JPH0861554A - Pressure control valve - Google Patents

Abstract

PURPOSE: To provide a pressure control valve which can prevent generation of noises and breakage and/or degradation likely to occur when the valve element is opened. CONSTITUTION: A pressure control valve is equipped with a mounting body 2 having a supply port 3 and exhaust port 4, a valve body 5 which has a seat part 21 formed between the supply port and exhaust port 4 and is mounted on the mounting body 2, a valve element 32 to be seated on the seat part 21, and a spring which is set as stretching between the body 5 of the valve and the seat part 21 and energizes the valve element 32 always to the seat part 21, wherein the arrangement further includes a pressing means 40 to press part of the valve element 32 to the seat part 21 when the valve is opened.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to noise prevention of a pressure control valve for controlling hydraulic pressure.

[0002]

2. Description of the Related Art A conventional pressure control valve has
Some are disclosed in Japanese Patent No. 64584. This type of pressure control valve is a valve body that shuts off the low pressure port and the high pressure port, a plug that is fitted in the valve body, and a spring that is stretched in the plug so that it is seated on the seat portion. Composed of pilot poppets.

In this pressure control valve, for example, when the working fluid in the high pressure port becomes a predetermined pressure or higher, the pilot poppet is separated from the seat portion by the working fluid in the high pressure port, and the working fluid is discharged from the high pressure port. Is discharged to the low pressure port side, the high pressure port and the low pressure port are communicated with each other, and the working fluid is caused to flow into the low pressure port, thereby preventing damage to the piping or the like on the high pressure port side. When the pressure of the high pressure port is lower than that of the low pressure port, the pressure control valve connects the high pressure port and the low pressure port to prevent the generation of bubbles and the like due to negative pressure on the high pressure port side.

Further, the conventional pressure control valve has a structure shown in FIG.
As shown in FIG. 5, a valve body 600, a connection member 301 that is connected to the high pressure port P while blocking the high pressure port P and the low pressure port T, a piston 603 that is seated on a valve seat 602 of the connection member 601, and a valve The plug 604 screwed to the main body 600, the poppet 607 that is seated on the seat portion 606 by being biased by the valve spring 605 stretched in the plug 604, and the poppet 607 that engages with the poppet 607 and And a shaft-shaped pusher 608 which receives the pressure of the working fluid.

Also in this pressure control valve, similar to the one described above (Japanese Utility Model Laid-Open No. 5-64584), for example, when the working fluid in the high pressure port P becomes a predetermined pressure or more, the high pressure port P Working fluid of poppet 6
07 is separated from the seat portion 606 to open the valve, and the urging force of the piston 603 in the shutoff direction is reduced, so that the piston 603 is connected to the connecting member 601.
Of the high pressure port P by opening the valve away from the valve seat 602 of
And the low pressure port T are communicated with each other.
In order to improve responsiveness when the valve 3 is separated from the valve seat 602 at the time of opening the valve, the poppet 607 receives pressure from the high pressure port P side.
A pusher 608 for pressing is provided.

[0006]

However, in the conventional pressure control valve (Japanese Utility Model Laid-Open No. 5-64584),
When the pulsation of a pressure pump that supplies hydraulic fluid to the high-pressure port is transmitted to the pilot poppet, the spring that biases the pilot poppet resonates with this pulsation, causing the pilot poppet to vibrate or move axially. Rocks in a direction perpendicular to. Then, due to the vibration and the like, the pilot poppet and the seat portion repeatedly collide with each other to generate noise, and the collision causes the pilot poppet and the seat portion to be damaged and deteriorated.

Also, in the conventional pressure control valve shown in FIG. 15, the poppet vibrated in the axial direction due to the pulsation of the pressure pump or the like repeatedly collides with the pusher due to this vibration and causes noise. was there.

The present invention has been made to solve such a problem, and an object of the present invention is to provide a pressure control valve capable of preventing generation of noise and deterioration of damage when the valve body is opened. And

[0009]

In order to solve the above problems, the pressure control valve of the present invention has, in claim 1, a supply port connected to the high pressure side and a discharge port connected to the low pressure side. A mounting body, a valve body having a seat portion formed between the supply port and the discharge port and mounted to the mounting body, a valve body seated on the seat portion, the valve body and the seat portion. A spring that is stretched between the springs and constantly biases the valve element toward the seat portion, and when a working fluid having a predetermined pressure or higher is applied to the supply port, the valve element is resisted against the spring force of the spring. In the pressure control valve which is separated from the seat portion and opens, a pressing means for pressing a part of the valve body against the seat portion when the valve is opened is provided.

According to a second aspect of the present invention, the pressing means is a spring seat provided between the spring and the valve body, and a surface for supporting the spring is inclined.

According to another aspect of the present invention, the pressing means forms the valve body asymmetrically, and the working fluid passing between the valve body and the seat portion when the valve is opened causes one of the valve body to move. The part is pressed against the seat part.

According to a fourth aspect of the present invention, the pressing means is configured to press a part of the valve body against the seat portion by shifting the axial center of the seat portion from the axial center of the valve body. Is.

According to a fifth aspect of the present invention, the spring seat is formed with a mountain-shaped portion protruding from a surface supporting the spring and having a height in the center, and a lower portion having a predetermined step from the apex of the mountain-shaped portion. The spring is supported by the apex of the mountain and the lower portion.

According to the present invention, a spring seat is provided between the spring and the valve body, and a spherical or hemispherical member is arranged between the spring seat and the valve body.

According to another aspect of the present invention, there is provided a mounting body having a supply port connected to the high pressure side and a discharge port connected to the low pressure side, and a seat portion formed between the supply port and the discharge port. A valve body having the valve body mounted on the mounting body; a valve body seated on the seat portion; a spring stretched between the valve body and the seat portion to constantly urge the valve body toward the seat portion; A pusher that engages with the body and receives the pressure of the working fluid from the supply port, and when a pressure equal to or higher than a predetermined pressure is applied to the supply port, the pusher resists the spring force of the spring. In a pressure control valve that opens the valve body by separating from the seat portion, at least one of the pusher and the valve body is formed of a damping material.

In the eighth aspect, the damping material is stainless steel.

[0017]

According to the pressure control valve of the first aspect of the invention as described above, in the first to fourth aspects, when the valve is opened, the valve body is not completely separated from the seat portion, and Since a part of the valve is separated from the seat in a state where a predetermined frictional resistance with the seat is generated, even if the pulsation of the oil pump or the like is transmitted through the supply port, the pulsation causes the valve element itself. It is possible to prevent the rocking of the valve body and prevent the valve body and the seat portion from colliding with each other. Therefore, it is possible to prevent noise due to the collision of the valve body and the seat portion, and to prevent the valve body and the seat portion from colliding with each other. It is also possible to prevent damage and deterioration of the.

