JPH04244605A - Pressure compensation valve - Google Patents
Pressure compensation valveInfo
- Publication number
- JPH04244605A JPH04244605A JP2909991A JP2909991A JPH04244605A JP H04244605 A JPH04244605 A JP H04244605A JP 2909991 A JP2909991 A JP 2909991A JP 2909991 A JP2909991 A JP 2909991A JP H04244605 A JPH04244605 A JP H04244605A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- port
- valve
- spool
- pressure chamber
- 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.)
- Granted
Links
- 230000000903 blocking effect Effects 0.000 claims description 4
- 238000001514 detection method Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005315 distribution function Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【０００１】0001
【産業上の利用分野】本発明は、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。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure compensating valve used in a hydraulic circuit, etc., which distributes and supplies pressure oil discharged from one hydraulic pump to a plurality of actuators.
【０００２】0002
【従来の技術】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６
０−１１７０６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。[Prior Art] When the discharge pressure oil of one hydraulic pump is supplied to a plurality of actuators, the pressure oil is supplied only to the actuator with a low load pressure.
A hydraulic circuit shown in Japanese Patent No. 0-11706 is known. In other words, a pressure compensation valve is provided on the inlet side of the directional control valve connected to each actuator, each pressure compensation valve is set at the highest load pressure of each actuator, and a hydraulic pump is connected to multiple actuators with different load pressures. This is a hydraulic circuit that can distribute and supply discharge pressure oil.
【０００３】0003
【発明が解決しようとする課題】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。[Problem to be Solved by the Invention] 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 into the low-pressure side pressure chamber, and for this purpose a shuttle valve is required to compare the load pressures of each actuator.
【０００４】そこで、本発明は前述の課題を解決できる
ようにした圧力補償弁を提供することを目的とする。SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a pressure compensating valve capable of solving the above-mentioned problems.
【課題を解決するための手段】弁本体１に入口ポート４
と出口ポート５を連通・遮断する弁６を設けてチェック
弁部９とし、前記弁本体１に、第１ポート１０に連通し
た第１圧力室１４の圧力で第２ポート１１と第３ポート
１２を連通し、第３ポート１２に連通した第２圧力室１
５の圧力で第２ポート１１と第３ポート１２を遮断する
スプール１３を設けて減圧弁部２１とし、前記スプール
１３をばね１７で第２ポート１１と第２ポート１２を遮
断する方向に押して前記弁６に当接した圧力補償弁。[Means for solving the problem] Inlet port 4 in valve body 1
A check valve part 9 is provided with a valve 6 that communicates and shuts off the outlet port 5 and the second port 11 and the third port 12 by the pressure of the first pressure chamber 14 communicating with the first port 10. The second pressure chamber 1 communicates with the third port 12.
A spool 13 that shuts off the second port 11 and the third port 12 at a pressure of 5 is provided as a pressure reducing valve part 21, and the spool 13 is pushed by a spring 17 in the direction of shutting off the second port 11 and the second port 12. Pressure compensating valve abutting valve 6.
【作 用】第１圧力室１４の圧力が第２圧力室１
５の圧力よりも高い時にはスプール１３が弁６より離れ
て入口ポート４の圧力と出口ポート５の圧力が等しくな
ると共に、第１圧力室１４の圧力と第２圧力室１５の圧
力が等しくなり、第１圧力室１４の圧力が第２圧力室１
５の圧力よりも低い時にはスプール１３で弁６が遮断方
向に押されて出口ポート５の圧力が入口ポート４の圧力
よりも第２圧力室１５と第１圧力室１４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
設けることでシャトル弁を用いずに各アクチュエータ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。[Function] The pressure in the first pressure chamber 14 changes to the second pressure chamber 1.
