WO2018179183A1 - 作業機械 - Google Patents
作業機械 Download PDFInfo
- Publication number
- WO2018179183A1 WO2018179183A1 PCT/JP2017/013074 JP2017013074W WO2018179183A1 WO 2018179183 A1 WO2018179183 A1 WO 2018179183A1 JP 2017013074 W JP2017013074 W JP 2017013074W WO 2018179183 A1 WO2018179183 A1 WO 2018179183A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- control valve
- pressure
- prime mover
- work machine
- oil
- Prior art date
Links
Images
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
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F3/00—Dredgers; Soil-shifting machines
- E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
- E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
- E02F3/36—Component parts
- E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
- E02F3/425—Drive systems for dipper-arms, backhoes or the like
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F3/00—Dredgers; Soil-shifting machines
- E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
- E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
- E02F3/36—Component parts
- E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
- E02F3/43—Control of dipper or bucket position; Control of sequence of drive operations
- E02F3/435—Control of dipper or bucket position; Control of sequence of drive operations for dipper-arms, backhoes or the like
-
- 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
- E02F9/2004—Control mechanisms, e.g. control levers
-
- 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
-
- 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
- E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
-
- 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
- E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
-
- 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
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
-
- 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
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2271—Actuators and supports therefor and protection therefor
-
- 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
-
- 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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- 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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
-
- 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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
- F15B11/10—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor in which the servomotor position is a function of the pressure also pressure regulators as operating means for such systems, the device itself may be a position indicating system
-
- 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
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/044—Removal or measurement of undissolved gas, e.g. de-aeration, venting or bleeding
-
- 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
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/047—Preventing foaming, churning or cavitation
-
- 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
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
-
- 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
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F3/00—Dredgers; Soil-shifting machines
- E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
- E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
- E02F3/30—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom
- E02F3/32—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom working downwardly and towards the machine, e.g. with backhoes
-
- 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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/027—Installations or systems with accumulators having accumulator charging devices
- F15B1/033—Installations or systems with accumulators having accumulator charging devices with electrical control means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/50—Monitoring, detection and testing means for accumulators
- F15B2201/51—Pressure detection
-
- 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
-
- 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
- F15B2211/20576—Systems with pumps with multiple pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
-
- 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
- F15B2211/275—Control of the prime mover, e.g. hydraulic 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
- F15B2211/30—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
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/575—Pilot pressure control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/625—Accumulators
-
- 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
-
- 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
-
- 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
- F15B2211/6316—Electronic controllers using input signals representing a pressure the pressure being a pilot 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. 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
- F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7053—Double-acting output members
-
- 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
- F15B2211/85—Control during special operating conditions
-
- 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
- F15B2211/85—Control during special operating conditions
- F15B2211/853—Control during special operating conditions during stopping
-
- 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
- F15B2211/857—Monitoring of fluid pressure systems
Definitions
- the present invention relates to a work machine such as a hydraulic excavator, and particularly to a work machine provided with an accumulator that recovers and regenerates potential energy.
- Work machines such as hydraulic excavators are composed of booms, arms, buckets, etc., and have working machines that rotate up and down by supplying pressure oil from a hydraulic pump to a hydraulic actuator. If the potential energy when the work machine descends due to its own weight is recovered and reused, the power consumption of the prime mover can be suppressed. Therefore, there is a working machine that recovers potential energy by storing return pressure oil from a hydraulic actuator in an accumulator, and recovering potential energy by discharging the stored pressure oil and supplying it to the hydraulic actuator.
- An object of the present invention is to provide a work machine that can suppress the pressure accumulation oil in the accumulator being automatically released when the prime mover is stopped, and the like, and the gas from being dissolved in the pressure accumulation oil.
- the present invention discharges a work machine body, a work machine attached to the work machine body, a hydraulic cylinder that drives the work machine, and pressure oil that drives the hydraulic cylinder.
- a pilot pump that outputs, a prime mover that drives the hydraulic pump and the pilot pump, and an operating device that generates an operation signal that drives the control valve by reducing the pilot pressure output from the pilot pump according to an operation;
- the control valve is bypassed to connect the bottom oil chamber of the hydraulic cylinder and the discharge pipe of the hydraulic pump and the accumulator is installed, the bottom oil chamber of the hydraulic cylinder in the bypass pipe, and the The pressure control valve provided between the accumulators, the discharge control valve provided between
- the present invention it is possible to prevent the accumulated oil in the accumulator from being automatically released when the prime mover stops, and the gas from being dissolved into the accumulated oil.
- FIG. 1 is a side view illustrating an external configuration of a hydraulic excavator that is a representative example of a work machine according to the present invention. It is a circuit diagram showing the principal part of the hydraulic system with which the working machine which concerns on 1st Embodiment of this invention was equipped. It is a flowchart showing the output procedure of the identification signal by the rotation state determination part with which the working machine which concerns on 1st Embodiment of this invention was equipped. It is a flowchart showing the control procedure of the pressure accumulation oil quantity by the pressure accumulation oil control part with which the working machine which concerns on 1st Embodiment of this invention was equipped. It is a circuit diagram showing the principal part of the hydraulic system with which the working machine which concerns on 2nd Embodiment of this invention was equipped.
- FIG. 1 is a side view showing an external configuration of a hydraulic excavator that is a typical example of a work machine according to the present invention.
- the front of the driver's seat (the left direction in the figure) is the front of the aircraft.
- the illustration of the hydraulic excavator does not limit the application target of the present invention, and the present invention can be applied to other types of work machines such as cranes as long as the work machine has a working machine that rotates up and down. .
- the hydraulic excavator shown in FIG. 1 includes a work machine body having a traveling body 1 and a revolving body 2 and a work machine (front work machine) 3.
- the traveling body 1 is a lower structure of the work machine and is a crawler type having left and right crawler belts 4.
- a post or the like fixed to the ground may be provided as a lower structure instead of the traveling body.
- the swivel body 2 is provided on the upper part of the traveling body 1 via a swivel wheel 6 so as to be turnable, and includes a cab 7 on the left front part.
- the structure is not limited to the structure in which the lower structure rotates with respect to the upper structure, such as the traveling body 1 and the revolving structure 2, but may have a structure in which the upper structure does not rotate with respect to the lower structure.
- a driver's seat (not shown) where an operator sits and an operating device (such as the operating device 25 in FIG. 2) operated by the operator are arranged.
- the work machine 3 includes a boom 11 rotatably attached to the front portion of the swing body 2, an arm 12 rotatably connected to the tip of the boom 11, and a bucket 13 rotatably connected to the tip of the arm 12. ing.
- the hydraulic excavator also includes left and right traveling motors 15, a swing motor 16, a boom cylinder 17, an arm cylinder 18, and a bucket cylinder 19. These are hydraulic actuators.
- the left and right traveling motors 15 respectively drive the left and right crawler belts 4 of the traveling body 1.
- the turning motor 16 drives the turning wheel 6 to turn the turning body 2 with respect to the traveling body 1.
- the boom cylinder 17 drives the boom 11 up and down.
- the arm cylinder 18 drives the arm 12 to the dump side (opening side) and the cloud side (scratching side).
