WO2014136649A1 - Pressure control valve - Google Patents

Pressure control valve Download PDF

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Publication number
WO2014136649A1
WO2014136649A1 PCT/JP2014/054891 JP2014054891W WO2014136649A1 WO 2014136649 A1 WO2014136649 A1 WO 2014136649A1 JP 2014054891 W JP2014054891 W JP 2014054891W WO 2014136649 A1 WO2014136649 A1 WO 2014136649A1
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WO
WIPO (PCT)
Prior art keywords
main
valve
flow path
pressure
high pressure
Prior art date
Application number
PCT/JP2014/054891
Other languages
French (fr)
Japanese (ja)
Inventor
加藤　靖丈
高史 山口
Original Assignee
豊興工業株式会社
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Filing date
Publication date
Application filed by 豊興工業株式会社 filed Critical 豊興工業株式会社
Publication of WO2014136649A1 publication Critical patent/WO2014136649A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/024—Pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/10—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve
    • F16K17/105—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve using choking or throttling means to control the fluid operation of the main valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure

Definitions

  • the present invention relates to a pressure control of a balance piston type including at least two valve bodies.
  • a pilot operated balance piston type pressure control valve described in Patent Document 1 controls a main valve that opens and closes a main flow path with two valve bodies.
  • a check valve is provided in a pilot flow path that connects a pressure receiving portion that forms a high pressure chamber of a main valve and a pilot pressure receiving portion that forms a working chamber of the main valve.
  • the check valve prevents the working fluid from flowing from the pilot pressure receiving portion to the pressure receiving portion.
  • the check valve does not control the flow rate of the working fluid flowing from the pressure receiving portion toward the pilot pressure receiving portion, and also prevents the working fluid from flowing from the pilot pressure receiving portion to the pressure receiving portion.
  • the main valve body easily generates chattering that repeatedly opens and closes the main flow path.
  • One aspect of the present invention is a pilot-operated pressure control valve having a main valve body that opens and closes a main flow path, a main high pressure chamber provided on one end side in the moving direction of the main valve body, A main working chamber provided on the other end side of the valve body in the moving direction, and a first pilot channel connecting the main high pressure chamber and the main working chamber, and a pressure difference between the main high pressure chamber and the main working chamber.
  • a first valve having a main valve for actuating the main valve body and a first valve body for opening and closing a flow path connecting the first pilot flow path to the low pressure side, on one end side in the moving direction of the first valve body
  • a first high pressure chamber provided, a first working chamber provided on the other end side in the moving direction of the first valve body, and a second pilot flow path connecting the first high pressure chamber and the first working chamber, and
  • the first valve in which the first valve body operates in accordance with the pressure difference between the first high pressure chamber and the first working chamber.
  • a second valve body that opens and closes the third pilot flow path connecting the second pilot flow path to the low pressure side, and the high pressure side fluid pressure in the direction to open the third pilot flow path is A second valve acting on the two-valve body, and a first throttle portion provided in the first pilot flow path, which throttles a part of the first pilot flow path, and includes a first pilot flow
  • the passage is characterized by allowing both a fluid flow from the main high pressure chamber side to the main action chamber side and a fluid flow from the main action chamber side to the main high pressure chamber side.
  • the flow rate of the fluid flowing in the first pilot flow path can be controlled by the first restrictor, and the fluid flows from the main high pressure chamber side to the main working chamber side in the first pilot flow path. Since both the fluid flow toward the main fluid chamber and the fluid flow toward the main high pressure chamber from the main working chamber side are possible, occurrence of chattering at the main valve can be suppressed.
  • valve 11 ... main valve body 11A ... main high pressure chamber 11B ... main low pressure chamber 11C ... main valve port 11E ... valve seat 11D ... main working chamber 12 ... check valve 20 ... first valve 21 1st valve body 21A ⁇ ⁇ 1st high pressure chamber 21B ⁇ ⁇ 1 1st low pressure chamber 21C 1st valve port 21E ...
  • Valve seat part 21D 1st working chamber 21G piston part 30 2nd valve 31 ⁇ 2nd valve body 31A ... Second High Pressure Chamber 31B... Second Low Pressure Chamber 31D... Piston Part 31C... Second Valve Port 31E... Valve Seat Part L1... Main Channel L2... First Pilot Channel R1... First Throttle Unit R2... Second Throttle Unit L5 ... 2nd pilot flow path L6 ... 3rd pilot flow path
  • the pressure control valve according to the present invention is applied to a relief valve for a hydraulic circuit.
  • (First embodiment) 1. Configuration of pressure control valve (see Fig. 1)
  • the pressure control valve 1 includes a main valve 10, a first valve 20, a second valve 30, and the like.
  • the pressure control valve 1 is a pilot operated valve in which these valves 10, 20, 30 are integrated.
  • the main valve 10 opens and closes the main flow path L1 through which the working fluid that drives the fluid circuit flows.
  • the main flow path L1 refers to a flow path from the high pressure generation source P on the high pressure side to the tank T on the low pressure side via P1 and P2.
  • the main valve body 11 opens and closes the main flow path L1.
  • a valve body (not shown) of the main valve 10 is provided with a main high pressure chamber 11A, a main low pressure chamber 11B, a main valve port 11C, a main working chamber 11D, and the like.
  • the main high pressure chamber 11A is provided on one end side of the main valve body 11 in the moving direction and is connected to the high pressure side.
  • the main low pressure chamber 11B is connected to the low pressure side.
  • the main high pressure chamber 11A and the main low pressure chamber 11B can communicate with each other through the main valve port 11C.
  • the main valve body 11 opens and closes the main valve port 11C by separating or abutting against a valve seat portion 11E provided at the outer edge of the main valve port 11C. Specifically, when the main valve body 11 is separated from the valve seat portion 11E, the main valve port 11C is opened. On the other hand, when the main valve body 11 contacts the valve seat portion 11E, the main valve port 11C is closed.
  • the main working chamber 11D is provided on the other end side of the main valve body 11 in the moving direction.
  • the main working chamber 11D is shut off from the main low pressure chamber 11B by the main valve body 11.
  • the valve body of the main valve 10 is provided with a first pilot flow path L2 that connects the main high pressure chamber 11A and the main working chamber 11D.
  • the first pilot flow path L2 connects the main high pressure chamber 11A and the main working chamber 11D via P2, P3, P4, and P5.
  • the first throttle channel R2 is provided with a first throttle portion R1.
  • the first restricting portion R1 is a fluid resistance portion that restricts a part of the first pilot flow path L2.
  • a pressure loss may occur before and after the first throttle portion R1. That is, when a fluid flow is generated in the first pilot flow path L2, the outlet side pressure of the first throttle portion R1 becomes lower than the inlet side pressure.
  • the fluid pressure in the main high pressure chamber 11A causes the main valve body 11 to act in a direction that opens the main valve port 11C.
  • the fluid pressure in the main working chamber 11 ⁇ / b> D causes the main valve body 11 to have a force in a direction to close the main valve port 11 ⁇ / b> C.
  • the spring 11F provided in the main working chamber 11D causes the main valve body 11 to act with an elastic force in a direction to close the main valve port 11C.
  • valve opening force the force for opening force.
  • the force in the direction of closing the main valve port 11C including the elastic force of the spring 11F is referred to as valve closing force.
  • the area where the main valve body 11 receives pressure from the working fluid in the main high pressure chamber 11A is smaller than the area where the main valve body 11 receives pressure from the working fluid in the main working chamber 11D.
  • the main valve body 11 operates according to the pressure difference between the main high-pressure chamber 11A and the main working chamber 11D.
  • the valve closing force exceeds the valve opening force, and the main valve port 11C is closed.
  • the flow path L4 connecting the first pilot flow path L2 to the low pressure side is opened and a fluid flow is generated in the first pilot flow path L2, the pressure in the main working chamber 11D is lower than the pressure in the main high pressure chamber 11A.
  • the main valve port 11C opens.
  • the flow path L4 connecting the first pilot flow path L2 to the low pressure side is closed, the pressure in the main working chamber 11D increases.
  • the main valve port 11C is closed.
  • the flow path L4 is a flow path that connects the first pilot flow path L2 to the low pressure side via P3 and the first high pressure chamber 21A.
  • a second throttle portion R2 is provided in series with the first throttle portion R1.
  • the second throttle portion R2 is provided closer to the main working chamber 11D than the first throttle portion R1, and throttles a part of the first pilot flow path L2. For this reason, when a fluid flow occurs in the first pilot flow path L2, a pressure difference also occurs before and after the second throttle portion R2.
  • the second diaphragm portion R2 is a variable diaphragm whose throttle opening is adjustable. For this reason, the person who manages the pressure control valve 1 can adjust the throttle opening of the second throttle portion R2.
  • a check valve 12 is provided in the bypass flow path L3 that bypasses the second throttle portion R2 and connects the inlet side P4 and the outlet side P5 of the second throttle portion R2.
