JPH10252705A - Pressure oil feeding device - Google Patents

Pressure oil feeding device

Info

Publication number
JPH10252705A
JPH10252705A JP9060387A JP6038797A JPH10252705A JP H10252705 A JPH10252705 A JP H10252705A JP 9060387 A JP9060387 A JP 9060387A JP 6038797 A JP6038797 A JP 6038797A JP H10252705 A JPH10252705 A JP H10252705A
Authority
JP
Japan
Prior art keywords
pressure
valve
circuit
hydraulic pump
actuators
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
Application number
JP9060387A
Other languages
Japanese (ja)
Inventor
Nobusane Yoshida
伸実 吉田
Hiroshi Endo
弘 遠藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Komatsu Ltd
Original Assignee
Komatsu Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Komatsu Ltd filed Critical Komatsu Ltd
Priority to JP9060387A priority Critical patent/JPH10252705A/en
Priority to KR1019980007205A priority patent/KR19980079912A/en
Priority to PCT/JP1998/001043 priority patent/WO1998041765A1/en
Publication of JPH10252705A publication Critical patent/JPH10252705A/en
Pending legal-status Critical Current

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use 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
    • F15B2211/20—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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or 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
    • F15B2211/405—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
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/41545—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple 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
    • F15B2211/40—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
    • F15B2211/40—Flow control
    • F15B2211/465—Flow control with pressure compensation
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Abstract

PROBLEM TO BE SOLVED: To reduce a loss when pressure oil is simultaneously fed to a plurality of actuators. SOLUTION: A pressure oil feeding device, a first and a second circuits 11 and 12 are connected to a first and a second discharge ports 10a and 10b of a double hydraulic pump 10. The first and second circuits 11 and 12 are connected to a first and a second actuators 17 and 18 through a first and a second operation valves 13 and 14 and a first and a second pressure compensating valves 15 and 16 and first and second pressure compensation valves 15 and 16 are set by the load pressure of the first and second actuators 17 and 18, whichever higher. The first and second circuits 11 and 12 are interconnected through a confluent valve 19, and the confluent valve 19 at which a pressure difference between the first and second circuits 11 and 12 occurs, forms a communication position.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本発明は、油圧ポンプの吐出
圧油を複数のアクチュエータに分配して供給する圧油供
給装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure oil supply device that distributes and supplies pressure oil discharged from a hydraulic pump to a plurality of actuators.

【０００２】[0002]

【従来の技術】油圧ポンプの吐出圧油を負荷の異なる複
数のアクチュエータに同時に供給すると、最も負荷の小
さいアクチュエータにのみ圧油が供給されて他のアクチ
ュエータには圧油が供給されない。2. Description of the Related Art When hydraulic oil discharged from a hydraulic pump is simultaneously supplied to a plurality of actuators having different loads, the hydraulic oil is supplied only to the actuator with the smallest load, and the hydraulic oil is not supplied to the other actuators.

【０００３】そこで、図１に示すように、油圧ポンプ１
の吐出路１ａに第１操作弁２、第２操作弁３を設け、こ
の第１・第２操作弁２，３と第１・第２アクチュエータ
４，５を接続する回路に圧力補償弁６を設け、第１アク
チュエータ４の負荷圧と第２アクチュエータ５の負荷圧
の高い方の圧力をシャトル弁７で検出し、その検出した
圧力を圧力補償弁６の受圧部６ａに供給するものが知ら
れている。[0003] Therefore, as shown in FIG.
A first operation valve 2 and a second operation valve 3 are provided in the discharge path 1a of the first embodiment, and a pressure compensating valve 6 is provided in a circuit connecting the first and second operation valves 2 and 3 and the first and second actuators 4 and 5. There is a known type in which the shuttle valve 7 detects the higher of the load pressure of the first actuator 4 and the load pressure of the second actuator 5 and supplies the detected pressure to the pressure receiving portion 6a of the pressure compensating valve 6. ing.

