JP2006029388A - Hydraulic relief valve - Google Patents

Hydraulic relief valve Download PDF

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JP2006029388A
JP2006029388A JP2004205867A JP2004205867A JP2006029388A JP 2006029388 A JP2006029388 A JP 2006029388A JP 2004205867 A JP2004205867 A JP 2004205867A JP 2004205867 A JP2004205867 A JP 2004205867A JP 2006029388 A JP2006029388 A JP 2006029388A
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valve
pressure
fluid pressure
hydraulic
relief
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JP4557283B2 (en
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Yasushi Watanabe
靖 渡辺
Shuji Sato
修治 佐藤
Makoto Narita
誠 成田
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CIVITEC RESEARCH KK
Japan Steel Works Ltd
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Japan Steel Works Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic relief valve capable of being used as a relief valve of high flow rate usable in a pressure accumulation-type hydraulic driving system or the like. <P>SOLUTION: This hydraulic relief valve comprises a main valve having a hydraulic source-side port and a relief-side port respectively communicating with a hydraulic source P and a relief side T, and communicating with each other through a valve flow channel, and having a valve element 7 for closing the valve flow channel by receiving the control fluid pressure P0 and opening the valve flow channel on the basis of the reduction in receiving the control fluid pressure, a sub-valve B receiving the fluid pressure and adjustment fluid pressure P1 from the hydraulic source P and performs hydraulic source-pressure overrun operation when the fluid pressure from the hydraulic source P is over the adjustment fluid pressure P1, and decompressing means 65, 68, 60b, 60c for opening the valve flow channel (P→T) by reducing the reception of control fluid pressure P0 in the main valve A in accompany with the hydraulic source-pressure overrun operation of the sub-valve. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

この発明は、例えば水圧鍛造プレス・水圧押出しプレス等の圧力３０ＭＰａのアキュムレータ蓄圧式水圧駆動システムなどに用いられ、流路圧力を検出し検出結果に従って開弁することで圧力供給を受ける側の圧力制限を可能とする、流体圧リリーフ弁に関するものである。   The present invention is used in, for example, an accumulator accumulator hydraulic drive system having a pressure of 30 MPa, such as a hydraulic forging press or a hydraulic extrusion press, and the pressure limit on the side receiving pressure supply by detecting the flow path pressure and opening the valve according to the detection result The present invention relates to a fluid pressure relief valve.

従来のアキュムレータ蓄圧式水圧駆動システムでは水圧シリンダー等のアクチュエータ類は全て、システム最大圧力が負荷されるものとして設計・製作しなければならなかった。なぜならばアキュムレータ蓄圧式の場合においてはアキュムレータの持つエネルギーが大きく、システム最大圧力より小さな圧力でタンクラインにリリーフさせようとすると、その差圧に見合った大流量のリリーフ弁を必要とするが、実用上、このような大流量リリーフ弁が世の中に存在せず、アクチュエータ類の圧力を制限することが困難であったためである。   In conventional accumulator accumulator hydraulic drive systems, all actuators such as hydraulic cylinders had to be designed and manufactured to be loaded with the maximum system pressure. Because in the case of accumulator accumulator type, the energy of the accumulator is large, and if you try to relieve the tank line at a pressure lower than the system maximum pressure, a relief valve with a large flow rate that matches the differential pressure is required. Moreover, this is because such a large flow rate relief valve does not exist in the world and it is difficult to limit the pressure of the actuators.

アキュムレータ蓄圧式で差圧が約７ＭＰａの場合、リリーフ流量はおおむね６５００リッター／分程度となるが、従来は小流量のものを除いて、最大圧力より低い圧力に制限して使用することが実現できていない。この小流量用のバルブには図４に示す「直動型」が使用されている。この直動型のバルブは、一般的には、ポンプ式水圧駆動システムに用いられており、市販品ではリリーフ流量で１００リッター／分程度のものが最大であり、大型水圧ポンプに用いられる機種であっても最大流量１，７００リッター／分、程度が実用上、直動型の最大である。   When the differential pressure is about 7MPa with the accumulator pressure accumulation type, the relief flow rate will be about 6500 liters / minute, but conventionally it can be used by limiting it to a pressure lower than the maximum pressure except for small flow rates. Not. The “direct acting type” shown in FIG. 4 is used for the small flow rate valve. This direct acting type valve is generally used in a pump-type hydraulic drive system, and a commercially available product with a relief flow rate of about 100 liters / minute is the largest, and it is a model used for a large hydraulic pump. Even if it is, the maximum flow rate of 1,700 liters / minute is practically the maximum of the direct acting type.

上記直動型バルブの基本構造について説明する。本図は非特許文献１に記載されている水圧リリーフ弁（pressure relief valve）断面図を引用したものである。
本水圧安全弁の圧力調整ばね１００は、ばね座板１０１を介してピストン１０２をシート１０３に押付けている。圧力調整ばね１００によるばね力はリリーフ弁の設定圧力であり、調整ナット１０４を回すことで変更することができる。調整ナット１０４は、ばね力の設定後にロックナット１０５で固定される。ポートＰにおける流体回路の圧力は、ピストン１０２に加わっており、上記ばね力による閉止力に対してこの回路圧力による力が上回った時にはピストン１０２はシート１０３からリフト上昇し、ポートＰはポートＴにつながりリリーフ弁として動作する。
ドイツ水圧機器メーカーｈａｕｈｉｎｃｏ社ホームページ、 Pressure relief valve DN3 DN6 DN10 断面図、［online］、［ 平成１６年３月１日検索］、インターネット＜ＵＲＬ：http://www.hauhinco.co.uk/I_Vlv0.htm＞ The basic structure of the direct acting valve will be described. This figure is a quotation from the cross-sectional view of a water pressure relief valve described in Non-Patent Document 1.
The pressure adjusting spring 100 of the water pressure safety valve presses the piston 102 against the seat 103 via the spring seat plate 101. The spring force by the pressure adjustment spring 100 is the set pressure of the relief valve, and can be changed by turning the adjustment nut 104. The adjustment nut 104 is fixed by the lock nut 105 after setting the spring force. The pressure of the fluid circuit at the port P is applied to the piston 102. When the force by the circuit pressure exceeds the closing force due to the spring force, the piston 102 lifts up from the seat 103, and the port P moves to the port T. Operates as a connection relief valve.
German hydraulic equipment maker hauhinco website, Pressure relief valve DN3 DN6 DN10 cross section, [online], [March 1, 2004 search], Internet <URL: http://www.hauhinco.co.uk/I_Vlv0. htm>

しかし、上記で説明したバルブでは、前記したように大流量のリリーフ弁として用いることは困難である。本発明が解決しようとする課題は、アキュムレータ蓄圧式水圧駆動システムなどにおいて利用可能で大流量のリリーフ弁として使用可能なものを提供することにある。さらに、望ましくは、
（１）システム最大圧力より低い圧力を任意に得ること
（２）システム最大圧力より低い圧力で規制し、それ以上の圧力を作動機器に作用させないための過負荷防止に対応すること、
を可能にすることを課題とする。 However, the valve described above is difficult to use as a relief valve with a large flow rate as described above. The problem to be solved by the present invention is to provide an accumulator pressure-accumulating water pressure drive system that can be used as a large flow relief valve. Furthermore, preferably
(1) Obtaining a pressure lower than the system maximum pressure arbitrarily (2) Regulating with a pressure lower than the system maximum pressure and responding to overload prevention so that no more pressure acts on the operating equipment,
The challenge is to make this possible.

