JP3435190B2 - Load response type hydraulic pressure control valve - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a load-responsive hydraulic control valve in which an inertia valve detects a set deceleration and sets a split point for starting a rear hydraulic pressure reduction control according to a load. Regarding

[0002]

2. Description of the Related Art Conventionally, as this type of load-responsive hydraulic control valve, for example, the one shown in FIG. 4 has been known. In FIG. 4, reference numeral 1 denotes a valve body, and a hydraulic pressure control plunger 2 and a hydraulic pressure control plunger 2 are provided on the upper right side of the valve body 1.
The hydraulic pressure control mechanism including the poppet valve 4 provided in the internal flow path 3 and the valve seat 5 fixed to the outlet side of the internal flow path 3 is incorporated.

An inertia valve chamber 6 is formed below the hydraulic pressure control mechanism, and a G ball 7 as an inertia valve is rotatably incorporated in the inertia valve chamber 6. The master hydraulic pressure P1 from the master cylinder is applied to the outer peripheral portion of the hydraulic pressure control plunger 2, the liquid passage 8, the chamber 9 outside the G ball 7, the orifice 10, the inertia valve chamber 6, the inlet hole 12 of the valve seat 11, the liquid. It is supplied to the actuator piston 14 mounted on the left side of the valve body 1 through the supply passage 13.

A proportioning spring 15 is interposed between the actuator piston 14 and the hydraulic pressure control plunger 2 of the hydraulic pressure control mechanism, and a dummy spring 16 is further incorporated therein. In such a load-responsive hydraulic control valve, the valve body 1 is mounted with a predetermined mounting angle corresponding to the set deceleration with respect to the vehicle horizontal axis XX, and the set deceleration is set by braking the vehicle. G is obtained
The ball 7 rolls and sits in the inlet hole 12 of the valve seat 11,
The liquid supply passage 13 to the actuator piston 14 is shut off, and the master hydraulic pressure P1 at that time is contained in the actuator piston 14 side.

On the other hand, the actuator piston 14 makes a stroke by the supply of the master hydraulic pressure P1 via the inertia valve chamber 6, and when the hydraulic pressure is confined by the operation of the G ball 7, the stroke is stopped. Containment fluid pressure P
By applying the spring load of the proportioning spring 15 according to G to the hydraulic pressure control plunger 2, the split point (split hydraulic pressure) for starting the pressure reduction control of the rear hydraulic pressure P2 is set.

Subsequently, when the master hydraulic pressure P1 exceeds the split point, the valve seat provided on the outlet side of the internal flow passage 3 of the hydraulic pressure control plunger 2 which has begun to move to the left as the master hydraulic pressure P1 increases. 5 abuts on the poppet valve 4 to cut off the supply of the rear hydraulic pressure P2, and thereafter, by repeatedly opening and closing the internal flow path 3 by reciprocating the master hydraulic pressure P1 of the hydraulic pressure control plunger 2, the rear hydraulic pressure P2 is opened and closed. Supply fluid pressure P2
Is reduced with a predetermined reducing ratio to prevent the rear wheels from being locked immediately before the braking is stopped and to secure the braking stability of the vehicle.

[0007]

However, in such a conventional load-responsive hydraulic control valve, the G ball 7 that determines the containment hydraulic pressure PG has the timing of closing the inlet hole 12 of the valve seat 11. Since the containment hydraulic pressure PG varies due to the variation, there is a problem that the rear hydraulic pressure P2 supplied to the rear wheel cylinder also varies.

The cause is that when the vehicle is braked, the G ball 7 rolls in the direction of arrow A in FIG. 5 until it abuts the valve seat 11 by the inertial force to block the inlet hole 12 and supply the pressure at that time. Although it will be confined in the passage 13, at that time, all the amount of the liquid that passes through the liquid passage 8 and the chamber 9 in the master liquid pressure P1 sent from the master cylinder is passed through the orifice 10 arranged in series. This is because it acts as a liquid flow force on the G ball 7. The brake pedal force of the vehicle may be strong or weak, and therefore, the liquid flow force acting on the G ball 7 may be large or small, which causes an uncertain in addition to the rolling of the G ball 7 due to the original deceleration. Acts as a force. Therefore, the timing at which the G ball 7 closes the inlet hole 12 also varies.

Further, in the conventional example, there is no device for controlling the uncertain influence, and the variation of the containment hydraulic pressure PG is reduced by slightly changing the diameter of the orifice 10 and the orifice angle θ. . The present invention has been made in view of such a conventional problem, and the containment hydraulic pressure PG is controlled by controlling the timing of closing the inlet hole without applying the liquid flow force to the inertia valve.
Of the rear hydraulic pressure P2 is eliminated.

