JPS61116104A - Hydraulic controller - Google Patents
Hydraulic controllerInfo
- Publication number
- JPS61116104A JPS61116104A JP23666984A JP23666984A JPS61116104A JP S61116104 A JPS61116104 A JP S61116104A JP 23666984 A JP23666984 A JP 23666984A JP 23666984 A JP23666984 A JP 23666984A JP S61116104 A JPS61116104 A JP S61116104A
- Authority
- JP
- Japan
- Prior art keywords
- actuator
- oil
- pump
- valve
- pressure
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/41—Flow control characterised by the positions of the valve element
- F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
- F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
- F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
- F15B2211/5154—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
- F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
- F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は液圧制御装置、特に１のポンプから吐出された
圧油で作動される複数の油圧アクチュエータを有する油
圧パワーショベル、舶用油圧ウィンチ、油圧搬送装置等
に好適な液圧制御装置に関するＯ
（従来の技術）
第２図に従来の液圧制御装置の油圧回路が示され、（１
）はポンプ、＋２１ 、 （３１はアクチュエータでポ
ンプ（１］から吐出された圧油を並列に供給して作動で
きるように接続されている。（４）はアクチュエータ（
３）への圧油の給排を司掌する方向切換弁、（５）はア
クチュエータ（２）への圧油の給排を司掌する方向切換
弁を示す。Detailed Description of the Invention (Industrial Application Field) The present invention relates to a hydraulic control device, particularly a hydraulic power shovel having a plurality of hydraulic actuators operated by pressure oil discharged from one pump, a marine hydraulic winch, O Regarding a Hydraulic Pressure Control Device Suitable for Hydraulic Conveyance Devices, etc. (Prior Art) A hydraulic circuit of a conventional hydraulic pressure control device is shown in FIG.
) is a pump;
3) is a directional switching valve that controls the supply and discharge of pressure oil to the actuator (2), and (5) is a directional switching valve that controls the supply and discharge of pressure oil to the actuator (2).
方向切換弁（４）及び（５）が図示のように中立位置Ｃ
４ｂ） 、 （５ｊ）を占めるときは、ポンプ（１）か
ら吐出された圧油は油路住３）、（１５，（ｌη、方向
切換弁＋４１ 、 （５１を通り、油路（ホ）、（ハ）
、抵抗αＤ、油路■をこの順に経てタンク（１３に流入
する。The directional control valves (4) and (5) are in neutral position C as shown.
4b), (5j), the pressure oil discharged from the pump (1) passes through the oil passage 3), (15, (lη, directional control valve +41, (51), and enters the oil passage (e), (c)
, resistance αD, and oil path ■in this order, it flows into the tank (13).
方向切換弁（４）を（４α）位置に切刃換えるとポンプ
（１）から吐出された圧油は油路Ｑ３１．（１！ｊ、σ
力、方向切換弁（４）、油路■を経てアクチュエータ（
３）に流入し、これをａ先方向に回転させる。その際ア
クチュエータ（３）から流出した油は油路Ｃυ、方向切
換弁（４１、油ｊｒ、（２７１，（ホ）、抵抗αＤ、油
路＠をこの順に経てタンク（１２１に流入する。逆に、
方向切換弁（４）を（４Ｃ）位置に切シ換えると、ポン
プ（１）から吐出された圧油は方向切換弁（４）から油
路（２υを経てアクチュエータ（３）に流入して、これ
をｂ矢方向に回転させる。その際、アクチュエータ（３
）から流出した油は油路■から方向切換弁（４）を経て
タンク（Ｌｚに流入する。When the cutting blade of the directional control valve (4) is changed to the (4α) position, the pressure oil discharged from the pump (1) flows through the oil path Q31. (1!j, σ
The actuator (
3) and rotates it in the direction a. At this time, the oil flowing out from the actuator (3) flows into the tank (121) through the oil path Cυ, the directional control valve (41, oil jr, (271, (e), the resistance αD, and the oil path @ in this order. ,
When the directional control valve (4) is switched to the (4C) position, the pressure oil discharged from the pump (1) flows from the directional control valve (4) through the oil path (2υ) to the actuator (3). Rotate this in the direction of arrow b.At this time, actuator (3
) flows into the tank (Lz) from the oil path (2) through the directional control valve (4).
