JP2013160318A - Hydraulic closed circuit system - Google Patents

Hydraulic closed circuit system Download PDF

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JP2013160318A
JP2013160318A JP2012023491A JP2012023491A JP2013160318A JP 2013160318 A JP2013160318 A JP 2013160318A JP 2012023491 A JP2012023491 A JP 2012023491A JP 2012023491 A JP2012023491 A JP 2012023491A JP 2013160318 A JP2013160318 A JP 2013160318A
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hydraulic
pump
pressure
port
closed circuit
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JP6009770B2 (en
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Shinji Terada
眞司 寺田
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Sumitomo Heavy Industries Ltd
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Sumitomo Heavy Industries Ltd
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Priority to JP2012023491A priority Critical patent/JP6009770B2/en
Priority to PCT/JP2012/078541 priority patent/WO2013118356A1/en
Priority to CN201280067659.8A priority patent/CN104067032B/en
Priority to KR1020147019533A priority patent/KR20140108278A/en
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    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • 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
    • F15B2211/20538—Type of pump constant 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
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/3052—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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/7054—Having equal piston areas
    • 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
    • F15B2211/765—Control of position or angle of the output member
    • F15B2211/7656—Control of position or angle of the output member with continuous position control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4078—Fluid exchange between hydrostatic circuits and external sources or consumers
    • F16H61/4139—Replenishing or scavenging pumps, e.g. auxiliary charge pumps

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Fluid Gearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic closed circuit system in which, even while a portion to be driven can be driven by a hydraulic fluid of a high flow, fine position control can be performed on the portion to be driven.SOLUTION: A hydraulic closed circuit system 100 capable of driving a hydraulic cylinder 3 is provided with: a hydraulic pump 1; an electric motor 2 for controlling the rotation of the hydraulic pump 1; a shuttle valve 7 in which a secondary side port 7b communicates with a first conduit C1 and a secondary side port 7c communicates with a second conduit C2; a charge pump 5 in which an ejection port communicates with a primary side port 7a of the shuttle valve 7; and a relief valve 8 which makes the charge pressure of the charge pump 5 a set pressure. The charge pump 5 maintains the first conduit C1 and the second conduit C2 at a charge pressure through the shuttle valve 7. The relief valve 8 can change the set pressure.

Description

本発明は、油圧シリンダ又は油圧モータを高流量の作動油で駆動可能な油圧閉回路システムに関し、特に、電動機によって駆動される油圧ポンプを備えた油圧閉回路システムに関する。   The present invention relates to a hydraulic closed circuit system capable of driving a hydraulic cylinder or a hydraulic motor with a high flow of hydraulic oil, and more particularly to a hydraulic closed circuit system including a hydraulic pump driven by an electric motor.

従来、作業機械に搭載される油圧モータ駆動用のＨＳＴ（Hydro Static Transmission）システムであり、エンジンに直結される油圧ポンプを駆動源として備えるＨＳＴシステムが知られている（例えば、特許文献１参照。）。   2. Description of the Related Art Conventionally, an HST (Hydro Static Transmission) system for driving a hydraulic motor mounted on a work machine and including a hydraulic pump directly connected to an engine as a drive source is known (see, for example, Patent Document 1). ).

また、油圧ショベルに搭載されるアームシリンダ駆動用の油圧閉回路であり、エンジンに直結される油圧ポンプを駆動源として備える油圧閉回路が知られている（例えば、特許文献２参照。）。   Further, a hydraulic closed circuit for driving an arm cylinder mounted on a hydraulic excavator, and a hydraulic closed circuit including a hydraulic pump directly connected to an engine as a drive source is known (for example, see Patent Document 2).

特開２００８−３２１９８号公報JP 2008-32198 A 特開昭６１−１２７９６７号公報JP-A 61-127967

しかしながら、特許文献１及び２に記載のＨＳＴシステム又は油圧閉回路は何れも、エンジンに直結された油圧ポンプを駆動源として用いるため、油圧ポンプの微小且つ正確な回転が求められる被駆動部の微小位置制御には不向きである。   However, since both the HST system and the hydraulic closed circuit described in Patent Documents 1 and 2 use a hydraulic pump directly connected to the engine as a driving source, the driven pump is required to have a minute and accurate rotation of the hydraulic pump. Not suitable for position control.

上述の点に鑑み、本発明は、高流量の作動油による被駆動部の駆動を可能としながらも低流量の作動油による被駆動部の微小位置制御を可能とする油圧閉回路システムを提供することを目的とする。   In view of the above, the present invention provides a hydraulic closed circuit system that enables the driven portion to be driven by a low flow rate of hydraulic fluid while allowing the driven portion to be driven by a low flow rate of hydraulic fluid. For the purpose.

