JPS61116105A - Hydraulic device for actuator - Google Patents
Hydraulic device for actuatorInfo
- Publication number
- JPS61116105A JPS61116105A JP23667184A JP23667184A JPS61116105A JP S61116105 A JPS61116105 A JP S61116105A JP 23667184 A JP23667184 A JP 23667184A JP 23667184 A JP23667184 A JP 23667184A JP S61116105 A JPS61116105 A JP S61116105A
- Authority
- JP
- Japan
- Prior art keywords
- actuator
- oil
- oil passage
- 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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
-
- 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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
-
- 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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
-
- 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
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
-
- 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
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/321—Directional control characterised by the type of actuation mechanically
- F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
-
- 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
- F15B2211/30—Directional control
- F15B2211/35—Directional control combined with flow control
-
- 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
- F15B2211/30—Directional control
- F15B2211/35—Directional control combined with flow control
- F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
-
- 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
- F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
-
- 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
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7053—Double-acting output members
-
- 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
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7058—Rotary output members
-
- 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
-
- 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
- F15B2211/78—Control of multiple output members
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は油圧ポンプを出て分流した圧油を制御弁を経て
複数のアクチエータヘ送って同各アクチェータを作動す
しアクチェータ用油圧装置の改良に関するものである。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to an improvement in a hydraulic system for actuators by sending pressure oil separated from a hydraulic pump to a plurality of actuators via a control valve to operate each actuator. It is.
（従来の技術）
従来の１個の油圧ポンプで複数のアクチェータを作動す
るアクチェータ用油圧装置を第２図により説明すると、
（１）が油圧ポンプ、 （２） （３）がアクチェータ
、 （４） （５）が方向制御弁、 （６） （７）
（８）がチェック弁、 （９） （１０）がリリーフ弁
、 （１１）が抵抗、 （１２）がタンク、 （１３）
（１４） （１５） （１６） （１７） （’１８
） （１９） （２０） （２１） （２２） （２３
） （２４） （２５） （２６） （２７） （２８
）が油路で、方向制御弁（４）を（４ａ）位置（または
（４ｃ）位置）に切り換えることにより、油圧ポンプ（
１）の圧油を油路（１３）−油路（１５）−油路（１７
）−油路（２０）−アクチェータ（３）−油路（２１）
−油路（２７）−油路（２５）−油路（２６）（方向制
御弁（４）が（４ｃ）位置のときは、油路（２１）−ア
クチェータ（３）−油路（２０）以外同じ）へ導いて、
アクチェータ（３）を作動させる。また方向制御弁（５
）を（５ａ）位置（または（５ｃ）位置）に切り換える
ことにより、油圧ポンプ（１）の圧油を油路（１３）→
油路（１４）−油路（１６）−油路（１８）−アクチェ
ータ（２）−油路（１９）−油路（２７）−油路（２５
）−油路（２６） （方向制御弁（５）が（５ｃ）位置
のときは、油路（］９）−アクチェータ（２）−油路（
１８）以外同じ）へ導いて、アクチェータ（２）を作動
させる。またアクチェータ（２） （３）をともに作動
させていて、アクチェータ（２）の負荷〉アクチェータ
（３）の負荷になったとき、チェック弁（６）は、アク
チェータ（２）からの排油が油路（１８）−油路（１６
）→油路（１４）−油路（１５）−油路り１７）−アク
チェータ（３）へと流通するのを防止する。またリリー
フ弁（９） （１０）は、アクチェータ（２）に外力が
作用したとき、油路（１Ｂ） （１９）に発生する異常
高圧を吸収して、油圧回路を保護する。またチェック弁
（７） （８）は、油路（１８） （１９）に負圧が生
じたとき、タンク（１２）から油を補給して、負圧を解
消する。また抵抗（１１）は１作動油が油路（２５）−
油路（２６）−タンク（１２）へ戻るときのフィルタ・
ターラ（図示せず）等の抵抗である。(Prior Art) A conventional actuator hydraulic system that operates multiple actuators with one hydraulic pump will be explained with reference to FIG.
