WO1993006314A1 - Hydraulic oil amount change-over controlling device for hydraulic excavator - Google Patents
Hydraulic oil amount change-over controlling device for hydraulic excavator Download PDFInfo
- Publication number
- WO1993006314A1 WO1993006314A1 PCT/JP1992/001225 JP9201225W WO9306314A1 WO 1993006314 A1 WO1993006314 A1 WO 1993006314A1 JP 9201225 W JP9201225 W JP 9201225W WO 9306314 A1 WO9306314 A1 WO 9306314A1
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- WO
- WIPO (PCT)
- Prior art keywords
- engine
- hydraulic pump
- hydraulic
- signal
- differential pressure
- Prior art date
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Classifications
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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
- E02F9/2292—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
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
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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
- F15B2211/20538—Type of pump constant 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
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
- F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
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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
- F15B2211/20584—Combinations of pumps with high and low 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
- F15B2211/25—Pressure control functions
- F15B2211/253—Pressure margin control, e.g. pump pressure in relation to 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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/26—Power control functions
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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
- F15B2211/31—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
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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
- F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
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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
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
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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
- F15B2211/605—Load sensing 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position
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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
- F15B2211/6654—Flow rate 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
- F15B2211/70—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
- F15B2211/7058—Rotary output members
Definitions
- the present invention uses a hydraulic breaker as an attachment instead of the socket normally installed as a working machine of a hydraulic digging machine.
- the present invention relates to a hydraulic oil excavating machine switching control device for a hydraulic excavating machine. Background technology
- the hydraulic pump driven by the engine is controlled by controlling the number of revolutions of the engine at 1, ⁇ 2, N 3 (reV / min).
- variable displacement hydraulic pump (referred to below as the main pump) 5 1 has a curved surface 'boom ⁇ i ⁇ service ⁇ ham L 0 ⁇ left running
- the five operating valves that drive each actuator unit are connected to the paranoel, respectively, and the main pump 52 has a right running bucket.
- Five switching valves for driving each actuator of the service are connected to the parallel, respectively.
- two pipes 5 4 ⁇ 5 connected to the ⁇ port of the service valve 53 are provided. 5 are connected to a hydraulic circuit from a service valve 56 on the left side to an actuating unit 57 such as a blower, and are joined respectively. It has become so .
- the pedal 58 for manipulating the attachment corresponds to a pipe ⁇ 'pressure control valve (hereinafter referred to as a PPC valve) 39.
- the control pump 40 is used as an oil pressure source.
- One of the two pilot surfaces 4 1 • 4 2 coming out of the PC valve 39 is one of the left nozzles of the service valve 56. And the other one is connected to the right-bay mouth cylinder.
- branch paths 4 3 • 4 4 are respectively provided in the above-mentioned pipe pi-t paths 4 1 • 4 2, and a solenoid-type pipe ⁇ -tot surface is provided. They are connected to the left and right port cylinders of the service valve 53 via the road switching valves 45 and 46.
- the solenoids of these pipe ⁇ '-sto circuit switching valves 45 and 46 are respectively connected to switching switches 50. is When the pumping machine 57 needs a flow of two pumps, such as during normal excavation work, set the switching switch 50 to the 0 side. When this is operated, the solenoids of the pipe-pitting circuit switching valves 45, 46 are excited, and the branching surfaces of the pilot-port surfaces 41, 42 are energized. 4 3 • 4 4 leads through, and a pad pressure corresponding to the operation amount of the pedal 58 is applied to the service valve 53 and the service valve 56. Works on each left or right nodal mouth cylinder
- Each operating valve sub-controls the discharge amount of the main pump according to the movement of the nozzle, especially when all the operation valves are in the neutral position.
- a relief valve 47 and a relief 48 are provided in the main circuit.
- the discharge amount of the main pump 52 is controlled by controlling the flow adjustment mechanism 49 of the main pump 52 by the upstream pressure of the orifice 48. .