上述の目的を達成するために、本発明の実施例に係る油圧閉回路システムは、第一ポート及び第二ポートを有する油圧シリンダ又は油圧モータを駆動可能な油圧閉回路システムであって、第一管路を通じて前記第一ポートに流体的に連通される第一ポンプポートと第二管路を通じて前記第二ポートに流体的に連通される第二ポンプポートとを有する油圧ポンプと、前記油圧ポンプの回転を制御する電動モータと、１つの一次側ポートと２つの二次側ポートとを有するシャトル弁であり、該二次側ポートの一方が前記第一管路に流体的に連通され、該二次側ポートの他方が前記第二管路に流体的に連通されるシャトル弁と、吐出ポートが前記シャトル弁の一次側ポートに流体的に連通されるチャージポンプと、前記チャージポンプによるチャージ圧を設定圧とするリリーフ弁とを備え、前記チャージポンプは、前記シャトル弁を通じて前記第一管路及び前記第二管路を前記チャージ圧にすることを特徴とする。   In order to achieve the above object, a hydraulic closed circuit system according to an embodiment of the present invention is a hydraulic closed circuit system capable of driving a hydraulic cylinder or a hydraulic motor having a first port and a second port. A hydraulic pump having a first pump port in fluid communication with the first port through a conduit and a second pump port in fluid communication with the second port through a second conduit; A shuttle valve having an electric motor for controlling rotation, one primary port and two secondary ports, wherein one of the secondary ports is in fluid communication with the first conduit; A shuttle valve in which the other of the secondary ports is in fluid communication with the second pipe, a charge pump in which a discharge port is in fluid communication with the primary port of the shuttle valve, and a charge pump by the charge pump. And a relief valve for the pressure and set pressure, the charge pump is characterized in the first conduit and the second conduit to the charge pressure through the shuttle valve.

上述の手段により、本発明は、高流量の作動油による被駆動部の駆動を可能としながらも低流量の作動油による被駆動部の微小位置制御を可能とする油圧閉回路システムを提供することができる。   By the above-mentioned means, the present invention provides a hydraulic closed circuit system that enables driving of a driven part with a low flow rate of hydraulic fluid while allowing the driven part to be controlled with a low flow rate of hydraulic fluid. Can do.

本発明の実施例に係る油圧閉回路システムの構成例を示す概略図である。It is the schematic which shows the structural example of the hydraulic closed circuit system which concerns on the Example of this invention. 主管路圧がチャージ圧未満のときの油圧閉回路システムの状態を示す図である。It is a figure which shows the state of a hydraulic closed circuit system when a main pipe line pressure is less than a charge pressure. 油圧ポンプが吐出する作動油で油圧シリンダを駆動するときの油圧閉回路システムの状態を示す図である。It is a figure which shows the state of a hydraulic closed circuit system when driving a hydraulic cylinder with the hydraulic fluid which a hydraulic pump discharges.

以下、図面を参照しつつ、本発明の実施例について説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図１は、本発明の実施例に係る油圧閉回路システム１００の構成例を示す概略図である。   FIG. 1 is a schematic diagram illustrating a configuration example of a hydraulic closed circuit system 100 according to an embodiment of the present invention.

油圧閉回路システム１００は、電動モータ２によって回転制御される油圧ポンプ１で油圧シリンダ３を駆動するシステムである。油圧シリンダ３は、例えば、大負荷容量油圧駆動式大型平面研削盤のテーブルを駆動するために用いられる。   The hydraulic closed circuit system 100 is a system in which the hydraulic cylinder 3 is driven by a hydraulic pump 1 whose rotation is controlled by the electric motor 2. The hydraulic cylinder 3 is used, for example, to drive a table of a large load capacity hydraulically driven large surface grinder.

本実施例では、油圧閉回路システム１００は、主に、油圧ポンプ１、電動モータ２、油圧シリンダ３、安全弁４Ｌ、４Ｒ、チャージポンプ５、電動モータ６、シャトル弁７、リリーフ弁８、センサ９、及び制御装置１０で構成される。   In this embodiment, the hydraulic closed circuit system 100 mainly includes a hydraulic pump 1, an electric motor 2, a hydraulic cylinder 3, safety valves 4L and 4R, a charge pump 5, an electric motor 6, a shuttle valve 7, a relief valve 8, and a sensor 9. And the control device 10.

油圧ポンプ１は、油圧シリンダ３を駆動する装置であり、例えば、固定容量型の双方向油圧ポンプである。なお、油圧ポンプ１は、可変容量型のポンプであってもよい。   The hydraulic pump 1 is a device that drives the hydraulic cylinder 3, and is, for example, a fixed displacement bidirectional hydraulic pump. The hydraulic pump 1 may be a variable displacement pump.

電動モータ２は、油圧ポンプ１の回転を制御する装置であり、例えば、ＡＣサーボモータである。   The electric motor 2 is a device that controls the rotation of the hydraulic pump 1, and is, for example, an AC servo motor.

油圧シリンダ３は、ピストン３ａによって隔てられる第一油室３Ｌ及び第二油室３Ｒを有する油圧アクチュエータである。第一油室３Ｌは、第一ポート３ｂ及び管路Ｃ１を通じて、油圧ポンプ１の第一ポンプポート１ａに流体的に連通され、第二油室３Ｒは、第二ポート３ｃ及び管路Ｃ２を通じて、油圧ポンプ１の第二ポンプポート１ｂに流体的に連通される。本実施例において、油圧シリンダ３は、ピストン３ａの両側に延びる２つのロッドを備えた両ロッドシリンダであり、２つのロッドのうちの一方が平面研削盤テーブル（図示せず。）に結合される。なお、油圧シリンダ３は、ピストン３ａの片側に延びる１つのロッドを備えた片ロッドシリンダであってもよく、平面研削盤テーブルが直接的にピストン３ａに結合されるような、ロッドのない構成であってもよい。   The hydraulic cylinder 3 is a hydraulic actuator having a first oil chamber 3L and a second oil chamber 3R separated by a piston 3a. The first oil chamber 3L is fluidly communicated with the first pump port 1a of the hydraulic pump 1 through the first port 3b and the conduit C1, and the second oil chamber 3R is communicated with the second port 3c and the conduit C2. The hydraulic pump 1 is in fluid communication with the second pump port 1b. In this embodiment, the hydraulic cylinder 3 is a double rod cylinder having two rods extending on both sides of the piston 3a, and one of the two rods is coupled to a surface grinder table (not shown). . The hydraulic cylinder 3 may be a single rod cylinder having one rod extending on one side of the piston 3a, and has a rod-free configuration in which a surface grinder table is directly coupled to the piston 3a. There may be.

