EP0439621B1 - Pressure oil feed circuit device for hydraulic cylinder of operation machine - Google Patents

Pressure oil feed circuit device for hydraulic cylinder of operation machine Download PDF

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Publication number
EP0439621B1
EP0439621B1 EP90912366A EP90912366A EP0439621B1 EP 0439621 B1 EP0439621 B1 EP 0439621B1 EP 90912366 A EP90912366 A EP 90912366A EP 90912366 A EP90912366 A EP 90912366A EP 0439621 B1 EP0439621 B1 EP 0439621B1
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EP
European Patent Office
Prior art keywords
pump
pressure
diameter piston
work implement
discharge passage
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.)
Expired - Lifetime
Application number
EP90912366A
Other languages
German (de)
French (fr)
Other versions
EP0439621A4 (en
EP0439621A1 (en
Inventor
Kiyoshi Kawasaki Fact. of K.K.K. S. SHIRAI
Teruo Kawasaki Fact. Of K.K.K. S. Akiyama
Shigeru Kawasaki Fact.Of K.K.K. S. Shinohara
Naoki Kawasaki Fact.Of K.K.K. S. Ishizaki
Takahide Kawasaki Fact.Of K.K.K. S. Takiguchi
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Komatsu Ltd
Original Assignee
Komatsu Ltd
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Publication date
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Publication of EP0439621A4 publication Critical patent/EP0439621A4/en
Application granted granted Critical
Publication of EP0439621B1 publication Critical patent/EP0439621B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
    • 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
    • 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
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, 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
    • F15B2211/20—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
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load 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
    • F15B2211/405—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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40561—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged upstream of the flow control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
    • F15B2211/50509—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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position
    • 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
    • F15B2211/7052—Single-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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • This invention relates to a hydraulic circuit apparatus for supplying fluid under pressure discharged by a hydraulic pump into hydraulic cylinders for actuating a work implement of a construction vehicle such as a power shovel or the like.
  • a hydraulic circuit apparatus arranged so as to supply fluid under pressure discharged by a hydraulic pump into hydraulic cylinders for a work implement through operating valves is heretofore well known.
  • EP-A-0 349 092 a hydraulic drive system is disclosed which may be operated in a normal mode and in a fine operation mode.
  • the discharge rate of a hydraulic pump is controlled to hold a differential pressure between a discharged pressure of the hydraulic pump and a load pressure of an actuator at a setting value.
  • the fine operation mode the flow rate supplied to the actuator at the same stroke of a control lever as that in the ordinary work is reduced to facilitate operation of the actuator at a finely adjusted speed for permitting fine operation with ease.
  • an instruction unit is only operated when the fine operation mode should be obtained.
  • the instruction unit is connected to a controller which operates a control force supplying device so arranged to apply a control force of a plunger to one end of a control valve.
  • the control valve is a part of the load-sensing control device and further comprises a drive part on the same side as the plunger and another drive part and spring on the side opposite to the plunger.
  • the control valve is used to connect a large-diameter pressure receiving portion of a regulator with a tank, with a discharge line of the pump or to connect this portion with both the tank and the discharge line at a ratio corresponding to the position of the control valve.
  • the regulator comprises a small-diameter pressure receiving portion connected to the discharge line of the pump.
  • the regulator is used for changing a swash plate of the pump and to thereby control the discharge rate of the pump and to hold the differential pressure at a setting value.
  • the present invention has for its object to provide a hydraulic circuit apparatus for supplying fluid under pressure into hydraulic cylinders for a work implement whereby stable operation of the working implement is also ensured during inching operation whereby the number of parts of the apparatus is decreased and the costs of manufacturing the apparatus is reduced.
  • the displacement regulating member of the variable displacement member of the variable displacement pump can be actuated in such a direction as to reduce the displacement of the pump by applying pushing forces to the load sensing valve so as to push its spool in such a direction as to communicate the discharge passage of the pump with the pressure receiving chamber of the large diameter piston.
  • the flow rate of fluid discharged by the variable displacement pump can be reduced, the amount of fluid under pressure to be supplied into the hydraulic cylinders for the work implement can be controlled finely to an extremely small amount so that the inching operational characteristic can be enhanced.