- the bucket cylinder 19 drives the bucket 13 to the dump side and the cloud side.
- FIG. 2 is a circuit diagram showing the principal part of the hydraulic system with which the working machine which concerns on 1st Embodiment of this invention was equipped.
- the work machine shown in FIG. 1 is equipped with a hydraulic system that drives the hydraulic cylinder 20.
- the hydraulic cylinder 20 is a hydraulic actuator that drives the work machine 3, and in this embodiment, the case of the boom cylinder 17 will be described.
- the hydraulic cylinder 20 may be an arm cylinder 18 or a bucket cylinder 19.
- the hydraulic system includes a hydraulic pump 21, a control valve 22, a pilot pump 23, an engine 24, an operating device 25, an accumulator 26, control valves 27 and 28, a hydraulic system controller 30, and the like.
- the hydraulic pump 21 is, for example, a variable displacement pump, and sucks the hydraulic oil stored in the tank and discharges it to the discharge line 21a as pressure oil that drives the hydraulic cylinder 20.
- the discharge pipe 21 a is connected to the control valve 22.
- the discharge pipe 21a is provided with a relief valve, and the maximum pressure of the discharge pipe 21a is defined by the relief valve.
- the pilot pump 23 is a fixed displacement type, and outputs a pilot pressure that is a source pressure of an operation signal for driving the control valve 22.
- the drive shafts of the hydraulic pump 21 and the pilot pump 23 are connected to the output shaft of the engine 24, and the hydraulic pump 21 and the pilot pump 23 are driven by the engine 24.
- a pilot relief valve 23a is provided in the discharge line of the pilot pump 23, and an upper limit value of the pilot pressure is defined by the pilot relief valve 23a.
- the engine 24 is a prime mover and is an internal combustion engine such as a diesel engine.
- the engine 24 is started by operating an engine switch (motor switch) 35 such as a key switch, and the rotational speed (engine rotational speed N) of the engine 24 is detected by a rotational speed sensor 36.
- the engine speed N during operation is set by the engine control dial 37.
- Signals from the engine switch 35, the rotation speed sensor 36, and the engine control dial 37 are input to an engine controller (motor control device) 38, and the engine controller 38 controls the engine 24 in accordance with these signals.
- the engine controller 38 sets the engine speed N, which is a detection result (detection signal) of the speed sensor 36, by the engine control dial 37.
- the fuel injection amount is controlled so as to approach the target rotational speed Nt.
- the engine controller 38 outputs a determination signal F 1 for the rotational state of the engine 24 based on the engine speed N detected by the engine speed sensor 36 to the hydraulic system controller 30. Output to the rotation state determination unit 31.
- the determination signal F1 of the rotation state of the engine 24 is a signal for identifying whether the rotation speed is insufficient for the work machine to work, for example.
- the engine speed N that is insufficient for the work machine to work is, for example, an engine speed N that is less than a set value Ns that is set lower than Nt, for example, based on the target engine speed Nt. This situation can also be determined by this set value Ns.
- the operating device 25 is a hydraulic pilot type lever device that generates an operation signal (hydraulic signal) for driving the control valve 22 by reducing the pilot pressure output from the pilot pump 23 according to the operation.
- the operating device 25 is configured to operate a pilot valve (pressure reducing valve) 25a with an operating lever.
- the pilot pump 23 is connected to the primary port of the pilot valve 25a, and the operation ports 22a and 22b of the control valve 22 are connected to the two secondary ports provided corresponding to the lever operation direction.
- the pilot pressure of the pilot pump 23 is reduced according to the operation amount, and an operation signal generated thereby is output to the operation port 22 a of the control valve 22.
- an operation signal generated in the same manner is output to the operation port 22 b of the control valve 22.
- the control valve 22 is a direction switching valve that controls the flow of pressure oil from the hydraulic pump 21 to the hydraulic cylinder 20, and in the present embodiment, is constituted by a hydraulically driven three-position switching valve.
- the control valve 22 is connected to the bottom oil chamber of the hydraulic cylinder 20 via the bottom pipeline 20a, to the rod oil chamber of the hydraulic cylinder 20 via the rod pipeline 20b, and to the tank via the tank pipeline.
- the connection destination of the discharge pipe 21a of the hydraulic pump 21 is switched to at least one of a bottom oil chamber, a rod oil chamber, and a tank.
- the spool of the control valve 22 is pushed by springs from both sides, and when not operated, the spool is in a neutral position and connects the discharge pipe 21a only to the tank.
- the spool moves upward in the figure, and the discharge pipe 21a is connected to the tank pipe and the bottom pipe 20a.
- the ratio of flowing to the bottom pipe line 20a increases, and the supply flow rate to the bottom oil chamber increases.
- the hydraulic cylinder 20 extends to raise the boom 11, and the return oil pushed out from the rod oil chamber is discharged to the tank via the control valve 22.
- the accumulator 26 is a regenerative device that stores the return pressure oil pushed out from the bottom oil chamber of the hydraulic cylinder 20 as regenerative energy when the work machine 3 descends.
- the bottom oil chamber (bottom pipe line 20 a) of the hydraulic cylinder 20 and the discharge pipe line 21 a of the hydraulic pump 21 are connected by bypassing the control valve 22 by the bypass line 41.
- the accumulator 26 is installed in the bypass conduit 41.
- a pressure accumulation control valve 27 is positioned between the bottom oil chamber of the hydraulic cylinder 20 and the accumulator 26, and is positioned between the accumulator 26 and the discharge line 21 a of the hydraulic pump 21.
- a control valve 28 for discharge is provided.
- control valves 27 and 28 are electromagnetically driven control valves that are driven by a command signal from the pressure accumulation oil control unit 32 of the hydraulic system controller 30, and may be on-off valves, but in this embodiment, proportional solenoid valves are used.
- the pressure accumulation control valve 27 in this embodiment is a normally closed electromagnetic valve, and normally disconnects the accumulator 26 from the bottom oil chamber of the hydraulic cylinder 20.
- the discharge control valve 28 is a normally open solenoid valve, and normally connects the accumulator 26 to the discharge line 21 a of the hydraulic pump 21.
- the solenoid is excited by a command signal from the pressure accumulation oil control unit 32, the control valve 28 is closed, and the connection between the accumulator 26 and the discharge pipe 21a of the hydraulic pump 21 is cut off.
- a check valve 42 is provided between the accumulator 26 and the accumulator 26, and a check valve 43 is provided between the discharge control valve 28 and the discharge pipe 21 a of the hydraulic pump 21.
- the pilot line connecting the operation port 22a of the control valve 22 and the pilot valve 25a is provided with a pressure sensor 51 for measuring the pressure applied to the operation port 22a (the magnitude of the operation signal P1 instructing the extension of the hydraulic cylinder 20). It has been.
- the pilot line connecting the operation port 22b of the control valve 22 and the pilot valve 25a is provided with a pressure sensor 52 for measuring the pressure applied to the operation port 22b (the magnitude of the operation signal P2 instructing the contraction of the hydraulic cylinder 20). It has been.
