WO2012093703A1 - 履帯式走行装置を備えた作業機の油圧駆動装置 - Google Patents
履帯式走行装置を備えた作業機の油圧駆動装置 Download PDFInfo
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- WO2012093703A1 WO2012093703A1 PCT/JP2012/050126 JP2012050126W WO2012093703A1 WO 2012093703 A1 WO2012093703 A1 WO 2012093703A1 JP 2012050126 W JP2012050126 W JP 2012050126W WO 2012093703 A1 WO2012093703 A1 WO 2012093703A1
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- pressure
- travel
- valve
- control valve
- flow rate
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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
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
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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
- E02F9/02—Travelling-gear, e.g. associated with slewing gears
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
- E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- 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
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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
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2271—Actuators and supports therefor and protection therefor
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2285—Pilot-operated systems
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2292—Systems with two or more pumps
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
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- 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
- E02F9/26—Indicating devices
- E02F9/267—Diagnosing or detecting failure of vehicles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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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
- F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/026—Pressure compensating 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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
- F15B19/002—Calibrating
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- 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
- E02F3/325—Backhoes of the miniature type
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- 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
- E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
- E02F3/963—Arrangements on backhoes for alternate use of different tools
- E02F3/964—Arrangements on backhoes for alternate use of different tools of several tools mounted on one machine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20523—Internal combustion engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—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
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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
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—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
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/321—Directional control characterised by the type of actuation mechanically
- F15B2211/322—Directional control characterised by the type of actuation mechanically actuated by biasing means, e.g. spring-actuated
- F15B2211/323—Directional control characterised by the type of actuation mechanically actuated by biasing means, e.g. spring-actuated the biasing means being adjustable
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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
- F15B2211/355—Pilot pressure control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/521—Pressure control characterised by the type of actuation mechanically
- F15B2211/522—Pressure control characterised by the type of actuation mechanically actuated by biasing means, e.g. spring-actuated
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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
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- F15B2211/528—Pressure 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
- F15B2211/575—Pilot pressure control
- F15B2211/5756—Pilot pressure control for opening a 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
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
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- 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
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- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
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- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
- F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
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- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
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- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/78—Control of multiple output members
- F15B2211/782—Concurrent control, e.g. synchronisation of two or more actuators
Definitions
- the present invention relates to a hydraulic drive device for a working machine equipped with a crawler type traveling device, and more particularly, to a hydraulic drive device for a working machine that facilitates ensuring straight travel performance during traveling.
- the hydraulic pump In a working machine equipped with a conventional crawler type traveling device, for example, a hydraulic drive device of an actuator of a hydraulic excavator, the hydraulic pump (main pump) has a hydraulic pressure so that the discharge pressure of the hydraulic pump (main pump) is higher than the maximum load pressure of multiple actuators by a target differential pressure.
- Some control the discharge flow rate of the pump, and such a hydraulic system is called a load sensing system.
- the differential pressure before and after the plurality of flow control valves is held at a predetermined differential pressure by the pressure compensation valve, and each of the actuators is controlled regardless of the load pressure of each actuator during the combined operation of simultaneously driving the plurality of actuators.
- Pressure oil can be supplied at a ratio corresponding to the opening area of the flow control valve.
- Such a load sensing system is described in Patent Document 1, for example.
- a differential pressure reducing valve that outputs a differential pressure between the discharge pressure of the hydraulic pump and the maximum load pressure of a plurality of actuators (hereinafter referred to as differential pressure PLS) as an absolute pressure is provided.
- the output pressure of the pressure reducing valve is guided to multiple pressure compensating valves, each target compensating differential pressure of the pressure compensating valve is set by the differential pressure PLS, and control is performed to maintain the differential pressure PLS before and after the flow control valve at the differential pressure PLS.
- the differential pressure PLS is determined according to the degree of saturation.
- the target compensation differential pressure of the pressure compensation valve that is, the differential pressure before and after the flow control valve, becomes smaller. It can be.
- a hydraulic system called an open circuit system equipped with an open center type direction switching valve is also widely used.
- this open circuit system for example, as described in Patent Document 2, normally, left and right traveling motors are independently supplied with pressure oil from two hydraulic pumps to perform traveling.
- two pressure oil supply oil passages for supplying pressure oil from two hydraulic pumps to two directional control valves for traveling are connected via meandering correction circuits.
- the valve device provided in the meandering correction circuit is switched from the shut-off position to the throttle communication position, otherwise the valve device Is kept at the shut-off position, thereby preventing deterioration in operability in cases other than the straight traveling operation, and when the straight traveling operation is performed, straight traveling correction of the traveling meander is made possible.
- a traveling device for example, a hydraulic drive device of a hydraulic mini excavator
- the rated traveling speed determined by the engine speed and the pump discharge flow rate is determined by the opening area of the flow control valve and the capacity of the traveling motor.
- the specifications of the left and right flow control valves and the left and right traveling motors are set to the same specifications.
- the actual speed difference (rotational speed difference) between the left and right traveling motors is affected by the opening area of the flow control valve and the volumetric efficiency of the traveling motor. Actually, product processing error, flow control valve opening area, travel motor manufacturing error, etc.
- a speed difference may occur between the left and right traveling motors during a traveling operation.
- the vehicle body meanders and cannot perform the intended straight traveling.
- the current countermeasure is to check the product at the time of shipment from the factory, for example, and if there is such a problem, replace the traveling motor to replace the part. The same applies when such a malfunction occurs during operation by the user after shipment from the factory.