Further, according to the pressure control valve of the first aspect of the present invention, in claim 5 and claim 6, the spring can be oscillated by the spring seat, so that the valve body and the opening circumference of the seat portion are provided. Since the frictional resistance of the contact surface between the valve body and the seat can be made small, the pressure difference (hiss) applied to the valve body when the valve is opened and closed can be made small. You can

Further, according to the pressure control valve of the second aspect of the present invention, since the pusher and the valve body, or one of them is made of the vibration damping material (stainless steel), the oil pump is opened when the valve is opened. Even if the pulsation of (1) is transmitted through the supply port and the pulsation causes the valve element itself to swing and collide with the valve element and the pusher, noise can be reduced.

[0020]

【Example】

First Embodiment Hereinafter, a pressure control valve that is a first embodiment of the present invention will be described with reference to the drawings.

FIG. 1 is a longitudinal sectional view showing a pressure control valve according to the first embodiment, FIG. 2A is a plan view showing a structure of a valve spring seat according to the first embodiment, and FIG. 2 is a view showing the structure of the valve spring seat in FIG.
Is an enlarged view of a main part showing the distribution of the pressing force of the valve spring applied to the valve body, FIG. 4 (a) is an enlarged view of the main part for explaining the operation of the valve body when the valve is open, and FIG. 4 (b) is an open view. It is a BB sectional view of Drawing 4 (a) for explaining operation of a valve element at the time of valve.

In FIG. 1, reference numeral 1 is a pressure control valve disposed in the mounting body 2, and 2 is a mounting body.
A supply port 3 which is open to the upper surface 2A and is connected to the high pressure side and a discharge port 4 which is orthogonal to the supply port 3 and is connected to the low pressure side are formed.

Reference numeral 5 denotes a valve body of the pressure control valve 1,
It is screwed into the supply port 3 via a seal ring 6,
The supply port 3 and the discharge port 4 are attached to the attachment body 2 in a closed state. Further, inside the bubble body 5, piston holes 7 are formed so as to penetrate both ends in the axial direction.

This piston hole 7 has a screw diameter hole portion 7A, a large diameter hole portion 7B, a medium diameter hole portion 7C, and a small diameter hole portion which are opened in the supply port 4, the diameter gradually decreasing from the upper opening toward the lower opening. 7D is a stepped hole that is continuous, and this medium diameter hole portion 7
C communicates with the discharge port 4 through the through hole 8.
Further, in the piston hole 7, the first piston 9 is arranged so as to reach the large-diameter hole portion 7B and the medium-diameter hole portion 7C and to leave a predetermined gap a between the inner peripheral surfaces thereof. .

The first piston 9 includes a small diameter portion 9A slidably fitted in the medium diameter hole portion 7C of the piston hole 7 and a large diameter portion extending from the small diameter portion 9A into the large diameter hole portion 7B. 9B and a small diameter portion 9A.
The tip of the valve seats on the first valve seat 10 formed in the small diameter hole portion 7D of the valve body 5 to form the first valve A.

Further, inside the first piston 9, the diameter of the piston hole 7 is gradually reduced from the large diameter hole portion 7B side toward the supply port 3 side, and the large diameter hole 11A, the medium diameter hole 11B and the small diameter hole are formed. A cylinder hole 11 continuous with 11C is formed,
The medium diameter hole 11B communicates with the through hole 8 through the through hole 12. A second piston 14 is slidably fitted in the medium-diameter hole 11B of the piston hole 7 via a seal ring 13.

The second piston 14 has a main body 14A.
The second end whose tip is formed in the small diameter hole 11C of the first piston 9
The second piston and the second valve seat 15 are seated on the valve seat 15.
The second valve B is constituted by
A shaft portion 14B that is reduced in diameter from A and extends into the large diameter hole 11A of the first piston 9 is integrally formed.

Inside the second piston 14, the first piston 14
A communication hole 16 opening in the large diameter hole 11A of the piston 9 and a throttle hole 17 opening in the supply port 3 are continuously formed, and the large diameter hole 11A and the supply port 3 are communicated with each other.

On the upper surface 5A of the valve body 5,
The block body 20 is screwed by screwing the screw shaft portion 20A into the screw diameter portion 7A.
At 0, a seat portion 21 that is reduced in diameter from the screw shaft portion 20A and extends into the large diameter hole 11A of the first piston 9 is integrally formed. The seat portion 21 is slidably fitted in the large diameter hole 11A via a seal ring 22, and a hydraulic chamber b is formed between the seat portion 21 and the inner peripheral surface of the large diameter hole portion 7A of the valve body 5. Is forming.

A hydraulic chamber c is defined between the seat portion 21 and the second piston 14, and the spring force of a spring 23 stretched in the hydraulic chamber c causes the second piston 1 to move.
4 is urged toward the supply port 4 side and is pressed against and engaged with the second valve seat 15.

The block body 20 has a screw hole portion 24 whose diameter gradually decreases from the upper end toward the supply port 4 side.
A, a stepped hole 24 in which the intermediate hole portion 24B and the poppet hole portion 24C are continuous is formed, and the screw hole 24A includes
The screw member 25 is screwed on.

The screw member 25 has a poppet hole portion 24.
A recess 26 that is coaxial with C and opens to the intermediate hole 24B is formed, and the recess 26 and the intermediate hole 24B of the block body 20 define the back pressure chamber d. Further, the poppet hole portion 24C is communicated with the hydraulic chamber b by the lateral hole 27 and the communication passage 28 formed in the seat portion 21.
Is communicated with the large diameter hole 11A of the first piston 9. The communication passage 28 is a stepped hole in which a communication hole 28A coaxial with the poppet hole portion 24C and the diameter of which gradually decreases from the poppet hole portion 24C toward the large diameter hole 11A and a throttle hole 28B are continuous.

Then, in the back pressure chamber d in the stepped hole 24,
A poppet 30, a valve spring 35, and a valve spring seat 40 are arranged.

The poppet 30 is integrally formed with a conical valve body 32 whose diameter is reduced from the main body 31. The valve body 32 is fitted in the communication hole 28A of the seal portion 21 and the seal portion 21 is formed. The valve body 32 and the third valve seat 33 form a third valve C by being seated on the third valve seat 33. In addition, the main body 31 of the poppet 30 has a valve body 32
A shaft portion 34 is formed so as to extend from the main body 31 on the side opposite to the side where is projected.

One end 35A of the valve spring 35 is externally fitted to the shaft 34 of the poppet 30 and press-engages with the upper surface of the main body 31, while the other end 35B is screwed with the screw member 2.
5 is in pressure engagement with a valve spring seat 40 fitted in the recess 26.

This valve spring seat 40 is shown in FIGS.
As shown in FIG. 5, an annular base portion 41 and a support portion 42 having an inclined surface 42A extending at a predetermined angle θ1 from the outer peripheral edge of one flat surface 41A of the base portion 41 are integrally formed. The valve spring seat 40 is fitted into the recess 26 from the base portion 36 side with the holding member 43 interposed between the valve spring seat 40 and the screw member 25, and the other end of the valve spring 35 is formed at the inclined surface 42A. The portion 35B is received and urged to engage and abut the holding member 43.