- a pressure sensor 53 that measures the discharge pressure of the hydraulic pump 21 is provided in a portion upstream of the control valve 22 in the discharge pipe 21 a of the hydraulic pump 21.
- a pressure sensor 54 for measuring the pressure of the accumulated oil in the accumulator 26 is provided at a portion of the bypass pipe 41 sandwiched between the check valve 42, the discharge control valve 28 and the accumulator 26. These pressure sensors 51-54 are electrically connected to the hydraulic system controller 30, and detection signals from the pressure sensors 51-54 are input to the hydraulic system controller 30.
- the hydraulic system controller 30 is a control device having a function of performing control as a pressure-accumulated oil discharging device that opens the control valve 28 for discharging when the engine speed N becomes less than the set value Ns.
- the hydraulic system controller 30 includes at least a rotation state determination unit 31 and a pressure accumulation oil control unit 32.
- the engine speed N detected by the speed sensor 36 is strictly less than the set value Ns.
- the case where it is estimated that the rotation speed N is less than the set value Ns is also included. This point will be described later in the second embodiment and the like.
- Ns, Ps (described later) and the like are set in advance and stored in the rotation state determination unit 31, the pressure accumulation oil control unit 32, or another storage device included in the hydraulic system controller 30, respectively, and when necessary, the rotation state determination unit 31, referred to by the pressure accumulation oil control unit 32.
- the rotation state determination unit 31 determines whether or not the engine speed N is less than the set value Ns, and outputs an identification signal F2 that is the determination result (for identifying the determination result).
- the rotational state determination unit 31 of the present embodiment calculates the engine rotational speed N based on the signal from the rotational speed sensor 36, and determines whether the engine rotational speed N is less than a set value Ns. At this time, when the identification signal F2 indicating that the engine speed N is less than the set value Ns is output, the rotation state determination unit 31 determines the start command signal (operation command signal) Se of the engine switch 35 and It is assumed that startup (operation) is instructed.
- the pressure accumulation oil control unit 32 controls the amount of oil supplied to or discharged from the accumulator 26 by controlling the opening degree of the control valves 27 and 28, and commands the recovery and regeneration of the potential energy of the work machine 3. .
- FIG. 3 is a flowchart showing a procedure for outputting an identification signal by the rotation state determination unit 31.
- the series of processes shown in the figure is repeatedly executed at a predetermined cycle time (for example, 0.1 s) by the rotation state determination unit 31 while the hydraulic system controller 30 is energized.
- the rotation state determination unit 31 calculates the engine rotation speed N based on the signal detected by the rotation speed sensor 36, and determines whether the engine rotation speed N is smaller than the set value Ns. If the engine speed N is smaller than the set value Ns (if N ⁇ Ns), the procedure proceeds to step S103, and if it is greater than or equal to the set value Ns (if N ⁇ Ns), the procedure proceeds to step S105.
- FIG. 4 is a flowchart showing a control procedure of the accumulated oil amount by the accumulated oil control unit 32.
- the series of processes shown in the figure is repeatedly executed at a predetermined cycle time (for example, 0.1 s) by the pressure accumulation oil control unit 32 while the hydraulic system controller 30 is energized.
- the pressure accumulation oil control unit 32 determines whether the operation signal P1 detected by the pressure sensor 51 is larger than the set value Ps (that is, whether the hydraulic cylinder 20 is extended). If the operation signal P1 is larger than the set value Ps (if P1> Ps), the procedure proceeds to step S205, and if it is equal to or less than the set value Ps (if P1 ⁇ Ps), the procedure proceeds to step S203. When the procedure moves to step S203, the pressure accumulation oil control unit 32 determines whether the operation signal P2 detected by the pressure sensor 52 is larger than the set value Ps (that is, whether the hydraulic cylinder 20 is contracted).
- step S204 the procedure proceeds to step S204, and if it is equal to or less than the set value Ps (if P2 ⁇ Ps), the procedure proceeds to step S207.
- the accumulated oil control unit 32 determines whether the discharge pressure Pp of the hydraulic pump 21 detected by the pressure sensor 53 is smaller than the pressure Pa of the accumulated oil in the accumulator 26 detected by the pressure sensor 54 (Pp ⁇ Pa) is determined. If the discharge pressure Pp is smaller than the pressure Pa (Pp ⁇ Pa), the procedure proceeds to step S205, and if it is equal to or higher than the pressure Pa, the procedure proceeds to step S206.
- Step S205 is a process of releasing the accumulated oil in the accumulator 26.
- step S205 the pressure accumulation oil control unit 32 demagnetizes the control valves 27 and 28, closes the pressure accumulation control valve 27, and simultaneously opens the discharge control valve 28 to the state shown in FIG. Thereby, the connection between the accumulator 26 and the bottom oil chamber of the hydraulic cylinder 20 is cut off, and the accumulator 26 is connected to the discharge pipe 21 a of the hydraulic pump 21.
- step S205 is executed via step S202
- regeneration is performed if the discharge pressure Pp of the hydraulic pump 21 is lower than the pressure Pa of the accumulated oil. The That is, the accumulated oil merges with the oil discharged from the hydraulic pump 21 and is supplied to the hydraulic cylinder 20 via the control valve 22.
- step S205 is executed via step S204. It is regenerated.
- the process of step S205 is executed without the determination of steps S202 and S204
- the accumulated oil in the accumulator 26 is returned to the tank via the control valve 22. It is.
- step S206 is a process of storing the return pressure oil from the hydraulic cylinder 20 in the accumulator 26 (accumulation process).
- the pressure accumulation oil control unit 32 excites the control valves 27 and 28, opens the pressure accumulation control valve 27, and closes the discharge control valve 28 at the same time. As a result, the connection between the discharge pipe 21 a of the hydraulic pump 21 and the accumulator 26 is cut off, and the bottom oil chamber of the hydraulic cylinder 20 is connected to the accumulator 26.
- the pressure oil pushed out from the bottom oil chamber of the hydraulic cylinder 20 flows into the accumulator 26 and is accumulated. Even if the bottom oil chamber of the hydraulic cylinder 20 has a pressure lower than the pressure Pa, the accumulated oil in the accumulator 26 does not flow into the bottom pipe line 20a by the check valve 42.
- Step S207 is a process for holding the pressure-accumulated oil in the accumulator 26 (without pressure accumulation and regeneration) when there is no operation when the engine 24 is normally started.
- the pressure accumulation oil control unit 32 demagnetizes the control valve 27 and simultaneously excites the control valve 28 to close both the control valves 27 and 28. As a result, the connection between the accumulator 26 and the discharge pipe 21a of the hydraulic pump 21 and the connection between the accumulator 26 and the bottom oil chamber of the hydraulic cylinder 20 are cut off, and the accumulated oil in the accumulator 26 is held.
- step S205 when the engine speed N is low, such as when the engine stalls, is lower than the set value Ns, the process of step S205 is executed and the control valve 28 for release is opened.
- the accumulator 26 is connected to the discharge pipe 21 a of the hydraulic pump 21.
- the pilot pressure output from the pilot pump 23 decreases as the engine speed decreases due to the override characteristic of the pilot relief valve 23a.
