JPS5832985A - Controller for hydraulic pump of variable capacity - Google Patents
Controller for hydraulic pump of variable capacityInfo
- Publication number
- JPS5832985A JPS5832985A JP56130277A JP13027781A JPS5832985A JP S5832985 A JPS5832985 A JP S5832985A JP 56130277 A JP56130277 A JP 56130277A JP 13027781 A JP13027781 A JP 13027781A JP S5832985 A JPS5832985 A JP S5832985A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic pump
- displacement
- servo
- cylinder chamber
- control device
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
この発明は１つの原動機で駆動される複数の可変容量形
油圧ポンプの制御装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a control device for a plurality of variable displacement hydraulic pumps driven by one prime mover.
第１図は従来の可変容量形油圧ポンプの制御装置を示す
図である。図において１は原動機、２．６は原動機１に
より駆動される可変容量形油圧ポンプ、４は原動機１の
動力を油圧ポンプ２．３に伝達するトランスミッション
、５．６は油圧ポンプ２．６の押しのけ容積制御装置で
あるバネ付シリンダで、シリンダ５、乙の変位量により
油圧ポンプ２．３の押しのけ容積すなわち斜板傾転角が
制御される。７．８はシリンダ５、乙のバネ、９１０は
シリンダ５．６のシリンダ室、１１は方向切換弁で、方
向切換弁１１がＡ位置のときには、油圧ポンプ２．３の
吐出圧力すなわち自己の吐出圧力がシリンダ室９．１０
に供給され、方向切換弁１１がＢ位置のときには、チェ
ック弁１２が設けられているため、油圧ポンプ２．６の
吐出圧力のうち高い方の吐出圧力がシリンダ室９．１ｏ
の両方に供給される。FIG. 1 is a diagram showing a conventional control device for a variable displacement hydraulic pump. In the figure, 1 is the prime mover, 2.6 is a variable displacement hydraulic pump driven by the prime mover 1, 4 is a transmission that transmits the power of the prime mover 1 to the hydraulic pump 2.3, and 5.6 is the displacement of the hydraulic pump 2.6. The displacement of the hydraulic pump 2.3, that is, the tilt angle of the swash plate, is controlled by the displacement amount of the cylinder 5 and the cylinder B, which is a spring-equipped cylinder that is a volume control device. 7.8 is the spring of the cylinder 5, B, 910 is the cylinder chamber of the cylinder 5.6, 11 is the directional control valve, and when the directional control valve 11 is in the A position, the discharge pressure of the hydraulic pump 2.3, that is, its own discharge. The pressure in the cylinder chamber is 9.10
Since the check valve 12 is provided, when the directional control valve 11 is in the B position, the higher discharge pressure of the hydraulic pump 2.6 is transferred to the cylinder chamber 9.1o.
supplied to both.
この制御装置においては、方向切換弁１１がＡ位置の場
合、自己の吐出圧力がシリンダ室９、１０に供給される
から、油圧ポンプ２．６の吐出圧力が所定値に達するま
では、油圧ポンプ２．６の斜板傾転角が最大であり、油
圧ポンプ２、乙の吐出流量が最大であるが、油圧ポンプ
２．３の吐出圧力が所定値以上になると、シリンダ５．
６がバネ７．８に抗して伸長し、油圧ポンプ２．６の斜
板傾転角が小さくなり、油圧ポンプ２、乙の吐出流量が
減少し、油圧ポンプ２．６の吸収馬力がほぼ一定に保持
される。また、方向切換弁１１が゛Ｂ位置の場合には、
油圧ポンプ２．６の吐出圧力のうち高い方の吐出圧力が
シリンダ室９．１０の両方に供給されるから、油圧ポン
プ２．６の吐出圧力が異なっていても、油圧ポンプ２、
乙の斜板傾転角が等しくなり、油圧ポンプ２、乙の吐出
流量が等しくなる。しかし、この場合には吐出圧力が低
い方の油圧ポンプたとえば油圧ポンプ２の吐出流量が、
吐出圧力が高い方の□油：″圧ポンプ６の吐出圧力に応
じて減少するから、油圧ポンプ２の吸収馬力が減少し、
原動機１の出力馬力を有効に利用できない。In this control device, when the directional control valve 11 is in the A position, its own discharge pressure is supplied to the cylinder chambers 9 and 10. Therefore, until the discharge pressure of the hydraulic pump 2.6 reaches a predetermined value, the hydraulic pump The swash plate tilting angle of cylinder 5.2.6 is the maximum, and the discharge flow rate of hydraulic pump 2.