換弁（５）、油路（１８、を静てアクチュエータ（２）
の押側室（２α）に入シ、そのピストン（２Ｃ）を押し
上げる。Shut down the switching valve (5) and oil line (18), and then turn off the actuator (2).
enters the push side chamber (2α) of the piston (2C) and pushes up the piston (2C).
アクチュエータ（２）の別個Ｗｉ Ｃ２ｂ）から排出さ
れた油は油路α優、方向切換弁（５）、油路勾、（ハ）
、抵抗αＢ、油路（至）を経てタンク（１７Ｊに流入す
る。逆に方向切換弁（５）を（５Ｃ）位置に切シ換える
と、ポンプ（１）から吐出された圧油は方向切換弁（５
）を経て油路翰を通シアクチュエータ（２）の引側室（
２ｈ）内に流入してピストン（２Ｃ）を降下させる。そ
の際押側室（２α）から排出された油は油路（ｌ→、方
向切換弁（５）を経てタンクα２に流入する。The oil discharged from the separate Wi C2b) of the actuator (2) is sent to the oil passage α Yu, the directional control valve (5), the oil passage gradient, (c)
, resistance αB, and the oil path (to) to flow into the tank (17J). Conversely, when the directional control valve (5) is switched to the (5C) position, the pressure oil discharged from the pump (1) is directional. Valve (5
) and the oil passageway through the pull side chamber of the shear actuator (2) (
2h) and lowers the piston (2C). At this time, the oil discharged from the push side chamber (2α) flows into the tank α2 via the oil passage (l→) and the directional switching valve (5).
（６）は負荷保持チェック弁で、アクチュエータ（２）
と（３）が同時に作動しているとき、アクチュエータ（
２）の負荷がアクチュエータ（３）の負荷よシ大きくな
った場合に、アクチュエータ（２）から排出された油が
油路（１６１、Ｃ４）、Ｃ９，αηを経てアクチュエー
タ（３）に流入するのを防止する。（９１、（ＩＱＩは
オーバロート０リリーフ弁でアクチュエータ（２）に外
力が作用したとき、油路αＢ 、 （１１に発生する異
常高圧を吸収する。（力。(6) is the load holding check valve, and the actuator (2)
and (3) are operating at the same time, the actuator (
When the load on actuator (3) becomes larger than the load on actuator (3), oil discharged from actuator (2) flows into actuator (3) via oil path (161, C4), C9, αη. prevent. (91, (IQI is an overrot 0 relief valve that absorbs the abnormal high pressure that occurs in the oil path αB, (11) when an external force acts on the actuator (2).
（８）はバキューム防止チェック弁で油路（ｌＩ１９又
は（１１内に真空が生じたとき、タンクα２からの油を
油路■、抵抗（１］）、油路□□□、（財）を経て油路
■又は（ハ）を通して油路（２）又はα■内に補給する
。抵抗ａυはオイルクーラ、通路抵抗等油路（ハ）から
タンクα２に至る経路中の抵抗を代表して示している。(8) is a vacuum prevention check valve, and when a vacuum is generated in the oil path (lI19 or (11), the oil from tank The resistance aυ is representative of the resistance in the path from the oil path (C) to the tank α2, such as the oil cooler and passage resistance. ing.