As a result, the valve spring 35 is moved to the valve spring seat 40.
Since the support portion 42 is stretched between the valve spring seat 40 and the poppet 30 in a state of being contracted from the low position 42b on the high position 42a side, the valve body 32 has the valve spring 35 in the low position 42a.
With a small pressing force on the b side, the valve spring 35
The third valve seat 3 of the seat portion 21 has a large pressing force on the a side.
3 is pressed and engaged. That is, poppet 3
As shown in FIG. 3, the valve body 32 of 0 has a pressure distribution of a portion 32a that receives a small pressing force Fs and a portion 32b that receives a large pressing force Fh in the circumferential direction, and the third valve seat of the seat portion 21 has a pressure distribution. You will be seated at 33.

Numerals 50 and 51 are tightening members screwed to the outer periphery of the screw member 25.

The pressure control valve of the first embodiment is constructed as described above. Next, the operation of the pressure control valve of the first embodiment will be described with reference to FIGS. 1 and 4 (a)-(b). Explain.

A working fluid of a predetermined pressure is supplied to the supply port 3 from a hydraulic pump or the like (not shown), and the working fluid is passed through the throttle hole 17-communication hole 18 of the second piston 14 into the hydraulic chamber c. It is filled, and the first valve A, the second
The valve B and the third valve C are closed, respectively, and the supply port 3 and the discharge port 4 are shut off.

(1) When the working fluid applied to the supply port 3 reaches a predetermined pressure or more, the working fluid is hydraulically pressured through the small-diameter hole portion 7D of the valve body 5, the throttle hole 17 of the second piston 14, and the communication hole 16. It flows into the chamber c and acts on the valve element 32 of the poppet 31 through the communication passage 28 of the seat member 21.

(2) Then, with this working fluid, as shown in FIG.
As shown in (a), the poppet 30 has a valve spring 35 in the vicinity of a portion 32a of the valve body 32 that receives a small pressing force.
The portion 35 that receives a large pressing force against the pressing force Fs of
While forming a contact surface S (with the vicinity of the portion 35b receiving a large pressing force as a fulcrum) in the vicinity of b and the third valve seat 33,
The valve body 3 is tilted toward the back pressure chamber c side until the pressure of the working fluid and the pressing force Fs of the valve spring 35 are balanced, and the valve body 3
A part of 2 is separated from the third valve seat of the seat portion 21 and opens.

At this time, as shown in FIG. 4 (a), the valve body 32 is pushed from the horizontal component force fh to the pushing force Fs of the pushing force Fh of the valve spring 35 which is tilted following the tilt of the poppet 30. 4b, the pressure Fa of the working fluid flowing from the radial direction of the opening of the third valve C into the back pressure chamber c is received while receiving the component force fp obtained by subtracting the horizontal component force fs.
Therefore, the frictional force Fm of the contact surface S between the valve body 32 and the third valve seat 33 increases due to the resultant force. Based on this contact surface S, the poppet 30 moves up and down by increasing or decreasing the inclination and sliding on the contact surface S according to the pressure of the working fluid.

(3) When a part of the valve element 32 is separated from the third valve seat 33 of the seat portion 21 and the third valve C is opened, the working fluid flows into the back pressure chamber c through this opening. At the same time, the gas flows from the lateral hole 27 into the discharge port 4 through the hydraulic chamber b, the gap a, the through hole 8 of the valve body 5.

(4) Then, the working fluid in the hydraulic chamber c flows out to the discharge port 4 side through the communication passage 28, and the pressure in the hydraulic chamber c decreases, so that the throttle hole of the second piston 14 is reduced. Due to 17, a pressure difference is generated between the hydraulic chamber c side of the second valve B and the supply port 3 side (the supply port 3 side has a large pressure), and the second piston 14 resists the spring force of the spring 23. It moves to the poppet 30 side, separates from the second valve seat 15, and opens the second valve B.

As a result, the discharge port 4 and the supply port 3 communicate with each other through the through hole 8 of the valve body 5, so that the working fluid is discharged from the supply port 3 to the discharge port 4 through the second valve B. The pressure on the supply port 3 side is lowered, and when the working fluid on the supply port 3 side becomes equal to or higher than a predetermined pressure, the piping on the supply port 3 side is prevented from bursting.

(5) Next, when the pressure of the working fluid in the supply port 3 is restored to the predetermined pressure, the working fluid having the predetermined pressure is supplied from the supply port 3 to the throttle hole 17 of the second piston 14.
-While it flows into the hydraulic chamber c through the communication hole 16 and acts on the valve element 32 of the poppet 30 through the communication passage 28 of the seat portion 21, this working fluid is applied to the valve spring 3.
Since the pressing force Fs of 5 is a small pressure, the poppet 30 is moved by the pressing forces Fs and Fh of the valve spring 35 in the direction in which the inclination is eliminated, that is, toward the seat portion 21 side, and the valve body 32
Seats on the third valve seat 33 of the seat portion 21 and closes the third valve C.

As a result, the pressure on the supply port 3 side of the second piston 14 and the pressure in the hydraulic chamber c become equal, and the spring 2
Due to the spring force of 3, the second piston 14 moves to the supply port 3 side, sits on the second valve seat 15, and the second valve B closes.

(6) When the pressure in the supply port 3 becomes lower than the pressure in the discharge port 4, the step portion of the large diameter portion 9B of the first piston 9 passes through the through hole 8-the gap a of the valve body 4. Between the pressure applied to the stepped portion of the large diameter hole 11A of the first piston 9 and the pressure applied to the stepped portion (first
The large diameter portion 9B of the piston 9 has a large pressure. ) Occurs.

As a result, the first piston 9 moves to the poppet 30 side together with the second piston 4, and the first piston 9 separates from the first valve seat 10 to open the first valve A. As a result, the working fluid on the discharge port side flows back to the supply port through the first valve, and the supply port 3 side becomes a negative pressure to prevent the generation of bubbles.

As described above, according to the pressure control valve of the first embodiment, the valve body 32 of the poppet 30 has the portion 32a that receives a small pressing force Fs and the portion 32b that receives a large pressing force Fh in the circumferential direction. When the third valve C is seated on the third valve seat 33 of the seat portion 21 with a pressure distribution and the third valve C is opened, the valve body 32 of the poppet 30 is completely closed.
3, the valve body 32 is pressed against the third valve seat 33 without being separated from the seat 3, and the pressing force by the component force of the valve spring 35 acts on the seat surface on the side of the small pressing force Fh of the valve spring 35, so that the valve body Since a part of the valve 32 is separated from the valve third valve seat 33, even if a pulsation of a hydraulic pump or the like (not shown) is transmitted to the pressure control valve 1 via the supply port 3, the pulsation causes the poppet 30 itself. Rocking can be prevented, and poppet 30
Does not collide with the seat portion 21, and noise due to the collision between the valve body 32 of the poppet 30 and the seat portion 21 can be prevented. Further, damage and deterioration of the valve body 32 and the seat portion 21 due to this collision can be prevented.

Second Embodiment A pressure control valve according to a second embodiment of the present invention will be described below with reference to the drawings.

