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WO2005024246A1 - Unite d'entrainement d'engins de travaux - Google Patents

Unite d'entrainement d'engins de travaux Download PDF

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Publication number
WO2005024246A1
WO2005024246A1 PCT/JP2004/003220 JP2004003220W WO2005024246A1 WO 2005024246 A1 WO2005024246 A1 WO 2005024246A1 JP 2004003220 W JP2004003220 W JP 2004003220W WO 2005024246 A1 WO2005024246 A1 WO 2005024246A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid pressure
cylinder
motor
pressure pump
pump
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.)
Ceased
Application number
PCT/JP2004/003220
Other languages
English (en)
Japanese (ja)
Inventor
Masatoshi Miki
Nobuaki Matoba
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.)
Caterpillar Japan Ltd
Caterpillar Mitsubishi Ltd
Original Assignee
Caterpillar Mitsubishi Ltd
Shin Caterpillar Mitsubishi 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 Caterpillar Mitsubishi Ltd, Shin Caterpillar Mitsubishi Ltd filed Critical Caterpillar Mitsubishi Ltd
Publication of WO2005024246A1 publication Critical patent/WO2005024246A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • 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
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • 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
    • E02F9/2221—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
    • E02F9/2285—Pilot-operated systems
    • 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
    • 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
    • F15B11/17—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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/20561—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
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • 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
    • F15B2211/20584—Combinations of pumps with high and low 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
    • F15B2211/27—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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional 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
    • F15B2211/405—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
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure 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
    • F15B2211/60—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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel
    • 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
    • F15B2211/75—Control of speed of the 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members

Definitions

  • the present invention relates to the drive of a working machine such as a hydraulic shovel.
  • Fig. 3 is a diagram of the structure of the hydraulic shovel as a working machine.
  • Fig. 4 is a conventional document that operates the hydraulic shovel.
  • FIG. 2 is a circuit diagram showing a configuration of the hydraulic system of FIG.
  • the upper revolving structure 2 is rotatably rotatably mounted on the lower traveling structure 1, and is swingably mounted on the upper revolving structure 2 and the upper revolving structure 2.
  • Cylinder 4a Note Cylinder
  • the remote valve 12 is operated to switch the control valve 11 and is driven by the fan 7 and the fan 7.
  • the hydraulic pump 11 is used to control the hydraulic pump.
  • each of the actuating units such as the boom cylinder V adam cylinder 4a and the socket cylinder 5a Due to the distribution to the data, the throttle loss at the control knob 11 is large, which is disadvantageous in terms of fuel consumption and production costs.
  • a plurality of actuators such as a bumper cylinder 3a, an arm cylinder V4a, and a socket cylinder 5a are connected in series.
  • the operation is difficult, and the load interferes with the operation.
  • the operation is difficult and there is a problem with the operation.
  • the load on the hydraulic pump side is low, the electric energy generated by the generator can be stored in the ⁇ V te, and when the load on the hydraulic pump side is high,
  • the power and electric power generated by the battery was used to drive the generator as an electric motor, and the torque was applied to a hydraulic pump to provide a pump and a pump.
  • there is also a need to save energy for example,
  • the hydraulic pressure of the hydraulic pump which is driven by the engine, is distributed to the plurality of hydraulic actuators by operating the n-type lubricator.
  • the hydraulic oil of the hydraulic pump is squeezed at the inlet port and is distributed to each actuator.
  • several hydraulic actuators are linked to each other, because problems such as reduction of fuel consumption and noise are considered.
  • Field P ⁇ There is a problem that the operation is difficult due to significant load interference.
  • the present invention has been made in view of the above points, and it is an object of the present invention to provide a drive device for a work machine capable of supplying an optimum power according to a load. It is what it is. Opening of the invention
  • the driving machine of the working machine of the present invention is a hydraulic pressure pump that is provided with a fluid pressure pump that performs variable displacement control of a fluid pressure pump that is regulated by a variable capacity means.
  • the closed circuit for controlling the operation speed of the tuner and the variable capacity means for regulating the flow of the fluid pressure pump in this closed circuit are different from the variable capacity means. Control of the capacity of the fluid pump to be adjusted and the control of the working fluid supplied from the fluid pump.
  • One inlet and one outlet. The fluid connected to the controller by the flow control by the non-snorp installed in parallel with the no-re-no-rep.