(1) is a hydraulic pump, (2) (3) is an actuator, (4) (5) is a directional control valve, (6) (7)
(8) is a check valve, (9) (10) is a relief valve, (11) is a resistor, (12) is a tank, (13)
(14) (15) (16) (17) ('18
) (19) (20) (21) (22) (23
) (24) (25) (26) (27) (28
) is the oil path, and by switching the directional control valve (4) to the (4a) position (or (4c) position), the hydraulic pump (
The pressure oil of 1) is transferred from oil passage (13) to oil passage (15) to oil passage (17).
) - Oil passage (20) - Actuator (3) - Oil passage (21)
- Oil passage (27) - Oil passage (25) - Oil passage (26) (When the directional control valve (4) is in the (4c) position, the oil passage (21) - Actuator (3) - Oil passage (20) Same as above)
Activate the actuator (3). Also, the direction control valve (5
) to the (5a) position (or (5c) position), the pressure oil of the hydraulic pump (1) is transferred from the oil path (13) to
Oil passage (14) - Oil passage (16) - Oil passage (18) - Actuator (2) - Oil passage (19) - Oil passage (27) - Oil passage (25
) - Oil passage (26) (When the directional control valve (5) is in the (5c) position, the oil passage (] 9) - Actuator (2) - Oil passage (
18)) to operate the actuator (2). In addition, when both actuators (2) and (3) are operated and the load on actuator (2) is greater than the load on actuator (3), the check valve (6) detects the drained oil from actuator (2). Road (18) - Oil road (16
)→Oil passage (14) - Oil passage (15) - Oil passage 17) - Prevents the flow from flowing to the actuator (3). Furthermore, the relief valves (9) (10) protect the hydraulic circuit by absorbing abnormal high pressure generated in the oil passage (1B) (19) when an external force acts on the actuator (2). Furthermore, when negative pressure is generated in the oil passages (18) and (19), the check valves (7) and (8) replenish oil from the tank (12) to eliminate the negative pressure. In addition, the resistance (11) is connected to the oil path (25) -
Oil line (26) - Filter when returning to tank (12)
This is a resistance such as a tala (not shown).
（発明が解決しようとする問題点）
前記第２図のアクチェータ用油圧装置では、アクチェー
タ（２）を矢印の方向（外力による強制降下方向または
自重降下方向）へ作動させ且つアクチェータ（３）を重
負荷で連動しないときに、アクチェータ（３）が作動し
ないという欠点があった。(Problems to be Solved by the Invention) In the actuator hydraulic system shown in FIG. There was a drawback that the actuator (3) did not operate when it was not interlocked with the load.
以下、矢印の方向を判り易くするために、自重降下の例
で上記欠点を詳しく説明する。アクチェータ（２）を自
重降下方向へ作動させるために、方向制御弁（５）を（
５Ｃ）位置に切り換えると、アクチェータ（２）のヘッ
ド側からの排油が油路（１８）−油路（２８）→油路（
２５）→油路（２６）→タンクは２）へ流れる。一方、
アクチェータ（２）のロンド側には、油圧ポンプ（１）
からの圧油が油路（１３）−油路（１４）−油路（１６
）→油路（１９）を経て流入する。このとき、アクチェ
ータ（３）を同時に連動させるために、方向制御弁（４
）を切り換えると、油圧ポンプ（１）からの圧油がアク
チェータ（２） （３）の系統に流れようとするが、ア
クチェータ（２）は、自重降下のため。Hereinafter, in order to make it easier to understand the direction of the arrow, the above drawbacks will be explained in detail using an example of dead weight descent. In order to operate the actuator (2) in the self-weight downward direction, the directional control valve (5) is
5C), the drained oil from the head side of the actuator (2) flows from oil path (18) to oil path (28) to oil path (
25) → oil path (26) → tank flows to 2). on the other hand,
A hydraulic pump (1) is installed on the rond side of the actuator (2).
The pressure oil from the oil passage (13) - oil passage (14) - oil passage (16
)→Flows in through the oil passage (19). At this time, in order to simultaneously interlock the actuator (3), the directional control valve (4
), the pressure oil from the hydraulic pump (1) tries to flow to the actuator (2) and (3) system, but the actuator (2) is lowered due to its own weight.
