WO2020161862A1 - Soupape régulatrice de pression - Google Patents

Soupape régulatrice de pression Download PDF

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Publication number
WO2020161862A1
WO2020161862A1 PCT/JP2019/004438 JP2019004438W WO2020161862A1 WO 2020161862 A1 WO2020161862 A1 WO 2020161862A1 JP 2019004438 W JP2019004438 W JP 2019004438W WO 2020161862 A1 WO2020161862 A1 WO 2020161862A1
Authority
WO
WIPO (PCT)
Prior art keywords
relief valve
pilot relief
seat member
pressure
balance piston
Prior art date
Application number
PCT/JP2019/004438
Other languages
English (en)
Japanese (ja)
Inventor
涼太 筒井
Original Assignee
株式会社島津製作所
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 株式会社島津製作所 filed Critical 株式会社島津製作所
Priority to PCT/JP2019/004438 priority Critical patent/WO2020161862A1/fr
Priority to JP2020570293A priority patent/JP7078140B2/ja
Publication of WO2020161862A1 publication Critical patent/WO2020161862A1/fr

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Classifications

    • 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
    • F16K17/06—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 special arrangements for adjusting the opening 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise

Definitions

  • the present invention relates to a pressure control valve used as a relief valve.
  • FIG. 5 is a sectional view of a conventional pressure control valve used as a relief valve. Note that FIG. 5 shows a state in which the pressure control valve is mounted on the housing 100 of the control valve or the like.
  • the conventional pressure control valve shown in FIG. 5 allows the hydraulic fluid in the housing 100 to flow out from the high pressure line 20 to the low pressure line 30 when the pressure of the hydraulic fluid in the high pressure line 20 exceeds a certain level. This is to prevent the pressure of above from exceeding a certain level.
  • This pressure control valve has a balance piston type configuration including a sleeve 10 supported by a valve body 7 and a balance piston 8 slidably arranged in the sleeve 10 with respect to the sleeve 10. There is.
  • the balance piston 8 is biased by a spring 9 as a biasing means in a direction in which the end portion on the high pressure line 20 side comes into contact with the valve seat region formed on the sleeve 10.
  • the balance piston 8 is formed with an orifice 8c that connects the high pressure line 20 and the intermediate chamber 11 inside the balance piston 8.
  • the pressure of the hydraulic fluid acting on the upstream surface (the surface on the high pressure line 20 side) 8a of the balance piston 8 is the sum of the pressure acting on the downstream surface (the surface on the low pressure line 30 side) 8b and the urging force of the spring 9.
  • the balance piston 8 slides in the sleeve 10 and separates from the valve seat area in the sleeve 10. As a result, the passage of the hydraulic fluid from the high pressure line 20 to the low pressure line 30 is opened, and the surplus hydraulic fluid of the high pressure line 20 is caused to flow out to the low pressure line 30, thereby ensuring the maximum pressure of the hydraulic fluid in the housing 100. There is.
  • This balance piston 8 moves by a pilot method. That is, the pilot relief valve 1 is disposed downstream of the balance piston 8 in order to control the flow rate of the balance piston 8 passing through the orifice 8c.
  • the pilot relief valve 1 is biased by the action of the spring 2 toward the valve seat surface of the seat member 3 arranged at one end of the sleeve 10.
  • the urging force of the pilot relief valve 1 on the seat member 3 can be adjusted by the pressure adjusting screw 6.
  • the pilot relief valve 1 separates from the valve seat surface of the seat member 3, and the intermediate chamber
  • the hydraulic fluid in 11 is discharged to the low pressure line 30.
  • the hydraulic fluid passes through the orifice 8c of the balance piston 8 and a pressure difference is generated between the upstream surface 8a and the downstream surface 8b of the balance piston 8, so that the balance piston 8 opens.
  • Patent Document 1 The pressure control valve having the above configuration is disclosed as a conventional technique in Patent Document 1.
  • a damper is formed between the balance piston 8 and the seat member 3 in order to prevent fluttering (chattering) occurring in the balance piston 8.
  • the opening area between the pilot relief valve 1 and the seat member 3 becomes small, so that the hydraulic pressure in the intermediate chamber 11 rises again.
  • the oscillation of the pilot relief valve 1 due to the repetition of such operations is called fluttering (chattering), and the fluttering causes vibration and noise in the pressure control valve.
  • FIG. 6 is a cross-sectional view of an improved pressure control valve used as a relief valve. Note that FIG. 6 shows a state in which the pressure control valve is mounted on the housing 100 of the control valve or the like.
  • the damping chamber 12 is formed in the seat member 4, and the orifice 4a that connects the damping chamber 12 and the intermediate chamber 11 of the balance piston 8 is formed.
  • the damping force is applied to the pilot relief valve 1.
  • this damping force it is possible to suppress overlap due to inertia in the pilot relief valve 1 and suppress the occurrence of fluttering.
  • the present invention has been made to solve the above problems, and an object thereof is to provide a pressure control valve capable of suppressing the generation of noise and vibration.
  • a balance piston type pressure control valve in a balance piston type pressure control valve, an orifice communicating with a high pressure line is formed, a balance piston having an intermediate chamber therein, and a valve seat abutting the balance piston are provided.
  • a sleeve member that slidably accommodates a balance piston, a pilot relief valve for controlling the flow of hydraulic fluid from an orifice in the balance piston into the intermediate chamber, and a seat member that includes a valve seat that abuts the pilot relief valve.