[0010]

In order to achieve the above object, the present invention closes an inlet hole that opens in a passage for liquid sent from a master cylinder by operating an inertia valve that senses a set deceleration. In a load-responsive hydraulic control valve for confining a master hydraulic pressure in an actuator piston communicating with an inlet hole, the inertial valve is arranged in parallel with the passage so as not to be affected by the hydraulic force of the liquid sent to the inertia valve. A sensor device for accommodating the inertia valve and closing the inlet hole is provided.

Further, according to the present invention, the sensor device includes an inertia valve, an inertia valve box, a push rod pushed by rolling of the inertia valve to close the inlet hole, and a return spring for returning the push rod. And the timing of closing the inlet hole is controlled by setting the load of the return spring. Further, in the present invention, the sensor device is provided with an orifice for applying a liquid flow force to the inertia valve from a side opposite to the push rod side, the inertia valve box being communicated with the orifice, and the sensor device being connected to the sensor device. An extension passage communicating with the passage is provided on the outside to control the timing of closing the inlet hole.

Further, the present invention is characterized in that the orifice diameter of the orifice is changed to control the timing of closing the inlet hole.

[0013]

According to the load-responsive hydraulic control valve of the present invention having such a configuration, the inertia valve is housed in parallel with the passage through which the liquid sent from the master cylinder flows, and the inlet is provided. A sensor device that closes the hole is provided to prevent the inertia valve from being affected by the liquid flow force of the liquid being sent, and the load is set by the return spring, and the push rod pushed by the rolling of the inertia valve causes the inlet to enter. Since the timing of closing the holes is controlled, it is possible to prevent variations in the containment liquid pressure, and as a result,
It is possible to prevent variation in the rear hydraulic pressure and obtain a stable braking force.

[0014]

Embodiments of the present invention will be described below with reference to the drawings. 1 and 2 are views showing an embodiment of the present invention. FIG. 1 is an overall sectional view of a load responsive hydraulic control valve, and FIG. 2 is a sectional view of a main part. First, the configuration will be described. In FIGS. 1 and 2, reference numeral 21 denotes a valve body,
Plunger housing hole 22 is formed in. A hydraulic pressure control plunger 23 is slidably stored in the plunger storage hole 22, and a poppet valve 25 is built in an internal flow path 24 of the hydraulic pressure control plunger 23. A valve seat 26 is provided on the outlet side of the internal flow path 24 of the hydraulic pressure control plunger 23.
Is provided, and the poppet valve 25 pressed by the return spring 27 can be seated on the valve seat 26.
The hydraulic pressure control plunger 23 moves to the left and the valve seat 2
When the poppet valve 25 is seated at 6, the supply of the rear hydraulic pressure P2 is set, and thereafter, the internal flow path 24 by the reciprocating movement of the hydraulic pressure control plunger 23 according to the increase of the master hydraulic pressure P1.
By repeatedly opening and closing, the rear hydraulic pressure P2 is reduced at a predetermined reducing ratio.

Reference numeral 28 is a liquid inlet into which the master hydraulic pressure P1 from the master cylinder is introduced, and the liquid inlet 28 communicates with the internal flow path 24 of the hydraulic pressure control plunger 23. Further, 29 is a liquid outlet for supplying the rear hydraulic pressure P2 to the rear wheel cylinder, and the liquid outlet 29 communicates with the internal flow path 24 of the hydraulic pressure control plunger 23. A piston accommodating hole 30 and a spring accommodating chamber 31 are formed in the valve body 21, an actuator piston 32 is slidably accommodated in the piston accommodating hole 30, and a proportioning spring 33 and a dummy spring are contained in the spring accommodating chamber 31. 34 are stored respectively. The proportioning spring 33 includes a spring receiving member 35 fixed to the actuator piston 32 and a hydraulic pressure control plunger 2.
The dummy spring 34 is provided between the spring receiving member 35 and the inner wall 37 of the valve body 21. The proportioning spring 33 is provided to set the split point.

Reference numeral 38 denotes a hydraulic pressure chamber formed in the valve body 21, and the hydraulic pressure chamber 38 is supplied with a master hydraulic pressure P1 or a containment hydraulic pressure PG from a liquid supply passage 38A, and these master hydraulic pressure P1 or the containment hydraulic pressure P1 is contained. The hydraulic pressure PG acts on the actuator piston 32, and the actuator piston 32
Stroke to the right. That is, the actuator piston 32 strokes rightward by the master hydraulic pressure P1 and stops the stroke at that time by the containment hydraulic pressure PG. The opening of the hydraulic chamber 38 is closed by a stop valve 39.

Here, 40 is a liquid passage formed in the valve body 21, and the liquid passage 40 communicates with the liquid inlet 28 via the plunger accommodating hole 22. Also, the valve body 21
A chamber 41 communicating with the liquid passage 40 is formed therein. 42 is a valve seat provided in the chamber 41, and the valve seat 42 has an inlet hole 43 communicating with the chamber 41.
Are formed.