FIG. 5 is a longitudinal sectional view showing a pressure control valve in the second embodiment, FIG. 6 (a) is a plan view showing the structure of a valve spring seat in the second embodiment, and FIG. 6 (b) is the present embodiment. 6 is a view of the valve spring seat in FIG.
7C is a DD arrow view of FIG. 7A showing the structure of the valve spring seat in the second embodiment, and FIG. 7A is an enlarged view of a main part for explaining the operation of the valve spring when the valve is open. 7 (b) is an enlarged view of a main part for explaining the operation of the valve element when the valve is opened.

In the second embodiment, a modification of the valve spring seat of the first embodiment is shown. In FIG. 5, the same reference numerals as those in FIG. 1 have the same structure, and therefore detailed description thereof will be omitted. To do.

In FIG. 5, the compression control valve 1 of the second embodiment
In the same manner as in the first embodiment, the valve spring seat 140 is fitted in the recess 26 of the screw member 25, and the other end 35B of the valve spring 35 is press-engaged.

This valve spring seat 140 is shown in FIG.
As shown in (c), an annular base portion 141 and an outer periphery of the base portion 140 form a predetermined angle θ with respect to a plane 141A of the base portion 141, and the height gradually increases toward the center. The two inclined surfaces 142A, 142A have a mountain-shaped portion 142 having a triangular cross section that intersects with the center line of the base portion 141 and has a line of intersection 142B, and a predetermined step (intersection) with the line of intersection 142B of the mountain-shaped portion 142. A plane portion 143 having a position lower than the line 142B and cut in a direction parallel to the intersection line 142B is formed.

The valve spring seat 140 is provided on the base 1
It is fitted into the recess 26 of the screw member 25 from the 41 side, and the other end portion 35B of the valve spring 35 is connected to the intersection line 142B and the flat surface portion 1.
43 and support. As a result, the valve spring 35 extends in the flat portion 143 side of the valve spring seat 140 in the state of intersection 1
The valve spring seat 140 and the poppet 3 in the state of contracting on the side of 42B.
Since it will be stretched between 0, the valve body 32 is the valve spring 3
5 has a small pressing force Fs on the extending side 32b, and a large pressing force Fh on the contracting side 32a of the valve spring 35, and is pressed and engaged with the third valve seat 33 of the seat portion 21.

The pressure control valve of the second embodiment is configured as described above. Next, the operation of the pressure control valve of the first embodiment will be described with reference to FIGS. 1 and 7 (a)-(b). Explain.

Since the operation of the pressure control valve of the second embodiment is basically the same as the procedure described in (1) to (6) of the first embodiment, an operation different from that of the first embodiment is performed. I will explain mainly.

When the working fluid applied to the supply port 3 reaches a predetermined pressure or higher, the poppet 30 has the valve element 32 and the third valve seat 33 as in (1) and (2) of the first embodiment.
While forming the contact surface S with the valve spring 35, the valve spring 35 is tilted toward the back pressure chamber c side, and a part of the valve element 32 is separated from the third valve seat of the seat portion 21 and opens, and the valve spring 35 is opened. The frictional resistance Fn of the contact surface S is generated in response to the component force fp and the pressure Fa of the working fluid flowing in the back pressure chamber c.

At this time, the other end portion 35B side of the valve spring 35 is, as shown in FIG. 7A, a mountain-shaped portion 1 of the valve spring seat 140.
Since it is swingable (inclinable) in the left-right direction with the intersection line 142B of 42 as a boundary, when the pressure of the working fluid received by the valve element 32 and its direction are transmitted to the valve spring 35, According to this pressure and its direction, the valve spring 35 freely swings with the line of intersection 142B of the valve spring seat 140 as a boundary.

When the valve spring 35 swings, the pressing forces Fs and Fh of the valve spring 35 transmitted to the poppet 30 are also
Since it changes according to the swing of the valve spring 35,
As shown in FIG. 7B, the valve body 32 of the poppet 30 rolls and moves in the circumferential direction of the opening of the third valve C, and the pressure Fa of the working fluid and the component force fp are as described above. Example 1
Since it works in a different direction from, the resultant force is due to the contact surface S
The frictional resistance Fn is smaller than the frictional resistance Fm of the first embodiment.

In such a state, the poppet 30
Is operated by the pressure of the working fluid from the communication passage 28 side.
While 2 rolls on the circumference of the opening, it moves to the back pressure chamber d side until the pressure of this working fluid and the frictional resistance Fn at the contact surface S between the valve body 32 and the third valve seat 33 are balanced. .

When a part of the valve element 32 is separated from the third valve seat 33 of the seat portion 21 and the third valve C is opened, the procedure described in (3) to (6) of the first embodiment. According to the above, the supply port 3 and the discharge port 4 are communicated with each other to prevent the piping and the like from bursting when the working fluid on the supply port 3 side has reached a predetermined pressure or higher, and the supply port 3 is set to a negative pressure. It is possible to prevent the formation of bubbles.

As described above, also in the pressure control valve of the second embodiment, as in the first embodiment, the valve body 32 of the poppet 30 is not completely separated from the third valve seat 33, and the valve body 32 is opened. While pressing the third valve seat 33, the pressing force by the component force of the valve spring 35 acts on the seat surface of the valve spring 35 on the side of the small pressing force Fh, and a part of the valve body 32 is separated from the valve third valve seat 33. Since it sits down, even if the pulsation of a hydraulic pump or the like (not shown) is transmitted to the pressure control valve 1 via the supply port 3, it is possible to prevent the poppet 30 itself from swinging due to this pulsation, and the poppet 30 is seated. It is possible to prevent noise due to the collision between the valve body 32 of the poppet 30 and the seat portion 21 without colliding with the portion 21. Further, damage and deterioration of the valve body 32 and the seat portion 21 due to this collision can be prevented.

Further, in the pressure control valve 1 according to the second embodiment, the valve body 32 of the poppet 30 is movable on the opening circumference of the third valve C by the action of the valve spring seat 140 so that the valve body 32 and the third valve C can be moved.
Since the frictional resistance Fn of the contact surface S with the valve seat 33 can be made smaller than the frictional resistance Fm of the first embodiment, the pressure difference (his) between when the third valve C is opened and when it is closed is reduced. it can.

Third Embodiment A pressure control valve according to a third embodiment of the present invention will be described below with reference to the drawings.

FIG. 8 is a longitudinal sectional view showing a pressure control valve in the third embodiment, and FIG. 9 (a) is an enlarged view of a main part for explaining the working fluid acting on the valve body of the fourth embodiment when the valve is opened. , Fig. 9
10B is an enlarged view of a main part for explaining the operation of the valve body of the fourth embodiment when the valve is opened, and FIG. 10 is an enlarged view of the main part for explaining the operation of the valve spring of the fourth embodiment.

The third embodiment shows a modification of the valve element 32 and the valve spring seat 40 of the poppet 30 in the first embodiment. In FIG. 8, the same symbols as those in FIG. 1 of the first embodiment are the same. Since it has the above-mentioned configuration, its detailed description is omitted.