（発明が解決しようとする問題点）
上記従来の装置においては、方向切換弁（５）が（５Ｃ
）位置に切シ換えられた状態でアクチュエータ（２）が
これに作用する外力又は自重を受けて矢印方向に作動中
（以下、「自重落下」という）に、アクチュエータ（３
）を重負荷で同時に作動させようとしてもアクチュエー
タ（３）が作動しない。即ち、アクチュエータ（２）の
自重落下中はポンプ（１）からの圧油が油路α３ 、
（１４）、 （１６１、方向切換弁（５）、油路α■を
経てアクチュエータ（２）の引側室（２ｂ）内に流入す
るが、この状態でアクチュエータ（３）を作動させるた
めに方向切換弁（４）を（４α）位置又は（４Ｃ）位置
に切シ換えても、アクチュエータ（２）の負荷圧力はア
クチュエータ（３）の負荷圧力より著しく小さいため、
ポンプｆｉ＋からの圧油は油路（１つ、（ｌηに流入せ
ず全て油路Ｉ。(Problems to be Solved by the Invention) In the above conventional device, the directional control valve (5) is (5C
) position and the actuator (2) is operating in the direction of the arrow under the influence of an external force acting on it or its own weight (hereinafter referred to as "self-weight drop"), when the actuator (3)
) at the same time with a heavy load, the actuator (3) will not operate. That is, while the actuator (2) is falling under its own weight, the pressure oil from the pump (1) flows through the oil path α3,
(14), (161, Directional switching valve (5), oil passage α■ flows into the pull-side chamber (2b) of the actuator (2), but in this state, the direction is switched in order to operate the actuator (3). Even if the valve (4) is switched to the (4α) position or the (4C) position, the load pressure on the actuator (2) is significantly smaller than the load pressure on the actuator (3).
Pressure oil from the pump fi+ flows into one oil passage (1), (all oil passages I without flowing into lη).
（１０を経てアクチュエータ（２）の引側室（２ｈ）内
に流入する。(Flows into the pull side chamber (2h) of the actuator (2) through 10.
従って、従来はアクチュエータ（２）の自重落下が完了
した後に方向切換弁（４）を作動位置（４α）又は（４
Ｃ）に切り換えてアクチュエータ（３）を作動させてい
たためサイクルタイムが長くなるという問題があった。Therefore, conventionally, after the actuator (2) has completely dropped its own weight, the directional control valve (4) is moved to the operating position (4α) or (4α).
Since the actuator (3) was operated by switching to C), there was a problem in that the cycle time became long.
（問題点を解決するための手段）
本発明は上記問題に対処するため、アクチュエータ（２
）の自重落下時においてる他のアクチュエータ（３）を
同時に作動できるようにし、サイクルタイムが長くなる
のを防止しようとするものであって、その要旨とすると
ころは１のポンプから吐出された液体を複数のアクチュ
エータに並列に供給するように接続してなる液圧制御装
置において、上記ポンプから上記アクチュエータに至る
液体供給流路に介装され、このアクチュエータが自重落
下する場合にのみ上記液体供給流路を遮断するロジック
弁を具えることを特徴とする液圧制御装置にある。(Means for Solving the Problems) In order to solve the above problems, the present invention provides an actuator (2
) is designed to enable the other actuator (3) to operate simultaneously when the pump (3) falls due to its own weight, thereby preventing the cycle time from increasing. In a hydraulic control device connected to supply a plurality of actuators in parallel, the liquid supply flow is interposed in a liquid supply flow path from the pump to the actuator, and the liquid supply flow is controlled only when the actuator falls under its own weight. The present invention provides a hydraulic control device characterized by comprising a logic valve that shuts off a flow.
（実施例）
本発明の１実施例が第１図に示され、第１図において、
翰はロジック弁（至）は電磁弁、０υはシャトル弁であ
る。ロジック弁翰はポンプ（１）から７クチユエータ（
２）への圧油供給路に介装され、その入口ポート（２９
α）は油路Ｉに、出口ボー） （２９ｊ５）は油路（Ｉ
Ｆ５に、制御ポート（２９Ｃ）は電磁弁（至）の出力ポ
ート（３０Ｃ）に連通する油路（ト）にそれぞれ連結さ
れている。電磁弁間は常時スプリング（３０ｆ）によシ
図示の中立位置（３０α）に保持されているが、アクチ
ュエータ（２）の自重落下時には電気信号Ｃ３７）を受
けてンレノイ）” （３０ｇ）が励磁されて励磁位置（
３０ｈ）を占める。(Embodiment) An embodiment of the present invention is shown in FIG. 1, in which:
翰 is a logic valve (to) is a solenoid valve, 0υ is a shuttle valve. The logic valve is connected to the pump (1) to the 7 cutter (
2), and its inlet port (29
α) is connected to oil path I, exit bow) (29j5) is connected to oil path (I
At F5, the control port (29C) is connected to an oil path (G) that communicates with the output port (30C) of the solenoid valve (T). The space between the solenoid valves is always held at the neutral position (30α) shown in the figure by a spring (30f), but when the actuator (2) falls under its own weight, the electric signal C37) is energized. to the excitation position (
30h).