  • the check valve 12 prevents the working fluid from flowing from the main high pressure chamber 11A side to the main working chamber 11D side, and allows the working fluid to flow from the main working chamber 11D side to the main high pressure chamber 11A side.
  • the first pilot flow path L2 is not provided with valves that control the flow direction of the fluid, which corresponds to a check valve. For this reason, in the first pilot flow path L2, both a fluid flow from the main high pressure chamber 11A side to the main action chamber 11D side and a fluid flow from the main action chamber 11D side to the main high pressure chamber 11A side can occur.
  • the first valve 20 opens and closes a flow path L4 that connects the first pilot flow path L2 to the low pressure side.
  • the structure of the first valve 20 according to the present embodiment is the same as the structure of the main valve 10.
  • the first valve body 21 opens and closes the flow path L4.
  • a valve body (not shown) of the first valve 20 is provided with a first high pressure chamber 21A, a first low pressure chamber 21B, a first valve port 21C, a first working chamber 21D, and the like.
  • the first high-pressure chamber 21A is provided on one end side in the moving direction of the first valve body 21 and is connected to the high-pressure side.
  • the first low pressure chamber 21B is connected to the low pressure side.
  • the first high pressure chamber 21A and the first low pressure chamber 21B can communicate with each other through the first valve port 21C.
  • the first valve body 21 opens and closes the first valve port 21C by being separated from or in contact with a valve seat portion 21E provided at the outer edge of the first valve port 21C. That is, when the first valve body 21 is separated from the valve seat portion 21E, the first valve port 21C is opened. When the first valve body 21 contacts the valve seat portion 21E, the first valve port 21C is closed.
  • the first working chamber 21D is provided on the other end side in the moving direction of the first valve body 21, and is shut off from the first low-pressure chamber 21B by the first valve body 21.
  • the valve body of the first valve 20 is provided with a second pilot flow path L5 that connects the first high pressure chamber 21A and the first working chamber 21D.
  • the second pilot flow path L5 connects the first high pressure chamber 21A and the first working chamber 21D via P6.
  • the third pilot portion R3 is provided in the second pilot channel L5.
  • the third restricting portion R3 is a fluid resistance portion that restricts a part of the second pilot flow path L5.
  • pressure loss may occur before and after the third throttle portion R3.
  • the outlet side pressure of the third throttle portion R3 becomes lower than the inlet side pressure.
  • the fluid pressure in the first high-pressure chamber 21A causes the first valve body 21 to have a force that opens the first valve port 21C.
  • the fluid pressure in the first working chamber 21 ⁇ / b> D causes the first valve body 21 to have a force in a direction to close the first valve port 21 ⁇ / b> C.
  • the spring 21F provided in the first working chamber 21D acts on the first valve body 21 with an elastic force in a direction to close the first valve port 21C.
  • the force that opens the first valve port 21C is referred to as valve opening force.
  • a force for closing the first valve port 21C including the elastic force of the spring 21F is referred to as a valve closing force.
  • the area where the first valve body 21 receives pressure from the working fluid in the first high pressure chamber 21A is smaller than the area where the first valve body 21 receives pressure from the working fluid in the first working chamber 21D.
  • the first valve body 21 operates according to the pressure difference between the first high pressure chamber 21A and the first working chamber 21D.
  • the first valve port 21C When the valve closing force falls below the valve opening force, the first valve port 21C is opened. When the third pilot flow path L6 is closed, the pressure in the first working chamber 21D increases. When the pressure in the first working chamber 21D becomes the same as the pressure in the first high pressure chamber 21A, the first valve port 21C is closed.
  • the second pilot flow path L5 is provided with a fourth throttle portion R4 in series with the third throttle portion R3.
  • the fourth throttle portion R4 is provided closer to the first working chamber 21D than the third throttle portion R3 and throttles a part of the second pilot flow path L5. For this reason, when a fluid flow occurs in the second pilot flow path L5, a pressure difference also occurs before and after the fourth throttle portion R4.
  • the second valve 30 opens and closes the third pilot flow path L6.
  • the second valve body 31 opens and closes the third pilot flow path L6.
  • the valve body (not shown) of the second valve 30 is provided with a second high pressure chamber 31A, a second low pressure chamber 31B, a second valve port 31C, and the like.
  • the second high pressure chamber 31A is partitioned into two spaces A and B by a piston portion 31D that can move in the second high pressure chamber 31A.
  • the piston portion 31D is displaced integrally with the second valve body 31.
  • the working fluid on the high pressure side is guided to the space A on the one end side in the displacement direction of the piston portion 31D. For this reason, the fluid pressure in the space A causes a force to open the third pilot flow path L6 to act on the piston portion 31D.
  • the space A may have a size such that the volume becomes substantially zero when the second valve port 31C is closed.
  • the working fluid on the high pressure side is guided to the space B on the other end side in the displacement direction of the piston portion 31D through the third pilot flow path L6.
  • the fluid pressure in the space B causes the force in the direction of closing the third pilot flow path L6 to act on the piston portion 31D, and the force in the direction of opening to act on the head of the second valve body 31, and the second The valve body 31 is balanced.
  • the area where the second valve body 31 receives pressure from the working fluid in the space A through the piston portion 31D is the pressure from the working fluid in the space B through the piston portion 31D. Greater than the area you receive.
  • a first diaphragm portion R1, a third diaphragm portion R3, and the like are provided as a diaphragm portion that restricts a part.
  • the second low pressure chamber 31B is connected to the low pressure side, and can communicate with the space B of the second high pressure chamber 31A through the second valve port 31C.
  • the second valve body 31 opens or closes the second valve port 31C by being separated from or abutting against a valve seat portion 31E provided at the outer edge of the second valve port 31C.
  • the second valve port 31C When the second valve body 31 is separated from the valve seat portion 31E, the second valve port 31C is opened. When the second valve body 31 comes into contact with the valve seat portion 31E, the second valve port 31C is closed.
  • the spring 31F provided in the second low-pressure chamber 31B causes the second valve body 31 to exert an elastic force in a direction to close the second valve port 31C.
  • valve opening force the force due to the fluid pressure acting on the space A
  • valve closing force the force due to the fluid pressure acting on the space A
  • the elastic force of the spring 31F hereinafter referred to as valve closing force
  • the third pilot flow path L6 opens. Therefore, as described above, since the first valve port 21C is opened, the flow path L4 is opened and the main valve port 11C is opened.
  • a part of the high-pressure supply flow path connecting the first high-pressure chamber 21A and the high-pressure side P that is, a part of the flow path from the high-pressure side P to the first high-pressure chamber 21A via P1, P2, P3 and the first high-pressure chamber.
  • a part of one pilot flow path L2 is shared.
  • squeeze part R1 is provided in the site
  • the flow rate of the working fluid flowing through the first pilot flow path L2 can be controlled by the first throttle portion R1.
  • the working fluid can flow from the main high pressure chamber 11A side to the main working chamber 11D side, and can flow from the main working chamber 11D side to the main high pressure chamber 11A side. Therefore, chattering can be prevented from occurring in the main valve 10.
  • the first pilot channel L2 is provided with a second throttle part R2 that throttles a part of the first pilot channel L2.
  • the second diaphragm portion R2 is a variable diaphragm whose throttle opening is adjustable.
  • a check valve 12 that prevents the working fluid from flowing from the main high pressure chamber 11A side to the main working chamber 11D side is provided in the bypass flow path L3 that bypasses the second throttle portion R2. It is characterized by. Thereby, when the main flow path L1 opens, the working fluid in the main working chamber 11D can be quickly discharged, so that the responsiveness of the main valve body 11 can be improved.
  • the working fluid on the high-pressure side P is guided to the one end side in the displacement direction of the piston portion 31D to act to open the third pilot flow path.
  • the working fluid on the high pressure side is guided to the other end side in the displacement direction of the piston portion 31D via the third pilot flow path L6.
  • the first throttle part R1 and the third throttle part R3 are provided as throttle parts that throttle down a part of the flow path. It is characterized by.
  • the present embodiment differs from the first embodiment in the position of the first aperture portion R1. Specifically, in the present embodiment, the working fluid supplied to the space A of the second valve 30 is also decompressed by the first throttle portion R1.
  • the present embodiment has the following features.
  • (A) The first high pressure chamber 21A of the first valve 20 is partitioned into two spaces A and B by the piston portion 21G, similarly to the second valve 30 according to the first embodiment.
  • (B) The second valve 30 is configured as a so-called direct-acting poppet valve that opposes the pressure on the high-pressure side P only by the elastic force of the spring 31F.
  • the working fluid on the high pressure side is guided to the space A on the one end side in the displacement direction of the piston portion 21G. For this reason, the working fluid pressure in the space A causes the piston portion 21G to exert a force in a direction to open the first pilot flow path L2.
  • the space A may have a size such that the volume becomes substantially zero when the first valve port 21C is closed.