【０００４】図１に示すものであれば、圧力補償弁６が
最も高い負荷圧でセットされるので、第１・第２操作弁
２，３の開度に応じた流量分配比で第１・第２アクチュ
エータ４，５に圧油を供給できる。In the case shown in FIG. 1, since the pressure compensating valve 6 is set at the highest load pressure, the first and second operating valves 2 and 3 are set at a flow distribution ratio corresponding to the opening degree of the first and second operating valves 2 and 3. Pressure oil can be supplied to the second actuators 4 and 5.

【０００５】[0005]

【発明が解決しようとする課題】かかる圧油供給装置で
あると、低圧側の圧力補償弁６の開口面積が小さく、そ
の圧力補償弁６を高圧の流体が流通するので、低圧側の
圧力補償弁６によって高圧の流体が絞られるからロスが
大である。With such a pressure oil supply device, the opening area of the low-pressure side pressure compensating valve 6 is small, and high-pressure fluid flows through the pressure compensating valve 6, so that the low-pressure side pressure compensating valve 6 can be used. Since the high-pressure fluid is throttled by the valve 6, the loss is large.

【０００６】そこで、本発明は前述の課題を解決できる
ようにした圧油供給装置を提供することを目的とする。Accordingly, an object of the present invention is to provide a pressure oil supply device capable of solving the above-mentioned problems.

【０００７】[0007]

【課題を解決するための手段及び作用・効果】第１の発
明は、駆動軸が同一で独立した複数の吐出ポートを有す
る可変容量型油圧ポンプユニットと、この複数の吐出ポ
ートと複数のアクチュエータを接続する複数の回路にそ
れぞれ設けた操作弁、圧力補償弁と、複数のアクチュエ
ータの最も高い負荷圧を検出し、その検出した負荷圧で
各圧力補償弁をセットすると共に、可変容量型油圧ポン
プユニットの容量を制御する手段と、前記複数の吐出ポ
ートの圧力が等しい時には前記複数の回路を連通し、圧
力差が生じた時に遮断する合流弁１９で構成したことを
特徴とする圧油供給装置である。A first aspect of the present invention is a variable displacement hydraulic pump unit having a plurality of independent discharge ports having the same drive shaft and a plurality of discharge ports and a plurality of actuators. The operation valve and the pressure compensation valve provided in each of the plurality of circuits to be connected, and the highest load pressure of the plurality of actuators are detected, and each pressure compensation valve is set with the detected load pressure, and the variable displacement hydraulic pump unit is set. A pressure oil supply device characterized by comprising a means for controlling the capacity of the pressure oil and a merging valve 19 which communicates with the plurality of circuits when the pressures of the plurality of discharge ports are equal and shuts off when a pressure difference occurs. is there.

【０００８】第１の発明によれば、各吐出ポートの圧力
は独立し、アクチュエータの外部負荷に見合う圧力とな
るし、複数のアクチュエータの負荷圧が異なる時には合
流弁１９が連通位置となって複数の回路が連通し、各圧
力補償弁は最も高い負荷圧でセットされるので、負荷圧
が低圧で要求流量が大の第１のアクチュエータと負荷圧
が高圧で要求流量が小の第２のアクチュエータに同時に
圧油を供給する時には、第２のアクチュエータに供給さ
れる流体の一部が第１のアクチュエータに供給される。According to the first aspect of the present invention, the pressure at each discharge port is independent and becomes a pressure corresponding to the external load of the actuator. When the load pressures of a plurality of actuators are different, the merging valve 19 becomes the communicating position and the plurality of Are connected to each other and each pressure compensating valve is set at the highest load pressure. Therefore, the first actuator having a low load pressure and a large required flow rate and the second actuator having a high load pressure and a small required flow rate are provided. When the pressure oil is supplied to the first actuator at the same time, a part of the fluid supplied to the second actuator is supplied to the first actuator.

【０００９】したがって、第２のアクチュエータに供給
される流体の一部が合流弁１９を流通する時に絞られる
だけであるから、複数のアクチュエータを同時作動する
時のロスが低減する。Therefore, since a part of the fluid supplied to the second actuator is only throttled when flowing through the merging valve 19, the loss when simultaneously operating a plurality of actuators is reduced.

