JPH0640409U - Pressure compensation valve - Google Patents
Pressure compensation valveInfo
- Publication number
- JPH0640409U JPH0640409U JP7526092U JP7526092U JPH0640409U JP H0640409 U JPH0640409 U JP H0640409U JP 7526092 U JP7526092 U JP 7526092U JP 7526092 U JP7526092 U JP 7526092U JP H0640409 U JPH0640409 U JP H0640409U
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- port
- valve
- pressure chamber
- spool
- Prior art date
- Legal status (The legal status 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 status listed.)
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Abstract
(57)【要約】 （修正有）
【構成】 弁本体２０に入口ポート２３と出口ポート２
４を連通、遮断する弁２５を設けてチェック弁部２８と
し、前記弁本体２０に第１・第２・第３ポート２９，３
０，３１を形成し、その第２ポート３０と第３ポート３
１を連通・遮断するスプール３３を嵌挿して第１圧力室
３４と第２圧力室３５と第３圧力室３６を構成し、その
スプール３３をばね３８で押して弁２５に当接し、前記
第３圧力室３６を第１ポート２９と第３ポート３１に連
通する切換弁５０を設けたもの。
【効果】 １つの油圧ポンプの吐出圧油を複数のアクチ
ュエータに供給する油圧回路に設けることでシャトル弁
を用いずに各アクチュエータに流量分配して供給できる
し、切換弁５０を切換えることで圧力補償特性を変更で
きる。
(57) [Summary] (Correction) [Structure] Inlet port 23 and outlet port 2 in valve body 20
A check valve portion 28 is provided by providing a valve 25 for connecting and disconnecting 4 and the valve body 20 is provided with first, second and third ports 29, 3
0, 31, forming the second port 30 and the third port 3
A first pressure chamber 34, a second pressure chamber 35, and a third pressure chamber 36 are formed by inserting a spool 33 that connects and disconnects 1 to each other, and the spool 33 is pressed by a spring 38 to abut the valve 25. A switching valve 50 that connects the pressure chamber 36 to the first port 29 and the third port 31 is provided. [Effect] By providing the discharge pressure oil of one hydraulic pump to a plurality of actuators in a hydraulic circuit, the flow rate can be distributed and supplied to each actuator without using a shuttle valve, and the pressure can be compensated by switching the switching valve 50. You can change the characteristics.
Description
【０００１】[0001]
本考案は、１つの油圧ポンプの吐出圧油を複数のアクチュエータに流量分配し て供給する油圧回路等に用いられる圧力補償弁に関する。 The present invention relates to a pressure compensating valve used in a hydraulic circuit or the like that distributes the discharge pressure oil of one hydraulic pump to a plurality of actuators in a flow rate distribution manner.
【０００２】[0002]
１つの油圧ポンプの吐出圧油を複数のアクチュエータに供給すると、負荷圧の 低いアクチュエータにのみ圧油が供給されてしまうので、例えば特開昭６０−１ １７０６号公報に示す油圧回路が知られている。すなわち各アクチュエータに接 続した方向制御弁の入口側に圧力補償弁をそれぞれ設け、各圧力補償弁を各アク チュエータの負荷圧における最も高い負荷圧でセットし、異なる負荷圧の複数の アクチュエータに油圧ポンプの吐出圧油を流量分配して供給できるようにした油 圧回路である。 When the pressure oil discharged from one hydraulic pump is supplied to a plurality of actuators, the pressure oil is supplied only to the actuator having a low load pressure. Therefore, for example, the hydraulic circuit disclosed in Japanese Patent Laid-Open No. Sho 60-11706 is known. There is. That is, a pressure compensating valve is provided on the inlet side of the directional control valve connected to each actuator, each pressure compensating valve is set at the highest load pressure among the actuators, and hydraulic pressure is applied to multiple actuators with different load pressures. This is an oil pressure circuit that allows the discharge pressure oil of the pump to be distributed and supplied.
