WO2005019656A1 - 油圧駆動制御装置 - Google Patents
油圧駆動制御装置 Download PDFInfo
- Publication number
- WO2005019656A1 WO2005019656A1 PCT/JP2004/011438 JP2004011438W WO2005019656A1 WO 2005019656 A1 WO2005019656 A1 WO 2005019656A1 JP 2004011438 W JP2004011438 W JP 2004011438W WO 2005019656 A1 WO2005019656 A1 WO 2005019656A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- hydraulic
- engine
- circuit
- control device
- state
- Prior art date
Links
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 18
- 238000007599 discharging Methods 0.000 claims abstract description 3
- 238000009412 basement excavation Methods 0.000 claims description 14
- 230000001629 suppression Effects 0.000 claims description 7
- 239000003921 oil Substances 0.000 abstract description 40
- 230000000694 effects Effects 0.000 abstract description 22
- 239000000446 fuel Substances 0.000 abstract description 22
- 230000001131 transforming effect Effects 0.000 abstract 1
- 238000000034 method Methods 0.000 description 12
- 238000010586 diagram Methods 0.000 description 10
- 230000001276 controlling effect Effects 0.000 description 5
- 238000002347 injection Methods 0.000 description 5
- 239000007924 injection Substances 0.000 description 5
- 238000011144 upstream manufacturing Methods 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000001514 detection method Methods 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000000875 corresponding effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
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- 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
- E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
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- 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
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- 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
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- 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
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- 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
- E02F9/2242—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance including an electronic controller
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- 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
- E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
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- 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
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- 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
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
- F02D29/04—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto peculiar to engines driving pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
- F15B2211/20523—Internal combustion engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
- F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
- F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/46—Control of flow in the return line, i.e. meter-out control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
- F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
Definitions
- the present invention relates to a hydraulic drive control device that controls a hydraulic drive system of a hydraulic shovel, for example.
- a hydraulic excavator includes a variable displacement hydraulic pump driven by an engine, and supplies and discharges hydraulic oil discharged from the hydraulic pump to various hydraulic actuators through control valves, thereby providing a working machine.
- the driving of the turning device and the traveling device is controlled.
- Patent Document 1 JP-A-2002-339904
- the output of the hydraulic pump is controlled to be constant, and when the hydraulic loss is reduced, the amount of oil discharged from the hydraulic pump increases and the work is performed. The amount will increase. Although a favorable effect of reducing fuel consumption per work amount can be obtained by increasing the work amount in this way, there is a problem that it is difficult for a user to realize the effect.
- the present invention has been made to solve such a problem, and provides a hydraulic drive control device capable of converting a hydraulic loss reduction effect into a fuel consumption reduction effect that is most easily perceived by a user.
- the purpose is.
- a hydraulic drive control device includes:
- a drive hydraulic circuit that drives the hydraulic actuator by supplying and discharging hydraulic oil discharged from a hydraulic pump driven by the engine to and from the hydraulic actuator through a control valve; and
- a hydraulic drive control device having a quick return circuit for directly returning a part of the discharged hydraulic oil to the tank,
- Engine control means for controlling the output of the engine is provided, and the engine control means performs control for suppressing the output of the engine when the quick return circuit is open. .
- a back pressure detecting means for detecting a back pressure of the quick return circuit is provided, and the engine control means is configured to control the engine based on a back pressure value detected by the back pressure detecting means. It is preferable to adjust the engine output suppression amount (second invention).
- the hydraulic actuator is an arm cylinder of a hydraulic shovel, and the quick return circuit is operated during an arm dump operation (third invention).
- a plurality of hydraulic circuit units for driving a hydraulic actuator by hydraulic oil discharged from a hydraulic pump driven by an engine are provided, and one hydraulic circuit in the plurality of hydraulic circuit units is provided.
- Hydraulic drive system configured to be able to switch between a merged state in which the hydraulic section and the other hydraulic circuit section are connected and driven, and a split state in which the one hydraulic circuit section and the other hydraulic circuit section are separately driven.
- An engine control means for controlling the output of the engine is provided, and the engine control means performs control for suppressing the output of the engine in accordance with switching from the merged state to the branch state. is there.