- the description of the discharge amount control of the main pump 51 is also omitted because it is the same as that of the main pump 52.
- the engine speed as shown in Fig. 2 above, the amount of oil required for the brake work and the fuel consumption of the engine are reduced.
- the specified load pressure ⁇ 0, immediately the absorption torque of the hydraulic pump ⁇ 0
- the oil fi necessary for the work is obtained.
- the fuel consumption of the engine is reduced by reducing the discharge amount of the pressure bomb, but the points A1, A2, and A3 above are indicated by B, etc.
- the fuel of the engine will decrease and the engine will be sufficient. It has been difficult to reduce fuel consumption of vehicles.
- the flow switching circuit as shown in Fig. 8 above there are the following problems.
- the circuit must be provided with two -port circuit switching valves 45 6 46, and the service valves 33 3 If two pipes 54, 55 are required to merge with the main surface of the actuator for dimmer 57, the hydraulic circuit must be combined. In addition, the reliability of the hydraulic excavator is reduced, and at the same time, the number of inspection and maintenance work is increased and the production cost is increased.
- the amount of oil to be supplied to the actuator 57 for the attachment is one-pump or two-pump two-stage switching. The flow rate cannot be finely adjusted.
- the present invention focuses on the above-mentioned conventional problems, and it is low in the case of operations such as burring operations that require a small amount of oil and sufficient for ordinary digging operations.
- the hydraulic pump is controlled by dosing to set the optimal amount of oil, and the hydraulic pump is also set.
- the engine that drives the pump should be driven at a low fuel consumption rate. Disclosure of the invention for the purpose of
- the present invention provides a variable displacement hydraulic pump, an engine for driving the hydraulic pump, an actuator driven by the hydraulic pump, An operation valve interposed in a pipeline between the hydraulic pump and the actuator, a load sensing control device for the hydraulic pump, a work mode switching device, The switching signal from the work mode switching device is input, the fuel injection amount signal is sent to the governor driving device of the engine, and the load sensing control device is sent to the load sensing control device. Since it is composed of a controller that outputs a differential pressure signal of the up-down flow of the operating valve, a relatively small amount of oil such as a breaker in a hydraulic excavator When driving a good actuator, set the work mode switching device to low.
- the controller When the engine is switched to the power mode, the controller outputs a low fuel injection amount signal to the engine governor drive, and the engine horsepower is increased. Along with the decrease, a differential pressure signal to reduce the differential pressure upstream and downstream of the actuator control valve is output to the load sensing control device. As a result, the capacity of the variable displacement hydraulic pump is reduced with respect to the predetermined operation amount of the operation valve for the actuator. Accordingly, the capacity of the variable displacement hydraulic pump is reduced, and the engine horsepower is reduced to a predetermined torque due to a decrease in the engine horsepower. Since the number of revolutions in the engine is also reduced, the discharge rate per unit time of the variable displacement type hydraulic bomb is reduced. Also
- the operation mode switching device When driving an actuator that requires a relatively large amount of oil, such as a digging operation, the operation mode switching device must be installed. When the mode is switched to the force set, the controller outputs a 13 ⁇ 4 fuel injection quantity signal to the engine governor drive. As the engine horsepower rises, a differential pressure signal that reduces the differential pressure upstream and downstream of the actuating valve for the actuator is reduced. Output to the hydraulic control unit, the capacity of the variable-capacity hydraulic pump increases with respect to the specified operation amount of the actuator for the actuator. Add. Therefore, as the capacity of the variable displacement hydraulic pump increases, the engine torque rises above the specified torque due to the increase in engine horsepower. Because the engine rotation speed is very large, the discharge per unit time of the variable displacement hydraulic pump increases.
- the controller described above uses the switching signal from the operation mode switching device to control the first engine fuel setting device and the first engine fuel setting device. Activate the load sensing differential pressure setting device to send the first engine fuel setting signal from the first engine fuel setting device.
