JPS5839097B2 - Norimonobrakekikeityouseigiyobenkumitatetie - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a power control valve assembly for a vehicle brake system, and more particularly, to communication between a first port connected to a wheel brake and a second port connected to a storage tank. a normally open discharge valve for controlling the discharge valve; a normally closed mouth valve for controlling communication between the first port and a third port connected to a source of pressurized fluid; Next, the present invention relates to a type Q) power control valve assembly for a vehicle brake system, which comprises an actuating member for opening the above-mentioned artificial valve.

In conventional control valve assemblies of the type described above, zero flow after initial pressure is introduced into the brake during valve actuation, and therefore:
The poor control of the rate of pressure rise can cause the driver to receive a false feel from the brake pedal.

The present invention aims to overcome the above-mentioned disadvantages in a power control valve assembly of the above-described type by progressively controlling the flow rate through the inlet valve after it has opened.

That is, the present invention provides a power control valve assembly of the type described above, in which the inlet valve has a valve seat adjacent to one end of the Q passage between the first port and the third port; a large-mouth valve member for opening and closing the passage in cooperation with the valve seat; a rod penetrating the passage from the opposite side of the valve seat with a gap therebetween; the valve seat side end of the rond is adapted to engage the inlet valve member to control the position of the inlet valve member relative to the valve seat; An end of a predetermined length adjacent to the end has a substantially constant cross-sectional area over the entire length, a portion of the rond following the end has a cross-sectional area smaller than the cross-sectional area of the end O, and the rond has a cross-sectional area that is smaller than the cross-sectional area of the end O. After separating the artificial valve member from the valve seat by moving further toward the valve seat in the axial direction from the position where the end on the valve seat side engages with the inlet valve member, the end and the passage are sequentially moved. It is characterized in that it can take a position in which the restriction of the inlet valve is defined by the above, and a position in which the restriction of the artificial valve is defined by the portion 45 following the end portion and the passage.

When the rond further moves toward the valve seat after engaging with the artificial valve member, it separates the inlet valve member from the valve seat and opens the large mouth valve, but initially the rond has a relatively large cross-sectional area at the end. A relatively large throttling effect between the inlet valve and the passage acts on the flow through the inlet valve.

When the rond further moves in the same direction and the end completely escapes from the passage toward the valve seat, a relatively small throttling effect occurs between the passage and the portion with a smaller cross-sectional area than the end of the rond. Acts on the flow flowing through the large mouth valve.

That is, the throttling effect of the large mouth valve gradually decreases after the large mouth valve opens, thereby avoiding sudden changes in the flow rate.

Preferably, said large mouth valve member is pressed against said valve seat by elastic means.

Preferably, the inlet valve member is also spherical.

Preferably, the mouth valve is axially spaced from the exhaust valve, and the exhaust valve comprises an axially movable exhaust valve member and an axially movable exhaust valve seat.

Preferably, said passageway communicates with a chamber whose opposite end of the valve seat communicates with said first port.

Preferably, the end portion of the rond and the portion of small cross-sectional area following it both have a circular cross section and are connected by a conical shoulder.

Hereinafter, the present invention will be described in detail with reference to the drawings.

In the embodiment shown, the body 1 has two parallel stepped through holes 2 for fluid flow between a first port 4 connected to the brake circuit and a second port 5 and 0 connected to the reservoir. a self-contained exhaust valve assembly 3 for controlling a 30) port) connected to a source of pressurized fluid via a filter assembly 8;
and (10) a self-contained prosthetic valve assembly 6 for controlling fluid flow between the ports 4 and 10).

As shown in FIG. 4, the actuating plunger 9 is provided with axial and radial passages 11, one end of which communicates with the second port 5, and a discharge valve seat 1 at the forward end of the plunger 9.
2 is provided.

A sealing material 13 , 14 is located between the plunger 9 and the bore portion 10 to provide a seal to the port 5 .

