JPH0451263Y2 - - Google Patents

Description

[Detailed description of the invention] [Industrial application field] This invention relates to a pressure regulating device that maintains a constant liquid pressure, and more specifically, a plurality of pressure regulating means are connected in series to gradually reduce the liquid pressure. This invention relates to a liquid pressure regulating device that discharges residual liquid.

[Prior Art] A pressure regulating valve is used to regulate the pressure of a pressure regulated portion of a hydraulic circuit. General pressure regulating valve (e.g.
-33359 Publication, Utility Model Application Publication No. 60-67471, and Japanese Utility Model Application Publication No. 61-66274), a valve seat is provided between the inlet connected to the pressure regulated part and the residual liquid port that discharges the residual liquid. A spherical or conical valve body, which is provided and receives hydraulic pressure on the inlet side, is pressed against the valve seat by a compression coil spring. Then, when the fluid pressure on the inlet side exceeds a predetermined value,
The valve element moves away from the valve seat against the compression coil spring, causing the liquid at the inlet to flow toward the residual liquid port, thereby lowering the liquid pressure in the pressure regulated part.

In a conventional pressure regulating device, one such pressure regulating valve is connected alone to a pressure regulated section to regulate the pressure of the pressure regulated section.

[Problem that the invention attempts to solve]

Therefore, when a conventional pressure regulating device consisting of one pressure regulating valve is used particularly for regulating ultra-high pressures, the following problems arise.

(1) Ultra-high pressure liquid passes from the inlet of the pressure regulating valve to the residual liquid port, passes through the valve seat and valve body, and drops to atmospheric pressure all at once, so the valve seat and valve body are subjected to a large pressure difference, accelerating wear. The life of the pressure regulating valve will be shortened.

(2) In order to suppress wear of the valve seat and valve body, expensive materials such as cemented carbide must be used;
Costs will rise.

(3) High-pressure liquid is ejected from the gap between the valve seat and the valve body in the form of a jet flow, which causes rapid wear of the parts that are hit by the jet flow, shortening the life of the valve. In addition, expensive hard materials are required to suppress this.

(4) The spring required to press the valve body against the valve seat against ultra-high pressure becomes larger.

Therefore, in a patent application dated September 26, 1988, the applicant proposed a liquid pressure regulating device that connects a plurality of pressure regulating means in series and discharges surplus liquid while gradually reducing the liquid pressure. In this embodiment of the pressure regulating device, the pressure regulating means are arranged such that their center lines are parallel to each other, and the liquid flows in a curved manner from the inlet of the pressure regulating device to the residual liquid port.

This invention relates to an improvement of the earlier patent application, and aims to provide a liquid pressure regulating device in which the operation of the valve bodies of each pressure regulating means is stabilized and the liquid flows smoothly to the leftover liquid port. purpose.

[Means for solving problems]

The liquid pressure regulating device according to this invention includes a plurality of pressure chambers formed in a body in a line in the axial direction, and the most upstream pressure chamber is connected to the pressure regulated part;
A valve seat is provided at the boundary between the upstream pressure chamber and the downstream pressure chamber, and a valve seat is provided at the boundary between the most downstream pressure chamber and the leftover liquid inlet. It has a valve body that receives hydraulic pressure from a pressure chamber on the upstream side, and a spring that presses each valve body against each valve seat.

[Effect]

Each valve seat and valve body receives the differential pressure between the upstream pressure chamber and the downstream pressure chamber, or the differential pressure between the most downstream pressure chamber and the residual liquid port. When the differential pressure exceeds the set load of each spring, the valve body separates from the valve seat, and liquid flows from the upstream pressure chamber to the downstream pressure chamber, or from the most downstream pressure chamber to the residual liquid port. flows. In this way, the liquid pressure in the pressure regulated part is gradually reduced and guided to the residual liquid port.

From the most upstream pressure chamber to the most downstream pressure chamber,
Since they are arranged in a line in the axial direction, the flow of liquid within the pressure regulating device is approximately linear.

〔Example〕

This invention will be described below with reference to embodiments shown in the drawings.