安全弁４Ｌは、管路Ｃ１内の圧力が所定圧力以上となった場合に、管路Ｃ１内の作動油を作動油タンクＴ１に逃がすための弁である。また、安全弁４Ｒは、管路Ｃ２内の圧力が所定圧力以上となった場合に、管路Ｃ２内の作動油を作動油タンクＴ１に逃がすための弁である。なお、以下では、管路Ｃ１及び管路Ｃ２を総称して「主管路」とし、管路Ｃ１内の圧力、及び、管路Ｃ２内の圧力を総称して「主管路圧」とする。   The safety valve 4L is a valve for releasing the hydraulic oil in the pipeline C1 to the hydraulic oil tank T1 when the pressure in the pipeline C1 becomes equal to or higher than a predetermined pressure. The safety valve 4R is a valve for releasing the hydraulic oil in the pipe C2 to the hydraulic oil tank T1 when the pressure in the pipe C2 becomes equal to or higher than a predetermined pressure. Hereinafter, the pipeline C1 and the pipeline C2 are collectively referred to as “main pipeline”, and the pressure in the pipeline C1 and the pressure in the pipeline C2 are collectively referred to as “main pipeline pressure”.

安全弁４Ｌは、作動油タンクＴ１に流体的に連通される管路Ｃ３と管路Ｃ１とを繋ぐ管路Ｃ４上に配置され、安全弁４Ｒは、管路Ｃ３と管路Ｃ２とを繋ぐ管路Ｃ５上に配置される。   The safety valve 4L is disposed on a pipe line C4 that connects the pipe line C3 and the pipe line C1 in fluid communication with the hydraulic oil tank T1, and the safety valve 4R is a pipe line C5 that connects the pipe line C3 and the pipe line C2. Placed on top.

チャージポンプ５は、管路Ｃ１及び管路Ｃ２のそれぞれの圧力が所定のチャージ圧以上となるように作動油を吐出する油圧ポンプであり、例えば、固定容量型の一方向油圧ポンプである。なお、チャージポンプ５は、可変容量型のポンプであってもよい。また、チャージポンプ５の１回転当たり吐出量は、油圧ポンプ１の１回転当たり吐出量よりも小さい。チャージポンプ５が吐出する作動油は、補助的なものであるためである。   The charge pump 5 is a hydraulic pump that discharges hydraulic oil such that each pressure in the pipe line C1 and the pipe line C2 is equal to or higher than a predetermined charge pressure. For example, the charge pump 5 is a fixed capacity type one-way hydraulic pump. The charge pump 5 may be a variable capacity pump. The discharge amount per rotation of the charge pump 5 is smaller than the discharge amount per rotation of the hydraulic pump 1. This is because the hydraulic oil discharged from the charge pump 5 is auxiliary.

電動モータ６は、チャージポンプ５の回転を制御する装置であり、例えば、ＡＣサーボモータである。電動モータ６は、チャージポンプ５が所定流速で作動油を継続的に吐出するよう、所定の回転速度で継続的に回転する。なお、電動モータ６は、チャージポンプ５の吐出圧が所定のチャージ圧となるようにチャージポンプ５の吐出量を変化させるべく、回転速度を変化させながら回転してもよい。   The electric motor 6 is a device that controls the rotation of the charge pump 5, and is, for example, an AC servo motor. The electric motor 6 continuously rotates at a predetermined rotation speed so that the charge pump 5 continuously discharges hydraulic oil at a predetermined flow rate. The electric motor 6 may rotate while changing the rotation speed so as to change the discharge amount of the charge pump 5 so that the discharge pressure of the charge pump 5 becomes a predetermined charge pressure.

シャトル弁７は、管路Ｃ１又は管路Ｃ２と作動油タンクＴ１及びチャージポンプ５のそれぞれとの間の作動油の流れを制御する弁であり、１つの一次側ポート７ａと２つの二次側ポート７ｂ、７ｃとを有する。   The shuttle valve 7 is a valve that controls the flow of hydraulic oil between the pipe C1 or the pipe C2 and each of the hydraulic oil tank T1 and the charge pump 5, and includes one primary port 7a and two secondary sides. Ports 7b and 7c.

一次側ポート７ａは、管路Ｃ６を介して、チャージポンプ５の吐出ポートに流体的に連通され、二次側ポートの一方７ｂは、管路Ｃ７を介して、管路Ｃ１に流体的に連通され、二次側ポートの他方７ｃは、管路Ｃ８を介して、管路Ｃ２に流体的に連通される。   The primary port 7a is fluidly communicated with the discharge port of the charge pump 5 via the conduit C6, and one of the secondary ports 7b is fluidly communicated with the conduit C1 via the conduit C7. The other side 7c of the secondary side port is fluidly connected to the pipe line C2 via the pipe line C8.