  • the pressure actuator The hydraulic fluid in the open circuit and the circuit that controls the operating speed of the pump
  • the hydraulic fluid in the pump is closed And a distribution circuit for distributing the fluid to the cut-out circuit, and the fluid pressure of the closed circuit is controlled by the variable capacity control of the fluid pressure pump in the closed circuit. Since a static pressure drive system that controls the speed of the actuator is used, there is a significant reduction in throttling due to the use of the system's ⁇ -one contact knob. In addition, since the brake power of the closed-circuit fluid pressure actuator is operated by the load, the energy efficiency can be greatly improved. In addition, the amount of heat generated by the working fluid due to throttling loss is smaller than that of the conventional system, so that the cooling device can be downsized. Open circuit fluid pressure pump Can be distributed to the body pressure actuator in the closed circuit. ⁇ The fluid pressure pump in the closed circuit can be reduced in size, and the pump clothing can be used. Easy to do, lower cost
  • the fluid pressure actuator for each circuit is unique.
  • the pump can be driven by the body pressure pump, and the working fluid is distributed from the body pressure pump to the closed circuit fluid body as needed.
  • the drive device of the work machine includes a boom operated by a boom cylinder, a boom operated by a boom cylinder, and a vehicular cylinder.
  • a working machine equipped with a working device in which a socket operated by a head cylinder is sequentially connected to a socket and
  • the first variable capacity • The variable capacity control of the first fluid pressure pump whose flow rate is adjusted by S
  • the first closing circuit for controlling the operating speed of the boom cylinder connected to the first fluid pressure pump is different from the first variable variable means described above.
  • the second fluid pressure pump whose flow rate is adjusted by the second fluid volume control means, is in contact with this second fluid pressure pump by the variable capacity control of the fluid pressure pump.
  • Variable capacity control of the third fluid pressure pump whose flow rate is regulated by the third fluid pressure pump and supplied from this third fluid pressure pump
  • the control of the supplied working fluid is achieved by the control of the flow rate by means of a flow control by means of a pipe snub which is placed in parallel with this control.
  • An Is circuit that controls the operating speed of the non-contact cylinder that is in contact with the unit, and the operation of the third fluid pressure pump in the circuit And a distribution circuit for distributing the fluid to the boom cylinder.
  • the second hydraulic pump uses a hydrostatic drive ft system, which controls the operating speed of the boom cylinder pump cylinder with variable control. Since it is used, the loss of a squeezer due to the conventional system's control port can be greatly reduced, and it is also possible to use a B Since the brake power can be recovered when the cylinder is operated ft by the load, the energy efficiency can be greatly improved. As compared with the above, the heat generated by the working fluid is reduced due to the throttle V loss, so that the cooling device can be miniaturized and the second cylinder cylinder can be used.
  • the first fluid pressure pump for the V-cushion ⁇ The second body pressure pump can be downsized, these pumps can be easily removed, and the pump can be lowered.
  • the cylinder for each circuit is independent It can be moved by a hydraulic pump. And it is necessary to distribute the working fluid from the third fluid pressure pump for the nozzle cylinder to the Bumushi V damper cylinder. Therefore, compared to the conventional system, it is possible to reduce the load interference and improve the operability.
  • the drive garment of the work machine of the present invention is an electric motor that has both functions of a motor and a generator, which is separated by the drive unit of the engine.
  • the surplus power of the generator and the engine • Electricity generated by the generator and electric power generated by the power of the Boom Vinder and the bumper cylinder • Electricity generated by the generator
  • the electric motor is driven by the electric power discharged from the battery. It is equipped with a charge / discharge circuit for assisting power, and when the Boom V and the A / C cylinder are operated by a load. Electric power is used for the electric power.
  • the surplus power generated by the power generator is Fill the charging / discharging circuit
  • the drive of the work machine of the present invention is
  • the speed of the conventional system is reduced. Squeeze with one renole. This greatly reduces the loss and recovers the braking force when the fluid pressure actuator in the closed circuit is activated by the load. In addition, the energy efficiency has been greatly improved and the system has been narrowed down compared to conventional systems. Since the working fluid generates less heat, the cooling device can be downsized and the flow rate of the hydraulic pump in the circuit closed.
  • ⁇ -Distributing to the fluid pressure actuators on the road can be easily performed.
  • the fluid pressure pump in the closed circuit can be reduced in size, and the pump can be mounted easily. If the stake is lowered, the stake can be reduced.