When the pressure is higher than 5, the spool 13 moves away from the valve 6, and the pressure in the inlet port 4 and the pressure in the outlet port 5 become equal, and the pressure in the first pressure chamber 14 and the pressure in the second pressure chamber 15 become equal, The pressure in the first pressure chamber 14 is
When the pressure is lower than the pressure in the second pressure chamber 15 and the first pressure chamber 14, the spool 13 pushes the valve 6 in the blocking direction, and the pressure in the outlet port 5 becomes lower than the pressure in the inlet port 4 by the pressure difference between the second pressure chamber 15 and the first pressure chamber 14. , by installing it on the inlet side of actuators with different load pressures, each actuator 1 can be connected without using a shuttle valve.
The flow rate can be distributed and supplied to the discharge pressure oil of two hydraulic pumps.
【０００５】[0005]
【実 施 例】図１に示すように、弁本体１には一
側孔２と他側孔３が相対向して形成され、その一側孔２
には入口ポート４と出口ポート５が形成してあると共に
、弁６が嵌挿され、その弁６はプラグ７に設けたストッ
パ杆８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９を構成している。前記他側孔３には第
１・第２・第３ポート１０，１１，１２が形成されてい
ると共に、スプール１３が嵌挿されて第１ポート１０に
開口した第１圧力室１４と第３ポート１２に開口した第
２圧力室１５を構成し、そのスプール１３はプラグ１６
との間に設けたばね１７で左方に押されてスプール１３
に一体的に設けた押杆１８が透孔１９より突出して前記
弁６をストッパ杆８に当接しかつ各ポートを遮断し、第
１圧力室１４内の圧力でスプール１３が右方に摺動する
と切欠き２０で第２ポート１１と第３ポート１２を連通
するようになって減圧弁部２１を構成している。前記入
口ポート４と第２ポート１１は油圧ポンプ２２のポンプ
吐出路２３に接続してポンプ吐出圧が供給され、出口ポ
ート５に供給路２４が接続し、第１ポート１０が負荷圧
導入路２５に接続して第１制御圧が供給され、第３ポー
ト１２が負荷圧検出路２６に接続して第２制御圧が供給
される。[Example] As shown in FIG. 1, a valve body 1 is formed with a hole 2 on one side and a hole 3 on the other side facing each other.
is formed with an inlet port 4 and an outlet port 5, and a valve 6 is fitted therein, and the valve 6 is regulated by a stopper rod 8 provided on the plug 7 so as not to slide to the left from the illustrated position. It constitutes the check valve section 9. First, second, and third ports 10, 11, and 12 are formed in the other side hole 3, and a spool 13 is inserted into the first pressure chamber 14 that opens to the first port 10, and a third A second pressure chamber 15 opens to the port 12, and the spool 13 is connected to the plug 16.
The spool 13 is pushed to the left by the spring 17 provided between the
A push rod 18, which is integrally provided with the valve 6, protrudes from the through hole 19 and abuts the valve 6 against the stopper rod 8 and blocks each port, and the pressure inside the first pressure chamber 14 causes the spool 13 to slide to the right. Then, the second port 11 and the third port 12 are communicated with each other through the notch 20, thereby forming a pressure reducing valve section 21. The inlet port 4 and the second port 11 are connected to a pump discharge passage 23 of a hydraulic pump 22 to be supplied with pump discharge pressure, the outlet port 5 is connected to a supply passage 24, and the first port 10 is connected to a load pressure introduction passage 25. The third port 12 is connected to the load pressure detection path 26 to supply the second control pressure.