すなわち、本発明の流体圧リリーフ弁のうち、請求項１記載の発明は、流体圧源とリリーフ側とにそれぞれ連通し、互いに弁流路を介して連通する流体圧源側ポートとリリーフ側ポートとを有し、制御用流体圧を受けて前記弁流路を閉じ、該制御用流体圧の受圧減少によって前記弁流路を開く弁体を備える主弁と、前記流体圧源からの流体圧と調整用流体圧とを受け、前記流体圧源からの流体圧が調整用流体圧を上回ると流体圧源圧超過時動作をする副弁と、該副弁の流体圧源圧超過時動作に従って前記主弁における制御用流体圧の受圧を減少させて前記弁流路を開放させる減圧手段とを備えることを特徴とする。   That is, among the fluid pressure relief valves of the present invention, the invention according to claim 1 is in communication with the fluid pressure source and the relief side, respectively, and communicates with each other via the valve flow path. A main valve including a valve body that receives the control fluid pressure to close the valve flow path and opens the valve flow path when the control fluid pressure is reduced, and a fluid pressure from the fluid pressure source. A sub-valve that operates when the fluid pressure from the fluid pressure source exceeds the fluid pressure for adjustment and exceeds the fluid pressure for adjustment, and the operation of the sub-valve when the fluid pressure source pressure exceeds Pressure reducing means for reducing the pressure of the control fluid pressure in the main valve to open the valve flow path.

請求項２記載の流体圧リリーフ弁の発明は、請求項１記載の発明において、前記主弁は、前記制御用流体圧の受圧減少時に、流体圧源からの流体圧によって弁体が動作して弁流路を開放するように構成されていることを特徴とする。   A fluid pressure relief valve according to a second aspect of the present invention is the fluid pressure relief valve according to the first aspect of the invention, wherein the main valve is configured such that the valve body is operated by the fluid pressure from the fluid pressure source when the control fluid pressure is decreased. It is characterized by opening the valve flow path.

請求項３記載の流体圧リリーフ弁の発明は、請求項１または２に記載の前記主弁の弁体は、流体圧源からの流体圧と、制御用流体圧の差圧によって動作するものであることを特徴とする。   According to a third aspect of the present invention, the valve body of the main valve according to the first or second aspect is operated by a differential pressure between a fluid pressure from a fluid pressure source and a control fluid pressure. It is characterized by being.

請求項４記載の流体圧リリーフ弁の発明は、請求項１〜３のいずれかに記載の発明において、前記制御用流体圧が、流体圧源の最大圧力以内において圧力の設定調整が可能とされていることを特徴とする。   A fluid pressure relief valve according to a fourth aspect of the present invention is the fluid pressure relief valve according to any one of the first to third aspects, wherein the control fluid pressure can be set and adjusted within the maximum pressure of the fluid pressure source. It is characterized by.

請求項５記載の流体圧リリーフ弁の発明は、請求項１〜４のいずれかに記載の発明において、前記主弁は、制御用流体が導入されて弁体に圧力を付加する制御用流体圧受圧室を備えており、前記制御用流体圧の受圧減少は、前記制御用流体圧受圧室から制御用流体を開閉弁を介して外部に流出させることにより行うことを特徴とする。   The invention of the fluid pressure relief valve according to claim 5 is the invention according to any one of claims 1 to 4, wherein the main valve is a control fluid pressure that introduces a control fluid and applies pressure to the valve body. A pressure receiving chamber is provided, and the pressure reduction of the control fluid pressure is performed by allowing the control fluid to flow out of the control fluid pressure receiving chamber through an on-off valve.

請求項６記載の流体圧リリーフ弁の発明は、請求項１〜５のいずれかに記載の発明において、前記副弁は、前記流体圧源からの流体圧と調整用流体圧との差圧によって少なくとも流体圧超過時動作としてストローク動作するピストンを備え、該ピストンのストローク動作に従って前記減圧手段を動作させるものであることを特徴とする。   The invention of a fluid pressure relief valve according to a sixth aspect of the present invention is the invention according to any one of the first to fifth aspects, wherein the sub valve is controlled by a differential pressure between a fluid pressure from the fluid pressure source and a regulating fluid pressure. At least a piston that performs a stroke operation as an operation when fluid pressure is exceeded is provided, and the pressure reducing means is operated according to the stroke operation of the piston.

すなわち、本発明によれば、副弁において流体圧源からの流体圧と調整用流体圧とを受け、流体圧源からの流体圧が調整用流体圧を上回る場合に、その状態が流体圧超過時動作として検出される。該動作は、減圧手段を制御して主弁において弁流路を閉じている弁体への制御用流体圧の受圧を減少させる。この結果、弁流路が開放されて流体圧源の流体がリリーフされ、流体圧源から供給される流体圧の圧力を低下させることができる。一方、流体圧源からの流体圧が低下して調整用流体圧以下になると、副弁における流体圧超過時動作がなくなり、したがって減圧手段による、主弁における制御用流体圧の受圧減少作用が失われる。その結果、主弁における制御用流体圧の受圧が復元し、該圧力が弁体に作用して弁流路を閉じる動作がなされる。この制御用流体圧の受圧によって、通常時には、弁体によって主弁の弁流路が閉じられるようにしておくことで、上記受圧復元に従って直ちに弁流路が閉じられることになる。弁流路が閉じられることで主弁における流体圧源からの流体のリリーフが停止される。リリーフ弁を閉じている際に、再度、流体圧源からの流体圧が上昇して前記調整用流体圧が上回った場合には、上記と同様にして主弁の弁流路が閉じられて流体のリリーフがなされ、再度、流体圧源からの流体圧が低下して前記調整用流体圧以下になった場合には、上記と同様にして主弁の弁流路が開かれて流体のリリーフが停止される。上記動作を繰り返すことにより、流体圧源からの流体圧を調整用流体圧を基準にしてシステム最大圧力より低い圧力に維持することができる。
なお、本発明の減圧手段は、主弁における制御用流体圧の受圧を減少させることができるものであればよく、制御用流体圧そのものの減圧や、主弁に対する制御用流体圧の供給停止や、主弁における制御用流体圧のリリースなどによって行うことができる。 That is, according to the present invention, when the sub-valve receives the fluid pressure from the fluid pressure source and the adjustment fluid pressure, and the fluid pressure from the fluid pressure source exceeds the adjustment fluid pressure, the state exceeds the fluid pressure. Detected as hourly motion. In this operation, the pressure reducing means is controlled to reduce the receiving pressure of the control fluid pressure to the valve body closing the valve flow path in the main valve. As a result, the valve flow path is opened, the fluid of the fluid pressure source is relieved, and the pressure of the fluid pressure supplied from the fluid pressure source can be reduced. On the other hand, when the fluid pressure from the fluid pressure source drops to below the adjusting fluid pressure, the sub valve does not operate when the fluid pressure exceeds, and therefore the pressure reducing means loses the effect of reducing the control fluid pressure received by the main valve. Is called. As a result, the receiving pressure of the control fluid pressure in the main valve is restored, and the pressure acts on the valve body to close the valve flow path. By receiving the control fluid pressure, the valve flow path of the main valve is normally closed by the valve element so that the valve flow path is immediately closed according to the pressure recovery. The relief of the fluid from the fluid pressure source in the main valve is stopped by closing the valve flow path. When the relief valve is closed and the fluid pressure from the fluid pressure source rises again and exceeds the adjustment fluid pressure, the valve flow path of the main valve is closed in the same manner as described above. When the fluid pressure from the fluid pressure source decreases to become the adjustment fluid pressure or less again, the valve flow path of the main valve is opened and the fluid relief is performed in the same manner as described above. Stopped. By repeating the above operation, the fluid pressure from the fluid pressure source can be maintained at a pressure lower than the system maximum pressure with reference to the adjusting fluid pressure.
The pressure reducing means of the present invention may be any means as long as it can reduce the receiving pressure of the control fluid pressure in the main valve, and the control fluid pressure itself can be reduced, the supply of the control fluid pressure to the main valve can be stopped, This can be done by releasing the control fluid pressure in the main valve.