- the hydraulic actuator in the one hydraulic circuit unit is an arm cylinder of a hydraulic shovel
- the hydraulic actuator in the other hydraulic circuit unit is a bucket cylinder of a hydraulic shovel.
- the discharge pressure of the hydraulic pump in the one hydraulic circuit or the hydraulic pump in the other hydraulic circuit reaches a predetermined value during the excavation operation performed by the simultaneous operation of the arm cylinder and the bucket cylinder. At this time, it is preferable that switching from the merged state to the split state is performed (a sixth invention).
- the hydraulic pressure loss is reduced by the opening operation of the quick return circuit, so that the operating pressure required to drive the hydraulic actuator is reduced, thereby reducing the required load on the engine. Is done. Further, at the time of opening the quick return circuit, the engine output is suppressed by the engine control means. According to the present invention, since the engine load is reduced by the opening operation of the quick return circuit and the engine output is suppressed accordingly, the operator operates even if the engine output drops. The fuel consumption can be reduced without a sense of discomfort. Therefore, the effect of reducing the oil pressure loss can be converted to the effect of reducing fuel consumption, which is most easily felt by the user.
- the one hydraulic circuit and the other hydraulic circuit are separated from the merged state in which one hydraulic circuit and the other hydraulic circuit are connected and driven.
- the engine output is suppressed as the engine load is reduced by reducing the hydraulic pressure loss by switching to the shunting state in which the hydraulic pressure is reduced.
- the hydraulic pressure loss is reduced.
- the reduction effect can be converted to a fuel consumption reduction effect that is most easily perceived by the user.
- FIG. 1 is a side view of a hydraulic shovel according to one embodiment of the present invention.
- FIG. 2 is a hydraulic circuit diagram of the hydraulic drive control device according to the first embodiment.
- FIG. 3 is a control map relating to engine output suppression control.
- FIG. 4 is a hydraulic circuit diagram of a hydraulic drive control device according to a second embodiment.
- FIG. 5 is a diagram illustrating an operation state of the hydraulic drive control device according to the second embodiment, wherein (a) is a simplified diagram of a merged state, and (b) is a state in which the merged state is switched to a divided state.
- the simplified diagram, (c) is a simplified diagram of the split state.
- FIG. 6 is a flowchart showing processing contents of merge / shunt switching control.
- FIG. 1 shows a side view of a hydraulic shovel according to one embodiment of the present invention. Also FIG. 2 shows a hydraulic circuit diagram according to the hydraulic drive control device of the first embodiment.
- the hydraulic excavator 1 includes a lower traveling body 2, an upper revolving body 4 disposed on the lower traveling body 2 via a revolving device 3,
- the upper slewing body 4 is provided with a driver's cab 5 provided at the front left position and a work implement 6 attached to the front center position of the upper slewing body 4.
- the work machine 6 has a boom 7, an arm 8 and a bucket 9 rotatably connected to the revolving superstructure 4 in this order from the side of the upper revolving superstructure 4.
- the hydraulic pressure is adjusted so as to correspond to the boom 7, the arm 8 and the bucket 9, respectively.
- Cylinders boost cylinder 10, arm cylinder 11, and bucket cylinder 12
- a hydraulic drive control device 15 provided in the hydraulic excavator 1 includes a diesel engine 16, a variable displacement hydraulic pump 17 driven by the engine 16, An operating means 18 is provided in the driver's cab 5.
- the engine 16 is provided with a fuel injection device 19 having an electronic governor 19a.
- a fuel injection signal based on a fuel injection characteristic map set corresponding to a target engine output characteristic is input from the controller 20.
- the storage area of the controller 20 stores the opening operation amount of the quick return circuit 42 which is positively correlated with the hydraulic loss reduction amount obtained by the operation of the quick return circuit 42 described later.
- a control map (see FIG. 3) obtained by setting the engine output suppression rate in accordance with the pressure value is stored in advance.
- the engine control device 21 including the fuel injection device 19 and the controller 20 corresponds to “engine control means” in the present invention.