【００１０】また、負荷圧が低圧で要求流量が小の第１
のアクチュエータと負荷圧が高圧で要求流量が大の第２
のアクチュエータに同時に圧油を供給する時には、合流
弁１９が連通位置と遮断位置に交互に切換えられるだけ
である。[0010] The first load having a low load pressure and a small required flow rate.
Actuator with high load pressure and high required flow rate
When pressure oil is supplied to the actuators at the same time, the junction valve 19 is merely switched alternately between the communicating position and the shutoff position.

【００１１】したがって、高圧の負荷圧でセットされた
圧力補償弁には第１のアクチュエータの負荷圧に見合う
低圧の流体が、その要求流量だけ流れるから、複数のア
クチュエータを同時作動する時のロスが低減する。Therefore, a low-pressure fluid corresponding to the load pressure of the first actuator flows through the pressure compensating valve set at a high load pressure by the required flow rate, so that a loss when simultaneously operating a plurality of actuators is lost. Reduce.

【００１２】第２の発明は、第１の発明における前記可
変容量型油圧ポンプユニットを、斜板式油圧ポンプのシ
リンダーブロック３０の外周寄りと内周寄りに複数のシ
リンダー孔を同芯状に設け、弁板３３の外周寄りと内周
寄りに高圧ポート、低圧ポートを同芯状に形成したもの
又は、可変容量型の複数の油圧ポンプを機械的に連結
し、かつ斜板を連結して同一容量となるようにしたもの
とした圧油供給装置である。According to a second aspect of the present invention, in the variable displacement hydraulic pump unit according to the first aspect, a plurality of cylinder holes are provided concentrically near an outer periphery and an inner periphery of a cylinder block 30 of the swash plate type hydraulic pump, A high-pressure port and a low-pressure port formed concentrically near the outer periphery and the inner periphery of the valve plate 33, or a plurality of variable displacement hydraulic pumps are mechanically connected, and a swash plate is connected to have the same capacity. This is a pressure oil supply device.

【００１３】第３の発明は、第１の発明における前記合
流弁１９を、スプリング力で遮断位置ａ、第１受圧部２
０の圧力で第１連通位置ｂ、第２受圧部２１の圧力で第
２連通位置ｃとなるものとし、その第１受圧部２０を一
方の回路、第２受圧部２１を他方の回路に接続した圧油
供給装置である。According to a third aspect of the present invention, the merging valve 19 of the first aspect of the present invention is configured such that the joining position
It is assumed that the first pressure receiving portion 20 is connected to one circuit and the second pressure receiving portion 21 is connected to the other circuit by setting the first communication position b at the pressure of 0 and the second communication position c at the pressure of the second pressure receiving portion 21. Pressure oil supply device.

【００１４】第３の発明によれば、回路の圧力で合流弁
１９が直接的に切換え作動するので、合流弁１９の切換
え作動が確実であるし、応答性が優れたものとなる。According to the third aspect of the present invention, the switching operation of the merging valve 19 is directly performed by the pressure of the circuit, so that the switching operation of the merging valve 19 is assured and the responsiveness is improved.

【００１５】第４の発明は、第１の発明における前記合
流弁１９を、スプリング力で遮断位置ａ、外部信号で連
通位置ｄとなるものとし、一方の回路と他方の回路の圧
力を検出する第１・第２圧力センサ４７，４８と、この
第１・第２圧力センサ４７，４８の検出圧力が入力され
て圧力差がある時に合流弁１９に外部信号を出力するコ
ントローラ４９を設けた圧油供給装置である。According to a fourth aspect of the present invention, the junction valve 19 in the first aspect of the present invention is set to a shut-off position a by a spring force and a communication position d by an external signal, and detects the pressure of one circuit and the other circuit. A pressure provided with first and second pressure sensors 47 and 48 and a controller 49 for outputting an external signal to the junction valve 19 when the pressure detected by the first and second pressure sensors 47 and 48 is input and there is a pressure difference. It is an oil supply device.

【００１６】第４の発明によれば、コントローラ４９を
用いていることによって合流弁１９を切換えるタイミン
グを任意に設定できる。According to the fourth aspect, by using the controller 49, the timing for switching the junction valve 19 can be arbitrarily set.

