WO2020161862A1 - Pressure control valve - Google Patents

Pressure control valve 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
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WO
WIPO (PCT)
Prior art keywords
relief valve
pilot relief
seat member
pressure
balance piston
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PCT/JP2019/004438
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French (fr)
Japanese (ja)
Inventor
涼太 筒井
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株式会社島津製作所
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Priority to PCT/JP2019/004438 priority Critical patent/WO2020161862A1/en
Priority to JP2020570293A priority patent/JP7078140B2/en
Publication of WO2020161862A1 publication Critical patent/WO2020161862A1/en

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    • 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

In the present invention, a damping chamber (12) is formed by a cap member (5), a pilot relief valve (1), and a seat member (3). Due to the action of the damping chamber (12) and an orifice (5a), a damping force acts against the pilot relief valve (1) when the pilot relief valve (1) moves in a direction away from the seat member (3). Meanwhile, when the pilot relief valve (1) moves toward the seat member (3), the pressure of a hydraulic fluid inside the damping chamber (12) increases and causes the cap member (5) to move away from the seat member (3). Consequently, the pressure in an intermediate chamber (11) and the pressure in the damping chamber (12) become the same, and the damping effect with respect to the pilot relief valve (1) no longer exists. Consequently, without incurring any resistance, the pilot relief valve (1) moves rapidly to a position where it contacts the seat member (3).

Description

圧力制御弁Pressure control valve
　この発明は、リリーフ弁として使用される圧力制御弁に関する。 The present invention relates to a pressure control valve used as a relief valve.
　図５は、リリーフ弁として使用される従来の圧力制御弁の断面図である。なお、図５においては、圧力制御弁がコントロールバルブ等におけるハウジング１００に装着された状態を示している。 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.
　図５に示す従来の圧力制御弁は、高圧ライン２０における作動液の圧力が一定以上となったときに、作動液を高圧ライン２０から低圧ライン３０に流出させることで、ハウジング１００内の作動液の圧力が一定以上となることを防止するためのものである。この圧力制御弁は、バルブボディ７に支持されるスリーブ１０と、このスリーブ１０内においてスリーブ１０に対して摺動可能に配設されたバランスピストン８とを備えたバランスピストン型の構成となっている。 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.
　バランスピストン８は、付勢手段としてのスプリング９により、高圧ライン２０側の端部がスリーブ１０に形成された弁座領域と当接する方向に付勢されている。また、このバランスピストン８には、高圧ライン２０とバランスピストン８内部の中間室１１とを連通するオリフィス８ｃが形成されている。このオリフィス８ｃを通過する作動液の流れが生ずると、バランスピストン８の高圧ライン２０側と低圧ライン３０側との間に圧力差が生ずる。そして、バランスピストン８における上流面（高圧ライン２０側の面）８ａに作用する作動液の圧力が、下流面（低圧ライン３０側の面）８ｂに作用する圧力とスプリング９による付勢力の合計値を上回ると、バランスピストン８がスリーブ１０内を摺動してスリーブ１０における弁座領域から離隔する。これにより、高圧ライン２０から低圧ライン３０に至る作動液の通路が開口し、高圧ライン２０の余剰作動液を低圧ライン３０に流出させることで、ハウジング１００内の作動液の最大圧力を保証している。 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. In addition, 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. When the flow of the hydraulic fluid passing through the orifice 8c occurs, a pressure difference occurs between the high pressure line 20 side and the low pressure line 30 side of 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. Above, 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.
　このバランスピストン８は、パイロット方式によって移動する。すなわち、バランスピストン８におけるオリフィス８ｃの通過流量を制御するため、バランスピストン８の下流にパイロットリリーフ弁１が配設されている。このパイロットリリーフ弁１は、スプリング２の作用により、スリーブ１０の一端に配設されたシート部材３における弁座面に向けて付勢されている。このパイロットリリーフ弁１のシート部材３に対する付勢力は、圧力調整ネジ６により調整することができる。パイロットリリーフ弁１における上流面（シート部材３側の面）に作用する作動液の圧力がスプリング２による付勢力を上回ると、パイロットリリーフ弁１はシート部材３の弁座面から離間し、中間室１１内の作動液を低圧ライン３０に流出させる。これにより、バランスピストン８におけるオリフィス８ｃ内を作動液が通過し、バランスピストン８における上流面８ａと下流面８ｂとの間に圧力差が生じることで、バランスピストン８が開弁する。 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. When the pressure of the hydraulic fluid acting on the upstream surface (the surface on the side of the seat member 3) of the pilot relief valve 1 exceeds the biasing force of the spring 2, 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. As a result, 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.