- the hydraulic pump 17 is connected to the pump port 23 and the primary return port 24 of the first directional control valve 22 composed of a three-position directional control valve, and is configured with a three-position directional switching valve. It is connected to the pump port 26 of the two-way control valve 25.
- the cylinder port 27 and the cylinder port 28 of the first directional control valve 22 are connected to the bottom-side A port 29 and the head-side port 30 of the arm cylinder 11, respectively.
- the cylinder ports 31 and 32 of the second directional control valve 25 It is connected to the B port 33 on the bottom side of the cylinder 11.
- the secondary return port 34 and the tank port 35 of the first directional control valve 22 and the tank port 36 of the second directional control valve 25 are connected to a tank 38 via an oil cooler 37, respectively. .
- the return circuit on the bottom side of the arm cylinder 11 is divided into a first return circuit 40 and a second return circuit 41.
- the first return circuit 40 sends the hydraulic oil discharged from the bottom side oil chamber 11a from the bottom side A port 29 to the tank 38 through the cylinder port 27 of the first directional control valve 22, the tank port 35, and the oil cooler 37. And a channel for guiding.
- the second return circuit 41 transfers the hydraulic oil discharged from the bottom oil chamber 11a from the bottom B port 33 to the tank 38 through the cylinder port 31, the tank port 36 of the second directional control valve 25, the tank port 36, and the oil cooler 37. And a channel for guiding.
- the second return circuit 41 is provided with a quick return valve 43 for switching to a quick return circuit 42 for directly circulating the hydraulic oil flowing through the circuit 41 to the tank 38.
- the quick return valve 43 includes a cylinder port 44 connected to the bottom B port 33 of the arm cylinder 11, a valve port 45 connected to the cylinder ports 31 and 32 of the second directional control valve 25, and a tank 38.
- a quick return valve body having a tank port 46, a pilot pressure oil input port 47, and a drain port 48 connected to each other, and a main valve 49 that opens and closes a flow path between the cylinder port 44 and the tank port 46.
- a control valve 50 for controlling the opening and closing operation of the main valve 49.
- the control valve 50 receives pilot pressure oil from a pilot valve 53, which will be described later, and switches the cylinder port 44 to communicate with the drain port 48. When operated, the main valve 49 is opened to connect the cylinder port 44 and the tank port 46.
- the operating means 18 includes an operating lever 51 and pilot valves 52 and 53 that are switched by tilting the operating lever 51.
- An input port of each pilot valve 52 and 53 has a pilot pressure. It is connected to a pilot pump 54 that generates oil.
- the output port of the pilot valve 52 is connected to one operating part 22a of the first directional control valve 22 and one operating part 25a of the second directional control valve 25, respectively.
- the output port of the pilot valve 53 is connected to the other operating part 22b of the first directional control valve 22, the other operating part 25b of the second directional control valve 25, and the operating part 50a of the control valve 50 in the quick return valve 43. Connect to each Has been.
- a pressure switch 56 is provided in a pilot pressure line 55 that connects the output port of the pilot valve 53 and the operation unit 50a of the control valve 50. Further, the quick return circuit 42 is provided with a pressure sensor (back pressure detecting means) 57 for detecting the back pressure of the circuit 42. The ⁇ N signal from the pressure switch 56 and the back pressure detection signal from the pressure sensor 57 are input to the controller 20.
- pilot pressure oil is sent out from the output port of the pilot valve 52, and the pilot pressure oil is supplied to one of the operation sections 22 a and 22 of the first direction control valve 22.
- the first directional control valve 22 and the second directional control valve 25 are respectively switched to the position A by acting on one of the operation units 25a of the second directional control valve 25.
- the hydraulic oil discharged from the hydraulic pump 17 is supplied to the bottom side A port 29 of the arm cylinder 11 via the first directional control valve 22 and to the bottom of the arm cylinder 11 via the second directional control valve 25.
- the oil is guided to the side B ports 33 and supplied to the bottom oil chamber 11a of the arm cylinder 11.
- pilot pressure oil is sent out from the output port of the pilot valve 53, and this pilot pressure oil is supplied to the other end of the first directional control valve 22.