負荷圧力が低くて、油圧ポンプ（１）からの圧油の全量
がアクチェータ（２）のロンド側のみに流入し、アクチ
ェータ（３）には１作動油が行き渡らなくて、アクチェ
ータ（３）が作動しない。即ち、アクチェータ（２）の
自重降下時には、アクチェータ（２）（３）を連動させ
ることができない。このようなときには、アクチェータ
（２） （３）の連動を諦めて、アクチェータ（２）の
自重降下完了後にアクチェータ（３）を単独で作動させ
なければならなくて、サイクルタイムが長くなるという
問題があった。When the load pressure is low, the entire amount of pressure oil from the hydraulic pump (1) flows only into the rond side of the actuator (2), and the hydraulic oil does not reach the actuator (3), causing the actuator (3) to operate. do not. That is, when the actuator (2) is lowered by its own weight, the actuators (2) and (3) cannot be interlocked. In such a case, the interlocking of actuators (2) and (3) must be given up and actuator (3) must be operated independently after the actuator (2) has completed its own weight descent, resulting in a longer cycle time. there were.
（問題点を解決するための手段）
本発明は前記の問題点に対処するもので、油圧ポンプを
出て分流した圧油を制御弁を経て複数のアクチエータヘ
送って同各アクチェータを作動するアクチェータ用油圧
装置において、前記各アクチェータのうち一方のアクチ
ェータに圧油を給排する第１．第２の油路と、同第１．
第２の油路を短絡する第３の油路と、同第３の油路に設
けられて開弁時に同第１．第２の油路を接続するロジッ
ク弁とを具えていることを特徴としたアクチェータ用油
圧装置に係わり、その目的とする処は、一方のアクチェ
ータの自重降下と他方のアクチェータの作動とを同時に
行うことができて、サイクルタイムを短縮できる改良さ
れたアクチェータ用油圧装置を供する点にある。(Means for Solving the Problems) The present invention addresses the above-mentioned problems, and is intended for use in an actuator that operates a plurality of actuators by sending pressure oil separated from a hydraulic pump to a plurality of actuators via a control valve. In the hydraulic system, the first actuator supplies and discharges pressure oil to one of the actuators. The second oil passage and the first oil passage.
A third oil passage that short-circuits the second oil passage, and a third oil passage that is provided in the third oil passage and that connects the first oil passage when the valve is opened. A hydraulic system for an actuator characterized by comprising a logic valve connecting a second oil passage, the purpose of which is to simultaneously lower the dead weight of one actuator and operate the other actuator. An object of the present invention is to provide an improved hydraulic system for an actuator that can reduce cycle time.
（実施例）
次に本発明のアクチェータ用油圧装置を第１図に示す一
実施例により説明すると、（１）が油圧ポンプ、 （２
） （３）がアクチェータ、 （４） （５）が方向制
御弁、 （６） （７） （８）がチェック弁、 （９
） （１０）がリリーフ弁、 （１１）が抵抗、 （１
２）がタンク、 （１３） （１４） （１５） （１
６） （２８）が油路、 （２９）がロジック弁、（２
９ａ）が同ロジック弁（２９）のシート部、 （２９ｂ
）が同ロジック弁（２９）のポペット（２９ｃ）が同ロ
ジック弁（２９）のスプリング、 （２９ｄ）が同ロジ
ック弁（２９）の絞り付油路、 （２９ｅ） （２９ｆ
）が同ロジック弁（２９）の油室、 （３０）が方向切
換弁、 （３０ａ）が同方向切換弁（３０）の切換位置
、 （３０ｂ）が同方向切換弁（３０）の中立位置、
（３１）が電磁式パイロット弁、 （３１ａ）が同電磁
式パイロット弁（３１）の切換位置、 （３１ｂ）が同
電磁式パイロット弁（３１）の中立位置、 （３２）
（３３） （３４） （３５） （３６） （３７）が
油路、 （３８） （３９）がスプリング、 （４０）
がソレノイド、 （４１）が電気信号ラインで、（５ａ
’）及び（５ｃ’）は方向制御弁（５）の切換過渡状態
を示している。(Example) Next, the actuator hydraulic system of the present invention will be explained using an example shown in FIG. 1. (1) is a hydraulic pump, (2)
) (3) is the actuator, (4) (5) is the directional control valve, (6) (7) (8) is the check valve, (9
) (10) is the relief valve, (11) is the resistance, (1
2) is the tank, (13) (14) (15) (1
6) (28) is the oil path, (29) is the logic valve, (2
9a) is the seat part of the logic valve (29), (29b)
) is the poppet (29c) of the logic valve (29) is the spring of the logic valve (29), (29d) is the oil passage with throttle of the logic valve (29), (29e) (29f)
) is the oil chamber of the logic valve (29), (30) is the directional switching valve, (30a) is the switching position of the same directional switching valve (30), (30b) is the neutral position of the same directional switching valve (30),
(31) is the electromagnetic pilot valve, (31a) is the switching position of the electromagnetic pilot valve (31), (31b) is the neutral position of the electromagnetic pilot valve (31), (32)
(33) (34) (35) (36) (37) is oil passage, (38) (39) is spring, (40)
is the solenoid, (41) is the electric signal line, and (5a
') and (5c') show switching transient states of the directional control valve (5).