具体的には、シャトル弁７は、管路Ｃ１内の圧力が所定のチャージ圧よりも低い場合、二次側ポート７ｂを通じて、チャージポンプ５が吐出する作動油を管路Ｃ１内に導入する。また、シャトル弁７は、管路Ｃ２内の圧力が所定のチャージ圧よりも低い場合、二次側ポート７ｃを通じて、チャージポンプ５が吐出する作動油を管路Ｃ２内に導入する。   Specifically, the shuttle valve 7 introduces hydraulic oil discharged from the charge pump 5 into the pipe line C1 through the secondary port 7b when the pressure in the pipe line C1 is lower than a predetermined charge pressure. Further, when the pressure in the pipe C2 is lower than the predetermined charge pressure, the shuttle valve 7 introduces hydraulic oil discharged from the charge pump 5 into the pipe C2 through the secondary port 7c.

リリーフ弁８は、一次側ポート８ａの圧力が所定の設定圧以上となった場合に一次側ポート８ａと二次側ポート８ｂとを流体的に連通して一次側ポート８ａの作動油を二次側ポート８ｂに流出させる弁である。   The relief valve 8 fluidly communicates the primary side port 8a and the secondary side port 8b when the pressure of the primary side port 8a becomes equal to or higher than a predetermined set pressure, and supplies the hydraulic fluid in the primary side port 8a to the secondary side. This is a valve that flows out to the side port 8b.

一次側ポート８ａは、管路Ｃ９を介して、管路Ｃ６に流体的に連通され、二次側ポート８ｂは、管路Ｃ１０を介して、作動油タンクＴ１に流体的に連通される。   The primary side port 8a is fluidly connected to the pipe line C6 via the pipe line C9, and the secondary side port 8b is fluidly connected to the hydraulic oil tank T1 via the pipe line C10.

本実施例では、リリーフ弁８は、電磁比例リリーフ弁であり、制御装置１０から供給される制御電流の大きさに応じて設定圧を変化させる。なお、リリーフ弁８の設定圧は、チャージポンプ５のチャージ圧に対応する。   In the present embodiment, the relief valve 8 is an electromagnetic proportional relief valve, and changes the set pressure according to the magnitude of the control current supplied from the control device 10. The set pressure of the relief valve 8 corresponds to the charge pressure of the charge pump 5.

センサ９は、油圧シリンダ３の動作状態を検出するセンサであり、例えば、ピストン３ａの変位を検出する位置センサである。センサ９は、検出した値を制御装置１０に対して出力する。   The sensor 9 is a sensor that detects the operating state of the hydraulic cylinder 3, and is, for example, a position sensor that detects the displacement of the piston 3a. The sensor 9 outputs the detected value to the control device 10.

制御装置１０は、油圧閉回路システム１００を制御するための装置であり、例えば、ＣＰＵ、ＲＡＭ、ＲＯＭ、入出力インタフェース等を備えたコンピュータである。   The control device 10 is a device for controlling the hydraulic closed circuit system 100 and is, for example, a computer including a CPU, a RAM, a ROM, an input / output interface, and the like.

また、制御装置１０は、ユーザ入力に応じて、平面研削盤テーブルの所要移動距離（現在位置から目標位置までの距離）、すなわち、ピストン３ａの所要移動距離を決定する。さらに、制御装置１０は、決定したピストン３ａの所要移動距離に応じて油圧ポンプ１の回転方向及び回転速度を決定し、決定した油圧ポンプ１の回転方向及び回転速度に対応する制御信号を電動モータ２に対して出力する。具体的には、制御装置１０は、ピストン３ａの所要移動距離が大きいほど油圧ポンプ１の回転速度が大きくなるように油圧ポンプ１の回転速度を決定する。また、制御装置１０は、ピストン３ａの所要移動距離が小さくなるにつれて、すなわち、目標位置に近づくにつれて、油圧ポンプ１の回転速度が小さくなるように、油圧ポンプ１の回転速度を決定する。   Moreover, the control apparatus 10 determines the required moving distance (distance from the current position to the target position) of the surface grinder table, that is, the required moving distance of the piston 3a, according to the user input. Further, the control device 10 determines the rotation direction and rotation speed of the hydraulic pump 1 according to the determined required moving distance of the piston 3a, and sends a control signal corresponding to the determined rotation direction and rotation speed of the hydraulic pump 1 to the electric motor. 2 is output. Specifically, the control device 10 determines the rotational speed of the hydraulic pump 1 so that the rotational speed of the hydraulic pump 1 increases as the required moving distance of the piston 3a increases. Further, the control device 10 determines the rotation speed of the hydraulic pump 1 so that the rotation speed of the hydraulic pump 1 decreases as the required moving distance of the piston 3a decreases, that is, as the target position is approached.

また、制御装置１０は、センサ９の出力に基づいてピストン３ａの位置、すなわち、平面研削盤テーブルの位置を監視しながら、平面研削盤テーブルが目標位置に到達したか否かを判定する。   Further, the control device 10 determines whether or not the surface grinder table has reached the target position while monitoring the position of the piston 3a, that is, the position of the surface grinder table, based on the output of the sensor 9.

平面研削盤テーブルが目標位置に到達したと判定した場合に、制御装置１０は、油圧ポンプ１の回転を停止させるための制御信号を電動モータ２に対して出力する。   When it is determined that the surface grinder table has reached the target position, the control device 10 outputs a control signal for stopping the rotation of the hydraulic pump 1 to the electric motor 2.