また、前記調整用流体圧をシステム最大圧力以内に設定調整可能にすることで、上記動作に従って維持される圧力を所望の圧力に調整することができる。   In addition, by enabling the adjustment fluid pressure to be set and adjusted within the system maximum pressure, the pressure maintained according to the above operation can be adjusted to a desired pressure.

また、副弁に流体圧超過時動作としてストローク動作するピストンを備え、該ピストンの動作に従って前記減圧手段を動作させるものとすれば、メカニカルな動作によって確実に制御を行うことができる。
なお、本発明において、流体圧力源となる流体、制御用流体圧を発生させる流体、調整用流体圧を発生させる流体の種別については特定のものに限定されるものではない。なお、制御用流体圧を発生させる流体、調整用流体圧を発生させる流体に油を採用することで、一般的な油圧部材を用いて容易に油圧回路を構成することができる。 Further, if the sub-valve is provided with a piston that performs a stroke operation as an operation when the fluid pressure exceeds, and the pressure reducing means is operated according to the operation of the piston, the control can be reliably performed by a mechanical operation.
In the present invention, the type of the fluid that becomes the fluid pressure source, the fluid that generates the control fluid pressure, and the fluid that generates the adjustment fluid pressure is not limited to a specific one. It should be noted that a hydraulic circuit can be easily configured using a general hydraulic member by employing oil as the fluid that generates the control fluid pressure and the fluid that generates the adjustment fluid pressure.

以上説明したように、本発明の流体圧リリーフ弁によれば、流体圧源とリリーフ側とにそれぞれ連通し、互いに弁流路を介して連通する流体圧源側ポートとリリーフ側ポートとを有し、制御用流体圧を受けて前記弁流路を閉じ、該制御用流体圧の受圧減少によって前記弁流路を開く弁体を備える主弁と、前記流体圧源からの流体圧と調整用流体圧とを受け、前記流体圧源からの流体圧が調整用流体圧を上回ると流体圧超過時動作をする副弁と、該副弁の流体圧超過時動作に従って前記主弁における制御用流体圧の受圧を減少させて前記弁流路を開放させる減圧手段とを備えるので、流体圧源からの流体圧をシステム最大圧力以下の所定圧力に維持、制限することができ、水圧シリンダー等の流体圧利用側で、システム最大圧力が負荷されるものとして設計・製作する必要がなくなる。また圧力規制によりそれ以上の圧力を水圧シリンダー等の作動機器に作用させないための過負荷防止を行なうことが可能となる。   As described above, according to the fluid pressure relief valve of the present invention, the fluid pressure source side port and the relief side port communicate with the fluid pressure source and the relief side, respectively, and communicate with each other via the valve flow path. A main valve including a valve body that receives the control fluid pressure to close the valve flow path and opens the valve flow path by reducing the pressure received by the control fluid pressure; and for adjusting the fluid pressure from the fluid pressure source A sub-valve that receives fluid pressure and operates when the fluid pressure from the fluid pressure source exceeds the adjustment fluid pressure, and the control valve in the main valve according to the operation when the sub-valve exceeds the fluid pressure. Pressure reducing means for reducing the pressure receiving pressure to open the valve flow path, so that the fluid pressure from the fluid pressure source can be maintained and limited to a predetermined pressure below the system maximum pressure, and fluid such as a hydraulic cylinder The maximum system pressure is applied on the pressure usage side. Necessary to design and manufacture as there is no. In addition, it is possible to prevent overload so as not to apply a pressure higher than that to the hydraulic cylinders or the like due to pressure regulation.

以下、この発明の一実施形態を添付図に基づいて説明する。
なお、本発明のリリーフ弁は、この実施形態では、主弁である親弁Ａ、副弁である子弁Ｂ、油圧機器ブロックＣから構成されている。
以下に、先ず親弁Ａの構成と機能を述べる。
ブロック状の親弁ボディ１に、流体圧源側である水圧一次側に連なる親弁水圧一次側ポート２と、リリーフ側である水圧二次側に連なる親弁水圧二次側ポート３とが高さ位置を異にして形成されており、両ポート２、３間に連通する親弁弁流路４が縦方向に形成され、該親弁弁流路４に環状の親弁弁座５が設置されている。該親弁弁座５の上方側の親弁ボディ１には、上方に開口する丸穴状の空洞が形成されており、該空洞内に嵌合するようにしてスリーブ６が設置され、その内側に、前記親弁弁座５にシート面７ａを介して当接可能な親弁ピストン７が軸方向に摺動可能に配置されている。図１では、親弁ピストン７は、その軸中心を境にして親弁ピストン７が下端側にストロークした状態と、上端側にストロークした状態に分けて描かれている。
なお、スリーブ６には、前記弁流路４に連通する複数のスリーブ連通穴６ａが形成され、親弁ボディ１には、該スリープ連通穴６ａの周囲を囲むようにして前記親弁水圧二次側ポート３に連通する環状流路１ａが形成されており、これらの環状流路１ａとスリーブ連通穴６ａを介して親弁水圧一次側ポート２と、弁流路４と、親弁水圧二次側ポート３とが連通している。親弁ピストンシート面７ａは、閉弁時に上記親弁弁座５に当接して親弁水圧一次側ポート２と親弁水圧二次側ポート３を分離する。 Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.
In this embodiment, the relief valve of the present invention comprises a master valve A that is a main valve, a slave valve B that is a sub valve, and a hydraulic equipment block C.
First, the configuration and function of the parent valve A will be described first.
The block-shaped parent valve body 1 has a parent valve water pressure primary side port 2 connected to the water pressure primary side on the fluid pressure source side and a parent valve water pressure secondary side port 3 connected to the water pressure secondary side on the relief side. Are formed at different positions, and a parent valve valve passage 4 communicating between both ports 2 and 3 is formed in a vertical direction, and an annular parent valve seat 5 is installed in the parent valve passage 4. Has been. The parent valve body 1 on the upper side of the parent valve valve seat 5 is formed with a round hole-like cavity that opens upward, and a sleeve 6 is installed so as to fit in the cavity, and the inner side thereof Further, a parent valve piston 7 that can come into contact with the parent valve valve seat 5 via a seat surface 7a is disposed so as to be slidable in the axial direction. In FIG. 1, the parent valve piston 7 is depicted by being divided into a state where the parent valve piston 7 strokes toward the lower end side and a state where the parent valve piston 7 strokes toward the upper end side.
The sleeve 6 is formed with a plurality of sleeve communication holes 6 a communicating with the valve flow path 4, and the parent valve body 1 surrounds the sleep communication hole 6 a with the parent valve water pressure secondary side port. 3 is formed, and the parent valve hydraulic pressure primary side port 2, the valve flow path 4, and the parent valve hydraulic pressure secondary side port via the annular flow path 1 a and the sleeve communication hole 6 a are formed. 3 communicates. When the valve is closed, the parent valve piston seat surface 7a abuts on the parent valve valve seat 5 to separate the parent valve water pressure primary side port 2 and the parent valve water pressure secondary side port 3.

