JPS63186004A - Hydraulic circuit - Google Patents
Hydraulic circuitInfo
- Publication number
- JPS63186004A JPS63186004A JP1509087A JP1509087A JPS63186004A JP S63186004 A JPS63186004 A JP S63186004A JP 1509087 A JP1509087 A JP 1509087A JP 1509087 A JP1509087 A JP 1509087A JP S63186004 A JPS63186004 A JP S63186004A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- stroke
- engine
- control valve
- hydraulic
- 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.)
- Pending
Links
- 238000010586 diagram Methods 0.000 description 10
- 239000000446 fuel Substances 0.000 description 5
- 230000007423 decrease Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 206010041235 Snoring Diseases 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 235000003642 hunger Nutrition 0.000 description 1
- 238000009377 nuclear transmutation Methods 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 230000015607 signal release Effects 0.000 description 1
- 230000037351 starvation Effects 0.000 description 1
Landscapes
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
〈産業上の利用分野〉
本発明は、建設機械等に備えられる圧力補償付制御弁を
有する油圧回路に関する。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a hydraulic circuit having a pressure-compensated control valve provided in construction machinery and the like.
〈従来の技術〉
第５図はこの種の従来の油圧回路の一例を示す回路図で
ある。この図において、１はアクチュエータ、例えば油
圧モータ、２もアクチュエータ、例えば油圧シリンダで
ある。３．４はこれらの油′圧モータ１、油圧シリンダ
２の駆動を制御する圧力補償付制御弁、５はこれにの圧
力補償付制御弁３．４の駆動を制御する操作信号を出力
する操作レバー、６はこの操作レバー５の操作信号（操
作レバーストロークＸＬ）を入力して、所定の演算処理
をおこない、圧力補償付制御弁３．４の駆動部に、その
スプールを移動させる駆動信号Ｓｏを出力する制御装置
である。７は圧力補償付制御弁３．４を介して油圧モー
タ１、油圧シリンダ２に圧油を供給する圧力補償付油圧
ポンプ、８は切換弁で、ロードセンシング圧すなわちポ
ンプ７の吐出圧とシャトル弁９を通って導かれるロード
圧とが一定となるように、ポンプ７の吐出量を決める切
換弁、１０は油圧ポンプ７を駆動するエンジン、１１は
このエンジン１０の回転数を指令する指令信号を出力す
る指令装置、すなわち燃料レバー、１２はこの燃料レバ
ー１１の指令信号を入力して、エンジン１０を駆動する
ための目標回転数信号ＮＯを出力する目標回転数設定装
置である。<Prior Art> FIG. 5 is a circuit diagram showing an example of this type of conventional hydraulic circuit. In this figure, 1 is an actuator, for example a hydraulic motor, and 2 is also an actuator, for example a hydraulic cylinder. 3.4 is a pressure-compensated control valve that controls the drive of these hydraulic motor 1 and hydraulic cylinder 2, and 5 is an operation that outputs an operation signal that controls the drive of the pressure-compensated control valve 3.4. The lever 6 inputs the operation signal (operation lever stroke XL) of the operation lever 5, performs predetermined arithmetic processing, and sends a drive signal So to the drive section of the pressure compensated control valve 3.4 to move the spool. This is a control device that outputs . 7 is a pressure-compensated hydraulic pump that supplies pressure oil to the hydraulic motor 1 and hydraulic cylinder 2 via a pressure-compensated control valve 3.4; 8 is a switching valve that controls the load sensing pressure, that is, the discharge pressure of pump 7, and the shuttle valve; 10 is an engine that drives the hydraulic pump 7; 11 is a command signal that commands the rotational speed of the engine 10; The output command device, that is, the fuel lever 12 is a target rotation speed setting device that inputs the command signal of the fuel lever 11 and outputs a target rotation speed signal NO for driving the engine 10.