- the traveling motor is a large device, and replacing it requires an excessive cost and work amount. Also, the certainty was low.
- the object of the present invention is to perform the traveling by supplying pressure oil from at least one hydraulic pump to the left and right traveling motors, and to make a special change to the main circuit without exchanging a large device such as a traveling motor. It is an object of the present invention to provide a hydraulic drive device for a working machine having a crawler type traveling device that can easily perform straight traveling correction of traveling meandering.
- the present invention provides an engine, a variable displacement main pump driven by the engine, and first and second traveling units driven by pressure oil discharged from the main pump.
- a plurality of flow control valves including a plurality of actuators including a hydraulic motor; first and second flow control valves for traveling that control flow rates of pressure oil supplied from the main pump to the plurality of actuators; And at least one of the first and second travel flow control valves, in the hydraulic drive device for a working machine having a crawler-type travel device having left and right crawler belts driven by rotation of the second travel hydraulic motor, respectively. It is assumed that a flow rate correction device for limiting the maximum flow rate output from one of the travel flow rate control valves to a preset flow rate is provided.
- the traveling meandering correction method by the flow rate correction apparatus includes the following two methods.
- One is a case in which adjustment is performed by attaching a flow rate correction device when it is found that there is a problem with traveling meandering, such as during a check before shipping the product of the working machine.
- the other is a case where a flow rate correction device is attached in advance to the hydraulic drive device of the work implement, and then adjustment is performed when it is found that there is a problem of traveling meandering.
- a flow rate correction device is attached in advance to the hydraulic drive device of the work implement, and then adjustment is performed when it is found that there is a problem of traveling meandering.
- it is known which side of the first and second travel flow control valves has a higher (or lower) rotational speed of the travel motor, so which of the first and second travel flow control valves
- a flow rate correction device may be attached to either side.
- the flow meander is attached in such a manner, and the maximum flow rate supplied to the first hydraulic motor is adjusted to be equal to the maximum flow rate supplied to the second hydraulic motor, so that the traveling meander Can be corrected.
- the traveling meander can be corrected.
- the flow correction device is installed in advance and adjustment is made when it is found that there is a problem with traveling meandering, it is not necessary to perform the work of attaching the flow correction device at the time of adjustment, so the straight movement of the traveling meander is quick. Correction can be performed. Further, since the flow rate correction device is attached to both sides of the first and second travel flow control valves, it is possible to widen the range of straight travel correction of the traveling meander.
- a plurality of pressure compensation valves including first and second travel pressure compensation valves that respectively control front and rear differential pressures of the plurality of flow control valves, and a discharge pressure of the main pump is a maximum load of the plurality of actuators.
- a pump control device that performs load sensing control of the displacement of the main pump so as to be higher than the pressure by a target differential pressure, and the plurality of pressure compensation valves have a differential pressure across the flow control valve that is equal to a discharge pressure of the main pump.
- the flow rate correction device includes: A target compensation differential pressure adjusting device that corrects a target compensation differential pressure of a travel pressure compensation valve corresponding to the travel flow control valve among the first and first travel pressure compensation valves.
- the maximum flow rate supplied to the first hydraulic motor and the second flow rate are corrected by correcting the opening of the traveling pressure compensation valve in the opening direction or the closing direction.
- the target compensation differential pressure adjusting device includes an adjustment pin having an adjustment pin for adjusting a biasing force of a spring that sets a target compensation differential pressure of the traveling pressure compensation valve. It is.
- the target compensation differential pressure adjustment device includes a pressure reducing valve that corrects the target compensation differential pressure of the traveling pressure compensation valve by reducing the pressure of a pilot hydraulic power source.
- Pressure reducing valve unit is a pressure reducing valve that corrects the target compensation differential pressure of the traveling pressure compensation valve by reducing the pressure of a pilot hydraulic power source.
- the hydraulic drive device for the working machine further includes a travel operation device including a remote control valve that generates a control pilot pressure for operating the travel flow control valve, and the flow correction device includes the travel correction device.
- a travel operation device including a remote control valve that generates a control pilot pressure for operating the travel flow control valve
- the flow correction device includes the travel correction device.
- a pressure control valve unit that is disposed between the remote control valve of the operating device and the travel flow control valve and includes a pressure control valve that reduces a control pilot pressure of the remote control valve.
- the hydraulic drive device for the working machine further includes a travel operation device including a remote control valve that generates a control pilot pressure for operating the travel flow control valve
- the flow rate correction device includes:
- the pressure reducing valve unit is provided between a remote control valve of the traveling operation device and the flow control valve for traveling, and includes a pressure reducing valve for reducing a control pilot pressure of the remote control valve.
- straight traveling correction of traveling meander can be easily performed without replacing a large device such as a traveling motor and without making any special change to the main circuit.
- FIG. 3 shows the appearance of the hydraulic excavator.
- a hydraulic excavator well known as a work machine includes an upper swing body 300, a lower traveling body 301, and a swing type front work machine 302.
- the front work machine 302 includes a boom 306, an arm 307, The bucket 308 is configured.
- the upper swing body 300 can swing the lower traveling body 301 by the rotation of the swing motor 5.
- a swing post 303 is attached to the front portion of the upper swing body 300, and a front work machine 302 is attached to the swing post 303 so as to be movable up and down.
- the swing post 303 can be rotated in the horizontal direction with respect to the upper swing body 300 by expansion and contraction of the swing cylinder 9. 12 can be turned up and down by expansion and contraction.