次に、前記親弁ピストン７のピストン上端部７ｂは、下方よりも大径に形成されて親弁ボディ１の上方に突出している。この親弁ボディ１の上方には、ピストン上端部７ｂが摺動可能な空洞を有するケース８が固定されており、該ケース８の上方に親弁カバー９が固定されている。
なお、親弁ピストン７が下降した時に、親弁ピストン７の上端面とケース８の内周面と親弁カバー８の下面との間で形成される空間によって、制御用流体圧室となる親弁上部油圧室１０が構成されており、該親弁上部油圧室１０と連通して外部に連なる圧油流路１１がケース８に形成されている。また、ピストン上端部７ｂの上端縁外周壁には、圧油流入凹部７ｃが環状に形成されている。 Next, the piston upper end portion 7 b of the parent valve piston 7 is formed with a larger diameter than below and protrudes above the parent valve body 1. A case 8 having a cavity in which the piston upper end portion 7 b can slide is fixed above the parent valve body 1, and a parent valve cover 9 is fixed above the case 8.
When the parent valve piston 7 is lowered, a space formed between the upper end surface of the parent valve piston 7, the inner peripheral surface of the case 8, and the lower surface of the parent valve cover 8 serves as a control fluid pressure chamber. A valve upper hydraulic chamber 10 is configured, and a pressure oil passage 11 communicating with the parent valve upper hydraulic chamber 10 and connected to the outside is formed in the case 8. Moreover, the pressure oil inflow recessed part 7c is cyclically | annularly formed in the upper end edge outer peripheral wall of the piston upper end part 7b.

また、親弁ピストン７の外周面には、ピストン上端部７ｂにおいて、油圧一次側シール１２と親弁ヘッド側ウエアリング１３と親弁ロッド側ウエアリング１４とが軸方向に順次装着されて、親弁上部油圧室１０とのシール性が保たれている。また、親弁ピストン７が上昇した際に、ピストン上端部７ｂの下端面とその下方のピストン７外周面とケース８内周面とスリーブ６上端面で形成される空間によって親弁ドレイン室１５が構成されており、該親弁ドレイン室１５は、スリーブ６から親弁ボディ１にかけて形成されて外部に連なる親弁ドレイン導通穴１６に連通しており、親弁ドレイン室１５に流入した油圧および水圧のドレインを親弁ドレイン導通穴１６を通して外部に排出している   In addition, a hydraulic primary side seal 12, a parent valve head side wear ring 13, and a parent valve rod side wear ring 14 are sequentially mounted in the axial direction on the outer peripheral surface of the parent valve piston 7 at the piston upper end 7b. The sealing performance with the valve upper hydraulic chamber 10 is maintained. When the parent valve piston 7 is raised, the parent valve drain chamber 15 is formed by the space formed by the lower end surface of the piston upper end portion 7b, the outer peripheral surface of the piston 7 below, the inner peripheral surface of the case 8, and the upper end surface of the sleeve 6. The main valve drain chamber 15 is formed from the sleeve 6 to the main valve body 1 and communicates with a main valve drain conduction hole 16 connected to the outside, and hydraulic pressure and water pressure flowing into the main valve drain chamber 15 are formed. Is drained to the outside through the parent valve drain conduction hole 16.

また、親弁ピストン７の下方側の外周面には、上方側から軸方向に順次、親弁ロッド側ウェアリング２０、親弁ロッド側水圧バックアップシール２１、親弁ロッド側水圧シール２２を装着しシールを行い水圧のリークを防いでいる。また作動水に含まれる微細なゴミや錆鉄粉でシールを傷つけることの無い様にコンタミシール２３を設けている。   Further, a parent valve rod side wear ring 20, a parent valve rod side hydraulic backup seal 21, and a parent valve rod side hydraulic seal 22 are attached to the outer peripheral surface of the lower side of the parent valve piston 7 in the axial direction from the upper side. Seals to prevent water pressure leaks. Moreover, the contamination seal | sticker 23 is provided so that the seal | sticker may not be damaged by the fine dust and rust iron powder which are contained in working water.

上記親弁Ａでは、親弁ピストン７が親弁ボディ１に組込まれたスリーブ６およびスリーブ６を固定したケース８をガイドとして上下にストローク作動する。親弁ピストン７上部の親弁上部油圧室１０には油圧ブロックＣを介して圧油を導いている。該圧油は、親弁水圧一次側ポート２にシステム最大の水圧が付与されている場合においても、親弁ピストン７を押し下げて親弁ピストンシート面７ａを上記親弁弁座５に当接させて弁流路４を閉じている。すなわち、本油圧制御によるトリガー式大流量水圧リリーフ弁においては、親弁ピストン７を油圧力で弁座５のシート面に押付けて閉弁状態を保持するものとしている。
一方、親弁上部油圧室１０の圧油圧力が所定圧以下に低下すると、親弁水圧一次側ポート２に付与される水圧によって親弁ピストン７が上昇し、親弁ピストンシート面７ａが上記親弁弁座５から離れて弁流路４が開かれて、親弁水圧一次側ポート２から親弁水圧二次側ポート３へと水がリリーフされる。 In the parent valve A, the parent valve piston 7 is moved up and down by using a sleeve 6 incorporated in the parent valve body 1 and a case 8 to which the sleeve 6 is fixed as a guide. Pressure oil is introduced into the parent valve upper hydraulic chamber 10 above the parent valve piston 7 via a hydraulic block C. The pressure oil pushes down the parent valve piston 7 to bring the parent valve piston seat surface 7a into contact with the parent valve seat 5 even when the system maximum water pressure is applied to the parent valve water pressure primary port 2. The valve flow path 4 is closed. That is, in the trigger type large flow rate water pressure relief valve by the hydraulic control, the parent valve piston 7 is pressed against the seat surface of the valve seat 5 with the oil pressure to keep the valve closed.
On the other hand, when the pressure oil pressure in the parent valve upper hydraulic chamber 10 falls below a predetermined pressure, the parent valve piston 7 rises due to the water pressure applied to the parent valve water pressure primary side port 2, and the parent valve piston seat surface 7a is The valve flow path 4 is opened away from the valve valve seat 5, and water is relieved from the parent valve water pressure primary side port 2 to the parent valve water pressure secondary side port 3.