次に、図２を参照しながら、主管路圧がチャージ圧未満のときの油圧閉回路システム１００の状態について説明する。なお、図２において、太い実線は、主管路圧よりもチャージ圧が高い状態を表す。また、図２は、図の明瞭化のため、センサ９及び制御装置１０の図示を省略している。   Next, the state of the hydraulic closed circuit system 100 when the main line pressure is less than the charge pressure will be described with reference to FIG. In FIG. 2, a thick solid line represents a state where the charge pressure is higher than the main pipeline pressure. In FIG. 2, illustration of the sensor 9 and the control device 10 is omitted for clarity.

本実施例では、電動モータ６は、油圧ポンプ１及び電動モータ２が停止している場合にも、所定の回転速度で継続的に回転し、チャージポンプ５を所定の回転速度で継続的に回転させている。その結果、チャージポンプ５は、所定の流速で作動油を継続的に吐出している。   In this embodiment, even when the hydraulic pump 1 and the electric motor 2 are stopped, the electric motor 6 continuously rotates at a predetermined rotation speed, and the charge pump 5 continuously rotates at a predetermined rotation speed. I am letting. As a result, the charge pump 5 continuously discharges hydraulic oil at a predetermined flow rate.

チャージポンプ５が継続的に作動油を吐出した結果、管路Ｃ６及び管路Ｃ９内の圧力がチャージ圧、すなわち、リリーフ弁８の設定圧に達すると、リリーフ弁８は、管路Ｃ１０を通じて、管路Ｃ６及び管路Ｃ９内の作動油を作動油タンクＴ１に流出させる。その結果、管路Ｃ６及び管路Ｃ９内の圧力は、チャージ圧に維持される。   As a result of the continuous discharge of the hydraulic oil by the charge pump 5, when the pressure in the pipe C6 and the pipe C9 reaches the charge pressure, that is, the set pressure of the relief valve 8, the relief valve 8 passes through the pipe C10. The hydraulic oil in the pipe line C6 and the pipe line C9 is discharged to the hydraulic oil tank T1. As a result, the pressure in the pipe C6 and the pipe C9 is maintained at the charge pressure.

このとき、管路Ｃ１内の圧力がチャージ圧未満であれば、シャトル弁７は、矢印ＡＲ１で示すように、二次側ポート７ｂ及び管路Ｃ７を通じて作動油を管路Ｃ１に供給する。この作動油の流れは、管路Ｃ１内の圧力がチャージ圧に達した場合に消失する。   At this time, if the pressure in the pipe line C1 is less than the charge pressure, the shuttle valve 7 supplies hydraulic oil to the pipe line C1 through the secondary side port 7b and the pipe line C7 as indicated by an arrow AR1. This flow of hydraulic oil disappears when the pressure in the pipe C1 reaches the charge pressure.

同様に、管路Ｃ２内の圧力がチャージ圧未満であれば、シャトル弁７は、矢印ＡＲ２で示すように、二次側ポート７ｃ及び管路Ｃ８を通じて作動油を管路Ｃ２に供給する。この作動油の流れは、管路Ｃ２内の圧力がチャージ圧に達した場合に消失する。   Similarly, if the pressure in the pipe line C2 is less than the charge pressure, the shuttle valve 7 supplies hydraulic oil to the pipe line C2 through the secondary port 7c and the pipe line C8 as indicated by an arrow AR2. This flow of hydraulic oil disappears when the pressure in the pipe C2 reaches the charge pressure.

このように、油圧閉回路システム１００は、管路Ｃ１及び管路Ｃ２内の圧力が常にチャージ圧以上となるようにする。これは、油圧ポンプ１の回転を開始させる前の主管路圧（以下、「初期圧」とする。）を予め増大させ、主管路内の作動油の圧縮度を予め増大させておくことを意味する。   In this way, the hydraulic closed circuit system 100 ensures that the pressure in the pipe line C1 and the pipe line C2 is always equal to or higher than the charge pressure. This means that the main line pressure before starting the rotation of the hydraulic pump 1 (hereinafter referred to as “initial pressure”) is increased in advance, and the degree of compression of the hydraulic oil in the main line is increased in advance. To do.

その結果、油圧閉回路システム１００は、油圧ポンプ１の回転による主管路内の作動油の体積変化（圧縮容量）を小さくして油圧制御剛性を高め、応答遅れを排除し、且つ、ポンプ回転角による作動油吐出容積の制御分解能を高めることができる。この効果は、大負荷容量油圧駆動式大型平面研削盤のように油圧シリンダ３や主管路内の作動油の容量が大きく、作動負荷圧に達するまでの圧縮容量が大きいほど顕著になる。この効果により、油圧閉回路システム１００は、高流量の作動油によるピストン３a（平面研削盤テーブル）の駆動を可能にしながら、ピストン３a（平面研削盤テーブル）の微小位置制御をも可能にする。   As a result, the hydraulic closed circuit system 100 reduces the volume change (compression capacity) of the hydraulic oil in the main pipeline due to the rotation of the hydraulic pump 1 to increase the hydraulic control rigidity, eliminate the response delay, and the pump rotation angle. The control resolution of the hydraulic oil discharge volume can be increased. This effect becomes more prominent as the capacity of the hydraulic oil in the hydraulic cylinder 3 and the main pipeline increases as the large load capacity hydraulically driven large surface grinding machine increases and the compression capacity to reach the operating load pressure increases. Due to this effect, the hydraulic closed circuit system 100 also enables minute position control of the piston 3a (surface grinder table) while allowing the piston 3a (surface grinder table) to be driven by a high flow rate of hydraulic fluid.