【００１７】[0017]

【発明の実施の形態】図２に示すように、ダブル油圧ポ
ンプ１０の第１・第２吐出ポート１０ａ，１０ｂに接続
した第１・第２回路１１，１２は第１・第２操作弁１
３，１４、第１・第２圧力補償弁１５，１６を経て第１
・第２アクチュエータ１７，１８にそれぞれ接続する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As shown in FIG. 2, first and second circuits 11, 12 connected to first and second discharge ports 10a, 10b of a double hydraulic pump 10 have first and second operating valves 1 and 2, respectively.
3, 14 and the first and second pressure compensating valves 15, 16
-Connect to the second actuators 17 and 18, respectively.

【００１８】前記第１回路１１と第２回路１２は合流弁
１９で連通・遮断される。この合流弁１９はスプリング
力で遮断位置ａに保持され、第１受圧部２０と第２受圧
部２１との圧力差によって第１連通位置ｂ、第２連通位
置ｃに切換えられる。第１受圧部２０は第１回路１１に
接続し、第２受圧部２１は第２回路１２に接続してい
る。The first circuit 11 and the second circuit 12 are connected and disconnected by a merge valve 19. The joining valve 19 is held at the shut-off position a by the spring force, and is switched to the first communication position b and the second communication position c by the pressure difference between the first pressure receiving portion 20 and the second pressure receiving portion 21. The first pressure receiving section 20 is connected to the first circuit 11, and the second pressure receiving section 21 is connected to the second circuit 12.

【００１９】第１アクチュエータ１７の負荷圧と第２ア
クチュエータ１８の負荷圧の高い方がシャトル弁２２で
検出され、その高い方の負荷圧がダブル油圧ポンプ１０
の第１容量制御部２３に作用し、第１・第２吐出ポート
１０ａ，１０ｂの高い方の圧力がシャトル弁２４で検出
され、その圧力が第２容量制御部２５に作用する。これ
によってその容量がポンプ吐出圧と負荷圧の差圧を一定
とするように制御される。なお、第１・第２吐出ポート
１０ａ，１０ｂの圧力をそれぞれ第２・第３容量制御部
に作用してポンプ吐出圧と負荷圧の差圧が一定となるよ
うに容量を制御しても良い。The higher one of the load pressure of the first actuator 17 and the load pressure of the second actuator 18 is detected by the shuttle valve 22, and the higher load pressure is detected by the double hydraulic pump 10.
, The higher pressure of the first and second discharge ports 10a, 10b is detected by the shuttle valve 24, and the pressure acts on the second capacity control unit 25. As a result, the displacement is controlled so that the differential pressure between the pump discharge pressure and the load pressure becomes constant. The displacements of the first and second discharge ports 10a and 10b may be applied to the second and third displacement control units to control the displacement so that the differential pressure between the pump discharge pressure and the load pressure becomes constant. .

【００２０】前記ダブル油圧ポンプ１０は図３に示すよ
うに、斜板式油圧ポンプのシリンダーブロック３０の外
周寄りに複数の第１シリンダー孔３１、内周寄りに複数
の第２シリンダー孔３２を同心状に形成し、弁板３３の
外周寄りに第１高圧ポート３４、第１低圧ポート３５、
内周寄りに第２高圧ポート３６、第２低圧ポート３７を
同心状に形成して独立した第１油圧ポンプと第２油圧ポ
ンプとしたものであって、駆動軸が同一で複数の吐出ポ
ートを有する可変容量型油圧ポンプユニットを構成して
いる。その第１油圧ポンプの吐出部（第１高圧ポート３
４）が第１吐出ポート１０ａ、第２油圧ポンプの吐出部
（第２高圧ポート３６）が第２吐出ポート１０ｂとな
る。As shown in FIG. 3, the double hydraulic pump 10 has a plurality of first cylinder holes 31 near the outer periphery of a cylinder block 30 of the swash plate type hydraulic pump and a plurality of second cylinder holes 32 near the inner periphery. And a first high-pressure port 34, a first low-pressure port 35 near the outer periphery of the valve plate 33,
A second high-pressure port 36 and a second low-pressure port 37 are formed concentrically near the inner periphery to form an independent first hydraulic pump and a second hydraulic pump. Having a variable displacement hydraulic pump unit. The discharge portion of the first hydraulic pump (the first high pressure port 3
4) is the first discharge port 10a, and the discharge part (second high-pressure port 36) of the second hydraulic pump is the second discharge port 10b.