The drawing is a longitudinal sectional view showing the structure of the pressure regulating device.
Inside the body 10, a plurality of (three in the illustrated embodiment) pressure chambers 12a, 12 are arranged in a line in the axial direction.
b, 12c are formed, and the inlet 14 is connected to a pressure regulated part of the hydraulic circuit, for example, the discharge port side of a pump, and communicates with the pressure chamber 12a on the most upstream side. The valve seats 16a, 16b, 16c are arranged at the downstream boundaries of the pressure chambers 12a, 12b, 12c, respectively, and the O-rings 18a, 18b, 18c are arranged in annular grooves around the valve seats 16a, 16b, 16c, respectively. This prevents liquid leakage around the periphery. In order to fix the axial positions of the valve seats 16a and 16b, the valve seat 16b, the spacer 20, the valve seat 16a, and the spacer 22 are fitted in order from the opening on the pressure chamber 12a side of the body 10, and the valve seat 16b is inserted into the body 1.
It is in contact with the step inside 0. The lid 24 is the body 1
body 1 so as to cover the opening on the pressure chamber 12a side of
0 on the pressure chamber 12a side, and the bolt 2
6 is fixed to the end surface of the body 10 on the pressure chamber 12a side. The O-ring 28 connects the body 1 with the lid 24.
The through hole 30 is formed in the spacer 22 and allows the pressure chamber 12a and the inlet 14 to communicate with each other.

The truncated conical valve bodies 32a, 32b, 32c are arranged downstream of the valve seats 16a, 16b, 16c, respectively, and can be seated thereon. Valve body 3
2a, 32b, 32c may be made of different materials, and valve seats 16a, 16b, 16c may be made of different materials.
They may also be made of different materials. Penetration rod 3
4 extends through the centers of the holes in the valve seats 16a, 16b, and 16c, and one end of the penetrating rod 34 passes through the lid 24 and reaches the outside of the body 10. Valve body 32a
are fixed to the penetrating rod 34 and move integrally with the penetrating rod 34, and the valve bodies 32b, 32c are fitted to the ends of the penetrating rod 34 inside the body 10 so as to be freely slidable in the axial direction. The O-rings 35b and 35c are connected to the valve body 32.
The valve body 32 is fitted into the annular groove on the inner circumference of the valve body 32c.
Liquid tightness is maintained between the inner peripheries of b and 32c and the periphery of the penetrating rod 34. The O-ring 36 is fitted into the penetrating portion of the penetrating rod 34 in the lid 24, and is prevented from coming off by the retaining ring 38, thereby maintaining liquid tightness in the penetrating portion. A spring seat 40 is fitted to the end of the penetrating rod 34 exposed to the outside from the lid 24, and a nut 42 is screwed into the end. Za 40 and Natsu 42
, and exerts an urging force in the direction of pulling the through rod 34 out of the body 10, that is, in the direction of pressing the valve body 32a against the valve seat 16a.
The adjustment screw 46 is screwed into the opening of the body 10 on the side opposite to the nut 42 to prevent the valve seat 16c from coming off, and the adjustment screw 48 is inserted into the inner hole of the adjustment screw 46 to prevent the valve seat 16c from coming off.
They are screwed together from the sides. The O-rings 50 and 52 are fitted into annular grooves on the outer periphery of the tips of the adjustment screws 46 and 48, respectively, and maintain liquid tightness at each outer periphery. The remaining liquid port 54 is formed as an inner hole of the adjustment screw 48 . The compression coil spring 56b is compressed between the valve body 32b and the valve seat 16c, and the compression coil spring 56b is compressed between the valve body 32b and the valve seat 16c.
Further, the compression coil spring 56c is compressed between the valve body 32c and the step at the tip of the adjusting screw 48, and presses the valve body 32c against the valve seat 16c. The stopper 58 is connected to the anti-nut 42 of the penetrating rod 34.
The valve body 32 from the penetrating rod 34 is fitted into the end of the side.
This prevents c from falling out.

The operation of the embodiment will be explained.

Valve bodies 32a, 32b, 32c and valve seat 16a,
16b and 16c are the pressure difference between the pressure chambers 12a and 12b as upstream pressure chambers and the pressure chambers 12b and 12c as downstream pressure chambers, and the pressure chamber 12c as the most downstream pressure chamber and residual liquid. Each receives a differential pressure with the port 54. Then, when each differential pressure exceeds the set load of the compression coil spring 44, 56b or 56c, the valve body 32a, 32b or 32c moves against the valve seat 16.
a, 16b or 16c, the pressure chamber 12a,
Liquid flows from the pressure chamber 12b to the pressure chambers 12b and 12c, or from the pressure chamber 12c to the leftover liquid port 54. In this way, the hydraulic pressure at the inlet 14 decreases sequentially, causing the inlet 1
4 to the residual liquid port 54. For example, if the pressure regulation value of the pressure regulated part is 600Kg・f/ ^cm2 , the pressure chamber 12
The hydraulic pressures of a, 12b, 12c and residual liquid port 54 are 600Kg・f/cm ² , 400Kg・f/cm ² , and 200Kg・
It is possible to set it to f/cm ² , 0Kg·f/cm ² . The set load of the compression coil spring 44 can be adjusted by turning the nut 42, and the set load of the compression coil springs 56b and 56c can be adjusted by turning the adjusting screw 4.
Adjustment can be made by turning 6 and 48. Therefore, the pressure regulation value at the inlet 14 can also be adjusted within a predetermined range by rotating the nut 42 and adjusting screws 46, 48.