  • a variable displacement pump 2 driven by an engine 1 has a discharge passage 2a connected with inlets of a plurality of operating valves 3, whose outlet sides are connected by their respective conduits 4 with hydraulic cylinders 5 of work implements, respectively.
  • Each conduit 4 is provided with a pressure compensating valve 6.
  • the load pressures P LS in the conduits 4 are compared by a shuttle valve 7, and a higher load pressure P LS detected as a result of the comparison is introduced into spring chambers of the pressure compensating valves 6 so that the valves 6 may be set at a pressure corresponding to the higher load pressure P LS .
  • the fluid under pressure discharged by one variable displacement pump 2 can be supplied to the hydraulic cylinders 5 for work implement.
  • the displacement of fluid from the variable displacement pump 2 is controlled so that the difference between the discharge pressure P 1 and the load pressure P LS is always kept constant.
  • a displacement regulating member 8 of the variable displacement pump 2 is actuated by a large piston 9 in such a direction as to reduce the displacement, and by a small piston 10 in such a direction as to increase the displacement. Further, a pressure receiving chamber 9a of the large piston 9 is controlled to be selectively connected through a load sensing valve 11 either with a fluid tank or with the discharge passage 2a, and a pressure receiving chamber 10a of the small piston 10 is connected with the discharge passage 2a.
  • the above-mentioned load sensing valve 11 has a spool arranged to be pushed by the pressure in the discharge passage 2a; that is, the discharge pressure P 1 and the thrust created by a proportional position action electromagnetic solenoid 12 in such a direction as to incresed the area of its port communicating with the pressure receiving chamber 9a of the large piston 9, and also pushed by the outlet pressure in the operating valves 3; that is, the load pressure P LS in such a direction as to reduce the area of the port thereof communicating with the pressure receiving chamber 9a.
  • This load sensing valve 11 is arranged to effect control such that where the thrust created by the proportional position action electromagnetic solenoid 12 is zero, and when the difference between the discharge pressure P 1 and the load pressure P LS (P 1 - P LS ) is increased, the pressure in the pressure receiving chamber 9a of the large piston 9 is increased so as to actuate the displacement regulating member 8 in such a direction as to reduce the displacement to thereby reduce the discharge flow rate per one revolution to reduce the discharge pressure P 1 .
  • the spool of the load sensing valve 11 is pushed in such a direction as to increase the area of the port thereof communicating with the pressure receiving chamber 9a so as to increase the pressure in the chamber 9a of the large piston 9 regardless of the pressure between the discharge pressure P 1 and the load pressure P LS to move the displacement regulating member 8 in a direction to reduce the displacement, thereby reducing the flow rate of fluid per one revolution.
  • the pressure difference between the discharge pressure P 1 and the load pressure P LS is reduced by the thrust created by the proportional position action solenoid 12 so as to reduce the discharge flow rate of fluid from the variable displacement pump 12.
  • the above-mentioned proportional position action electromagnetic solenoid 12 is supplied with electric current from a controller 13, to which a mode signal from a mode change-over switch 14 is inputted.
  • a mode signal from a mode change-over switch 14 is inputted.
  • the proportional position action electromagnetic solenoid 12 is not supplied with electric current, whilst when an inching operation mode signal is inputted by the mode change-over switch 14 to the controller 13, the electromagnetic solenoid 12 is supplied with electric current.
  • the flow rate of fluid discharged by the variable displacement pump 2 becomes less than that in the normal operation, so that the flow rate of fluid to be supplied into the hydraulic cylinders 5 for work implement changes in proportion to the stroke of the operating valves 3 as shown by a dotted line "A" in Fig. 2 and becomes less than the flow rate of fluid in the normal operation as shown by a solid line B in Fig. 2, thus rendering it possible to effect fine control of the amount of fluid supplied into the hydraulic cylinders 5 for the work implement to improve the inching operation characteristic.
  • Fig. 3 shows the second embodiment of the present invention.
  • a pilot pump 15 is driven by an engine 1, and a discharge passage 15a of the pump 15 is connected through a change-over valve 16 with a pressure receiving section 11a of a load sensing valve 11.
  • the change-over valve 16 is arranged to be kept at its shut-off position I by the resilient force of a spring mounted therein, and also kept at its communicating position II when its solenoid 16 is energized.
  • the solenoid 16 is supplied with electric current from a power supply through a mode change-over switch 14 and the controller 13.
  • a change-over valve 16 is changed over to its communicating position II so that the pilot fluid under pressure from a pilot pump 15 is supplied into a pressure receiving section 11a of a load sensing valve 11, and as a result, its spool is pushed in such a direction as to increase the area of the port thereof communicating with pressure receiving chamber 9a of a large piston 9, thereby reducing the amount of fluid discharged by a variable displacement pump 2.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