【０００６】次に作動を説明する。油圧ポンプ２２のポ
ンプ吐出圧が低圧で負荷圧導入路２５、負荷圧検出路２
６の圧力がゼロの時には弁６、スプール１３が図１に示
す位置となって供給路２４の圧力で弁６が摺動して出口
ポート５と入口ポート４が遮断して逆流を防止する。油
圧ポンプ２２のポンプ吐出圧が高くなると図２のように
弁６が押されて入口ポート４と出口ポート５が連通して
出口ポート５より供給路２４に供給され、図３に示すよ
うにストロークエンドまで弁６が摺動すると第２ポート
１１と第３ポート１２が連通する。図２の状態で第１制
御圧が第２制御圧より高い場合にはスプール１３が右方
に押されて第２ポート１１が切欠き２０で第３ポート１
２に連通して第３ポート１２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２４の供給圧は等しくなる。図２の状態で第２制御弁
が第１制御圧より高い場合にはスプール１３が左方に押
されて第２ポート１１と第３ポート１２が遮断し、押杆
１８で弁６を入口ポート４と出口ポート５を遮断する方
向に押すので入口ポート４と出口ポート５の開口面積が
小さくなって供給圧がポンプ吐出圧より低くなる。Next, the operation will be explained. When the pump discharge pressure of the hydraulic pump 22 is low, the load pressure introduction path 25 and the load pressure detection path 2
When the pressure of the valve 6 is zero, the valve 6 and the spool 13 are in the position shown in FIG. 1, and the pressure of the supply path 24 causes the valve 6 to slide, thereby blocking the outlet port 5 and the inlet port 4 to prevent backflow. When the pump discharge pressure of the hydraulic pump 22 increases, the valve 6 is pushed as shown in FIG. 2, the inlet port 4 and the outlet port 5 are communicated, and the supply is supplied from the outlet port 5 to the supply path 24, and the stroke is increased as shown in FIG. When the valve 6 slides to the end, the second port 11 and the third port 12 communicate with each other. If the first control pressure is higher than the second control pressure in the state shown in FIG.
2, the pressure of the third port 12, that is, the second control pressure, becomes a pressure corresponding to the first control pressure, and the pump discharge pressure and the supply pressure of the supply path 24 become equal. When the second control valve pressure is higher than the first control pressure in the state shown in FIG. 4 and the outlet port 5, the opening area of the inlet port 4 and the outlet port 5 becomes smaller, and the supply pressure becomes lower than the pump discharge pressure.
【０００８】このように、減圧弁部２１の第１圧力室１
４に供給される第１制御圧が第２圧力室１５に供給され
る第２制御圧よりも高い時にはポンプ吐出圧が減圧され
て第３ポート１２の圧力（第２制御圧）が第１ポート１
０の圧力（第１制御圧）と同一となると共に、入口ポー
ト４の圧力（ポンプ吐出圧）と出口ポート５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／ｃ
ｍ２ 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１１と第３ポート１２が連通せず
にポンプ吐出圧が第３ポート１２に供給されないと共に
、弁６により入口ポート４と出口ポート５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１
２０ｋｇ／ｃｍ２ 、第１制御圧１０ｋｇ／ｃｍ２ 、
第２制御圧１００ｋｇ／ｃｍ２ の時には供給圧３０ｋ
ｇ／ｃｍ２となる。In this way, the first pressure chamber 1 of the pressure reducing valve section 21
When the first control pressure supplied to the second pressure chamber 15 is higher than the second control pressure supplied to the second pressure chamber 15, the pump discharge pressure is reduced and the pressure at the third port 12 (second control pressure) is lowered to the first control pressure at the third port 12. 1
0 (first control pressure), and the pressure at the inlet port 4 (pump discharge pressure) and the pressure at the outlet port 5 (supply pressure) are also the same. For example, pump discharge pressure 120kg/
cm2, when the first control pressure is 100kg/cm2, the second control pressure is 100kg/cm2, and the supply pressure is 120kg/c.
m2. Similarly, when the second control pressure is higher than the first control pressure, the second port 11 and the third port 12 do not communicate with each other, and the pump discharge pressure is not supplied to the third port 12. , the opening area of the outlet port 5 decreases, and the supply pressure is lower than the port discharge pressure by the second control pressure and the first control pressure.
It is lowered by the difference in control pressure. For example, pump discharge pressure 1
20kg/cm2, first control pressure 10kg/cm2,
When the second control pressure is 100kg/cm2, the supply pressure is 30k.
g/cm2.
【０００９】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２４を方向制御弁の入口ポートに接続し
、負荷圧導入路２５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２６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 a hydraulic circuit that supplies pressure oil discharged from one hydraulic pump to a plurality of actuators, the supply path 24 is connected to the inlet port of the directional control valve, and the load pressure introduction path 25 is connected to the hydraulic circuit. If the load pressure of the actuator is introduced and the load pressure detection path 26 is communicated with each pressure compensation valve, the flow can be distributed and supplied to each actuator as in the conventional case.