この油圧回路にあって、油圧モータ１および油圧シリン
ダ２、すなわち圧力補償付制御弁３．４をそれぞれ単独
に操作する場合、圧力補償付制御弁３．４の駆動部に与
えられる駆動信号ＳＯ１すなわちこれらの駆動信号ＳＯ
によって作動する圧力補償付制御弁３．４のスプールの
作動量であるスプールストロークＳと、油圧モータ１、
油圧シリンダ２等のアクチュエータの速度Ｖとの関係は
第６図に示す特性線１３で示すものである。つまり、エ
ンジン１０の回転数を最高回転数から徐々に落とすと、
スプールストロークＳが１００％に至らない中間地点で
流量が飽和してしまい、それ以上スプールを移動させて
もポンプ７の能力上、アクチュエータ速度■が増加しな
いようになっている。そして、この従来の油圧回路では
、操作レバー５の操作信号、すなわち操作レバーストロ
ークＸＬと、上述のスプールストロークＳとの関係は第
７図の特性線１４で示すように一定の関係となっており
、この第７図の特性線１４と第６図の特性線１３で示さ
れる関係から、操作レバーストロークＸＬと、アクチュ
エータ速度Ｖとは第８図の特性線１５で示す関係となる
。In this hydraulic circuit, when the hydraulic motor 1 and the hydraulic cylinder 2, that is, the pressure-compensated control valve 3.4, are each operated independently, the drive signal SO1, that is, given to the drive section of the pressure-compensated control valve 3.4, is These drive signals SO
The spool stroke S, which is the operating amount of the spool of the pressure compensated control valve 3.4 operated by the hydraulic motor 1,
The relationship with the speed V of the actuator such as the hydraulic cylinder 2 is shown by a characteristic line 13 shown in FIG. In other words, if the rotation speed of the engine 10 is gradually reduced from the maximum rotation speed,
The flow rate is saturated at an intermediate point where the spool stroke S does not reach 100%, and even if the spool is moved further, the actuator speed (2) will not increase due to the capacity of the pump 7. In this conventional hydraulic circuit, the relationship between the operation signal of the operation lever 5, that is, the operation lever stroke XL, and the above-mentioned spool stroke S is a constant relationship as shown by the characteristic line 14 in FIG. From the relationship shown by the characteristic line 14 in FIG. 7 and the characteristic line 13 in FIG. 6, the operating lever stroke XL and the actuator speed V have a relationship shown by the characteristic line 15 in FIG. 8.
〈発明が解決しようとする問題点〉
ところで、上述のように構成される従来の油圧回路にあ
っては、エンジン１０の回転数を落としな場合には、油
圧モータ１、油圧シリンダ２等の７クチユエータの速度
を制御しうる領域であるメータリング域が狭くなり、そ
れ故、当該アクチュエータの操作がしすらくなって、オ
ペレータの疲労を招くとともに、微操作が困難となる不
具合がある。<Problems to be Solved by the Invention> By the way, in the conventional hydraulic circuit configured as described above, when the rotational speed of the engine 10 is to be reduced, the hydraulic motor 1, the hydraulic cylinder 2, etc. The metering range, which is the range in which the speed of the actuator can be controlled, becomes narrow, and therefore the actuator becomes difficult to operate, causing operator fatigue and making fine control difficult.
また、油圧モータ１と油圧シリンダ２との複合操作時に
は、圧力補償付制御弁３．４、油圧ポンプ７を含むシス
テムの特性上、圧力補１古付制御弁３．４に対する指令
流量が油圧ポンプ７の最大吐出量を越えると圧力の低い
方のみが制御され、高い方の制御が実際上難しくなり、
複合操作が困難となるが、上述した従来の油圧回路にあ
ってはエンジン１０の回転数を落とすにつれて上述のよ
うにメータリング域が狭くなり、油圧ポンプ７の最大吐
出量が減るので、上記した複合操作が困難となる度合が
増加する不具合もある。In addition, during combined operation of the hydraulic motor 1 and the hydraulic cylinder 2, due to the characteristics of the system including the pressure compensation control valve 3.4 and the hydraulic pump 7, the command flow rate for the pressure compensation 1 old control valve 3.4 will be different from the hydraulic pump. If the maximum discharge amount of 7 is exceeded, only the lower pressure side will be controlled, and it will become difficult to control the higher pressure side.
Although complex operations become difficult, in the conventional hydraulic circuit described above, as the rotation speed of the engine 10 is reduced, the metering range narrows as described above, and the maximum discharge amount of the hydraulic pump 7 decreases. There are also defects that increase the degree to which complex operations become difficult.
