JPH0694002A - Fluid controller - Google Patents
Fluid controllerInfo
- Publication number
- JPH0694002A JPH0694002A JP4240404A JP24040492A JPH0694002A JP H0694002 A JPH0694002 A JP H0694002A JP 4240404 A JP4240404 A JP 4240404A JP 24040492 A JP24040492 A JP 24040492A JP H0694002 A JPH0694002 A JP H0694002A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- main
- pilot
- main valve
- 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
Landscapes
- Fluid-Pressure Circuits (AREA)
- Injection Moulding Of Plastics Or The Like (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は射出成形機などに使用
される流体制御装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid control device used in an injection molding machine or the like.
【０００２】[0002]
【従来の技術】従来、流体制御装置としては、図４に示
すようなものがある。この流体制御装置は、圧力源１と
アクチュエータ２とを接続するメインライン３に、上流
側より順次、電磁比例減圧弁５と、圧力補償弁６と、電
磁比例絞り弁７を設けている。上記圧力補償弁６は、電
磁比例絞り弁７の前後の差圧を一定に制御する。また、
上記電磁比例絞り弁７とアクチュエータ２との間のメイ
ンライン３にサージ圧吸収弁８を接続している。2. Description of the Related Art Conventionally, there is a fluid control device as shown in FIG. In this fluid control device, a main line 3 connecting the pressure source 1 and the actuator 2 is provided with an electromagnetic proportional pressure reducing valve 5, a pressure compensating valve 6, and an electromagnetic proportional throttle valve 7 sequentially from the upstream side. The pressure compensating valve 6 controls the differential pressure across the electromagnetic proportional throttle valve 7 to be constant. Also,
A surge pressure absorption valve 8 is connected to the main line 3 between the electromagnetic proportional throttle valve 7 and the actuator 2.
【０００３】[0003]
【発明が解決しようとする課題】ところで、上記従来の
流体制御装置では、圧力の制御をメインライン３に設け
た電磁比例減圧弁５で行い、また、流量制御をメインラ
イン３に設けた圧力補償弁６と電磁比例絞り弁７とによ
って行い、サージ圧の吸収をサージ圧吸収弁８で行って
いる。すなわち、上記従来の流体制御装置では、圧力制
御のために電磁比例減圧弁５と、流量制御用の圧力補償
のための圧力補償弁６と、サージ圧吸収のためのサージ
圧吸収弁８という、各々大きなスペースを有する主弁が
必要であるため、全体寸法が大きくなり、コストも高く
なるという問題がある。By the way, in the above-mentioned conventional fluid control apparatus, the pressure control is performed by the electromagnetic proportional pressure reducing valve 5 provided in the main line 3, and the flow rate control is performed by the pressure compensating valve provided in the main line 3. The valve 6 and the electromagnetic proportional throttle valve 7 are used, and the surge pressure absorption valve 8 absorbs the surge pressure. That is, in the above-described conventional fluid control device, there are an electromagnetic proportional pressure reducing valve 5 for pressure control, a pressure compensating valve 6 for pressure compensation for flow rate control, and a surge pressure absorbing valve 8 for absorbing surge pressure. Since a main valve each having a large space is required, there is a problem that the overall size becomes large and the cost becomes high.
【０００４】そこで、この発明の目的は、圧力制御と圧
力補償とサージ圧吸収の３機能を一つの主弁で行わしめ
ることによって、構造をコンパクトにし、かつ安価に構
成できる流体制御装置を提供することにある。Therefore, an object of the present invention is to provide a fluid control device which is compact in structure and inexpensive in construction by performing one function of three functions of pressure control, pressure compensation and surge pressure absorption. Especially.