【０００３】 かかる油圧回路に用いる圧力補償弁は高圧側圧力室と低圧側圧力室の圧力差及 び入口圧力と出口圧力の圧力差によって出力圧を制御する構造であるから、低圧 側圧力室に最も高い負荷圧を導入する必要があり、このために各アクチュエータ の負荷圧を比較するシャトル弁が必要となる。The pressure compensating valve used in such a hydraulic circuit has a structure in which the output pressure is controlled by the pressure difference between the high pressure side pressure chamber and the low pressure side pressure chamber and the pressure difference between the inlet pressure and the outlet pressure. It is necessary to introduce the highest load pressure, which requires a shuttle valve to compare the load pressure of each actuator.
【０００４】 そこで、本出願人は先に前述の課題を解決できるようにした圧力補償弁を提案 した。 すなわち、図１に示すように弁本体１に入口ポート２と出口ポート３を連通・ 遮断する弁４を設けてチェック弁部５とし、前記弁本体１に、第１ポート６に連 通した第１圧力室７の圧力で第２ポート８と第３ポート９を連通し、第３ポート ９に連通した第２圧力室１０の圧力で第２ポート８と第３ポート９を遮断するス プール１１を設けて減圧弁部１２とし、前記スプール１１をばね１３で第２ポー ト８と第３ポート９を遮断する方向に押して前記弁４に当接した圧力補償弁。Therefore, the present applicant has previously proposed a pressure compensating valve capable of solving the above-mentioned problems. That is, as shown in FIG. 1, the valve body 1 is provided with a valve 4 that connects and disconnects the inlet port 2 and the outlet port 3 to form a check valve portion 5, and the valve body 1 is connected to the first port 6 with a first valve 6. Spool 11 that connects the second port 8 and the third port 9 with the pressure of the first pressure chamber 7 and shuts off the second port 8 and the third port 9 with the pressure of the second pressure chamber 10 that communicates with the third port 9 Is provided as a pressure reducing valve section 12, and the spool 11 is pushed by a spring 13 in a direction to shut off the second port 8 and the third port 9, and abuts against the valve 4.
【０００５】 かかる圧力補償弁であると、第１圧力室７の圧力が第２圧力室１０の圧力より も高い時にはスプール１１が弁４より離れて入口ポート２の圧力と出口ポート３ の圧力が等しくなると共に、第１圧力室７の圧力と第２圧力室１０の圧力が等し くなり、第１圧力室７の圧力が第２圧力室１０の圧力よりも低い時にはスプール １１で弁４が遮断方向に押されて出口ポート３の圧力が入口ポート２の圧力より も第２圧力室１０と第１圧力室７の圧力差だけ低くなるから、負荷圧の異なるア クチュエータの入口側に設けるこことでシャトル弁を用いずに各アクチュエータ に１つの油圧ポンプの吐出圧油を流量分配して供給できる。With such a pressure compensating valve, when the pressure in the first pressure chamber 7 is higher than the pressure in the second pressure chamber 10, the spool 11 is separated from the valve 4 so that the pressure at the inlet port 2 and the pressure at the outlet port 3 are increased. When the pressures of the first pressure chamber 7 and the pressure of the second pressure chamber 10 become equal and the pressure of the first pressure chamber 7 is lower than the pressure of the second pressure chamber 10, the valve 4 is operated by the spool 11 Since it is pushed in the shut-off direction and the pressure of the outlet port 3 becomes lower than the pressure of the inlet port 2 by the pressure difference between the second pressure chamber 10 and the first pressure chamber 7, it is provided on the inlet side of the actuators with different load pressures. With, it is possible to distribute the flow rate of the pressure oil discharged from one hydraulic pump to each actuator without using the shuttle valve.
【０００６】[0006]
かかる圧力補償弁であると、第１圧力室７の圧力と第２圧力室１０との圧力と によって圧力補償特性の設定が決定されるので、アクチュエータの種類に応じた 圧力補償特性が得られない。 With such a pressure compensating valve, since the setting of the pressure compensating characteristic is determined by the pressure of the first pressure chamber 7 and the pressure of the second pressure chamber 10, the pressure compensating characteristic corresponding to the type of actuator cannot be obtained. .