This invention intends to provide a pressure oil feed circuit device for a hydraulic cylinder of an operation machine which can control a pump discharge flow rate so that the difference between a pump discharge pressure and a load pressure becomes constant during the normal operation of the operation machine and can control the discharge flow rate of the pump so as to decrease it during the fine operation of the operation machine. The pressure oil feed circuit device includes a larger diameter piston (9) for operating the capacity regulation member (8) of a variable capacity pump (2) in such a direction as to reduce the pump capacity; a smaller diameter piston (10) for operating the capacity regulation member (8) of the variable capacity pump (2) in such a direction as to increase the pump capacity, the smaller diameter piston (10) having a small diameter piston pressure receiving chamber (10a) connected to the pump discharge passage (2a); a load sensing valve (11) for establishing/cutting off communication between the pressure receiving chamber (9a) of the larger diameter piston and the pump discharge passage; and means (12, 13, 14) for providing the load sensing valve with a push force exerted in the direction of establishing communication between the pump discharge passage (2a) and the larger diameter piston pressure receiving chamber (9a).

Description

    TECHNICAL FIELD OF THE INVENTION
  • This invention relates to a hydraulic circuit apparatus for supplying fluid under pressure discharged by a hydraulic pump into hydraulic cylinders for actuating a work implement of a construction vehicle such as a power shovel or the like.
    • BACKGROUND ART OF THE INVENTION
  • A hydraulic circuit apparatus arranged so as to supply fluid under pressure discharged by a hydraulic pump into hydraulic cylinders for a work implement through operating valves is heretofore well known.
  • In case of conducting earth scraping-off operation and slope correcting operation by a power shovel, it is necessary to perform inching operation of the work implement of the power shovel. This inching operation of the work implement is achieved by supplying extremely small amounts of fluid under pressure discharged by a hydraulic pump into hydraulic cylinders for the work implement.
  • However, it is quite difficult to control finely the amount of fluid under pressure to be supplied into the hydraulic cylinders for the work implement and it is also quite difficult to inch the work implement as desired. As a result the operational accuracy in earth scapping-off operation and slope correcting operation becomes low.
  • One solution to overcome the problems involved in inching operation is given in EP-A-0 349 092, which application was published after the priority date of the present application.
  • In EP-A-0 349 092 a hydraulic drive system is disclosed which may be operated in a normal mode and in a fine operation mode. In the normal mode the discharge rate of a hydraulic pump is controlled to hold a differential pressure between a discharged pressure of the hydraulic pump and a load pressure of an actuator at a setting value. In the fine operation mode the flow rate supplied to the actuator at the same stroke of a control lever as that in the ordinary work is reduced to facilitate operation of the actuator at a finely adjusted speed for permitting fine operation with ease. According to one embodiment of EP-A-0 349 092 an instruction unit is only operated when the fine operation mode should be obtained. The instruction unit is connected to a controller which operates a control force supplying device so arranged to apply a control force of a plunger to one end of a control valve. The control valve is a part of the load-sensing control device and further comprises a drive part on the same side as the plunger and another drive part and spring on the side opposite to the plunger.
  • The control valve is used to connect a large-diameter pressure receiving portion of a regulator with a tank, with a discharge line of the pump or to connect this portion with both the tank and the discharge line at a ratio corresponding to the position of the control valve.
  • Further, the regulator comprises a small-diameter pressure receiving portion connected to the discharge line of the pump. The regulator is used for changing a swash plate of the pump and to thereby control the discharge rate of the pump and to hold the differential pressure at a setting value.
    • SUMMARY OF THE INVENTION
  • The present invention has for its object to provide a hydraulic circuit apparatus for supplying fluid under pressure into hydraulic cylinders for a work implement whereby stable operation of the working implement is also ensured during inching operation whereby the number of parts of the apparatus is decreased and the costs of manufacturing the apparatus is reduced.