【０００５】[0005]
【課題を解決するための手段】上記目的を達成するた
め、この発明の流体制御装置は、圧力源とアクチュエー
タとの間のメインラインに、上流側より順次、２次ポー
トをタンクポートとポンプポートとに切換接続する主弁
と絞り弁を設け、上記主弁のバネ室を上記主弁と絞り弁
との間のメインラインに接続し、上記主弁のパイロット
室にパイロットラインを介して電磁比例減圧弁を接続
し、上記パイロット室に絞りを有するパイロットライン
を介して上記圧力源を接続し、上記主弁のパイロット室
に、上記絞り弁の前後の差圧に応動して、上記絞り弁の
前後の差圧が一定になるように上記主弁を動作させるパ
イロット式圧力補償弁を接続したことを特徴としてい
る。In order to achieve the above object, the fluid control system of the present invention has a main line between a pressure source and an actuator, in which secondary ports are sequentially provided from the upstream side to a tank port and a pump port. A main valve and a throttle valve that are switch-connected to and are provided, the spring chamber of the main valve is connected to the main line between the main valve and the throttle valve, and the pilot chamber of the main valve is electromagnetically proportional to the pilot line via a pilot line. A pressure reducing valve is connected, and the pressure source is connected to the pilot chamber via a pilot line having a throttle, and the pilot chamber of the main valve responds to the differential pressure before and after the throttle valve, It is characterized in that a pilot type pressure compensating valve for operating the main valve is connected so that the differential pressure between the front and the rear is constant.
【０００６】また、上記主弁と上記絞り弁との間のメイ
ンラインに分岐ポートを接続するのが望ましい。It is also desirable to connect a branch port to the main line between the main valve and the throttle valve.
【０００７】[0007]
【作用】絞りを通して圧力源からの流体が電磁比例減圧
弁上流側に導かれ、この電磁比例減圧弁によって主弁の
パイロット室の圧力が一定に制御される。一方、主弁の
バネ室には主弁の二次側の圧力がパイロットラインを通
して導かれる。したがって、主弁はその二次圧が電磁比
例減圧弁の設定圧に応じた圧力になるように動作して圧
力制御を行う。The fluid from the pressure source is guided to the upstream side of the electromagnetic proportional pressure reducing valve through the throttle, and the pressure in the pilot chamber of the main valve is controlled to be constant by this electromagnetic proportional pressure reducing valve. On the other hand, the pressure on the secondary side of the main valve is introduced into the spring chamber of the main valve through the pilot line. Therefore, the main valve operates so that its secondary pressure becomes a pressure according to the set pressure of the electromagnetic proportional pressure reducing valve, and performs pressure control.
【０００８】一方、パイロット式圧力補償弁は、主弁の
パイロット室の圧力と絞り弁の二次側の圧力との差に応
動して、主弁のパイロット室の圧力と絞り弁の二次側の
圧力との差、つまり絞り弁の前後の差圧が一定になるよ
うに主弁を動作させるべく動作する。このように、パイ
ロット式圧力補償弁と主弁とによって、絞り弁の圧力補
償を行う。On the other hand, the pilot type pressure compensating valve responds to the difference between the pressure in the pilot chamber of the main valve and the pressure in the secondary side of the throttle valve, and the pressure in the pilot chamber of the main valve and the secondary side of the throttle valve. Of the throttle valve, that is, the pressure difference before and after the throttle valve is constant, so that the main valve is operated. In this way, the pilot type pressure compensation valve and the main valve perform pressure compensation of the throttle valve.
【０００９】一方、メインラインにサージ圧が働くと、
主弁の二次側からそのバネ室にサージ圧が導かれ、主弁
の二次側ポートをタンクポートに連通させてサージ圧を
吸収する。On the other hand, when surge pressure acts on the main line,
Surge pressure is introduced from the secondary side of the main valve to the spring chamber, and the secondary side port of the main valve communicates with the tank port to absorb the surge pressure.
【００１０】このように、この流体制御装置は電磁比例
減圧弁と主弁で、圧力制御弁の働きを行い、パイロット
式圧力補償弁と主弁とによって圧力補償弁の働きを行
い、主弁のバネ室に導くパイロットラインと主弁とによ
ってサージ圧吸収弁の働きをするのである。このよう
に、この流体制御装置はメインラインに設けた一つの主
弁に、圧力制御弁と圧力補償弁とサージ圧吸収弁の働き
を行わしめることができるから、コンパクトになり、安
価に構成できるのである。As described above, the fluid control system includes the electromagnetic proportional pressure reducing valve and the main valve, which serve as the pressure control valve, and the pilot type pressure compensating valve and the main valve serve as the pressure compensating valve. The pilot line leading to the spring chamber and the main valve function as a surge pressure absorption valve. Thus, in this fluid control device, one main valve provided in the main line can function as a pressure control valve, a pressure compensating valve, and a surge pressure absorbing valve, so that it can be made compact and inexpensive. Of.