　以上のような構成を有する圧力制御弁は、特許文献１における従来技術として開示されている。なお、特許文献１においては、バランスピストン８に生ずるフラッタリング（チャタリング）を防止するため、バランスピストン８とシート部材３との間にダンパを形成している。 The pressure control valve having the above configuration is disclosed as a conventional technique in Patent Document 1. 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.
国際公開２０１７／０４６９５５号International Publication 2017/046955
　図５に示す構成を有する圧力制御弁においては、パイロットリリーフ弁１がシート部材３における弁座面から離隔するときに、パイロットリリーフ弁１には慣性力が働くため、パイロットリリーフ弁１に対する作動液の圧力とスプリング２による付勢力とのバランス位置をオーバーラップして開口面積が大きくなり、パイロット流量が過大に流れる現象が生ずる。このような現象が発生したときには、バランスピストン８における中間室１１の圧力降下が大きくなるため、パイロットリリーフ弁１に作用する作動液の液圧が小さくなり、スプリング９による付勢力によってパイロットリリーフ弁１はシート部材３から離隔する方向に押し戻される。そうすると、パイロットリリーフ弁１とシート部材３との間の開口面積が小さくなるため、中間室１１内の液圧は再度上昇する。このような動作が繰り返されることによるパイロットリリーフ弁１の発振は、フラッタリング（チャタリング）と呼ばれ、フラッタリングにより、圧力制御弁において振動や騒音が発生する。 In the pressure control valve having the configuration shown in FIG. 5, when the pilot relief valve 1 separates from the valve seat surface of the seat member 3, an inertial force acts on the pilot relief valve 1, so that the hydraulic fluid for the pilot relief valve 1 is increased. There is a phenomenon in which the opening area becomes large by overlapping the balance position of the pressure of 1 and the urging force of the spring 2, and the pilot flow rate becomes excessive. When such a phenomenon occurs, the pressure drop of the intermediate chamber 11 in the balance piston 8 becomes large, so that the hydraulic pressure of the hydraulic fluid acting on the pilot relief valve 1 becomes small, and the urging force of the spring 9 makes the pilot relief valve 1 Are pushed back in a direction away from the sheet member 3. Then, 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.
　このような問題を解決するため、シート部材にダンピング室を形成した圧力制御弁も提案されている。図６は、リリーフ弁として使用される改良された圧力制御弁の断面図である。なお、図６においては、圧力制御弁がコントロールバルブ等におけるハウジング１００に装着された状態を示している。 In order to solve such problems, a pressure control valve with a damping chamber formed in the seat member has also been proposed. 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.
　図６に示す圧力制御弁においては、シート部材４内にダンピング室１２を形成するとともに、このダンピング室１２とバランスピストン８における中間室１１とを連通するオリフィス４ａを形成している。このような構成を有する圧力制御弁によれば、ダンピング室１２とオリフィス４ａの作用により、パイロットリリーフ弁１がシート部材４から離隔する方向に移動するときに、パイロットリリーフ弁１に対して減衰力が作用する。この減衰力により、パイロットリリーフ弁１における慣性によるオーバーラップを抑制して、フラッタリングの発生を抑制することが可能となる。 In the pressure control valve shown in FIG. 6, 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. According to the pressure control valve having such a configuration, when the pilot relief valve 1 moves in the direction away from the seat member 4 due to the action of the damping chamber 12 and the orifice 4a, the damping force is applied to the pilot relief valve 1. Works. With this damping force, it is possible to suppress overlap due to inertia in the pilot relief valve 1 and suppress the occurrence of fluttering.