本発明は、上記した従来技術における実情に鑑みてなさ
れたもので、その目的は、アクチュエータの速度を制御
しうるメータリング域を比較的広くすることができる油
圧回路を提供することにある。The present invention has been made in view of the above-mentioned actual situation in the prior art, and its purpose is to provide a hydraulic circuit that can relatively widen the metering range in which the speed of an actuator can be controlled.
く問題点を解決するための手段〉
この目的を達成するために本発明は、複数のアクチュエ
ータと、これらのアクチュエータの駆動を制御する圧力
補償付制御弁と、これらの圧力補償付制御弁の駆動を制
御する操作信号を出力する操作レバーと、圧力補償付制
御弁を介してアクチュエータのそれぞれに圧油を供給す
る油圧ポンプと、この油圧ポンプを駆動するエンジンを
備えたものにおいて、エンジンの回転数の変化に応じて
、操作レバーのストロークと圧力補償付制御弁のスプー
ルのストロークとの相関関係を変化させる手段を設けた
構成にしである。Means for Solving the Problems To achieve this object, the present invention provides a plurality of actuators, pressure compensated control valves that control the driving of these actuators, and a pressure compensated control valve that controls the driving of these pressure compensated control valves. An operating lever that outputs an operating signal to control the actuator, a hydraulic pump that supplies pressure oil to each of the actuators via a pressure-compensated control valve, and an engine that drives this hydraulic pump. The structure includes means for changing the correlation between the stroke of the operating lever and the stroke of the spool of the pressure-compensated control valve in accordance with changes in the pressure compensation control valve.
く作用〉
本発明は上記のように構成しであることから、例えばエ
ンジンの回転数を落としたときには、操作レバーのスト
ロークに対する圧力補償付制御弁のスプールのストロー
クの割合を下げることができ、これにより、操作レバー
のストロークに対するアクチュエータ速度の割合が下が
り、アクチュエータを制御しうるメータリング域が広が
り、このエンジン回転数の下げ時におけるアクチュエー
タの操作性を向上させることができる。Since the present invention is configured as described above, for example, when the engine speed is reduced, the ratio of the stroke of the spool of the pressure compensated control valve to the stroke of the operating lever can be lowered. This reduces the ratio of the actuator speed to the stroke of the operating lever, widens the metering range in which the actuator can be controlled, and improves the operability of the actuator when the engine speed is reduced.
〈実施例〉
以下、本発明の油圧回路の一実施例を図に基づいて説明
する。<Example> Hereinafter, an example of the hydraulic circuit of the present invention will be described based on the drawings.
第１図は本発明の一実施例を示す回路図、第２図は第１
図に示す一実施例に備えられる制御装置の基本構成を示
す説明図で゛ある。これらの図において、前述した第５
図荷示すものと同一のものは同一符号で示しである。す
なわち、第１図において、１．２はそれぞれアクチュエ
ータを構成する油圧モータ、油圧シリンダ、３．４はこ
れらの油圧モータ１、油圧シリンダ２を駆動する圧力’
Ｍ ｆｆｆ付制御弁、５はこれらの圧力補償付制御弁３
．４を切換える操作信号を出方する操作レバーく操作レ
バーストロークＸＬ）、７は圧力補償１寸油圧ポンプ、
８は切換弁、９はシャトル弁、１ｏは油圧ポンプ７を駆
動するエンジン、１１は燃料レバー、１２はエンジン１
０を駆動するための目標回転数信号Ｎｏを出力する目標
回転数設定装置である。Fig. 1 is a circuit diagram showing one embodiment of the present invention, and Fig. 2 is a circuit diagram showing an embodiment of the present invention.
FIG. 2 is an explanatory diagram showing the basic configuration of a control device provided in one embodiment shown in the figure. In these figures, the fifth
Components that are the same as those shown in the figures are designated by the same reference numerals. That is, in FIG. 1, 1.2 is a hydraulic motor and a hydraulic cylinder that constitute an actuator, and 3.4 is a pressure that drives these hydraulic motor 1 and hydraulic cylinder 2.