- the pressure (operation signals P1, P2) that can be applied to the operation ports 22a, 22b is lowered, and the control valve 22 is in a neutral position regardless of whether the operation device 25 is operated.
- the accumulated oil in the accumulator 26 flows down to the tank through the discharge control valve 28, the check valve 43, and the control valve 22. That is, even if the operator gets off without restarting the engine 24 when the engine 24 is stopped, etc., the accumulated pressure in the accumulator 26 is connected to the tank via the control valve 22 that returns to the neutral position hydraulically. Oil is automatically released. Therefore, even if the procedure for releasing the accumulated oil in the accumulator 26 is forgotten when the engine 24 is stopped or the like, the gas in the gas chamber in the accumulator 26 can be prevented from dissolving into the accumulated oil. Further, by releasing the pressure accumulation oil in the accumulator 26, it is possible to prevent the pressure oil from being unexpectedly ejected during maintenance work of the accumulator 26 or the hydraulic piping, for example.
- the engine controller 38 determines the rotation state of the engine 24, and the rotation state determination unit 31 is provided so that the rotation state determination unit 31 separately determines the rotation state of the engine 24.
- the rotational state determination unit 31 can detect an abnormality in the rotational state of the engine 24 that could not be detected by the engine controller 38. Thereby, it is possible to more reliably suppress forgetting to remove the accumulated oil in the accumulator 26.
- either the determination by the engine controller 38 or the determination by the rotation state determination unit 31 may be excluded from the basic information of the pressure accumulation oil control.
- the determination of the engine controller 38 is removed, for example, the determination in step S101 of the procedure of FIG. 3 by the rotation state determination unit 31 is omitted.
- the rotation state determination unit 31 itself is omitted, and the determination signal F1 of the engine controller 38 is 1 or 0 in the determination in step S201 of the procedure of FIG. Determine.
- the engine controller 38 is a rotational state determination unit.
- the set value Ns used in the engine controller 38 and the rotation state determination unit 31 may be the same value or different values. For example, if the set value Ns used in the rotational state determination unit 31 is set higher than the set value Ns used in the engine controller 38, energy efficiency can be reduced, but gas dissolution into the pressure-accumulated oil can be further suppressed.
- the discharge control valve 28 is of a normally closed type, when a rotation abnormality occurs in the engine 24, a command signal is not output from the pressure accumulation oil control unit 32 due to an electrical system failure or the like. If the solenoid cannot be excited, the accumulated oil in the accumulator 26 is not released. In contrast, in this embodiment, since the control valve 28 is a normally open type, the accumulator 26 is naturally connected to the discharge line 21 a of the hydraulic pump 21 in a situation where the command signal cannot be output from the pressure accumulation oil control unit 32. At this time, if the engine 24 is stopped or the like, the control valve 22 becomes neutral, so that the accumulated oil can be discharged to the tank. However, when it is not assumed that a command signal cannot be output from the pressure accumulation oil control unit 32, the discharge control valve 28 may be a normally closed type.
- FIG. 5 is a circuit diagram showing the main part of the hydraulic system provided in the work machine according to the second embodiment of the present invention. This figure corresponds to FIG. 2 of the first embodiment.
- elements corresponding to those described in the first embodiment are denoted by the same reference numerals as those in FIG.
- the present embodiment is different from the first embodiment in that a pressure sensor 55 for detecting the pilot pressure Po output from the pilot pump 23 is provided, and the engine speed N is determined based on the signal from the pressure sensor 55 by the rotation state determination unit 31. It is a point to determine whether or not it is less than the set value Ns. Since other points of the present embodiment are the same as those of the first embodiment, description thereof will be omitted, and differences from the first embodiment will be described below.
- the rotation speed of the pilot pump 23 varies depending on the engine rotation speed N.
- the signal of the pressure sensor 55 is input to the rotation state determination unit 31 and it is estimated from the magnitude relationship between the pilot pressure Po and the set value Pq that the engine speed N has decreased below the set value Ns.
- the set value Pq is a value of the pilot pressure Po when the engine speed N is the set value Ns, and is set in advance and stored in another storage device included in the rotation state determination unit 31 or the hydraulic system controller 30. It is referred to by the rotation state determination unit 31 when necessary. Other configurations are the same as those of the first embodiment.
- FIG. 6 is a flowchart showing the output procedure of the identification signal by the rotation state determination unit 31 of this embodiment. This figure corresponds to FIG. 3 of the first embodiment.
- the series of processes shown in FIG. 6 is repeatedly executed by the rotation state determination unit 31 at a predetermined cycle time (for example, 0.1 s) while the hydraulic system controller 30 is energized.
- step S102 The procedure in FIG. 6 is different from the procedure in FIG. 3 only in that the process in step S102 is replaced by step S102a.
- the other processes in steps S101 and S103-S105 are the same as the processes with the same numbers in FIG. is there.
- the procedure proceeds to step S102.
- step S102a the rotation state determination unit 31 determines whether the pilot pressure Po detected by the pressure sensor 55 is smaller than the set value Pq.
- the procedure of the pressure accumulation oil control unit 32 is the same as that of the first embodiment. Also in this embodiment, the same effect as the first embodiment can be obtained.
- FIG. 7 is a circuit diagram showing the main part of the hydraulic system provided in the work machine according to the third embodiment of the present invention. This figure corresponds to FIG. 2 of the first embodiment.
- elements corresponding to those described in the first embodiment are denoted by the same reference numerals as those in FIG.
- This embodiment is different from the first embodiment in that a tank pipe line 61 and a tank valve 62 are added. Since other points of the present embodiment are the same as those of the first embodiment, description thereof will be omitted, and differences from the first embodiment will be described below.
- the tank pipe 61 branches from between the control valves 27 and 28 in the bypass pipe 41 (strictly, between the check valve 42 and the discharge control valve 28) and does not pass through the control valve 22 (bypass the control valve 22).
- the tank valve 62 is a normally open type electromagnetically driven on / off valve, and is provided in the middle of the tank pipeline 61.
- the tank valve 62 is driven by a command signal from the pressure accumulation oil control unit 32 to open and close the tank pipeline 61.
- the tank pipe 61 may be provided with an oil filter (not shown) or a check valve (not shown) for preventing backflow, but in the present embodiment, other control valves of the tank valve 62 are not provided (however, are necessary). Depending on the situation). Then, when it is determined that the engine speed N is less than the set value Ns, the pressure accumulation oil control unit 32 of the present embodiment opens the tank valve 62 together with the control valve 28 when opening the control valve 28 for discharge. Execute the process.
- FIG. 8 is a flowchart showing a control procedure of the accumulated oil amount by the accumulated oil control unit provided in the work machine according to the third embodiment of the present invention.
- This figure corresponds to FIG. 4 of the first embodiment.
- the series of processes shown in the figure is repeatedly executed at a predetermined cycle time (for example, 0.1 s) by the pressure accumulation oil control unit 32 while the hydraulic system controller 30 is energized.