- the first load sensing differential pressure setting signal is output to the engine fuel signal generator and the HiJ SC first port sense sensor is output. Output from the differential pressure setting device to the mouth sensing differential pressure signal generator, or the second engine fuel setting device and the second engine fuel setting device.
- the sensing differential pressure setting device Activate the sensing differential pressure setting device to output a second engine fuel setting signal from the second engine fuel setting device to the engine fuel signal generator.
- the second mouth sensing differential pressure setting signal is sent from the second load sensing differential pressure setting device to the load sensing differential pressure.
- a signal generator outputs the engine fuel injection amount signal from the engine fuel signal generator to a governor drive of the engine and the load sensor.
- the load sensing differential signal from the differential sensing signal generator is configured to be output to the load sensing control device.
- the switcher receives a switching signal from the work mode switching device, the switching signal causes the first engine fuel setting to be performed.
- Meter and the first load sensing differential pressure setter, or the second engine fuel setter and the second ⁇ —dose sensing differential pressure The setting device is activated.
- the first engine fuel setting signal is output to the engine fuel signal generator and the first load cell is output.
- the sensing differential pressure setting signal is output to the first mouthpiece sensing differential pressure signal generator and the second setting device is activated, the second sensor is activated.
- the engine fuel setting signal is output to the engine fuel signal generator, and the second load sensing differential pressure setting signal is output to the second load sensing. It is output to the differential pressure signal generator, and the fuel injection amount signal from the engine fuel signal generator is output.
- the load sensing control device includes a displacement control cylinder for the hydraulic pump and a load sensing device for supplying hydraulic pressure to the displacement control cylinder.
- the load sensing control valve reduces the capacity of the hydraulic pump by increasing the pressure difference between the upstream and downstream of the operation valve, and reduces the capacity of the hydraulic pump.
- the capacity of the hydraulic pump is increased by reducing the pressure difference downstream, and the port pressure is increased.
- the capacity of the hydraulic pump is reduced by increasing the differential sensing pressure signal, and the hydraulic pump is decreased by decreasing the load sensing differential pressure signal.
- the load sensing control device is configured to increase the capacity, so that when the operation valve is squeezed to speed up the actuator, the operation valve Since the pressure difference of the flow is increased, the hydraulic pump operates so that the capacity of the hydraulic pump is reduced and wasteful power is reduced. In addition, if the opening of the operating valve is increased to speed up the actuating unit, the pressure difference between the upstream and downstream of the operating valve decreases, so that the capacity of the hydraulic pump increases. And supply the required flow rate.
- the load sensing differential pressure signal is increased for the same operation amount of the operation valve, the capacity of the hydraulic pump is reduced, and the hydraulic pressure per unit time is reduced.
- the discharge amount of the pump is small and the load sensing differential pressure signal is reduced, the capacity of the hydraulic pump increases and the hydraulic pump per unit time increases.
- a variable displacement hydraulic pump an engine for driving the hydraulic pump, an actuator driven by the hydraulic pump, An operation valve interposed in a pipeline between the hydraulic pump and the actuator, a load-sensing control device for the hydraulic pump, and a capacity control of the hydraulic pump.
- a sensor a face-count sensor of the engine, a hydraulic sensor of the actuator, and a work mode switching device.
- Engine Input the signals of the rotation speed sensor and the hydraulic pressure sensor of the actuator, and specify the settings specified by the operation mode switching device.
- the engine computes the control signal at which the engine has the lowest fuel consumption at horsepower, and the load sensing control device and the engine governor described above are calculated.
- the hydraulic drilling machine Since it is composed of a controller that outputs to the drive unit, the hydraulic drilling machine has a relatively small flow rate, such as a break force, in the hydraulic drilling machine.
- the load sensor When driving the actuator which is good with the oil amount, if the operation valve is operated by the operation rail provided separately, the load sensor
- the capacity of the variable displacement type hydraulic pump is controlled by the ring capacity control device in accordance with the opening of the operating valve.