　一方、図６に示す圧力制御弁においては、パイロットリリーフ弁１がシート部材４に近接する方向に移動するときに、ダンピング室１２内の圧力が上昇する。これにより、パイロットリリーフ弁１に作用する作動液の圧力が大きくなり、パイロットリリーフ弁の応答性が悪くなる。バランスピストン８はパイロットリリーフ弁１の開閉動作に対応して開閉制御されていることから、パイロットリリーフ弁１の応答性の低下により開閉動作が不安定になると、作動液の圧力制御のバランスが乱れ、パイロットリリーフ弁１またはバランスピストン８が発振し、圧力制御弁において振動や騒音が発生する。 On the other hand, in the pressure control valve shown in FIG. 6, when the pilot relief valve 1 moves toward the seat member 4, the pressure in the damping chamber 12 rises. As a result, the pressure of the hydraulic fluid acting on the pilot relief valve 1 increases, and the responsiveness of the pilot relief valve deteriorates. Since the balance piston 8 is controlled to open/close in response to the opening/closing operation of the pilot relief valve 1, if the opening/closing operation becomes unstable due to a decrease in responsiveness of the pilot relief valve 1, the balance of hydraulic fluid pressure control is disturbed. The pilot relief valve 1 or the balance piston 8 oscillates, causing vibration and noise in the pressure control valve.
　この発明は上記課題を解決するためになされたものであり、騒音や振動の発生を抑制することが可能な圧力制御弁を提供することを目的とする。 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.
　請求項１に記載の発明は、バランスピストン型の圧力制御弁において、高圧ラインに連通するオリフィスが形成され、内部に中間室を有するバランスピストンと、前記バランスピストンと当接する弁座を備え、前記バランスピストンをスライド可能に収納するスリーブと、前記バランスピストンにおけるオリフィスから前記中間室への作動液の流入を制御するためのパイロットリリーフ弁と、前記パイロットリリーフ弁と当接する弁座を備えるシート部材と、前記パイロットリリーフ弁および前記シート部材との間にダンピング室を形成するとともに、前記中間室と前記ダンピング室とを連通するオリフィスが形成され、前記シート部材と当接する位置と前記シート部材から離隔する位置との間を移動可能なキャップ部材と、を備えたことを特徴とする。 According to a first aspect of the present invention, 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. And a cap member movable between the positions.
　請求項１に記載の発明によれば、パイロットリリーフ弁がシート部材から離隔する方向に移動するときには、キャップ部材におけるダンピング室およびオリフィスの作用によりパイロットリリーフ弁のオーバーラップを抑制し、パイロットリリーフ弁がシート部材に近接する方向に移動するときには、キャップ部材がシート部材から離隔することによりパイロットリリーフ弁の応答性の低下を防止することができる。これにより、圧力制御弁における騒音や振動の発生を抑制することが可能となる。 According to the invention described in claim 1, when the pilot relief valve moves in the direction away from the seat member, the action of the damping chamber and the orifice in the cap member suppresses the overlap of the pilot relief valve, and the pilot relief valve is When the cap member moves away from the seat member when moving in the direction of approaching the seat member, it is possible to prevent the responsiveness of the pilot relief valve from decreasing. This makes it possible to suppress the generation of noise and vibration in the pressure control valve.
この発明に係る圧力制御弁における圧力制御動作を示す断面図である。It is sectional drawing which shows the pressure control operation|movement in the pressure control valve which concerns on this invention. この発明に係る圧力制御弁における圧力制御動作を示す断面図である。It is sectional drawing which shows the pressure control operation|movement in the pressure control valve which concerns on this invention. この発明に係る圧力制御弁における圧力制御動作を示す断面図である。It is sectional drawing which shows the pressure control operation|movement in the pressure control valve which concerns on this invention. この発明に係る圧力制御弁における圧力制御動作を示す断面図である。It is sectional drawing which shows the pressure control operation|movement in the pressure control valve which concerns on this invention. リリーフ弁として使用される従来の圧力制御弁の断面図である。It is sectional drawing of the conventional pressure control valve used as a relief valve. リリーフ弁として使用される改良された圧力制御弁の断面図である。FIG. 6 is a cross-sectional view of an improved pressure control valve used as a relief valve.