  • the working fluid on the high pressure side is guided to the space B on the other end side in the displacement direction of the piston portion 21G via the first pilot flow path L2. For this reason, the working fluid pressure in the space B causes the force in the direction of closing the first pilot flow path L2 to act on the piston portion 21G, and the force in the direction of opening to act on the head of the first valve body 21, One valve body 21 is balanced.
  • the area where the first valve body 21 receives pressure from the working fluid in the space A through the piston portion 21G is the pressure from the working fluid in the space B through the piston portion 21G. Greater than the area you receive.
  • the 2nd valve 30 concerning the above-mentioned embodiment was a system which changes relief pressure by adjusting the elastic force of a spring
  • the present invention is not limited to this.
  • a system may be used in which a force corresponding to the elastic force of the spring is generated by an electromagnetic force using a solenoid coil, and the relief pressure is changed by adjusting the electromagnetic force.
  • the diaphragm described in the claims is configured by the first diaphragm R1 and the third diaphragm R3, but the present invention is not limited to this.
  • the present invention is not limited to the above-described embodiment as long as it matches the gist of the invention described in the claims. That is, the configuration is not limited to the pressure control valve shown in the above-described embodiment, and the configurations shown in the above-described first to third embodiments may be appropriately combined.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Safety Valves (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

A pilot-operated pressure control valve is provided with a main valve, a first valve, and a first throttle section. The main valve has: a main valve body which opens and closes a main flow passage; a main high-pressure chamber which is provided on one end side of the main valve in the direction of movement thereof; a main action chamber which is provided on the other end side of the main valve body in the direction of movement thereof; and a first pilot flow passage which connects the main high-pressure chamber and the main action chamber. The first pilot flow passage permits both a fluid flow from the main high-pressure chamber side to the main action chamber side and a fluid flow from the main action chamber side to the main high-pressure chamber side.

Description

圧力制御弁Pressure control valve 関連出願の相互参照Cross-reference of related applications
　本国際出願は、２０１３年３月７日に日本国特許庁に出願した日本国特許出願第２０１３－４５５４８号に基づく優先権を主張するものであり、日本国特許出願第２０１３－４５５４８号の全内容を本国際出願に援用する。 This international application claims priority based on Japanese Patent Application No. 2013-45548 filed with the Japan Patent Office on March 7, 2013. All of Japanese Patent Application No. 2013-45548 The contents are incorporated into this international application.
　本発明は、少なくとも２個の弁体を備えるバランスピストン型の圧力制御に関する。 The present invention relates to a pressure control of a balance piston type including at least two valve bodies.
　例えば、特許文献１に記載のパイロット操作方式のバランスピストン型の圧力制御弁は、メイン流路を開閉するメインバルブを２つの弁体にて制御している。 For example, a pilot operated balance piston type pressure control valve described in Patent Document 1 controls a main valve that opens and closes a main flow path with two valve bodies.
特開平３－２６５７７０号公報JP-A-3-265770
　特許文献１の圧力制御弁には、メインバルブの高圧室をなす受圧部とメインバルブの作用室をなすパイロット受圧部とを繋ぐパイロット流路に逆止弁が設けられている。当該逆止弁は、パイロット受圧部から受圧部に作動流体が流通することを阻止する。 In the pressure control valve of Patent Document 1, a check valve is provided in a pilot flow path that connects a pressure receiving portion that forms a high pressure chamber of a main valve and a pilot pressure receiving portion that forms a working chamber of the main valve. The check valve prevents the working fluid from flowing from the pilot pressure receiving portion to the pressure receiving portion.
　ところで、逆止弁は、受圧部からパイロット受圧部に向けて流通する作動流体の流量制御するものではなく、かつ、パイロット受圧部から受圧部に作動流体が流通することを阻止するため、メインバルブの主弁体がメイン流路の開閉を繰り返すチャタリングを発生し易い。 By the way, the check valve does not control the flow rate of the working fluid flowing from the pressure receiving portion toward the pilot pressure receiving portion, and also prevents the working fluid from flowing from the pilot pressure receiving portion to the pressure receiving portion. The main valve body easily generates chattering that repeatedly opens and closes the main flow path.
　少なくとも２個の弁体を備えるバランスピストン型の圧力制御弁において、主弁体のチャタリング発生を抑制することが望ましい。 ¡In a balanced piston type pressure control valve having at least two valve bodies, it is desirable to suppress chattering in the main valve body.
　一局面の本発明は、パイロット操作方式の圧力制御弁において、メイン流路を開閉する主弁体を有するメインバルブであって、主弁体の移動方向一端側に設けられたメイン高圧室、主弁体の移動方向他端側に設けられたメイン作用室、及びメイン高圧室とメイン作用室とを繋ぐ第１パイロット流路を有し、かつ、メイン高圧室とメイン作用室との圧力差に応じて主弁体が作動するメインバルブと、第１パイロット流路を低圧側に繋ぐ流路を開閉する第１弁体を有する第１バルブであって、第１弁体の移動方向一端側に設けられた第１高圧室、第１弁体の移動方向他端側に設けられた第１作用室、及び第１高圧室と第１作用室とを繋ぐ第２パイロット流路を有し、かつ、第１高圧室と第１作用室との圧力差に応じて第１弁体が作動する第１バルブと、第２パイロット流路を低圧側に繋ぐ第３パイロット流路を開閉する第２弁体を有する第２バルブであって、当該第３パイロット流路を開く向きの高圧側流体圧が第２弁体に作用する第２バルブと、第１パイロット流路に設けられた第１絞り部であって、第１パイロット流路の一部を絞る第１絞り部とを備え、第１パイロット流路は、メイン高圧室側からメイン作用室側に向かう流体流れ、及びメイン作用室側からメイン高圧室側に向かう流体流れのいずれも許容することを特徴とする。 One aspect of the present invention is a pilot-operated pressure control valve having a main valve body that opens and closes a main flow path, a main high pressure chamber provided on one end side in the moving direction of the main valve body, A main working chamber provided on the other end side of the valve body in the moving direction, and a first pilot channel connecting the main high pressure chamber and the main working chamber, and a pressure difference between the main high pressure chamber and the main working chamber. And a first valve having a main valve for actuating the main valve body and a first valve body for opening and closing a flow path connecting the first pilot flow path to the low pressure side, on one end side in the moving direction of the first valve body A first high pressure chamber provided, a first working chamber provided on the other end side in the moving direction of the first valve body, and a second pilot flow path connecting the first high pressure chamber and the first working chamber, and The first valve in which the first valve body operates in accordance with the pressure difference between the first high pressure chamber and the first working chamber. And a second valve body that opens and closes the third pilot flow path connecting the second pilot flow path to the low pressure side, and the high pressure side fluid pressure in the direction to open the third pilot flow path is A second valve acting on the two-valve body, and a first throttle portion provided in the first pilot flow path, which throttles a part of the first pilot flow path, and includes a first pilot flow The passage is characterized by allowing both a fluid flow from the main high pressure chamber side to the main action chamber side and a fluid flow from the main action chamber side to the main high pressure chamber side.
　これにより、一局面の本発明では、第１パイロット流路に流れる流体を第１絞り部で流量制御可能であり、かつ、流体は第１パイロット流路において、メイン高圧室側からメイン作用室側に向かう流体流れ、及びメイン作用室側からメイン高圧室側に向かう流体流れのいずれも可能であるので、メインバルブにてチャタリングが発生することを抑制できる。 Thus, in the present invention of one aspect, the flow rate of the fluid flowing in the first pilot flow path can be controlled by the first restrictor, and the fluid flows from the main high pressure chamber side to the main working chamber side in the first pilot flow path. Since both the fluid flow toward the main fluid chamber and the fluid flow toward the main high pressure chamber from the main working chamber side are possible, occurrence of chattering at the main valve can be suppressed.
　以下、本発明の実施形態を図面と共に説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
本発明の第１実施形態に係る圧力制御弁を示す図である。It is a figure which shows the pressure control valve which concerns on 1st Embodiment of this invention. 本発明の第２実施形態に係る圧力制御弁を示す図である。It is a figure which shows the pressure control valve which concerns on 2nd Embodiment of this invention. 本発明の第３実施形態に係る圧力制御弁を示す図である。It is a figure which shows the pressure control valve which concerns on 3rd Embodiment of this invention.