- the load-sensing control device of the variable displacement type hydraulic pump is composed of a hydraulic cylinder, a capacity control device, a driving cylinder, and a hydraulic pressure control device.
- the upstream and downstream oil pressures of the operating valve interposed in the pipe between the pump and the actuator are defined as the pipe port pressure, and the pipe pi
- the pressure difference of the hydraulic pump is increased, and the capacity of the hydraulic pump is reduced by increasing the control signal from the controller. Since the load sensing valve is configured to be operated, the capacity sensor of the hydraulic pump and the rotation speed sensor of the engine When the hydraulic pressure sensor of the actuator and the control signal input port from the operation mode switching device are input to the controller, the control
- the engine is operated with the minimum burnout at the specified horsepower specified by the operation mode switching device at The control signal is calculated, and the control signal is output to the load sensing capacity control device and the governor drive device of the engine. Therefore, when the engine is set to be driven with the minimum combustion in normal excavation work, a relatively small flow rate such as breaker work is required. Even if the operation mode is switched to a work mode that requires a large amount of oil, the engine is driven at the number of revolutions at which the engine has the minimum fuel at the horsepower.
- the control signal for operating the engine with the minimum fuel injection is the engine torque and the engine that is the minimum fuel injection power on the horsepower such as the engine.
- the load-sensing control device of the hydraulic pump is configured to control the hydraulic pressure upstream and downstream of the operation valve.
- load sensing is performed.
- the control pressure is supplied to the cylinder driven by the displacement control device of the hydraulic pump by the valve to reduce the capacity of the hydraulic pump.
- the control signal for operating the engine with the minimum fuel is the engine torque and the engine 11 speed that provide the minimum fuel consumption on the engine or other horsepower curve.
- FIGS. 1 and 2 are diagrams showing a first embodiment of the present invention
- FIG. 1 is a diagram showing an overall control circuit in the first embodiment
- FIG. 2 is a diagram showing the overall control circuit in the first embodiment
- FIG. 1 is a diagram showing details of the controller
- FIGS. 3 and 4 are diagrams showing a second embodiment of the present invention
- FIG. 3 is a diagram showing the second embodiment.
- Fig. 4 shows the overall control surface in the embodiment
- Fig. 4 shows the details of the controller in Fig. 3
- Fig. 5 and Fig. 6 show the control system.
- FIG. 5 is a diagram showing an embodiment common to the first embodiment and the second embodiment of the invention
- FIG. 5 is a diagram showing the horsepower of the engine in the plane T on one revolution N of the engine Fig.
- FIG. 6 shows the iso-combustion curve
- Fig. 6 shows the iso-absorption torque diagram TB and TS drawn on the hydraulic pump capacity V-pressure P plane
- Fig. 7 shows the conventional
- Fig. 8 shows the adjustment of the oil level of the hydraulic pump by engine surface rolling in the technology of Fig. 8
- Fig. 8 shows the merged switching of multiple hydraulic pumps in the conventional technology. It is a diagram showing a circuit BEST MODE FOR CARRYING OUT THE INVENTION
- 1 is an engine
- 1a is a gannon drive of the engine 1
- 2 is A hydraulic pump driven by the engine 1
- 3 is a breaker
- 4 is a line 5 a, 5 connecting the hydraulic pump 2 and the brake force 3.
- b a break force operating valve interposed
- 6a is a breaker operating resor for operating the breaker operating valve 4
- 1 and 6 are the breaker operating valves.
- a bi-port operation valve that generates a pipe port pressure corresponding to the operation amount of the operation lever 6a is used to drive the swash plate 2a of the hydraulic pump 2.
- the capacity control cylinder 7a is provided in the bottom chamber 7b of the capacity control cylinder 7, and urges the piston 7d in the direction of the rod chamber 7c.
- Spring, 7e oblique piston 7d ⁇ 2 is a piston rod for connecting to a
- 8 is a load sensing valve for switching the control pressure of the capacity control cylinder 7.