シャトル弁ｃ３１）の１方の入力ポート（３１α）は油
路Ｃ３２を介して油路（１６１に連通し、他方の入カポ
−） （３１ｊ）は油路（ハ）を介して油路Ｉに連通し
、出力ポート（３１Ｃ）は油路（ロ）を介して電磁弁（
至）Ｏ入カポ−） （３０ｇ）に連通している。電磁弁
（７）の他の入カポ−） （３ｔＭ）は油路檜を介して
油路Ｇ２に連通している。他の構成は第２図に示すもの
と同様であシ、対応する部材には同じ符号が付されてい
る。One input port (31α) of the shuttle valve c31) communicates with oil passage (161) via oil passage C32, and the other input port (31j) communicates with oil passage I via oil passage (c). The output port (31C) is connected to the solenoid valve (
(to) O-in capo) (30g). The other input port (3tM) of the solenoid valve (7) communicates with the oil passage G2 via the oil passage pipe. The rest of the structure is the same as that shown in FIG. 2, and corresponding members are given the same reference numerals.
しかして、アクチュエータ（２）が自重落下するとき、
即ち方向切換弁（５）が（５Ｃ）位置に切シ換えられた
状態でアクチュエータ（２）がこれに作用する外力又は
自重を受けて矢印方向に作動される場合には電気信号＜
３７）が電磁弁（至）のソレノイｌ” （３Ｑｙ）に供
給され電磁弁（７）は励磁位置（３０ｂ）を占める。す
ると、油路α褐又は（Ｌｅ内の圧油のうちいずれか高圧
の方がシャトル弁Ｇυで選択されて油路（ロ）、（至）
を経てロジック弁（イ）の制御ポー） （２９Ｃ）に導
入され、 ロジック弁のは油路α４）、ＣＩＦＧの圧力
の如何に拘らず閉とな）、油路Ｉと油路（Ｌｅとを遮断
する。この結果、ポンプ（１）からの圧油はアクチュエ
ータ（２）に供給されることはない。従って、アクチュ
エータ（２）が自重落下中においても方向切換弁（４）
を作動位置（４α）又は（４Ｃ）に切り換えればポンプ
（１）から吐出された圧油はアクチュエータ（２）に流
入せず全て方向切換弁（４）を経てアクチュエータ（３
）へ供給されアクチュエータ（３）が作動する。Therefore, when the actuator (2) falls under its own weight,
That is, when the actuator (2) is operated in the direction of the arrow by an external force acting on it or its own weight with the directional control valve (5) switched to the (5C) position, the electric signal <
37) is supplied to the solenoid l'' (3Qy) of the solenoid valve (to), and the solenoid valve (7) occupies the excitation position (30b).Then, the pressure oil in the oil path α brown or (Le), whichever is higher pressure is selected by the shuttle valve Gυ, and the oil path (B) and (to) are selected.
It is introduced into the control port (29C) of the logic valve (A) through the logic valve (A), which closes regardless of the pressure of CIFG, oil path α4), oil path I and oil path (Le). As a result, pressure oil from the pump (1) is not supplied to the actuator (2).Therefore, even when the actuator (2) is falling under its own weight, the directional control valve (4)
If the pump (1) is switched to the operating position (4α) or (4C), the pressure oil discharged from the pump (1) will not flow into the actuator (2), but will all flow through the directional control valve (4) to the actuator (3).
) and actuates the actuator (3).
アクチュエータ（２）の自重落下中、アクチュエータ（
２）の押側室（２α）から流出した油は油路ｔＬＢ、方
向制御弁（５）、油路罰、（財）、チェック弁（８）、
油路（ハ）。While the actuator (2) is falling due to its own weight, the actuator (
The oil flowing out from the push side chamber (2α) of 2) is sent to the oil passage tLB, the directional control valve (5), the oil passage tLB, the check valve (8),
Oil road (c).