　１… 圧力制御弁　１０… メインバルブ　１１… 主弁体　１１Ａ… メイン高圧室　１１Ｂ… メイン低圧室　１１Ｃ… メイン弁口　１１Ｅ… 弁座部　１１Ｄ… メイン作用室　１２… 逆止弁　２０… 第１バルブ　２１… 第１弁体　２１Ａ… 第１高圧室　２１Ｂ… 第１低圧室　２１Ｃ… 第１弁口　２１Ｅ… 弁座部　２１Ｄ… 第１作用室　２１Ｇ… ピストン部　３０… 第２バルブ　３１… 第２弁体　３１Ａ… 第２高圧室　３１Ｂ… 第２低圧室　３１Ｄ… ピストン部　３１Ｃ… 第２弁口　３１Ｅ… 弁座部　Ｌ１… メイン流路　Ｌ２… 第１パイロット流路　Ｒ１… 第１絞り部　Ｒ２… 第２絞り部　Ｌ５… 第２パイロット流路Ｌ６… 第３パイロット流路 1 ... pressure control valve 10 ... main valve 11 ... main valve body 11A ... main high pressure chamber 11B ... main low pressure chamber 11C ... main valve port 11E ... valve seat 11D ... main working chamber 12 ... check valve 20 ... first valve 21 1st valve body 21A 高 圧 1st high pressure chamber 21B 低 圧 １ 1st low pressure chamber 21C 1st valve port 21E ... Valve seat part 21D 1st working chamber 21G piston part 30 2nd valve 31 弁 2nd valve body 31A … Second High Pressure Chamber 31B… Second Low Pressure Chamber 31D… Piston Part 31C… Second Valve Port 31E… Valve Seat Part L1… Main Channel L2… First Pilot Channel R1… First Throttle Unit R2… Second Throttle Unit L5 ... 2nd pilot flow path L6 ... 3rd pilot flow path
　以下に説明する「発明の実施形態」は実施形態の一例を示すものである。つまり、特許請求の範囲に記載された発明特定事項等は、下記の実施形態に示された具体的手段や構造等に限定されるものではない。 The “embodiment of the invention” described below shows an example of the embodiment. In other words, the invention specific items described in the claims are not limited to the specific means and structures shown in the following embodiments.
　そして、本実施形態は、油圧回路用のリリーフ弁に本発明に係る圧力制御弁を適用したものである。
　（第１実施形態）
　１．圧力制御弁の構成（図１参照）
　圧力制御弁１は、メインバルブ１０、第１バルブ２０及び第２バルブ３０等を有する。圧力制御弁１は、これらのバルブ１０、２０、３０が一体化されたパイロット操作方式のバルブである。 In this embodiment, the pressure control valve according to the present invention is applied to a relief valve for a hydraulic circuit.
(First embodiment)
1. Configuration of pressure control valve (see Fig. 1)
The pressure control valve 1 includes a main valve 10, a first valve 20, a second valve 30, and the like. The pressure control valve 1 is a pilot operated valve in which these valves 10, 20, 30 are integrated.
　１．１　メインバルブ
　メインバルブ１０は、流体回路を駆動する作動流体が流通するメイン流路Ｌ１を開閉する。メイン流路Ｌ１は、高圧側である高圧発生源ＰからＰ１、Ｐ２を経由して低圧側であるタンクＴに至る流路をいう。 1.1 Main Valve The main valve 10 opens and closes the main flow path L1 through which the working fluid that drives the fluid circuit flows. The main flow path L1 refers to a flow path from the high pressure generation source P on the high pressure side to the tank T on the low pressure side via P1 and P2.
　主弁体１１は、メイン流路Ｌ１を開閉する。メインバルブ１０のバルブボディ（図示せず。）には、メイン高圧室１１Ａ、メイン低圧室１１Ｂ、メイン弁口１１Ｃ及びメイン作用室１１Ｄ等が設けられている。 The main valve body 11 opens and closes the main flow path L1. A valve body (not shown) of the main valve 10 is provided with a main high pressure chamber 11A, a main low pressure chamber 11B, a main valve port 11C, a main working chamber 11D, and the like.
　メイン高圧室１１Ａは、主弁体１１の移動方向一端側に設けられて高圧側に接続されている。メイン低圧室１１Ｂは、低圧側に接続されている。メイン高圧室１１Ａとメイン低圧室１１Ｂとは、メイン弁口１１Ｃを通して連通可能である。 The main high pressure chamber 11A is provided on one end side of the main valve body 11 in the moving direction and is connected to the high pressure side. The main low pressure chamber 11B is connected to the low pressure side. The main high pressure chamber 11A and the main low pressure chamber 11B can communicate with each other through the main valve port 11C.
　主弁体１１は、メイン弁口１１Ｃの外縁に設けられた弁座部１１Ｅに対して離間又は当接することにより、メイン弁口１１Ｃを開閉する。具体的には、主弁体１１が弁座部１１Ｅから離間すると、メイン弁口１１Ｃが開かれる。一方、主弁体１１が弁座部１１Ｅに当接するとメイン弁口１１Ｃが閉じられる。 The main valve body 11 opens and closes the main valve port 11C by separating or abutting against a valve seat portion 11E provided at the outer edge of the main valve port 11C. Specifically, when the main valve body 11 is separated from the valve seat portion 11E, the main valve port 11C is opened. On the other hand, when the main valve body 11 contacts the valve seat portion 11E, the main valve port 11C is closed.
　メイン作用室１１Ｄは、主弁体１１の移動方向他端側に設けられている。メイン作用室１１Ｄは、主弁体１１によりメイン低圧室１１Ｂと遮断されている。メインバルブ１０のバルブボディには、メイン高圧室１１Ａとメイン作用室１１Ｄとを繋ぐ第１パイロット流路Ｌ２が設けられている。第１パイロット流路Ｌ２は、Ｐ２、Ｐ３、Ｐ４、Ｐ５を経由してメイン高圧室１１Ａとメイン作用室１１Ｄとを繋ぐ。 The main working chamber 11D is provided on the other end side of the main valve body 11 in the moving direction. The main working chamber 11D is shut off from the main low pressure chamber 11B by the main valve body 11. The valve body of the main valve 10 is provided with a first pilot flow path L2 that connects the main high pressure chamber 11A and the main working chamber 11D. The first pilot flow path L2 connects the main high pressure chamber 11A and the main working chamber 11D via P2, P3, P4, and P5.
　第１パイロット流路Ｌ２には、第１絞り部Ｒ１が設けられている。第１絞り部Ｒ１は、第１パイロット流路Ｌ２の一部を絞った流体抵抗部である。第１パイロット流路Ｌ２に流体流れが生じたときに、第１絞り部Ｒ１の前後で圧力損失が発生し得る。つまり、第１パイロット流路Ｌ２に流体流れが生じると、第１絞り部Ｒ１の出口側圧力は、入口側圧力よりも低くなる。 The first throttle channel R2 is provided with a first throttle portion R1. The first restricting portion R1 is a fluid resistance portion that restricts a part of the first pilot flow path L2. When a fluid flow occurs in the first pilot flow path L2, a pressure loss may occur before and after the first throttle portion R1. That is, when a fluid flow is generated in the first pilot flow path L2, the outlet side pressure of the first throttle portion R1 becomes lower than the inlet side pressure.
　メイン高圧室１１Ａの流体圧は、メイン弁口１１Ｃを開く向きの力を主弁体１１に作用させる。メイン作用室１１Ｄの流体圧は、メイン弁口１１Ｃを閉じる向きの力を主弁体１１に作用させる。メイン作用室１１Ｄ内に設けられたばね１１Ｆは、メイン弁口１１Ｃを閉じる向きの弾性力を主弁体１１に作用させる。以下、メイン弁口１１Ｃを開く向きの力を開弁力という。ばね１１Ｆの弾性力も含めてメイン弁口１１Ｃを閉じる向きの力を閉弁力という。 The fluid pressure in the main high pressure chamber 11A causes the main valve body 11 to act in a direction that opens the main valve port 11C. The fluid pressure in the main working chamber 11 </ b> D causes the main valve body 11 to have a force in a direction to close the main valve port 11 </ b> C. The spring 11F provided in the main working chamber 11D causes the main valve body 11 to act with an elastic force in a direction to close the main valve port 11C. Hereinafter, the force for opening the main valve port 11C is referred to as valve opening force. The force in the direction of closing the main valve port 11C including the elastic force of the spring 11F is referred to as valve closing force.
　主弁体１１において、主弁体１１がメイン高圧室１１Ａの作動流体から圧力を受ける面積は、主弁体１１がメイン作用室１１Ｄの作動流体から圧力を受ける面積より小さい。主弁体１１は、メイン高圧室１１Ａとメイン作用室１１Ｄとの圧力差に応じて作動する。 In the main valve body 11, the area where the main valve body 11 receives pressure from the working fluid in the main high pressure chamber 11A is smaller than the area where the main valve body 11 receives pressure from the working fluid in the main working chamber 11D. The main valve body 11 operates according to the pressure difference between the main high-pressure chamber 11A and the main working chamber 11D.