【００２１】次に作動を説明する。第１アクチュエータ
１７が低圧で要求流量大、第２アクチュエータ１８が高
圧で要求流量小の時。第１回路１１の圧力Ｐ1 が第２回
路１２の圧力Ｐ2 よりも低いので、合流弁１９は第２連
通位置ｃとなり、第２回路１２の流体の一部が第１回路
１１に流入する。第２アクチュエータ１８の負荷圧が容
量制御部２３に作用してダブル油圧ポンプ１０の容量は
第２アクチュエータ１８の負荷圧に見合う容量となる。Next, the operation will be described. When the first actuator 17 is at a low pressure and the required flow rate is large, and when the second actuator 18 is at a high pressure and the required flow rate is small. The pressure P 1 of the first circuit 11 is lower than the pressure P 2 of the second circuit 12, the confluence valve 19 and the second communication position c, and the part of the fluid in the second circuit 12 flows into the first circuit 11 . The load pressure of the second actuator 18 acts on the capacity control unit 23, and the capacity of the double hydraulic pump 10 becomes a capacity corresponding to the load pressure of the second actuator 18.

【００２２】このように、第１回路１１の圧力Ｐ1 はア
クチュエータ１７の外部負荷の大きさに見合う低圧で、
第２回路１２の圧力Ｐ2 は第２アクチュエータ１８の外
部負荷の大きさに見合う高圧であるし、第２回路１２の
流体の一部が第１アクチュエータ１７に応援される。し
たがって、第１アクチュエータ１７に大流量を供給して
高速で作動できるし、第２アクチュエータ１８に第１ア
クチュエータ１７よりも高い圧力の流体を供給して大き
な力で作動できる。As described above, the pressure P 1 of the first circuit 11 is a low pressure corresponding to the magnitude of the external load of the actuator 17,
The pressure P 2 of the second circuit 12 is a high pressure corresponding to the magnitude of the external load of the second actuator 18, and a part of the fluid of the second circuit 12 is supported by the first actuator 17. Therefore, a large flow rate can be supplied to the first actuator 17 to operate at a high speed, and a fluid having a higher pressure than the first actuator 17 can be supplied to the second actuator 18 to operate with a large force.

【００２３】また、第１圧力補償弁１５は高圧側の負荷
圧で開口面積小となるが、流通する流体の圧力が低圧で
あるからロスが少なく、第２回路１２の流体の一部が合
流弁１９を流量する際に絞られるが、その流量は少ない
から、ロスが小となる。The opening area of the first pressure compensating valve 15 is reduced by the load pressure on the high pressure side. However, since the pressure of the flowing fluid is low, the loss is small, and a part of the fluid of the second circuit 12 joins. The valve 19 is throttled when the flow rate is reduced, but the flow rate is small, so that the loss is small.

【００２４】第１アクチュエータ１７が低圧で要求流量
小、第２アクチュエータ１８が高圧で要求流量大の時。
前述と同様に合流弁１９は第２連通位置ｃとなって、第
１回路１１と第２回路１２が連通し、第１圧力補償弁１
５が高圧側の負荷圧で絞られるので、第１回路１１の圧
力Ｐ1 と第２回路１２のＰ2 は同一となり、合流弁１９
が遮断位置ａとなる。これによって第１回路１１の圧力
Ｐ1 が低圧、第２回路１２の圧力Ｐ2 が高圧となって、
合流弁１９は第２連通位置ｃとなる。この動作を繰り返
しする。When the first actuator 17 is low pressure and the required flow rate is small, and the second actuator 18 is high pressure and the required flow rate is large.
As described above, the merging valve 19 is at the second communication position c, the first circuit 11 and the second circuit 12 are in communication, and the first pressure compensating valve 1
Because 5 is throttled in the load pressure of the high pressure side, P 2 of the pressure P 1 and the second circuit 12 of the first circuit 11 becomes the same, merging valve 19
Becomes the cutoff position a. As a result, the pressure P 1 of the first circuit 11 becomes low and the pressure P 2 of the second circuit 12 becomes high,
The junction valve 19 is at the second communication position c. This operation is repeated.