- a is a solenoid connected to the controller 10 for the port sensing valve 8
- 8 b is a port connected to the upstream line 5 a of the operation valve 4.
- a pilot cylinder of the dosing valve 8, 8 c is a pipe of the load sensing valve 8 connected to the downstream pipe 5 of the operating valve 4.
- Rot cylinder, 8 d is a differential pressure setting spring of load sensing valve 8
- 9 is a control pump as a control pressure source of displacement control cylinder 7, 1 0 inputs the switching signal from the work mode switching device.
- the fuel injection amount signal is supplied to the governor driving device S1a of the engine 1 and the solenoid of the load sensing valve 8 of the load sensing control device.
- the controller 10 is an engine fuel setter 11, 1 3 ⁇ ⁇ -Dosing differential pressure setting device 1 2, 1 4, engine fuel signal generator 1
- ⁇ consists of a dosing differential pressure signal generator 16.
- 17 to 23 are working mode switching devices, 17 is a power supply, 18 is a drilling mode button 5, a break force mode button ⁇ , and each return spring 18a , 18b work mode switch button, 19 is a magnet ⁇ 20 is a spring, 21 is a work mode switch, 22 is a self-holding switch Switches, 23 are splashes, and 24 are tanks.
- Torque of the engine — surface turnover In Fig. 5 showing the equal horsepower and equal-flame fuel curve on the N-plane.
- Fig. 5 showing the equal horsepower and equal-flame fuel curve on the N-plane.
- A is equal fuel-efficient power and the center is fuel. ⁇ 100%
- HPS is equal horsepower in excavation mode
- ⁇ ⁇ is equal horsepower curve in blast mode
- TS and ⁇ are The engine torque at the contact point between the above-mentioned HPS and HPB and the isometric fuel tube is shown.
- the drilling machine When the drilling machine is to be operated in the normal drilling mode, when the drilling mode button S of the working mode switching button 18 is pressed, the magnet Since the voltage of the power supply 17 is not applied to the switch 19, the magnet 19 is demagnetized, and the work mode switching switch 21 is driven by the spring 20. Connected to contact A. Therefore, the voltage of the power supply 17 is applied to the engine fuel setter 11 and the load sensing differential pressure setter 12 of the controller 10 ⁇ . Therefore, the engine fuel setting signal HS set by the engine fuel setting device 11 is applied to the engine fuel signal generator 15 and the mouth differential pressure difference. ⁇ The load sensing differential pressure setting signal set by the setting unit 12 is output to the differential pressure signal generator 16.
- the engine flint signal generator 15 is an additive function generator, and outputs the engine fuel signal i N corresponding to the engine fuel setting signal to the controller 10. As a result, the engine horsepower increases because the power is output to the governor driving device g1a of the engine 1.
- the load sensing differential pressure signal generator 16 is a decreasing factor generator, and has a low load corresponding to the above-mentioned load sensing differential pressure setting signal ⁇ 3.
- the sensing differential pressure signal iv is output from the control port 10 to the solenoid 8a of the load sensing valve 8, the load sensor The swing valve 8 moves in the direction a and the hydraulic oil in the bottom chamber 7b of the capacity control cylinder 7 is drained, so that the capacity of the hydraulic pump 2 increases. .
- the unit is driven by the high engine rotation and the hydraulic pump capacity.
- the hydraulic pump discharge amount can be increased, and each actuator can be operated at a high speed to improve the working efficiency.
- the operation mode switching button 18 of the operation mode switching button 18 is used.
- the button is pressed, the voltage of the power supply 17 is applied to the magnet 19, so that the magnet 19 is excited and the break mode is activated.
- the self-maintaining switch 22 is maintained at the C contact point, so that the magnet 19 retains the excitation and the work mode is maintained.
- the mode switching switch 21 is connected to the contact point ⁇ against the spring 20 and continues to be connected.