次に子弁Ｂの構成と機能を図１および図２に基づいて述べる。
子弁Ｂは、親弁ボディ１の側壁に横向きにして取り付けられており、筒状の子弁ボディ３０内に子弁ピストン３１が軸方向に摺動可能に配置されている。なお、図１、２では、子弁ピストン３１は、その軸中心を境にして子弁ピストン３１が一端側にストロークした状態と、他端側にストロークした状態に分けて描かれている。
子弁ボディ１の一端（水圧側）には、子弁水圧カバー３２が固定されており、この子弁水圧カバー３２の内面と子弁ボディ３０の内面と子弁ピストン３１の先端面とで形成される空間によって子弁水圧側チャンバ室３３が構成されている。この子弁水圧側チャンバ室３３は、子弁ボディ３１の水圧側端部に形成した子弁水圧側導通穴３５に連通している。子弁水圧側導通穴３５は、前記親弁ボディ１に形成され、一端が親弁水圧一次側ポート２に連通する水圧一次側子バルブ導通穴２５に連通しており、これら導通穴２５、３５によって水圧一次側の水が子弁水圧側チャンバ室３３に導入されて一次側の水圧が子弁水圧側ピストン端３１ａに付与されるように構成されている。子弁ピストン３１の水圧側の外周面には、軸方向に順次、子弁水圧側シール３６および子弁水圧側バックアップシール３７、子弁水圧側ウェアリング３８を装着してシールを行い水圧のリークを防いでいる。また作動水に含まれる微細なゴミや錆鉄粉でシールを傷つけることの無い様に先端側に子弁水圧コンタミシール３９を装着している。 Next, the configuration and function of the child valve B will be described with reference to FIGS.
The child valve B is attached to the side wall of the parent valve body 1 in a lateral direction, and a child valve piston 31 is disposed in the cylindrical child valve body 30 so as to be slidable in the axial direction. In FIGS. 1 and 2, the child valve piston 31 is depicted by being divided into a state where the child valve piston 31 strokes toward one end side and a state where the child valve piston 31 strokes toward the other end side.
A child valve water pressure cover 32 is fixed to one end (hydraulic side) of the child valve body 1, and is formed by the inner surface of the child valve water pressure cover 32, the inner surface of the child valve body 30, and the front end surface of the child valve piston 31. A child valve water pressure side chamber chamber 33 is constituted by the space formed. The child valve water pressure side chamber 33 communicates with a child valve water pressure side conduction hole 35 formed at the water pressure side end of the child valve body 31. The child valve water pressure side conduction hole 35 is formed in the parent valve body 1, and one end thereof communicates with a water pressure primary side child valve conduction hole 25 communicating with the parent valve water pressure primary side port 2. Thus, the water on the primary side of the hydraulic pressure is introduced into the sub-valve water pressure side chamber chamber 33, and the water pressure on the primary side is applied to the sub-valve water pressure side piston end 31a. On the outer peripheral surface on the water pressure side of the child valve piston 31, a child valve water pressure side seal 36, a child valve water pressure side backup seal 37, and a child valve water pressure side wear ring 38 are sequentially attached in the axial direction to perform sealing, thereby leaking water pressure. Is preventing. In addition, a child valve hydraulic pressure contamination seal 39 is mounted on the tip side so as not to damage the seal with fine dust or rust iron powder contained in the working water.

上記シール３６、３７、ウェアリング３８の内側では、子弁ピストン３１の中央部がやや大径に形成されており、この大径部を収納するように子弁ボディ１に大径の空隙が形成されている。この大径の空隙と子弁ピストン３１の大径部の肩部との間で形成される空間によって子弁ドレイン室４０が構成されており、この子弁ドレイン室４０に流入する油圧および水圧のドレインは子弁ボディ１に設けた子弁ドレイン導通穴４１を通じてバルブ外部に排出される。   Inside the seals 36 and 37 and the wear ring 38, the central portion of the child valve piston 31 is formed with a slightly larger diameter, and a large-diameter gap is formed in the child valve body 1 so as to accommodate the larger diameter portion. Has been. A child valve drain chamber 40 is constituted by a space formed between the large-diameter gap and the shoulder of the large-diameter portion of the child valve piston 31, and the hydraulic pressure and water pressure flowing into the child valve drain chamber 40 are configured. The drain is discharged to the outside of the valve through a child valve drain conduction hole 41 provided in the child valve body 1.

上記子弁ピストン３１の大径部の下端が位置する子弁ボディ１には、大径部下端を囲むように大径に形成された子弁油圧室４２が設けられており、該子弁油圧室４２は、子弁ボディ１に形成した子弁油圧側導通穴４３に連通しており、子弁油圧側導通穴４３は、油圧ブロックＣに接続されて圧油が導入されるように構成されている。   The child valve body 1 in which the lower end of the large diameter portion of the child valve piston 31 is positioned is provided with a child valve hydraulic chamber 42 formed in a large diameter so as to surround the lower end of the large diameter portion. The chamber 42 communicates with a child valve hydraulic side conduction hole 43 formed in the child valve body 1, and the child valve hydraulic side conduction hole 43 is connected to the hydraulic block C and configured to introduce pressure oil. ing.

子弁ピストン３１の外周面には、上記大径部において、軸方向に順次、子弁油圧側ウェアリング４５、子弁ドレイン逆流防止用シール４６、子弁油圧側シール４７を装着してシールを行い、油圧のリークを防いでいる。
また子弁ピストン３１は、油圧側ピストン端部３１ｂが上記子弁ボディ３１端から突出しており、その突出部において子弁油圧側カバー５０と子弁油圧側ロッドシール５１とが設けられて前記子弁油圧室４２が密閉されている。子弁ピストン３１の油圧側ピストン端部３１ｂは、子弁油圧側ロッドシール５１のさらに端部側で子弁ブッシュ５２を摺動可能に挿通しており、子弁ブッシュ５２と油圧側ピストン端部３１ｂとの間に子弁油圧側ダストシール５３が配置されている。子弁ブッシュ５２は、子弁油圧側カバー５０の端部に固定された子弁ブッシュ押さえ５４によって固定されている。また、油圧側ピストン端部３１ｂは、子弁ブッシュ押さえ５４を超えて外部に突出しており、その先端には、トリガーロッド５５が突き出し位置の調整を行えるようにねじ込まれている。突き出し位置の調整が行われたトリガーロッド５５は、ロックナット５６によって位置固定が行なわれる。
上記子弁Ｂでは、子弁ピストン３１を介して、子弁水圧側チャンバー室３３で得られる水圧と、子弁油圧室４２で得られる調整用油圧（調整用流体圧）との差圧が得られる。水圧が調整用油圧を超える場合、その差圧によって流体圧源圧超過動作として子弁ピストン３１が油圧側端部へと押されるようにストロークし、トリガーロッド５５が前進する。一方、水圧が調整用油圧を下回ると、その差圧によって、子弁ピストン３１が水圧側端部へと押されるようにストロークし、トリガーロッド５５が後退する。 On the outer peripheral surface of the child valve piston 31, a child valve hydraulic side wear ring 45, a child valve drain backflow prevention seal 46, and a child valve hydraulic side seal 47 are attached in order in the axial direction at the large diameter portion. To prevent hydraulic leaks.
The child valve piston 31 has a hydraulic side piston end 31b protruding from the end of the child valve body 31, and a child valve hydraulic side cover 50 and a child valve hydraulic side rod seal 51 are provided at the protruding portion. The valve hydraulic chamber 42 is sealed. The hydraulic-side piston end 31b of the child valve piston 31 is slidably inserted through the child valve bush 52 on the further end side of the child valve hydraulic-side rod seal 51, and the child valve bush 52 and the hydraulic side piston end portion are inserted. A sub-valve hydraulic pressure side dust seal 53 is arranged between 31b and 31b. The child valve bush 52 is fixed by a child valve bush presser 54 fixed to the end of the child valve hydraulic side cover 50. Further, the hydraulic side piston end portion 31b protrudes beyond the child valve bush presser 54, and a trigger rod 55 is screwed into the tip so that the protruding position can be adjusted. The position of the trigger rod 55 whose protrusion position has been adjusted is fixed by a lock nut 56.
In the child valve B, a pressure difference between the water pressure obtained in the child valve hydraulic pressure side chamber 33 and the adjustment hydraulic pressure (adjustment fluid pressure) obtained in the child valve hydraulic chamber 42 is obtained via the child valve piston 31. It is done. When the water pressure exceeds the adjustment hydraulic pressure, the trigger valve 55 moves forward by the differential pressure so that the child valve piston 31 is pushed toward the hydraulic pressure side end as the fluid pressure source pressure excess operation. On the other hand, when the hydraulic pressure falls below the adjustment hydraulic pressure, the differential valve pressure causes the child valve piston 31 to stroke so as to be pushed toward the hydraulic pressure side end, and the trigger rod 55 moves backward.