  • To achieve the above-mentioned object a hydraulic circuit apparatus according to claims 1 or 3 is provided.
  • Further features for advantageous embodiments of the invention are disclosed by the subclaims.
  • According to the present invention incorporating the above-mentioned aspects, since the flow rate of fluid discharged by the variable displacement pump is controlled in such a manner that the difference between the discharge pressure of the pump and the load pressure is always kept constant, a stable operation of the work implement is ensured, and also during inching operation of the work implement the displacement regulating member of the variable displacement member of the variable displacement pump can be actuated in such a direction as to reduce the displacement of the pump by applying pushing forces to the load sensing valve so as to push its spool in such a direction as to communicate the discharge passage of the pump with the pressure receiving chamber of the large diameter piston. Accordingly, since during inching operation of the work implement the flow rate of fluid discharged by the variable displacement pump can be reduced, the amount of fluid under pressure to be supplied into the hydraulic cylinders for the work implement can be controlled finely to an extremely small amount so that the inching operational characteristic can be enhanced.
  • The above-mentioned and other objects, aspects and advantages of the present invention will become apparent to those skilled in the art when reference is made to the following description and the accompanying drawings in which preferred embodiments incorporating the principles of the present invention are shown by way of example only.
    • BRIEF DESCRIPTION OF THE DRAWINGS
    • Fig. 1 is a hydraulic circuit diagram showing a first embodiment of the present invention;
    • Fig. 2 is a graph showing the relationship between the flow rate of fluid under pressure supplied into hydraulic cylinders for a work implement and the stroke of an operating valve associated therewith; and
    • Fig. 3 is a hydraulic circuit diagram showing a second embodiment of the present invention.
    DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
  • The present invention will now be described in detail below by way of several preferred embodiments thereof with reference to the accompanying drawings.
  • Referring first to Figs. 1 and 2, the first embodiment of the present invention is described.
  • A variable displacement pump 2 driven by an engine 1 has a discharge passage 2a connected with inlets of a plurality of operating valves 3, whose outlet sides are connected by their respective conduits 4 with hydraulic cylinders 5 of work implements, respectively. Each conduit 4 is provided with a pressure compensating valve 6. The load pressures PLS in the conduits 4 are compared by a shuttle valve 7, and a higher load pressure PLS detected as a result of the comparison is introduced into spring chambers of the pressure compensating valves 6 so that the valves 6 may be set at a pressure corresponding to the higher load pressure PLS.
  • By so doing, the fluid under pressure discharged by one variable displacement pump 2 can be supplied to the hydraulic cylinders 5 for work implement.
  • The displacement of fluid from the variable displacement pump 2 is controlled so that the difference between the discharge pressure P1 and the load pressure PLS is always kept constant.
  • Stating more specifically, a displacement regulating member 8 of the variable displacement pump 2 is actuated by a large piston 9 in such a direction as to reduce the displacement, and by a small piston 10 in such a direction as to increase the displacement. Further, a pressure receiving chamber 9a of the large piston 9 is controlled to be selectively connected through a load sensing valve 11 either with a fluid tank or with the discharge passage 2a, and a pressure receiving chamber 10a of the small piston 10 is connected with the discharge passage 2a.
