WO2014136649A1 - Soupape de réglage de pression - Google Patents

Soupape de réglage de pression 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
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English (en)
Japanese (ja)
Inventor
加藤　靖丈
高史 山口
Original Assignee
豊興工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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/fr

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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

La présente invention concerne une soupape de réglage de pression actionnée par un pilote pourvue d'une soupape principale, d'une première soupape et d'une première section papillon des gaz. La soupape principale présente : un corps de soupape principale qui ouvre et ferme un passage d'écoulement principal ; une chambre à haute pression principale qui est disposée sur un côté d'extrémité de la soupape principale dans sa direction de mouvement ; une chambre d'action principale qui est disposée sur l'autre côté d'extrémité du corps de soupape principale dans sa direction de mouvement ; et un premier passage d'écoulement pilote qui raccorde la chambre à haute pression principale à la chambre d'action principale. Le premier passage d'écoulement pilote permet un écoulement de fluide du côté de la chambre à haute pression principale au côté de la chambre d'action principale et un écoulement de fluide du côté de la chambre d'action principale au côté de la chambre à haute pression principale.
PCT/JP2014/054891 2013-03-07 2014-02-27 Soupape de réglage de pression WO2014136649A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013045548A JP6068203B2 (ja) 2013-03-07 2013-03-07 圧力制御弁
JP2013-045548 2013-03-07

Publications (1)

Publication Number Publication Date
WO2014136649A1 true WO2014136649A1 (fr) 2014-09-12

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JP (1) JP6068203B2 (fr)
WO (1) WO2014136649A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105805073A (zh) * 2016-05-29 2016-07-27 浙江大学 一种具有定向阻尼的插装式溢流阀主阀
EP3377738A4 (fr) * 2015-11-19 2019-08-28 Wärtsilä Finland Oy Agencement et procédé de régulation de pression

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5172726A (ja) * 1974-12-20 1976-06-23 Toyooki Kogyo Kk Atsuryokuseigyoben
JPS5738901U (fr) * 1980-08-16 1982-03-02
JPS58173855U (ja) * 1982-05-18 1983-11-21 ヤンマーディーゼル株式会社 油圧式減速逆転機の油圧制御装置

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2815964B2 (ja) * 1990-03-15 1998-10-27 石川島播磨重工業株式会社 逃し弁装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5172726A (ja) * 1974-12-20 1976-06-23 Toyooki Kogyo Kk Atsuryokuseigyoben
JPS5738901U (fr) * 1980-08-16 1982-03-02
JPS58173855U (ja) * 1982-05-18 1983-11-21 ヤンマーディーゼル株式会社 油圧式減速逆転機の油圧制御装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3377738A4 (fr) * 2015-11-19 2019-08-28 Wärtsilä Finland Oy Agencement et procédé de régulation de pression
CN105805073A (zh) * 2016-05-29 2016-07-27 浙江大学 一种具有定向阻尼的插装式溢流阀主阀
CN105805073B (zh) * 2016-05-29 2017-08-25 浙江大学 一种具有定向阻尼的插装式溢流阀主阀

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JP6068203B2 (ja) 2017-01-25
JP2014173644A (ja) 2014-09-22

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