Reference numeral 44 denotes a holding member that fits into the valve seat 42 and holds the valve seat 42. The holding member 44 is supported by a support member 45 fitted into the valve body 21. Support member 4
5 and O-ring 4 to prevent liquid leakage between the valve body 21
6 is interposed. Support member 45 and holding member 44
A liquid supply passage 38A is formed therein, and the liquid supply passage 38A communicates with the chamber 41 via the inlet hole 43 of the valve seat 42.

The chamber 41 and the liquid passage 40 constitute a passage 47 through which the master hydraulic pressure P1 sent from the master cylinder flows. A sensor device 52 including an inertia valve 48, an inertia valve box 49, a push rod 50, and a return spring 51 is provided in the chamber 41 substantially in parallel with the passage 47. Therefore, the inertia valve 48
Is surrounded on all sides by an inertial valve box 49 and a chamber 41
Are isolated from each other, and are not directly affected by the hydraulic force of the master hydraulic pressure P1 sent from the master cylinder.

An inertia valve chamber 53 is formed in the inertia valve box 49, and an inertia valve 48 made of a steel ball is rotatably accommodated in the inertia valve chamber 53. An opening 54 is formed in the inertia valve box 49, and the opening 54 is formed by the push rod 50.
Is inserted. An inertia valve box 49 around the spring receiving portion 55 and the opening portion 54 fixed to the end portion of the push rod 50.
A return spring 51 is interposed between the inner wall 56 and the inner wall 56.

The tension of the return spring 51 causes the spring receiving portion 55 of the push rod 50 to contact the inertia valve 48.
When the inertia valve 48 rolls, the push rod 50 is pushed by the inertia valve 48 to close the inlet hole 43 of the valve seat 42. The return spring 51 returns to the position before the inertia valve 48 rolls when the brake applied to the vehicle is released. Further, the return spring 51 has a function of controlling not only when the brake is released but also when the push rod 50 closes the inlet hole 43 when the brake is applied.

That is, by selecting the spring load of the return spring 51, the timing at which the push rod 50 closes the inlet hole 43 is determined in balance with the inertial force acting on the inertia valve 48. That is, if the spring force of the return spring 51 is increased, the timing of closing the inlet hole 43 is delayed,
The weaker the spring force, the faster. The space on the left and right of the inertia valve 48 in the inertia valve box 49 communicates with each other by a groove 57.

Next, the operation will be described. When the master hydraulic pressure P1 rises due to the depression of the brake pedal, the master hydraulic pressure P1 changes from the liquid inlet 28 to the hydraulic pressure control plunger 23.
The master hydraulic pressure P1 is supplied as a rear hydraulic pressure P2 to the rear wheel cylinder through the internal flow path 24 and the liquid outlet 29 of the master valve, while the master hydraulic pressure P1 is applied to the liquid passage 40, the chamber 41, the inlet hole 43 of the valve seat 42, the liquid supply passage 38 A, enters the hydraulic chamber 38, and acts on the actuator piston 32. Therefore, the actuator piston 32 receives the master hydraulic pressure P1 and starts a stroke to the right as the master hydraulic pressure P1 increases.

When the set deceleration, which is determined by the mounting inclination angle of the valve body 21 with respect to the vehicle horizontal axis XX, is reached in the control state by the increase of the master hydraulic pressure P1, the inertia valve 48 senses the set deceleration and The push rod 50 is pressed by rolling by a distance L in the direction indicated by the arrow B in FIG. 2 by inertial force. The push rod 50 is pushed by the inertia valve 48 and travels against the return spring 51 until it abuts against the inlet hole 43 of the valve seat 42 to close the inlet hole 43.

When the inlet hole 43 is closed, the liquid supply passage 38A to the actuator piston 32 is cut off, and the master hydraulic pressure P1 acting on the left side of the actuator piston 32 is contained. Therefore, the actuator piston 32 stops at a stroke corresponding to the containment hydraulic pressure PG, and the spring load due to the compression of the proportioning spring 33 at that stroke is applied to the hydraulic pressure control plunger 23 to detect the set deceleration. The split point is set based on the containment hydraulic pressure PG of.

When the master hydraulic pressure P1 exceeds the split point, the hydraulic pressure control plunger 23 moves to the left as the master hydraulic pressure P1 increases, the valve seat 26 hits the poppet valve 25, and the rear hydraulic pressure is increased. The supply of the pressure P2 is set, and thereafter, the opening and closing of the internal flow path 24 is repeated by the reciprocating movement of the hydraulic pressure control plunger 23 according to the increase of the master hydraulic pressure P1, and then the rear hydraulic pressure P2 is reduced to a predetermined reducing ratio. Depressurize with.