α場をこの順に経てアクチュエータ（２）の引側室（２
ｂ）内に入るので、油路（１１内にバキュームが発生す
ることはない。なお、アクチュエータ（２）の押側室（
２（りと引側室（２ｈ）の面積差に伴う余剰油は油路（
５）、１２！１９、抵抗（ＬＤ、油路（イ）を経てタン
ク（Ｌ７Ｊに排出され、アクチュエータ（２）の引側室
（２ｈ）には抵抗αＤによって発生する背圧によシ自己
排出油が再生されることはない。The pull side chamber (2) of the actuator (2) passes through the α field in this order.
b), so no vacuum is generated in the oil passage (11).
2 (Excess oil due to the difference in area between the two side chambers (2h) is removed from the oil path (
5), 12!19, The oil is discharged to the tank (L7J) through the resistance (LD) and the oil path (A), and the oil is self-drained into the pull side chamber (2h) of the actuator (2) due to the back pressure generated by the resistance αD. is never played.
アクチュエータ（２）を押し上げ方向に作動させるとき
は方向制御弁（５）を（５α）位置に切り換える。この
際電気信号（９）は印加されず、電磁弁（７）は中立位
置（３０ｃＬ）に保持されている。この状態においてポ
ンプ（１）から吐出された油圧がアクチュエータ（２）
の負荷圧よシ高い場合、即ち油路Ｉ内の圧力が油路回内
の圧力よシ高いときは、ロジック弁四の制御ポート（２
９Ｃ）には油路αｅ内の油が油路■、Ｉ３５、電磁弁（
至）、油路弼を経て供給されるので、ロジック弁翰のホ
ハツ） Ｃ２９ｄ−”）は油路Ｉ内の圧油によって押圧
されスプリング（２９りに抗して右方に移動し、油路（
１４）と油路叫とが連通ずる。従って、ポンプ（１）か
ら吐出された圧油はロジック弁四を通ってアクチュエー
タ（２）の押側室（２α）内に流入してピストン（２Ｃ
）を押し上げる。When operating the actuator (2) in the upward direction, the direction control valve (5) is switched to the (5α) position. At this time, the electric signal (9) is not applied, and the solenoid valve (7) is held at the neutral position (30 cL). In this state, the hydraulic pressure discharged from the pump (1) is applied to the actuator (2).
When the load pressure is higher than the pressure in the oil passage I, that is, when the pressure inside the oil passage I is higher than the pressure inside the oil passage
9C), the oil in oil path αe is connected to oil path ■, I35, and solenoid valve (
Since it is supplied through the oil passage 2, the logic valve C29d-") is pressed by the pressure oil in the oil passage I and moves to the right against the force of the spring (29). (
14) and the oil road cry are connected. Therefore, the pressure oil discharged from the pump (1) passes through the logic valve 4, flows into the push side chamber (2α) of the actuator (2), and flows into the piston (2C).
) to push up.
上記操作部ち、方向切換弁（５）を（５α）位置に切シ
換えた状態において、アクチュエータ（２）の負荷圧が
ポンプ（１）の吐出圧よ勺高いとき即ち油路（Ｌｅ内の
圧力が油路Ｉ内の圧力よシ大きいときにもロジック弁四
の制御ポート（２９Ｃ）には油路（ＬＤ内の圧力が導か
れているため、ロジック弁翰のポベツ） （２９ｄ）は
閉止状態となり、油路（１６Ｉから油路（１４）へ油の
逆流を阻止し、ロジック弁翰は第２図に示す負荷保持チ
ェック弁（６）の機能を果す。When the load pressure of the actuator (2) is much higher than the discharge pressure of the pump (1), when the directional control valve (5) is switched to the (5α) position, that is, the pressure in the oil passage (Le) is Even when the pressure is greater than the pressure in oil passage I, the oil passage (29d) is closed because the pressure in LD is guided to the control port (29C) of logic valve 4. This prevents oil from flowing backward from the oil passage (16I) to the oil passage (14), and the logic valve handle functions as the load holding check valve (6) shown in FIG.