- the first operation valve 22 and the second operation valve 25 are respectively switched to the position B by acting on the other operation unit 25b of the operation unit 22b and the second direction control valve 25, respectively.
- the pressure oil discharged from the hydraulic pump 17 is guided to the head side port 30 of the arm cylinder 11 via the first directional control valve 22 and supplied to the head side oil chamber l ib of the arm cylinder 11. .
- the hydraulic oil in the bottom side oil chamber 11a of the arm cylinder 11 is recovered from the bottom side A port 29 to the tank 38 via the first directional control valve 22 and the oil cooler 37, and the bottom side B port From 33, it is collected in the tank 38 via the second directional control valve 25 and the oil cooler 37.
- the arm 8 is turned forward and An arm dump operation is performed.
- the pilot pressure oil from the throttle valve 53 acts on the operating portion 50a of the control valve 50 in the quick return valve 43 to switch the control valve 50 to the open position.
- the main valve 49 of the valve 43 is opened, and the quick return circuit 42 is opened. With the opening operation of the quick return circuit 42, most of the return oil flowing through the second return circuit 41 is directly returned to the tank 38, and the hydraulic pressure loss is significantly reduced.
- the ON signal from the pressure switch 56 is input to the controller 20, so that the strong controller 20 receives the input signal from the quick return circuit 42. 42 recognizes that it is in the open operation state. Then, the controller 20 obtains the engine output suppression rate by referring to the control map shown in FIG. 3 based on the pressure value of the quick return circuit 42 detected by the pressure sensor 57, and obtains the obtained engine output suppression rate.
- the target engine output value is calculated from the engine output value immediately before the quick return circuit 42 is opened, and the electronic governor 19a is controlled so that the engine output value becomes equal to the target engine output value.
- the controller 20 controls the electronic governor 19a so that the engine output value becomes 266 PS.
- the hydraulic pressure loss is reduced by the opening operation of the quick return circuit 42, so that the operating pressure required to contract the arm cylinder 11 is reduced.
- the required load on the engine 16 is reduced.
- the quick return circuit 42 is opened, the output of the engine 16 is suppressed by the engine control device 21.
- the engine load is reduced by the opening operation of the quick return circuit 42, and the engine output is suppressed accordingly.
- Fuel consumption can be reduced without feeling uncomfortable. Therefore, the effect of reducing the hydraulic pressure loss can be converted to the fuel efficiency reduction effect that the user can most easily feel.
- FIG. 4 connects (merges) a first hydraulic circuit unit and a second hydraulic circuit unit, which will be described later, and extends the arm cylinder 11 and the bucket cylinder 12 to excavate the arm. This shows the circuit status when performing packet excavation.
- the hydraulic drive control device 60 of the present embodiment includes a first hydraulic circuit unit that mainly drives the arm cylinder 11 with pressure oil discharged from a variable displacement first hydraulic pump 17A that uses the engine 16 as a drive source. 61 and a second hydraulic circuit portion 62 that mainly drives the bucket cylinder 12 with the pressure oil discharged from the variable displacement second hydraulic pump 17B driven by the engine 16 as a driving source.
- the first hydraulic circuit 61 includes an arm flow direction control valve 63 for controlling the supply flow rate and the supply / discharge direction of the pressure oil from the first hydraulic pump 17A to the arm cylinder 11.
- the pump port is connected to the output port of the first hydraulic pump 17A via the first discharge passage 64
- the cylinder A port is connected to the bottom of the arm cylinder 11 via the supply / discharge passage 65.
- the cylinder B port is connected to the head-side oil chamber of the arm cylinder 11 via a supply / discharge flow path 66
- the tank port is connected to the tank 38 via a drain flow path 67, respectively.
- a pressure sensor 68 is provided in the first discharge channel 64, and a pressure detection signal from the pressure sensor 68 is input to the controller 20. Further, a pressure compensating valve 69 with a first check function of an external pilot pressure operation type for allowing the flow from upstream to downstream and restricting the flow from downstream to upstream is provided in the supply / discharge channel 65. I have.
