JPS6198665A - Multi-directional control valve device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field of the Invention] The present invention relates to a multi-directional control valve device for a brake pressure generating device of a hydraulic brake system with slip control for an automobile.

A multi-way control valve arrangement of this kind comprises a control slide valve slidably guided longitudinally within a valve housing and a first hydraulic fluid passage leading from a source of hydraulic fluid to a pressure chamber of a pressure generating device. , a plurality of control valves that integrally control the second hydraulic fluid passage flowing out from the pressure chamber to the fluid reservoir and are slidable in the longitudinal direction, and the output is controlled from the outside as a multi-directional valve. has been done.

[Prior Art of the Invention and its Problems] This type of multi-directional control valve device is used, for example, in a brake pressure generation device of a hydraulic brake system with slip control for automobiles, and in this brake pressure generation device, the brake pedal By stepping on the brake pedal, the braking operation is initiated and at the same time hydraulic fluid can flow out from the suction port into the pressure chamber containing the booster piston. At one end of a braking operation, such a multi-way control valve arrangement allows hydraulic fluid in the pressure chamber to flow back to the fluid reservoir.

This type of conventional multi-directional control valve device (West German Patent No. 33
No. 38249, 2), the valve member actuated by the brake pedal via a lever transmission mechanism is designed as a control slide valve, and the disadvantage of this valve member is that, especially after a long actuation time, the control slide cannot be activated. Clearances due to moving parts often occur, which allow unwanted hydraulic fluid to escape into the pressure behind the booster piston, or some of the incoming hydraulic fluid is immediately forced back into the backflow passage.
There is no possibility of a complete rise in pressure in the pressure chamber.

OBJECTS OF THE INVENTION The objects of the invention are, firstly, to provide significantly less wear and reliability in operation; secondly, the forces to be controlled are relatively very small; and thirdly, , in any switching position a total of three connections are connected to each other simultaneously,
A fourth object is to provide the above-mentioned multi-directional control valve device which has a simple structure and can change the control time within a narrow limit range by simple adjustment.

[Summary of the Invention and Effects thereof] According to the present invention, the above-mentioned object is achieved by providing a multi-way control valve device having first and second valve sleeves coaxially disposed in a housing hole with one behind the other. For example, the closing member of each of the first and second valve sleeves has a space between the first valve sleeve and the second valve sleeve,
the valve sleeve and the control slide valve; the housing hole is configured in a stepped shape; By forming a plurality of valve member housing chambers (a spring chamber, a valve chamber, and a booster backflow chamber) corresponding to a plurality of housing connection portions in the plurality of large-diameter stepped portions,
has been achieved.

Preferably, the first valve sleeve connects a pressure chamber from a spring chamber connected to a pressure source on one side of the first valve sleeve to a pressure chamber through a housing connection and a hydraulic fluid hole on the other side of the first valve sleeve. A passage for hydraulic fluid is formed to a valve chamber connected to the valve chamber, and at the end of the first valve sleeve facing the first valve sphere, there is a knob-like shape extending to sandwich the first valve sphere. A flange is provided for interacting with the arm of the member;
A portion of the knob-shaped member abuts against the second valve sleeve, and the knob-shaped member is movable under the action of the second valve sleeve.

Preferably, the first valve ball interacting with the first valve sleeve is held by a frame, which frame comprises a support plate engaged in a groove in the housing bore. The frame body has a circular apex portion with a large number of teeth arranged so as to partially sandwich the valve bulb body, and a plurality of openings are formed in the support plate. The arm portion of the knot-shaped member is penetrated.

Advantageously, the end of the control slide valve facing the second valve sleeve is formed with a head, which head is formed with a rounded top with a number of teeth. and
The circular apex portion is arranged to sandwich at least a portion of the second valve ball disposed between the head portion and the second valve sleeve, so that the second valve ball is attached to the valve brake. It is prevented from moving transversely to the longitudinal direction.