【０００７】 そこで、本考案は前述の課題を解決できるようにした圧力補償を提供すること を目的とする。Therefore, the present invention has an object to provide pressure compensation capable of solving the above-mentioned problems.
【０００８】[0008]
弁本体２０に入口ポート２３と出口ポート２４を連通・遮断する弁２５を設け てチェック弁部２８とし、前記弁本体２０に、第１ポート２９に連通した第１圧 力室３４の圧力で第２ポート３０と第３ポート３１を連通し、第３ポート３１に 連通した第２圧力室３５の圧力で第２ポート３０と第３ポート３１を遮断するス プール３３を設けて減圧弁部４２とし、前記スプール３３をばね３８で第２ポー ト３０と第３ポート３１を遮断する方向に押して前記弁２５に当接し、前記スプ ール３３を第２ポート３０を第１ポート３１に連通する方向に押す第３圧力室３ ６を形成し、この第３圧力室３６を第１ポート２９、第３ポート３１に連通制御 する切換弁５０を設けた圧力補償弁。 The valve body 20 is provided with a valve 25 that connects and disconnects the inlet port 23 and the outlet port 24 to form a check valve portion 28, and the valve body 20 is connected to the first port 29 by the pressure of the first pressure chamber 34 that communicates with the first port 29. A decompression valve section 42 is provided by providing a spool 33 that connects the second port 30 and the third port 31 and shuts off the second port 30 and the third port 31 by the pressure of the second pressure chamber 35 that communicates with the third port 31. , A direction in which the spring 33 pushes the spool 33 in a direction to shut off the second port 30 and the third port 31 and contacts the valve 25, and the spool 33 communicates with the second port 30 and the first port 31. A pressure compensating valve provided with a switching valve 50 that forms a third pressure chamber 36 that is pressed against and that controls the third pressure chamber 36 to communicate with the first port 29 and the third port 31.
【０００９】[0009]
第１圧力室３４の圧力が第２圧力室３５の圧力よりも高い時にはスプール３３ が弁２５より離れて入口ポート２３の圧力と出口ポート２４の圧力が等しくなる と共に、第１圧力室３４の圧力と第２圧力室３５の圧力が等しくなり、第１圧力 室３４の圧力が第２圧力室３５の圧力よりも低い時にはスプール３３で弁２５が 遮断方向に押されて出口ポート２４の圧力が入口ポート２３の圧力よりも第２圧 力室３５と第１圧力室３４の圧力差だけ低くなるから、負荷圧の異なるアクチュ エータの入口側に設けるこことでシャトル弁を用いずに各アクチュエータに１つ の油圧ポンプの吐出圧油に流量分配して供給できるし、切換弁５０を切換えるこ とで圧力補償特性を変更できる。 When the pressure in the first pressure chamber 34 is higher than that in the second pressure chamber 35, the spool 33 moves away from the valve 25 so that the pressure at the inlet port 23 becomes equal to the pressure at the outlet port 24, and the pressure in the first pressure chamber 34 increases. When the pressure in the first pressure chamber 34 is lower than the pressure in the second pressure chamber 35, the valve 25 is pushed in the blocking direction by the spool 33 and the pressure at the outlet port 24 becomes the inlet. Since the pressure difference between the second pressure chamber 35 and the first pressure chamber 34 becomes lower than the pressure of the port 23, it is provided on the inlet side of the actuators having different load pressures. It is possible to distribute the flow rate to the discharge pressure oil of one of the hydraulic pumps, and to change the pressure compensation characteristics by switching the switching valve 50.