- the second hydraulic circuit section 62 includes a packet flow direction control valve 70 for controlling the supply flow rate and the supply / discharge direction of the pressure oil to and from the bucket cylinder 12 with the power of the second hydraulic pump 17B.
- the pump port is connected to the output port of the second hydraulic pump 17B via the second discharge passage 71
- the cylinder A port is connected to the packet via the supply / discharge passage 72.
- the cylinder B port is connected to the head-side oil chamber of the bucket cylinder 12 via a supply / discharge channel 73
- the tank port is connected to the tank 38 via a drain channel 74, respectively.
- a pressure sensor 75 is provided in the second discharge flow path 71, and a pressure detection signal from the pressure sensor 75 is input to the controller 20. Further, a pressure compensating valve 76 having a second check function of an external pilot pressure operation type is provided in the supply / discharge channel 72 to allow a flow from the upstream to the downstream and restrict the flow from the downstream to the upstream. Has been done.
- the first discharge flow path 64 and the second discharge flow path 71 are connected by a merging / diverting passage 78 having a merging / diverting valve 77 interposed.
- the merge / shunt valve 77 is provided with an electromagnetic switching valve 80 which receives supply of pressure oil from the first hydraulic pump 17A depressurized by the pressure reducing valve (constant secondary pressure reducing valve) 79. Switching is performed by switching based on a command signal. By changing the switching timing of the electromagnetic switching valve 80 in this manner, the pressure setting for opening and closing the junction valve 77 can be changed according to various situations.
- a proportional valve (electromagnetic proportional valve) or a throttle 81 is interposed between the junction valve 77 and the solenoid-operated switching valve 80. By operating the junction valve 77 little by little, the junction valve is operated. It is designed to reduce the shock associated with switching 77
- a bypass passage 82 is provided between the first hydraulic circuit section 61 and the second hydraulic circuit section 62 to bypass both hydraulic circuit sections 61, 62. That is, the bypass passage 82 is provided with both hydraulic circuits so as to guide a part of the pressure oil circulated through the second discharge passage 71 to a passage downstream of the pressure compensation valve 69 with the first check function. Connect parts 61 and 62.
- the bypass passage 82 allows the flow of pressure oil into the arm high-speed flow control valve 83, which is the same flow direction control valve as the arm flow direction control valve 63, and the arm cylinder 11, and allows the reverse flow.
- a pressure compensating valve 84 with a check function of an external pilot pressure operation type for regulating pressure is interposed in the order of the upstream force.
- the arm flow direction control valve 63 and the arm high speed flow control valve 83 are operated in cooperation as described below.
- the arm high-speed flow control valve 83 is opened after the arm flow direction control valve 63 is opened.
- the arm high-speed flow control valve 83 is closed. Only the arm flow direction control valve 63 is opened.
- the controller 20 is connected to a monitor panel 85 for setting a selected operation mode, a throttle dial 86 for setting an engine target speed, and the like.
- the operations to be selected include the rocking (excavation) operation of the arm 8 and the rocking (excavation) operation of the packet 9, and the like, and the pressure switches 87, 88, 89 installed on the operation lever (not shown). , 90 are used to issue various work commands.
- FIG. 5 shows the simplified diagram of FIG. In FIG. 5, (a) shows the merged state, (b) shows the state when the state is switched from the merged state to the split state, and (c) shows the split state.
- the first hydraulic circuit portion 61 and the second hydraulic circuit portion 62 are joined by setting the joining / diverting valve 77 to the open state, so that the second hydraulic pump 17B
- the hydraulic oil is supplied to the first hydraulic circuit section 61 via the merging / diverting passage 78 and the bypass passage 82.
- the maximum pump capacity of each of the hydraulic pumps 17A and 17B is set to 1.0P
- the first hydraulic pump 17A is required.
- the arm cylinder 11 is driven by 1.5P by adding 0.5P of the second hydraulic pump 17B to the 1.0P of the second hydraulic pump 17B.
- the pressure of each of the hydraulic pumps 17A and 17B is, for example, 100 kgf / cm 2 .
- the arm cylinder is operated by the pressure compensating valve 84 with a check function.