  • Multiple fluid pressure functions The fluid pressure actuator of each circuit can be driven by a unique fluid pressure pump, and the fluid pressure of the open circuit can be changed as needed. Since pressure oil is supplied from the pump to the fluid pressure actuator in the closed circuit, load interference is reduced as compared with the conventional system. Then, the interlocking operation can be easily performed.
  • the drive of the work machine includes a boom operated by a boom cylinder, a boom operated by a boom cylinder, and a dynamo.
  • a work machine provided with a work station in which buckets operated by a bucket cylinder are sequentially connected, the rotation speed of the first motor is controlled.
  • the flow rate of the first hydraulic pump in contact with the first motor is adjusted to P, and the flow rate of the first hydraulic pump is adjusted to P, so that the pump is in contact with the first hydraulic pump.
  • the second closed circuit to be controlled is connected to the third motor by controlling the speed of rotation of a third motor different from the first motor and the second motor.
  • the rotation speed of the third hydraulic pump is controlled and provided from the third hydraulic pump.
  • the working fluid is supplied to the control valve and the HX-mounted diaper valve in parallel with the control valve.
  • Open circuit that controls the operation speed of the bucket cylinder, which is controlled by the inlet 1 to the knurl, and the hydraulic pump of the whistle 3 of this circuit.
  • a distributing circuit for distributing the working fluid of the first embodiment to the bobbin cylinder. From the pump ⁇ Since the operating speed of the bumper and the amp V-Vinder is controlled by controlling the rotational speed of the second fluid pressure pump, the conventional system This significantly reduces the throttle loss caused by the unit's control and reduces the number of throttles that can be actuated by the load.
  • the working fluid of the working fluid Since the heat generation is small, the cooling unit can be downsized.
  • the flow rate of the third fluid pressure pump for the packet cylinder is controlled by the The first fluid pressure pin for the bumper cylinder and for the damper is allocated to the V and V cylinders.
  • the electric motor and the second hydraulic pump are smaller than the second hydraulic pump. These pumps make the motor easier and lower the cost. If the Boom Cinder, Arm Cylinder, and Voke V Cinder are operated dynamically, the cylinder for each circuit will be used independently. It can be driven by a hydraulic pump and, if necessary, from a third hydraulic pump for the nozzle cylinder to a boom cylinder and an amm cylinder. Pressure Since oil is supplied, load interference is reduced compared to the conventional system. ⁇ Interlocking operation can be facilitated.
  • the drive of the work machine of the present invention is a small number of the first lightning thrusters.
  • the second motor has the function of a motor and is driven by an engine to be driven by the first motor.
  • a generator that supplies power to the second and third motors, the surplus power from the generators and the brake power of the Bumshinda and Amushinda
  • the generator has a first electric motor having a blindfold and a charge / discharge circuit for charging / discharging the electric power generated by the second electric motor to a battery.
  • the generator generates a braking force that indicates that the binder or the amplifier has been actuated by a load.
  • the power recovered by the action or the surplus power generated at low load is charged to the battery V of the charging / discharging circuit, and the power is supplied from the battery at high load. Since the engine output is smoothed, it is possible to reduce the size of the engine as compared to the conventional system, and to reduce the engine output.
  • FIG. 1 is a hydraulic circuit diagram showing an embodiment of a drive device for a work machine according to the present invention
  • FIG. 2 is another embodiment of a drive device for a work machine according to the present invention
  • FIG. 3 is a hydraulic circuit diagram showing the configuration of the hydraulic machine as a working machine
  • FIG. 4 is a side view showing the a-shavel
  • FIG. 4 is a hydraulic circuit diagram showing a hydraulic system for operating the conventional hydraulic shovel. The best mode for carrying out the invention is shown in FIG.
  • a power transmission device 20 for distributing the power of the engine 7 is connected to the engine 7 which is a power source, and the power transmission device 20 is connected to the power transmission device 20.
  • Bi-tilt type variable displacement as first fluid pressure pump for driving a boom cylinder ⁇ a as first fluid pressure actuator Hydraulic pump 21 and a second hydraulic pump for driving the damper cylinder 4a as a second hydraulic pressure actuator.
  • Double tilt type variable displacement hydraulic pressure The third pump 22 and the one-sided tilt as the third fluid pressure pump for driving the packet cylinder 5a as the third fluid pressure actuator
  • a hydraulic variable pressure pump 23 of a rollable variable displacement type is mounted on each.
  • 22 23 include the first and second needles and the first, second and third swash plate control devices 21a for controlling the tilt angle of the swash plate as the third capacity variable means. , 22a,, 23a Force S
  • Each of the hydraulic pumps 23 has a first and a second hydraulic pump 24 to which a charge pump 24 is connected.