In FIG. 8, the compression control valve 1 of the third embodiment
In the same manner as in the first embodiment, the valve spring seat 240 is fitted in the recess 26 of the screw member 25, and the other end portion 35B of the valve spring 35 is press-engaged.

The valve spring seat 240 has a circular plate portion 240A for supporting the other end portion 35B of the valve spring 35, and the plate portion 240A has a shaft portion 240 protruding toward the poppet 30.
B and a hemispherical swinging portion 240C protruding toward the support member 43 side
(It may be a spherical shape) is integrally formed and is urged by the spring force of the valve spring 35 so that the oscillating portion 240.
The peripheral surface of C is in abutting engagement.

Further, the valve body 232 of the poppet 230 is
A hollow portion 232 in which a part of this conical peripheral surface is cut
A is provided and formed asymmetrically.

Thus, the pressure control valve of the third embodiment is
Although configured as described above, the operation of the pressure control valve of the third embodiment will now be described with reference to FIGS. 8, 9A, and 9B.
Description will be made based on 0. Also in the third embodiment, the basic operation of the pressure control valve is the same as the above (1) to (6).
Since the operation is similar to the above, only the points different from the first embodiment will be described below.

When the working fluid applied to the supply port 3 reaches or exceeds a predetermined pressure, the working fluid passes through the throttle hole 17-communication hole 18-hydraulic pressure chamber c of the second piston 14 and the communication passage 28.
Acts on the valve body 232 of the poppet 230.

When the working fluid acts on the valve body 232, the poppet 230 is moved to the back pressure chamber side against the pressing force of the valve spring 35, and the valve body 232 is separated from the third valve seat 33 of the seat portion 21. Then, the third valve C is opened. And the working fluid is the third
It flows into the back pressure chamber c from the opening of the valve C.

At this time, the working fluid flows along the conical peripheral surface of the valve body 232 of the poppet 230, but as shown in FIG. 9A, a recess 232A of the valve body 232 is formed. On the side, the flow direction of the working fluid is changed by the recess 232A, and a reaction force Fu that presses the valve body 232 from a direction orthogonal to the axial direction of the poppet 230 is generated. As a result, the poppet 230 is moved in a direction orthogonal to the axial direction, and a portion of the valve body 232 (a portion where the recessed portion 232A is not formed) is pressed and engaged with the third valve seat 33 of the seat portion 21.

Then, a part of the valve body 232 is formed in the seat portion 2
When pressed by the first third valve seat 33, a contact surface S is formed between a part of the valve body 232 and the third valve seat 33, and as shown in FIG. The frictional force Fl of the contact surface S is generated by receiving the component force fp of the valve spring 35 and the reaction force Fu shown in FIG.

At this time, the other end side of the valve spring 35 is, as shown in FIG. 10, a hemispherical swinging portion 23 of the valve spring seat 240.
Since the reaction force Fu of the working fluid received by the valve body 232 and its direction are transmitted to the valve spring 35, the valve spring 35 can be oscillated by 2C according to the reaction force Fu and its direction. The other end portion 35B side freely swings.

When the valve spring 35 swings, the pressing forces Fs and Fh of the valve spring 35 transmitted to the poppet 230 are transmitted.
However, the reaction force Fu of the working fluid that presses the valve body 232 of the poppet 30 and the component force fp of the valve spring 35 work in different directions from each other because they also change according to the swing of the valve spring 35. The resultant force causes the valve body 232 to roll on the circumferential direction of the opening of the third valve C. That is, since the reaction force Fu of the working fluid and the component force fp of the valve spring 35 of the third embodiment act in directions different from those of the first embodiment, the frictional resistance Fl of the contact surface S due to the resultant force is It is smaller than the frictional resistance Fm of Example 1.

In such a state, the poppet 230
Is operated by the pressure of the working fluid from the communication passage 28 side.
While 32 rolls on the circumference of the opening, it moves to the back pressure chamber d side until the pressure of this working fluid and the frictional resistance Fl at the contact surface S between the valve body 232 and the third valve seat 33 are balanced. .

As described above, also in the pressure control valve of the third embodiment, the valve body 23 of the poppet 230 is the same as in the first embodiment.
2 acts so as to incline while pressing the valve body 232 against the third valve seat 33 without completely separating from the third valve seat 33, and a part of the valve body 232 is removed from the third valve seat 33. Since the seats are separated from each other, even if the pulsation of an oil pump (not shown) or the like is transmitted to the pressure control valve 1 via the supply port 3, the poppet 30 itself can be prevented from swinging due to the pulsation, and the valve body 232. Does not collide with the seat portion 21, noise due to the collision between the valve body 232 of the poppet 230 and the seat portion 21 can be prevented, and damage and deterioration of the valve body 232 and the seat portion 21 due to this collision can be prevented. You can

Further, in the pressure control valve 1 of the third embodiment, the hemispherical oscillating portion 240C of the valve spring seat 240 acts on the valve body 232 of the poppet 230 by the third valve, as in the second embodiment. The valve body 232 can be moved in the circumferential direction of the opening C.
Since the frictional resistance Fl of the contact surface S between the third valve seat 33 and the third valve seat 33 can be made small, the pressure difference (hiss) applied to the poppet 230 between when the third valve C is open and when it is closed is small. can do.

Fourth Embodiment A pressure control valve according to a fourth embodiment of the present invention will be described below with reference to the drawings.

FIG. 11 is a longitudinal sectional view showing a pressure control valve according to the fourth embodiment, and FIGS. 12 (a) and 12 (b) are enlarged views showing the operation of the valve body when the valve is opened.

The fourth embodiment shows a modification of the poppet 230 in the first embodiment, and in FIG. 11, the same reference numerals as those in FIG. 1 of the first embodiment and FIG. 8 of the third embodiment have the same configurations. Therefore, detailed description thereof will be omitted.

In FIG. 11, a poppet 330 has an asymmetrical shape in which a part of the main body 331 and the valve body 332 is cut off in the axial direction.

As described above, the pressure control valve of the fourth embodiment is
Although configured as described above, the operation of the pressure control valve of the fourth embodiment will be described next with reference to FIGS. 11 and 12A and 12B. In addition, also in the fourth embodiment, the basic operation of the pressure control valve (1) to
(6) Since it operates in the same way as described, in the following,
Differences from the first embodiment will be described.

When the working fluid supplied from the oil port or the like (not shown) to the supply port 3 reaches a predetermined pressure or higher, the working fluid is restricted to the throttle hole 17-communication hole 18 of the second piston 14.
-Poppet 330 from communication passage 28 through hydraulic chamber c
Acting on the valve body 232.

When the working fluid acts on the valve body 332, the poppet 230 is moved to the back pressure chamber d side against the pressing force of the valve spring 35, and the valve body 332 is separated from the third valve seat 33 of the seat portion 21. Then, the third valve C is opened. Then, the working fluid flows into the back pressure chamber d from the opening of the third valve C.