【００２５】図４は第２の実施の形態を示し、第１油圧
ポンプ４０と第２油圧ポンプ４１を機械的に連結し、そ
の第１油圧ポンプ４０の斜板４２と第２油圧ポンプ４１
の斜板４３を連結して同一容量となるようにして駆動軸
が同一で複数の吐出ポートを有する可変容量型油圧ポン
プユニットとしてある。第１油圧ポンプ４０の容量制御
部４４と第２油圧ポンプ４１の容量制御部４５にシャト
ル弁２２の出力圧を供給する。FIG. 4 shows a second embodiment in which a first hydraulic pump 40 and a second hydraulic pump 41 are mechanically connected, and a swash plate 42 of the first hydraulic pump 40 and a second hydraulic pump 41 are connected.
And a variable displacement hydraulic pump unit having the same drive shaft and a plurality of discharge ports by connecting the swash plates 43 to each other. The output pressure of the shuttle valve 22 is supplied to the displacement control unit 44 of the first hydraulic pump 40 and the displacement control unit 45 of the second hydraulic pump 41.

【００２６】第１油圧ポンプ４０の吐出ポート４０ａに
接続した第１回路１１と第２油圧ポンプ４１の吐出ポー
ト４１ａに接続した第２回路１２は合流弁１９で連通・
遮断される。この合流弁１９はスプリング力で遮断位置
ａに保持され、ソレノイド４６に通電されると連通位置
ｄとなる。前記第１回路１１の圧力を第１圧力センサ４
７で検出し、第２回路１２の圧力を第２圧力センサ４８
で検出してコントローラ４９にそれぞれ入力する。コン
トローラ４９は第１圧力センサ４７と第２圧力センサ４
８の検出圧力差が生じた時にソレノイド４６に通電す
る。The first circuit 11 connected to the discharge port 40a of the first hydraulic pump 40 and the second circuit 12 connected to the discharge port 41a of the second hydraulic pump 41 communicate with each other via the junction valve 19.
Will be shut off. The merging valve 19 is held at the shut-off position a by the spring force, and becomes the communication position d when the solenoid 46 is energized. The pressure of the first circuit 11 is determined by the first pressure sensor 4
7, the pressure of the second circuit 12 is detected by the second pressure sensor 48.
And input to the controller 49. The controller 49 includes the first pressure sensor 47 and the second pressure sensor 4
When the detected pressure difference of 8 occurs, the solenoid 46 is energized.

【００２７】次に作動を説明する。第１回路１１の圧力
Ｐ1 と第２回路１２の圧力Ｐ2 とに差が生じると合流弁
１９が連通位置ｄとなるし、第１・第２油圧ポンプ４
０，４１の容量は同一容量に制御されるので、前述の第
１の実施の形態と同様に作動する。Next, the operation will be described. Pressure P 1 and the merging valve 19 and is a difference between the pressure P 2 results in the second circuit 12 of the first circuit 11 is the communicating position d, the first and second hydraulic pumps 4
Since the capacities of 0 and 41 are controlled to the same capacity, they operate in the same manner as in the first embodiment.

【００２８】前記合流弁１９は受圧部に供給されるパイ
ロット圧油で連通位置ｄとなるものとしても良い。この
場合はコントローラ４９で電磁弁を切換えてパイロット
圧油を合流弁１９の受圧部に供給するようにする。The junction valve 19 may be set to the communication position d by pilot pressure oil supplied to the pressure receiving portion. In this case, the controller 49 switches the solenoid valve to supply the pilot pressure oil to the pressure receiving portion of the merge valve 19.

【図面の簡単な説明】[Brief description of the drawings]

【図１】従来例を示す油圧回路図である。FIG. 1 is a hydraulic circuit diagram showing a conventional example.

【図２】本発明の第１の実施の形態を示す油圧回路図で
ある。FIG. 2 is a hydraulic circuit diagram showing the first embodiment of the present invention.