- the lower traveling body 301 includes a central frame 304, and a blade 305 that moves up and down by the expansion and contraction of the blade cylinder 7 is attached to the central frame 304.
- the lower traveling body 301 includes a crawler-type travel device 315 that travels by driving the left and right crawler belts 310 and 311 by the rotation of the travel motors 6 and 8.
- 1A and 2B show a hydraulic drive device for a working machine according to a first embodiment of the present invention.
- the hydraulic drive device in the present embodiment is discharged from the engine 1, the main main pump 2 driven by the engine 1, the pilot pump 3 driven by the engine 1 in conjunction with the main pump 2, and the main pump 2.
- a plurality of actuators 5, 6, 7, 8, 9, 10, 11, 12 driven by the pressurized oil and a control valve 4 are provided.
- the working machine including the crawler type traveling apparatus is, for example, a hydraulic mini excavator
- the actuator 5 is a swing motor of the hydraulic excavator
- the actuators 6 and 8 are left and right traveling motors
- the actuator 7 is a blade.
- the actuator 9 is a swing cylinder
- the actuators 10, 11, and 12 are a boom cylinder, an arm cylinder, and a bucket cylinder, respectively.
- the control valve 4 is connected to the supply oil passage 2a of the main pump 2, and has a plurality of valve sections 13, 14, 15, 16, 17 for controlling the direction and flow rate of the pressure oil supplied from the main pump 2 to each actuator. , 18, 19, 20 and the signal oil by selecting the highest load pressure (hereinafter referred to as the maximum load pressure) PLmax among the load pressures of the plurality of actuators 5, 6, 7, 8, 9, 10, 11, 12
- a plurality of shuttle valves 22a, 22b, 22c, 22d, 22e, 22f, and 22g output to the passage 21 and a supply oil passage 2a of the main pump 2 are provided to limit the maximum discharge pressure (maximum pump pressure) of the main pump 2.
- the differential pressure PLS with respect to ax exceeds a certain fixed value set by the spring 25a, a part of the discharge flow rate of the main pump 2 is returned to the tank 0, and the differential pressure PLS is less than the fixed value set by the spring 25a.
- an unload valve 25 for keeping. Outlet sides of the unload valve 25 and the main relief valve 23 are connected to the tank oil passage 29 in the control valve 2 and connected to the tank 0.
- the valve section 13 includes a flow control valve 26a and a pressure compensation valve 27a
- the valve section 14 includes a flow control valve 26b and a pressure compensation valve 27b
- the valve section 15 includes a flow control valve 26c and a pressure compensation valve 27c
- the valve section 16 is composed of a flow control valve 26d and a pressure compensation valve 27d
- the valve section 17 is composed of a flow control valve 26e and a pressure compensation valve 27e
- the valve section 18 is composed of a flow control valve 26f and a pressure
- the valve section 19 includes a flow rate control valve 26g and a pressure compensation valve 27g
- the valve section 20 includes a flow rate control valve 26h and a pressure compensation valve 27h.
- the flow control valves 26a to 26h control the direction and flow rate of the pressure oil supplied from the main pump 2 to the actuators 5 to 12, respectively.
- the pressure compensation valves 27a to 27h are differential pressures before and after the flow control valves 26a to 26h. To control each.
- the pressure compensating valves 27a to 27h have valve-opening side pressure receiving portions 28a, 28b, 28c, 28d, 28e, 28f, 28g, and 28h for setting a target differential pressure.
- the pressure receiving portions 28a to 28h include a differential pressure reducing valve 24.
- the target compensation differential pressure is set by the absolute pressure of the differential pressure PLS between the hydraulic pump pressure Pd and the maximum load pressure PLmax (hereinafter referred to as the absolute pressure PLS). In this way, by controlling the differential pressure across the flow control valves 26a-26h to the same differential pressure PLS, the pressure compensation valves 27a-27h have the maximum differential pressure across the flow control valves 26a-26h equal to the hydraulic pump pressure Pd.
- Control is performed so as to be equal to the differential pressure PLS from the load pressure PLmax.
- the discharge flow rate of the main pump 2 is distributed according to the opening area ratio of the flow rate control valves 26a to 26h regardless of the load pressure of the actuators 5 to 12. Combined operability can be ensured.
- the differential pressure PLS decreases according to the degree of supply shortage, and the pressure compensation valves 27a to 27h control accordingly.
- the discharge flow rate of the main pump 2 can be distributed to ensure composite operability.
- the hydraulic drive device is connected to the supply oil passage 3 a of the pilot pump 3, and includes an engine speed detection valve device 30 that outputs an absolute pressure according to the discharge flow rate of the pilot pump 3, and an engine speed detection valve device 30.
- a pilot hydraulic pressure source 33 having a pilot relief valve 32 that is connected to the downstream side and keeps the pressure of the pilot oil passage 31 constant, and a flow control valve 26a that is connected to the pilot oil passage 31 and uses the hydraulic pressure of the pilot hydraulic pressure source 32 as a source pressure.
- Remote control valves for generating control pilot pressures a, b, c, d, d, f, g, h, i, j, k, l, m, n, o, p for operating up to 26h
- Operation lever devices (operation devices) 34a, 34b, 34c, 34d, 34e, 34f, 34g, and 34h are provided.
- the engine speed detection valve device 30 includes an oil passage 30e that connects the supply oil passage 3a of the pilot pump 3 to the pilot oil passage 31, a throttle element (fixed throttle) 30f provided in the oil passage 30e, and an oil passage 30e. And a flow rate detecting valve 30a connected in parallel to the throttle element 30f and a differential pressure reducing valve 30b.