The plunger 9 is formed with a flange 23 adjacent its forward end, and a return spring 24 for the plunger 9 acts between the rearward end of the mouth valve assembly 6 and the flange 23 to force the flange 23 into the hole 2. Press so as to engage the stepped portion 19.

The discharge valve assembly 3 includes a ball valve member 15 carried by the open end of a ball carrier 16 integral with a forwardly extending push rod 17.
Contains.

The carrier 16 is slidably guided in a counterbore 9' at the forward end of the plunger 9 by a pin 16' extending through a lateral bore in the carrier 16 and connected to the plunger 9.
is guided within a pair of diametrically opposed axial grooves 18 .

The valve assembly 3 further includes a spring 21 to support the plunger 9.
It includes a frusto-conical Q-cage 20 that snaps into a tubular boss 22 at the forward end of the cage.

Spring 21 is used only during inspection of the valve assembly.

The mouth valve assembly 6 preferably has two parts 2 in abutting engagement with each other.
5.26, is held in the large diameter portion 27 of the hole 2, and is held in contact with the stepped portion 28 in the hole 2 by an externally threaded plug 29, and the plug 29
By removing it, both valve assemblies 3, 6 can be removed from their ends of the bore 2.

Valve assembly 6 further includes a ball valve member 30 biased toward an annular valve seat 31 formed at the forward end of a stepped axial passageway 32 within body portion 26 , and includes a ball valve member 30 biased toward an annular valve seat 31 formed at the forward end of a stepped axial passage 32 within body portion 26 The aforementioned biasing force is provided by a spring 33 held in place by a frustoconical cage 34 that snaps into a rim 35 on the forward end of the extension 36o.

Tubular extension 361 is provided with radial slots to provide a passageway for fluid flow between valve seat 31 and chamber 38 of valve member 30.
A counterbore 37 is provided to provide for this when the valve is moved away from the valve seat by the push rod 17.

A radial passage 39 connects the chamber 38 to an annular recess 40 on the exterior of the body portion 25, which connects directly (via the filter assembly 8) to the 30th port 7.

A sealing material 4L42 is provided on the exterior of each body portion 25,26 to seal the recess 40.

The large diameter section 43 at the tip of the push rod 17 is slidable with a constant diameter within the narrow diameter section 44 of the passage 32, and the section 43 is converted into a long small diameter section 45 by an inclined diameter changing section 46. connected.

The operation of the control valve assembly will be explained.

When the plunger 9 is moved forward, the discharge valve seat 12 first engages with the ball valve member 15 and is moved to a position where communication between the 10th port 4 and the second port 5 is cut off by θ.

When the plunger 9 moves further forward, the ball carrier 16 is released by the spring 2.
11 is forced to move forward against the resistance of
As shown in FIG. 6, the ball valve member 30 of the large mouth valve assembly is moved away from the valve seat.

Pressurized fluid begins to flow from the third port 7 through the passage 42 to the first port 4.

The fluid flow passing through the valve initially when the valve is opened is subjected to a restricting action at the large diameter portion 43 at the tip of the push rod 17.

This flow area is reasonably and precisely controlled and is almost independent of the valve opening during the initial stroke.

As the plunger 9 moves further forward, the small diameter portion 45 of the rod 17o) comes out of the passage 32 and moves towards the valve seat 31.
), the throttling effect in passage 32 on fluid flow is reduced.

The transition from a state of high throttling to a state of low throttling is controlled by the shape of the diameter changing section 46 between the sections 43 and 45 of the rod 11.

The gradual actuation of the inlet valve according to the invention described above has the advantage of preventing abrupt changes in flow rate that occur when opening and closing conventional control valves, i.e., where fluid flow is determined solely by the position of the valve member relative to the valve seat. be.

A device for advancing the actuator plunger 9 will be described below.