The ends of the first and second valve sleeves facing the first and second valve balls, respectively, are each formed with a disc-type or flange-type end member, and a front surface of the end member has a first end member. and a second valve ball, and the cylindrical shafts of the first and second valve sleeves are guided in a hermetically sealed manner within the housing bore.

To enable separate opening and closing of the multi-way control valve arrangement, the effective outer diameters of the cylindrical shafts of the first and second valve sleeves and the effective diameters of the valve seats are made equal.

Advantageously, the cylindrical shafts of the first and second valve sleeves are smaller than the effective cross-sectional area of the first and second valve sleeves carrying said valve seats for the first and second valve balls. The cross-sectional area is greater than or equal to the effective cross-sectional area of the valve seat. In order to reduce the manufacturing cost and replace the parts with simple parts, the housing hole is divided into a number of steps with different diameters, and the housing hole supporting the first and second valve sleeves is The steps have equal cross-sectional areas, while the steps of the housing bore forming the spring chamber, the valve chamber and the booster backflow chamber have equal cross-sectional areas.

[Example] Hereinafter, an example of the present invention will be described with reference to the drawings.

The drawing schematically shows a brake actuating device as a brake pressure generating device, which main actuating device has a housing 1 . A cylinder bore 2 is formed in this housing 1, and this cylinder bore 2 substantially consists of three cylinder bores 3+4*0. The cylinder hole 5 has a medium diameter portion whose diameter is increased compared to the cylinder hole 4 of the cylinder hole 2. On the other hand, the cylinder hole 4 has a large diameter portion which has the largest diameter in the cylinder hole 2. have.

The cylinder hole portion 3 has a small diameter portion with the smallest diameter,
This cylinder hole 3 accommodates two mask cylinder screws 1 to 6 and 7 that are slidable in the axial direction. An output chamber 8 is formed by the mask cylinder piston 6 and the housing 1. This output chamber 8 is in hydraulic communication with a wheel brake 10 via a housing connection 9 and a pressure circuit connected thereto. This wheel brake 10 is arranged, for example, on the front axle of a motor vehicle.

The mask cylinder piston 6 is provided with a central valve 12, which separates the output chamber 8 and the annular chamber when the mask cylinder piston 6 is axially displaced over a small, definable distance in the direction of actuation. 13 has been cut off. At the same time as this central valve 12 is closed, the connection between the hydraulic fluid chamber 14 and the output chamber 8 is also interrupted, so that the brake circuit communicating with the output chamber 8 becomes a closed hydraulic system.

Mask cylinder piston 7 is mask cylinder piston 6
The mask cylinder piston 7 and the mask cylinder piston 6 form an output chamber 15.

Communication from this output chamber 15 to the wheel brake 17 is established by means of the housing connection 16 . This mask cylinder piston 7 is also provided with a central valve 19, one of which corresponds to the central valve 12 of the mask cylinder piston 6, and which is operated in the same way as the central valve 12. .

Furthermore, the mask cylinder piston 7 located close to the pedal
A push rod 20 is formed therein. This push rod 20 extends inside the cylinder hole 4 of the cylinder hole 2, and one end of the push rod 20 attached to the pedal is supported by a booster screw 1-21. An annular chamber 22 is formed between the mask cylinder piston 7 and the booster piston 21,
This annular chamber 22 serves as a filling chamber in the filling stage.

A hydraulic fluid hole 23 leads from this annular chamber 22 to the hydraulic fluid chamber 14 .

One end of the booster piston 21 remote from the annular chamber 22 delimits the pressure chamber 25 of the hydraulic power booster. In this pressure chamber 22, an auxiliary pressure can be adjusted in response to the strength of the brake application. The booster piston 21 is connected to an actuating piston 26 which is mechanically connected via a pedal rod 27 to a brake pedal 28 . Further, the configuration of this hydraulic power booster includes a multi-directional control valve device 29, and two of the multi-directional control valve devices are provided with a control slide valve 30, which is a control slide valve. 30 and has a predetermined position relative to the valve housing 31 surrounding the valve housing 30 . On the left side of the control slide valve 30 as viewed in the drawing, a booster backflow chamber 32 is formed as a valve member receiving chamber, and this booster backflow chamber 32 is connected to the unpressurized fluid reservoir 11 by means of a housing connection 33 . It is connected.