6 expands against the spring 7.8, the tilting angle of the swash plate of the hydraulic pump 2.6 becomes smaller, the discharge flow rate of the hydraulic pump 2 and O decreases, and the absorbed horsepower of the hydraulic pump 2.6 becomes almost the same. held constant. Furthermore, when the directional control valve 11 is in the 'B' position,
Since the higher discharge pressure of the hydraulic pumps 2.6 is supplied to both cylinder chambers 9.10, even if the discharge pressures of the hydraulic pumps 2.6 are different, the hydraulic pumps 2.
The tilting angles of the swash plates of the hydraulic pumps 2 and 2 become equal, and the discharge flow rates of the hydraulic pumps 2 and 2 become equal. However, in this case, the discharge flow rate of the hydraulic pump with lower discharge pressure, such as hydraulic pump 2, is
□Oil with higher discharge pressure: ``Since it decreases according to the discharge pressure of the pressure pump 6, the absorption horsepower of the hydraulic pump 2 decreases,
The output horsepower of the prime mover 1 cannot be used effectively.
この発明は上述の問題点を解決するためになされたもの
で、原動機の出力馬力を有効に利用することのできる可
変容量形油圧ポンプの制御装置を提供することを目的と
する。The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a control device for a variable displacement hydraulic pump that can effectively utilize the output horsepower of a prime mover.
この目的を達成するため、この発明においては１つの原
動機で駆動される第１、第２可変容量形油圧ポンプを制
御する装置において、上記第１、第２可変容量形油圧ポ
ンプの押しのけ容積を制御する第１、第２押しのけ容積
制御装置と、その第１、第２押しのけ容積制御装置と上
記第１、第２可変容量形油圧ポンプの吐出側管路とを接
続する第１、第２管路と、その第１、第２管路に設けら
れた第１、第２絞りと、上記第１、第２管路の上記第１
、第２絞りよりも上記第１、第２押しのけ容積制御装置
側を接続する接続管路とを設ける。In order to achieve this object, the present invention provides a device for controlling first and second variable displacement hydraulic pumps driven by one prime mover, which controls the displacement of the first and second variable displacement hydraulic pumps. first and second displacement control devices, and first and second pipe lines connecting the first and second displacement control devices and the discharge side pipe lines of the first and second variable displacement hydraulic pumps. , first and second apertures provided in the first and second conduits, and first and second apertures provided in the first and second conduits.
, and a connecting conduit connecting the first and second displacement control devices closer to the second throttle.
第２図はこの発明に係る可変容量形油圧ポンプの制御装
置を示す図である。図において１６．１４は可変容量形
油圧ポンプ２．３の吐出側管路とバネ付シリンダ５、乙
のシリンダ室９ζ １０とを接続する管路、１５．１６
は管路１６．１４に設けられた絞り、１７は管路１３．
１４の絞り１５．１６よりもシリンダ５．６側を接続す
る接である。FIG. 2 is a diagram showing a control device for a variable displacement hydraulic pump according to the present invention. In the figure, 16.14 is a conduit connecting the discharge side conduit of the variable displacement hydraulic pump 2.3, the spring-equipped cylinder 5, and the cylinder chamber 9ζ 10, and 15.16
17 is a throttle provided in the pipe line 16.14, and 17 is a throttle provided in the pipe line 13.
This is a connection connecting the cylinder 5.6 side with respect to the throttle 15.16 of No. 14.