- the input side of the flow rate detection valve 30 a is connected to the supply oil passage 3 a of the pilot pump 3, and the output side of the flow rate detection valve 30 a is connected to the pilot oil passage 31.
- the flow rate detection valve 30a has a variable throttle 30c that increases the opening area as the passing flow rate increases, and the discharge oil of the pilot pump 3 passes through both the throttle element 30f and the variable throttle 30c of the flow rate detection valve 30a. Flow to the pilot oil passage 31 side. At this time, a differential pressure increases and decreases as the passing flow rate increases in the throttle element 30f and the variable throttle portion 30c of the flow rate detection valve 30a, and the differential pressure reducing valve 30b outputs the differential pressure as the absolute pressure Pa. To do. Since the discharge flow rate of the pilot pump 3 varies depending on the rotation speed of the engine 1, the discharge flow rate of the pilot pump 3 can be detected by detecting the differential pressure across the throttle element 30f and the variable throttle portion 30c.
- variable throttle portion 30c increases the opening area as the passing flow rate increases (as the front-rear differential pressure increases), so that the degree of increase in the front-rear differential pressure becomes milder as the passing flow rate increases. It is configured as follows.
- the main pump 2 is a variable displacement hydraulic pump, and includes a pump control device 35 for controlling the tilt angle (capacity) thereof.
- the pump control device 35 includes a horsepower control tilt actuator 35a, an LS control valve 35b, and an LS control tilt actuator 35c.
- the horsepower control tilt actuator 35a reduces the tilt angle of the main pump 2 when the discharge pressure of the main pump 2 increases, and limits the input torque of the main pump 2 so as not to exceed the preset maximum torque. This limits the horsepower consumed by the main pump 2 and prevents the engine 1 from being stopped (engine stall) due to overload.
- the LS control valve 35b has pressure receiving portions 35d and 35e opposed to each other, and the pressure receiving portion 35d has an absolute pressure Pa (first pressure) generated by the differential pressure reducing valve 30b of the engine speed detection valve device 30 through the oil passage 40. Stipulated value) is introduced as a target differential pressure (target LS differential pressure) of load sensing control, the absolute pressure PLS generated by the differential pressure reducing valve 24 is guided to the pressure receiving part 35e, and the absolute pressure PLS is greater than the absolute pressure Pa.
- PLS target LS differential pressure
- the pressure of the pilot hydraulic source 33 is guided to the LS control tilt actuator 35c to reduce the tilt angle of the main pump 2, and when the absolute pressure PLS becomes lower than the absolute pressure Pa (PLS ⁇ Pa).
- the LS control tilting actuator 35c is connected to the tank T to increase the tilting angle of the main pump 2, so that the discharge pressure Pd of the main pump 2 is higher by the absolute pressure Pa (target differential pressure) than the maximum load pressure PLmax. Inclination amount of main pump 2 (displacement volume) Control to.
- the control valve 35b and the LS control tilting actuator 35c are configured so that the discharge pressure Pd of the main pump 2 is higher than the maximum load pressure PLmax of the plurality of actuators 5, 6, 7, 8, 9, 10, 11, 12, and the load sensing control target.
- a load sensing type pump control means for controlling the tilting of the main pump 2 so as to increase by the differential pressure is configured.
- the absolute pressure Pa is a value that changes according to the engine speed
- the absolute pressure Pa is used as the target differential pressure of the load sensing control
- the target compensated differential pressure of the pressure compensation valves 27a to 27h is used for the main pump 2.
- the actuator speed can be controlled in accordance with the engine speed.
- the variable throttle portion 30c of the flow rate detection valve 30a of the engine speed detection valve device 30 is configured so that the degree of increase in the front-rear differential pressure becomes moderate as the passing flow rate increases.
- the set pressure of the spring 25a of the unload valve 25 is the absolute pressure Pa (target difference of load sensing control) generated by the differential pressure reducing valve 30b of the engine speed detecting valve device 30 when the engine 1 is at the rated maximum speed. Pressure).
- the hydraulic drive device shown in FIGS. 1A and 2B rotates the left travel motor 6 when the operation levers of the operation lever devices 34b and 34d for travel are operated with a full stroke in the right direction in the drawing with the intention of a straight traveling operation.
- the flow control valve 26b is provided on the side where the valve-opening side pressure receiving portion 28b for setting the target differential pressure of the pressure compensation valve 27b for left travel is located.
- a flow rate correction device 39 is provided for limiting the maximum flow rate output from the flow rate to a preset flow rate.
- the flow rate correction device 39 is a target compensation differential pressure adjustment device that corrects the target compensation differential pressure of the traveling pressure compensation valve 27b by the biasing force of the target compensation differential pressure adjustment spring 36b.
- the target compensation differential pressure of the left travel pressure compensation valve 27b is adjusted using the pressure adjusting device to correct the maximum flow rate of the travel flow control valve 26b.
- FIG. 2A is a cross-sectional view of normal pressure compensation valves 27b and 27d for right and left travel without the flow rate correction device 39
- FIG. 2B is a pressure compensation valve 27b and 27d for left and right travel with the flow rate correction device 39.
- FIG. 2A and FIG. 2B the symbols for the right traveling motor 8, the right traveling flow control valve 26d, and the right traveling pressure compensation valve 27d are shown in parentheses.
- the left and right traveling pressure compensation valves 27b and 27d are inserted into the pressure compensation valve portion of the housing 38 of the traveling valve sections 14 and 16 of the control valve 4 so as to be slidable in the axial direction.