【００１０】[0010]
図２に示すように、弁本体２０には一側孔２１と他側孔２２が相対向して形成 され、その一側孔２１には入口ポート２３と出口ポート２４が形成してあると共 に、弁２５が嵌挿され、その弁２５はプラグ２６に設けたストッパ杆２７で図示 位置より左方に摺動しないように規制されてチェック弁部２８を構成している。 前記他側孔２２は小径孔２２ａと大径孔２２ｂより成り、小径孔２２には第１ ・第２ポート２９，３０、大径孔２２ｂに第３ポート３１が形成されていると共 に、小径孔２２ａと大径孔２２ｂに亘って第４ポート３２が形成され、スプール ３３は小径部３３ａと大径部３３ｂで段部３３ｃを有し、そのスプール３３が他 側孔２２に嵌挿されて第１ポート２９に開口した第１圧力室３４と第３ポート３ １に開口した第２圧力室３５と第４ポート３２に開口した第３圧力室３６を構成 し、そのスプール３３はプラグ３７との間に設けたばね３８で左方に押されてス プール３３に一体的に設けた押杆３９が透孔４０より突出して前記弁２５をスト ッパ杆２７に当接しかつ各ポートを遮断し、第１圧力室３４内の圧力でスプール ３３が右方に摺動すると油孔４１で第２ポート３０と第３ポート３１を連通する ようになって減圧弁部４２を構成している。 As shown in FIG. 2, one side hole 21 and the other side hole 22 are formed in the valve body 20 so as to face each other, and an inlet port 23 and an outlet port 24 are formed in the one side hole 21. A valve 25 is fitted in the valve 25, and the valve 25 is restricted by a stopper rod 27 provided on a plug 26 so as not to slide to the left from the position shown in the drawing, thereby forming a check valve portion 28. The other side hole 22 is composed of a small diameter hole 22a and a large diameter hole 22b. The small diameter hole 22 has first and second ports 29 and 30, and the large diameter hole 22b has a third port 31. A fourth port 32 is formed across the small diameter hole 22a and the large diameter hole 22b, and the spool 33 has a small diameter portion 33a and a large diameter portion 33b with a stepped portion 33c, and the spool 33 is fitted into the other side hole 22. A first pressure chamber 34 opened to the first port 29, a second pressure chamber 35 opened to the third port 31 and a third pressure chamber 36 opened to the fourth port 32, the spool 33 of which has a plug 37. A push rod 39 integrally provided on the spool 33 is pushed to the left by a spring 38 provided between the valve 25 and the stop rod 27 so that the valve 25 abuts the stopper rod 27 and shuts off each port. Then, the spool 33 slides to the right due to the pressure in the first pressure chamber 34. Then the second port 30 with the oil hole 41 is a third port 31 constitute a pressure reducing valve 42 so as to communicate.
【００１１】 前記入口ポート２３と第２ポート３０は油孔ポンプ４３のポンプ吐出路４４に に接続してポンプ吐出圧が供給され、出口ポート２４に供給路４５が接続し、第 １ポート２９が負荷圧導入路４６に接続して第１制御圧が供給され、第３ポート ３１が負荷検出路４７に接続して第２制御圧が供給される。The inlet port 23 and the second port 30 are connected to the pump discharge passage 44 of the oil hole pump 43 to be supplied with pump discharge pressure, the outlet port 24 is connected to the supply passage 45, and the first port 29 is The first control pressure is supplied by connecting to the load pressure introducing path 46, and the second control pressure is supplied by connecting the third port 31 to the load detecting path 47.
【００１２】 前記第１ポート２９と第４ポート３２と第３ポート３１は切換弁５０で連通・ 遮断され、この切換弁５０はバネ５１で第１位置Ａに保持されて第１ポート２９ と第４ポート３２を連通し、受圧部５２の圧油で第２位置Ｂに切換えらられて第 ３ポート３１と第４ポート３２を連通している。The first port 29, the fourth port 32, and the third port 31 are connected / disconnected by a switching valve 50, and the switching valve 50 is held at a first position A by a spring 51 so that the first port 29 and the third port 31 are connected to each other. The fourth port 32 is communicated, and the pressure oil of the pressure receiving portion 52 is switched to the second position B to communicate the third port 31 and the fourth port 32.