　以下、この発明の実施の形態を図面に基づいて説明する。図１から図４は、この発明に係る圧力制御弁における圧力制御動作を示す断面図である。なお、図１から図４においては、圧力制御弁がコントロールバルブ等におけるハウジング１００に装着された状態を示している。 Embodiments of the present invention will be described below with reference to the drawings. 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.
　この圧力制御弁は、例えば、フォークリフト等に搭載される作動液として作動油を使用するコントロールバルブにおいて、高圧ライン２０における作動液の圧力が一定以上となったときに、作動液を高圧ライン２０から低圧ライン３０に流出させることで、ハウジング１００内の作動液の圧力が一定以上となることを防止するためのものである。この圧力制御弁は、バルブボディ７に支持される弁収納体としてのスリーブ１０と、このスリーブ１０内においてスリーブ１０に対して摺動可能に配設された主弁体としてのバランスピストン８とを備えたバランスピストン型の構成となっている。 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.
　バランスピストン８は、付勢手段としてのスプリング９により、高圧ライン２０側の端部がスリーブ１０に形成された弁座領域と当接する方向に付勢されている。また、このバランスピストン８には、高圧ライン２０とバランスピストン８内部の中間室１１とを連通するオリフィス８ｃが形成されている。このオリフィス８ｃを通過する作動液の流れが生ずると、バランスピストン８の高圧ライン２０側と低圧ライン３０側との間に圧力差が生ずる。そして、バランスピストン８における上流面（高圧ライン２０側の面）８ａに作用する作動液の圧力が、下流面（低圧ライン３０側の面）８ｂに作用する圧力とスプリング９による付勢力の合計値を上回ると、バランスピストン８がスリーブ１０内を摺動してスリーブ１０における弁座領域から離隔する。これにより、高圧ライン２０から低圧ライン３０に至る作動液の通路が開口し、高圧ライン２０の余剰作動液を低圧ライン３０に流出させることで、ハウジング１００内の作動液の最大圧力を保証している。 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. In addition, 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. When the flow of the hydraulic fluid passing through the orifice 8c occurs, a pressure difference occurs between the high pressure line 20 side and the low pressure line 30 side of 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. Above, 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.
　このバランスピストン８は、パイロット方式によって移動する。すなわち、バランスピストン８におけるオリフィス８ｃの通過流量を制御するため、バランスピストン８の下流にパイロットリリーフ弁１が配設されている。このパイロットリリーフ弁１は、スプリング２の作用により、スリーブ１０の一端に配設されたシート部材３における弁座面に向けて付勢されている。このパイロットリリーフ弁１のシート部材３に対する付勢力は、圧力調整ネジ６により調整することができる。パイロットリリーフ弁１における上流面（シート部材３側の面）に作用する作動液の圧力がスプリング２による付勢力を上回ると、パイロットリリーフ弁１はシート部材３の弁座面から離間し、中間室１１内の作動液を低圧ライン３０に流出させる。これにより、バランスピストン８におけるオリフィス８ｃ内を作動液が通過し、バランスピストン８における上流面８ａと下流面８ｂとの間に圧力差が生じることで、バランスピストン８が開弁する。 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. When the pressure of the hydraulic fluid acting on the upstream surface (the surface on the side of the seat member 3) of the pilot relief valve 1 exceeds the biasing force of the spring 2, 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. As a result, 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.
　シート部材３とバランスピストン８との間には、キャップ部材５が配設されている。このキャップ部材５は、シート部材３と当接した状態において、パイロットリリーフ弁１およびシート部材３との間にダンピング室１２を形成する。すなわち、キャップ部材５とシート部材３とが当接したときには、図１に示すように、キャップ部材５とパイロットリリーフ弁１とシート部材３とによりダンピング室１２が形成される。この状態においては、キャップ部材５とパイロットリリーフ弁１との間には、わずかな隙間が形成される。キャップ部材５には、バランスピストン８の中間室１１とダンピング室１２とを連通するオリフィス５ａが形成されている。このキャップ部材５は、スプリング９によりシート部材３方向に付勢され、シート部材３と当接する位置とシート部材３から離隔する位置との間を移動可能となっている。 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.
　次に、以上のような構成を有する圧力調整弁による作動液のリリーフ動作について説明する。 Next, the relief operation of the hydraulic fluid by the pressure control valve having the above configuration will be described.