第６図はシリンダ５．６のシリンダ室９．１０内の圧力
すなわち制御圧力と油圧ポンプ２１．６の吐出流量との
関係を示すグラフである。このグラフに示すように、シ
リンダ室９．１０内の圧力力く８によって縮小しており
、油圧ポンプ２、乙の斜板傾転角が最大であり、油圧ポ
ンプ２．６の吐出流量はＱｍａｘであるが、シリンダ室
９．１０内の圧力がｐ 以上に力ると、ノ（ネ７．８に
抗してシリンダ５．６が伸長するから、油圧ポンプ２．
６の斜板傾転角が小さく々す、油圧ポンプ゛２．５の吐
出流量が減少する。FIG. 6 is a graph showing the relationship between the pressure in the cylinder chamber 9.10 of the cylinder 5.6, that is, the control pressure, and the discharge flow rate of the hydraulic pump 21.6. As shown in this graph, the pressure force inside the cylinder chamber 9.10 is reduced by Q8, the swash plate tilt angle of the hydraulic pump 2 and B is the maximum, and the discharge flow rate of the hydraulic pump 2.6 is Qmax. However, when the pressure in the cylinder chamber 9.10 exceeds p, the cylinder 5.6 expands against the pressure of the hydraulic pump 2.
As the tilting angle of the swash plate 6 becomes smaller, the discharge flow rate of the hydraulic pump 2.5 decreases.
この制御装置においては、−開閉弁１８が閉のときには
、油圧ポンプ２．５の吐出圧力が絞り１５１６を介して
シリンダ室９．１０に導かれる。しだがって、油圧ポン
プ２．６の吐出圧力がｐ。に達するまでは、油圧ポンプ
２．６の吐出流量はＱｍａｘであシ、油圧ポンプ２．６
の吐出圧力がｐ 以上になると、油圧ポンプ２．６の吐
出買置が減少して、油圧ポンプ２．６の吸収馬力がほぼ
一定に保持される。たとえば、油圧ポンプ２．６の吐出
圧力がそれぞれｐｌ、ｐ２であると、油圧ポンプ２．６
の吐出流量はそれぞれＱｌ、Ｑ２となり油圧ポンプ２．
６の吸収馬力はそれぞれ原動機１の出力馬力の約５０ｑ
６である。そして、この状態で開閉弁１８を開にすると
、シリンダ室？、１０に導かれる圧力は、絞り１５．１
６によって圧力ｐ 、 ｐ２の平均値ｐａとなるから
、油圧ポンプ２６の吐出流量は吐出流量Ｑ１、Ｑ２の平
均値Ｑａとなる。すなわち、油圧ポンプ２の吐出流量は
ＱｌからＱ へと減少し、油圧ポンプ６の吐出流量はＱ
２からＱａへと増加して、油圧ポンプ２．６の吐出流量
が等しくなる。この場合、油圧ポンプ２．６の吐出圧力
ｐ１、ｐ２は変らないので、油圧ポンプ２の吸収馬力が
減少し、油圧ポンプ６の吸収馬力が増加し、たとえば油
圧ポンプ２の吸収馬力が原動機１の出力馬力の３０％だ
とすると、油圧ポンプ３の吸収馬力は原動機１の出力馬
力の約７０チとなり、原動機１の出力馬力を１００％近
く利用することができる。In this control device, - when the on-off valve 18 is closed, the discharge pressure of the hydraulic pump 2.5 is led to the cylinder chamber 9.10 via the throttle 1516; Therefore, the discharge pressure of the hydraulic pump 2.6 is p. The discharge flow rate of the hydraulic pump 2.6 is Qmax until the hydraulic pump 2.6 reaches
When the discharge pressure of the hydraulic pump 2.6 becomes equal to or higher than p, the discharge capacity of the hydraulic pump 2.6 decreases, and the absorbed horsepower of the hydraulic pump 2.6 is kept almost constant. For example, if the discharge pressures of the hydraulic pump 2.6 are pl and p2, respectively, then the hydraulic pump 2.6
The discharge flow rates of hydraulic pump 2. are Ql and Q2, respectively.
The absorption horsepower of 6 is approximately 50q of the output horsepower of prime mover 1.