M fff-equipped control valve, 5 these pressure-compensated control valves 3
．． 4 is the operating lever that outputs the operating signal to switch the operating lever stroke XL), 7 is the pressure compensation 1-inch hydraulic pump,
8 is a switching valve, 9 is a shuttle valve, 1o is an engine that drives the hydraulic pump 7, 11 is a fuel lever, 12 is an engine 1
This is a target rotation speed setting device that outputs a target rotation speed signal No for driving 0.
そして、６ａは操作レバー５の操作信号、すなわち操作
レバーストロークＸＬを入力し、圧力補償付制御弁３．
４の駆動部にスプールストロークＳを得るための駆動信
号Ｓ○を出力する制御装置である。6a inputs the operating signal of the operating lever 5, that is, the operating lever stroke XL, and the pressure compensated control valve 3.
This is a control device that outputs a drive signal S○ for obtaining a spool stroke S to the drive unit No. 4.
この制御装置６ａは、信号線１６によって目標回転数設
定装置１２に接続されており、第２図に示すように、目
標回転数設定装置１２から出力される目標回転数信号Ｎ
Ｏを入力して、この目標回転数信号に対応したゲインＫ
を出力する関数発生手段１７と、この関数発生手段１７
がら出力されるゲインにと上述した操作レバー５の操作
による操作信号、すなわち操作レバーストロークＸＬと
を乗算し、圧力補償付制御弁３．４を駆動する駆動信号
Ｓ○を出力する乗算器１８とを有している。This control device 6a is connected to the target rotation speed setting device 12 by a signal line 16, and as shown in FIG.
By inputting O, the gain K corresponding to this target rotation speed signal is calculated.
a function generating means 17 that outputs
a multiplier 18 which multiplies the gain outputted from the control lever 5 by the operation signal from the operation of the control lever 5 described above, that is, the control lever stroke XL, and outputs a drive signal S○ for driving the pressure compensated control valve 3.4; have.
なお、関数発生手段１７には、例えばエンジン１０の最
高回転数に対する目標回転数信号Ｎｏの割合と、最大値
が１となるゲインにとの関数間ｊ系が設定されており、
目標回転数信号ＮｏがＮｍａｘに等しいときはに＝１が
出力され、Ｎｍａｘに満たないときは、Ｋ１、Ｋ２で例
示する１に満たないゲインＫが出力されるようになって
いる。Note that the function generating means 17 is set with a j system between functions, for example, the ratio of the target rotational speed signal No to the maximum rotational speed of the engine 10 and the gain whose maximum value is 1.
When the target rotational speed signal No is equal to Nmax, =1 is output, and when it is less than Nmax, a gain K less than 1, exemplified by K1 and K2, is output.
上述した関数発生手段１７と乗算器１８とを含む制御装
置６ａと信号線１６とによって、エンジン１０の回転数
の変化に応じて操作レバー５のストロークと圧力補償付
制御弁３．４のスプールストロークとの相関関係を変化
させる手段が構成されている。The control device 6a including the function generating means 17 and the multiplier 18 described above and the signal line 16 control the stroke of the operating lever 5 and the spool stroke of the pressure compensated control valve 3.4 in response to changes in the rotational speed of the engine 10. Means for changing the correlation between the two is configured.