次に油圧機器ブロックＣの構成と機能を述べる。一例として本ブロックには油圧源より２１ＭＰａの圧油が供給され、制御用圧油ライン６０と調整用圧油ライン７０とに分岐している。制御用圧油ライン６０では、閉弁油圧力設定用減圧弁６１を介してチェック弁６２、絞り弁６３、電磁弁６４が介設され、さらに子弁のトリガーロッド５５により制御されるピン式切換弁６５が介設されている。ピン式切換弁６５は、トリガーロッド５５が後退した位置にあるときに開き、トリガーロッド５５が前進したときに閉じるようにされている。   Next, the configuration and function of the hydraulic equipment block C will be described. As an example, this block is supplied with 21 MPa of pressure oil from a hydraulic source, and branches into a control pressure oil line 60 and an adjustment pressure oil line 70. In the control pressure oil line 60, a check valve 62, a throttle valve 63, and an electromagnetic valve 64 are provided via a valve closing oil pressure setting pressure reducing valve 61, and a pin type switching controlled by a trigger rod 55 of a child valve. A valve 65 is interposed. The pin type switching valve 65 is opened when the trigger rod 55 is in the retracted position, and is closed when the trigger rod 55 is advanced.

また、制御用圧油ライン６０は、ピン式切換弁６５の下流側でチェック弁６６に至る圧油供給ライン６０ａとポペット弁６８に至るポペット弁閉止ライン６０ｂとに分岐しており、供給ライン６０ａは親弁の圧油流路１１に連通している。圧油タンクライン６０ｄは、ポペット弁６８の下流側で圧油タンク（図示しない、以下同じ）に接続されており、圧油が供給されている際には、ポペット弁６８が閉じられて圧油タンクへの接続が解かれている。また、圧油流路１１は、排油ライン６０ｃを介してポペット弁６８に接続されており、ポペット弁６８が開くことによって圧油流路１１と圧油タンク側とが連通する。上記ピン式切替弁６５、ポペット弁６８、圧油タンクライン６０ｄ、排油ライン６０ｃによって本発明の減圧手段が構成されている。
上記制御用圧油ライン６０では、電磁弁６４を常に励磁することで、閉弁油圧力設定用減圧弁６１で１８ＭＰａに減圧された油圧（制御用流体圧）を発生させ親弁ピストン７の閉弁状態を作る。 The control pressure oil line 60 is branched into a pressure oil supply line 60a that reaches the check valve 66 on the downstream side of the pin type switching valve 65 and a poppet valve closing line 60b that reaches the poppet valve 68. Is communicated with the pressure oil passage 11 of the parent valve. The pressure oil tank line 60d is connected to a pressure oil tank (not shown, the same applies hereinafter) on the downstream side of the poppet valve 68, and when the pressure oil is supplied, the poppet valve 68 is closed to pressurize the pressure oil. Connection to tank is broken. Moreover, the pressure oil flow path 11 is connected to the poppet valve 68 via the oil drain line 60c, and when the poppet valve 68 is opened, the pressure oil flow path 11 and the pressure oil tank side communicate with each other. The above-mentioned pin type switching valve 65, poppet valve 68, pressure oil tank line 60d, and oil discharge line 60c constitute the pressure reducing means of the present invention.
In the control pressure oil line 60, the solenoid valve 64 is always excited to generate a hydraulic pressure (control fluid pressure) reduced to 18 MPa by the valve closing oil pressure setting pressure reducing valve 61 to close the parent valve piston 7. Create a valve state.

一方、調整用圧油ライン７０では、油圧力制限用減圧弁７１、油圧力保持用チェック弁７２、圧力変動吸収用油圧アキュムレータ７３、圧力スイッチ７４、子弁ピストン作動時の水圧力設定用の油圧リリーフ弁７５を介して子弁油圧側導通穴４３に接続されている。 上記調整用圧油ライン７０では、油圧力制限用減圧弁７１で１８ＭＰａに減圧された油圧（調整用油圧）を発生させ、子弁ピストン３１の全閉状態を作る。子弁ピストン作動時の水圧力設定用の油圧リリーフ弁７５を１７ＭＰａにセットする。チェック弁７２で油圧を封じ込め、さらに子弁ピストン３１がストローク作動したときの圧力変動をアキュムレータ７３で抑えている。
なお、図中８０は、水圧シリンダなどの一次水圧利用側である。 On the other hand, in the adjustment pressure oil line 70, an oil pressure limiting pressure reducing valve 71, an oil pressure holding check valve 72, a pressure fluctuation absorbing hydraulic accumulator 73, a pressure switch 74, and a hydraulic pressure for setting water pressure when the child valve piston is operated. It is connected to the child valve hydraulic side conduction hole 43 through a relief valve 75. In the adjusting pressure oil line 70, the hydraulic pressure (adjusting hydraulic pressure) reduced to 18 MPa by the oil pressure limiting pressure reducing valve 71 is generated to make the child valve piston 31 fully closed. The hydraulic relief valve 75 for setting the water pressure when the child valve piston is operated is set to 17 MPa. The check valve 72 contains oil pressure, and the accumulator 73 suppresses pressure fluctuation when the sub-valve piston 31 is stroked.
In the figure, reference numeral 80 denotes a primary water pressure use side such as a water pressure cylinder.

以下に、上記実施形態の動作について説明する。
上記実施形態では親弁ピストン７と並列に子弁ピストン３１を設置し、この子弁ピストン３１を、調整用圧油ライン７０を介して供給され、油圧リリーフ弁７５で設定される任意の設定水圧力に見合った油圧力で押さえ付けていてるものである。一次側の水圧力がこの油圧力に打ち勝った瞬間に子弁ピストン３１がストローク作動して、トリガーロッド５５によってピン式切換弁６５をメカニカルに切換えることで圧油の供給が停止されるとともに、親弁ピストン７を閉弁状態にしているポペット弁６８を瞬時に切換え、親弁上部油圧室１０が油圧タンクラインＴＯにつながる。親弁ピストン７は閉弁力を失い、同時に水圧力によって上方ヘストローク作動し水圧一次側Ｐが水圧タンクラインＴにつながり、圧抜き動作が行なわれ全開となる。本発明において、子弁ピストン３１の油圧力を上記のように油圧リリーフ弁７５で任意に設定することで、システム最大圧力より低い圧力を任意に得ている。またこの圧力規制によりそれ以上の圧力を作動機器に作用させないための過負荷防止を行なっている。 The operation of the above embodiment will be described below.
In the above embodiment, the child valve piston 31 is installed in parallel with the parent valve piston 7, and this child valve piston 31 is supplied via the adjusting pressure oil line 70 and is optionally set water set by the hydraulic relief valve 75. It is pressed down with the oil pressure commensurate with the pressure. At the moment when the primary water pressure overcomes this oil pressure, the sub-valve piston 31 performs a stroke operation, and the pin type switching valve 65 is mechanically switched by the trigger rod 55 to stop the supply of pressure oil, and switching the poppet valve 68 has a valve piston 7 in a closed state instantaneously, Oyaben upper hydraulic chamber 10 is connected to the hydraulic tank line T O. The parent valve piston 7 loses its closing force, and at the same time, is actuated upwardly by the water pressure to connect the water pressure primary side P to the water pressure tank line T, and the pressure releasing operation is performed to be fully opened. In the present invention, the oil pressure of the child valve piston 31 is arbitrarily set by the hydraulic relief valve 75 as described above, whereby a pressure lower than the system maximum pressure is arbitrarily obtained. In addition, this pressure regulation prevents overload so that no higher pressure is applied to the operating equipment.