It is 6. Then, when the on-off valve 18 is opened in this state, the cylinder chamber? , 10 is the pressure introduced into the throttle 15.1
6, the pressures p and p2 become the average value pa, so the discharge flow rate of the hydraulic pump 26 becomes the average value Qa of the discharge flow rates Q1 and Q2. That is, the discharge flow rate of the hydraulic pump 2 decreases from Ql to Q, and the discharge flow rate of the hydraulic pump 6 decreases from Q1 to Q1.
2 to Qa, the discharge flow rate of the hydraulic pump 2.6 becomes equal. In this case, the discharge pressures p1 and p2 of the hydraulic pump 2.6 do not change, so the absorption horsepower of the hydraulic pump 2 decreases, and the absorption horsepower of the hydraulic pump 6 increases. If it is 30% of the output horsepower, the absorption horsepower of the hydraulic pump 3 is about 70 inches of the output horsepower of the prime mover 1, and nearly 100% of the output horsepower of the prime mover 1 can be utilized.
第４図はこの発明に係る他の可変容量形油圧ポンプの制
御装置を示す図である。図において１９．２０は油圧ポ
ンプ２．６の押しのけ容積制御装置、２１．２２は油圧
源、２６．２４は油圧源２１．２２に接続されたサーボ
弁、２５．２６はサーボ弁２６．２４のバネ、２７．２
８はサーボ弁２３２４のパイロットポー吟で、パイロッ
トポート２７．２８には管路１６．１４が接続されてい
る。FIG. 4 is a diagram showing another control device for a variable displacement hydraulic pump according to the present invention. In the figure, 19.20 is the displacement control device of the hydraulic pump 2.6, 21.22 is the hydraulic power source, 26.24 is the servo valve connected to the hydraulic power source 21.22, and 25.26 is the servo valve 26.24. Spring, 27.2
8 is a pilot port of the servo valve 2324, and a pipe line 16.14 is connected to the pilot port 27.28.
２９．６０は、サーボ弁２６．２４に接続されたサーボ
ピストンで、サーボピストン２９．３０の変位量によシ
、油圧ポンプ２．６の押しのけ容量すなわち斜板傾転角
が制御される。29.60 is a servo piston connected to a servo valve 26.24, and the displacement of the servo piston 29.30 controls the displacement of the hydraulic pump 2.6, that is, the swash plate tilt angle.
第５図は第４図に示した制御装置１９の構造を示す断面
図である。図において６１はサーボ弁２３のスプール、
６２・はサーボ弁２６のスリーブ、′５６は一端がサー
ボ弁２５の弁体に回動可能に取付けられたフィードバッ
クレバー、３４．６５はレバー３６に設けられたピンで
、ピン３４．３５はそれぞれサーボピストン２９、スリ
ーブ３２に係合している。３／）、３７はサーボピスト
ン２９の両側に形成されたシリンダ室である。なお、制
御装置２０の構造も同様である。FIG. 5 is a sectional view showing the structure of the control device 19 shown in FIG. 4. In the figure, 61 is the spool of the servo valve 23;
62 is the sleeve of the servo valve 26, '56 is a feedback lever whose one end is rotatably attached to the valve body of the servo valve 25, 34.65 is a pin provided on the lever 36, and the pins 34 and 35 are respectively It engages with the servo piston 29 and sleeve 32. 3/), 37 are cylinder chambers formed on both sides of the servo piston 29. Note that the structure of the control device 20 is also similar.