- the procedure of FIG. 8 is different from the procedure of FIG. 4 in that the process of steps S205 to S207 is replaced by the process of steps S205a to S207a and the process of step S208a is added. Except for this point, the second embodiment is the same as the first embodiment (FIG. 4).
- Step S205a is a process for releasing the accumulated oil in the accumulator 26, and the release process of the present embodiment is different from the release process of the first embodiment.
- the accumulator control unit 32 demagnetizes the control valves 27, 28 and the tank valve 62, closes the accumulator control valve 27, and simultaneously opens the discharge control valve 28 and the tank valve 62, as shown in FIG.
- the control valve 22 is in the neutral position as the engine speed N decreases as described above. As a result, the connection between the accumulator 26 and the bottom oil chamber of the hydraulic cylinder 20 is cut off, the accumulator 26 is connected to the tank via the bypass line 41 and the tank line 61, and the accumulated oil is discharged.
- Step S208a is a regeneration process, and the behavior of the pressure-accumulated oil is the same as the release process that is executed during operation in the first embodiment.
- the pressure accumulation oil control unit 32 demagnetizes the control valves 27 and 28 to excite the tank valve 62, closes the pressure accumulation control valve 27 and the tank valve 62, and simultaneously opens the discharge control valve 28. Since the control valve 22 is driven during the execution of step S208a, the accumulated oil in the accumulator 26 merges with the discharge oil of the hydraulic pump 21 to drive the hydraulic cylinder 20.
- step S206a the pressure accumulation oil control unit 32 excites the control valves 27 and 28 and the tank valve 62, opens the pressure accumulation control valve 27, and closes the discharge control valve 28 and the tank valve 62 at the same time.
- step S207a the pressure accumulation oil control unit 32 moves from step S201 to S203 to step S207a, executes the process of holding pressure accumulation oil, and ends the procedure of FIG.
- the behavior of the pressure-accumulated oil when step S207a is executed is the same as the behavior of the pressure-accumulated oil when step S207 of the first embodiment is executed.
- step S207a the pressure accumulation oil control unit 32 demagnetizes the control valve 27 to excite the control valve 28 and the tank valve 62, and closes the control valves 27 and 28 and the tank valve 62.
- the procedure of the rotation state determination unit 31 is the same as that of the first embodiment.
- the tank valve 62 is opened in addition to the discharge control valve 28 when step S205a is executed.
- the control valve 22 is bypassed and the accumulator 26 is connected to the tank. Therefore, the accumulated pressure oil can be reliably discharged even if the control valve 22 does not return to the neutral position when the engine is abnormal for some reason. it can. In addition to the certainty of discharging the accumulated oil, the speed is improved.
- tank valve 62 is also a normally open type like the control valve 28 for discharge, it contributes to the suppression of forgetting to release the accumulated oil.
- FIG. 9 is a circuit diagram showing the main part of the hydraulic system provided in the work machine according to the fourth embodiment of the present invention. This figure corresponds to FIG. 2 of the first embodiment. 9, elements corresponding to those described in the first embodiment are denoted by the same reference numerals as those in FIG.
- This embodiment is different from the first embodiment in that a normally open and hydraulically driven discharge control valve 28a is used in place of the electromagnetically driven discharge control valve 28. Since other points of the present embodiment are the same as those of the first embodiment, description thereof will be omitted, and differences from the first embodiment will be described below.
- a branch pipe 63 branches from a portion upstream of the operating device 25 in the discharge pipe of the pilot pump 23.
- the branch pipe 63 is connected to the operation port of the discharge control valve 28 a via an electromagnetically driven switching valve 65 and a pilot pipe 64.
- the switching valve 65 is driven by a command signal from the pressure accumulating oil control unit 32, and connects the pilot line 64 to the tank during normal time (demagnetization) and connects the pilot line 64 to the branch line 63 during excitation.
- FIG. 10 is a flowchart showing a control procedure of the accumulated oil amount by the accumulated oil control unit provided in the work machine according to the fourth embodiment of the present invention.
- This figure corresponds to FIG. 4 of the first embodiment.
- the series of processes shown in the figure is repeatedly executed at a predetermined cycle time (for example, 0.1 s) by the pressure accumulation oil control unit 32 while the hydraulic system controller 30 is energized.
- the command objects in steps S205 to S207 are the control valves 27 and 28
- the command objects in steps S205b to S207b are the pressure control valve 27 and the switching valve 65.
- the present embodiment is different from the first embodiment.
- Steps S205 to S207 and Steps S205b to S207b are in a corresponding relationship, and there is no difference in the flow of the accumulated oil. That is, the control valves 27 and 28a of the present embodiment that are directly related to the intake and discharge of the pressure accumulation oil open and close under the same conditions as the control valves 27 and 28 of the first embodiment.
- the switching valve 65 When the switching valve 65 is demagnetized, the operation port is connected to the tank via the pilot line 64 and the switching valve 65, so that the discharge control valve 28a is opened.
- step S206b the pressure accumulation oil control unit 32 excites the control valve 27 and the switching valve 65.
- the operation port is connected to the pilot pump 23 via the pilot pipe 64, the switching valve 65, and the branch pipe 63, whereby the discharge control valve 28a is closed.
- the accumulator 26 is connected to the bottom oil chamber of the hydraulic cylinder 20 and accumulated, as in the case where step S206 is executed in the first embodiment.
- step S207b the pressure accumulation oil control unit 32 demagnetizes the control valve 27 and excites the switching valve 65. As a result, the control valves 27 and 28a are closed, and the pressure accumulation oil in the accumulator 26 is held in the same manner as when step S207 is executed in the first embodiment.
- FIG. 11 is a circuit diagram showing the main part of the hydraulic system provided in the work machine according to the fifth embodiment of the present invention. This figure corresponds to FIG. 9 of the fourth embodiment.
- elements corresponding to those described in the fourth embodiment are denoted by the same reference numerals as those in FIG.
- This embodiment is different from the fourth embodiment in that the rotation state determination unit 31 of the hydraulic system controller 30 is omitted. Since other points of the present embodiment are the same as those of the first embodiment, description thereof will be omitted, and differences from the first embodiment will be described below.
- the pilot pressure Po output from the pilot pump 23 decreases as the engine speed N decreases.
- the control valve 28a for discharge does not operate and is in the open position. That is, when the normally open type control valve 28a is used that is closed by inputting the pilot pressure Po to the operation port, the accumulator 26 is connected to the tank when the rotation of the engine 24 is abnormal regardless of the position of the switching valve 65. Even if the procedure of identifying the rotation abnormality of the engine 24 and opening the release control valve 28a in step S201 in FIG. 4 is omitted, in the present embodiment, the control valve 28a is naturally hydraulically when the rotation of the engine 24 is abnormal. open.
- step S201 of controlling the pressure-accumulated oil when the pressure-accumulated oil control unit 32 is normal (steps S202 to S207 in FIG. 4) is omitted while the function (step S201) of discharging the pressure-accumulated oil when abnormal is omitted.
- 28a itself also serves as a pressure-accumulating oil discharge device that functions in the event of an abnormality.