- the pressure receiving chamber 64b where the valve-opening pressure receiving portion 63b for feedback is located is closed by a plug 65b.
- the target compensation differential pressure adjusting spring 36b that biases in the valve opening direction is disposed in the pressure receiving chamber 64b.
- the target compensation differential pressure adjusting springs 36b and 36d are for preferentially supplying pressure oil to the traveling motors 6 and 8 during the traveling combined operation to stabilize traveling.
- the target compensation differential pressure adjusting springs 36b and 36d are used to correct the target compensation differential pressure of the pressure compensation valve 27b in the flow rate correction device 39.
- Some types of pressure compensation valves do not include the target compensation differential pressure adjustment springs 36b and 36d. In that case, a dedicated target compensation differential pressure adjustment spring may be newly incorporated.
- the flow rate correction device 39 (target compensation differential pressure adjustment device) is configured by a plug 37 with an adjustment mechanism that adjusts the biasing force of the target compensation differential pressure adjustment spring 36b.
- the plug 37 with adjusting mechanism is an adjusting device for adjusting the maximum flow rate of the flow control valve 26b, and includes a plug body 37a, an adjustment pin 37b incorporated in the plug body 37a, and a lock nut 37c. .
- the screw size of the plug body 37a is the same as that of the plug 65b.
- the adjustment pin 37b protrudes into the male threaded portion 37e that engages with the plug main body 37a, the pressure receiving chamber 64d, the spring receiver 37f that engages with the target compensation differential pressure adjusting spring 36b, and the opposite side of the pressure receiving chamber 64d.
- a tool operation unit 37g having a hexagonal cross section is provided.
- a tool such as a box wrench is attached to the tool operation unit 37g and rotated to change the axial position of the adjustment pin 37b, and the target compensation differential pressure adjustment spring 36b By adjusting the urging force, the target compensation differential pressure of the pressure compensation valve 27b is adjusted. After the target compensation differential pressure is adjusted, the position of the adjustment pin 37b is fixed by tightening the lock nut 37c, and the adjustment of the target compensation differential pressure is completed.
- a normal pressure compensation valve 27b not equipped with the flow rate correction device 39 shown in FIG. 2A is attached as the pressure compensation valve 27b for left running. Yes.
- the flow control valve 26b is supplied from the pressure oil of the pilot hydraulic source 33.
- 26d, control pilot pressures d, h for operating are generated and guided to the flow control valves 26b, 26d.
- the pressure oil discharged from the main pump 2 is guided to the left and right traveling motors 6 and 8 via the pressure compensation valves 27b and 27d and the flow rate control valves 26b and 26d.
- the actuator load pressures of the left and right traveling motors 6 and 8 guided to the valve-opening pressure receiving portions 28b and 28d of the left and right traveling pressure compensating valves 27b and 27d are equal, but in rare cases, the weight balance of the fuselage and the traveling motor are rare. Due to the manufacturing error, the left and right traveling motors 6 and 8 may be different in speed (rotational speed difference), and traveling meandering may occur.
- the plug 65b provided on the valve-opening side receiving portion 28b (or 28d) side of the traveling pressure compensation valve 27b (or 27d) having the lower rotational speed is removed, and as shown in FIG. 37, the adjusting pin 37b of the plug 37 with adjusting mechanism is operated as described above and adjusted in the right direction in the figure, and the urging force of the target compensating differential pressure adjusting spring 36b is increased, whereby the pressure compensating valve 27b (or 27d) is adjusted.
- straight running correction of the traveling meander can be performed.
- straight traveling correction of traveling meandering can be easily performed without replacing a large device such as a traveling motor. Further, it is possible to easily perform straight-line correction of traveling meandering without adding any special change to the main circuit ⁇ Second Embodiment> 4A and 4B show a hydraulic drive device for a working machine according to a second embodiment of the present invention.
- the first embodiment is adjusted by providing a flow rate correction device 39 (target compensation differential pressure adjustment device) when there is a problem at the time of checking before shipment, whereas before the shipment.
- flow rate correction devices 39A and 39B target compensation differential pressure adjustment
- the flow rate correction devices 39A and 39B are configured by plugs 37A and 37B with adjustment mechanisms that adjust the urging forces of the target compensation differential pressure adjustment springs 36b and 36d, respectively.
- the plugs 37A and 37B with adjustment mechanism are configured in the same manner as the plug 37 with adjustment mechanism in the flow rate correction device 39 (target compensation differential pressure adjustment device) of the first embodiment. .
- the adjustment pins 37b and 37b (see FIG. 2B) of the plugs 37A and 37B with adjustment mechanism are fixed at the initial positions, and the biasing force of the target compensation differential pressure adjustment spring 36b is set to a specified value.
- the flow control valves 26b and 26d are operated from the pressure oil of the pilot hydraulic source 33. Control pilot pressures d and h are generated and guided to the flow control valves 26b and 26d.
- the pressure oil discharged from the main pump 2 is guided to the left and right traveling motors 6 and 8 via the pressure compensation valves 27b and 27d and the flow rate control valves 26b and 26d.
- the actuator load pressures of the left and right traveling motors 6 and 8 guided to the valve-opening pressure receiving portions 28b and 28d of the left and right traveling pressure compensating valves 27b and 27d are equal, but in rare cases, the weight balance of the fuselage and the traveling motor are rare. Due to the manufacturing error, the left and right traveling motors 6 and 8 may be different in speed (rotational speed difference), and traveling meandering may occur.