A channel-shaped cross-section Φ balance beam 47 abuts at each end a tappet 67, which is fitted onto the rear end of the reduced diameter of the respective actuating plunger 9, and the beam 4
A pair of plates 48 are welded to the center in the longitudinal direction of the balance beam 47 and are spaced apart from each other and project forward.A rod 50 is attached to the plate 48 and extends rearward through an opening 65 in the base of the balance beam 47
A pin 49 is provided for connection with the (FIG. 2).

Externally threaded spigot 5 screwed into rod 50
A rubber block 53 is bonded to a circular plate 51 having a diameter of 2.

The rod 50 can freely slide within the hole 66 of the main body 1 during brake operation.

A cylindrical cup-shaped member 54 having a dish-shaped plate 55 inside.
is provided, the plate 55 is suitable for engaging with the tip of the rubber block 53, and the member 54 is attached to the mounting flange 5 of the main body 1.
9 (FIG. 5) between three circumferentially spaced ribs 60 of a housing 57 attached to the housing 57 by bolts 58.

A foot pedal 61 carries a roller 62 for engaging an outer end 63 of the tip 54, which projects outwardly through an opening 64 in the end of the housing 5T. .

When the foot pedal is operated, the tip-shaped member 54 moves forward, and the dish-shaped plate 55 engages with the tip 56 of the rubber block 53, causing the balance beam 47 and both actuating plungers 9 to move forward.

The rubber block 53 has a foot pedal 61 and an operating plunger 9.
It provides an elastic connection between the

[Brief explanation of drawings]

FIG. 1 is an end view of a pedal-actuated dual control valve assembly as an embodiment of the present invention. FIG. 2 is a plan view, partially in section, of the valve assembly of FIG. 1, with the pedal shown in the retracted position. 3 is a side view of the valve assembly of FIG. 1; FIG. FIG. 4 is an enlarged partial cross-sectional side view of a portion of the valve assembly of FIG. 1; 5 is a cross-sectional view of the valve assembly of FIG. 1; FIG. FIG. 6 is a partial cross-sectional view of the inlet valve of FIG. 4, showing the ball valve member in a slightly open position. FIG. 7 is a view similar to FIG. 6 but showing the valve member in a more open position. In the figure, 1 is the main body, 2 is a through hole, 3 is a discharge valve, 4 is a port connected to a wheel brake, 5 is a port connected to a storage tank, 6 is an inlet valve, and I is connected to a pressurized fluid source. port, 9 is an operating plunger, 15 is a ball valve member, 17 is a push rod, 30 is a ball valve member, 31 is a valve seat, 43 is a rod 1T
45 is the small diameter portion of the rod 1T, 46 is the large diameter portion at the end of the rod.
47 is a balance beam, 6γ is a tappet, 53 is a rubber block, 61 is a foot pedal, and 32 is a passage.

Claims (1)

[Claims] 1 A normally open discharge valve that controls zero communication between the 10th port connected to the vehicle brake and the 20th port connected to the storage tank, the 20th port connected to the first port and the pressurized fluid source A power control valve assembly for a vehicle brake system of the type comprising a normally closed large mouth valve that controls zero communication with three ports, and an actuating member that closes the discharge valve when activated and then opens the artificial valve, The inlet valve 6 includes a valve seat 31 adjacent to one end of the passage 32 between the first port 4 and the third port 7, and a large mouth valve that cooperates with the valve seat to open and close the passage. The member 30 comprises a rod 17 passing through the passage from the opposite side of the valve seat with clearance over the entire length of the passage, said rod being axially movable relative to said passage; The end 43 of a predetermined length adjacent the seat end of the rod is adapted to engage the inlet valve member to control the position of the inlet valve member relative to the valve seat. The rod has a substantially constant cross-sectional area over its entire length, and a portion 45 following the end of the rod has a cross-sectional area smaller than the cross-sectional area of the end; After the artificial valve member is separated from the valve seat by further moving in the axial direction toward the valve seat from the position where it engages with the valve seat, the valve member is sequentially moved to a position where the end portion and the passage define the restriction of the inlet valve. and a position in which a constriction of the large-mouth valve is defined by the portion 45 following the end and the passage.