  • The above-mentioned load sensing valve 11 has a spool arranged to be pushed by the pressure in the discharge passage 2a; that is, the discharge pressure P1 and the thrust created by a proportional position action electromagnetic solenoid 12 in such a direction as to incresed the area of its port communicating with the pressure receiving chamber 9a of the large piston 9, and also pushed by the outlet pressure in the operating valves 3; that is, the load pressure PLS in such a direction as to reduce the area of the port thereof communicating with the pressure receiving chamber 9a. This load sensing valve 11 is arranged to effect control such that where the thrust created by the proportional position action electromagnetic solenoid 12 is zero, and when the difference between the discharge pressure P1 and the load pressure PLS (P1 - PLS) is increased, the pressure in the pressure receiving chamber 9a of the large piston 9 is increased so as to actuate the displacement regulating member 8 in such a direction as to reduce the displacement to thereby reduce the discharge flow rate per one revolution to reduce the discharge pressure P1. Whilst, where the thrust created by the solenoid 12 is zero, and when the difference between the discharge pressure P1 and the load pressure PLS (P1 - PLS) is reduced, the pressure in the pressure receiving chamber 9a of the large piston 9 is reduced so as to actuate the displacement regulating member 8 in such a direction as to increase the displacement to thereby increase the discharge flow rate per one revolution to incresae the discharge pressure P1, whereby controlling the displacement of fluid from the variable displacement pump 2 so that the difference between the discharge pressure P1 and the load pressure PLS (P1 - PLS) may always be kept constant. Further, when a thrust is created by the proportion position action electromagnetic solenoid 12, the spool of the load sensing valve 11 is pushed in such a direction as to increase the area of the port thereof communicating with the pressure receiving chamber 9a so as to increase the pressure in the chamber 9a of the large piston 9 regardless of the pressure between the discharge pressure P1 and the load pressure PLS to move the displacement regulating member 8 in a direction to reduce the displacement, thereby reducing the flow rate of fluid per one revolution.
  • Stating in brief, the pressure difference between the discharge pressure P1 and the load pressure PLS is reduced by the thrust created by the proportional position action solenoid 12 so as to reduce the discharge flow rate of fluid from the variable displacement pump 12.
  • The above-mentioned proportional position action electromagnetic solenoid 12 is supplied with electric current from a controller 13, to which a mode signal from a mode change-over switch 14 is inputted. When a normal mode signal is inputted by the mode change-over switch 14 to the controller 13, the proportional position action electromagnetic solenoid 12 is not supplied with electric current, whilst when an inching operation mode signal is inputted by the mode change-over switch 14 to the controller 13, the electromagnetic solenoid 12 is supplied with electric current.
  • Such being the arrangement, during inching of the work implement, the flow rate of fluid discharged by the variable displacement pump 2 becomes less than that in the normal operation, so that the flow rate of fluid to be supplied into the hydraulic cylinders 5 for work implement changes in proportion to the stroke of the operating valves 3 as shown by a dotted line "A" in Fig. 2 and becomes less than the flow rate of fluid in the normal operation as shown by a solid line B in Fig. 2, thus rendering it possible to effect fine control of the amount of fluid supplied into the hydraulic cylinders 5 for the work implement to improve the inching operation characteristic.
  • Fig. 3 shows the second embodiment of the present invention. In this embodiment, a pilot pump 15 is driven by an engine 1, and a discharge passage 15a of the pump 15 is connected through a change-over valve 16 with a pressure receiving section 11a of a load sensing valve 11. The change-over valve 16 is arranged to be kept at its shut-off position I by the resilient force of a spring mounted therein, and also kept at its communicating position II when its solenoid 16 is energized. The solenoid 16 is supplied with electric current from a power supply through a mode change-over switch 14 and the controller 13.
  • Further, the component parts shown in Fig. 3 with the same reference numerals as those used in the first embodiment shown in Fig. 1 are the same component parts, and therefore description of them is omitted herein to avoid duplication of explanation.
  • In the second embodiment shown in Fig. 3, when a mode change-over switch 14 is located at its inching operation mode position so as to input an inching operation mode signal from the switch 14 to a controller 13 and send an electric current to a solenoid 16a, thereby energizing the same, a change-over valve 16 is changed over to its communicating position II so that the pilot fluid under pressure from a pilot pump 15 is supplied into a pressure receiving section 11a of a load sensing valve 11, and as a result, its spool is pushed in such a direction as to increase the area of the port thereof communicating with pressure receiving chamber 9a of a large piston 9, thereby reducing the amount of fluid discharged by a variable displacement pump 2.