- the adjustment pin 37b of the plug 37A (or 37B) with an adjustment mechanism attached to the traveling pressure compensation valve 27b (or 27d) having the lower rotational speed is operated as described above to adjust to the right in the figure, and the target compensation difference
- the opening of the pressure compensation valve 27b (or 27d) is corrected in the opening direction, and the flow rate to the left traveling motor 6 (or 8) is adjusted to the right traveling motor 8 ( Or adjust to be equal to 6).
- straight running correction of the traveling meander can be performed.
- the flow rate correction devices 39A and 39B configured by the plugs 37A and 37B with adjustment mechanisms for adjusting the urging forces of the target compensation differential pressure adjustment springs 36b and 36d are preliminarily applied to the pressure compensation valves 27b and 27d for left and right traveling.
- the flow rate correction devices 39A and 39B are attached to both the pressure compensating valves 27b and 27d for the left and right traveling, it is possible to widen the straight traveling correction range of the traveling meander.
- the present embodiment can provide the same effects as those of the first embodiment. Further, according to the present embodiment, it is not necessary to perform the work of attaching the flow rate correction device at the time of adjustment, so that the straight traveling correction of the traveling meander can be performed quickly. In addition, since the flow rate correction devices 39A and 39B are attached to both the pressure compensating valves 27b and 27d for the left and right traveling, it is possible to widen the straight traveling correction range of the traveling meander.
- ⁇ Third Embodiment> 5A and 5B show a hydraulic drive device for a working machine according to a third embodiment of the present invention.
- the flow compensation device 39 (target compensation differential pressure adjustment device) is configured by the plug 37 with an adjustment mechanism that adjusts the urging force of the eye compensation differential pressure adjustment spring 36b or 36d in the first embodiment.
- the flow rate correction device 69 (target compensation differential pressure adjusting device) reduces the pressure of the pilot hydraulic power source 33 to the target compensation differential pressure of the left travel pressure compensation valve 27b (or travel pressure compensation valve 27d).
- the pressure reducing valve unit 140 including the pressure reducing valve 40 to be corrected is configured.
- the pressure reducing valve 40 includes an adjustment device (adjustment mechanism 73) for adjusting the maximum flow rate of the flow control valve 26b for left travel (or the flow control valve 26d for right travel).
- the hydraulic drive device shown in FIGS. 5A and 5B has a left travel motor 6 when the operation levers of the operation lever devices 34b and 34d for travel are operated in the right direction in the figure with a full stroke in order to perform a straight traveling operation.
- the right traveling motor 8 is lower than the rotational speed of the right traveling motor 8, and the left traveling is on the side where the valve-opening pressure receiving portion 28b for setting the target differential pressure of the pressure compensating valve 27b for left traveling is located.
- a pressure reducing valve unit 140 having a pressure reducing valve 40 for correcting the target compensation differential pressure of the pressure compensating valve 27b for use by reducing the pressure of the pilot hydraulic pressure source 33 is connected.
- the pressure reducing valve unit 140 has a pipe 71 in which the pressure reducing valve 40 is arranged, and the upstream side of the pipe 71 is connected to an oil passage 39 that guides the pressure oil from the pilot hydraulic power source 33 to the differential pressure reducing valve 24, and the downstream side. Is connected to a correction pressure receiving portion 66b additionally provided on the side where the valve opening side pressure receiving portion 28b for setting the target differential pressure of the pressure compensation valve 27b is located.
- the pressure reducing valve 40 has an adjusting mechanism 73 that adjusts the urging force of the spring 72 that sets the pressure reducing valve output pressure as an adjusting device for adjusting the maximum flow rate of the flow control valve 26b.
- the adjustment mechanism 73 includes an adjustment pin and a lock nut (not shown) incorporated in the pressure reducing valve 40, like the plug 37 with an adjustment mechanism shown in FIG. 2B.
- the pressure reducing valve 40 generates pressure oil having a pressure according to the setting of the spring 72 based on the pressure oil from the pilot hydraulic power source 33, and guides this pressure oil to the corrected pressure receiving portion 66b of the travel pressure compensating valve 27b. Adjust the target compensation differential pressure when driving.
- Pilot pressures d and h are generated and guided to the flow control valves 26b and 26d.
- the pressure oil discharged from the main pump 2 is guided to the left and right traveling motors 6 and 8 via the pressure compensation valves 27b and 27d and the flow rate control valves 26b and 26d.
- the actuator load pressures of the left and right traveling motors 6 and 8 guided to the valve-opening pressure receiving portions 28b and 28d of the left and right traveling pressure compensating valves 27b and 27d are equal, but in rare cases, the weight balance of the fuselage and the traveling motor are rare. Due to the manufacturing error, the left and right traveling motors 6 and 8 may be different in speed (rotational speed difference), and traveling meandering may occur.
- the valve-opening side pressure receiving portion 28b (or 28d) of the running pressure compensation valve 27b (or 27d) having the lower rotation speed is used.
- the pressure reducing valve unit 140 is connected to the side where is located, and the pressure oil from the pilot oil passage 39 is reduced by the pressure reducing valve 40 and guided to the corrected pressure receiving portion 66b (or 66d).
- ⁇ Fourth Embodiment> 6A and 6B show a hydraulic drive device for a working machine according to a fourth embodiment of the present invention.
- the third embodiment is adjusted by connecting a pressure reducing valve unit 140 which is a flow rate correction device 69 (target compensation differential pressure adjustment device) when there is a problem at the time of check before shipment.