- the process of step S201 is omitted, as long as the control valve 28a is operated when the rotation of the engine 24 is abnormal, the rotation state determination unit 31 and the device used for the determination process are unnecessary. Therefore, although the engine switch 35, the rotation speed sensor 36, the engine control dial 37, and the engine controller 38 are omitted in FIG. 11, they are actually present to ensure the normal function of the work machine.
- the engine can be omitted even if the rotational state determination unit 31 is omitted as in the present embodiment. It is possible to realize the automatic discharge of the accumulated oil when the rotation abnormality is 24.
- the configuration in which the bottom side of the boom cylinder 17 is connected to the swing body 2 and the rod side is connected to the boom 11 is illustrated, but the bottom side of the boom cylinder may be connected to the swing body and the rod side may be connected to the boom. good. Even in this case, when the work implement descends, that is, when the boom cylinder contracts, the return pressure oil is pushed out from the bottom side, so the circuit configuration does not change.
- etc. Using the engine 24 (internal combustion engine) as a prime mover was illustrated, this invention is applicable also to the working machine which employ
- rotational speed sensor 38 ... engine controller (prime motor control device), 41 ... bypass Pipe, 51-55 ... Pressure sensor, 61 ... Tank pipe, 62 ... Tank valve, N ... Engine speed, Ns ... Installation Values, P1, P2 ... operation signal, Po ... pilot pressure, Se ... start command signal
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Analytical Chemistry (AREA)
- Chemical & Material Sciences (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
Abstract
Description
・作業機械
図1は本発明に係る作業機械の代表例である油圧ショベルの外観構成を表す側面図である。以下の説明において断り書きのない場合は運転席の前方(同図中では左方向)を機体の前方とする。但し、油圧ショベルの例示は本発明の適用対象を限定するものではなく、上下に回動する作業機を持つ作業機械であれば、クレーン等の他種の作業機械にも本発明は適用され得る。
図2は本発明の第1実施形態に係る作業機械に備えられた油圧システムの要部を表す回路図である。同図に示したように、図1に示した作業機械には油圧シリンダ20を駆動する油圧システムが備わっている。油圧シリンダ20は作業機3を駆動する油圧アクチュエータであり、本実施形態ではブームシリンダ17である場合を説明するが、油圧シリンダ20をアームシリンダ18又はバケットシリンダ19とすることもできる。この油圧システムは、油圧ポンプ21、コントロールバルブ22、パイロットポンプ23、エンジン24、操作装置25、アキュムレータ26、制御弁27,28、油圧システムコントローラ30等を備えている。
図3は回転状態判定部31による識別信号の出力手順を表すフローチャートである。同図に示した一連の処理は、油圧システムコントローラ30に通電されている間、回転状態判定部31によって所定のサイクルタイム(例えば0.1s)で繰り返し実行される。
(1)本実施形態においては、エンスト時を含めてエンジン回転数Nが設定値Nsを下回るような低速回転である場合、ステップS205の処理が実行され放出用の制御弁28が開かれてアキュムレータ26が油圧ポンプ21の吐出管路21aに接続する。このとき、パイロットリリーフ弁23aのオーバーライド特性によってパイロットポンプ23から出力されるパイロット圧がエンジン回転数の低下に伴って低下する。すると操作ポート22a,22bに掛かり得る圧力(操作信号P1,P2)が下がり、コントロールバルブ22は操作装置25の操作の有無に関係なく中立位置になる。これによりアキュムレータ26内の蓄圧油は放出用の制御弁28、チェック弁43、コントロールバルブ22を通ってタンクに流れ落ちる。つまりエンジン24が停止した場合等にエンジン24を再始動せずにオペレータが降車したとしても、油圧的に自然と中立位置に復帰するコントロールバルブ22を介してタンクに繋がることでアキュムレータ26内の蓄圧油が自動的に放出される。従ってエンジン24が停止した場合等にアキュムレータ26内の蓄圧油の放出手続きをし忘れても、蓄圧油にアキュムレータ26内のガス室内のガスが溶け出すことを抑制できる。またアキュムレータ26内の蓄圧油が放出されることで、例えばアキュムレータ26や油圧配管の整備作業中において不測に圧油が噴出することも防止できる。
図5は本発明の第2実施形態に係る作業機械に備えられた油圧システムの要部を表す回路図である。同図は第1実施形態の図2に対応している。図5において第1実施形態で説明した要素に対応する要素には図2と同符号を付してある。本実施形態が第1実施形態と相違する点は、パイロットポンプ23が出力するパイロット圧Poを検出する圧力センサ55を設け、回転状態判定部31によって圧力センサ55の信号に基づきエンジン回転数Nが設定値Ns未満か否かを判定する点である。本実施形態の他の点は第1実施形態と同様であるので説明を省略することとし、第1実施形態との相違点について以下に説明する。
図7は本発明の第3実施形態に係る作業機械に備えられた油圧システムの要部を表す回路図である。同図は第1実施形態の図2に対応している。図7において第1実施形態で説明した要素に対応する要素には図2と同符号を付してある。本実施形態が第1実施形態と相違する点は、タンク管路61とタンク弁62が加わった点である。本実施形態の他の点は第1実施形態と同様であるので説明を省略することとし、第1実施形態との相違点について以下に説明する。
図9は本発明の第4実施形態に係る作業機械に備えられた油圧システムの要部を表す回路図である。同図は第1実施形態の図2に対応している。図9において第1実施形態で説明した要素に対応する要素には図2と同符号を付してある。本実施形態が第1実施形態と相違する点は、電磁駆動式の放出用の制御弁28に代えてノーマルオープン型で油圧駆動式の放出用の制御弁28aを用いた点である。本実施形態の他の点は第1実施形態と同様であるので説明を省略することとし、第1実施形態との相違点について以下に説明する。
図11は本発明の第5実施形態に係る作業機械に備えられた油圧システムの要部を表す回路図である。同図は第4実施形態の図9に対応している。図11において第4実施形態で説明した要素に対応する要素には図9と同符号を付してある。本実施形態が第4実施形態と相違する点は、油圧システムコントローラ30の回転状態判定部31を省略した点である。本実施形態の他の点は第1実施形態と同様であるので説明を省略することとし、第1実施形態との相違点について以下に説明する。
以上の実施形態は適宜組み合わせ可能である。例えば第3実施形態や第4実施形態で第2実施形態と同様に圧力センサ55の信号を基にエンジン24の回転状態を判定する構成としても良い。また、第4実施形態や第5実施形態で第3実施形態のようなタンク弁62を加えた構成とすることもできる。
Claims (8)
- 作業機械本体と、前記作業機械本体に取り付けられた作業機と、前記作業機を駆動する油圧シリンダと、前記油圧シリンダを駆動する圧油を吐出する油圧ポンプと、前記油圧ポンプの吐出管路の接続先を切り換えて前記油圧シリンダのボトム油室、ロッド油室及びタンクの少なくとも1つに接続するコントロールバルブと、前記コントロールバルブを駆動するパイロット圧を出力するパイロットポンプと、前記油圧ポンプ及び前記パイロットポンプを駆動する原動機と、前記パイロットポンプから出力されたパイロット圧を操作に応じて減圧し前記コントロールバルブを駆動する操作信号を生成する操作装置と、前記油圧シリンダからの戻り圧油を蓄えるアキュムレータを備えた作業機械において、