- the voltage of the power supply 17 is applied to the engine fuel setting device 13 and ⁇ -dosing differential pressure setting device 14 in the ⁇ 0.
- the low fuel consumption setting signal Hb set in the fuel consumption setting device 13 is transferred to the fuel consumption signal generator 15.
- the low-end sensing voltage setting signal ⁇ Pb set by the load sensing differential pressure setting device 14 is the differential pressure signal generator. It is output to 16.
- the engine fuel signal generator 15 is an additional function generator, which corresponds to the low engine fuel setting signal Hb described above.
- the engine horsepower is low because the engine fuel signal i N is output from the controller 10 to the governor drive 1a of the engine 1. Go down. And mouth — Dosen 3 6314
- the signal differential pressure signal generator 16 is a small function generator, and corresponds to the low load sensing differential pressure setting signal APb.
- iV is output from the controller 10 to the solenoid 8a of the load sensing valve 8
- the load sensing valve 8 moves to the b position.
- the hydraulic pump 2 moves in the direction and the hydraulic oil is supplied from the control pump 9 to the bottom chamber 7 b of the capacity control cylinder 7, so that the capacity of the hydraulic pump 2 is reduced.
- the breaker mode is operated with low engine turnover and low hydraulic pump capacity. Hydraulic pump discharge rate can be reduced.
- the first engine fuel setting device 11 and the first load sensing differential pressure setting device 12 in the con- troller 10 are provided.
- Either one of the second engine fuel setting device 13 and the second load sensing differential pressure setting device 14 is omitted, and the engine is replaced with the engine engine. It is also possible to preset the engine injection amount and the load sensing differential pressure of the load sensing control device.
- the setting devices 1 1> 12 or 13 or 14 in the controller 10 is omitted, switching from the work mode switching device is performed.
- the operation in the working mode not omitted is the same as that of the above-described embodiment, but the operation mode in the working mode omitted is omitted. Is set so that the engine fuel injection amount is set in advance. The governor was driven, and the load-sensing controller was set in advance. This will be the differential sensing pressure.
- reference numeral 1 denotes an engine 2 and a hydraulic pump driven by the engine 1.
- 3 is a brake force
- 4 is a brake force operation valve interposed in the pipelines 5a, 5b connecting the hydraulic bob 2 and the brake force 3
- 6a is A brake force operating lever 6 for operating the brake force operating valve 4
- 6 is an outlet pressure corresponding to the operation amount of the brake force operating lever 6 a.
- the pressure control cylinder 8 for driving the slope 2 a of the hydraulic pump 2 is controlled by the control valve 7 for driving the slope 2 a of the hydraulic pump 2.
- An opening sensing valve for switching, 9 is a control pump 27 as a control pressure valve of a capacity control cylinder 7, and a control pump 27 is a downstream 5 b of the operation valve 4.
- Hydraulic pressure Hydraulic sensor for converting to a pneumatic signal 18 is a working mode switching switch of a hydraulic excavating machine, S is an excavation mode button, and B is a brake force mode Mode button, 25 is a pump capacity sensor that detects the capacity of the hydraulic pump 2
- 26 is a sensor that detects the number of face changes of the engine 1
- the rotational speed sensor 30 is a pump of the hydraulic sensor 27 of the actuator 3, the work mode switching switch 18, and the hydraulic pump 2.
- the detection signal and command signal from the capacity sensor 25 and the engine speed sensor 26 of the engine 1 are input and the work mode is switched.
- the control signal i N ′ and i V that allow the engine 1 to operate with the minimum fuel consumption at the predetermined horsepower specified by the switch 18 are calculated, and the control signal i W To the governor drive 1a of the engine 1 and the control signal iV to the solenoid 8a of the load sensing valve 8 Roller, 8b is a port connected to the upstream pipe 5a of the operation valve 4—a pilot cylinder of the dosing valve 8, and 8c is a port cylinder of the operation valve 4.