- a pressure reducing valve unit 140 which is a flow rate correction device 69 (target compensation differential pressure adjustment device) when there is a problem at the time of check before shipment.
- the flow rate correction device 69A is provided in the valve housings on the valve-opening side pressure receiving portions 28b, 28d of both the left and right traveling pressure compensation valves 27b, 27d.
- 69B target compensation differential pressure adjusting device
- the configuration of the pressure reducing valve units 140A and 140B is the same as that of the pressure reducing valve unit 140 of the third embodiment, and has pressure reducing valves 40b and 40d and pipes 71b and 71d in which the pressure reducing valves 40b and 40d are respectively arranged.
- the upstream side of 71b, 71d is connected to an oil passage 39 that guides the pressure oil from the pilot hydraulic source 33 to the differential pressure reducing valve 24, and the downstream side is a valve-opening side pressure for setting the target differential pressure of the pressure compensating valves 27b, 27d.
- the pressure receiving portions 66b and 66d are additionally provided on the side where the portions 28b and 28d are located.
- the pressure reducing valves 40b and 40d are adjusting devices 73b and 73d for adjusting the urging forces of the springs 72b and 72d for setting the pressure reducing valve output pressure as adjusting devices for adjusting the maximum flow rates of the flow control valves 26b and 26d, respectively. Have.
- the springs 72b and 72d of the pressure reducing valves 40b and 40d are set to zero, and the output pressure of the pressure reducing valves 40b and 40d is set as the tank pressure.
- the flow control valves 26b and 26d are operated from the pressure oil of the pilot hydraulic source 33. Control pilot pressures d and h are generated and guided to the flow control valves 26b and 26d.
- the pressure oil discharged from the main pump 2 is guided to the left and right traveling motors 6 and 8 via the pressure compensation valves 27b and 27d and the flow rate control valves 26b and 26d.
- the actuator load pressures of the left and right traveling motors 6 and 8 guided to the valve-opening pressure receiving portions 28b and 28d of the left and right traveling pressure compensating valves 27b and 27d are equal, but in rare cases, the weight balance of the fuselage and the traveling motor are rare. Due to the manufacturing error, the left and right traveling motors 6 and 8 may be different in speed (rotational speed difference), and traveling meandering may occur.
- the valve-opening side pressure receiving portion 28b (or 28d) of the running pressure compensation valve 27b (or 27d) having the lower rotation speed is used.
- the adjustment pin of the adjustment mechanism 73b (or 73d) of the pressure reducing valve 40b (or 40d) of the pressure reducing valve unit 140A (or 140B) connected to the side where is located the biasing force of the spring 72b (or 72d) is increased.
- the output pressure is increased to correct the opening of the pressure compensation valve 27b (or 27d) in the opening direction so that the flow rate to the left traveling motor 6 (or 8) becomes equal to that of the right traveling motor 8 (or 6). Adjust to.
- straight running correction of the traveling meander can be performed.
- the pressure reducing valve units 140A and 140B are attached in advance to both the left and right pressure compensating valves 27b and 27d, so that it is not necessary to perform additional work for installing the pressure reducing valve unit when meandering. It is possible to perform straight running correction of traveling meandering. Moreover, since pressure reducing valve units 140A and 140B (flow rate correction device or target compensation differential pressure adjusting device) are attached to both pressure compensation valves 27b and 27d for left and right traveling, the range of straight traveling correction of traveling meandering is widened. can do.
- the present embodiment can provide the same effects as those of the first embodiment. Further, according to the present embodiment, it is not necessary to perform the work of attaching the flow rate correction device at the time of adjustment, so that the straight traveling correction of the traveling meander can be performed quickly. Moreover, since pressure reducing valve units 140A and 140B (flow rate correction device or target compensation differential pressure adjusting device) are attached to both pressure compensation valves 27b and 27d for left and right traveling, the range of straight traveling correction of traveling meandering is widened. can do.
- ⁇ Fifth Embodiment> 7A and 7B show a hydraulic drive device for a working machine according to a fifth embodiment of the present invention.
- the flow rate correction devices 39 and 69 are configured by target compensation differential pressure adjustment devices in the first to fourth embodiments, whereas the flow rate correction device 79 is replaced with a travel operation lever device 34b (
- the pressure control valve unit 142 includes a pressure control valve 42 that is disposed between the remote control valve 34d) and the flow control valve 26b (or 26d) and reduces the control pilot pressure of the remote control valve.
- the pressure control valve 42 includes an adjustment device (adjustment mechanism 83) for adjusting the maximum flow rate of the left flow control valve 26b (or the right flow control valve 26d).
- the hydraulic drive device shown in FIGS. 7A and 7B has the left travel motor 6 when the operation levers of the operation lever devices 34b and 34d for travel are operated with full strokes in the right direction in the drawing with the intention of straight traveling operation. Is higher than the rotational speed of the right travel motor 8, and the forward control pilot pressure d is flowed out of the control pilot pressure cd generated by the remote control valve of the control lever device 34b for left travel.
- a pressure control valve unit 142 having a pressure control valve 42 for reducing the forward control pilot pressure d is connected to a pipe leading to the control valve 26b.
- the pressure control valve unit 142 has a pipe 81 in which the pressure control valve 42 is arranged, and the upstream side of the pipe 81 is connected to a remote control valve of the left travel operation lever device 34b that outputs a forward control pilot pressure d.
- the downstream side is connected to the tank line.