【００１３】 次に作動を説明する。 油圧ポンプ４３のポンプ吐出圧が低圧で負荷圧導入路４６、負荷圧検出路４７ の圧力がゼロの時には弁２５、スプール３３が図２に示す位置となって供給路４ ５の圧力で弁２５が摺動して出口ポート２４と入口ポート２３が遮断して逆流を 防止する。 油圧ポンプ４３のポンプ吐出圧が高くなると図３のように弁２５が右方に押さ れて入口ポート２３と出口ポート２５が連通して出口ポート２５より供給路４５ に供給され、ストロークエンドまで弁２５が摺動すると第２ポート３０と第３ポ ート３１が連通する。 図３の状態で第１ポート２９の第１制御圧が第３ポート３１の第２制御圧より 高い場合にはスプール３３が右方に押されて第２ポート３０が油孔４１で第３ポ ート３１に連通して第３ポート３１の圧力、つまり第２制御圧は第１制御圧に見 合う圧力となり、ポンプ吐出圧と供給路４５の供給圧は等しくなる。 図３の状態で第２制御圧が第１制御圧より高い場合にはスプール３３が左方に 押されて第２ポート３０と第３ポート３１が遮断し、押杆３９で弁２５を入口ポ ート２３と出口ポート２４を遮断する方向に押すので入口ポート２３と出口ポー ト２４の開口面積が小さくなって供給路４５の供給圧がポンプ吐出圧より低くな る。Next, the operation will be described. When the pump discharge pressure of the hydraulic pump 43 is low and the pressures of the load pressure introducing path 46 and the load pressure detecting path 47 are zero, the valve 25 and the spool 33 are in the positions shown in FIG. Slides to block the outlet port 24 and the inlet port 23 and prevent backflow. When the pump discharge pressure of the hydraulic pump 43 becomes high, the valve 25 is pushed to the right as shown in FIG. When 25 slides, the second port 30 and the third port 31 communicate with each other. In the state shown in FIG. 3, when the first control pressure of the first port 29 is higher than the second control pressure of the third port 31, the spool 33 is pushed to the right and the second port 30 has the oil hole 41 and the third port. The pressure of the third port 31, which is in communication with the port 31, that is, the second control pressure becomes a pressure commensurate with the first control pressure, and the pump discharge pressure and the supply pressure of the supply passage 45 become equal. When the second control pressure is higher than the first control pressure in the state shown in FIG. 3, the spool 33 is pushed to the left to shut off the second port 30 and the third port 31, and the push rod 39 is used to open the valve 25 at the inlet port. Since the port 23 and the outlet port 24 are pushed in the blocking direction, the opening area of the inlet port 23 and the outlet port 24 becomes smaller, and the supply pressure of the supply passage 45 becomes lower than the pump discharge pressure.