一方、水圧一次側Ｐの圧力が低下すると子弁では油圧力が一次側水圧に勝り、子弁ピストン３１は油圧力によって押し戻され、トリガーロッド５５の後退によってピン式切換弁６５が復帰し（開き）、親弁上部油圧室１０に油圧が送られるとともに、ポペット弁６８が閉じて親弁上部油圧室１０と油圧タンクラインＴＯとの接続が解かれる。これにより親弁上部油圧室１０では油圧による閉弁力が回復し、親弁ピストン７は下方ヘストロークし水圧一次側Ｐを密閉状態とする。水圧一次側Ｐは水圧源アキュムレータにつながっており再び水圧一次側圧力Ｐが上昇し、任意の設定圧力に達した時点でリリーフ作動を繰り返す。
これを連続して繰り返し、水圧回路の圧力は任意の設定圧力に一定に保たれる。 On the other hand, when the pressure on the water pressure primary side P decreases, the oil pressure at the child valve exceeds the water pressure on the primary side, the child valve piston 31 is pushed back by the oil pressure, and the pin type switching valve 65 is returned (opened) by the retraction of the trigger rod 55. ), together with the Oyaben upper hydraulic chamber 10 pressure is sent, the poppet valve 68 is connected to the hydraulic tank line T O and the parent valve upper hydraulic chamber 10 is released to close. As a result, the valve closing force due to the hydraulic pressure is recovered in the parent valve upper hydraulic chamber 10, and the parent valve piston 7 strokes downward to bring the hydraulic primary side P into a sealed state. The water pressure primary side P is connected to a water pressure source accumulator, and when the water pressure primary side pressure P rises again and reaches an arbitrary set pressure, the relief operation is repeated.
This is repeated continuously, and the pressure of the hydraulic circuit is kept constant at an arbitrary set pressure.

以上のように上記実施形態によって、流路圧力をメカニカルに検出し流路をタンクラインに開弁することで水圧シリンダーの圧力制限を可能とする。例えば流体源である水圧源のアキュムレータと、利用側である水圧シリンダーをつなぐ配管流路の間に組込むことができる大流量水圧リリーフ弁が得られる。配管流路中に組込んだバルブブロックなどから枝状に主弁ピストンと副弁ピストンを設置し、主弁ピストンはシステム最大圧力下で開くことの無い油圧力にて通常は閉弁状態とする。副弁ピストンはシステム最大圧力より低い、規制したい任意の設定水圧力に見合った油圧力で押さえ付ける。この油圧力は減圧弁、リリ−フ弁などにて自由に設定できるようにするのが望ましい。水圧力がこの油圧力に打ち勝った瞬間に副弁ピストンがストローク作動してピン式切換弁をメカニカルに切換えることで、親弁ピストンを閉弁状態にしているポペット弁を瞬時に全開とし、親弁上部油圧室が油圧タンクラインにつながるものである。   As described above, according to the above embodiment, the pressure of the hydraulic cylinder can be limited by mechanically detecting the flow path pressure and opening the flow path to the tank line. For example, a high flow rate water pressure relief valve can be obtained that can be incorporated between the accumulator of the water pressure source that is the fluid source and the pipe flow path that connects the water pressure cylinder that is the user side. A main valve piston and a sub-valve piston are installed in a branch shape from a valve block or the like incorporated in the piping flow path, and the main valve piston is normally closed with hydraulic pressure that does not open under the maximum system pressure. . The sub-valve piston is pressed with an oil pressure that is lower than the system maximum pressure and that matches the set water pressure you want to regulate. It is desirable that the oil pressure can be freely set by a pressure reducing valve, a relief valve or the like. At the moment when the water pressure overcomes this oil pressure, the sub-valve piston strokes and mechanically switches the pin type switching valve. The upper hydraulic chamber is connected to the hydraulic tank line.

従来のアキュムレータ蓄圧式水圧駆動システムでは水圧シリンダー等のアクチュエータ類は全て、システム最大圧力３０ＭＰａが負荷されるものとして設計・製作しなければならなかったが、上記実施形態によれば、任意の設定圧力でメカニカルに開弁し、流路が全開となる構造を採用することで、システム最大圧力より低い圧力を任意に得ることが可能となる。また、この圧力規制によりそれ以上の圧力を水圧シリンダー等の作動機器に作用させないための過負荷防止を行なうことが可能となる。おおむねリリーフ流量６５００リッター／分程度にて、最大使用圧力２３ＭＰａの圧力制限が可能となり、最大圧力より低い圧力に制限して使用することが実現できた。   In the conventional accumulator accumulator hydraulic drive system, all actuators such as a hydraulic cylinder had to be designed and manufactured to be loaded with a system maximum pressure of 30 MPa, but according to the above embodiment, any set pressure can be set. Thus, it is possible to arbitrarily obtain a pressure lower than the system maximum pressure by adopting a structure in which the valve is mechanically opened and the flow path is fully opened. In addition, this pressure regulation makes it possible to prevent overload so that no higher pressure is applied to the operating device such as a hydraulic cylinder. In general, at a relief flow rate of about 6500 liters / minute, a pressure limit of a maximum working pressure of 23 MPa was possible, and it was possible to use it with a pressure lower than the maximum pressure.

以上、本発明について上記実施形態に基づいて説明したが、本発明は、上記実施形態の説明に限定されるものではなく、本発明の範囲内において適宜変更が可能である。   Although the present invention has been described based on the above embodiment, the present invention is not limited to the description of the above embodiment, and can be appropriately changed within the scope of the present invention.

本発明の一実施形態のトリガー式大流量水圧リリーフ弁を示す図であり、（ａ）図は（ｂ）図のＩ−Ｉ線平面断面図、（ｂ）図は縦断面図である。BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the trigger type | mold large flow rate water pressure relief valve of one Embodiment of this invention, (a) A figure is the II sectional view taken on the line of (b) figure, (b) The figure is a longitudinal cross-sectional view. 同じくトリガー式大流量水圧リリーフ弁の副弁の断面図である。It is a sectional view of a sub valve of a trigger type large flow rate water pressure relief valve similarly. 同じくトリガー式大流量水圧リリーフ弁の回路模式図である。It is a circuit schematic diagram of a trigger type large flow rate water pressure relief valve. 従来の直動型リリーフ弁の縦断面図である。It is a longitudinal cross-sectional view of the conventional direct acting type relief valve.