【００１１】また、上記主弁と絞り弁との間のメインラ
インに分岐ポートとを設けた場合には、上記分岐ポート
に圧力源を接続することによって、上記主弁とパイロッ
ト式圧力補償弁にバイパス型圧力補償弁として動作させ
て、リリーフ型の圧力制御を行うことができる。この場
合、主弁のポンプポートに接続する圧力源はパイロット
圧力源として働く。一方、上記分岐ポートを閉鎖した場
合には、上記主弁とパイロット式圧力補償弁は減圧型圧
力補償弁と動作し、流量マッチ形の制御を行うことにな
る。When a branch port is provided in the main line between the main valve and the throttle valve, a pressure source is connected to the branch port so that the main valve and the pilot type pressure compensating valve are connected. It can be operated as a bypass type pressure compensation valve to perform relief type pressure control. In this case, the pressure source connected to the pump port of the main valve acts as a pilot pressure source. On the other hand, when the branch port is closed, the main valve and the pilot type pressure compensating valve operate together with the pressure reducing type pressure compensating valve to perform the flow rate matching type control.
【００１２】[0012]
【実施例】以下、この発明を図示の実施例により詳細に
説明する。The present invention will be described in detail below with reference to the embodiments shown in the drawings.
【００１３】図１に示すように、この発明の流体制御装
置は、圧力源１と油圧シリンダ２との間のメインライン
３に、上流側から順次、３位置形の主弁１１と電磁比例
絞り弁７とを設けている。上記主弁１１は二次側ポート
ＡをポンプポートＰとタンクポートＴに切換える。上記
主弁１１のバネ室１２にはパイロットライン１３を介し
て主弁１１の二次側のメインライン３を接続する一方、
上記主弁１１のパイロット室１４には、パイロットライ
ン１５を介して電磁比例減圧弁１６を接続している。上
記パイロット室１４と電磁比例減圧弁１６との間のパイ
ロットライン１５には、中間に絞りとしの流量調整弁１
７を有するパイロットライン１８を介し、主弁１１のポ
ンプポートＰと圧力源１との間のメインライン３を接続
している。さらに、上記主弁１１のパイロット室１４に
はパイロットライン２２を介してパイロット式圧力補償
弁２１を接続している。このパイロット式圧力補償弁２
１のバネ室には、パイロットライン２３を介して電磁比
例絞り弁７の制御ポートＣに接続して、このパイロット
式圧力補償弁２１のバネ室に電磁比例絞り弁７の二次側
の圧力を導くようにしている。As shown in FIG. 1, in the fluid control system of the present invention, a main line 3 between a pressure source 1 and a hydraulic cylinder 2 is sequentially arranged from the upstream side to a 3-position main valve 11 and an electromagnetic proportional throttle. Valve 7 is provided. The main valve 11 switches the secondary port A to the pump port P and the tank port T. While the main chamber 3 on the secondary side of the main valve 11 is connected to the spring chamber 12 of the main valve 11 via a pilot line 13,
An electromagnetic proportional pressure reducing valve 16 is connected to the pilot chamber 14 of the main valve 11 via a pilot line 15. In the pilot line 15 between the pilot chamber 14 and the electromagnetic proportional pressure reducing valve 16, a flow rate adjusting valve 1 having a throttle in the middle is provided.
The main line 3 between the pump port P of the main valve 11 and the pressure source 1 is connected via a pilot line 18 having a valve 7. Further, a pilot type pressure compensating valve 21 is connected to the pilot chamber 14 of the main valve 11 via a pilot line 22. This pilot type pressure compensation valve 2
The spring chamber of No. 1 is connected to the control port C of the electromagnetic proportional throttle valve 7 via the pilot line 23, and the secondary chamber pressure of the electromagnetic proportional throttle valve 7 is supplied to the spring chamber of this pilot type pressure compensation valve 21. I am trying to guide you.
【００１４】また、２５はタンク、２６は主弁１１と電
磁比例絞り弁７との間のメインライン３に接続した分岐
ポート、３１,３２はコントローラである。Further, 25 is a tank, 26 is a branch port connected to the main line 3 between the main valve 11 and the electromagnetic proportional throttle valve 7, and 31 and 32 are controllers.