- the flow of pressurized oil into da 11 will be stopped.
- the flow rate supplied from the second hydraulic pump 17B to the arm cylinder 11 decreases due to the increase in the load pressure of the arm cylinder 11, and the flow branches smoothly to the state shown in FIG.
- the pressure of the first hydraulic pump 17A becomes 300 kgf / cm 2 and the pressure of the second hydraulic pump 17B becomes 250 kgfZcm 2 .
- step S1 it is determined based on the ON signals from the various pressure switches 87, 88, 89, 90 whether or not the work mode is excavation.
- the process proceeds to step S2, and when the work mode is not excavation, the process proceeds to step S3.
- step S3 when the junction valve 77 is at the closed position, the process returns to step S1 as the open position, and when the junction valve 77 is at the open position, the process returns to step S1 as the open position.
- step S2 it is determined whether or not simultaneous excavation operation by the arm 8 and the bucket 9 is performed.
- the process proceeds to step S3.
- step S4 it is determined whether or not the junction valve 77 is in the open position. If the junction valve 77 is in the open position, the process proceeds to step S5. If the junction valve 77 is in the closed position, the process proceeds to step S6.
- step S5 it is determined whether or not PlorP2 ⁇ 250 kgf / cm 2 (24.5 MPa) is satisfied.
- P1 is the pressure detected by the pressure sensor 68
- P2 is the pressure detected by the pressure sensor 75. If P1 or P2 is equal to or greater than 250 kgf / cm 2 , the branching valve 77 is set to the closed position to change the flow (S7). On the other hand, if PlorP2 ⁇ 250 kgf / cm 2 is not satisfied, the process returns to step S1.
- step S6 it is determined whether or not PlandP2 is smaller than 220 kgf / cm 2 (21.6 MPa). If both P1 and P2 are less than 220 kgf / cm 2 , Is set to the open position to bring them together (S8). On the other hand, if PlandP2 is not larger than 220 kgf / cm 2 , the process returns to step S1.
- the engine control device 21 suppresses the output of the engine 16 (for example, ⁇ 3%) with the switching from the merged state to the branched state in step S7. Have been.
- the hydraulic drive control device 60 of the present embodiment switched by hydraulic pressure losses P1 or P2 is a branching state if a 2 50kgfZcm 2 or more in a merging state is reduced, the engine output Te is Align thereto Since it is configured to be suppressed, it is possible to reduce the fuel consumption by lowering the engine output without a sense of incongruity. Therefore, the effect of reducing the oil pressure loss can be converted to the effect of reducing the fuel consumption that the user can most easily feel. If both P1 and P2 are less than 220 kgfZcm 2 in the split state, the arm or the packet can be driven at high speed in the merge state.
- switching between the merged state and the branched state is performed based on the discharge pressure of the hydraulic pumps 17A and 17B, so that the merged state is changed to the branched state.
- Switching can be performed more appropriately, and the fuel consumption reduction effect can be optimized.
- the switching between the merged state and the branched state is performed. Hunting can be avoided at times, and there is an advantage that the reliability of the switching operation is improved.
- the hydraulic shovel 1 independently mounts the hydraulic drive control devices 15 and 69.
- the hydraulic shovel 1 includes the hydraulic drive control devices 15 and 60. It is needless to say that the fuel economy can be further reduced by this configuration.