Since the pressure chambers 12a, 12b, and 12c are arranged in a line in the axial direction, the flow of liquid within the pressure regulating device is approximately linear, and the valve bodies 32a,
The operations of 32b and 32c are stabilized, and the flow of liquid within the pressure regulator becomes smooth.

[Effect of idea]

Thus, according to this invention, the valve seat, the valve body that can sit on the valve seat and receive the hydraulic pressure of the upstream pressure chamber, and the spring that biases the valve body toward the valve seat are combined. The pressure regulating means including the pressure regulating means are connected in series, and the liquid in the pressure regulated part is gradually reduced in each pressure regulating means and guided to the residual liquid port, so that the pressure in the pressure regulated part is regulated. Each valve seat and valve body is subject to the differential pressure between the upstream pressure chamber and the downstream pressure chamber, or the differential pressure between the most downstream pressure chamber and the residual liquid port, reducing the load and causing wear. It is possible to suppress the damage and increase the service life, and also to avoid the use of expensive materials. Furthermore, since the jet flow from the gap between the valve body and the valve seat is weakened, wear caused by the high-pressure jet flow is suppressed, and the biasing force required for the spring for biasing the valve body is reduced. The spring can be made smaller.

In this device, the pressure chambers from the most upstream side to the most downstream side are arranged in a line in the axial direction, so the flow of liquid in the pressure regulator becomes almost linear, and as a result, each The operation of the valve body is stabilized, and the liquid flows smoothly to the leftover liquid port.

[Brief explanation of drawings]

The drawing is a longitudinal sectional view showing the structure of a liquid pressure regulating device according to an embodiment of the invention. 10...Body, 12a, 12b, 12c...
Pressure chamber, 16a, 16b, 16c... Valve seat, 32
a, 32b, 32c... Valve body, 44, 56b, 5
6c...Compression coil spring, 54...Left liquid port.

Claims (1)

[Claims for Utility Model Registration] (1) A plurality of pressure chambers 12a, 12b formed in the body 10 in a line in the axial direction, with the most upstream pressure chamber 12a connected to the pressure regulated part, 12
c, and valve seats 16a, 16b disposed at the boundaries between the upstream pressure chambers 12a, 12b and the downstream pressure chambers 12b, 12c, and the boundary between the most downstream pressure chamber 12c and the residual liquid port 54, respectively. , 16c and
Valve bodies 32a, 32b, 32c can be seated on the respective valve seats 16a, 16b, 16c and receive the hydraulic pressure of the pressure chambers 12a, 12b, 12c upstream with respect to the valve seats 16a, 16b, 16c; The valve bodies 32a, 32b, 32c are connected to each valve seat 16a,
Spring 44, 56b pressing against 16b, 16c,
56c. (2) A common penetrating rod 34 connects all valve seats 16a, 16
The valve element 32a on the most upstream side moves integrally with the through rod 34, and the other valve elements 32b and 32c extend in the axial direction with respect to the through rod 34. A utility model characterized in that the spring 44 for the most upstream valve body 32a is fitted so as to be relatively movable and presses the most upstream valve body 32a against the valve seat 16a via the through rod 34. A liquid pressure regulating device according to claim 1. (3) Valve bodies 32b and 3 other than the most upstream valve body 32a
The springs 56b and 56c for 2c are
Utility model registration claim 1 or 2, characterized in that the valve bodies 32b, 56c are compressed between the energized valve bodies 32b, 32c and the next stage valve seat 16b or stopper 48. liquid pressure regulator. (4) The preload of the spring 44 for the most upstream valve body 32a is adjusted by a nut 42 that is fitted onto the through rod 34 outside the body 10 and screwed into the through rod 34. A liquid pressure regulating device according to claim 2 of the utility model registration claim. (5) Valve bodies 32b and 3 other than the most upstream valve body 32a
The liquid according to claim 3 of the utility model registration claim, characterized in that the preload of the springs 56b, 56c for 2c is adjusted by the axial position of the valve seat 16b or stopper 48 with which the springs 56b, 56c come into contact. pressure regulating device.