制御装置１９においては、スプール３１の変位量はバネ
２５の力とパイロットポート２７に作用する圧力による
力とで決定されろ。また、たとえば第５図に示す状態か
ら、スプール３１が左方に変位すると、油圧源２１の圧
油がシリンダ室３６に供給され、一方シリンダ室３７が
タンクに連通するため、サーボピストン２９が左行する
が、このときレバー３６によってスリーブ６２もサーボ
ピストン２９の変位に応じて変位するので、サーボピス
トン２９がスプール３１の変位量に応じた量だけ変位し
たとき、油圧源２１の圧油はスリーブ６２によってシリ
ンダ室６６には供給されなくなり、一方シリンダ室３７
とタンクとの連通がスリーブ６２によって遮断されるか
ら、サーボピストン２９が停止する。すなわち、サーボ
ピストン２９の変位量はスプール６１の変位量に応じた
値となるから、油圧ポンプ２の斜板傾転角はスプール３
１の変位量に応じた値と々る。このように、スプール３
１の変位量はバネ２５の力とパイロットポート２７に作
用する圧力による力とで決定され、まだ油圧ポンプ２の
斜板傾転角はスプール６１の変位量に応じた値となる。In the control device 19, the amount of displacement of the spool 31 is determined by the force of the spring 25 and the force due to the pressure acting on the pilot port 27. For example, when the spool 31 is displaced to the left from the state shown in FIG. At this time, the sleeve 62 is also displaced by the lever 36 in accordance with the displacement of the servo piston 29, so when the servo piston 29 is displaced by an amount corresponding to the displacement of the spool 31, the pressure oil of the hydraulic source 21 is transferred to the sleeve. 62, the cylinder chamber 66 is no longer supplied, while the cylinder chamber 37
Since the communication between the cylinder and the tank is cut off by the sleeve 62, the servo piston 29 stops. That is, since the amount of displacement of the servo piston 29 is a value corresponding to the amount of displacement of the spool 61, the swash plate tilt angle of the hydraulic pump 2 is equal to the amount of displacement of the spool 3.
The value changes according to the amount of displacement of 1. In this way, spool 3
1 is determined by the force of the spring 25 and the force due to the pressure acting on the pilot port 27, and the swash plate tilt angle of the hydraulic pump 2 still has a value corresponding to the displacement of the spool 61.
また、制御装置２０においてもこの動作は同様である。Further, this operation is similar in the control device 20 as well.
したがって、第４図に示した制御装置は第２図に示した
制御装置と同様に油圧ポンプ２．３の吐出量を制御する
から、原動機１の出力馬力を１００チ近く利用すること
ができる。Therefore, since the control device shown in FIG. 4 controls the discharge amount of the hydraulic pump 2.3 in the same way as the control device shown in FIG. 2, nearly 100 horsepower of the output horsepower of the prime mover 1 can be utilized.
なお、上述実施例においては、接続管路１７に開閉弁１
８を設けたが、シリンダ室９．１０、パイロットポート
２７．２８に油圧ポンプ２．６の吐出圧力を供給する制
御すなわち自己の吐出圧力による制御を行なう必要がな
いときには、開閉弁１８を省略してもよい。In addition, in the above-mentioned embodiment, the on-off valve 1 is provided in the connection pipe 17.
However, the on-off valve 18 may be omitted when there is no need to control the supply of the discharge pressure of the hydraulic pump 2.6 to the cylinder chamber 9.10 and the pilot port 27.28, that is, to perform control using its own discharge pressure. You can.
以上説明したように、この発明に係る可変容量形油圧ポ
ンプの制御装置においては、両油圧ポンプの吐出流量を
同じにする制御をしたときに、原動機のほぼ全出力馬力
を利用することができる。As explained above, in the control device for a variable displacement hydraulic pump according to the present invention, when the discharge flow rate of both hydraulic pumps is controlled to be the same, almost the entire output horsepower of the prime mover can be utilized.
とくに、一方の油圧ポンプを無負荷とした場合には、他
方の油圧ポンプに原動機のほぼ全出力馬力を伝えること
ができるから、２つの油圧ポンプの吐出油をバルブ等で
合流させることなく、１つのアクチーエータに原動機の
ほぼ全出力馬力を伝達することができる。このように、
この発明の効果は顕著である。In particular, when one hydraulic pump is left unloaded, almost the full output horsepower of the prime mover can be transmitted to the other hydraulic pump, so the oil discharged from the two hydraulic pumps can be combined without merging at a valve or the like. Almost the entire output horsepower of the prime mover can be transmitted to one actuator. in this way,
The effects of this invention are remarkable.