At this time, the working fluid flows along the conical peripheral surface of the valve body 332 of the poppet 330, but as shown in FIG. 12A, a part of the valve body 332 is cut off. On the side, since the portion receiving the pressure of the working fluid is smaller than that on the opposite side, the valve body 332 cannot maintain the balance of the pressure of the working fluid, and the poppet 330 is moved in the direction orthogonal to the axial direction. A part of the valve body 232 (a part where the poppet 330 is cut off) is pressed and engaged with the third valve seat 33 of the seat portion 21.

Then, a part of the valve body 332 is seated on the seat portion 2.
When pressed by the first valve seat 33, the contact surface S is formed between a part of the valve body 332 and the third valve seat 33, and as shown in FIG. The frictional resistance Fq of the contact surface S is generated by receiving the component force fp of the valve spring 35 and the pressure of the working fluid shown in FIG.

At this time, the other end portion 35B side of the valve spring 35 has a valve spring seat 240 on the side similar to that shown in FIG.
Thus, the valve body 332 rolls on the circumference of the opening of the third valve C because it is swingable.

In such a state, the poppet 30
Due to the pressure of the working fluid from the side of the communication passage 28, the contact surface S between the pressure of this working fluid and the valve body 232 and the third valve seat 33.
As described above, the valve body 232 moves toward the back pressure chamber side while swinging in the circumferential direction of the opening of the third valve C until the frictional resistance Fp in Eq.

As described above, also in the pressure control valve of the fourth embodiment, the valve element 33 of the poppet 330 is the same as in the first embodiment.
2 acts so as to incline while pressing the valve body 332 against the third valve seat 33 without completely separating from the third valve seat 33, and a part of the valve body 332 is separated from the third valve seat 33. Since the seat is separated, even if pulsation of an oil pump or the like (not shown) is transmitted to the pressure control valve 1 via the supply port 3, the pulsation can prevent the poppet 330 itself from swinging,
The poppet 330 does not collide with the seat portion 21,
Noise due to the collision between the valve body 332 of the poppet 330 and the seat portion 21 can be prevented, and the valve body 332 due to this collision can be prevented.
It is also possible to prevent damage and deterioration of the seat portion 21.

Further, in the pressure control valve 1 of the fourth embodiment, the hemispherical oscillating portion 240C of the valve spring seat 240 acts on the valve body 332 of the poppet 3230 to cause the third valve to operate in the same manner as in the third embodiment. The valve body 332 can be moved in the circumferential direction of the opening C.
Since the frictional resistance Fl of the contact surface S between the third valve seat 33 and the third valve seat 33 can be made small, the pressure difference (hiss) applied to the poppet 330 between when the third valve C is open and when it is closed is small. can do.

Embodiment 5 Hereinafter, a pressure control valve that is Embodiment 5 of the present invention will be described with reference to the drawings.

FIG. 13 is a vertical sectional view showing a pressure control valve according to the fifth embodiment.

The fifth embodiment shows a modification of the first embodiment. In FIG. 13, the same reference numerals as those in FIG. 1 of the first embodiment and FIG. 8 of the third embodiment have the same configuration. , Its detailed description is omitted.

In FIG. 13, the communication passage 428 of the seat portion 421 is formed such that this axis and the axis of the recess 26 of the screw member 25 are offset from each other.

Then, the poppet 30 has the communication passage 4
28, the valve element 32 is seated on the third valve seat 433 formed in the seat portion 21 to close the third valve C, and the valve spring seat 240 (similar to the third embodiment). In the first embodiment described above, the valve spring 35 is slanted and stretched between
The third valve seat 433 is press-engaged with a pressing force distribution similar to.

As described above, according to the pressure control valve of the fifth embodiment, as in the first embodiment, the poppet 30 is seated on the third valve seat 433 with a pressure distribution, so that the first embodiment is described. The same effect as can be obtained. That is, in the fifth embodiment, the valve element 32 of the poppet 30 is opened when the valve is opened.
Does not completely separate from the third valve seat 433, but acts so as to incline while pressing the valve body 32 against the third valve seat 433, and a part of the valve body 32 separates from the third valve seat 433. Since it sits down, even if a pulsation of an oil pump or the like (not shown) is transmitted to the pressure control valve 1 via the supply port 3, the pulsation can prevent the poppet 330 itself from swinging,
Noise due to the collision between the valve body 32 of the poppet 30 and the seat portion 421 can be prevented, and damage and deterioration of the valve body 32 and the seat portion 421 due to the collision can be prevented.

Further, in the pressure control valve of the fifth embodiment, the hemispherical oscillating portion 2 of the valve spring seat 240 is the same as in the third embodiment.
The action of 40C causes the valve element 32 of the poppet 30 to move to the third valve C.
Since the frictional resistance of the contact surface S between the valve body 32 and the third valve seat 433 can be made small by allowing the third valve C to move in the circumferential direction, the third valve C can be opened and closed. The pressure difference (his) applied to the poppet 30 can be reduced.

Sixth Embodiment A pressure control valve according to a sixth embodiment of the present invention will be described below with reference to the drawings.

FIG. 14 is a vertical sectional view showing a pressure control valve according to the sixth embodiment.

In FIG. 14, 501 is a mounting body 502.
Is a pressure control valve, 502 is a mounting body,
A supply port 503 that opens to the upper surface 502A and is connected to the high pressure side and a discharge port 504 that is orthogonal to the supply port 503 and that is connected to the low pressure side are formed therein.

Reference numeral 505 denotes a valve body of the pressure control valve 501, which is screwed into the supply port 503 via a seal ring 506. Further, inside the bubble body 505, piston holes 507 are formed so as to penetrate both ends in the axial direction.

The piston hole 507 has a screw diameter hole portion 507A whose diameter gradually decreases from the upper opening toward the lower opening.
It is a stepped hole in which a large diameter hole portion 507B and a small diameter hole portion 507C opening in the discharge port 504 are continuous, and reach the large diameter hole portion 507B and the small diameter hole portion 507C and the inner peripheral surface of each of them. The first piston 509 is arranged with a predetermined gap a therebetween.

This first piston 509 has a piston hole 5
Large-diameter portion 509B arranged in the large-diameter hole portion 507B of 07
And a small-diameter portion 509B extending from the large-diameter portion 509A through the small-diameter hole portion 507C of the valve body 505 are integrally formed. The tip of the small-diameter portion 509A is formed in the supply port 503. The first valve A is configured by being seated on the first valve seat 510. As a result, the supply port 503 and the discharge port 504 are shut off.

Further, inside the first piston 509, the supply port 5 is provided from the large diameter hole portion 507B side of the piston hole 507.
A cylinder hole 511 is formed in which a large-diameter hole 511A and a small-diameter hole 511B are continuously reduced in diameter toward the 03 side, and the large-diameter hole 511A communicates with the gap a by a through hole 512. . A second piston 514 is slidably fitted into the large diameter hole 511A of the cylinder hole 511 via a seal ring 513.