　メイン高圧室１１Ａとメイン作用室１１Ｄとが同一圧力であるときには、閉弁力が開弁力を上回り、メイン弁口１１Ｃは閉じた状態となる。第１パイロット流路Ｌ２を低圧側に繋ぐ流路Ｌ４が開かれて第１パイロット流路Ｌ２に流体流れが生じると、メイン作用室１１Ｄ内の圧力がメイン高圧室１１Ａ内の圧力より低下する。 When the main high pressure chamber 11A and the main working chamber 11D are at the same pressure, the valve closing force exceeds the valve opening force, and the main valve port 11C is closed. When the flow path L4 connecting the first pilot flow path L2 to the low pressure side is opened and a fluid flow is generated in the first pilot flow path L2, the pressure in the main working chamber 11D is lower than the pressure in the main high pressure chamber 11A.
　これによって閉弁力が開弁力を下回ると、メイン弁口１１Ｃが開く。第１パイロット流路Ｌ２を低圧側に繋ぐ流路Ｌ４が閉じられると、メイン作用室１１Ｄ内の圧力が上昇する。メイン作用室１１Ｄ内の圧力がメイン高圧室１１Ａ内の圧力と同じになると、メイン弁口１１Ｃは閉じる。流路Ｌ４は、Ｐ３、第１高圧室２１Ａを経由して第１パイロット流路Ｌ２を低圧側に繋ぐ流路である。 When this causes the valve closing force to fall below the valve opening force, the main valve port 11C opens. When the flow path L4 connecting the first pilot flow path L2 to the low pressure side is closed, the pressure in the main working chamber 11D increases. When the pressure in the main working chamber 11D becomes the same as the pressure in the main high pressure chamber 11A, the main valve port 11C is closed. The flow path L4 is a flow path that connects the first pilot flow path L2 to the low pressure side via P3 and the first high pressure chamber 21A.
　第１パイロット流路Ｌ２には、第１絞り部Ｒ１と直列に第２絞り部Ｒ２が設けられている。第２絞り部Ｒ２は、第１絞り部Ｒ１よりメイン作用室１１Ｄ側に設けられて第１パイロット流路Ｌ２の一部を絞る。このため、第１パイロット流路Ｌ２に流体流れが生じたときには、第２絞り部Ｒ２の前後においても圧力差が生じる。 In the first pilot flow path L2, a second throttle portion R2 is provided in series with the first throttle portion R1. The second throttle portion R2 is provided closer to the main working chamber 11D than the first throttle portion R1, and throttles a part of the first pilot flow path L2. For this reason, when a fluid flow occurs in the first pilot flow path L2, a pressure difference also occurs before and after the second throttle portion R2.
　第２絞り部Ｒ２は、絞り開度が調整自在な可変絞りである。このため、圧力制御弁１を管理等する者は、第２絞り部Ｒ２の絞り開度を調整できる。第２絞り部Ｒ２を迂回して第２絞り部Ｒ２の入口側Ｐ４と出口側Ｐ５とを繋ぐバイパス流路Ｌ３には、逆止弁１２が設けられている。 The second diaphragm portion R2 is a variable diaphragm whose throttle opening is adjustable. For this reason, the person who manages the pressure control valve 1 can adjust the throttle opening of the second throttle portion R2. A check valve 12 is provided in the bypass flow path L3 that bypasses the second throttle portion R2 and connects the inlet side P4 and the outlet side P5 of the second throttle portion R2.
　逆止弁１２は、メイン高圧室１１Ａ側からメイン作用室１１Ｄ側に作動流体が流通することを阻止し、メイン作用室１１Ｄ側からメイン高圧室１１Ａ側に作動流体が流通することを許容する。 The check valve 12 prevents the working fluid from flowing from the main high pressure chamber 11A side to the main working chamber 11D side, and allows the working fluid to flow from the main working chamber 11D side to the main high pressure chamber 11A side.
　本実施形態に係る第１パイロット流路Ｌ２には、逆止弁に相当する、流体の流通方向を制御するバルブ類は設けられていない。このため、第１パイロット流路Ｌ２においては、メイン高圧室１１Ａ側からメイン作用室１１Ｄ側に向かう流体流れ、及びメイン作用室１１Ｄ側からメイン高圧室１１Ａ側に向かう流体流れのいずれも生じ得る。 The first pilot flow path L2 according to the present embodiment is not provided with valves that control the flow direction of the fluid, which corresponds to a check valve. For this reason, in the first pilot flow path L2, both a fluid flow from the main high pressure chamber 11A side to the main action chamber 11D side and a fluid flow from the main action chamber 11D side to the main high pressure chamber 11A side can occur.
　１．２　第１バルブ
　第１バルブ２０は、第１パイロット流路Ｌ２を低圧側に繋ぐ流路Ｌ４を開閉する。本実施形態に係る第１バルブ２０の構造は、メインバルブ１０の構造と同様である。 1.2 First Valve The first valve 20 opens and closes a flow path L4 that connects the first pilot flow path L2 to the low pressure side. The structure of the first valve 20 according to the present embodiment is the same as the structure of the main valve 10.
　第１弁体２１は、流路Ｌ４を開閉する。第１バルブ２０のバルブボディ（図示せず。）には、第１高圧室２１Ａ、第１低圧室２１Ｂ、第１弁口２１Ｃ及び第１作用室２１Ｄ等が設けられている。 The first valve body 21 opens and closes the flow path L4. A valve body (not shown) of the first valve 20 is provided with a first high pressure chamber 21A, a first low pressure chamber 21B, a first valve port 21C, a first working chamber 21D, and the like.
　第１高圧室２１Ａは、第１弁体２１の移動方向一端側に設けられて高圧側に接続されている。第１低圧室２１Ｂは、低圧側に接続されている。第１高圧室２１Ａと第１低圧室２１Ｂとは、第１弁口２１Ｃを通して連通可能である。 The first high-pressure chamber 21A is provided on one end side in the moving direction of the first valve body 21 and is connected to the high-pressure side. The first low pressure chamber 21B is connected to the low pressure side. The first high pressure chamber 21A and the first low pressure chamber 21B can communicate with each other through the first valve port 21C.
　第１弁体２１は、第１弁口２１Ｃの外縁に設けられた弁座部２１Ｅに対して離間又は当接することにより、第１弁口２１Ｃを開閉する。つまり、第１弁体２１が弁座部２１Ｅから離間すると、第１弁口２１Ｃが開かれる。第１弁体２１が弁座部２１Ｅに当接すると第１弁口２１Ｃが閉じられる。 The first valve body 21 opens and closes the first valve port 21C by being separated from or in contact with a valve seat portion 21E provided at the outer edge of the first valve port 21C. That is, when the first valve body 21 is separated from the valve seat portion 21E, the first valve port 21C is opened. When the first valve body 21 contacts the valve seat portion 21E, the first valve port 21C is closed.
　第１作用室２１Ｄは、第１弁体２１の移動方向他端側に設けられ、かつ、第１弁体２１により第１低圧室２１Ｂと遮断されている。そして、第１バルブ２０のバルブボディには、第１高圧室２１Ａと第１作用室２１Ｄとを繋ぐ第２パイロット流路Ｌ５が設けられている。第２パイロット流路Ｌ５は、Ｐ６を経由して第１高圧室２１Ａと第１作用室２１Ｄとを繋ぐ。 The first working chamber 21D is provided on the other end side in the moving direction of the first valve body 21, and is shut off from the first low-pressure chamber 21B by the first valve body 21. The valve body of the first valve 20 is provided with a second pilot flow path L5 that connects the first high pressure chamber 21A and the first working chamber 21D. The second pilot flow path L5 connects the first high pressure chamber 21A and the first working chamber 21D via P6.
　第２パイロット流路Ｌ５には、第３絞り部Ｒ３が設けられている。第３絞り部Ｒ３は、第２パイロット流路Ｌ５の一部を絞った流体抵抗部である。第２パイロット流路Ｌ５に流体流れが生じたときに、第３絞り部Ｒ３の前後で圧力損失が発生し得る。第２パイロット流路Ｌ５に流体流れが生じると、第３絞り部Ｒ３の出口側圧力は、入口側圧力よりも低くなる。 The third pilot portion R3 is provided in the second pilot channel L5. The third restricting portion R3 is a fluid resistance portion that restricts a part of the second pilot flow path L5. When a fluid flow occurs in the second pilot flow path L5, pressure loss may occur before and after the third throttle portion R3. When a fluid flow is generated in the second pilot flow path L5, the outlet side pressure of the third throttle portion R3 becomes lower than the inlet side pressure.
　第１高圧室２１Ａの流体圧は、第１弁口２１Ｃを開く向きの力を第１弁体２１に作用させる。第１作用室２１Ｄの流体圧は、第１弁口２１Ｃを閉じる向きの力を第１弁体２１に作用させる。 The fluid pressure in the first high-pressure chamber 21A causes the first valve body 21 to have a force that opens the first valve port 21C. The fluid pressure in the first working chamber 21 </ b> D causes the first valve body 21 to have a force in a direction to close the first valve port 21 </ b> C.