  • a damping chamber is formed between the pilot relief valve and the seat member, and an orifice is formed to connect the intermediate chamber and the damping chamber, and the orifice is separated from the position where the seat member comes into contact with the seat member.
  • a cap member movable between the positions.
  • FIG. 6 is a cross-sectional view of an improved pressure control valve used as a relief valve.
  • 1 to 4 are sectional views showing the pressure control operation in the pressure control valve according to the present invention. 1 to 4 show a state in which the pressure control valve is mounted on the housing 100 of the control valve or the like.
  • This pressure control valve is, for example, a control valve that uses hydraulic oil as the hydraulic fluid mounted on a forklift or the like, and when the pressure of the hydraulic fluid in the high pressure line 20 reaches a certain level or higher, the hydraulic fluid is removed from the high pressure line 20. This is to prevent the pressure of the hydraulic fluid in the housing 100 from exceeding a certain level by causing the hydraulic fluid to flow out to the low pressure line 30.
  • This pressure control valve includes a sleeve 10 as a valve housing body supported by the valve body 7, and a balance piston 8 as a main valve body slidably arranged in the sleeve 10 with respect to the sleeve 10. It has a balanced piston type configuration.
  • the balance piston 8 is biased by a spring 9 as a biasing means in a direction in which the end portion on the high pressure line 20 side comes into contact with the valve seat region formed on the sleeve 10.
  • the balance piston 8 is formed with an orifice 8c that connects the high pressure line 20 and the intermediate chamber 11 inside the balance piston 8.
  • the pressure of the hydraulic fluid acting on the upstream surface (the surface on the high pressure line 20 side) 8a of the balance piston 8 is the sum of the pressure acting on the downstream surface (the surface on the low pressure line 30 side) 8b and the urging force of the spring 9.
  • the balance piston 8 slides in the sleeve 10 and separates from the valve seat area in the sleeve 10. As a result, the passage of the hydraulic fluid from the high pressure line 20 to the low pressure line 30 is opened, and the surplus hydraulic fluid of the high pressure line 20 is caused to flow out to the low pressure line 30, thereby ensuring the maximum pressure of the hydraulic fluid in the housing 100. There is.
  • This balance piston 8 moves by a pilot method. That is, the pilot relief valve 1 is disposed downstream of the balance piston 8 in order to control the flow rate of the balance piston 8 passing through the orifice 8c.
  • the pilot relief valve 1 is biased by the action of the spring 2 toward the valve seat surface of the seat member 3 arranged at one end of the sleeve 10.
  • the urging force of the pilot relief valve 1 on the seat member 3 can be adjusted by the pressure adjusting screw 6.
  • the pilot relief valve 1 separates from the valve seat surface of the seat member 3, and the intermediate chamber
  • the hydraulic fluid in 11 is discharged to the low pressure line 30.
  • the hydraulic fluid passes through the orifice 8c of the balance piston 8 and a pressure difference is generated between the upstream surface 8a and the downstream surface 8b of the balance piston 8, so that the balance piston 8 opens.
  • a cap member 5 is arranged between the seat member 3 and the balance piston 8.
  • the cap member 5 forms a damping chamber 12 between the pilot relief valve 1 and the seat member 3 when the cap member 5 is in contact with the seat member 3. That is, when the cap member 5 and the seat member 3 come into contact with each other, the damping chamber 12 is formed by the cap member 5, the pilot relief valve 1, and the seat member 3, as shown in FIG. In this state, a slight gap is formed between the cap member 5 and the pilot relief valve 1.
  • the cap member 5 is formed with an orifice 5a that connects the intermediate chamber 11 of the balance piston 8 and the damping chamber 12 to each other.
  • the cap member 5 is biased in the direction of the seat member 3 by a spring 9 and is movable between a position in contact with the seat member 3 and a position in which it is separated from the seat member 3.
  • the pressure of the hydraulic fluid in the high pressure line 20 further rises, the opening degree of the pilot relief valve 1 becomes a certain amount or more, and the pressure of the hydraulic fluid acting on the upstream surface (the surface on the high pressure line 20 side) 8a of the balance piston 8 is increased.
  • the pressure acting on the downstream surface (the surface on the low-pressure line 30 side) 8b exceeds the total value of the urging force of the spring 9, the balance piston 8 slides in the sleeve 10 as shown in FIG. Away from the valve seat area at.
  • the pilot relief valve 1 moves toward the seat member 3 and eventually the pilot relief valve 1 and the seat member 3 come into contact with each other as shown in FIG.
  • the hydraulic pressure of the hydraulic fluid in the damping chamber 12 formed by the cap member 5, the pilot relief valve 1, and the seat member 3 increases.
  • the cap member 5 is separated from the sheet member 3 as shown in FIG. Therefore, the intermediate chamber 11 and the damping chamber 12 have the same pressure, and the damping effect on the pilot relief valve 1 is lost. Therefore, the pilot relief valve 1 quickly moves to a position where it comes into contact with the seat member 3 without receiving resistance.
  • the pilot relief valve 1 when the pilot relief valve 1 moves in the direction away from the seat member 3, the pilot relief valve 1 is operated by the action of the damping chamber 12 and the orifice 5a in the cap member 5.
  • the cap member 5 When the pilot relief valve 1 moves in the direction of approaching the seat member 3, the cap member 5 is separated from the seat member 3 to prevent deterioration of responsiveness of the pilot relief valve 1. it can. This makes it possible to suppress the generation of noise and vibration in the pressure control valve.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)
  • Details Of Valves (AREA)