In the conventional example, the inertia valve 48 has a passage 47 for the master hydraulic pressure P1 sent from the master cylinder.
Since they exist in series, the fluid flow force receives an uncertain force, and the timing of closing the inlet hole 43 of the valve seat 42 varies, resulting in an uncertain variation in the containment hydraulic pressure PG. And the rear hydraulic pressure P2 also fluctuated, but in the present embodiment, in order to eliminate the influence of uncertainties due to the hydraulic force, the master hydraulic pressure P1 is eliminated.
A sensor device 52 having an inertial valve 48 built therein is provided in parallel with a passage 47 through which air flows, and the timing of closing the inlet hole 43 with the push rod 50 is controlled by adjusting the load of the return spring 51. It is possible to prevent variations in the hydraulic pressure PG. As a result, it is possible to prevent variation in the rear hydraulic pressure P2 and obtain a stable braking force.

Next, FIG. 3 is a cross-sectional view of an essential part showing another embodiment of the present invention. In this embodiment, the timing at which the push rod 50 closes the inlet hole 43 is additionally controlled. In FIG. 3, reference numeral 58 denotes an extension passage communicating with the chamber 41.
8 extends along the side wall 59 of the inertia valve box 49 opposite the push rod 50. An orifice 60 is formed on the side wall 59. Therefore, the chamber 41 communicates with the inertia valve chamber 53 via the extension passage 58 and the orifice 60.

A small amount of the liquid from the master cylinder sent to the chamber 41 is applied from behind the inertia valve 48 via the extension passage 58 and the orifice 60 to promote the rolling of the inertia valve 48, The timing at which the push rod 50 closes the inlet hole 43 can be changed. Orifice 60 for timing control
This is done by adjusting the orifice diameter of.

Also in this embodiment, the same effect as that of the above embodiment can be obtained.

[0031]

As described above, according to the present invention, a sensor device having an inertia valve incorporated therein is provided in parallel with the passage of the liquid sent from the master cylinder, and the inertia valve causes the liquid flow. Since the timing of closing the inlet hole is controlled by the push rod by adjusting the return spring while avoiding the influence of force, it is possible to prevent the containment hydraulic pressure PG from fluctuating. It is possible to prevent the rear hydraulic pressure P2 from fluctuating and obtain a stable braking force.

[Brief description of drawings]

FIG. 1 is an overall sectional view showing an embodiment of the present invention.

FIG. 2 is a cross-sectional view of an essential part showing an embodiment of the present invention.

FIG. 3 is a cross-sectional view of essential parts showing another embodiment of the present invention.

FIG. 4 is an overall sectional view showing a conventional example.

FIG. 5 is a sectional view of a main part showing a conventional example.

[Explanation of symbols]

21: Valve body 22: Plunger storage hole 23: Hydraulic pressure control plunger 24: Internal flow path 25: Poppet valve 26: Seat 27: Return spring 28: Liquid inlet 29: Liquid outlet 30: Piston housing hole 31: Spring storage room 32: Actuator piston 33: Proportioning spring 34: Dummy spring 35: Spring receiving member 36: Retainer 37: Inner wall 38: hydraulic chamber 38A: Liquid supply passage 39: Shut-off valve 40: Liquid passage 41: Chamber 42: valve seat 43: Inlet hole 44: Holding member 45: Support member 46: O-ring 47: Passage 48: Inertial valve 49: Inertial valve box 50: Push rod 51: Return spring 52: Sensor device 53: Inertial valve chamber 54: opening 55: Spring receiving part 56: Inner wall 57: groove 58: Extension passage 59: Side wall 60: Orifice

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Claims (3)

(57) [Claims] 1. A load-responsive type in which a master hydraulic pressure is confined in an actuator piston communicating with the inlet hole by closing an inlet hole opening in a passage for a liquid sent from a master cylinder by operating an inertia valve which is aware of a set deceleration. A fluid pressure control valve is provided with a sensor device for accommodating the inertial valve in parallel with the flow path and closing the inlet hole so that the inertial valve is not affected by the fluid flow force of the liquid sent to the inertial valve. The sensor device includes an inertia valve, an inertia valve box, and the inertia valve.
A push lock that is pushed by the rolling of the valve and closes the inlet hole.
And a return spring that returns the push rod.
The timing of closing the inlet hole by setting the load of the return spring
Control push button and push rod
Is a load-responsive hydraulic control valve, which is loosely inserted in the inertia valve box . 2. The inertial valve box is provided with an orifice for applying a fluid flow force to the inertial valve from a side opposite to the pushrod side, and the sensor apparatus is connected to the orifice and communicates with the orifice. provided extending passage communicating the passage to the outside, the load responsive fluid control valve according to claim 1, characterized in that to control the timing for closing the inlet hole. 3. The load-responsive hydraulic control valve according to claim 2 , wherein the orifice diameter of the orifice is changed to control the timing of closing the inlet hole.