（作用）
次に前記第１図のアクチェータ用油圧装置の作用を説明
する。アクチェータ（２）を自重降下方向に作動させる
とき、方向制御弁（５）を（５ｃ“）位置に切り換える
。油圧ポンプ（１）からの圧油は、油路（１９）からア
クチェータ（２）に流入せず、油路（１３）−油路（１
５）−油路（１７）−油路（２８）−油路（２５） −
油路（２６）−タンク（１２）へ流れて、アンロードさ
れたままの状態になる。アクチェータ（２）のヘッド側
からの排油は、油路（１８）一方向制御弁（５）の（５
Ｃ“）の絞り部→油路（２７）−油路（２５）→油路（
２６） −タンク（１２）へ導かれる。このとき、アク
チェータ（２）のロッド側には９作動油が流入しなけれ
ばならないが、油圧ポンプ（１）からの圧油は前述のよ
うにアクチェータ（２）に流入しない。このとき。(Function) Next, the function of the actuator hydraulic system shown in FIG. 1 will be explained. When operating the actuator (2) in the direction of lowering its own weight, the direction control valve (5) is switched to the (5c'') position. Pressure oil from the hydraulic pump (1) is transferred from the oil path (19) to the actuator (2). No inflow, oil passage (13) - oil passage (1
5) - Oil passage (17) - Oil passage (28) - Oil passage (25) -
The oil flows from the oil path (26) to the tank (12) and remains unloaded. Drained oil from the head side of the actuator (2) is drained through the oil passage (18) and the one-way control valve (5) (5).
C") throttle part → oil passage (27) - oil passage (25) → oil passage (
26) - led to tank (12). At this time, the hydraulic oil must flow into the rod side of the actuator (2), but the pressure oil from the hydraulic pump (1) does not flow into the actuator (2) as described above. At this time.
ロジック弁（２９）の方向切換弁（３０）及び電磁式パ
イロット弁（３１）の状態は、方向切換弁（３０）につ
いては、油路（１９） （３２） （３４）の圧力が低
いため、スプリング（３８）により（３０ｂ）の位置に
あって、油路（３５）（３６）が接続していない。一方
、電磁式パイロット弁（３１）については、アクチェー
タ（２）が自重降下である旨の電気信号を信号ライン（
４１）を介し受けて、ソレノイド（４０）が励磁される
。そのため、電磁式パイロット弁（３１）がスプリング
（３９）に抗しく３１ａ）の位置に切り替わり、油路（
３６） （３７）が接続する。なお電磁式パイロット弁
（３１）は１油路（１８）の圧力〉油路（１９）の圧力
で、アクチェータ（２）が縮み方向に作動しているとき
にだけ電気信号が入って、方向切換弁（３０）が切り替
わる。従ってロジック弁（２９）は、油室（２９ｃ）が
油路（３５） （３６） （３７）を介しタンク（１２
）に接続して低圧になるため、油室（２９ｅ）に作用す
る油路（１８） （３３）の圧力の方が勝って、ポペッ
ト（２９ｂ）をスプリング（２９ｃ）に抗して押し開く
。そのため、アクチェータ（２）のロッド側には、ヘッ
ド側からの排油が油路（１８）−油路（３３）−油路（
３２）−油路（１９）を経て流入する。即ち、アクチェ
ータ（２）の自己排油がロッド側に再生される。このよ
うにアクチェータ（２）の自己排油がロッド側に再生さ
れる結果、油路（１９）に所定圧力以上の圧力が発生し
、その圧力が油路（３２） （３４）を経て方向切換弁
（３０）をスプリング（３８）に抗して切り換え、 （
３０ａ）の位置になって、油路（３５）と油路（３６）
、とを遮断する。方向切換弁（３ｏ）により、油路（３
５）と油路（３６）とが遮断されると、油室（２９ｆ）
の圧力が油室（２９ｅ）の圧力の圧力と等しくなり、ボ
ベッ１− （２９ｂ）がスプリング（２９ｃ）により戻
されて、シート部（２９ａ）が着座する。即ち、油路（
３３） （３２）が遮断され、油路（１９）の圧力が所
定圧力以上になると、再生回路が遮断状態になり、油路
（１９）の圧力が過大に上昇するのが防止される。この
ようにロジック弁（２９）は、適当に開度を調整しなが
ら、アクチェータ（２）のロッド側が負圧にならず且つ
異常に高圧にならないように再生流量を調整する作用を
もっている。アクチェータ（２）を油圧ポンプ（１）の
吐出油により強制降下させる場合は、方向制御弁（５）
を（５ｃ）の位置に切り換える。このとき、電磁式パイ
ロット弁（３１）には、電気信号が入らず、ソレノイド
（４０）は励磁されていないため、（３１ｂ）の位置に
あり 油路（３６） （３７）は遮断状態になるので、
ロジック弁（２９）は閉じたままである。アクチェータ
（２）を上昇させるときは、方向制御弁（５） ヲ（５
ａ’）または（５ａ）の位置に切り換える。このとき、
油圧ポンプ（１）の吐出油は、油路（１３）−油路（１
４）−油路（１６）−油路（１８）へ流れて、アクチェ
ータ（２）のロッド側へ流入する。一方、アクチェータ
（２）の排油は、油路（１９）−油路（２７）−油路（
２５）−油路（２６）−タンク（１２）へ戻る。このと
きには、ロジック弁（２９）に電気信号が入らず、同ロ
ジック弁（２９）は閉じたままで、何等の作用もしない
。The state of the directional control valve (30) and the electromagnetic pilot valve (31) of the logic valve (29) is as follows: It is in the position (30b) due to the spring (38), and the oil passages (35) and (36) are not connected. On the other hand, regarding the electromagnetic pilot valve (31), an electric signal indicating that the actuator (2) is lowering due to its own weight is sent to the signal line (