前記コントロールバルブをバイパスして前記油圧シリンダのボトム油室と前記油圧ポンプの吐出管路を接続すると共に前記アキュムレータを設置したバイパス管路と、
前記バイパス管路における前記油圧シリンダのボトム油室と前記アキュムレータの間に設けた蓄圧用の制御弁と、
前記バイパス管路における前記アキュムレータと前記油圧ポンプの吐出管路の間に設けた放出用の制御弁と、
前記原動機の回転数が設定値未満になったら前記放出用の制御弁を開く制御を行う制御装置を備えたことを特徴とする作業機械。 - 請求項1に記載の作業機械において、前記制御装置は、
前記原動機の回転数が前記設定値未満か否かを判定する回転状態判定部と、
前記回転状態判定部の判定結果に基づき前記原動機の回転数が前記設定値未満であると判定された場合に前記放出用の制御弁を開く指令信号を出力する蓄圧油制御部を備えていることを特徴とする作業機械。 - 請求項2に記載の作業機械において、
前記原動機の回転数を検出する回転数センサ、又は前記パイロットポンプが出力するパイロット圧を検出する圧力センサを備えており、
前記回転状態判定部は、前記回転数センサ又は前記圧力センサの信号に基づき前記原動機の回転数が前記設定値未満か否かを判定することを特徴とする作業機械。 - 請求項2に記載の作業機械において、
前記原動機の回転数を検出する回転数センサと、
前記原動機を制御する制御装置であって、前記回転数センサで検出された検出結果に基づき前記原動機の回転状態の判定信号を出力する原動機制御装置を備え、
前記回転状態判定部は、前記原動機制御装置の判定信号に基づき前記原動機の回転状態が不良であると判定された場合に前記原動機の回転数が前記設定値未満であることを識別する識別信号を出力することを特徴とする作業機械。 - 請求項2に記載の作業機械において、
前記原動機の回転数を検出する回転数センサと、
前記原動機の起動を指令する原動機スイッチを備え、
前記回転状態判定部は、前記原動機スイッチから起動指令信号が入力され、かつ前記回転数センサで検出された前記原動機の回転数が前記設定値未満である場合に、前記原動機の回転数が前記設定値未満であることを識別する識別信号を出力することを特徴とする作業機械。 - 請求項2に記載の作業機械において、
前記バイパス管路における前記蓄圧用の制御弁と前記放出用の制御弁の間から分岐し前記コントロールバルブをバイパスして前記タンクに接続するタンク管路と、
前記タンク管路を開閉するタンク弁を備え、
前記蓄圧油制御部は、前記原動機の回転数が前記設定値未満であることが識別された場合に前記放出用の制御弁と共に前記タンク弁を開くことを特徴とする作業機械。 - 請求項2に記載の作業機械において、前記放出用の制御弁は、前記蓄圧油制御部の指令信号により励磁されて閉じる電磁駆動式でノーマルオープン型の制御弁であることを特徴とする作業機械。
- 請求項1に記載の作業機械において、前記放出用の制御弁は、前記パイロットポンプが出力するパイロット圧が入力されて閉じる油圧駆動式でノーマルオープン型の制御弁であることを特徴とする作業機械。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2019508462A JP6752963B2 (ja) | 2017-03-29 | 2017-03-29 | 作業機械 |
US16/327,928 US10801532B2 (en) | 2017-03-29 | 2017-03-29 | Work machine |
KR1020197004026A KR102160761B1 (ko) | 2017-03-29 | 2017-03-29 | 작업 기계 |
CN201780049202.7A CN109563861B (zh) | 2017-03-29 | 2017-03-29 | 作业机械 |
PCT/JP2017/013074 WO2018179183A1 (ja) | 2017-03-29 | 2017-03-29 | 作業機械 |
EP17903524.1A EP3604827B1 (en) | 2017-03-29 | 2017-03-29 | Working machine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2017/013074 WO2018179183A1 (ja) | 2017-03-29 | 2017-03-29 | 作業機械 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2018179183A1 true WO2018179183A1 (ja) | 2018-10-04 |
Family
ID=63674378
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2017/013074 WO2018179183A1 (ja) | 2017-03-29 | 2017-03-29 | 作業機械 |
Country Status (6)
Country | Link |
---|---|
US (1) | US10801532B2 (ja) |
EP (1) | EP3604827B1 (ja) |
JP (1) | JP6752963B2 (ja) |
KR (1) | KR102160761B1 (ja) |
CN (1) | CN109563861B (ja) |
WO (1) | WO2018179183A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2019124227A (ja) * | 2018-01-11 | 2019-07-25 | 株式会社小松製作所 | 油圧回路 |
JP2020085194A (ja) * | 2018-11-29 | 2020-06-04 | 日立建機株式会社 | 建設機械 |
CN111577714A (zh) * | 2020-05-18 | 2020-08-25 | 山东临工工程机械有限公司 | 一种液压***及工程机械 |
WO2024057384A1 (ja) * | 2022-09-13 | 2024-03-21 | 株式会社ニチダイ | 油圧装置及び作動方法 |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6552996B2 (ja) * | 2016-06-07 | 2019-07-31 | 日立建機株式会社 | 作業機械 |
KR102078224B1 (ko) * | 2017-03-27 | 2020-02-17 | 히다치 겡키 가부시키 가이샤 | 작업 기계의 유압 제어 시스템 |
US11067004B2 (en) * | 2018-03-27 | 2021-07-20 | Pratt & Whitney Canada Corp. | Gas turbine engine fluid system with accumulator and hydraulic accessory |
WO2021097699A1 (zh) * | 2019-11-20 | 2021-05-27 | 徐州重型机械有限公司 | 液压*** |
US12018458B2 (en) * | 2020-06-17 | 2024-06-25 | Hitachi Construction Machinery Co., Ltd. | Construction machine |
WO2021261051A1 (ja) * | 2020-06-22 | 2021-12-30 | 日立建機株式会社 | 建設機械 |
WO2023229409A1 (ko) * | 2022-05-27 | 2023-11-30 | 레디로버스트머신 주식회사 | 건설기계용 붐 에너지 회수 유압시스템 |
WO2023234641A1 (ko) * | 2022-06-02 | 2023-12-07 | 레디로버스트머신 주식회사 | 에너지 재생 기능이 포함된 건설기계용 붐 실린더의 낙하방지 유압밸브 시스템 |
WO2023234642A1 (ko) * | 2022-06-02 | 2023-12-07 | 레디로버스트머신 주식회사 | 에너지 재생 기능이 포함된 건설기계용 붐 실린더의 낙하방지 유압밸브 어셈블리를 포함하는 붐 에너지 회수 시스템 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009275771A (ja) * | 2008-05-13 | 2009-11-26 | Caterpillar Japan Ltd | 流体圧アクチュエータ制御回路 |
JP2012013203A (ja) * | 2010-07-05 | 2012-01-19 | Kobelco Cranes Co Ltd | 作業機械の駆動装置 |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4831679B1 (ja) | 1969-12-02 | 1973-10-01 | ||
US6167701B1 (en) * | 1998-07-06 | 2001-01-02 | Caterpillar Inc. | Variable rate ride control |
JP4294563B2 (ja) * | 2004-09-10 | 2009-07-15 | 日立建機株式会社 | 作業機械 |
JP2007170485A (ja) * | 2005-12-20 | 2007-07-05 | Shin Caterpillar Mitsubishi Ltd | エネルギ回収・再生装置 |
JP4831679B2 (ja) | 2006-05-23 | 2011-12-07 | キャタピラー エス エー アール エル | 作業機械における油圧制御システム |
JP2008089023A (ja) * | 2006-09-29 | 2008-04-17 | Kobelco Contstruction Machinery Ltd | 油圧アクチュエータの制御装置及びこれを備えた作業機械 |