【図３】ダブル油圧ポンプの断面図である。FIG. 3 is a sectional view of a double hydraulic pump.

【図４】本発明の第２の実施の形態を示す油圧回路図で
ある。FIG. 4 is a hydraulic circuit diagram showing a second embodiment of the present invention.

【符号の説明】[Explanation of symbols]

１…油圧ポンプ ２…第１操作弁 ３…第２操作弁 ４…第１アクチュエータ ５…第２アクチュエータ ６…圧力補償弁 ７…シャトル弁 １０…ダブル油圧ポンプ １１…第１回路 １２…第２回路 １３…第１操作弁 １４…第２操作弁 １５…第１圧力補償弁 １６…第２圧力補償弁 １７…第１アクチュエータ １８…第２アクチュエータ １９…合流弁 ４０…第１油圧ポンプ ４１…第２油圧ポンプ ４７…第１圧力センサ ４８…第２圧力センサ ４９…コントローラ DESCRIPTION OF SYMBOLS 1 ... Hydraulic pump 2 ... 1st operating valve 3 ... 2nd operating valve 4 ... 1st actuator 5 ... 2nd actuator 6 ... Pressure compensating valve 7 ... Shuttle valve 10 ... Double hydraulic pump 11 ... 1st circuit 12 ... 2nd circuit DESCRIPTION OF SYMBOLS 13 ... 1st operating valve 14 ... 2nd operating valve 15 ... 1st pressure compensating valve 16 ... 2nd pressure compensating valve 17 ... 1st actuator 18 ... 2nd actuator 19 ... Merging valve 40 ... 1st hydraulic pump 41 ... 2nd Hydraulic pump 47 ... first pressure sensor 48 ... second pressure sensor 49 ... controller

Claims (4)

【特許請求の範囲】[Claims] 【請求項１】 駆動軸が同一で独立した複数の吐出ポー
トを有する可変容量型油圧ポンプユニットと、この複数
の吐出ポートと複数のアクチュエータを接続する複数の
回路にそれぞれ設けた操作弁、圧力補償弁と、複数のア
クチュエータの最も高い負荷圧を検出し、その検出した
負荷圧で各圧力補償弁をセットすると共に、可変容量型
油圧ポンプユニットの容量を制御する手段と、前記複数
の吐出ポートの圧力が等しい時には前記複数の回路を連
通し、圧力差が生じた時に遮断する合流弁１９で構成し
たことを特徴とする圧油供給装置。1. A variable displacement hydraulic pump unit having a plurality of independent discharge ports having the same drive shaft, operating valves provided respectively in a plurality of circuits connecting the plurality of discharge ports and a plurality of actuators, and a pressure compensation. A valve, means for detecting the highest load pressure of the plurality of actuators, setting each pressure compensating valve with the detected load pressure, and controlling the capacity of the variable displacement hydraulic pump unit; and A pressure oil supply device comprising: a confluence valve 19 that connects the plurality of circuits when the pressures are equal and shuts off when a pressure difference occurs. 【請求項２】 前記可変容量型油圧ポンプユニットを、
斜板式油圧ポンプのシリンダーブロック３０の外周寄り
と内周寄りに複数のシリンダー孔を同芯状に設け、弁板
３３の外周寄りと内周寄りに高圧ポート、低圧ポートを
同芯状に形成したもの又は、可変容量型の複数の油圧ポ
ンプを機械的に連結し、かつ斜板を連結して同一容量と
なるようにしたものとした請求項１記載の圧油供給装
置。2. The variable displacement hydraulic pump unit,
A plurality of cylinder holes are provided concentrically near the outer periphery and inner periphery of the cylinder block 30 of the swash plate type hydraulic pump, and a high pressure port and a low pressure port are formed concentrically near the outer periphery and inner periphery of the valve plate 33. 2. The pressure oil supply device according to claim 1, wherein a plurality of variable displacement hydraulic pumps are mechanically connected and swash plates are connected so as to have the same capacity. 【請求項３】 前記合流弁１９を、スプリング力で遮断
位置ａ、第１受圧部２０の圧力で第１連通位置ｂ、第２
受圧部２１の圧力で第２連通位置ｃとなるものとし、そ
の第１受圧部２０を一方の回路、第２受圧部２１を他方
の回路に接続した請求項１記載の圧油供給装置。3. The merging valve 19 is turned on by a spring force into a shut-off position a, by the pressure of the first pressure receiving portion 20 into a first communication position b,
The pressure oil supply device according to claim 1, wherein the second communication position (c) is set at the pressure of the pressure receiving portion (21), and the first pressure receiving portion (20) is connected to one circuit and the second pressure receiving portion (21) is connected to the other circuit. 【請求項４】 前記合流弁１９を、スプリング力で遮断
位置ａ、外部信号で連通位置ｄとなるものとし、一方の
回路と他方の回路の圧力を検出する第１・第２圧力セン
サ４７，４８と、この第１・第２圧力センサ４７，４８
の検出圧力が入力されて圧力差がある時に合流弁１９に
外部信号を出力するコントローラ４９を設けた請求項１
記載の圧油供給装置。4. The first and second pressure sensors 47, which detect the pressure of one circuit and the other circuit, wherein the junction valve 19 is brought to a shut-off position a by a spring force and a communication position d by an external signal. 48, and the first and second pressure sensors 47, 48
2. A controller 49 for outputting an external signal to the junction valve 19 when the detected pressure is inputted and there is a pressure difference.
A pressurized oil supply device as described.
JP9060387A 1997-03-14 1997-03-14 Pressure oil feeding device Pending JPH10252705A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP9060387A JPH10252705A (en) 1997-03-14 1997-03-14 Pressure oil feeding device
KR1019980007205A KR19980079912A (en) 1997-03-14 1998-03-05 Pressure oil supply device
PCT/JP1998/001043 WO1998041765A1 (en) 1997-03-14 1998-03-12 Pressure oil supplying apparatus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP9060387A JPH10252705A (en) 1997-03-14 1997-03-14 Pressure oil feeding device