【００１５】上記構成の流体制御装置によれば、電磁比
例減圧弁１６は、圧力源１からパイロットライン１８お
よび流量調整弁１７を通して供給された流体の圧力を所
定の圧力に制御する。これによって、主弁１１のパイロ
ット室の圧力は、電磁比例減圧弁１６の設定圧力に制御
され、主弁１１の二次ポートＡの圧力は上記設定圧より
もそのバネ室１２のバネ圧に相当した分だけ低い圧力に
なるように圧力制御される。このように、主弁１１と電
磁比例減圧弁１６の組み合わせによって圧力制御を行
う。According to the fluid control device having the above structure, the electromagnetic proportional pressure reducing valve 16 controls the pressure of the fluid supplied from the pressure source 1 through the pilot line 18 and the flow rate adjusting valve 17 to a predetermined pressure. As a result, the pressure in the pilot chamber of the main valve 11 is controlled to the set pressure of the electromagnetic proportional pressure reducing valve 16, and the pressure of the secondary port A of the main valve 11 corresponds to the spring pressure of the spring chamber 12 rather than the set pressure. The pressure is controlled so that the pressure becomes lower by the amount. In this way, pressure control is performed by the combination of the main valve 11 and the electromagnetic proportional pressure reducing valve 16.
【００１６】一方、電磁比例絞り弁７が右側のシンボル
位置に切り換えられている場合には、パイロット式圧力
補償弁２１は電磁比例絞り弁７の二次側の圧力と主弁１
１のパイロット室の圧力に応じて応動して、主弁１１の
パイロット室１４の圧力と電磁比例絞り弁７の二次側の
圧力との差が所定の圧力、つまり、電磁比例絞り弁７の
一次側と二次側との差圧が所定の圧力になるように、主
弁１１を動作を制御して、電磁比例絞り弁７の圧力補償
を行う。つまり、主弁１１とパイロット式圧力補償弁２
１とによって電磁比例絞り弁７の圧力補償を行うのであ
る。On the other hand, when the electromagnetic proportional throttle valve 7 is switched to the symbol position on the right side, the pilot pressure compensating valve 21 is connected to the secondary side pressure of the electromagnetic proportional throttle valve 7 and the main valve 1.
1 in response to the pressure in the pilot chamber 1, the difference between the pressure in the pilot chamber 14 of the main valve 11 and the pressure on the secondary side of the electromagnetic proportional throttle valve 7 is a predetermined pressure, that is, the electromagnetic proportional throttle valve 7 The operation of the main valve 11 is controlled so that the pressure difference between the primary side and the secondary side becomes a predetermined pressure, and the pressure of the electromagnetic proportional throttle valve 7 is compensated. That is, the main valve 11 and the pilot type pressure compensation valve 2
1 compensates the pressure of the electromagnetic proportional throttle valve 7.
【００１７】また、メインラインに油圧シリンダ２の急
停止などによってサージ圧が生じた場合に、メインライ
ン３の圧力がパイロットライン１３を通して主弁１２の
バネ室１２に導かれ、主弁１１は左側のシンボル位置に
なって、メインライン３の圧力をタンクポートＴに開放
し、メインライン３のサージ圧を吸収する。このように
パイロットライン１３と主弁１１との組み合わせがサー
ジ圧吸収弁として動作するのである。When surge pressure is generated in the main line due to sudden stop of the hydraulic cylinder 2 or the like, the pressure in the main line 3 is introduced into the spring chamber 12 of the main valve 12 through the pilot line 13, and the main valve 11 is left side. At the symbol position of, the pressure of the main line 3 is released to the tank port T and the surge pressure of the main line 3 is absorbed. In this way, the combination of the pilot line 13 and the main valve 11 operates as a surge pressure absorption valve.
【００１８】このように、この流体制御装置はメインラ
イン３の一つの主弁１１を圧力制御弁の主弁として動作
させ、圧力補償弁の主弁として動作させ、さらに、サー
ジ圧吸収弁としても動作させるのである。つまり、上記
主弁１１と他のパイロットラインに設けた電磁比例減圧
弁１６とパイロット式圧力補償弁１２とパイロットライ
ン１３との組み合わせでもって、これらの３つの機能を
発揮できるので、スペースが小さくなり、小型かつ安価
になる。また、分岐ポート２６に圧力源をつなぐと、上
記主弁１１とパイロット式圧力補償弁２１は組み合わさ
ってバイパス型圧力補償弁としての動作を行う。As described above, this fluid control system operates one main valve 11 of the main line 3 as a main valve of a pressure control valve, as a main valve of a pressure compensation valve, and also as a surge pressure absorption valve. Make it work. That is, the combination of the main valve 11 and the electromagnetic proportional pressure reducing valve 16 provided in the other pilot line, the pilot type pressure compensating valve 12 and the pilot line 13 can achieve these three functions, so that the space is reduced. , Smaller and cheaper. When a pressure source is connected to the branch port 26, the main valve 11 and the pilot type pressure compensating valve 21 are combined to operate as a bypass type pressure compensating valve.