41), the solenoid (40) is energized. Therefore, the electromagnetic pilot valve (31) resists the spring (39) and switches to the position 31a), causing the oil passage (
36) (37) connects. In addition, the electromagnetic pilot valve (31) receives an electric signal only when the actuator (2) is operating in the retraction direction at the pressure of the oil passage (18) > the pressure of the oil passage (19), and the direction is changed. The valve (30) is switched. Therefore, in the logic valve (29), the oil chamber (29c) is connected to the tank (12) through the oil passages (35) (36) (37).
), the pressure in the oil passages (18) and (33) acting on the oil chamber (29e) prevails, pushing the poppet (29b) open against the spring (29c). Therefore, on the rod side of the actuator (2), drained oil from the head side flows from oil path (18) to oil path (33) to oil path (
32) - enters via oil channel (19); That is, the self-drained oil of the actuator (2) is recycled to the rod side. As a result of the self-drained oil of the actuator (2) being regenerated to the rod side in this way, a pressure higher than a predetermined pressure is generated in the oil passage (19), and this pressure passes through the oil passages (32) and (34) to switch the direction. Switch the valve (30) against the spring (38) and (
30a) and connect the oil passage (35) and oil passage (36).
, and cut off. The directional control valve (3o) allows the oil passage (3
5) and the oil passage (36) are blocked, the oil chamber (29f)
The pressure in the oil chamber (29e) becomes equal to the pressure in the oil chamber (29e), the bobber (29b) is returned by the spring (29c), and the seat part (29a) is seated. In other words, the oil passage (
33) When (32) is shut off and the pressure in the oil passage (19) becomes equal to or higher than a predetermined pressure, the regeneration circuit is shut off and the pressure in the oil passage (19) is prevented from increasing excessively. In this way, the logic valve (29) has the function of adjusting the regeneration flow rate so that the rod side of the actuator (2) does not become negative pressure or abnormally high pressure while appropriately adjusting the opening degree. When the actuator (2) is forcibly lowered by the oil discharged from the hydraulic pump (1), use the directional control valve (5).
switch to position (5c). At this time, the electromagnetic pilot valve (31) receives no electric signal and the solenoid (40) is not energized, so it is in the position (31b) and the oil passages (36) and (37) are in a blocked state. So,
Logic valve (29) remains closed. When raising the actuator (2), open the directional control valve (5)
a') or (5a). At this time,
The oil discharged from the hydraulic pump (1) is routed between oil passage (13) and oil passage (1).