Connected to the control slide valve 30 of the multi-way control valve arrangement 29 is a lever actuating device actuated by a lever, which essentially consists of two levers 34,35, which The levers 34,35 are arranged parallel to each other. In this arrangement, one end of the lever 35 is formed with a spherical head which is rigidly connected to the valve housing 31 and the other end of the lever 35 engages in a recess in the actuating piston 26. has been done.

In the drawing, the upper end of the lever 34 rests on a control slide valve 30 of the multi-way control valve arrangement 29. Lever 3 according to the drawing
The lower end of 4 is in contact with the booster piston 21. Both levers 34,35 are connected to each other by a pivot connection 37.

The operation of the brake system described above is as follows.

In the brake release position, all moving parts are in the positions shown in the drawing. When a pedal force is applied to the brake pedal 28, the actuating piston 26 is slid outward in the drawing. An auxiliary pressure responsive to the position of the brake pedal 28 is regulated via two multi-way control valve arrangements connected to an accumulator 38 as a pressure source. booster piston 2
1, the pressure in the pressure chamber 25 of the hydraulic power booster is increased to a predetermined level, and the booster piston 21 begins to move in the actuating direction. As a result, the hydraulic fluid arranged in the annular chamber 22 is pressurized, this hydraulic fluid is introduced into the hydraulic fluid chamber 14 via the hydraulic fluid hole 23, and further this hydraulic fluid is transferred from the hydraulic fluid chamber 14 to the fluid reservoir 18. is refluxed to. Due to the increased pressure in the working chamber 15, the wheel brakes 17 on the rear axle of the motor vehicle are pressurized. Further, the hydraulic pressure in the working chamber 15 also acts on the mask cylinder piston 6, and the mask cylinder piston 6 moves in the working direction. A hydraulic pressure is then generated in the working chamber 8, which is transmitted to the brake wheel 10 by the housing connection 9 and the pressure circuit connected thereto.

As soon as the wheels of the motor vehicle enter the slip limit region, this slip condition is detected by an electronic slip control device (not shown). As a result, corresponding control signals are transmitted to the suction valve 24 and the solenoid valves 40.degree. 39.41, 4.2, respectively. The electromagnet 65 of this suction valve 24 is excited,
A hydraulic connection between the hydraulic fluid chamber 14 and the pressure circuit 43 is established. For this reason, the suction valve 24 is connected to the fluid reservoir 18.
This is the position where the valve passage towards is closed. The accumulator 38 is also arranged in the pressure circuit 43, and the pressure in this accumulator 38 is transferred to the annular chamber 1 via the suction valve 24, the pressure circuit 66, the hydraulic fluid chamber 14, and the hydraulic fluid hole 23°45.
It propagates and rises to 3.22. As soon as a hydraulic fluid connection is established between the pressure chamber 25 and the accumulator 38 and between the reannular chamber 13.22, respectively, the solenoid valve 39.
41 is moved to the open position, and the solenoid valves 40 and 42
is placed in the open position. The pressure in the wheel cylinder of the wheel 10.17, which has entered the slip limit range, is then discharged towards the reservoir 46.47. When the pressure in the wheel brake 10.17 of the corresponding wheel decreases, the solenoid valves 40, 42 are closed, and the solenoid valve 3 is closed.
9.40 opens a passage for hydraulic fluid, and the hydraulic fluid flows from the accumulator 38 to the suction valve 24 and the hydraulic fluid chamber 1.
4 and via the central valve 12.19, at the same time protecting the booster piston 21 from continuous movement in the operating direction. As soon as the tendency towards locking in the wheel or wheels has passed, the suction valve 24 opens the valve passage from the hydraulic fluid chamber 14 to the fluid reservoir 18. At the same time, the suction valve 24 closes the hydraulic fluid connection leading to the pressure chamber 25.