- 8 d is the differential pressure setting of the load sensing valve 8
- the spring 7a is provided in the bottom chamber 7b of the displacement control cylinder 7, and biases the piston 7d in the direction of the rod chamber 7c.
- 17 is a power supply
- 19 is a magnet
- 21 is a changeover switch
- 20 is a spring
- 22 is a hold switch
- 23 is a spring. .
- 1a is a cano
- a drive unit 8a is a solenoid of the load sensing valve 8
- 30 is a controller
- the controller 30 is a target value setting unit 31 for setting the target engine surface turn number NS and the target engine torque TS for the cutting mode.
- Capacity difference calculator 3 3 for calculating the Calculate the difference NS between the target engine plane turn number NS and the actual engine plane turn number N detected from the engine turn sensor 26.
- the engine surface turn difference calculator 34 and the breaker mode setting engine are also provided for the breaker mode.
- the difference ⁇ NB between the engine plane number NB and the actual engine plane number N detected by the engine rotation number sensor 26 is used to calculate the difference ⁇ NB.
- the excavation mode button S of the mode switching switch 18 is pressed, Since the voltage of the power supply 17 was not applied to the magnet 19, the magnet 19 was demagnetized, and the switch 21 was turned on by the spring 20. Connected to contact A. Obedience Then, the target engine plane turn number NS and the target engine torque TS are set by the target setting device 31 in the controller 30, and the target engine torque TS is set.
- the target engine torque TS and the detected value P of the hydraulic sensor 27 are input to the capacity difference calculator 33.
- TS kPVS
- TS kPVS
- the control signal i V is set to a large value when the capacitance difference signal ⁇ VS is small. If the actual pump capacitance V detected by the pump capacitance sensor 25 with respect to the pump capacitance VS is too large, the capacitance difference signal VS becomes smaller. Since the control signal i V increases, the urging force of the solenoid 8a that pushes the load sensing valve 8 to the right increases. Accordingly, since the control pressure of the control pump 9 is supplied to the bottom chamber 7b of the capacity control cylinder 7, the load rod of the capacity control cylinder 7 is controlled. 7e moves to the right to control the slope 2a of the variable displacement hydraulic pump 2 in a direction to decrease the displacement.
- the capacitance difference signal AVS becomes 0, that is, the actual The pump capacitance V is controlled so that it becomes the target pump capacitance VS.
- the target engine plane number NS and the engine plane number sensor 26 set by the target value setting unit 31 are detected.
- the actual engine plane number N is input to the engine rotation number difference output unit 34, the target engine plane number NS and the engine number N are obtained.
- the difference ⁇ NS is also set to have a small value. For example, the actual engine plane number N detected by the engine plane number sensor 26 with respect to the target engine plane number NS is small.
- the engine surface speed difference signal ANS becomes large and the control signal i N also becomes large, so that the governor drive device moves a lot and a lot of fuel is injected. Then, the engine plane number N is added, and the engine plane number difference signal NS is 0, that is, the actual engine plane number N is equal to the target engine plane number.
- Excavation work is performed at the target engine surface NS and the target engine torque TS, which is controlled to be the number of turns NS and has the minimum fuel. be able to .
- the mode switching switch When working in a breaker mode that uses approximately 50% of the hydraulic oil volume in the normal drilling operation, the mode switching switch must be used. Pressing the power mode button B on the switch 18 causes the voltage of the power supply 17 to be applied to the magnet 19.
- the switching switch 21 is connected to the contact B against the spring 20 and the hold switch 22 is connected to the contact C, so that the breaker mode is applied. Even when the button B is released, the breaker mode is maintained by the hold switch 22 and the target in the controller 30 is maintained.
- the power supply voltage is supplied to the setting device 32. Accordingly, the target engine rotation speed NB and the target engine torque TB are set by the target value setting device 32, and the same as in the ordinary drilling mode described above. Then, the braking force operation can be performed using the target engine surface turnover NB and the target engine torque TB that are the minimum fuel.
