leading to a hydraulic actuator (B).
A valve housing (14) having a valve seat (53) with a valve hole (52) leading to the input port (27) facing the center.
A valve seat member (49) fixed inside the valve hole (52);
A valve shaft (54) supported on a valve housing (14) and formed in a cylindrical shape coaxial with the valve shaft and capable of sliding in the axial direction; and a valve seat (53) seated on the valve seat (53).
2) A valve body (55) provided at one end of the valve shaft (54) so as to be able to shut off between the output port (36) and a control pressure chamber facing the other end of the valve shaft (54). A movable core (39) housed in the control pressure chamber (38) so that the fluid pressure of the control pressure chamber (38) acts on both ends in the axial direction and having a movable core (39) connected to the other end of the valve shaft (54); In the valve device, the valve body (55) is formed in a ring shape and is formed coaxially and integrally with one end of the valve shaft (54), and the valve hole (52) is formed in the valve shaft (54).
And a passage (57) for constantly communicating between the control pressure chamber (38) and the pressure receiving area facing the valve hole (52) side of the valve body (55) seated on the valve seat (53),
An electromagnetic valve device characterized in that it is set to have a pressure receiving area facing a control pressure chamber (38) of the valve shaft (54). 2. A valve housing (14) having an input port (27) leading to a fluid pressure source (M) and an output port (36) leading to a fluid pressure actuator (B).
A valve housing (14) having a valve seat (53) with a valve hole (52) leading to the input port (27) facing the center.
A valve seat member (49) fixed inside the valve hole (52);
A valve shaft (54) supported on a valve housing (14) and formed in a cylindrical shape coaxial with the valve shaft and capable of sliding in the axial direction; and a valve seat (53) seated on the valve seat (53).
2) A valve body (55) provided at one end of the valve shaft (54) so as to be able to shut off between the output port (36) and a control pressure chamber facing the other end of the valve shaft (54). A movable core (39) housed in the control pressure chamber (38) so that the fluid pressure of the control pressure chamber (38) acts on both ends in the axial direction and having a movable core (39) connected to the other end of the valve shaft (54); In the valve device, a passage (57) for constantly communicating the valve hole (52) and the control pressure chamber (38) is provided in the valve shaft (54), and an output chamber (62) communicating with the output port (36). And receiving the fluid pressure of the control pressure chamber (38) at both ends and controlling the control pressure chamber (38).
The valve shaft (54) is coaxially fitted to a cylindrical body (61) which is spring-biased and slidably fitted to the valve housing (14) so as to allow relative sliding in the axial direction. Between the control pressure chamber (38) and the output chamber (62), between the valve shaft (54) and the cylindrical body (61) and between the valve housing (14) and the cylindrical body (61). A seal means (60) for preventing the flow of the working fluid is provided, and when the valve body (55) separates from the valve seat (53), the annular passage (65) communicating with the valve hole (52) is connected to the valve body. (55) formed between the orifice valve seat member (64) and fixed to the valve housing (14); and the orifice valve seat member (64) can be seated on the orifice valve seat member (64).
The orifice valve element (66) provided at the end on the side of the output chamber (62) of (1) outputs the annular path (65) when the cylindrical body (61) moves toward the control pressure chamber (38). When the orifice valve body (66) is seated on the orifice valve seat member (64) accompanying the movement of the cylindrical body (61) toward the output chamber (62), the annular path ( 65) An electromagnetic valve device comprising an orifice valve (67) for restricting the flow of fluid between the output chamber (62) and the output chamber (62). 3. The passage (57) is provided in the valve shaft (54).
The solenoid valve device according to claim 2, wherein an orifice (58) is provided in the middle of the valve. 4. The sealing means (60) faces the end face of the cylinder (61) on the side opposite to the orifice valve (67), and receives the pressure of the control pressure chamber (38). An electromagnetic seal according to claim 2 or 3, characterized in that it is an annular seal member which is slidable in the pushing direction of the valve housing and which is interposed between the valve housing (14) and the valve shaft (54). Valve device.