US7634911B2 (en) * | 2007-06-29 | 2009-12-22 | Caterpillar Inc. | Energy recovery system |
WO2012082728A2 (en) * | 2010-12-13 | 2012-06-21 | Eaton Corporation | Hydraulic system for energy regeneration in a work machine such as a wheel loader |
CN202081450U (zh) * | 2011-01-11 | 2011-12-21 | 浙江大学 | 一种油液混合动力挖掘机动臂势能差动回收*** |
US10280948B2 (en) * | 2014-04-04 | 2019-05-07 | Volvo Construction Equipment Ab | Hydraulic system and method for controlling an implement of a working machine |
JP6205339B2 (ja) * | 2014-08-01 | 2017-09-27 | 株式会社神戸製鋼所 | 油圧駆動装置 |
WO2016147283A1 (ja) * | 2015-03-16 | 2016-09-22 | 日立建機株式会社 | 建設機械 |
US9932993B2 (en) * | 2015-11-09 | 2018-04-03 | Caterpillar Inc. | System and method for hydraulic energy recovery |
DE102016002134A1 (de) * | 2016-02-23 | 2017-08-24 | Liebherr-Mining Equipment Colmar Sas | Vorrichtung zur Rekuperation von hydraulischer Energie sowie Arbeitsmaschine mit entsprechender Vorrichtung |
DE102016007267A1 (de) * | 2016-06-15 | 2017-12-21 | Liebherr-Mining Equipment Colmar Sas | Vorrichtung zur Rekuperation von hydraulischer Energie mittels einer Verschaltung von zwei Differentialzylindern |
DE102016007286A1 (de) * | 2016-06-15 | 2017-12-21 | Liebherr-Mining Equipment Colmar Sas | Vorrichtung zur Rekuperation von hydraulischer Energie mit energieeffizienter Nachfüllung der Stangenseiten von Differentialzylindern und gleichzeitiger Druckübersetzung |
KR102062193B1 (ko) * | 2016-09-23 | 2020-01-03 | 히다찌 겐끼 가부시키가이샤 | 작업 기계의 압유 에너지 회생 장치 |
-
2017
- 2017-03-29 JP JP2019508462A patent/JP6752963B2/ja active Active
- 2017-03-29 KR KR1020197004026A patent/KR102160761B1/ko active IP Right Grant
- 2017-03-29 CN CN201780049202.7A patent/CN109563861B/zh active Active
- 2017-03-29 US US16/327,928 patent/US10801532B2/en active Active
- 2017-03-29 WO PCT/JP2017/013074 patent/WO2018179183A1/ja unknown
- 2017-03-29 EP EP17903524.1A patent/EP3604827B1/en active Active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009275771A (ja) * | 2008-05-13 | 2009-11-26 | Caterpillar Japan Ltd | 流体圧アクチュエータ制御回路 |
JP2012013203A (ja) * | 2010-07-05 | 2012-01-19 | Kobelco Cranes Co Ltd | 作業機械の駆動装置 |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2019124227A (ja) * | 2018-01-11 | 2019-07-25 | 株式会社小松製作所 | 油圧回路 |
JP2020085194A (ja) * | 2018-11-29 | 2020-06-04 | 日立建機株式会社 | 建設機械 |
CN111577714A (zh) * | 2020-05-18 | 2020-08-25 | 山东临工工程机械有限公司 | 一种液压***及工程机械 |
CN111577714B (zh) * | 2020-05-18 | 2022-04-29 | 山东临工工程机械有限公司 | 一种液压***及工程机械 |
WO2024057384A1 (ja) * | 2022-09-13 | 2024-03-21 | 株式会社ニチダイ | 油圧装置及び作動方法 |
JP7474908B1 (ja) | 2022-09-13 | 2024-04-25 | 株式会社ニチダイ | 油圧装置及び作動方法 |
Also Published As
Publication number | Publication date |
---|---|
US20190186106A1 (en) | 2019-06-20 |
JPWO2018179183A1 (ja) | 2019-06-27 |
US10801532B2 (en) | 2020-10-13 |
CN109563861A (zh) | 2019-04-02 |
KR102160761B1 (ko) | 2020-09-28 |
EP3604827B1 (en) | 2023-09-20 |
KR20190026889A (ko) | 2019-03-13 |
CN109563861B (zh) | 2020-11-20 |
EP3604827A4 (en) | 2020-11-25 |
JP6752963B2 (ja) | 2020-09-09 |
EP3604827A1 (en) | 2020-02-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2018179183A1 (ja) | 作業機械 | |
KR101580933B1 (ko) | 쇼벨 및 쇼벨의 제어방법 | |
CN107614896B (zh) | 挖土机及挖土机的驱动方法 | |
JP4897612B2 (ja) | 作業機械 | |
WO2019130451A1 (ja) | 作業機械 | |
US20140345265A1 (en) | Hydraulic drive system | |
JP4806390B2 (ja) | 作業機械 | |
JP5096417B2 (ja) | 建設機械の油圧制御装置 | |
JP5113603B2 (ja) | 電動式作業機械 | |
KR102514523B1 (ko) | 건설기계의 유압 제어 장치 및 유압 제어 방법 | |
JP6842393B2 (ja) | 作業機械の圧油エネルギ回収装置 | |
JP7478588B2 (ja) | 油圧ショベル駆動システム | |
EP2628861B1 (en) | Control device for working machine | |
EP2811077B1 (en) | Boom driving system for hybrid excavator and control method therefor | |
JP2008190694A (ja) | オートデセル制御機能を備えた制御装置及びその制御方法 | |
JP2020085194A (ja) | 建設機械 | |
JP7460604B2 (ja) | ショベル | |
JP5534358B2 (ja) | 圧油エネルギ回収装置及びこれを用いた建設機械 | |
EP4345316A1 (en) | Construction machine | |
JP3088584B2 (ja) | 建設機械の油圧駆動装置 | |
JP6615868B2 (ja) | ショベルおよびショベルの駆動方法 | |
JP2021036126A (ja) | 作業機械の圧油エネルギ回収装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 17903524 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 20197004026 Country of ref document: KR Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 2019508462 Country of ref document: JP Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 2017903524 Country of ref document: EP Effective date: 20191029 |