　高圧ライン２０における作動液の圧力が圧力制御弁のリリーフ圧より小さいときには、図１に示すように、スプリング９の作用によりパイロットリリーフ弁１とシート部材３とが当接しており、高圧ライン２０から低圧ライン３０に至る通路は、閉じられている。また、バランスピストン８は、スプリング９の作用により、スリーブ１０の弁座領域と当接している。 When the pressure of the hydraulic fluid in the high pressure line 20 is lower than the relief pressure of the pressure control valve, the pilot relief valve 1 and the seat member 3 are in contact with each other by the action of the spring 9, as shown in FIG. The passage leading to the low pressure line 30 is closed. The balance piston 8 is in contact with the valve seat region of the sleeve 10 by the action of the spring 9.
　高圧ライン２０における作動液の圧力が圧力制御弁のリリーフ圧より大きくなると、図２に示すように、パイロットリリーフ弁１がシート部材３の弁座面から離隔する。これにより高圧ライン２０からの作動液がバランスピストン８における中間室１１およびキャップ部材５に形成されたオリフィス５ａを介して低圧ライン３０に流れる。 When the pressure of the hydraulic fluid in the high-pressure line 20 becomes higher than the relief pressure of the pressure control valve, the pilot relief valve 1 separates from the valve seat surface of the seat member 3, as shown in FIG. As a result, the hydraulic fluid from the high pressure line 20 flows into the low pressure line 30 via the intermediate chamber 11 in the balance piston 8 and the orifice 5a formed in the cap member 5.
　高圧ライン２０における作動液の圧力がさらに上昇し、パイロットリリーフ弁１の開度が一定以上となって、バランスピストン８における上流面（高圧ライン２０側の面）８ａに作用する作動液の圧力が、下流面（低圧ライン３０側の面）８ｂに作用する圧力とスプリング９による付勢力の合計値を上回ると、図３に示すように、バランスピストン８がスリーブ１０内を摺動し、スリーブ１０における弁座領域から離隔する。これにより、高圧ライン２０から低圧ライン３０に至る作動液の通路が開口し、高圧ライン２０の余剰作動液を低圧ライン３０に流出させることで、ハウジング１００内の作動液の最大圧力をリリーフ圧とすることができる。 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. When 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. 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, so that the maximum pressure of the hydraulic fluid in the housing 100 becomes the relief pressure. can do.
　ここで、図２および図３に示すパイロットリリーフ弁１がシート部材３から離隔する方向に移動するときには、キャップ部材５の上流側（高圧ライン２０側）の圧力が下流側（低圧ライン３０側）に比べて大きいため、キャップ部材５はシート部材３に押し付けられ、キャップ部材５とパイロットリリーフ弁１とシート部材３とによりダンピング室１２が形成されている。このため、ダンピング室１２とオリフィス５ａの作用により、パイロットリリーフ弁１がシート部材３から離隔する方向に移動するときに、パイロットリリーフ弁１に対して減衰力が作用する。この減衰力により、パイロットリリーフ弁１における慣性によるオーバーラップを抑制して、フラッタリングの発生を抑制することが可能となる。 Here, when the pilot relief valve 1 shown in FIGS. 2 and 3 moves in a direction away from the seat member 3, the pressure on the upstream side (high pressure line 20 side) of the cap member 5 is on the downstream side (low pressure line 30 side). Therefore, the cap member 5 is pressed against the seat member 3, and the cap member 5, the pilot relief valve 1, and the seat member 3 form a damping chamber 12. Therefore, the damping force acts on the pilot relief valve 1 when the pilot relief valve 1 moves away from the seat member 3 due to the action of the damping chamber 12 and the orifice 5a. With this damping force, it is possible to suppress overlap due to inertia in the pilot relief valve 1 and suppress the occurrence of fluttering.
　一方、図３に示す状態から高圧ライン２０における作動液の圧力が低下したときには、バランスピストン８は、図３に示すスリーブ１０の弁座領域から離隔した状態から、図２に示すスリーブ１０の弁座領域と当接した状態となるまで移動する。 On the other hand, when the pressure of the hydraulic fluid in the high-pressure line 20 is reduced from the state shown in FIG. 3, the balance piston 8 is moved from the valve seat region of the sleeve 10 shown in FIG. 3 to the valve of the sleeve 10 shown in FIG. Move until it is in contact with the seat area.