- the present invention relates to a construction in which a hydraulic breaker is mounted as an attachment instead of a bucket normally mounted as a working machine of a hydraulic excavator.
- a hydraulic breaker is mounted as an attachment instead of a bucket normally mounted as a working machine of a hydraulic excavator.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Fluid-Pressure Circuits (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE69225951T DE69225951T2 (de) | 1991-09-27 | 1992-09-25 | Steuergerät zum umschalten der hydraulischen ölmenge für bagger |
US08/064,055 US5481875A (en) | 1991-09-27 | 1992-09-25 | Apparatus for changing and controlling volume of hydraulic oil in hydraulic excavator |
EP92920393A EP0558765B1 (en) | 1991-09-27 | 1992-09-25 | Hydraulic oil amount change-over controlling device for hydraulic excavator |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3/274930 | 1991-09-27 | ||
JP3274930A JP3064574B2 (ja) | 1991-09-27 | 1991-09-27 | 油圧掘削機における作業油量切換制御装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1993006314A1 true WO1993006314A1 (en) | 1993-04-01 |
Family
ID=17548527
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1992/001225 WO1993006314A1 (en) | 1991-09-27 | 1992-09-25 | Hydraulic oil amount change-over controlling device for hydraulic excavator |
Country Status (5)
Country | Link |
---|---|
US (1) | US5481875A (ja) |
EP (1) | EP0558765B1 (ja) |
JP (1) | JP3064574B2 (ja) |
DE (1) | DE69225951T2 (ja) |
WO (1) | WO1993006314A1 (ja) |
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1991
- 1991-09-27 JP JP3274930A patent/JP3064574B2/ja not_active Expired - Fee Related
-
1992
- 1992-09-25 US US08/064,055 patent/US5481875A/en not_active Expired - Lifetime
- 1992-09-25 DE DE69225951T patent/DE69225951T2/de not_active Revoked
- 1992-09-25 WO PCT/JP1992/001225 patent/WO1993006314A1/ja not_active Application Discontinuation
- 1992-09-25 EP EP92920393A patent/EP0558765B1/en not_active Revoked
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JPS62220703A (ja) * | 1986-03-22 | 1987-09-28 | Hitachi Constr Mach Co Ltd | 建設機械の油圧制御装置 |
JPH02164941A (ja) * | 1988-12-19 | 1990-06-25 | Hitachi Constr Mach Co Ltd | 土木・建設機械の油圧駆動装置 |
JPH02291436A (ja) * | 1989-01-18 | 1990-12-03 | Hitachi Constr Mach Co Ltd | 油圧建設機械の駆動制御装置 |
JPH0374605A (ja) * | 1989-08-16 | 1991-03-29 | Komatsu Ltd | 作業機シリンダの圧油供給装置 |
JPH03212524A (ja) * | 1990-01-18 | 1991-09-18 | Komatsu Ltd | アタッチメントの流量切換え装置 |
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Title |
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See also references of EP0558765A4 * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7269490B2 (en) | 2003-08-25 | 2007-09-11 | Komatsu Ltd. | Construction machine |
US7483814B2 (en) | 2003-09-02 | 2009-01-27 | Komatsu Ltd. | Construction machinery |
CN114458461A (zh) * | 2022-03-08 | 2022-05-10 | 雷沃工程机械集团有限公司 | 一种挖掘机发动机功率自动辨识方法 |
Also Published As
Publication number | Publication date |
---|---|
US5481875A (en) | 1996-01-09 |
EP0558765A4 (en) | 1994-06-01 |
DE69225951T2 (de) | 1998-12-24 |
JP3064574B2 (ja) | 2000-07-12 |
EP0558765A1 (en) | 1993-09-08 |
EP0558765B1 (en) | 1998-06-17 |
JPH0586635A (ja) | 1993-04-06 |
DE69225951D1 (de) | 1998-07-23 |
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