【００１４】 このように、減圧弁部４２の第１圧力室３４に供給される第１制御圧が第２圧 力室３５に供給される第２制御圧よりも高い時には第２ポート３０と第３ポート ３１が連通してポンプ吐出圧が減圧されて第３ポート３１の圧力（第２制御圧） が第１ポート２９の圧力（第１制御圧）と同一となると共に、入口ポート２３の 圧力（ポンプ吐出圧）と出口ポート２４の圧力（供給圧）が同一となる。例えば ポンプ吐出圧１２０ｋｇ／ｃｍ2 、第１制御圧１００ｋｇ／ｃｍ2 の時には第２ 制御圧１００ｋｇ／ｃｍ2 、供給圧１２０ｋｇ／ｃｍ2 となる。 同様に第１制御圧よりも第２制御圧が高い場合には第２ポート３０と第３ポー ト３１が連通せずにポンプ吐出圧が第３ポート３１に供給されないと共に、弁２ ５により入口ポート２３と出口ポート２４の開口面積が減少して供給圧はポート 吐出圧よりも第２制御圧と第１制御圧の差圧分だけ低くなる。例えば、ポンプ吐 出圧１２０ｋｇ／ｃｍ2 、第１制御圧１０ｋｇ／ｃｍ2 、第２制御圧１００ｋｇ ／ｃｍ2 の時には供給圧３０ｋｇ／ｃｍ2 となる。As described above, when the first control pressure supplied to the first pressure chamber 34 of the pressure reducing valve portion 42 is higher than the second control pressure supplied to the second pressure chamber 35, the second port 30 and the second port 30 are connected to each other. The pressure of the third port 31 (the second control pressure) becomes the same as the pressure of the first port 29 (the first control pressure) because the three ports 31 communicate with each other, and the pump discharge pressure is reduced. (Pump discharge pressure) and outlet port 24 pressure (supply pressure) become the same. For example, when the pump discharge pressure is 120 kg / cm 2 and the first control pressure is 100 kg / cm 2 , the second control pressure is 100 kg / cm 2 and the supply pressure is 120 kg / cm 2 . Similarly, when the second control pressure is higher than the first control pressure, the second port 30 and the third port 31 do not communicate with each other, the pump discharge pressure is not supplied to the third port 31, and the valve 25 causes the inlet port to flow. The opening area of the port 23 and the outlet port 24 decreases, and the supply pressure becomes lower than the port discharge pressure by the pressure difference between the second control pressure and the first control pressure. For example, when the pump discharge pressure is 120 kg / cm 2 , the first control pressure is 10 kg / cm 2 , and the second control pressure is 100 kg / cm 2 , the supply pressure is 30 kg / cm 2 .
【００１５】 以上の様であるから、１つの油圧ポンプの吐出圧油を複数のアクチュエータに 供給する油圧回路において、供給路４５を方向制御弁の入口ポートに接続し、負 荷圧導入路４６に自己のアクチュエータの負荷圧を導入し、負荷圧検出路４７を 各圧力補償弁毎に連通すれば、従来と同様に各アクチュエータに流量分配して供 給できる。As described above, in the hydraulic circuit that supplies the discharge pressure oil of one hydraulic pump to the plurality of actuators, the supply passage 45 is connected to the inlet port of the directional control valve, and the load pressure introduction passage 46 is connected. If the load pressure of its own actuator is introduced and the load pressure detection path 47 is connected to each pressure compensating valve, the flow rate can be distributed and supplied to each actuator as in the conventional case.
【００１６】 以上の説明は切換弁５０がない場合であり、切換弁５０を第１位置Ａとして第 １ポート２９と第４ポート３２を連通すると第３受圧室３６に作用する第１制御 圧でスプール３３が右方に押されるので、第２制御圧が第１制御圧より高い場合 に、スプール３３が左方に押されて押杆３９で弁２５を入口ポート２３と出口ポ ート２４を遮断する方向に押す力が前述の説明の場合よりも大きくなって供給圧 が前述の説明の場合よりも低くなる圧力補償特性となる。The above description is for the case where the switching valve 50 is not provided. When the switching valve 50 is set to the first position A and the first port 29 and the fourth port 32 are communicated with each other, the first control pressure applied to the third pressure receiving chamber 36 is used. Since the spool 33 is pushed to the right, when the second control pressure is higher than the first control pressure, the spool 33 is pushed to the left and the push rod 39 moves the valve 25 to the inlet port 23 and the outlet port 24. The force for pushing in the shut-off direction is larger than that in the case described above, and the supply pressure is lower than that in the case described above.
【００１７】 切換弁５０を第２位置Ｂとした時には第３ポート３１と第４ポート３２が連通 するので、前述の説明と同じ圧力補償特性となる。When the switching valve 50 is set to the second position B, the third port 31 and the fourth port 32 communicate with each other, so that the same pressure compensation characteristic as that described above is obtained.