　そして、高圧ライン２０における作動液の圧力がさらに低下すると、パイロットリリーフ弁１がシート部材３方向に移動し、やがて、図４に示すように、パイロットリリーフ弁１とシート部材３とが当接する。この時には、キャップ部材５とパイロットリリーフ弁１とシート部材３とにより形成されるダンピング室１２内の作動液の液圧が上昇する。これにより、図４に示すように、キャップ部材５がシート部材３から離隔する。このため、中間室１１とダンピング室１２が同圧となり、パイロットリリーフ弁１に対するダンピング効果がなくなる。従って、パイロットリリーフ弁１は抵抗を受けることなく、速やかにシート部材３と当接する位置まで移動する。 Then, when the pressure of the hydraulic fluid in the high-pressure line 20 further decreases, 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. At this time, 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. As a result, 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.
　以上のように、この発明に係る圧力制御弁によれば、パイロットリリーフ弁１がシート部材３から離隔する方向に移動するときには、キャップ部材５におけるダンピング室１２およびオリフィス５ａの作用によりパイロットリリーフ弁１のオーバーラップを抑制し、パイロットリリーフ弁１がシート部材３に近接する方向に移動するときには、キャップ部材５がシート部材３から離隔することによりパイロットリリーフ弁１の応答性の低下を防止することができる。これにより、圧力制御弁における騒音や振動の発生を抑制することが可能となる。 As described above, according to the pressure control valve of the present invention, 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. 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.
　１　　　パイロットリリーフ弁
　２　　　スプリング
　３　　　シート部材
　５　　　キャップ部材
　５ａ　　オリフィス
　８　　　バランスピストン
　８ｃ　　オリフィス
　９　　　スプリング
　１０　　スリーブ
　１１　　中間室
　１２　　ダンピング室
　２０　　高圧ライン
　３０　　低圧ライン
　１００　ハウジング
  1 Pilot relief valve 2 Spring 3 Seat member 5 Cap member 5a Orifice 8 Balance piston 8c Orifice 9 Spring 10 Sleeve 11 Intermediate chamber 12 Damping chamber 20 High pressure line 30 Low pressure line 100 Housing

Claims (1)

  1. 　バランスピストン型の圧力制御弁において、
    　高圧ラインに連通するオリフィスが形成され、内部に中間室を有するバランスピストンと、
    　前記バランスピストンと当接する弁座を備え、前記バランスピストンをスライド可能に収納するスリーブと、
    　前記バランスピストンにおけるオリフィスから前記中間室への作動液の流入を制御するためのパイロットリリーフ弁と、
    　前記パイロットリリーフ弁と当接する弁座を備えるシート部材と、
    　前記パイロットリリーフ弁および前記シート部材との間にダンピング室を形成するとともに、前記中間室と前記ダンピング室とを連通するオリフィスが形成され、前記シート部材と当接する位置と前記シート部材から離隔する位置との間を移動可能なキャップ部材と、
    　を備えたことを特徴とする圧力制御弁。
          In the balance piston type pressure control valve,
    An orifice communicating with the high-pressure line is formed, and a balance piston having an intermediate chamber inside,
    A valve seat that abuts the balance piston, and a sleeve that slidably accommodates the balance piston,
    A pilot relief valve for controlling the flow of hydraulic fluid from the orifice in the balance piston into the intermediate chamber;
    A seat member having a valve seat that contacts the pilot relief valve;
    A damping chamber is formed between the pilot relief valve and the seat member, and an orifice that connects the intermediate chamber and the damping chamber is formed, and a position abutting the seat member and a position separated from the seat member. A cap member movable between
    A pressure control valve characterized by having.
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JP2005240993A (en) * 2004-02-25 2005-09-08 Volvo Construction Equipment Holding Sweden Ab Pilot operated relief valve
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 (en) * 2015-09-18 2017-03-23 株式会社 島津製作所 Pressure control valve

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