　第１作用室２１Ｄ内に設けられたばね２１Ｆは、第１弁口２１Ｃを閉じる向きの弾性力を第１弁体２１に作用させる。以下、第１弁口２１Ｃを開く向きの力を開弁力という。ばね２１Ｆの弾性力を含む、第１弁口２１Ｃを閉じる向きの力を閉弁力という。 The spring 21F provided in the first working chamber 21D acts on the first valve body 21 with an elastic force in a direction to close the first valve port 21C. Hereinafter, the force that opens the first valve port 21C is referred to as valve opening force. A force for closing the first valve port 21C including the elastic force of the spring 21F is referred to as a valve closing force.
　第１弁体２１において、第１弁体２１が第１高圧室２１Ａの作動流体から圧力を受ける面積は、第１弁体２１が第１作用室２１Ｄの作動流体から圧力を受ける面積より小さい。第１弁体２１は、第１高圧室２１Ａと第１作用室２１Ｄとの圧力差に応じて作動する。 In the first valve body 21, the area where the first valve body 21 receives pressure from the working fluid in the first high pressure chamber 21A is smaller than the area where the first valve body 21 receives pressure from the working fluid in the first working chamber 21D. The first valve body 21 operates according to the pressure difference between the first high pressure chamber 21A and the first working chamber 21D.
　第１高圧室２１Ａと第１作用室２１Ｄとが同一圧力であるときには、閉弁力が開弁力を上回り、第１弁口２１Ｃは閉じた状態となる。第２パイロット流路Ｌ５を低圧側に繋ぐ第３パイロット流路Ｌ６が開かれて第２パイロット流路Ｌ５に流体流れが生じると、第１作用室２１Ｄ内の圧力が第１高圧室２１Ａ内の圧力より低下する。 When the first high pressure chamber 21A and the first working chamber 21D have the same pressure, the valve closing force exceeds the valve opening force, and the first valve port 21C is closed. When the third pilot flow path L6 connecting the second pilot flow path L5 to the low pressure side is opened and a fluid flow is generated in the second pilot flow path L5, the pressure in the first working chamber 21D is increased in the first high pressure chamber 21A. Lower than pressure.
　これによって閉弁力が開弁力を下回ると、第１弁口２１Ｃが開く。第３パイロット流路Ｌ６が閉じられると、第１作用室２１Ｄ内の圧力が上昇する。第１作用室２１Ｄ内の圧力が第１高圧室２１Ａ内の圧力と同じになると、第１弁口２１Ｃは閉じる。 When the valve closing force falls below the valve opening force, the first valve port 21C is opened. When the third pilot flow path L6 is closed, the pressure in the first working chamber 21D increases. When the pressure in the first working chamber 21D becomes the same as the pressure in the first high pressure chamber 21A, the first valve port 21C is closed.
　第２パイロット流路Ｌ５には、第３絞り部Ｒ３と直列に第４絞り部Ｒ４が設けられている。第４絞り部Ｒ４は、第３絞り部Ｒ３より第１作用室２１Ｄ側に設けられて第２パイロット流路Ｌ５の一部を絞る。このため、第２パイロット流路Ｌ５に流体流れが生じたときには、第４絞り部Ｒ４の前後においても圧力差が生じる。 The second pilot flow path L5 is provided with a fourth throttle portion R4 in series with the third throttle portion R3. The fourth throttle portion R4 is provided closer to the first working chamber 21D than the third throttle portion R3 and throttles a part of the second pilot flow path L5. For this reason, when a fluid flow occurs in the second pilot flow path L5, a pressure difference also occurs before and after the fourth throttle portion R4.
　１．３　第２バルブ
　第２バルブ３０は、第３パイロット流路Ｌ６を開閉する。具体的には、第２弁体３１は、第３パイロット流路Ｌ６を開閉する。第２バルブ３０のバルブボディ（図示せず。）には、第２高圧室３１Ａ、第２低圧室３１Ｂ及び第２弁口３１Ｃ等が設けられている。 1.3 Second Valve The second valve 30 opens and closes the third pilot flow path L6. Specifically, the second valve body 31 opens and closes the third pilot flow path L6. The valve body (not shown) of the second valve 30 is provided with a second high pressure chamber 31A, a second low pressure chamber 31B, a second valve port 31C, and the like.
　第２高圧室３１Ａは、第２高圧室３１Ａ内を移動可能なピストン部３１Ｄにより２つの空間Ａ、Ｂに仕切られている。ピストン部３１Ｄは、第２弁体３１と一体的に変位する。
　ピストン部３１Ｄの変位方向一端側の空間Ａには、高圧側の作動流体が導かれている。このため、空間Ａ内の流体圧は、第３パイロット流路Ｌ６を開く向きの力をピストン部３１Ｄに作用させる。空間Ａは、第２弁口３１Ｃが閉じられたときに、体積が略０となるような大きさであってもよい。 The second high pressure chamber 31A is partitioned into two spaces A and B by a piston portion 31D that can move in the second high pressure chamber 31A. The piston portion 31D is displaced integrally with the second valve body 31.
The working fluid on the high pressure side is guided to the space A on the one end side in the displacement direction of the piston portion 31D. For this reason, the fluid pressure in the space A causes a force to open the third pilot flow path L6 to act on the piston portion 31D. The space A may have a size such that the volume becomes substantially zero when the second valve port 31C is closed.
　ピストン部３１Ｄの変位方向他端側の空間Ｂには、第３パイロット流路Ｌ６を介して高圧側の作動流体が導かれている。このため、空間Ｂ内の流体圧は、第３パイロット流路Ｌ６を閉じる向きの力をピストン部３１Ｄに作用させると共に、開く向きの力を第２弁体３１の頭部に作用させ、第２弁体３１に平衡作用する。 The working fluid on the high pressure side is guided to the space B on the other end side in the displacement direction of the piston portion 31D through the third pilot flow path L6. For this reason, the fluid pressure in the space B causes the force in the direction of closing the third pilot flow path L6 to act on the piston portion 31D, and the force in the direction of opening to act on the head of the second valve body 31, and the second The valve body 31 is balanced.
　第２弁体３１において、第２弁体３１がピストン部３１Ｄを介して空間Ａの作動流体から圧力を受ける面積は、第２弁体３１がピストン部３１Ｄを介して空間Ｂの作動流体から圧力を受ける面積より大きい。 In the second valve body 31, the area where the second valve body 31 receives pressure from the working fluid in the space A through the piston portion 31D is the pressure from the working fluid in the space B through the piston portion 31D. Greater than the area you receive.
　高圧側Ｐからピストン部３１Ｄの変位方向他端側に至る流路、つまり、高圧側ＰからＰ１、Ｐ２、Ｐ３、Ｐ６を経由して空間Ｂに至る流路Ｌ７には、当該流路Ｌ７の一部を絞る絞り部として、第１絞り部Ｒ１及び第３絞り部Ｒ３等が設けられている。 The flow path from the high pressure side P to the other end side in the displacement direction of the piston portion 31D, that is, the flow path L7 from the high pressure side P to the space B via P1, P2, P3, P6, A first diaphragm portion R1, a third diaphragm portion R3, and the like are provided as a diaphragm portion that restricts a part.
　第２低圧室３１Ｂは、低圧側に接続され、第２弁口３１Ｃを通して第２高圧室３１Ａの空間Ｂと連通可能である。第２弁体３１は、第２弁口３１Ｃの外縁に設けられた弁座部３１Ｅに対して離間又は当接することにより、第２弁口３１Ｃを開閉する。 The second low pressure chamber 31B is connected to the low pressure side, and can communicate with the space B of the second high pressure chamber 31A through the second valve port 31C. The second valve body 31 opens or closes the second valve port 31C by being separated from or abutting against a valve seat portion 31E provided at the outer edge of the second valve port 31C.
　第２弁体３１が弁座部３１Ｅから離間すると、第２弁口３１Ｃが開かれる。第２弁体３１が弁座部３１Ｅに当接すると第２弁口３１Ｃが閉じられる。第２低圧室３１Ｂ内に設けられたばね３１Ｆは、第２弁口３１Ｃを閉じる向きの弾性力を第２弁体３１に作用させる。 When the second valve body 31 is separated from the valve seat portion 31E, the second valve port 31C is opened. When the second valve body 31 comes into contact with the valve seat portion 31E, the second valve port 31C is closed. The spring 31F provided in the second low-pressure chamber 31B causes the second valve body 31 to exert an elastic force in a direction to close the second valve port 31C.
　第２弁口３１Ｃを開く向きの力、つまり空間Ａに作用する流体圧による力（以下、開弁力という。）が、ばね３１Ｆの弾性力（以下、閉弁力という。）より大きくなると、第２弁口３１Ｃが開く。ばね３１Ｆの弾性力を変更すると、第２弁口３１Ｃが開く圧力（以下、この圧力をリリーフ圧という。）を変更できる。 When the force for opening the second valve port 31C, that is, the force due to the fluid pressure acting on the space A (hereinafter referred to as valve opening force) becomes larger than the elastic force of the spring 31F (hereinafter referred to as valve closing force), The second valve port 31C is opened. When the elastic force of the spring 31F is changed, the pressure at which the second valve port 31C opens (hereinafter, this pressure is referred to as relief pressure) can be changed.