Claims (4)

  1. A hydraulic circuit apparatus for supplying fluid under pressure into a plurality of hydraulic cylinders (5) for a work implement arranged so as to connect a discharge passage (2a) of a variable displacement pump (2) through operating valves (3) with the cylinders for the work implement, said apparatus comprising:
    a large diameter piston (9) for actuating a displacement regulating member (8) of said variable displacement pump (2) in such a direction as to reduce the displacement of the pump;
    a small diameter piston (10) having a pressure receiving chamber (10a) connected with said discharge passage (2a) of the pump and adapted to actuate the displacement regulating member (8) of said pump in such a direction as to increase the displacement of the pump (2);
    a load sensing valve (11) adapted to connect or disconnect a pressure receiving chamber (9a) of said large diameter piston (9) with or from the discharge passage (2a) of said pump (2);
    means (12, 13, 14) for applying pushing forces to the load sensing valve (11) so as to push its spool in such a direction as to communicate the discharge passage (2a) of said pump (2) with the pressure receiving chamber (9a) of said large diameter piston (9);
    pressure compensating valves (6) interposed between said hydraulic cylinders (5) for a work implement and said operating valves (3); and
    a shuttle valve (7) for comparing load pressures (PLS) in the output conduits (4) of said pressure compensating valves (6) to introduce a higher load pressure into a pressure receiving section provided on one side of said load sensing valve (11),
    wherein during normal operation of the work implement the flow rate of fluid discharged by the pump (2) is controlled in such a manner that the difference between the discharge pressure (P1) of the pump (2) and the load pressure (PLS) is always kept constant, whilst during inching operation of the work implement the flow rate of the fluid discharged by the pump (2) is reduced.
  2. A hydraulic circuit apparatus according to claim 1, characterized in that said pushing force applying means (12, 13, 14) comprises:
    a proportional position action electromagnetic solenoid (12) provided on one side of said load sensing valve (11) ;
    a mode change-over switch (14) for the electromagnetic solenoid (12); and
    a controller (13) adapted to receive an inching operation mode signal transmitted by the mode change-over switch (14) and to send an electric current to said electromagnetic solenoid (12).
  3. A hydraulic circuit apparatus for supplying fluid under pressure into a plurality of hydraulic cylinders (5) for a work implement arranged so as to connect a discharge passage (2a) of a variable displacement pump (2) through operating valves (3) with the cylinders (5) for the work implement, said apparatus comprising:
    a large diameter piston (9) for actuating a displacement regulating member (8) of said variable displacement pump (2) in such a direction as to reduce the displacement of the pump;
    a small diameter piston (10) having a pressure receiving chamber (10a) connected with said discharge passage (2a) of the pump (2) and adapted to actuate the displacement regulating member (8) of said pump in such a direction as to increase the displacement of the pump;
    a load sensing valve (11) adapted to connect or disconnect a pressure receiving chamber (9a) of said large diameter piston (9) with or from the discharge passage (2a) of said pump (2); and
    a means (13, 14, 15, 16, 16a) for applying pushing forces to the load sensing valve (11) so as to push its spool in such a direction as to communicate the discharge passage (2a) of said pump (2) with the pressure receiving chamber (9a) of said large diameter piston (9),
    wherein during normal operation of the work implement a flow rate of fluid discharged by the pump (2) is controlled in such a manner that the difference between the discharge pressure (P1) of the pump (2) and load pressure (PLS) is always kept constant, whilst during inching operation of the work implement the flow rate of fluid discharged by the pump (2) is reduced; and
    said pushing force applying means (13, 14, 15, 16, 16a) comprises:
    a pilot pump (15);
    a conduit (15a) for introducing pilot fluid under pressure discharged by the pilot pump (15) into a pressure receiving section (lla) provided on one side of said load sensing valve (11);
    a change-over valve (16) provided in the conduit (15a);
    a proportional position action electromagnetic solenoid (16a) provided on one side of the change-over valve (16);
    a mode change-over switch (14) for the electromagnetic solenoid (16a), and
    a controller (13) adapted to receive an inching operation mode signal transmitted by the mode change-over switch (14) and to send an electric current to said electromagnetic solenoid (16a).
  4. Hydraulic circuit apparatus according to claim 3, characterized in that pressure compensating valves (6) are interposed between said hydraulic cylinders (5) for a work implement and said operating valves (3) and a shuttle valve (7) is provided for comparing load pressures in the output conduits (4) of said pressure compensating valves (6) to introduce a higher load pressure into a pressure receiving section provided on one side of said load sensing valve (11).
EP90912366A 1989-08-16 1990-08-16 Pressure oil feed circuit device for hydraulic cylinder of operation machine Expired - Lifetime EP0439621B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP1210053A JPH0374605A (en) 1989-08-16 1989-08-16 Pressure oil feeder for working machine cylinder
JP210053/89 1989-08-16
PCT/JP1990/001050 WO1991002904A1 (en) 1989-08-16 1990-08-16 Pressure oil feed circuit device for hydraulic cylinder of operation machine