For this purpose, the suction valve 24 is provided with a valve sleeve 50. This valve sleeve 5o is supported in the first housing hole 49, and this valve sleeve 50 is supported by a spring 5.
It is possible to slide against a biasing force of 1. This valve sleeve 5
A closing member 52 is held and guided within o.

A longitudinal hole is formed in this closing member 52, and a valve seat 54 is provided at one end of this longitudinal hole. This valve seat 54 interacts with a valve ball 55 , which is partially held by a frame 56 . On the side of the valve ball 55 remote from the valve sleeve 50, a closing member 58 is supported in the second housing bore 57. This closing member 58 has a valve seat 59 . When the hydraulic fluid connection 48 to the pressure circuit 43 is closed, this valve seat 59 rests against the valve ball 55. A fingertip-shaped protrusion 6 is provided on the side of the valve sleeve 50 facing the valve bulb 55.
0.60- is formed. These protrusions, 60.
60' extends with play into the corresponding opening 61°61' of the frame 56. The frame 56 holds the valve ball 55 and is supported within the groove 62 of the valve housing 75. A plunger 64 is supported within the bore 63 of the valve housing 75 at one end of the valve sleeve 50 remote from the valve ball 55 . This plunger 64 is slidable by an electromagnet 65, and one end of this plunge broom 64 abuts against the valve sleeve 50.

The suction valve 24 operates as follows.

In the state shown in the drawings (brake release position), the valve sleeve 50 in its initial position is located in the first housing hole 49.
on the left side. That is, the valve sleeve 50 is biased to this initial position by the spring 51. Housing connection part 48
The pressure inside and in the pressure circuit 43 presses the closing member 58 with the valve seat 59 against the valve ball 55 . During this pressing, the pressure in the housing connection 48 and in the pressure circuit 43 is effectively exerted on the ring-shaped cross-section of this closure member 58 . In this position, the hydraulic fluid in the hydraulic fluid chamber 14 of the connected device flows through the pressure circuit 66, the housing connection 67, the opening 61 between the projection 60° 60' and the frame 56.
．． 61 ′, the longitudinal bore 53 , the hydraulic fluid bore 68 , the lateral bore 69 , the housing connection 70 and the circuit 71 into the oil reservoir 18 . Here, when any one of the wheels enters the slip limit region, the electromagnet 65 is energized, as a result of which the protrusion 60° 60- moves into the collar 7.
2, the plunger 65 moves the valve sleeve 50 to the right. The closing member 58 then moves away from the valve ball 55.

In this state, the length of the discharge portion 60.60 is such that the valve seat 54 of the closing member 52 comes into contact with the valve bulb 55 just before the closing member 58 moves away from the valve bulb 55; and housing connection portion 67 to housing connection portion 7
The length is such that it blocks the passage of hydraulic fluid to 0. In the state where the passage of hydraulic fluid from the housing connection part 67 to the housing connection part 70 is blocked, the housing connection part 48
Since the pressure at is no longer acting on the ring-shaped cross-section when opened, the hydraulic fluid flows from the pressure chamber 25 to the pressure circuit 43, the housing connection 48, the longitudinal bore 73 of the closing member 58, the valve chamber 74, the housing connection 67. and flows freely into the hydraulic fluid chamber 14 via the pressure circuit 66. The hydraulic fluid then flows from this hydraulic fluid chamber 14 via the hydraulic fluid hole 23.45 into the annular chamber 13.22, and from the annular chamber 13.22 via the central valve 12.19. It flows out into the action chambers 8 and 15.