The second piston 514 is seated on the second valve seat 515 formed in the large diameter hole 511A of the first piston 509, and the second valve B is operated by the second piston 514 and the second valve seat 515. I am configuring.

Further, inside the second piston 514, a communication hole 516 which opens into the large diameter hole 511A of the first piston 509 and a vertical through hole 517 which opens into the supply port 503 are continuously formed. A pusher 518 is fitted in the through hole 517.

The pusher 518 is made of a vibration damping material (for example, stainless steel), and is a cylindrical portion 518A slidably fitted in the vertical through hole 517 of the second piston 514.
The shaft portion 518B protruding from the cylindrical portion 518A to the large diameter hole 511A side of the first piston 509 is integrally formed. Further, the cylindrical portion 518A is formed with a throttle hole 518C which communicates the inside with the communication hole 516.

The upper surface 505A of the valve body 505
The block body 520 is screwed on the screw shaft portion 520A by screwing the screw shaft portion 520A onto the screw diameter portion 507A.
The block body 520 is integrally formed with a seat portion 521 that is reduced in diameter from the screw shaft portion 520A and extends into the large diameter hole 511A of the first piston 509. The seat portion 521 is slidably fitted in the large-diameter hole 511A via a seal ring 522, and defines a hydraulic chamber b with the second piston 514.

The block body 520 has a screw hole portion 524A, an intermediate hole portion 524B, and a poppet hole portion 524C that gradually decrease in diameter from the upper end toward the supply port 503 side.
Is formed with a stepped hole 524, and a screw member 525 is screwed into the screw hole 524A.

The screw member 525 has a poppet hole 5
Recess 52 that is coaxial with 24C and opens into the intermediate hole 524B
6 is formed, and the recess 526 and the block body 52 are formed.
The back pressure chamber c is defined by the zero hole 524B. Further, the poppet hole portion 524C is communicated with the gap a by the lateral hole 527, and the shaft portion 518B of the pusher 518 is slidable with a predetermined gap in the communication hole 528 formed in the seat portion 521. It is stored in.

Then, in the back pressure chamber c in the stepped hole 524, a poppet 530 and a valve spring 535 made of a damping material (for example, stainless steel) are arranged.

This poppet 530 is integrally formed with a conical valve body 532 whose diameter is reduced from the main body 531.
The valve body 532 is fitted in the communication hole 528 of the seal portion 521, and is seated on the third valve seat 533 formed in the seal portion 521, so that the valve body 532 and the third valve seat 533 form a third seat. It constitutes the valve C. Further, the valve body 532 of the poppet 530 is biased by the spring force of the spring 534 stretched between the projection 518D and the step portion of the communication hole 516 to engage the shaft portion 518B of the pusher 518. Have been combined.

The valve spring 535 is stretched between the poppet 530 and the recess 526 of the screw member 525, and the spring force of the valve spring 535 causes the valve body 532 to move to the third valve seat 533.
Is urged to. A fastening member 550 is screwed to the outer periphery of the screw member 525.

The pressure control valve of the sixth embodiment is constructed as described above. Next, the operation of the pressure control valve of the sixth embodiment will be described.

The supply port 503 is supplied with a working fluid of a predetermined pressure from a hydraulic pump or the like (not shown), and the presser 5
The working fluid is filled in the hydraulic chamber b through the throttle hole 518C of 18 and the communication hole 516, and the first valve A,
The second valve B and the third valve C are closed, respectively, and the supply port 503 and the discharge port 504 are shut off.

(A) When the working fluid supplied from the hydraulic pump (not shown) or the like to the supply port 503 reaches a predetermined pressure or more, the working fluid is formed into a cylindrical shape of the small diameter hole portion 511B of the first piston 509-the pusher 518. While flowing into the portion 518A, a part of the working fluid flows from the throttle hole 518C through the hydraulic chamber b-communication hole 528 (gap between the shaft 518B of the pusher 518) and the valve body 532 of the poppet 530. Act on.

(B) Then, the tubular portion 518 of the presser 518.
The working fluid that has flowed into A causes the presser 518 to move to the spring 53.
While moving toward the poppet 530 side against the spring force of No. 4, the movement of the pusher 518 pushes the poppet 530, and the movement of the pusher 518 follows the poppet 5.
30 moves to the back pressure chamber c side against the spring force of the valve spring 535. This causes the valve body 532 of the poppet 530 to move to the third position.
The third valve C is opened away from the valve seat 533.

(C) When the valve body 532 is separated from the third valve seat 533 of the seat portion 521 and the third valve C is opened, the working fluid flows into the back pressure chamber c through this opening. At the same time, it flows into the discharge port 504 from the lateral hole 527 through the gap a.

(D) Then, as a result of the working fluid in the hydraulic chamber b flowing out to the discharge port 504 side through the communication hole 528, the pressure in the hydraulic chamber b decreases, so the presser 518 is pressed.
The pressure difference between the hydraulic chamber c and the supply port 503 side due to the restriction hole 518C (the supply port 503 side has a large pressure).
Occurs, the second piston 514 moves to the poppet 530 side, separates from the second valve seat 515, and opens the second valve B.

As a result, the discharge port 504 and the supply port 503 have a clearance a−the through hole 512 of the first piston 509.
Since the working fluid is discharged from the supply port 503 to the discharge port 504, the pressure on the supply port 503 side is reduced, and when the working fluid on the supply port 503 side becomes equal to or higher than a predetermined pressure, the supply port It is intended to prevent the 503 side piping from bursting.

(E) Next, when the pressure of the working fluid in the supply port 503 is restored to a predetermined pressure, it flows into the hydraulic chamber b through the throttle hole 518 of the pusher 518, and the communication hole of the seat portion 21. Valve body 53 of poppet 530 through 528
However, since this working fluid is smaller than the pressure of the working fluid in the back pressure chamber c, the poppet 53
0 moves to the seat portion 521 side by the spring force of the valve spring 535 and the pressure of the working fluid in the back pressure chamber c, and the valve body 532
Is seated on the third valve seat 533 of the seat portion 521, and the third valve C
And the pusher 518 is moved to the second piston 514 side against the spring force of the spring 534.

As a result, the pressure applied to the second piston 514 on the side of the supply port 503 and the pressure of the hydraulic chamber b become equal, and the second piston 514 is moved to the side of the supply port 503 by the urging of the spring 534. , The second valve B is closed.

(F) When the pressure in the supply port 503 becomes lower than the pressure in the discharge port 504, the pressure applied to the step portion of the large diameter portion 509A of the first piston 509 through the gap a and the hydraulic chamber. A pressure difference (the large-diameter portion 509A of the first piston 509 becomes a large force) is generated from the inside of b through the second piston 514 and the pressure applied to the step portion of the large-diameter hole 511A of the first piston 509. To do.

As a result, the first piston 509 moves to the poppet 530 side together with the second piston 514, and the first piston 509 separates from the first valve seat 510 to open the first valve A. As a result, the working fluid on the discharge port 504 side flows back to the supply port 503 through the first valve A, and the supply port 503 side becomes a negative pressure to prevent the generation of bubbles.