Publications (3)

Publication Number Publication Date
EP0439621A1 EP0439621A1 (en) 1991-08-07
EP0439621A4 EP0439621A4 (en) 1993-04-28
EP0439621B1 true EP0439621B1 (en) 1996-10-16

Family

ID=16583031

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90912366A Expired - Lifetime EP0439621B1 (en) 1989-08-16 1990-08-16 Pressure oil feed circuit device for hydraulic cylinder of operation machine

Country Status (5)

Country Link
EP (1) EP0439621B1 (en)
JP (1) JPH0374605A (en)
KR (1) KR920701692A (en)
DE (1) DE69028913T2 (en)
WO (1) WO1991002904A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008054876A1 (en) 2008-12-18 2010-07-01 Deere & Company, Moline hydraulic system
DE102008054880A1 (en) 2008-12-18 2010-07-01 Deere & Company, Moline hydraulic system

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2651079B2 (en) * 1991-07-24 1997-09-10 日立建機株式会社 Hydraulic construction machinery
JP3064574B2 (en) * 1991-09-27 2000-07-12 株式会社小松製作所 Working oil amount switching control device for hydraulic excavator
JP2568507Y2 (en) * 1991-09-27 1998-04-15 株式会社小松製作所 Fine operation mode control device for construction machinery
DE4210252C1 (en) * 1992-03-28 1993-09-02 O & K Orenstein & Koppel Ag, 13581 Berlin, De
DE4313597B4 (en) * 1993-04-26 2005-09-15 Linde Ag Method of operating an adjustable hydrostatic pump and hydrostatic drive system adapted therefor
JP3477687B2 (en) * 1993-11-08 2003-12-10 日立建機株式会社 Flow control device
GB2311385B (en) * 1996-03-23 2000-07-19 Trinova Ltd A fluid power control circuit
DE19930618A1 (en) * 1999-07-02 2001-01-04 Mannesmann Rexroth Ag Hydraulic control arrangement for supplying pressure medium to preferably several hydraulic consumers
JP2012092670A (en) * 2010-10-25 2012-05-17 Kanzaki Kokyukoki Manufacturing Co Ltd Pump unit
DE102013216395B4 (en) 2013-08-19 2019-01-17 Danfoss Power Solutions a.s. CONTROL DEVICE FOR HYDRAULIC ADJUSTING PUMPS AND ADJUSTING PUMP WITH A CONTROL DEVICE
WO2020067084A1 (en) 2018-09-26 2020-04-02 イーグル工業株式会社 Fluid circuit

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4487018A (en) * 1982-03-11 1984-12-11 Caterpillar Tractor Co. Compensated fluid flow control

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5969505A (en) * 1982-10-14 1984-04-19 Daikin Ind Ltd Cavitation preventing circuit
DE3713824A1 (en) * 1987-04-24 1988-11-03 Rexroth Mannesmann Gmbh Valve arrangement

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4487018A (en) * 1982-03-11 1984-12-11 Caterpillar Tractor Co. Compensated fluid flow control

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008054876A1 (en) 2008-12-18 2010-07-01 Deere & Company, Moline hydraulic system
DE102008054880A1 (en) 2008-12-18 2010-07-01 Deere & Company, Moline hydraulic system

Also Published As

Publication number Publication date
KR920701692A (en) 1992-08-12
DE69028913T2 (en) 1997-02-13
DE69028913D1 (en) 1996-11-21
WO1991002904A1 (en) 1991-03-07
JPH0374605A (en) 1991-03-29
EP0439621A4 (en) 1993-04-28
EP0439621A1 (en) 1991-08-07

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