4) - Oil passage (16) - Flows into the oil passage (18) and flows into the rod side of the actuator (2). On the other hand, the drain oil from the actuator (2) is drained from oil passage (19) - oil passage (27) - oil passage (
25) - Oil passage (26) - Return to tank (12). At this time, no electric signal is applied to the logic valve (29), and the logic valve (29) remains closed and does not perform any action.
アクチェータ（２）の自重降下とアクチェータ（３）の
作動とをともに行う場合、上述のように油圧ポンプ（１
）の吐出油は、アクチェータ（２）に費やされることが
なくて、アクチェータ（３）を作動させることができる
。またアクチェータ（２）が自重降下するとき、従来例
では、アクチェータ（２）のロッド側油路（１９）が負
圧になりがちであったが、油をタンク（１２）からチェ
ック弁（８）を経てアクチェータ（２）のロッド側油路
（１９）へ吸入するので、アクチェータ（２）のロッド
側油路（１９）が負圧になるのが防止される。しがしこ
の従来の負圧防止対策は消極的であり、アクチェータ（
２）の降下速度が早い場合には、大量の油を補給する必
要がある。When lowering the dead weight of the actuator (2) and operating the actuator (3), the hydraulic pump (1) is used as described above.
) can operate the actuator (3) without being wasted on the actuator (2). In addition, when the actuator (2) falls under its own weight, in the conventional example, the rod side oil passage (19) of the actuator (2) tends to have negative pressure, but oil is removed from the tank (12) by the check valve (8). Since the pressure is drawn into the rod-side oil passage (19) of the actuator (2) through the air, the rod-side oil passage (19) of the actuator (2) is prevented from becoming negative pressure. However, conventional negative pressure prevention measures are passive, and the actuator (
If the descent speed in 2) is fast, it is necessary to replenish a large amount of oil.
通常、チェック弁（８）の容量は、充分でなく、往々に
してアクチェータ（２）のロンド側油路（１９）に負圧
が発生する。ところが本油圧装置の場合には、ロジック
弁（２９）により、積極的に再生するので、アクチェー
タ（２）のロンド側油路（工９）に負圧が発生しない。Normally, the capacity of the check valve (8) is not sufficient, and negative pressure often occurs in the rond side oil passage (19) of the actuator (2). However, in the case of this hydraulic system, since the logic valve (29) actively regenerates, negative pressure is not generated in the rond side oil passage (engine 9) of the actuator (2).
なお方向制御弁（３０）及び電磁式パイロット弁（３１
）は説明を判りやす（するために付加したにすぎず、同
じ機能を有するものであれば。In addition, the directional control valve (30) and the electromagnetic pilot valve (31)
) is just added to make the explanation easier to understand, as long as it has the same function.
他の機器に換えても差支えない。また方向制御弁（５）
の構成も図示の例に限定されない。There is no problem in replacing it with another device. Also directional control valve (5)
The configuration is also not limited to the illustrated example.
（発明の効果）
本発明のアクチェータ用油圧装置は前記のように油圧ポ
ンプを出て分流した圧油を制御弁を経て複数のアクチエ
ータヘ送って同各アクチェータを作動するアクチェータ
用油圧装置において、前記各アクチェータのうち一方の
アクチェータに圧油を給排する第１．第２の油路と、同
第１．第２の油路を短絡する第３の油路と、同第３の油
路に設けられて開弁時に同第１．第２の油路を接続する
ロジック弁とを具えており、一方のアクチェータ（前記
実施例では（２））を自重降下させるとき、油圧ポンプ
からの圧油を使用せず１ これを他方のアクチェータ（
前記実施例では（３））に回すことができ、一方のアク
チェータの自重降下と他方のアクチェータの作動とを同
時に行うことができて、サイクルタイムを短縮できる効
果がある。(Effects of the Invention) The actuator hydraulic system of the present invention is an actuator hydraulic system that sends pressure oil branched from the hydraulic pump to a plurality of actuators via a control valve to operate each of the actuators. A first step for supplying and discharging pressure oil to one of the actuators. The second oil passage and the first oil passage. A third oil passage that short-circuits the second oil passage, and a third oil passage that is provided in the third oil passage and that connects the first oil passage when the valve is opened. When lowering one actuator ((2) in the above embodiment) by its own weight, it is connected to the other actuator without using pressure oil from the hydraulic pump. (
In the embodiment described above, it is possible to turn to (3)), and the dead weight lowering of one actuator and the operation of the other actuator can be performed simultaneously, which has the effect of shortening the cycle time.