　高圧側Ｐの圧力がリリーフ圧より大きくなると、第３パイロット流路Ｌ６が開く。このため、上述したように、第１弁口２１Ｃが開くため、流路Ｌ４が開き、メイン弁口１１Ｃが開く。 When the pressure on the high pressure side P becomes higher than the relief pressure, the third pilot flow path L6 opens. Therefore, as described above, since the first valve port 21C is opened, the flow path L4 is opened and the main valve port 11C is opened.
　本実施形態では、第１高圧室２１Ａと高圧側Ｐとを繋ぐ高圧供給流路、つまり高圧側ＰからＰ１、Ｐ２、Ｐ３を経由して第１高圧室２１Ａに至る流路の一部と第１パイロット流路Ｌ２の一部とは共通化されている。そして、第１絞り部Ｒ１は、第１パイロット流路Ｌ２のうち高圧供給流路と共通化された部位に設けられている。 In the present embodiment, a part of the high-pressure supply flow path connecting the first high-pressure chamber 21A and the high-pressure side P, that is, a part of the flow path from the high-pressure side P to the first high-pressure chamber 21A via P1, P2, P3 and the first high-pressure chamber. A part of one pilot flow path L2 is shared. And 1st aperture | diaphragm | squeeze part R1 is provided in the site | part shared with the high voltage | pressure supply flow path among the 1st pilot flow paths L2.
　２．本実施形態に係る圧力制御弁の特徴
　本実施形態では、第１パイロット流路Ｌ２に流れる作動流体を第１絞り部Ｒ１で流量制御可能である。作動流体は、第１パイロット流路Ｌ２において、メイン高圧室１１Ａ側からメイン作用室１１Ｄ側に向かって流れることができ、及びメイン作用室１１Ｄ側からメイン高圧室１１Ａ側に向かって流れることができるので、メインバルブ１０にてチャタリングが発生することを抑制できる。 2. Features of Pressure Control Valve According to this Embodiment In this embodiment, the flow rate of the working fluid flowing through the first pilot flow path L2 can be controlled by the first throttle portion R1. In the first pilot flow path L2, the working fluid can flow from the main high pressure chamber 11A side to the main working chamber 11D side, and can flow from the main working chamber 11D side to the main high pressure chamber 11A side. Therefore, chattering can be prevented from occurring in the main valve 10.
　本実施形態では、第１パイロット流路Ｌ２には、第１パイロット流路Ｌ２の一部を絞る第２絞り部Ｒ２が設けられていることを特徴とする。これにより、メインバルブ１０にてチャタリングが発生することを更に抑制できる。 In the present embodiment, the first pilot channel L2 is provided with a second throttle part R2 that throttles a part of the first pilot channel L2. As a result, the occurrence of chattering in the main valve 10 can be further suppressed.
　本実施形態では、第２絞り部Ｒ２は、絞り開度が調整自在な可変絞りであることを特徴とする。これにより、第１パイロット流路Ｌ２を流通する流量を容易に最適化できる。延いては、様々な仕様に容易に対応できる。 In the present embodiment, the second diaphragm portion R2 is a variable diaphragm whose throttle opening is adjustable. Thereby, the flow volume which distribute | circulates the 1st pilot flow path L2 can be optimized easily. As a result, it can easily cope with various specifications.
　本実施形態では、第２絞り部Ｒ２を迂回するバイパス流路Ｌ３に、メイン高圧室１１Ａ側からメイン作用室１１Ｄ側に作動流体が流通することを阻止する逆止弁１２が設けられていることを特徴とする。これにより、メイン流路Ｌ１が開くときに、メイン作用室１１Ｄ内の作動流体を迅速に排出できるので、主弁体１１の応答性を向上させることができる。 In the present embodiment, a check valve 12 that prevents the working fluid from flowing from the main high pressure chamber 11A side to the main working chamber 11D side is provided in the bypass flow path L3 that bypasses the second throttle portion R2. It is characterized by. Thereby, when the main flow path L1 opens, the working fluid in the main working chamber 11D can be quickly discharged, so that the responsiveness of the main valve body 11 can be improved.
　本実施形態では、ピストン部３１Ｄの変位方向一端側には、高圧側Ｐの作動流体が導かれて第３パイロット流路を開く向きの力が作用している。ピストン部３１Ｄの変位方向他端側には、第３パイロット流路Ｌ６を介して高圧側の作動流体が導かれている。そして、高圧側からピストン部３１Ｄの変位方向他端側に至る流路には、当該流路の一部を絞る絞り部として、第１絞り部Ｒ１及び第３絞り部Ｒ３が設けられていることを特徴とする。 In the present embodiment, the working fluid on the high-pressure side P is guided to the one end side in the displacement direction of the piston portion 31D to act to open the third pilot flow path. The working fluid on the high pressure side is guided to the other end side in the displacement direction of the piston portion 31D via the third pilot flow path L6. And in the flow path from the high pressure side to the other end side in the displacement direction of the piston part 31D, the first throttle part R1 and the third throttle part R3 are provided as throttle parts that throttle down a part of the flow path. It is characterized by.
　これにより、本実施形態では、チャタリングの発生を抑制しつつ、第２バルブ３０において、高圧側Ｐの作動流体が直接的に低圧側（タンクＴ）に流通しないので、圧力制御弁１のオーバライド特性を向上させることができる。 Thereby, in this embodiment, since the working fluid on the high pressure side P does not flow directly to the low pressure side (tank T) in the second valve 30 while suppressing the occurrence of chattering, the override characteristic of the pressure control valve 1 Can be improved.
　（第２実施形態）
　本実施形態は、図２に示すように、第１実施形態と比較して第１絞り部Ｒ１の位置が異なっている。具体的には、本実施形態では、第２バルブ３０の空間Ａに供給される作動流体も第１絞り部Ｒ１により減圧される構成とされている。 (Second Embodiment)
As shown in FIG. 2, the present embodiment differs from the first embodiment in the position of the first aperture portion R1. Specifically, in the present embodiment, the working fluid supplied to the space A of the second valve 30 is also decompressed by the first throttle portion R1.
　（第３実施形態）
　本実施形態は、図３に示すように、以下の特徴を有する。
（ａ）第１バルブ２０の第１高圧室２１Ａが、第１実施形態に係る第２バルブ３０と同様に、ピストン部２１Ｇにより２つの空間Ａ、Ｂに仕切られる。
（ｂ）第２バルブ３０が、ばね３１Ｆの弾性力のみで高圧側Ｐの圧力に対向する、いわゆる直動式のポペット弁として構成される。 (Third embodiment)
As shown in FIG. 3, the present embodiment has the following features.
(A) The first high pressure chamber 21A of the first valve 20 is partitioned into two spaces A and B by the piston portion 21G, similarly to the second valve 30 according to the first embodiment.
(B) The second valve 30 is configured as a so-called direct-acting poppet valve that opposes the pressure on the high-pressure side P only by the elastic force of the spring 31F.
　ピストン部２１Ｇの変位方向一端側の空間Ａには、高圧側の作動流体が導かれている。このため、空間Ａ内の作動流体圧は、第１パイロット流路Ｌ２を開く向きの力をピストン部２１Ｇに作用させる。空間Ａは、第１弁口２１Ｃが閉じられたときに、体積が略０となるような大きさであってもよい。 The working fluid on the high pressure side is guided to the space A on the one end side in the displacement direction of the piston portion 21G. For this reason, the working fluid pressure in the space A causes the piston portion 21G to exert a force in a direction to open the first pilot flow path L2. The space A may have a size such that the volume becomes substantially zero when the first valve port 21C is closed.
　ピストン部２１Ｇの変位方向他端側の空間Ｂには、第１パイロット流路Ｌ２を介して高圧側の作動流体が導かれている。このため、空間Ｂ内の作動流体圧は、第１パイロット流路Ｌ２を閉じる向きの力をピストン部２１Ｇに作用させると共に、開く向きの力を第１弁体２１の頭部に作用させ、第１弁体２１に平衡作用する。 The working fluid on the high pressure side is guided to the space B on the other end side in the displacement direction of the piston portion 21G via the first pilot flow path L2. For this reason, the working fluid pressure in the space B causes the force in the direction of closing the first pilot flow path L2 to act on the piston portion 21G, and the force in the direction of opening to act on the head of the first valve body 21, One valve body 21 is balanced.
　第１弁体２１において、第１弁体２１がピストン部２１Ｇを介して空間Ａの作動流体から圧力を受ける面積は、第１弁体２１がピストン部２１Ｇを介して空間Ｂの作動流体から圧力を受ける面積より大きい。 In the first valve body 21, the area where the first valve body 21 receives pressure from the working fluid in the space A through the piston portion 21G is the pressure from the working fluid in the space B through the piston portion 21G. Greater than the area you receive.