このように構成した実施例にあっては、圧力補償付制御
弁３．４の単独駆動時、燃料レバー１１の操作に伴い、
目標回転数設定装置１２、信号線１６を介して関数発生
手段１７に目標回転数信号ＮＯが入力され、この目標回
転数信号Ｎｏに対応するゲインＫがこの関数発生手段１
７がら乗算器１８に出力され、乗算器１８では操作レバ
＝５の操作に伴う操作レバーストロークＸＬとゲインに
とを乗算して圧力補償付制御弁３．４の駆動部に駆動信
号Ｓ○を出力するが、このときの圧力補償付制御弁３．
４のスプールのストロークＳと操作レバーストロークＸ
Ｌとの関係は第３図に示すようになる。すなわち、目標
回転数信号ＮＯがエンジン最高回転数に等しいときはゲ
インにはに＝１であり、したがってＫ −ＸＬ＝ＸＬと
なって特性線１４で示すように従来と同様の関係となる
が、エンジン１０の回転数が最高回転数から下げられた
場合、すなわち目標回転数信号ＮｏがＮｍａｘより小さ
くなっている場合には、関数発生手段１７から出力され
るゲインには例えばに□、Ｋ２のように小さい値となり
、したがって乗算器１８において求められる値ＸＬより
小さい値となる。その結果、スプールストロークＳと操
作レバーストロークＸＬとの関係は、例えばに＝に２の
ときは特性線１つで示すものになり、Ｋ＝に２のときは
特性線２０で示すものとなり、操作レバーストロークＸ
Ｌが１００％となってもスプールストロークＳは１００
％よりも小さい値となる。そして、この第３図に示す関
係と、前述した第６図に示す関係とから、油圧モータ１
、油圧シリンダ２等のアクチュエータの速度Ｖと、操作
レバーストロークＸＬとの関係は、第４図に示すものと
なる。この第４図において、２１は前述したゲインＫか
に１で第３図の特性線１つに対応する特性線、２２は前
述したゲインＫかに２で第３図の特性線２０に対応する
特性線である。In the embodiment configured in this way, when the pressure compensated control valve 3.4 is driven independently, when the fuel lever 11 is operated,
A target rotation speed signal NO is input to the function generation means 17 via the target rotation speed setting device 12 and the signal line 16, and the gain K corresponding to this target rotation speed signal No is input to the function generation means 1.
7 is output to the multiplier 18, and the multiplier 18 multiplies the operating lever stroke XL and the gain associated with the operation of the operating lever=5 to provide a drive signal S○ to the drive section of the pressure compensated control valve 3.4. At this time, the pressure compensated control valve 3.
4. Spool stroke S and operation lever stroke X
The relationship with L is shown in FIG. That is, when the target rotational speed signal NO is equal to the maximum engine rotational speed, the gain is 1, and therefore K - XL = XL, which is the same relationship as the conventional one as shown by the characteristic line 14. When the rotation speed of the engine 10 is lowered from the maximum rotation speed, that is, when the target rotation speed signal No is smaller than Nmax, the gain output from the function generation means 17 is set to □, K2, etc. Therefore, it becomes a smaller value than the value XL found in the multiplier 18. As a result, the relationship between the spool stroke S and the operating lever stroke XL is, for example, as shown by one characteristic line when K = 2, and as shown by 20 characteristic lines when K = 2. Lever stroke
Even if L is 100%, spool stroke S is 100
The value is smaller than %. From the relationship shown in FIG. 3 and the relationship shown in FIG. 6 described above, the hydraulic motor 1
, the relationship between the speed V of the actuator such as the hydraulic cylinder 2 and the operating lever stroke XL is as shown in FIG. In FIG. 4, 21 corresponds to the characteristic line 1 in FIG. 3 with the aforementioned gain K to 1, and 22 corresponds to the characteristic line 20 in FIG. 3 with the aforementioned gain K to 2. It is a characteristic line.
したがって、本実施例は、第４図の特性図から明らかな
ように、エンジン１０の回転数を下げた場合にもアクチ
ュエータ速度Ｖを制御しろるメータリング域として、エ
ンジン１０が最高回転数の場合と同等のものが得られる
。これにより、エンジン１０の回転数下げ時にあっても
、油圧モータ１、油圧シリンダ２等のアクチュエータの
操作が容易で、オペレータの疲労を軽減でき、また微操
作が容易となる。Therefore, as is clear from the characteristic diagram in FIG. 4, in this embodiment, as a metering range in which the actuator speed V can be controlled even when the engine 10 rotation speed is lowered, when the engine 10 is at the maximum rotation speed, You will get something equivalent to . As a result, even when the rotational speed of the engine 10 is lowered, the actuators such as the hydraulic motor 1 and the hydraulic cylinder 2 can be easily operated, reducing operator fatigue and facilitating fine operation.