なお、制御装置１０は、駆動対象の重量（例えば、平面研削盤テーブル及びその上に置かれる被加工物の合計重量である。）に応じてチャージ圧を変化させてもよい。   Note that the control device 10 may change the charge pressure in accordance with the weight of the drive target (for example, the total weight of the surface grinder table and the workpiece placed thereon).

具体的には、制御装置１０は、重量センサ（図示せず。）が検出した駆動対象の重量に応じてリリーフ弁８に対して出力する制御電流の大きさを変化させ、リリーフ弁８の設定圧、すなわちチャージ圧を変化させる。   Specifically, the control device 10 changes the magnitude of the control current output to the relief valve 8 according to the weight of the drive target detected by the weight sensor (not shown), and sets the relief valve 8. The pressure, that is, the charge pressure is changed.

より具体的には、駆動対象の重量が大きいほどリリーフ弁８の設定圧、すなわちチャージ圧が大きくなるようにする。主管路内の作動油の圧縮度を増大させることによって、駆動対象の重量が大きいほど大きくなる、油圧ポンプ１の回転による主管路内の作動油の体積変化（圧縮容量）の影響を打ち消すためである。   More specifically, the set pressure of the relief valve 8, that is, the charge pressure is increased as the weight of the driving target is increased. In order to counteract the influence of the volume change (compression capacity) of the hydraulic fluid in the main pipeline due to the rotation of the hydraulic pump 1, which increases as the weight of the drive target increases, by increasing the degree of compression of the hydraulic fluid in the main pipeline. is there.

これにより、油圧閉回路システム１００は、駆動対象の重量の違いにかかわらず、ピストン３a（平面研削盤テーブル）の微小位置制御の立ち上がり特性を安定させることができる。   Thereby, the hydraulic closed circuit system 100 can stabilize the rising characteristics of the minute position control of the piston 3a (surface grinder table) regardless of the difference in the weight of the driven object.

また、制御装置１０は、油圧閉回路システム１００が待機状態にある場合、リリーフ弁８の設定圧を下げ、チャージポンプ５を無負荷運転させるようにしてもよい。   In addition, when the hydraulic closed circuit system 100 is in a standby state, the control device 10 may reduce the set pressure of the relief valve 8 and cause the charge pump 5 to operate without load.

具体的には、制御装置１０は、操作者の入力に基づいて油圧閉回路システム１００が待機状態にあるか否かを判定し、待機状態にあると判定した場合に、リリーフ弁８に対して出力する制御電流の大きさを変化させ、リリーフ弁８の設定圧、すなわちチャージ圧を低下させる。   Specifically, the control device 10 determines whether or not the hydraulic closed circuit system 100 is in a standby state based on an operator's input, and when it is determined that the hydraulic closed circuit system 100 is in a standby state, The magnitude of the control current to be output is changed to reduce the set pressure of the relief valve 8, that is, the charge pressure.

これにより、油圧閉回路システム１００は、油圧閉回路システム１００が待機状態にある場合にエネルギが無駄に消費されるのを防止することができる。   Thereby, the hydraulic closed circuit system 100 can prevent wasteful consumption of energy when the hydraulic closed circuit system 100 is in a standby state.

次に、図３を参照しながら、油圧ポンプ１が吐出する作動油で油圧シリンダ３を駆動するときの油圧閉回路システム１００の状態について説明する。なお、図３において、太い点線は、油圧ポンプ１が第一ポンプポート１ａから油圧シリンダ３の第一油室３Ｌに向けて作動油を吐出した結果、管路Ｃ１、Ｃ４、Ｃ７内の圧力が上昇した状態を表す。また、太い実線は、管路Ｃ２内の圧力よりもチャージ圧が高い状態を表す。また、図３は、図の明瞭化のため、センサ９及び制御装置１０の図示を省略している。   Next, the state of the hydraulic closed circuit system 100 when the hydraulic cylinder 3 is driven by the hydraulic oil discharged from the hydraulic pump 1 will be described with reference to FIG. In FIG. 3, the thick dotted line indicates that the hydraulic pump 1 discharges the hydraulic oil from the first pump port 1a toward the first oil chamber 3L of the hydraulic cylinder 3, and as a result, the pressure in the pipelines C1, C4, and C7 Represents an elevated state. A thick solid line represents a state in which the charge pressure is higher than the pressure in the pipe line C2. In FIG. 3, the sensor 9 and the control device 10 are not shown for clarity.

図３で示すように、油圧閉回路システム１００は、操作者の入力に応じて電動モータ２により油圧ポンプ１を回転させ、ピストン３ａ（平面研削盤テーブル）を矢印ＡＲ３で示す方向に移動させるように油圧シリンダ３を駆動する。   As shown in FIG. 3, the hydraulic closed circuit system 100 rotates the hydraulic pump 1 by the electric motor 2 in accordance with an operator input, and moves the piston 3 a (surface grinder table) in the direction indicated by the arrow AR 3. The hydraulic cylinder 3 is driven.

このとき、管路Ｃ１及び第一油室３Ｌには油圧ポンプ１により作動油が供給されて管路Ｃ１及び第一油室３Ｌ内の作動油の圧縮度が増大する。その結果、管路Ｃ１及び第一油室３Ｌ内の作動油の圧力は増大する。   At this time, hydraulic oil is supplied to the pipe line C1 and the first oil chamber 3L by the hydraulic pump 1, and the degree of compression of the hydraulic oil in the pipe line C1 and the first oil chamber 3L increases. As a result, the pressure of the hydraulic oil in the pipe line C1 and the first oil chamber 3L increases.