The multi-way control valve arrangement 29 has a 1liIII slide valve 30 which is slidably guided in the valve housing 31 in the longitudinal direction. Further, a head portion 102 is formed in the control slide valve 30, and a vent hole 96 is formed in the control slide valve 30. The head portion 102 is supported by the valve housing 31 via a spring 80. A circular apex portion 81 having a large number of teeth is formed on the front surface of the head portion 102 . This circular top portion 81 extends in the longitudinal direction, and holds and guides the valve ball 82. This valve ball 82 is the valve sleeve 8
It interacts with the valve seat 83 of No. 4. This valve sleeve 8
4 is supported within the valve housing 31. The end of the valve sleeve 84 located opposite the valve seat 83 has a cage-shaped portion 8 .
It is in contact with 5. This cage-shaped part 85 supports a valve sleeve 87 via an arm part 86, more precisely a part 89 of the flange 21 of the valve sleeve 87, and this flange part 89 has a valve seat 8.
8 is formed. The end of the valve sleeve 87 remote from the valve ball 90 abuts an annular disc 91 . This annular disc 91 is connected to the valve housing 3 via a spring 92.
1 is supported.

The valve ball 90 is guided by a support plate 93,
This support plate 93 is held fixed to the valve housing 31 by radial arm portions 94 . Also,
The valve plate 93 is formed with a circular apex 95 having a large number of teeth, and the circular apex 95 is arranged so as to sandwich the valve sphere 90 therebetween. Therefore, in the valve housing 31,
The housing hole 103 is formed in a stepped structure, and has a valve member housing chamber with a large diameter, that is, a spring chamber 99, a valve chamber 100, and a booster backflow chamber 32.

The operation of the multi-directional control valve device 29 will be described below.

When the brake pedal 29 is actuated, the push rod 27 opens the control slide valve 30 to the left via the actuation piston 26 and the lever 34. Due to this sliding movement, the valve ball 82 seats on the valve seat 83 of the control sleeve 84, and the valve ball 82 is moved from the pressure chamber 25 to the hydraulic fluid hole 101, the valve sleeve 84, the booster backflow chamber 32, and the housing connection. Part 33
and closing the hydraulic fluid connection reaching the fluid reservoir 11 through the fluid circuit 97 . In particular, when the valve ball 82 is seated on the valve seat 83 of the valve sleeve, the screen-shaped portion 85 in contact with the valve sleeve 84 separates the valve sleeve 87 from the valve ball 90 via its arm portions 86° and 86'. will be moved. The blind-shaped portion 85 then slides the valve sleeve 87 to the left. The hydraulic fluid can flow out from the accumulator 38 into the pressure chamber 25 through the fluid circuit 98, the spring v99 as a valve member housing chamber, the valve sleeve 87, the valve chamber 100 as a valve member housing chamber, and the hydraulic fluid hole 101. Therefore, the length of the arm portions 86, 86- is such that the valve ball 82 is
Immediately after seating on the valve seat 83 of the valve sleeve 87 or simultaneously with the seating of the valve ball 82 on the valve seat 83, the valve sleeve 87 is moved and the valve passage between the valve ball 82 and the valve seat 83 is opened. The opening operation of the valve passage between the sphere 90 and the valve seat 88 is performed continuously.

[Brief explanation of the drawing]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The drawing is a longitudinal sectional view schematically showing a multi-directional control valve device according to an embodiment of the present invention and a brake actuation device as a brake pressure generating device incorporating this multi-directional control valve device. DESCRIPTION OF SYMBOLS 1...Housing, 6.7...Mask cylinder piston, 8,15...Output chamber, 10.17...Wheel brake, 11,18.46.47...Fluid reservoir, 13.22 ... annular chamber, 14 ... hydraulic fluid chamber,
21... Booster piston, 23.45.10'l.
...Hydraulic fluid hole, 24...Suction valve, 26...Operating screws 1 to 28...Brake pedal, 29...Multi-directional control valve device, 30...Control sliding valve, 31 ... Valve housing, 32 ... Booster backflow chamber, 33, 104,
105...Housing connection part, 34.35...Lever, 38...Accumulator, 39.40.4L 4
2... Solenoid valve, 81... Round top, 82.90...
Valve ball, 83.88... Valve seat, 84.87... Valve sleeve, 89... Flange portion, 91... Annular disc, 92... Spring, 93... Support plate, 94...
...Arm part, 95...Circular top part, 99...Spring chamber, 10
0... Valve chamber, 103... Housing hole. Applicant's agent Patent attorney Takehiko Suzue'-25-