Abstract

Dans la présente invention, une chambre d'amortissement (12) est formée par un élément bouchon (5), une soupape de décharge pilote (1) et un élément siège (3). Du fait de l'action de la chambre d'amortissement (12) et d'un orifice (5a), une force d'amortissement agit contre la soupape de décharge pilote (1) lorsque la soupape de décharge pilote (1) s'éloigne de l'élément siège (3). Pendant ce temps, lorsque la soupape de décharge pilote (1) se déplace vers l'élément siège (3), la pression d'un fluide hydraulique dans la chambre d'amortissement (12) augmente et amène l'élément bouchon (5) à s'éloigner de l'élément siège (3). Par conséquent, la pression dans une chambre intermédiaire (11) et la pression dans la chambre d'amortissement (12) deviennent identiques, et l'effet d'amortissement par rapport à la soupape de décharge pilote (1) n'existe plus. Par conséquent, sans provoquer de résistance, la soupape de décharge pilote (1) se déplace rapidement jusqu'à atteindre une position où elle entre en contact avec l'élément siège (3).
PCT/JP2019/004438 2019-02-07 2019-02-07 Soupape régulatrice de pression WO2020161862A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2019/004438 WO2020161862A1 (fr) 2019-02-07 2019-02-07 Soupape régulatrice de pression
JP2020570293A JP7078140B2 (ja) 2019-02-07 2019-02-07 圧力制御弁

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/004438 WO2020161862A1 (fr) 2019-02-07 2019-02-07 Soupape régulatrice de pression

Publications (1)

Publication Number Publication Date
WO2020161862A1 true WO2020161862A1 (fr) 2020-08-13

Family

ID=71947709

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/004438 WO2020161862A1 (fr) 2019-02-07 2019-02-07 Soupape régulatrice de pression

Country Status (2)

Country Link
JP (1) JP7078140B2 (fr)
WO (1) WO2020161862A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62167977U (fr) * 1986-04-14 1987-10-24
JP2005240993A (ja) * 2004-02-25 2005-09-08 Volvo Construction Equipment Holding Sweden Ab パイロット作動型リリーフバルブ
US20160326721A1 (en) * 2013-12-26 2016-11-10 Doosan Infracore Co., Ltd. Pressure peak reduction valve for excavator and pressure peak reduction system for excavator comprising same
WO2017046955A1 (fr) * 2015-09-18 2017-03-23 株式会社 島津製作所 Soupape de régulation de pression

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20080015653A (ko) * 2006-08-16 2008-02-20 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 압력제어밸브
JP6655928B2 (ja) * 2015-09-28 2020-03-04 ナブテスコ株式会社 リリーフ弁

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62167977U (fr) * 1986-04-14 1987-10-24
JP2005240993A (ja) * 2004-02-25 2005-09-08 Volvo Construction Equipment Holding Sweden Ab パイロット作動型リリーフバルブ
US20160326721A1 (en) * 2013-12-26 2016-11-10 Doosan Infracore Co., Ltd. Pressure peak reduction valve for excavator and pressure peak reduction system for excavator comprising same
WO2017046955A1 (fr) * 2015-09-18 2017-03-23 株式会社 島津製作所 Soupape de régulation de pression

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JPWO2020161862A1 (ja) 2021-10-07
JP7078140B2 (ja) 2022-05-31

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