一方、管路Ｃ２及び第二油室３Ｒからは油圧ポンプ１により作動油が吸い出されて管路Ｃ２及び第二油室３Ｒ内の作動油の圧縮度が減少する。その結果、管路Ｃ２及び第二油室３Ｒ内の作動油の圧力は減少する。   On the other hand, hydraulic oil is sucked out from the pipeline C2 and the second oil chamber 3R by the hydraulic pump 1, and the degree of compression of the hydraulic oil in the pipeline C2 and the second oil chamber 3R decreases. As a result, the pressure of the hydraulic oil in the pipe line C2 and the second oil chamber 3R decreases.

管路Ｃ２及び第二油室３Ｒ内の作動油の圧力が減少してチャージ圧を下回ると、シャトル弁７は、矢印ＡＲ４で示すように、二次側ポート７ｃ及び管路Ｃ８を通じて作動油を管路Ｃ２に供給する。このとき、チャージポンプ５は、矢印ＡＲ４１で示すように、管路Ｃ６を通じて作動油をシャトル弁７に供給する。この作動油の流れは、管路Ｃ２及び第二油室３Ｒ内の圧力がチャージ圧に達した場合に消失する。   When the pressure of the hydraulic oil in the pipe line C2 and the second oil chamber 3R decreases and falls below the charge pressure, the shuttle valve 7 removes the hydraulic oil through the secondary side port 7c and the pipe line C8 as indicated by an arrow AR4. Supply to line C2. At this time, the charge pump 5 supplies hydraulic oil to the shuttle valve 7 through the conduit C6 as indicated by an arrow AR41. This flow of hydraulic oil disappears when the pressure in the pipe C2 and the second oil chamber 3R reaches the charge pressure.

なお、油圧ポンプ１を所定の回転速度以上で回転させているときのチャージ圧は、油圧ポンプ１を駆動させる前のチャージ圧と異なる値であってもよく、例えば、油圧ポンプ１を駆動させる前のチャージ圧より低い値であってもよい。チャージ圧の利用目的が異なるからである。具体的には、油圧ポンプ１を駆動させる前のチャージ圧が油圧制御剛性を高めて作動油の体積弾性の安定化を図るためのものであるのに対し、油圧ポンプ１を回転させているときのチャージ圧は、主管路で不足した作動油を補充してキャビテーション等の発生を防止するためのものであるからである。また、油圧ポンプ１を回転させているときのチャージ圧をより低い値にすることで、チャージポンプ５を回転させる電動モータ６の負荷を低減させることができるからである。なお、この場合、制御装置１０は、例えば油圧ポンプ１の回転速度に応じてリリーフ弁８に対して出力する制御電流の大きさを変化させる。具体的には、制御装置１０は、油圧ポンプ１の回転速度が増大するにつれてリリーフ弁８の設定圧、すなわちチャージ圧を低下させる。   The charge pressure when the hydraulic pump 1 is rotated at a predetermined rotational speed or higher may be different from the charge pressure before driving the hydraulic pump 1, for example, before driving the hydraulic pump 1. It may be a value lower than the charge pressure. This is because the usage purpose of the charge pressure is different. Specifically, the charge pressure before driving the hydraulic pump 1 is for increasing the rigidity of the hydraulic control and stabilizing the bulk elasticity of the hydraulic oil, while the hydraulic pump 1 is rotating. This is because the charge pressure is for replenishing the hydraulic fluid that is insufficient in the main pipeline to prevent the occurrence of cavitation and the like. Moreover, it is because the load of the electric motor 6 that rotates the charge pump 5 can be reduced by setting the charge pressure when the hydraulic pump 1 is rotated to a lower value. In this case, the control device 10 changes the magnitude of the control current output to the relief valve 8 according to the rotational speed of the hydraulic pump 1, for example. Specifically, the control device 10 decreases the set pressure of the relief valve 8, that is, the charge pressure, as the rotational speed of the hydraulic pump 1 increases.

このように、油圧閉回路システム１００は、油圧ポンプ１の回転により管路Ｃ１及び管路Ｃ２のうちの一方の圧力がチャージ圧を下回った場合に、シャトル弁７を通じて作動油を補充する。すなわち、油圧閉回路システム１００は、管路Ｃ１及び管路Ｃ２のうちの一方における作動油の体積が減少した場合に、その体積変化分（圧縮容量分）を補うために、シャトル弁７を通じて作動油を供給する。   Thus, the hydraulic closed circuit system 100 replenishes hydraulic oil through the shuttle valve 7 when the pressure of one of the pipe C1 and the pipe C2 falls below the charge pressure due to the rotation of the hydraulic pump 1. That is, the hydraulic closed circuit system 100 operates through the shuttle valve 7 in order to compensate for the volume change (compression capacity) when the volume of hydraulic oil in one of the pipe C1 and the pipe C2 decreases. Supply oil.

以上の構成により、油圧閉回路システム１００は、高流量の作動油によるピストン３ａ（平面研削盤）の位置制御を実現でき、且つ、低流量の作動油によるピストン３ａ（平面研削盤）の微小位置制御を実現できる。   With the above configuration, the hydraulic closed circuit system 100 can realize the position control of the piston 3a (surface grinding machine) with a high flow rate of hydraulic fluid, and the minute position of the piston 3a (surface grinding machine) with the low flow rate of hydraulic fluid. Control can be realized.