【００１０】図４は第２実施例を示し、スプール１３の
盲穴３０にピストン３１を嵌挿し、このピストン３１を
弱いばね１７でプラグ１６に押しつけ、そのばね室３２
を孔３３で第２ポート１１に連通してある。かかる構成
であればスプール１３の第２圧力室１５の受圧面積を減
少して第１圧力室１４の受圧面積と同一にできるし、ピ
ストン３１の径を変えることで第１圧力室１４と第２圧
力室１５の受圧面積差を変更して流量分配機能の精度を
任意に調整できる。すなわち、押杆１８が弁６に当接し
て圧力補償機能を有するとき、チェック弁部９の弁６及
び減圧弁部２１のスプール１３に作用する圧力の受圧面
積をすべて等しくし、アクチュエータへの供給流量をね
らい値に等しくさせることができる。しかし、慣性体の
ハンチング防止対策時のように、アクチュエータへの供
給流量をねらい値に対し多くする必要がでてくる。この
時はピストン３１の径を小さくし、前記チェック弁部及
び減圧弁部の各受圧面積を変えることができ、結果とし
て、アクチュエータへの供給流量をねらい値に対し変え
ることができるから慣性体を動かすアクチュエータのハ
ンチング防止を可能とする。FIG. 4 shows a second embodiment, in which a piston 31 is fitted into a blind hole 30 of a spool 13, this piston 31 is pressed against a plug 16 by a weak spring 17, and its spring chamber 32 is pressed against the plug 16.
is communicated with the second port 11 through a hole 33. With such a configuration, the pressure receiving area of the second pressure chamber 15 of the spool 13 can be reduced to be the same as the pressure receiving area of the first pressure chamber 14, and by changing the diameter of the piston 31, the pressure receiving area of the first pressure chamber 14 and the second pressure chamber 15 can be reduced. By changing the pressure receiving area difference of the pressure chambers 15, the accuracy of the flow distribution function can be adjusted as desired. That is, when the push rod 18 comes into contact with the valve 6 and has a pressure compensating function, the pressure receiving area of the pressure acting on the valve 6 of the check valve section 9 and the spool 13 of the pressure reducing valve section 21 is made equal, and the pressure is supplied to the actuator. The flow rate can be made equal to the target value. However, when taking measures to prevent hunting of the inertial body, it becomes necessary to increase the flow rate supplied to the actuator relative to the target value. At this time, the diameter of the piston 31 can be reduced to change the pressure receiving areas of the check valve section and the pressure reducing valve section, and as a result, the flow rate supplied to the actuator can be changed to the target value, so the inertial body can be changed. It is possible to prevent hunting of the moving actuator.
【００１１】図５は第３実施例を示し、スプール１３に
第２ポート１１と第３ポート１２を連通するための絞り
４０を形成し、油圧ポンプ２２のポンプ吐出圧を絞り４
０を通して第３ポート１２に供給するようにしてある。
このようにすれば、第２ポート１１と第３ポート１２が
連通した時にポンプ吐出圧が減圧して第３ポート１２に
供給されるので、例えば図６のように負荷圧検出路２６
にリリーフ弁４１を設けてもポンプ吐出圧を保持できる
。図６において、５０は方向制御弁、５１はアクチュエ
ータ、５２はポンプ容量制御弁である。FIG. 5 shows a third embodiment, in which a throttle 40 is formed in the spool 13 for communicating the second port 11 and the third port 12, and the pump discharge pressure of the hydraulic pump 22 is controlled by the throttle 40.
0 to the third port 12. In this way, when the second port 11 and the third port 12 communicate with each other, the pump discharge pressure is reduced and supplied to the third port 12, so that, for example, as shown in FIG.
Even if a relief valve 41 is provided in the pump, the pump discharge pressure can be maintained. In FIG. 6, 50 is a direction control valve, 51 is an actuator, and 52 is a pump displacement control valve.