  • the pump 2122 pumps the excess oil out of the hydraulic oil as a working fluid that also functions as a hydraulic motor when it receives the supply of hydraulic oil.
  • the flushing valve 25 for discharging to the 42, the low-pressure reflex valve 26 for holding the low-pressure side pressure, and the cylinder dropping operation
  • the vane valve 45 mounted on the boom cylinder 3a is constituted by the valve and the leaf valve 29a, 29b.
  • the knockout unit 46 provided on the drum cylinder 4a has the same flame V-single as the knockout unit 45 on the bumper cylinder 3a.
  • the knob 30 the low-pressure relief valve 31, the electromagnetic switching valves 32 a, 32 b, the check valve 33 for preventing the load, and the one-piece relief valves 34 a, 34 b. Is configured 4 and the first closed circuit to the boom cylinder 3a.
  • the first closed circuit A adjusts the flow rate by the first swash plate control device 21a, that is, the hydraulic pump in the swash plate control of the hydraulic pump 21 that is variably controlled. It controls the operation speed of the Poom cylinder 3a connected to the pump 21.
  • This second closed circuit B is controlled by a swash plate control of a hydraulic pump 22 whose flow rate is adjusted by a second swash plate control device 22 a, that is, a variable displacement control. It controls the operation speed of the arm cylinder 4a connected to the pump 22.
  • an open circuit C is provided for the Ket cylinder 5a.
  • the open circuit C is controlled by a third swash plate control device 23 a to adjust the flow rate, that is, to control the swash plate of the hydraulic pump 23 whose capacity is variably controlled, and the hydraulic pump 23.
  • 2 3 Control device for controlling hydraulic oil supplied from 3 to 3 5 and the BX in parallel with this control port
  • the flow rate control by the knob 62 controls the operating speed of the bucket V to V5a connected to the control knob 35.
  • the hydraulic pressure of the hydraulic pump 23 is distributed to the bumper V3a and the arm cylinder 4a from the pump side force. 5
  • the circuit -D is branched, and the check valves 36 and 38 and the hydraulic oil of the hydraulic pump 23 are supplied to the distribution circuit D of the
  • Magnetic proportional changeover valve 37 for supplying to 3a and + magnetic proportional changeover valve 39 for supplying the hydraulic oil of hydraulic pump 23 to damper cylinder 4a are provided 1 It has been.
  • the discharge line of the charge pump 24 includes a charge switch valve 40 for supplying the pressure oil of the charge pump 24 to the low pressure line.
  • the suction P of the hydraulic pump 23 and the charge pump 24 that is separated from the BX by the BX is connected to the tank 42 c c )
  • the power transmission device 20 as a drive unit of the engine 7 includes a motor and a generator.
  • a notch 65 is connected to the motor / generator 63 via an inverter / inverter 64, and the motor / generator 63 is connected to the motor / generator 63.
  • V 65 constitutes a charging / discharging circuit F, and the surplus power of the engine 7 at the time of light or negative is converted to electric power by the generator 63 which functions as a generator.
  • the brake power of the pump V 3a and the pump 4a is converted to electric power by a power generator 63 that functions as a generator, and These electric powers are controlled by the inter- ter / 64 to charge the battery 65.
  • the electric power controlled by the discharge control of the battery 65 from the invertor / con- nector 64 is supplied to the motor.
  • the electric power is supplied to the electric machine 63 to drive the electric power of the engine 7 by driving the electric motor 63 as an electric motor.
  • the pressure oil of the hydraulic pump 21 is supplied from the solenoid-operated switching valve 27b to the bottom chamber of the boom cylinder 3a, and the other side of the rod chamber of the boom cylinder 3a.
  • the hydraulic oil is returned to the hydraulic pump 21 from the electromagnetic switching valve 27a.
  • the return chamber oil from the mouth chamber of the boom cylinder 3a is supplied from the hydraulic pump 21 to the bottom chamber of the boom cylinder 3a. Is less than the amount of oil to be returned. The shortage is supplied from the charge pump 24 to the hydraulic pump 21 through the check valve 40 for the chassis.
  • the swash plate of the hydraulic pump 21 is controlled in the opposite direction to the above-described stretching operation.
  • the hydraulic pump 21 acts as a motor, and the braking force is reduced.
  • the engine 7 is absorbed by the other hydraulic pumps via the power transmission device 20.