　（その他の実施形態）
　上述の実施形態に係る第２バルブ３０は、ばねの弾性力を調整することによってリリーフ圧を変更する方式であったが、本発明はこれに限定されるものではない。例えば、ソレノイドコイルを利用した電磁力により、上記ばねの弾性力に相当する力を発生させるとともに、当該電磁力を調整することによってリリーフ圧を変更する方式であってもよい。 (Other embodiments)
Although the 2nd valve 30 concerning the above-mentioned embodiment was a system which changes relief pressure by adjusting the elastic force of a spring, the present invention is not limited to this. For example, a system may be used in which a force corresponding to the elastic force of the spring is generated by an electromagnetic force using a solenoid coil, and the relief pressure is changed by adjusting the electromagnetic force.
　上述の実施形態では、特許請求の範囲に記載された絞り部は、第１絞り部Ｒ１及び第３絞り部Ｒ３により構成されていたが、本発明はこれに限定されるものではない。
　本発明は、特許請求の範囲に記載された発明の趣旨に合致するものであればよく、上述の実施形態に限定されるものではない。つまり、上述の実施形態に示された圧力制御弁に限定されるものではなく、上述の第１～第３実施形態に示された構成を適宜組み合わせてもよい。 In the above-described embodiment, the diaphragm described in the claims is configured by the first diaphragm R1 and the third diaphragm R3, but the present invention is not limited to this.
The present invention is not limited to the above-described embodiment as long as it matches the gist of the invention described in the claims. That is, the configuration is not limited to the pressure control valve shown in the above-described embodiment, and the configurations shown in the above-described first to third embodiments may be appropriately combined.

Claims (6)

  1. 　パイロット操作方式の圧力制御弁において、
    　メイン流路を開閉する主弁体を有するメインバルブであって、前記主弁体の移動方向一端側に設けられたメイン高圧室、前記主弁体の移動方向他端側に設けられたメイン作用室、及び前記メイン高圧室と前記メイン作用室とを繋ぐ第１パイロット流路を有し、かつ、前記メイン高圧室と前記メイン作用室との圧力差に応じて前記主弁体が作動するメインバルブと、
    　前記第１パイロット流路を低圧側に繋ぐ流路を開閉する第１弁体を有する第１バルブであって、前記第１弁体の移動方向一端側に設けられた第１高圧室、前記第１弁体の移動方向他端側に設けられた第１作用室、及び前記第１高圧室と前記第１作用室とを繋ぐ第２パイロット流路を有し、かつ、前記第１高圧室と前記第１作用室との圧力差に応じて前記第１弁体が作動する第１バルブと、
    　前記第２パイロット流路を低圧側に繋ぐ第３パイロット流路を開閉する第２弁体を有する第２バルブであって、当該第３パイロット流路を開く向きの高圧側流体圧が前記第２弁体に作用する第２バルブと、
    　前記第１パイロット流路に設けられた第１絞り部であって、前記第１パイロット流路の一部を絞る第１絞り部とを備え、
    　前記第１パイロット流路は、前記メイン高圧室側から前記メイン作用室側に向かう流体流れ、及び前記メイン作用室側から前記メイン高圧室側に向かう流体流れのいずれも許容することを特徴とする圧力制御弁。     In the pilot operated pressure control valve,
    A main valve having a main valve body for opening and closing a main flow path, a main high pressure chamber provided on one end side in the moving direction of the main valve body, and a main action provided on the other end side in the moving direction of the main valve body A main pilot body that has a first pilot flow path connecting the main high pressure chamber and the main working chamber, and the main valve element operates in accordance with a pressure difference between the main high pressure chamber and the main working chamber. A valve,
    A first valve having a first valve body that opens and closes a flow path connecting the first pilot flow path to a low pressure side, the first high pressure chamber provided on one end side in the moving direction of the first valve body; A first working chamber provided on the other end side of the one valve body in the moving direction; a second pilot flow path connecting the first high pressure chamber and the first working chamber; and the first high pressure chamber A first valve that operates the first valve body in accordance with a pressure difference with the first working chamber;
    A second valve having a second valve body that opens and closes a third pilot flow path connecting the second pilot flow path to the low pressure side, wherein the high pressure side fluid pressure in the direction of opening the third pilot flow path is the second valve. A second valve acting on the valve body;
    A first throttle part provided in the first pilot channel, the first throttle part throttles a part of the first pilot channel,
    The first pilot flow path allows both a fluid flow from the main high pressure chamber side to the main working chamber side and a fluid flow from the main working chamber side to the main high pressure chamber side. Pressure control valve.
  2. 　前記第１パイロット流路には、前記第１パイロット流路の一部を絞る第２絞り部が設けられていることを特徴とする請求項１に記載の圧力制御弁。 2. The pressure control valve according to claim 1, wherein the first pilot flow path is provided with a second throttle portion that throttles a part of the first pilot flow path.
  3. 　前記第２絞り部は、絞り開度が調整自在な可変絞りであることを特徴とする請求項２に記載の圧力制御弁。 The pressure control valve according to claim 2, wherein the second throttle part is a variable throttle whose throttle opening is adjustable.
  4. 　前記第２絞り部を迂回して前記第２絞り部の入口側と出口側とを繋ぐバイパス流路に設けられた逆止弁であって、前記メイン高圧室側から前記メイン作用室側に流体が流通することを阻止する逆止弁を備えることを特徴とする請求項２又は３に記載の圧力制御弁。 A check valve provided in a bypass flow path that bypasses the second restrictor and connects the inlet side and the outlet side of the second restrictor, the fluid flowing from the main high pressure chamber side to the main working chamber side The pressure control valve according to claim 2, further comprising a check valve that prevents the gas from flowing.
  5. 　前記第１高圧室と高圧側とを繋ぐ高圧供給流路の一部と前記第１パイロット流路の一部とは共通化されており、
    　前記第１絞り部は、前記第１パイロット流路のうち前記高圧供給流路と共通化された部位に設けられていることを特徴とする請求項１ないし４のいずれか１項に記載の圧力制御弁。     A part of the high-pressure supply flow path connecting the first high-pressure chamber and the high-pressure side and a part of the first pilot flow path are shared.
    5. The pressure according to claim 1, wherein the first throttle portion is provided in a portion of the first pilot flow path that is shared with the high pressure supply flow path. Control valve.
  6. 　前記第２バルブは、前記第２弁体と一体的に変位するピストン部を有し、
    　前記ピストン部の変位方向一端側には、高圧側の流体が導かれて前記第３パイロット流路を開く向きの力が作用し、
    　前記ピストン部の変位方向他端側には、前記第３パイロット流路を介して高圧側の流体が導かれ、
    　さらに、高圧側から前記ピストン部の変位方向他端側に至る流路には、当該流路の一部を絞る絞り部が設けられていることを特徴とする請求項５に記載の圧力制御弁。     The second valve has a piston portion that is integrally displaced with the second valve body,
    On the one end side in the displacement direction of the piston portion, a high-pressure fluid is guided to open the third pilot flow path,
    The high pressure side fluid is guided to the other end side in the displacement direction of the piston part via the third pilot flow path,
    The pressure control valve according to claim 5, further comprising: a throttle portion that throttles a part of the flow path from the high pressure side to the other end side in the displacement direction of the piston portion. .
PCT/JP2014/054891 2013-03-07 2014-02-27 Pressure control valve WO2014136649A1 (en)

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CN105805073A (en) * 2016-05-29 2016-07-27 浙江大学 Cartridge overflow valve main valve with directional damper
EP3377738A4 (en) * 2015-11-19 2019-08-28 Wärtsilä Finland Oy Pressure regulating arrangement and method

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JPS5738901U (en) * 1980-08-16 1982-03-02
JPS58173855U (en) * 1982-05-18 1983-11-21 ヤンマーディーゼル株式会社 Hydraulic control device for hydraulic reduction/reversing machine

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JP2815964B2 (en) * 1990-03-15 1998-10-27 石川島播磨重工業株式会社 Relief valve device

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JPS5172726A (en) * 1974-12-20 1976-06-23 Toyooki Kogyo Kk ATSURYOKUS EIGYOBEN
JPS5738901U (en) * 1980-08-16 1982-03-02
JPS58173855U (en) * 1982-05-18 1983-11-21 ヤンマーディーゼル株式会社 Hydraulic control device for hydraulic reduction/reversing machine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3377738A4 (en) * 2015-11-19 2019-08-28 Wärtsilä Finland Oy Pressure regulating arrangement and method
CN105805073A (en) * 2016-05-29 2016-07-27 浙江大学 Cartridge overflow valve main valve with directional damper
CN105805073B (en) * 2016-05-29 2017-08-25 浙江大学 A kind of plug-in overflow valve main valve that there is orientation to damp

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