以上、本発明の好ましい実施例について詳説したが、本発明は、上述した実施例に制限されることはなく、本発明の範囲を逸脱することなしに上述した実施例に種々の変形及び置換を加えることができる。   Although the preferred embodiments of the present invention have been described in detail above, the present invention is not limited to the above-described embodiments, and various modifications and substitutions can be made to the above-described embodiments without departing from the scope of the present invention. Can be added.

例えば、上述の実施例では、油圧閉回路システム１００は、油圧ポンプ１で油圧シリンダ３を駆動する構成であるが、油圧ポンプ１で油圧モータを駆動する構成であってもよい。   For example, in the above-described embodiment, the hydraulic closed circuit system 100 is configured to drive the hydraulic cylinder 3 with the hydraulic pump 1, but may be configured to drive the hydraulic motor with the hydraulic pump 1.

また、上述の実施例では、油圧閉回路システム１００は、大負荷容量油圧駆動式大型平面研削盤のテーブルを移動させるために用いられるが、射出成形機の射出シリンダや可動プラテンを移動するために用いられてもよく、他の工作機械の構成部品を移動するために用いられてもよい。   In the above-described embodiment, the hydraulic closed circuit system 100 is used for moving the table of the large load capacity hydraulically driven large surface grinder, but for moving the injection cylinder and the movable platen of the injection molding machine. It may be used to move other machine tool components.

１・・・油圧ポンプ １ａ・・・第一ポンプポート １ｂ・・・第二ポンプポート ２・・・電動モータ ３・・・油圧シリンダ ３ａ・・・ピストン ３ｂ・・・第一ポート ３ｃ・・・第二ポート ３Ｌ・・・第一油室 ３Ｒ・・・第二油室 ４Ｌ、４Ｒ・・・安全弁 ５・・・チャージポンプ ６・・・電動モータ ７・・・シャトル弁 ７ａ・・・一次側ポート ７ｂ、７ｃ・・・二次側ポート ８・・・リリーフ弁 ８ａ・・・一次側ポート ８ｂ・・・二次側ポート ９・・・センサ １０・・・制御装置 ２０・・・チェック弁 １００・・・油圧閉回路システム Ｔ１・・・タンク Ｃ１〜Ｃ１１・・・管路   DESCRIPTION OF SYMBOLS 1 ... Hydraulic pump 1a ... 1st pump port 1b ... 2nd pump port 2 ... Electric motor 3 ... Hydraulic cylinder 3a ... Piston 3b ... 1st port 3c ... 2nd port 3L ... 1st oil chamber 3R ... 2nd oil chamber 4L, 4R ... Safety valve 5 ... Charge pump 6 ... Electric motor 7 ... Shuttle valve 7a ... Primary side Port 7b, 7c ... Secondary side port 8 ... Relief valve 8a ... Primary side port 8b ... Secondary side port 9 ... Sensor 10 ... Control device 20 ... Check valve 100 ... Hydraulic closed circuit system T1 ... Tank C1-C11 ... Pipe

Claims (3)

第一ポート及び第二ポートを有する油圧シリンダ又は油圧モータを駆動可能な油圧閉回路システムであって、
第一管路を通じて前記第一ポートに流体的に連通される第一ポンプポートと第二管路を通じて前記第二ポートに流体的に連通される第二ポンプポートとを有する油圧ポンプと、
前記油圧ポンプの回転を制御する電動モータと、
１つの一次側ポートと２つの二次側ポートとを有するシャトル弁であり、該二次側ポートの一方が前記第一管路に流体的に連通され、該二次側ポートの他方が前記第二管路に流体的に連通されるシャトル弁と、
吐出ポートが前記シャトル弁の一次側ポートに流体的に連通されるチャージポンプと、
前記チャージポンプによるチャージ圧を設定圧とするリリーフ弁と、を備え、
前記チャージポンプは、前記シャトル弁を通じて前記第一管路及び前記第二管路を前記チャージ圧にする、
ことを特徴とする油圧閉回路システム。 A hydraulic closed circuit system capable of driving a hydraulic cylinder or hydraulic motor having a first port and a second port,
A hydraulic pump having a first pump port in fluid communication with the first port through a first conduit and a second pump port in fluid communication with the second port through a second conduit;
An electric motor for controlling the rotation of the hydraulic pump;
A shuttle valve having one primary port and two secondary ports, wherein one of the secondary ports is in fluid communication with the first conduit and the other of the secondary ports is the first port. A shuttle valve in fluid communication with the two conduits;
A charge pump whose discharge port is in fluid communication with the primary port of the shuttle valve;
A relief valve having a charge pressure by the charge pump as a set pressure,
The charge pump sets the first and second pipes to the charge pressure through the shuttle valve;
Hydraulic closed circuit system characterized by that. 前記チャージポンプは、前記油圧シリンダ又は前記油圧モータを作動油で駆動する前に、前記シャトル弁を通じて前記第一管路及び前記第二管路を前記チャージ圧にする、
ことを特徴とする請求項１に記載の油圧閉回路システム。 The charge pump, before driving the hydraulic cylinder or the hydraulic motor with hydraulic oil, the first pipe and the second pipe through the shuttle valve to the charge pressure;
The hydraulic closed circuit system according to claim 1. 前記リリーフ弁は、前記設定圧を変更可能である、
ことを特徴とする請求項１又は２に記載の油圧閉回路システム。 The relief valve can change the set pressure,
The hydraulic closed circuit system according to claim 1, wherein the hydraulic closed circuit system is provided.
JP2012023491A 2012-02-06 2012-02-06 Hydraulic closed circuit system Expired - Fee Related JP6009770B2 (en)

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