【００１８】[0018]
第１圧力室３４の圧力が第２圧力室３５の圧力よりも高い時にはスプール３３ が弁２５より離れて入口ポート２３の圧力と出口ポート２４の圧力が等しくなる と共に、第１圧力室３４の圧力と第２圧力室３５の圧力が等しくなり、第１圧力 室３４の圧力が第２圧力室３５の圧力よりも低い時にはスプール３３で弁２５が 遮断方向に押されて出口ポート２４の圧力が入口ポート２３の圧力よりも第２圧 力室３５と第１圧力室３４の圧力差だけ低くなる。 このようであるから、この圧力補償弁を油圧ポンプの吐出圧油を複数のアクチ ュエータに供給する油圧回路に設けることでシャトル弁を用いずに１つの油圧ポ ンプの吐出圧油を複数のアクチュエータに流量分配して供給できる。 また、第３圧力室３６に第１ポート２９の圧油を供給した時と第３圧力室３６ に第３ポート３１の圧油を供給した時でスプール３３が押杆３９で弁２５を入口 ポート２３と出口ポート２４を遮断する方向に押す力が異なるので、圧力補償特 性の設定を変更できる。例えばパワーショベルのブームを上げる時にはゆるい圧 力補償特性、下げる時には厳密な圧力補償特性とすることができる。 When the pressure in the first pressure chamber 34 is higher than that in the second pressure chamber 35, the spool 33 moves away from the valve 25 so that the pressure at the inlet port 23 becomes equal to the pressure at the outlet port 24, and the pressure in the first pressure chamber 34 increases. When the pressure in the first pressure chamber 34 is lower than the pressure in the second pressure chamber 35, the valve 25 is pushed in the blocking direction by the spool 33 and the pressure at the outlet port 24 becomes the inlet. It is lower than the pressure of the port 23 by the pressure difference between the second pressure chamber 35 and the first pressure chamber 34. Because of this, by providing this pressure compensating valve in the hydraulic circuit that supplies the hydraulic fluid discharged from the hydraulic pump to multiple actuators, the hydraulic fluid discharged from one hydraulic pump can be used for multiple actuators without using a shuttle valve. Flow rate can be distributed to and supplied. Further, when the pressure oil of the first port 29 is supplied to the third pressure chamber 36 and when the pressure oil of the third port 31 is supplied to the third pressure chamber 36, the spool 33 is a push rod 39 and opens the valve 25 into the inlet port. Since the pressing force of 23 and the outlet port 24 in the blocking direction are different, the setting of the pressure compensation characteristic can be changed. For example, when raising the boom of a power shovel, the pressure compensation characteristic may be loose, and when lowered, the pressure compensation characteristic may be strict.
【図１】従来の圧力補償弁の断面図である。FIG. 1 is a sectional view of a conventional pressure compensation valve.
【図２】本考案の実施例を示す圧力補償弁の断面図であ
る。FIG. 2 is a sectional view of a pressure compensation valve showing an embodiment of the present invention.
【図３】圧力補償弁の動作説明図である。FIG. 3 is an operation explanatory view of a pressure compensation valve.
２０…弁本体、２３…入口ポート、２４…出口ポート、
２５…弁、２８…チェック弁部、２９…第１ポート、３
０…第２ポート、３１…第３ポート、３３…スプール、
３４…第１圧力室、３５…第２圧力室、３６…第３圧力
室、３８…ばね、４２…減圧弁部、５０…切換弁。20 ... Valve body, 23 ... Inlet port, 24 ... Outlet port,
25 ... Valve, 28 ... Check valve part, 29 ... First port, 3
0 ... second port, 31 ... third port, 33 ... spool,
34 ... 1st pressure chamber, 35 ... 2nd pressure chamber, 36 ... 3rd pressure chamber, 38 ... Spring, 42 ... Pressure reducing valve part, 50 ... Switching valve.