【００１９】図２は、第２の実施例を示している。図１
に示す実施例の電磁比例絞り弁７は制御ポートＣを有す
るものであるが、この電磁比例絞り弁３７には制御ポー
トが設けられていなく、パイロット式圧力補償弁２１の
バネ室はこの電磁比例絞り弁３７の下流側に接続してい
る。この点のみが図１に示す実施例と異なる。FIG. 2 shows a second embodiment. Figure 1
The electromagnetic proportional throttle valve 7 of the embodiment shown in FIG. 6 has a control port C. However, the electromagnetic proportional throttle valve 37 is not provided with a control port, and the spring chamber of the pilot type pressure compensation valve 21 has the electromagnetic proportional throttle valve. It is connected to the downstream side of the throttle valve 37. Only this point is different from the embodiment shown in FIG.
【００２０】図３は、図２に示す分岐ポート２６に圧力
源１を接続し、主弁１１のポンプポートＰにパイロット
圧力源３１を接続したものである。こうすることによっ
て主弁１１とパイロット式圧力補償弁２１の組み合わせ
によってバイパス型圧力補償弁として動作し、リリーフ
形の圧力制御が行われるのである。すなわち、分岐ポー
ト２６を設けることによって、この流体制御装置は図２
に示す減圧形の圧力補償を行う流量マッチ制御と、図３
に示すバイパス形の圧力補償を行う圧力マッチ制御とを
選択することができるのである。In FIG. 3, the pressure source 1 is connected to the branch port 26 shown in FIG. 2, and the pilot pressure source 31 is connected to the pump port P of the main valve 11. By doing so, the combination of the main valve 11 and the pilot type pressure compensating valve 21 operates as a bypass type pressure compensating valve, and the relief type pressure control is performed. That is, by providing the branch port 26, this fluid control device is
Fig. 3 shows the flow rate match control for pressure reduction type pressure compensation shown in Fig.
It is possible to select the pressure match control for performing the bypass type pressure compensation shown in FIG.
【００２１】[0021]
【発明の効果】以上より明らかなように、この発明の流
体制御装置はメインラインの主弁のパイロット室に絞り
を通して圧力源の流体を導き、この主弁のパイロット室
の圧力を電磁比例減圧弁で制御し、かつ、パイロット式
圧力補償弁で制御する一方、この主弁のバネ室に主弁の
二次側の圧力をパイロットラインを介して導き、この主
弁をパイロット室とバネ室の圧力に応じてポンプポート
とタンクポートに切換え接続せしめるようにしているの
で、このメインラインに設けられた主弁一つでもって、
圧力制御と圧力補償とサージ圧吸収を行わしめることが
できる。したがって、この発明によれば、小型化がで
き、かつ、製作コストを安価にすることができる。As is apparent from the above, the fluid control device of the present invention introduces the fluid of the pressure source through the pilot chamber of the main valve of the main line to introduce the fluid of the pressure source, and the pressure in the pilot chamber of the main valve is proportional to the electromagnetic proportional pressure reducing valve. The pressure on the secondary side of the main valve is introduced to the spring chamber of the main valve via the pilot line, and the pressure on the main chamber is adjusted to the pressure of the pilot chamber and the spring chamber. It is designed so that it can be switched and connected to the pump port and the tank port according to, so with only one main valve installed in this main line,
It can perform pressure control, pressure compensation, and surge pressure absorption. Therefore, according to the present invention, the size can be reduced and the manufacturing cost can be reduced.
【００２２】また、上記主弁の二次側と主弁によって圧
力補償される絞り弁との間のメインラインに分岐ポート
を設けると、この流体制御装置の主弁を減圧形の圧力補
償弁として動作させたり、リリーフ形の圧力補償弁とし
て動作させたりすることができ、広い用途に適用するこ
とができる。If a branch port is provided in the main line between the secondary side of the main valve and the throttle valve whose pressure is compensated by the main valve, the main valve of this fluid control device can be used as a pressure reducing type pressure compensating valve. It can be operated or operated as a relief type pressure compensation valve, and can be applied to a wide range of applications.