As described above, according to the pressure control valve of the sixth embodiment, since the pusher 518 and the poppet 530 are formed of the vibration damping material (stainless steel), the third valve C is opened. Then, pulsation of a hydraulic pump or the like (not shown) is transmitted to the pressure control valve 501 via the supply port 503, and the pulsation causes the poppet 530 itself to swing, and the valve body 532 of the poppet 530 and the seat portion 521. Even if and collide with each other, the sound due to the collision becomes smaller than before. As a result, noise generated when the pressure control valve operates can be reduced. Noise can be prevented.

In the sixth embodiment, the poppet 530 is used.
Although the presser 518 and the presser 518 are formed of a vibration damping material (stainless steel), the present invention is not limited to this, and either the poppet 530 or the presser 518 may be formed of the vibration damping material. Even if there is, it is possible to obtain the same effect.

[0132]

As described above, according to the pressure control valve of the first aspect of the present invention, when the valve is opened, the valve body is not completely separated from the seat portion, and a part of the valve body is located between the seat portion and the seat portion. Since the seat is separated from the seat in a state where a predetermined frictional resistance is generated, even if the pulsation of the oil pump or the like is transmitted through the supply port, the pulsation prevents the valve body itself from rocking. Therefore, noise due to the collision between the valve body and the seat portion can be prevented, and damage and deterioration of the valve body and the seat portion due to the collision can be prevented.

Further, since the spring can be swung by the spring seat, the valve body can be moved in the circumferential direction of the opening of the seat portion, and the frictional resistance of the contact surface between the valve body and the seat portion can be made small. Therefore, the pressure difference (hiss) applied to the valve body at the time of valve opening and valve closing can be made small, and the operation delay can be reduced.

Further, according to the pressure control valve of the second aspect of the present invention, since the pusher and the valve body, or one of them is formed of the vibration damping material (stainless steel), the hydraulic pump is opened when the valve is opened. Even if the pulsation such as the above is transmitted to the pressure control valve through the supply port, and the pulsation causes the valve element itself to vibrate and the valve element and the seat portion collide with each other, noise can be reduced.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing a pressure control valve according to a first embodiment of the present invention.

2A and 2B are views showing a configuration of a valve spring seat according to the first embodiment of the present invention, in which FIG. 2A is a plan view of the valve spring seat, and FIG.
FIG.

FIG. 3 is an enlarged view of an essential part showing the distribution of the pressing force of the valve spring applied to the valve body according to the first embodiment of the present invention.

FIG. 4 is a view for explaining the operation of the valve element when the valve is opened in the first embodiment of the present invention, (a) is an enlarged view of a main part,
(B) is a BB arrow line view of (a).

FIG. 5 is a vertical sectional view showing a pressure control valve according to a second embodiment of the present invention.

6A and 6B are views showing a configuration of a valve spring seat in Embodiment 2 of the present invention, where FIG. 6A is a plan view of the valve spring seat, FIG. 6B is a view taken along the line CC of FIG. 6A, and FIG. FIG. 7A is a view on arrow DD of FIG.

7A and 7B are diagrams showing the operation of the valve spring and the valve body according to the second embodiment of the present invention, FIG. 7A is an enlarged view of a main part showing the operation of the valve spring, and FIG.
FIG. 7 is an enlarged view of a main part showing the operation of the valve body.

FIG. 8 is a vertical sectional view showing a pressure control valve according to a third embodiment of the present invention.

FIG. 9 is a view for explaining the operation of the valve body in the third embodiment of the present invention, and (a) is an enlarged view of the essential part for explaining the working fluid that acts on the valve body of the fourth embodiment when the valve is opened. FIG. 1B is an enlarged view of the main parts for explaining the operation of the valve body of the fourth embodiment when the valve is open.

FIG. 10 is an enlarged view of a main part for explaining the operation of the valve spring according to the third embodiment of the present invention.

FIG. 11 is a vertical sectional view showing a pressure control valve according to a fourth embodiment of the present invention.

FIG. 12 is an enlarged view of an essential part showing the operation of the valve element when the valve is opened in the fourth embodiment of the present invention.

FIG. 13 is a vertical sectional view showing a pressure control valve according to a fifth embodiment of the present invention.

FIG. 14 is a vertical sectional view showing a pressure control valve according to a sixth embodiment of the present invention.

FIG. 15 is a vertical sectional view showing a conventional pressure control valve.

[Explanation of symbols]

 1 Pressure Control Valve 2 Mounting Body 3 Supply Port 4 Discharge Port 5 Valve Body 21 Seat Part 32 Valve Body 35 Valve Spring (Spring) 40 Valve Spring Seat (Spring Seat)

Claims (8)

[Claims] 1. A mounting main body having a supply port connected to a high-pressure side and a discharge port connected to a low-pressure side; and a seat portion formed between the supply port and the discharge port. A valve body that can be attached to the mounting body,
A valve body that is seated on the seat portion and a spring that is stretched between the valve body and the seat portion and constantly urges the valve body toward the seat portion are provided, and a working fluid having a predetermined pressure or higher is applied to the supply port. Then, in the pressure control valve in which the valve body separates from the seat portion and opens against the spring force of the spring, when the valve is opened, a part of the valve body is pressed against the seat portion. A pressure control valve provided with means. 2. The pressure according to claim 1, wherein the pressing means is a spring seat provided between the spring and the valve body, and a surface supporting the spring is inclined. Control valve. 3. The pressing means forms the valve body asymmetrically, and a part of the valve body is partially moved by the working fluid passing between the valve body and the seat portion when the valve is opened. The pressure control valve according to claim 1, wherein the pressure control valve is configured to be pressed against the portion. 4. The pressing means is configured such that a part of the valve body is pressed against the seat portion by offsetting the axis of the seat portion from the axis of the valve body. The pressure control valve according to claim 1. 5. The spring seat is formed with a mountain-shaped portion projecting from a surface supporting the spring and having a height in the center, and a low portion having a predetermined step from the apex of the mountain-shaped portion. The pressure control valve according to claim 2, wherein a spring is supported by the apex of the mountain portion and the lower portion. 6. A spring seat is provided between the spring and the valve body, and a spherical or hemispherical member is arranged between the spring seat and the valve body. The pressure control valve according to claim 4. 7. A mounting main body having a supply port connected to a high-pressure side and a discharge port connected to a low-pressure side, and a seat portion formed between the supply port and the discharge port. A valve body that can be attached to the mounting body,
A valve body seated on the seat portion, a spring that is stretched between the valve body and the seat portion and constantly urges the valve body toward the seat portion, and a working fluid from a supply port that engages with the valve body When a pressure equal to or higher than a predetermined pressure is applied to the supply port, the pusher resists the spring force of the spring and opens the valve body by separating from the seat portion. In the pressure control valve for valve | bulb, at least one of the said pusher or the said valve body was formed with the damping material, The pressure control valve characterized by the above-mentioned. 8. The pressure control valve according to claim 7, wherein the damping material is stainless steel.