以上本発明を実施例ついて説明したが、勿論本発明はこ
のような実施例にだけ局限されるものではなく２本発明
の精神を逸脱しない範囲で種々の設計の改変を施しうる
ちのである。Although the present invention has been described above with reference to embodiments, it goes without saying that the present invention is not limited to these embodiments, and can be modified in various ways without departing from the spirit of the present invention.
第１図は本発明に係わるアクチェータ用油圧装置の一実
施例を示す油圧回路図、第２図は従来のアクチェータ用
油圧装置を示す油圧回路図である（１）・・・油圧ポン
プ、 （２） （３） ・・・アクチェータ、 （４
） （５） ・・・制御弁、 （１８） （１９）
・・・第１゜第２の油路、 （２９）・・・ロジック
弁、 （３２Ｘ３３）・・・第３の油路。Fig. 1 is a hydraulic circuit diagram showing an embodiment of the actuator hydraulic system according to the present invention, and Fig. 2 is a hydraulic circuit diagram showing a conventional actuator hydraulic system (1)...Hydraulic pump, (2) ) (3) ...actuator, (4
) (5) ...control valve, (18) (19)
...1st degree second oil passage, (29)...logic valve, (32X33)...third oil passage.
Claims (1)
クチエータヘ送って同各アクチエータを作動するアクチ
エータ用油圧装置において，前記各アクチエータのうち
一方のアクチエータに圧油を給排する第１，第２の油路
と，同第１，第２の油路を短絡する第３の油路と，同第
３の油路に設けられて開弁時に同第１，第２の油路を接
続するロジック弁とを具えていることを特徴としたアク
チエータ用油圧装置。In an actuator hydraulic system that sends pressure oil separated from a hydraulic pump to a plurality of actuators via a control valve to operate each of the actuators, a first and a first actuator supply and discharge pressure oil to one of the actuators. a third oil passage that short-circuits the first and second oil passages; and a third oil passage that is provided in the third oil passage and connects the first and second oil passages when the valve is opened. A hydraulic device for an actuator characterized by comprising a logic valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23667184A JPS61116105A (en) | 1984-11-12 | 1984-11-12 | Hydraulic device for actuator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23667184A JPS61116105A (en) | 1984-11-12 | 1984-11-12 | Hydraulic device for actuator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS61116105A true JPS61116105A (en) | 1986-06-03 |
Family
ID=17004055
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23667184A Pending JPS61116105A (en) | 1984-11-12 | 1984-11-12 | Hydraulic device for actuator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61116105A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6319402A (en) * | 1986-07-08 | 1988-01-27 | Hitachi Constr Mach Co Ltd | Hydraulic circuit |
| EP0833013A1 (en) * | 1996-09-30 | 1998-04-01 | Mailleux S.A. | Hydraulic control device for a lifting cylinder of an arm of an agricultural loader |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5549116B2 (en) * | 1971-10-25 | 1980-12-10 |
-
1984
- 1984-11-12 JP JP23667184A patent/JPS61116105A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5549116B2 (en) * | 1971-10-25 | 1980-12-10 |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6319402A (en) * | 1986-07-08 | 1988-01-27 | Hitachi Constr Mach Co Ltd | Hydraulic circuit |
| EP0833013A1 (en) * | 1996-09-30 | 1998-04-01 | Mailleux S.A. | Hydraulic control device for a lifting cylinder of an arm of an agricultural loader |
| FR2754000A1 (en) * | 1996-09-30 | 1998-04-03 | Mailleux Sa | HYDRAULIC CONTROL DEVICE FOR THE LIFTING JACK OF AN AGRICULTURAL LOADER ARM |
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