  • the amount of oil returning from the bottom chamber of the cylinder 3a to the hydraulic pump 21 is supplied to the rod chamber.
  • the excess oil is returned to the tank 42 from the flushing knob 25 because it is greater than the oil to be washed.
  • the stretching action of the film cylinder 4a is also possible.
  • the hydraulic cylinder is a hydraulic cylinder.
  • the pump 21 and the arm cylinder 4a are driven by the hydraulic pump 22, and the bucket cylinder 5a is driven by the hydraulic pump 23-£).
  • the hydraulic pump 21 acts as a motor and drives the electric / generator 63 via the power transmission 20.
  • the motor 63 converts the brake power of the pump cylinder 3a into electric power, and converts the power through the inverter / con- nector 64. To charge the battery 65.
  • the bumper cylinder 3a In addition to the bumper cylinder 4a, the bumper cylinder 3a
  • Hydraulic pumps 21 and 22 of the closed circuits A and B 9 Musi y 3a ⁇ The work of the arm shiny 4a »Since it is used for the B-in pressure drive system that controls the 3 ⁇ 4 ⁇
  • the squeezing loss caused by the knuckle is greatly reduced, and the boom cylinder 3a of the closed circuit A is operated by the load.
  • the arm of the closed circuit B is used.
  • 4a Force S The brake operated when the cylinder is extended by the S load. Energy efficiency, which greatly improves energy efficiency.
  • the actuator When the actuator is linked, the load is large. When the power of the engine 7 is insufficient, the engine is operated via the inverter / inverter 64 from the controller 65.
  • the power transmission 20 is driven by the electric motor 63,
  • the engine 7 drives the electric generator 63 to generate a lightning force, and the m-force is used as an in-notter. / V via the computer 64
  • the output of the engine 7 can be smoothed.
  • the engine includes this engine.
  • the electric motor 51 The second electric motor having the function of the electric motor for driving the damper V 4a
  • the motor 53 as a third motive for driving the bucket V-cylinder 5a includes an i-motor-generator 52 and a generator 51, 52. Moment for controlling the current of the motive 53 They are connected to each other via the ⁇ -units 54 55 and 56 via the wiring.
  • An electric / generator 51 is connected to a hydraulic pump 57 as a fluid pressure pump of the whistle 1 which can be rotated in the normal and reverse directions for driving the bobbin cylinder 3a.
  • Electric • Generator 52 is connected to a hydraulic pump 57 as a fluid pressure pump of the whistle 1 which can be rotated in the normal and reverse directions for driving the bobbin cylinder 3a.
  • a hydraulic pump 58 is connected as a reversible second hydraulic pump for driving the one-minder 4a, and the motor 53 is provided with a packet system.
  • a hydraulic pump 59 as a third hydraulic pump for driving the cylinder 5a is connected. Hydraulic pumps 57 and 58 also function as hydraulic motors when supplied with hydraulic oil.
  • a first closed circuit A is provided for the boom cylinder 3a.
  • the first closed circuit A controls the rotation speed of the electric motor / generator 51 so that the discharge flow rate of the hydraulic pump 57 connected to the electric motor 51 is controlled. To Then, the operation speed of the boom cylinder 3a connected to the pressure pump 57 is controlled.
  • the second closed circuit B controls the rotation speed of the electric generator 52, and the discharge flow of the hydraulic pump 58 connected to the electric generator 52 is controlled by the second closed circuit B. By adjusting the pressure, the operating speed of the arm cylinder 4a connected to the pressure pump 58 is controlled.
  • an open circuit C is provided for the socket cylinder '5a.
  • This open circuit C is used for rotating the motor 53.
  • the rotation speed of the hydraulic pump 59 connected to the electric motor 53 is controlled, and the hydraulic pump 59 is supplied with the power from the hydraulic pump 59.
  • the hydraulic oil connected to the control valve 35 is connected to the control valve 35.
  • This circuit is used to control the operating speed of the cylinder 5a.
  • the control knob 35 of this circuit C is used.
  • the generator 50, the electric motor • The generator 51 52 and the electric motor 53 include a battery 60, which is used to charge and discharge the battery 60. It is connected via a notch 61 to generate the surplus power from the generator 50 and the brake power of the prime cylinder 3a and the arm cylinder 4a.
  • a charge / discharge circuit E for charging / discharging the power and electric power generated by the generators 51 and 52 to / from the note V 60 is provided by these notches y 60 and dy. It is composed of an inverter / notter 61.