符号の説明Explanation of symbols

Ａ 親弁
Ｂ 子弁
Ｃ 油圧機器ブロック
Ｐ 水圧一次側ポート
Ｔ 水圧二次側ポート
ＰＯ 油圧一次側ポート
ＴＯ 油圧二次側ポート
１ 親弁ボディー
２ 親弁水圧一次側ポート
３ 親弁水圧二次側ポート
４ 親弁弁流路
５ 親弁弁座
６ スリーブ
７ 親弁ピストン
７ａ 親弁ピストンシート面
７ｂ 親弁ピストン上端部
８ ケース
１０ 親弁上部油圧室
１１ 親弁圧油導入路
３０ 子弁ボディー
３１ 子弁ピストン
３１ａ 子弁水圧側ピストン端
３１ｂ 子弁油圧側ピストン端
３２ 子弁水圧側カバー
３３ 子弁水圧側チャンバー室
３５ 子弁水圧側導通穴
４２ 子弁油圧室
４３ 子弁油圧側導通穴
５５ トリガーロッド
６０ 制御用圧油ライン
６０ａ 制御油ライン
６０ｂ ポペット弁閉止ライン
６０ｃ 排油ライン
６０ｄ 油圧タンクライン
６１ 閉弁油圧力設定用減圧弁
６５ ピン式切換弁
６８ ポペット弁
７０ 調整用圧油ライン
７１ 油圧力制限用減圧弁
７５ 油圧リリーフ弁
８０ 一次水圧利用側 A Oyaben B Koben C hydraulic equipment block P pressure primary port T pressure secondary port P O Hydraulic primary port T O hydraulic secondary port 1 Oyaben body 2 Oyaben pressure primary port 3 Oyaben pressure two Secondary port 4 Parent valve flow path 5 Parent valve valve seat 6 Sleeve 7 Parent valve piston 7a Parent valve piston seat surface 7b Parent valve piston upper end portion 8 Case 10 Parent valve upper hydraulic chamber 11 Parent valve pressure oil introduction path 30 Child valve Body 31 Child valve piston 31a Child valve water pressure side piston end 31b Child valve oil pressure side piston end 32 Child valve water pressure side cover 33 Child valve water pressure side chamber chamber 35 Child valve water pressure side conduction hole 42 Child valve hydraulic pressure chamber 43 Child valve hydraulic pressure side conduction Hole 55 Trigger rod 60 Pressure oil line for control 60a Control oil line 60b Poppet valve closing line 60c Oil drain line 60d Hydraulic tank line 61 Valve closing oil pressure setting Use pressure reducing valve 65 pin selector valve 68 poppet valve 70 for adjusting the pressure oil line 71 hydraulic force limiting pressure reducing valve 75 the hydraulic relief valve 80 primary pressure utilization side

Claims (6)

流体圧源とリリーフ側とにそれぞれ連通し、互いに弁流路を介して連通する流体圧源側ポートとリリーフ側ポートとを有し、制御用流体圧を受けて前記弁流路を閉じ、該制御用流体圧の受圧減少によって前記弁流路を開く弁体を備える主弁と、前記流体圧源からの流体圧と調整用流体圧とを受け、前記流体圧源からの流体圧が調整用流体圧を上回ると流体圧源圧超過時動作をする副弁と、該副弁の流体圧源圧超過時動作に従って前記主弁における制御用流体圧の受圧を減少させて前記弁流路を開放させる減圧手段とを備えることを特徴とする流体圧リリーフ弁。 A fluid pressure source side port and a relief side port that communicate with the fluid pressure source and the relief side, respectively, and communicate with each other via the valve flow path, receive the control fluid pressure, and close the valve flow path; The main valve having a valve body that opens the valve flow path by reducing the pressure of the control fluid pressure, and the fluid pressure from the fluid pressure source and the adjustment fluid pressure are received, and the fluid pressure from the fluid pressure source is for adjustment. A sub-valve that operates when the fluid pressure source pressure is exceeded when the fluid pressure is exceeded, and the valve flow path is opened by decreasing the pressure of the control fluid pressure received by the main valve according to the operation of the sub-valve when the fluid pressure source pressure is exceeded. A fluid pressure relief valve comprising: a pressure reducing means for causing the fluid pressure relief. 前記主弁は、前記制御用流体圧の受圧減少時に、流体圧源からの流体圧によって弁体が動作して弁流路を開放するように構成されていることを特徴とする請求項１記載の流体圧リリーフ弁。 The said main valve is comprised so that a valve body may operate | move with the fluid pressure from a fluid pressure source, and a valve flow path may be open | released when the pressure-receiving pressure of the said control fluid pressure is reduced. Fluid pressure relief valve. 前記主弁の弁体は、流体圧源からの流体圧と、制御用流体圧の差圧によって動作するものであることを特徴とする請求項１または２に記載の流体圧リリーフ弁。 The fluid pressure relief valve according to claim 1 or 2, wherein the valve body of the main valve is operated by a differential pressure between a fluid pressure from a fluid pressure source and a control fluid pressure. 前記制御用流体圧は、流体圧源の最大圧力以内において圧力の設定調整が可能とされていることを特徴とする請求項１〜３のいずれかに記載の流体圧リリーフ弁。 The fluid pressure relief valve according to any one of claims 1 to 3, wherein the control fluid pressure can be set and adjusted within a maximum pressure of a fluid pressure source. 前記主弁は、制御用流体が導入されて弁体に圧力を付加する制御用流体圧受圧室を備えており、前記制御用流体圧の受圧減少は、前記制御用流体圧受圧室から制御用流体を開閉弁を介して外部に流出させることにより行うことを特徴とする請求項１〜４のいずれかに記載の流体圧リリーフ弁。 The main valve includes a control fluid pressure receiving chamber that introduces a control fluid and applies pressure to the valve body, and the control fluid pressure receiving pressure is decreased from the control fluid pressure receiving chamber. The fluid pressure relief valve according to any one of claims 1 to 4, wherein the fluid pressure is made to flow outside through an on-off valve. 前記副弁は、前記流体圧源からの流体圧と調整用流体圧との差圧によって少なくとも流体圧超過時動作としてストローク動作するピストンを備え、該ピストンのストローク動作に従って前記減圧手段を動作させるものであることを特徴とする請求項１〜５のいずれかに記載の流体圧リリーフ弁。







The sub-valve includes a piston that performs a stroke operation as an operation at least when the fluid pressure is exceeded by a differential pressure between a fluid pressure from the fluid pressure source and an adjustment fluid pressure, and operates the pressure reducing unit according to the stroke operation of the piston. The fluid pressure relief valve according to any one of claims 1 to 5, wherein:







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Publication number Priority date Publication date Assignee Title
CN103363163A (en) * 2012-03-27 2013-10-23 上海御能动力科技有限公司 Decompression valve for electro-hydraulic servo injection modeling machine
CN107885245A (en) * 2018-01-03 2018-04-06 福建瑞铼泊流体装备有限公司 A kind of intelligent pressure control system
CN113374907A (en) * 2021-06-29 2021-09-10 西安航天动力试验技术研究所 Adjustable air pressure type pressure relief device and water hammer suppression method based on same
KR102724222B1 (en) 2019-12-20 2024-10-31 캐논 가부시끼가이샤 Valve apparatus, holding apparatus, lithography apparatus, and method of manufacturing article

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103363163A (en) * 2012-03-27 2013-10-23 上海御能动力科技有限公司 Decompression valve for electro-hydraulic servo injection modeling machine
CN107885245A (en) * 2018-01-03 2018-04-06 福建瑞铼泊流体装备有限公司 A kind of intelligent pressure control system
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CN113374907A (en) * 2021-06-29 2021-09-10 西安航天动力试验技术研究所 Adjustable air pressure type pressure relief device and water hammer suppression method based on same

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