アクチュエータ（２）を自重落下でなくポンプ（１）か
らの吐出圧を導いて強制的に降下させるときけ方向切換
弁（５）を（５Ｃ）位置に切シ換えるが、この場合には
電気信号Ｃ３７）が電磁弁（７）Ｋ印加されないので、
電磁弁−は（３０α）位置に保持されたままとなる。従
って、ロジック弁艷の制御ポート（２９Ｃ）には油路（
Ｌｅ内の圧力が導かれているので、ロジック弁翰のポペ
ット（２９ｃＬ）は油路Ｉ内の圧油に押圧されて開とな
シ、ポンプ（１）からの圧油はロジック弁■を通ってア
クチュエータ（２）の引側室（２９ｂ）に供給され、ピ
ストン（２Ｃ）を降下させる。When the actuator (2) is forcibly lowered by guiding the discharge pressure from the pump (1) instead of dropping by its own weight, the directional control valve (5) is switched to the (5C) position. Since K37) is not applied to solenoid valve (7),
The solenoid valve remains held at the (30α) position. Therefore, the control port (29C) of the logic valve has an oil passage (
Since the pressure in Le is guided, the poppet (29 cL) of the logic valve is pushed open by the pressure oil in the oil passage I, and the pressure oil from the pump (1) passes through the logic valve ■. is supplied to the pull-side chamber (29b) of the actuator (2), and lowers the piston (2C).
かくして、方向切換弁（５）の操作位置と、油路帖内の
圧力とを検出することによシアクチュエータ（２）を自
重落下させるときにのみ電気信号Ｇηを印加し、それ以
外のときは電気信号（９）が印加されないようにし、油
路α荀又はαｅのいずれか高い方の圧油をロジック弁翰
の制御ボー） （２９Ｃ）に導くことによって、アクチ
ュエータ（２）が自重落下する場合にのみ油路（Ｉ４）
又はａｅ内の圧力の如何を問わずロジック弁四を閉とし
、油路Ｉと（ｌｅとの連通を遮断できる。Thus, by detecting the operating position of the directional control valve (5) and the pressure in the oil passage, the electric signal Gη is applied only when the shear actuator (2) is allowed to fall under its own weight, and at other times. When the actuator (2) falls under its own weight by preventing the electric signal (9) from being applied and guiding the pressure oil from the oil passage αx or αe, whichever is higher, to the logic valve control valve (29C). Ninomiya Oilway (I4)
Alternatively, logic valve 4 can be closed regardless of the pressure in ae, and communication between oil path I and (le) can be cut off.
（発明の作用及び効果）
以上実施例について具体的に説明したように、本発明に
おいては１のポンプから吐出された液体を複数のアクチ
ュエータに並列に供給するように接続してなる液圧制御
装置において、上記ポンプから上記アクチュエータに至
る液体供給流路に介装され、このアクチュエータが自重
落下する場合にのみ上記液体供給流路を遮断するロジッ
ク弁を具えているので、当該アクチュエータが自重落下
中においても他のアクチュエータにポンプから吐出され
た圧油を供給してこれを同時に作動させることが可能と
なシ、この液圧制御装置のサイクルタイムを短縮できる
。(Operations and Effects of the Invention) As described above in detail with respect to the embodiments, the present invention provides a hydraulic control device in which the liquid discharged from one pump is connected to a plurality of actuators in parallel. The device is equipped with a logic valve that is interposed in the liquid supply flow path from the pump to the actuator and shuts off the liquid supply flow path only when the actuator falls under its own weight. It is also possible to supply pressure oil discharged from the pump to other actuators and operate them simultaneously, thereby shortening the cycle time of this hydraulic pressure control device.
なお、図示のようにロジック弁翰の下流側即ち油路（ｌ
Ｅ９内の油を制御ポー） （２９Ｃ）に導くことによシ
、このロジック弁翰に負荷保持チェック弁の機能を伴せ
奏させることができるので、液圧制御装置のサイズ、重
量、コスト上昇を最少限にとどめることが可能となる。In addition, as shown in the figure, the downstream side of the logic valve
By guiding the oil in E9 to the control port (29C), this logic valve can perform the function of a load holding check valve, thereby reducing the size, weight, and cost of the hydraulic control device. can be kept to a minimum.