Claims (7)

[Claims] (1) a control slide valve slidably guided longitudinally within the valve housing; a first hydraulic fluid passageway for discharging hydraulic fluid from a source of hydraulic fluid to a pressure chamber of the brake pressure generating device; A multi-directional control valve device comprising a plurality of control valves that are longitudinally slidable and control a second hydraulic fluid passageway for flowing hydraulic fluid from a chamber to a fluid reservoir, wherein the control valve is configured to control a plurality of control valves that are slidable in a longitudinal direction. the housing has first and second valve sleeves disposed coaxially within a housing bore formed in the housing; a first valve ball disposed between the second valve sleeve and a second valve sleeve disposed between the second valve sleeve and the control slide valve; It is composed of a valve ball, and the housing hole is structured in a stepped shape.
The plurality of large-diameter step portions in the housing hole have a plurality of valve member accommodation chambers (
A multi-directional control valve device characterized in that a spring chamber, a valve chamber, and a booster backflow chamber are formed. (2) the first valve sleeve has a spring chamber connected to the pressure source on one side of the first valve sleeve to a housing connection and a hydraulic fluid hole on the other side of the first valve sleeve; A hydraulic fluid passage is formed through the valve chamber to the valve chamber connected to the pressure chamber, and the end of the first valve sleeve facing the first valve sphere has a groove so as to sandwich the first valve sphere. a flange portion is provided which interacts with an arm portion of the cage-shaped member extending in the direction, a portion of the cage-shaped member abutting against the second valve sleeve; The multi-way control valve device according to claim 1, wherein the multi-way control valve device is movable by the action of the second valve sleeve. (3) the first valve ball interacting with the first valve sleeve is held by a frame, the frame comprising a support plate engaged in a groove in the housing bore; and the frame has a circular top portion having a large number of teeth and arranged so as to partially sandwich the first valve ball;
Alternatively, the support plate has a sleeve-shaped attachment member, and the support plate has a plurality of openings, and the arms of the cage-shaped member pass through these openings. A multi-directional control valve device according to item 1 or 2 of the range. (4) A head portion is formed at the end of the control slide valve facing the second valve sleeve, and this head portion is formed with a circular top portion having a large number of teeth. The circular top portion is arranged to sandwich at least a portion of the second valve ball disposed between the head portion and the second valve sleeve, so that the second valve ball is disposed between the head portion and the second valve sleeve. The multi-way control valve device according to any one of claims 1 to 3, wherein the multi-way control valve device is prevented from moving in a lateral direction with respect to the longitudinal direction of the brake. (5) A flange portion is formed at each end of the first and second valve sleeves facing the first and second valve spheres, and the front surface of the flange portion is provided with a flange portion. A valve seat is formed for each of the second valve balls, and the cylindrical shafts of the first and second valve sleeves are supported and guided in a gas-tight manner within the housing bore. A multi-directional control valve device according to any one of claims 1 to 4. (6) the cylindrical shafts of said first and second valve sleeves are smaller than the effective cross-sectional area of said first and second valve sleeves holding said valve seats for said first and second valve balls; Claims 1 to 5, characterized in that the cross-sectional area is larger than or equal to the effective cross-sectional area of the valve seat, respectively.
The multi-directional control valve device according to any one of the items. (7) The housing hole is divided into a number of stepped portions having different diameters, and the stepped portions of the housing hole supporting the first and second valve sleeves each have an equal cross-sectional area. On the other hand, the stepped portions of the housing hole forming the spring chamber, the valve chamber, and the booster backflow chamber, respectively,
The multi-way control valve device according to any one of claims 1 to 6, characterized in that the multi-way control valve device has equal cross-sectional areas.