第１図は従来の可変容量形油圧ポンプの制御装置を示す
図、第２図はこの発明に係る可変容量形油圧ポンプの制
御装置を示す図、第６図は制御圧力と吐出流量との関係
を示すグラフ、第４図はこの発明に係る他の可変容量形
油圧ポンプの制御装置を示す図、第５図は第４図に示し
た押しのけ容積制御装置を示す断面図である。
１・・・原動機
２．６・・・可変容量形油圧ポンプ
５．６・・・バネ付シリンダ
７．８−バネ ９．１０・・・シ１ノンタ゛室
１６．１４・・・管路 １５．１６・・・絞り１７
・・・接続管路 １８・・・吋閉弁１９．２０・
・・押しのけ容積制御装置２６．２４・・・サーボ弁
２５．２６・・・ノ（ネ２７．２８・・・パイロットポ
ート
２９．３０・・・サーボピストン
代理人弁理士 中村純之助
第２ 図
九ｐ１ｐＬｐ２
等１Ｗ乙圧力FIG. 1 is a diagram showing a conventional variable displacement hydraulic pump control device, FIG. 2 is a diagram showing a variable displacement hydraulic pump control device according to the present invention, and FIG. 6 is a diagram showing the relationship between control pressure and discharge flow rate. FIG. 4 is a diagram showing another control device for a variable displacement hydraulic pump according to the present invention, and FIG. 5 is a sectional view showing the displacement control device shown in FIG. 4. 1... Prime mover 2.6... Variable displacement hydraulic pump 5.6... Cylinder with spring 7. 8-Spring 9.10... S1 non-tank chamber 16. 14... Pipe line 15. 16...Aperture 17
...Connecting pipe line 18...7 closing valve 19.20.
... Displacement volume control device 26.24 ... Servo valve
25.26...ノ(ne27.28...Pilot port 29.30...Servo piston agent patent attorney Junnosuke Nakamura No. 2 Figure 9 p1pLp2 etc. 1W B pressure
Claims (1)
ンプを制御する装置において、上記第１、第２可変容量
形油圧ポンプの押しのけ容積を制御する第１、第２押し
のけ容積制御装置と、その第１、第２押しのけ容積制御
装置と上記第１、第２可変容量形油圧ポンプの吐出側管
路とを接続する第１、第２管路と、その第１、第２管路
に設けられた第１、第２絞りと、上記第１、第２管路の
上記第１、第２絞りよりも上記第１、第２押しのけ容積
制御装置側を接続する接続管路とを具備することを特徴
とする可変容量形油圧ポンプの制御装置。A device for controlling first and second variable displacement hydraulic pumps driven by one prime mover, comprising first and second displacement control devices for controlling displacement of the first and second variable displacement hydraulic pumps; , first and second pipe lines connecting the first and second displacement control devices and the discharge side pipes of the first and second variable displacement hydraulic pumps, and the first and second pipe lines. first and second throttles provided, and a connecting pipe line that connects the first and second displacement control device sides of the first and second pipe lines with respect to the first and second throttles. A control device for a variable displacement hydraulic pump, characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56130277A JPS5832985A (en) | 1981-08-21 | 1981-08-21 | Controller for hydraulic pump of variable capacity |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56130277A JPS5832985A (en) | 1981-08-21 | 1981-08-21 | Controller for hydraulic pump of variable capacity |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5832985A true JPS5832985A (en) | 1983-02-26 |
| JPS6246711B2 JPS6246711B2 (en) | 1987-10-03 |
Family
ID=15030453
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56130277A Granted JPS5832985A (en) | 1981-08-21 | 1981-08-21 | Controller for hydraulic pump of variable capacity |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5832985A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2391288A (en) * | 2002-07-30 | 2004-02-04 | Lotus Car | An electrically operated hydraulic fluid control valve |
-
1981
- 1981-08-21 JP JP56130277A patent/JPS5832985A/en active Granted
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2391288A (en) * | 2002-07-30 | 2004-02-04 | Lotus Car | An electrically operated hydraulic fluid control valve |
| GB2391288B (en) * | 2002-07-30 | 2004-12-22 | Lotus Car | An electrically operated valve for controlling flow of hydraulic fluid |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6246711B2 (en) | 1987-10-03 |
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