  • the return oil amount from the mouth cylinder, the chamber power, and the like of the boom cylinder 3a is changed from the hydraulic pump 57 to the bottom cylinder 3a of the boom cylinder 3a. Since the amount of oil supplied to the chamber is less than the amount of oil supplied to the chamber, the insufficient amount of return oil is supplied from the charge pump 24 via the check valve 40 for the charge. Supplied to hydraulic pump 57.
  • the speed of extension of the pump V 3a is further increased.
  • the hydraulic opening is controlled by controlling the rotation of the motor 53 with the puff control unit 56.
  • the bypass valve 62 is closed, and the electromagnetic ratio switching valve is switched.
  • the electric motor / generator 51 operates as a generator, and generates electric power.
  • the amount of oil returned from the bottom chamber power of the pump cylinder 3a to the hydraulic pump 57 is greater than the amount of oil supplied to the rod chamber.
  • the surplus oil is returned to the tank 42 from the flushing valve 25.
  • the motive motor 53 When the extension cylinder 5a is extended or retracted, the motive motor 53 is driven to supply hydraulic oil from the hydraulic pump 59 and to operate the pipe cylinder. 62 is closed, and the outlet of the control port 35 is controlled so that the pressurized oil is supplied to the bucket cylinder 5a and the expansion and contraction operation is performed.
  • bypass valve 62 is used in accordance with the amount of each cylinder's reno. Is closed, and the aP of the solenoid-operated directional control valves 37 and 39 is controlled, and the hydraulic oil of the hydraulic pump 59 is supplied to the Boom cylinder 3a and the Cylinder cylinder 4a. It is controlled so that the cylinder speed corresponding to the supplementary operation can be obtained.
  • the rotation speed of the hydraulic pumps 57, 58 in the closed circuit AB is controlled by the motor • generator 5152, so that the boom cylinder V in the closed circuit AB is controlled.
  • the Hydraulic pressure pin of the pharmacy 4a 57 57 58 Electric / generators 51 and 52 can be reduced in size, so that pumps / motors / generators can be mounted easily and the cost can be reduced.
  • C cylinders 3a, 4a and 5a can be driven by a unique hydraulic pump, and if necessary, from a hydraulic pump 59 for driving a bucket cylinder. Since the pressurized oil is supplied to the bumper cylinder 3a and the dam cylinder 4a, the load interference is reduced as compared with the conventional system, and the operation is easier. Easy to become
  • Electric * generators 51 and 52 that have the function of a generator that generates brake power when the pump 3a and the arm 4a are operated by the load. Charges and discharges the power recovered by power generation and generated during low loads, and excess power.
  • engine 7 Since power is supplied from 60 and the output of engine 7 is smoothed, engine 7 can be downsized compared to the conventional system. . Possibility of industrial use
  • the present invention is not limited to the hydraulic shovel, but may be used for other working machines such as da, burd, and z.

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  • Physics & Mathematics (AREA)
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Abstract

Installé dans un vérin de flèche (3a) se trouve un premier circuit fermé (A) permettant de commander la vitesse de pompage du vérin de flèche (3a) relié à une pompe de refoulement d'huile (21), par commande de plateau oscillant de la pompe de refoulement d'huile (21). Installé dans un vérin de bras (4a) se trouve un second circuit fermé (B) permettant de commander la vitesse de pompage du vérin de bras (4a) relié à une pompe de refoulement d'huile (22), par commande de plateau oscillant de la pompe de refoulement d'huile (22). Installé dans un vérin de benne (5a) se trouve un circuit ouvert (C) permettant de commander la vitesse de pompage d'un vérin de benne (5a) relié à une soupape de commande (35), par commande de plateau oscillant d'une pompe de refoulement d'huile (23) et par régulation de débit à l'aide de la soupape de commande (35) permettant de réguler l'huile de travail alimentée à partir de la pompe de refoulement d'huile (23). A partir de la soupape de commande (35) du côté pompe du circuit ouvert (C) bifurque un circuit de distribution (D) permettant de distribuer l'huile de travail de la pompe de refoulement d'huile (23) au vérin de flèche (3a) et au vérin de bras (4a). Une puissance maximum peut être fournie en fonction d'une charge.
PCT/JP2004/003220 2003-09-01 2004-03-11 Unite d'entrainement d'engins de travaux Ceased WO2005024246A1 (fr)

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JP2003308915A JP2005076781A (ja) 2003-09-01 2003-09-01 作業機械の駆動装置
JP2003-308915 2003-09-01

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