第１図は本発明の１実施例を示す油圧回路図、第２図は
従来の液圧制御装置の１例を示す油圧回路図である。
ポンプ・・・（１）、アクチュエータ・・・（２１ｊ３
１、ロジック弁・・・翰FIG. 1 is a hydraulic circuit diagram showing an embodiment of the present invention, and FIG. 2 is a hydraulic circuit diagram showing an example of a conventional hydraulic pressure control device. Pump...(1), Actuator...(21j3
1. Logic valve...Kan
Claims (1)
タに並列に供給するように接続してなる液圧制御装置に
おいて、上記ポンプから上記アクチユエータに至る液体
供給流路に介装され、このアクチユエータが自重落下す
る場合にのみ上記液体供給流路を遮断するロジツク弁を
具えることを特徴とする液圧制御装置。In a hydraulic pressure control device that is connected to supply liquid discharged from one pump to a plurality of actuators in parallel, the actuator is installed in a liquid supply flow path from the pump to the actuator, and the actuator is prevented from falling under its own weight. A hydraulic control device comprising a logic valve that shuts off the liquid supply flow path only when the liquid supply flow path is performed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23666984A JPS61116104A (en) | 1984-11-12 | 1984-11-12 | Hydraulic controller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23666984A JPS61116104A (en) | 1984-11-12 | 1984-11-12 | Hydraulic controller |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS61116104A true JPS61116104A (en) | 1986-06-03 |
Family
ID=17004028
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23666984A Pending JPS61116104A (en) | 1984-11-12 | 1984-11-12 | Hydraulic controller |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61116104A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001208008A (en) * | 1999-12-15 | 2001-08-03 | Caterpillar Inc | Hydraulic circuit having pressure equalization during regeneration |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5549112B2 (en) * | 1977-04-28 | 1980-12-10 |
-
1984
- 1984-11-12 JP JP23666984A patent/JPS61116104A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5549112B2 (en) * | 1977-04-28 | 1980-12-10 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001208008A (en) * | 1999-12-15 | 2001-08-03 | Caterpillar Inc | Hydraulic circuit having pressure equalization during regeneration |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4020867A (en) | Multiple pressure compensated flow control valve device of parallel connection used with fixed displacement pump | |
| US3874269A (en) | Hydraulic actuator controls | |
| JPH09268604A (en) | Flow combining device for full equipment | |
| CN105909588B (en) | The oil pressure actuated systems of unloading valve and hydraulic excavator | |
| US4153075A (en) | Load responsive control valve | |
| JPH1061603A (en) | Control system for separating and relaxing inductive load | |
| US4080994A (en) | Control arrangement for supplying pressure fluid to at least two hydraulically operated consumer devices | |
| JPS61116104A (en) | Hydraulic controller | |
| JPH01501650A (en) | load compensation valve | |
| EP0314704A1 (en) | Load responsive system using load responsive pump control of a bypass type | |
| JP2015209932A (en) | Pilot type flow control valve | |
| CN106246550A (en) | Control device, control method and the compressor of a kind of guiding valve | |
| JP3538466B2 (en) | Main steam stop valve switchgear | |
| US2953163A (en) | Self-clearing valve | |
| KR100225979B1 (en) | Apparatus for combining the inner flow in hydraulic equipment having two sets of hydraulic circuits | |
| CN218581932U (en) | Pilot pressure reducing valve group, hydraulic system and operation machine | |
| US2540183A (en) | Balanced poppet valving system | |
| JP3558862B2 (en) | Hydraulic system | |
| US3319422A (en) | Speed governing systems for steam turbines | |
| JPH08254201A (en) | Control device for plurality of actuators | |
| KR200350674Y1 (en) | Load Limit and Metering Manifold of Servo Actuator for Airframe Structural Test | |
| JPS59121202A (en) | Fluid pressure device | |
| KR20050065944A (en) | Load limit and metering manifold of servo actuator for airframe structural test | |
| SU1479718A1 (en) | Hydraulic drive for mounted machine | |
| JPH10252706A (en) | Hydraulic control circuit |