また、油圧モータ１と油圧シリンダ２との複合操作時に
あっては、エンジン１０の回転数の下げに伴って油圧ポ
ンプ７の最大吐出量が減るものの上述のようにメータリ
ング域を比較的広く確保できるので、油圧モータ１、油
圧シリンダ２のそれぞれの制御が保障され、この複合操
作が比較的容易となる。In addition, during combined operation of the hydraulic motor 1 and the hydraulic cylinder 2, the maximum discharge amount of the hydraulic pump 7 decreases as the rotation speed of the engine 10 decreases, but as mentioned above, a relatively wide metering range is ensured. Therefore, control of each of the hydraulic motor 1 and the hydraulic cylinder 2 is ensured, and this combined operation becomes relatively easy.
〈発明の効果〉
本発明の油圧回路は、以上のように構成しであることか
ら、アクチュエータの速度を制御しうるメータリング域
を比較的広くすることができ、それ故、従来に比べてア
クチュエータの操作性を向上させることができる効果が
ある。<Effects of the Invention> Since the hydraulic circuit of the present invention is configured as described above, it is possible to relatively widen the metering range in which the speed of the actuator can be controlled. This has the effect of improving operability.
第１図は本発明の油圧回路の一実施例を示す回路図、第
２図は第１図に示す一実施例に備えられる制御装置の基
本構成を示す説明図、第３図および第４図は第１図に示
す実施例において得られる特性図、第５図は従来の油圧
回路を示す回路図、第６図、第７図、および第８図は第
５図に示す油圧回路において得られる特性図である。
１・・・・・・油圧モータ（アクチュエータ）、２・・
・・・・油圧シリンダ（アクチュエータ）、３．４・・
・・・・圧力補償付制御弁、５・・・・・・操作レバー
、６ａ・・・・・・制御装置、７・・・・・・圧力補償
付油圧ポンプ、１０・・・・・・エンジン、１１・・・
・・・燃料レバー、１２・・・・・・目標回転数設定装
置、１６・・・・・・信号線、１７・・・・・・関数発
生手段、１８・・・・・・乗算器。
第１図
！−−−−油圧も−り（アクチュエ−７） １０
・−ｍ＝エンジン２−−−−油圧、シリンク“（アクチ
ユエ−り） １７・−・・で百科レバー３−・−圧
力補イ＃：Ｔ ％ＩＪ押＃ １２−−−
一目碑り転較毅定、挟置４−−−−圧ｆＪ補°慴付朝鼾
弁 ｔ６・−一一信号遁５−−−−棟作レバー
１７−−−− ＩＳｌ’ｌ製茫生
手餓６Ｏ−−−−ｅＪＷＨ置 ｔａ−−
−−＊１に器７−−−−圧力柚゛彊イ１３島圧次ンア第
２図
第３図 第４図
捕イ乍しバ＝ストロークＸＬ
ｆｉイ乍レバースドロー７ＸＬ第５図
第６図
第７図 第８図FIG. 1 is a circuit diagram showing an embodiment of the hydraulic circuit of the present invention, FIG. 2 is an explanatory diagram showing the basic configuration of a control device provided in the embodiment shown in FIG. 1, and FIGS. 3 and 4. is a characteristic diagram obtained in the embodiment shown in Fig. 1, Fig. 5 is a circuit diagram showing a conventional hydraulic circuit, and Figs. 6, 7, and 8 are obtained in the hydraulic circuit shown in Fig. 5. It is a characteristic diagram. 1...Hydraulic motor (actuator), 2...
...Hydraulic cylinder (actuator), 3.4...
... Control valve with pressure compensation, 5 ... Operation lever, 6a ... Control device, 7 ... Hydraulic pump with pressure compensation, 10 ... Engine, 11...