- the hydraulic drive control device according to the present invention can be used not only as a hydraulic excavator but also as a hydraulic drive control device for construction machines such as a wheel loader and the like, agricultural machines, industrial vehicles and the like.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Structural Engineering (AREA)
- Civil Engineering (AREA)
- Fluid Mechanics (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Combustion & Propulsion (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US10/567,674 US7441407B2 (en) | 2003-08-20 | 2004-08-09 | Hydraulic drive control device |
JP2005513268A JP4271194B2 (ja) | 2003-08-20 | 2004-08-09 | 油圧駆動制御装置 |
GB0602745A GB2421984B (en) | 2003-08-20 | 2004-08-09 | Hydraulic drive control device |
Applications Claiming Priority (2)
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JP2003-296557 | 2003-08-20 | ||
JP2003296557 | 2003-08-20 |
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WO2005019656A1 true WO2005019656A1 (ja) | 2005-03-03 |
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PCT/JP2004/011438 WO2005019656A1 (ja) | 2003-08-20 | 2004-08-09 | 油圧駆動制御装置 |
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Country | Link |
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US (1) | US7441407B2 (ja) |
JP (2) | JP4271194B2 (ja) |
KR (1) | KR100704219B1 (ja) |
CN (2) | CN101144490B (ja) |
GB (1) | GB2421984B (ja) |
WO (1) | WO2005019656A1 (ja) |
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- 2004-08-09 GB GB0602745A patent/GB2421984B/en not_active Expired - Fee Related
- 2004-08-09 US US10/567,674 patent/US7441407B2/en active Active
- 2004-08-09 KR KR1020067002975A patent/KR100704219B1/ko active IP Right Grant
- 2004-08-09 CN CN2007101667065A patent/CN101144490B/zh not_active Expired - Fee Related
- 2004-08-09 JP JP2005513268A patent/JP4271194B2/ja not_active Expired - Fee Related
- 2004-08-09 CN CNB2004800236470A patent/CN100451352C/zh not_active Expired - Fee Related
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2009
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Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006123704A1 (ja) * | 2005-05-18 | 2006-11-23 | Komatsu Ltd. | 建設機械の油圧制御装置 |
GB2441258A (en) * | 2005-05-18 | 2008-02-27 | Komatsu Mfg Co Ltd | Hydraulic controller of construction machinery |
GB2441258B (en) * | 2005-05-18 | 2010-01-27 | Komatsu Mfg Co Ltd | Hydraulic control device for construction machinery |
KR100975266B1 (ko) | 2005-05-18 | 2010-08-11 | 가부시키가이샤 고마쓰 세이사쿠쇼 | 건설기계의 유압제어장치 |
US7992384B2 (en) | 2005-05-18 | 2011-08-09 | Komatsu Ltd. | Hydraulic control device of construction machinery |
JP2012500370A (ja) * | 2008-08-20 | 2012-01-05 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | 流体力学的負荷に圧力を供給するための圧力供給装置、および、圧力供給方法 |
KR20180111982A (ko) * | 2016-09-21 | 2018-10-11 | 가부시키가이샤 고마쓰 세이사쿠쇼 | 작업 차량 및 유압 제어 방법 |
KR102123481B1 (ko) | 2016-09-21 | 2020-06-16 | 가부시키가이샤 고마쓰 세이사쿠쇼 | 작업 차량 및 유압 제어 방법 |
US11408145B2 (en) | 2016-09-21 | 2022-08-09 | Komatsu Ltd. | Work vehicle and hydraulic control method |
CN113195904A (zh) * | 2019-01-28 | 2021-07-30 | 神钢建机株式会社 | 工程机械中的液压缸的驱动装置 |
US11725673B2 (en) | 2019-01-28 | 2023-08-15 | Kobelco Construction Machinery Co., Ltd. | Drive device for hydraulic cylinder in work machine |
CN113195904B (zh) * | 2019-01-28 | 2023-08-29 | 神钢建机株式会社 | 工程机械中的液压缸的驱动装置 |
Also Published As
Publication number | Publication date |
---|---|
US7441407B2 (en) | 2008-10-28 |
GB0602745D0 (en) | 2006-03-22 |
CN100451352C (zh) | 2009-01-14 |
JP2009150553A (ja) | 2009-07-09 |
KR100704219B1 (ko) | 2007-04-09 |
CN101144490A (zh) | 2008-03-19 |
JPWO2005019656A1 (ja) | 2007-10-04 |
KR20060031702A (ko) | 2006-04-12 |
CN1836110A (zh) | 2006-09-20 |
JP4799624B2 (ja) | 2011-10-26 |
GB2421984B (en) | 2007-03-21 |
JP4271194B2 (ja) | 2009-06-03 |
GB2421984A (en) | 2006-07-12 |
US20060230752A1 (en) | 2006-10-19 |
CN101144490B (zh) | 2010-06-23 |
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