【図１】 この発明の第１実施例の流体制御装置の回路
図である。FIG. 1 is a circuit diagram of a fluid control system according to a first embodiment of the present invention.
【図２】 この発明の第２実施例の流体制御装置の回路
図である。FIG. 2 is a circuit diagram of a fluid control system in a second embodiment of the present invention.
【図３】 この発明の第３実施例の流体制御装置の回路
図である。FIG. 3 is a circuit diagram of a fluid control system in a third embodiment of the present invention.
【図４】 従来の流体制御装置の回路図である。FIG. 4 is a circuit diagram of a conventional fluid control device.
１,３１…圧力源、２…油圧シリンダ、３…メインライ
ン、７…電磁比例絞り弁、１１…主弁、１２…バネ室、
１３,１５,１８,２２…パイロットライン、１４…パイ
ロット室、１６…電磁比例減圧弁、２１…パイロット式
圧力補償弁。1, 31 ... Pressure source, 2 ... Hydraulic cylinder, 3 ... Main line, 7 ... Electromagnetic proportional throttle valve, 11 ... Main valve, 12 ... Spring chamber,
13, 15, 18, 22 ... Pilot line, 14 ... Pilot chamber, 16 ... Electromagnetic proportional pressure reducing valve, 21 ... Pilot type pressure compensating valve.
Claims (2)
のメインライン(３)に、上流側より順次、２次ポート
(Ａ)をタンクポート(Ｔ)とポンプポート(Ｐ)とに切換接
続する主弁(１１)と絞り弁(７)を設け、上記主弁(１１)
のバネ室(１２)を上記主弁(１１)と絞り弁(７)との間の
メインライン(３)に接続し、上記主弁(１１)のパイロッ
ト室(１４)にパイロットライン(１５)を介して電磁比例
減圧弁(１６)を接続し、上記パイロット室(１４)に絞り
(１７)を有するパイロットライン(１８)を介して上記圧
力源(１)を接続し、上記主弁(１１)のパイロット室(１
４)に、上記絞り弁(７)の前後の差圧に応動して、上記
絞り弁(７)の前後の差圧が一定になるように上記主弁
(１１)を動作させるパイロット式圧力補償弁(２１)を接
続したことを特徴とする流体制御装置。1. A main line (3) between a pressure source (1) and an actuator (2) is provided with a secondary port sequentially from an upstream side.
The main valve (11) and the throttle valve (7) for switching and connecting (A) to the tank port (T) and the pump port (P) are provided, and the main valve (11)
The spring chamber (12) of the main valve (11) is connected to the main line (3) between the throttle valve (7), and the pilot line (15) is connected to the pilot chamber (14) of the main valve (11). Connect the solenoid proportional pressure reducing valve (16) via the
The pressure source (1) is connected through a pilot line (18) having (17), and the pilot chamber (1) of the main valve (11) is connected.
4) In response to the differential pressure across the throttle valve (7), the main valve is adjusted so that the differential pressure across the throttle valve (7) becomes constant.
A fluid control system comprising a pilot type pressure compensating valve (21) for operating (11).
て、上記主弁(１１)と上記絞り弁(７)との間のメインラ
イン(３)に分岐ポート(２６)を接続したことを特徴とす
る流体制御装置。2. The fluid control device according to claim 1, wherein a branch port (26) is connected to a main line (3) between the main valve (11) and the throttle valve (7). Fluid control device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4240404A JP2871333B2 (en) | 1992-09-09 | 1992-09-09 | Fluid control device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4240404A JP2871333B2 (en) | 1992-09-09 | 1992-09-09 | Fluid control device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0694002A true JPH0694002A (en) | 1994-04-05 |
| JP2871333B2 JP2871333B2 (en) | 1999-03-17 |
Family
ID=17058967
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4240404A Expired - Fee Related JP2871333B2 (en) | 1992-09-09 | 1992-09-09 | Fluid control device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2871333B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2020063843A (en) * | 2019-12-10 | 2020-04-23 | 株式会社クボタ | Hydraulic system for work machine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3455488B2 (en) | 1999-11-12 | 2003-10-14 | 日精樹脂工業株式会社 | Hydraulic drive of injection molding machine |
-
1992
- 1992-09-09 JP JP4240404A patent/JP2871333B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2020063843A (en) * | 2019-12-10 | 2020-04-23 | 株式会社クボタ | Hydraulic system for work machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2871333B2 (en) | 1999-03-17 |
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