Claims (2)
ト２４を連通・遮断する弁２５を設けてチェック弁部２
８とし、前記弁本体２０に、第１ポート２９に連通した
第１圧力室３４の圧力で第２ポート３０と第３ポート３
１を連通し、第３ポート３１に連通した第２圧力室３５
の圧力で第２ポート３０と第３ポート３１を遮断するス
プール３３を設けて減圧弁部４２とし、 前記スプール３３をばね３８で第２ポート３０と第３ポ
ート３１を遮断する方向に押して前記弁２５に当接した
圧力補償弁において、 前記スプール３３を第２ポート３０と第３ポート３１を
連通する方向に押す第３圧力室３６を形成し、この第３
圧力室３６を第１ポート２９と第３ポート３１に連通す
る切換弁５０を設けたことを特徴とする圧力補償弁。1. The check valve portion 2 is provided with a valve 25 that connects and disconnects an inlet port 23 and an outlet port 24 in a valve body 20.
8, the valve body 20 is connected to the second port 30 and the third port 3 by the pressure of the first pressure chamber 34 communicating with the first port 29.
The second pressure chamber 35 communicating with 1 and communicating with the third port 31.
A pressure reducing valve portion 42 is provided by providing a spool 33 that shuts off the second port 30 and the third port 31 with the pressure of, and the spool 33 is pushed by a spring 38 in a direction to shut off the second port 30 and the third port 31. In the pressure compensating valve that abuts 25, a third pressure chamber 36 that pushes the spool 33 in a direction in which the second port 30 and the third port 31 communicate with each other is formed.
A pressure compensating valve comprising a switching valve 50 that connects the pressure chamber 36 to the first port 29 and the third port 31.
圧力室３６に連通する第１位置Ａと、第３ポート３１を
第３圧力室３６に連通する第２位置Ｂに切換えるものと
した請求項１記載の圧力補償弁。2. The switching valve 50 has a first port 29 and a third port.
The pressure compensating valve according to claim 1, wherein the first position A communicating with the pressure chamber 36 and the second position B communicating with the third port 31 are switched to the second position B.
Priority Applications (8)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992075260U JP2593967Y2 (en) | 1992-10-29 | 1992-10-29 | Pressure compensation valve |
| PCT/JP1993/001534 WO1994010454A1 (en) | 1992-10-23 | 1993-10-22 | Pressure oil supply system having a pressure compensating valve |
| KR1019950701574A KR950704617A (en) | 1992-10-23 | 1993-10-22 | Pressurized fluid supply system |
| DE1993628382 DE69328382T2 (en) | 1992-10-23 | 1993-10-22 | PRESSURE OIL SUPPLY SYSTEM WITH PRESSURE COMPENSATING VALVE |
| EP93923052A EP0747601B1 (en) | 1992-10-23 | 1993-10-22 | Pressure oil supply system having a pressure compensating valve |
| US08/411,817 US5651390A (en) | 1992-10-23 | 1993-10-22 | Pressurized fluid supply system |
| US08/600,505 US5784885A (en) | 1992-10-23 | 1996-02-13 | Pressurized fluid supply system |
| US08/742,777 US5845678A (en) | 1992-10-23 | 1996-10-31 | Pressurized fluid supply system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992075260U JP2593967Y2 (en) | 1992-10-29 | 1992-10-29 | Pressure compensation valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0640409U true JPH0640409U (en) | 1994-05-31 |
| JP2593967Y2 JP2593967Y2 (en) | 1999-04-19 |
Family
ID=13571076
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1992075260U Expired - Lifetime JP2593967Y2 (en) | 1992-10-23 | 1992-10-29 | Pressure compensation valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2593967Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1999035408A1 (en) * | 1998-01-12 | 1999-07-15 | Hitachi Construction Machinery Co., Ltd. | Pressure compensating valves |
-
1992
- 1992-10-29 JP JP1992075260U patent/JP2593967Y2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1999035408A1 (en) * | 1998-01-12 | 1999-07-15 | Hitachi Construction Machinery Co., Ltd. | Pressure compensating valves |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2593967Y2 (en) | 1999-04-19 |
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