【００１２】0012
【発明の効果】第１圧力室１４の圧力が第２圧力室１５
の圧力よりも高い時にはスプール１３が弁６より離れて
入口ポート４の圧力と出口ポート５の圧力が等しくなる
と共に、第１圧力室１４の圧力と第２圧力室１５の圧力
が等しくなり、第１圧力室１４の圧力が第２圧力室１５
の圧力よりも低い時にはスプール１３で弁６が遮断方向
に押されて出口ポート５の圧力が入口ポート４の圧力よ
りも第２圧力室１５と第１圧力室１４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。Effect of the invention: The pressure in the first pressure chamber 14 is reduced to the second pressure chamber 15.
When the pressure is higher than the pressure of The pressure in the first pressure chamber 14 becomes the second pressure chamber 15.
When the pressure is lower than the pressure of the second pressure chamber 15 and the first pressure chamber 14, the spool 13 pushes the valve 6 in the blocking direction, and the pressure of the outlet port 5 becomes lower than the pressure of the inlet port 4 by the pressure difference between the second pressure chamber 15 and the first pressure chamber 14. Therefore, by providing this pressure compensation valve in the hydraulic circuit that supplies the discharge pressure oil of a hydraulic pump to multiple actuators, the flow rate of the discharge pressure oil of one hydraulic pump to multiple actuators can be adjusted without using a shuttle valve. Can be distributed and supplied.
【図１】圧力補償弁の第１実施例を示す断面図である。FIG. 1 is a sectional view showing a first embodiment of a pressure compensation valve.
【図２】圧力補償弁の動作説明図である。FIG. 2 is an explanatory diagram of the operation of the pressure compensation valve.
【図３】圧力補償弁の動作説明図である。FIG. 3 is an explanatory diagram of the operation of the pressure compensation valve.
【図４】圧力補償弁の第２実施例を示す断面図である。FIG. 4 is a sectional view showing a second embodiment of the pressure compensation valve.
【図５】圧力補償弁の第３実施例を示す断面図である。FIG. 5 is a sectional view showing a third embodiment of the pressure compensation valve.
【図６】圧力補償弁を備えた油圧回路図である。FIG. 6 is a hydraulic circuit diagram with a pressure compensation valve.
１ 弁本体、４ 入口ポート、５ 出口ポート、
６ 弁、９ チェック弁、１０第１ポート、１１
第２ポート、１２ 第３ポート、１３ スプール
、１４第１圧力室、１５ 第２圧力室、１７ ばね
、２１ 減圧弁部。1 Valve body, 4 Inlet port, 5 Outlet port,
6 valve, 9 check valve, 10 first port, 11
2nd port, 12 3rd port, 13 spool, 14 first pressure chamber, 15 second pressure chamber, 17 spring, 21 pressure reducing valve section.
Claims (1)
５を連通・遮断する弁６を設けてチェック弁部９とし、
前記弁本体１に、第１ポート１０に連通した第１圧力室
１４の圧力で第２ポート１１と第３ポート１２を連通し
、第３ポート１２に連通した第２圧力室１５の圧力で第
２ポート１１と第３ポート１２を遮断するスプール１３
を設けて減圧弁部２１とし、前記スプール１３をばね１
７で第２ポート１１と第３ポート１２を遮断する方向に
押して前記弁６に当接したことを特徴とする圧力補償弁
。1. A check valve part 9 is provided in the valve body 1 with a valve 6 for communicating and blocking the inlet port 4 and the outlet port 5,
In the valve body 1, the pressure of the first pressure chamber 14 communicating with the first port 10 communicates the second port 11 and the third port 12, and the pressure of the second pressure chamber 15 communicating with the third port 12 communicates the second port 11 and the third port 12. Spool 13 that blocks the second port 11 and the third port 12
is provided as the pressure reducing valve part 21, and the spool 13 is connected to the spring 1.