Publications (1)

Publication Number Publication Date
JPH10252705A true JPH10252705A (en) 1998-09-22

Family

ID=13140695

Family Applications (1)

Application Number Title Priority Date Filing Date
JP9060387A Pending JPH10252705A (en) 1997-03-14 1997-03-14 Pressure oil feeding device

Country Status (3)

Country Link
JP (1) JPH10252705A (en)
KR (1) KR19980079912A (en)
WO (1) WO1998041765A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160221562A1 (en) * 2013-09-16 2016-08-04 Ipgate Ag Electrically-driven pressure regulator and volume-delivery unit
US11104317B2 (en) 2013-09-16 2021-08-31 Ipgate Ag Brake device and method for operating a brake device

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005047709A1 (en) * 2003-11-14 2005-05-26 Komatsu Ltd. Hydraulic pressure control device of construction machinery
US7559197B2 (en) 2005-08-31 2009-07-14 Caterpillar Inc. Combiner valve control system and method

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3044171A1 (en) * 1980-11-24 1982-06-16 Linde Ag, 6200 Wiesbaden DRIVE SYSTEM WITH AT LEAST TWO SUBSYSTEMS
JP2810711B2 (en) * 1989-08-25 1998-10-15 東芝機械株式会社 Merging valve device for load sensing type hydraulic circuit
JPH05126104A (en) * 1991-11-06 1993-05-21 Yutani Heavy Ind Ltd Hydraulic circuit for construction machine
JP3515150B2 (en) * 1993-12-10 2004-04-05 カヤバ工業株式会社 Multiple piston pump
JPH0942205A (en) * 1995-07-26 1997-02-10 Kobe Steel Ltd Pump control device for hydraulic machine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160221562A1 (en) * 2013-09-16 2016-08-04 Ipgate Ag Electrically-driven pressure regulator and volume-delivery unit
US10421447B2 (en) * 2013-09-16 2019-09-24 Ipgate Ag Electrically-driven pressure regulator and volume-delivery unit
US11104317B2 (en) 2013-09-16 2021-08-31 Ipgate Ag Brake device and method for operating a brake device

Also Published As

Publication number Publication date
WO1998041765A1 (en) 1998-09-24
KR19980079912A (en) 1998-11-25

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