... Fuel lever, 12 ... Target rotation speed setting device, 16 ... Signal line, 17 ... Function generating means, 18 ... Multiplier. Figure 1! ----- Hydraulic pressure (actuator 7) 10
・-m=Engine 2----Hydraulic pressure, syringe "(actu-yue-ri)" 17---Encyclopedia lever 3----Pressure compensation #:T %IJ press #12----
Ichimoku transmutation firmness, clamping 4 ---- Pressure fJ compensation morning snoring valve t6 - 11 signal release 5 ---- Munsaku lever 17 ---- ISl'l Seiyu Hand starvation 6O---eJWH placement ta---
---*1 Pressure 13 Pressure 13 Figure 2 Figure 3 Figure 4 Capture bar = Stroke XL
Fi I Revers Draw 7XL Fig. 5 Fig. 6 Fig. 7 Fig. 8
Claims (1)
タの駆動を制御する圧力補償付制御弁と、これらの圧力
補償付制御弁の駆動を制御する操作信号を出力する操作
レバーと、上記圧力補償付制御弁を介して上記アクチユ
エータのそれぞれに圧油を供給する油圧ポンプと、この
油圧ポンプを駆動するエンジンとを備えた油圧回路にお
いて、上記エンジンの回転数の変化に応じて上記操作レ
バーのストロークと圧力補償付制御弁のスプールのスト
ロークとの相関関係を変化させる手段を設けたことを特
徴とする油圧回路。(1) A plurality of actuators, a pressure-compensated control valve that controls the drive of these actuators, an operating lever that outputs an operation signal that controls the drive of these pressure-compensated control valves, and the pressure-compensated control valve described above. In a hydraulic circuit comprising a hydraulic pump that supplies pressure oil to each of the actuators via a hydraulic pump and an engine that drives the hydraulic pump, the stroke and pressure of the operating lever are compensated according to changes in the rotational speed of the engine. A hydraulic circuit characterized by being provided with means for changing the correlation between the attached control valve and the stroke of the spool.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1509087A JPS63186004A (en) | 1987-01-27 | 1987-01-27 | Hydraulic circuit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1509087A JPS63186004A (en) | 1987-01-27 | 1987-01-27 | Hydraulic circuit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63186004A true JPS63186004A (en) | 1988-08-01 |
Family
ID=11879146
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1509087A Pending JPS63186004A (en) | 1987-01-27 | 1987-01-27 | Hydraulic circuit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63186004A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1990002268A1 (en) * | 1988-08-31 | 1990-03-08 | Hitachi Construction Machinery Co., Ltd. | Hydraulic driving apparatus |
| WO1995004227A1 (en) * | 1993-07-30 | 1995-02-09 | Kabushiki Kaisha Kobe Seiko Sho | Hydraulic device for a working machine |
| JP2010112475A (en) * | 2008-11-06 | 2010-05-20 | Hitachi Constr Mach Co Ltd | Hydraulic drive device for work machine |
| WO2013007061A1 (en) * | 2011-07-14 | 2013-01-17 | 长沙中联重工科技发展股份有限公司 | Concrete pumping device, series cylinder and stroke end adaptive compensation method thereof |
| CN114635885A (en) * | 2022-05-18 | 2022-06-17 | 徐工集团工程机械股份有限公司建设机械分公司 | Oil cylinder driven closed type traveling system and working method thereof |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61252902A (en) * | 1985-05-02 | 1986-11-10 | ダンフオス アクチエセルスカベト | Controller for at least one hydraulic operating actuator |
-
1987
- 1987-01-27 JP JP1509087A patent/JPS63186004A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61252902A (en) * | 1985-05-02 | 1986-11-10 | ダンフオス アクチエセルスカベト | Controller for at least one hydraulic operating actuator |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1990002268A1 (en) * | 1988-08-31 | 1990-03-08 | Hitachi Construction Machinery Co., Ltd. | Hydraulic driving apparatus |
| WO1995004227A1 (en) * | 1993-07-30 | 1995-02-09 | Kabushiki Kaisha Kobe Seiko Sho | Hydraulic device for a working machine |
| US5537819A (en) * | 1993-07-30 | 1996-07-23 | Kabushiki Kaisha Kobe Seiko Sho | Hydraulic device for working machine |
| CN1034969C (en) * | 1993-07-30 | 1997-05-21 | 株式会社神户制钢所 | Hydraulic device for a working machine |
| JP2010112475A (en) * | 2008-11-06 | 2010-05-20 | Hitachi Constr Mach Co Ltd | Hydraulic drive device for work machine |
| WO2013007061A1 (en) * | 2011-07-14 | 2013-01-17 | 长沙中联重工科技发展股份有限公司 | Concrete pumping device, series cylinder and stroke end adaptive compensation method thereof |
| CN114635885A (en) * | 2022-05-18 | 2022-06-17 | 徐工集团工程机械股份有限公司建设机械分公司 | Oil cylinder driven closed type traveling system and working method thereof |
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