7, the pressure compensating valve is pressed in a direction to shut off the second port 11 and the third port 12 and comes into contact with the valve 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2909991A JP2916955B2 (en) | 1991-01-31 | 1991-01-31 | Pressure compensation valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2909991A JP2916955B2 (en) | 1991-01-31 | 1991-01-31 | Pressure compensation valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04244605A true JPH04244605A (en) | 1992-09-01 |
| JP2916955B2 JP2916955B2 (en) | 1999-07-05 |
Family
ID=12266902
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2909991A Expired - Lifetime JP2916955B2 (en) | 1991-01-31 | 1991-01-31 | Pressure compensation valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2916955B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996001952A1 (en) * | 1994-07-12 | 1996-01-25 | Komatsu Ltd. | Pressure compensating valve |
| WO1996001951A1 (en) * | 1994-07-12 | 1996-01-25 | Komatsu Ltd. | Pressure compensating valve |
| EP0751300A1 (en) * | 1994-03-15 | 1997-01-02 | Komatsu Ltd. | Pressure compensating valve and pressure oil supply device using said pressure compensating valve |
| US5651390A (en) * | 1992-10-23 | 1997-07-29 | Kabushiki Kaisha Komatsu Seisakusho | Pressurized fluid supply system |
| US5794510A (en) * | 1993-09-28 | 1998-08-18 | Komatsu Ltd. | Pressurized fluid feed system |
| WO1999035408A1 (en) * | 1998-01-12 | 1999-07-15 | Hitachi Construction Machinery Co., Ltd. | Pressure compensating valves |
| JP2007002900A (en) * | 2005-06-22 | 2007-01-11 | Komatsu Ltd | Pilot valve |
-
1991
- 1991-01-31 JP JP2909991A patent/JP2916955B2/en not_active Expired - Lifetime
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5784885A (en) * | 1992-10-23 | 1998-07-28 | Kabushiki Kaisha Komatsu Seisakusho | Pressurized fluid supply system |
| US5845678A (en) * | 1992-10-23 | 1998-12-08 | Kabushiki Kaisha Komatsu Seisakusho | Pressurized fluid supply system |
| US5651390A (en) * | 1992-10-23 | 1997-07-29 | Kabushiki Kaisha Komatsu Seisakusho | Pressurized fluid supply system |
| US5794510A (en) * | 1993-09-28 | 1998-08-18 | Komatsu Ltd. | Pressurized fluid feed system |
| EP0751300A1 (en) * | 1994-03-15 | 1997-01-02 | Komatsu Ltd. | Pressure compensating valve and pressure oil supply device using said pressure compensating valve |
| EP0751300A4 (en) * | 1994-03-15 | 1999-06-16 | Komatsu Mfg Co Ltd | Pressure compensating valve and pressure oil supply device using said pressure compensating valve |
| US5735311A (en) * | 1994-07-12 | 1998-04-07 | Komatsu, Ltd. | Pressure compensation valve |
| WO1996001951A1 (en) * | 1994-07-12 | 1996-01-25 | Komatsu Ltd. | Pressure compensating valve |
| WO1996001952A1 (en) * | 1994-07-12 | 1996-01-25 | Komatsu Ltd. | Pressure compensating valve |
| US5738134A (en) * | 1994-07-12 | 1998-04-14 | Komatsu Ltd. | Pressure compensation valve |
| WO1999035408A1 (en) * | 1998-01-12 | 1999-07-15 | Hitachi Construction Machinery Co., Ltd. | Pressure compensating valves |
| EP0967398A1 (en) * | 1998-01-12 | 1999-12-29 | Hitachi Construction Machinery Co., Ltd. | Pressure compensating valves |
| US6135149A (en) * | 1998-01-12 | 2000-10-24 | Hitachi Construction Machinery Co., Ltd. | Pressure compensating valves |
| EP0967398A4 (en) * | 1998-01-12 | 2003-05-07 | Hitachi Construction Machinery | Pressure compensating valves |
| JP2007002900A (en) * | 2005-06-22 | 2007-01-11 | Komatsu Ltd | Pilot valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2916955B2 (en) | 1999-07-05 |
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