- the pressure control valve 42 is a variable relief valve, and has an adjustment mechanism 83 that adjusts the biasing force of the spring 82 that sets the relief pressure as an adjustment device for adjusting the maximum flow rate of the flow control valve 26b.
- the adjustment mechanism 83 includes an adjustment pin and a lock nut (not shown) incorporated in the pressure control valve 42, like the plug 37 with an adjustment mechanism shown in FIG. 2B.
- the pressure control valve 42 limits the maximum pressure of the forward control pilot pressure d generated by the remote control valve of the left travel operation lever device 34b to a pressure corresponding to the setting of the spring 82, and the stroke of the flow control valve 26b. Regulate and control flow rate.
- Pilot pressures d and h are generated and guided to the flow control valves 26b and 26d.
- the pressure oil discharged from the main pump 2 is guided to the left and right traveling motors 6 and 8 via the pressure compensation valves 27b and 27d and the flow rate control valves 26b and 26d.
- the actuator load pressures of the left and right traveling motors 6 and 8 guided to the valve-opening pressure receiving portions 28b and 28d of the left and right traveling pressure compensating valves 27b and 27d are equal, but in rare cases, the weight balance of the fuselage and the traveling motor are rare. Due to the manufacturing error, the left and right traveling motors 6 and 8 may be different in speed (rotational speed difference), and traveling meandering may occur.
- the control pilot pressure d (or h) for operating the flow control valve having the higher rotation speed is set to the flow control valve 26b (or The pressure control valve unit 142 is connected between the pipe line leading to 26d) and the tank line. Then, the control pin pressure d (or h) is reduced by operating the adjustment pin of the adjustment mechanism 83 of the pressure control valve 42 to weaken the biasing force of the spring 82, and the stroke of the flow control valve 26b (or 26d) is reduced.
- the straight traveling correction of the traveling meander can be performed.
- ⁇ Sixth Embodiment> 8A and 8B show a hydraulic drive device for a working machine according to a sixth embodiment of the present invention.
- the flow rate correcting device 79 is disposed between the remote control valve of the operating lever device 34b (or 34d) for travel and the flow control valve 26b (or 26d), and the remote control valve
- the flow rate correction device 89 is connected to the remote control valve of the operating lever device 34b (or 34d) for travel and the flow rate control.
- the pressure reducing valve unit 143 is disposed between the valves 26b (or 26d) and includes a pressure reducing valve 43 for reducing the control pilot pressure of the remote control valve.
- the pressure reducing valve 43 includes an adjustment device (adjustment mechanism 93) for adjusting the maximum flow rate of the flow control valve 26b for left travel (or the flow control valve 26d for right travel).
- the hydraulic drive device shown in FIGS. 8A and 8B has a left travel motor 6 when the operation levers of the operation lever devices 34b and 34d for travel are operated with a full stroke in the right direction in the drawing with the intention of a straight traveling operation. Is higher than the rotational speed of the right travel motor 8, and the forward control pilot pressure d is flowed out of the control pilot pressure cd generated by the remote control valve of the control lever device 34b for left travel.
- a pressure reducing valve unit 143 provided with a pressure reducing valve 43 for reducing the forward control pilot pressure d is connected to a conduit leading to the control valve 26b.
- the pressure reducing valve unit 143 has a pipe 91 in which the pressure reducing valve 43 is arranged, and the upstream side of the pipe 91 is connected to a remote control valve of a left traveling operation lever device 34b that outputs a forward control pilot pressure d.
- the downstream side is connected to a conduit that guides the forward control pilot pressure d to the flow control valve 26b.
- the pressure reducing valve 43 has an adjusting mechanism 93 that adjusts the urging force of the spring 92 that sets the pressure reducing valve output pressure as an adjusting device for adjusting the maximum flow rate of the flow control valve 26b for left travel.
- the adjustment mechanism 93 includes an adjustment pin and a lock nut (not shown) incorporated in the pressure reducing valve 43, like the plug 37 with an adjustment mechanism shown in FIG. 2B.
- the pressure reducing valve 43 reduces the maximum pressure of the forward control pilot pressure d generated by the remote control valve of the left travel operation lever device 34b to a pressure corresponding to the setting of the spring 92, and regulates the stroke of the flow control valve 26b. The flow rate is controlled.
- Pilot pressures d and h are generated and guided to the flow control valves 26b and 26d.
- the pressure oil discharged from the main pump 2 is guided to the left and right traveling motors 6 and 8 via the pressure compensation valves 27b and 27d and the flow rate control valves 26b and 26d.
- the actuator load pressures of the left and right traveling motors 6 and 8 guided to the valve-opening pressure receiving portions 28b and 28d of the left and right traveling pressure compensating valves 27b and 27d are equal, but in rare cases, the weight balance of the fuselage and the traveling motor are rare. Due to the manufacturing error, the left and right traveling motors 6 and 8 may be different in speed (rotational speed difference), and traveling meandering may occur.
- the control pilot pressure d (or h) for operating the flow control valve having the higher rotation speed is set to the flow control valve 26b (or 26 d) is connected to the pressure reducing valve unit 143. Then, by operating the adjustment pin of the adjustment mechanism 93 of the pressure reducing valve 43 to weaken the biasing force of the spring 92, the control pilot pressure d (or h) is reduced, and the stroke of the flow control valve 26b (or 26d) is regulated. Then, by adjusting the output flow rate of the flow rate control valve 26b (or 26d), straight running correction of the traveling meander can be performed.
- FIG. 9 shows a hydraulic drive device for a working machine according to a seventh embodiment of the present invention.
- the hydraulic drive apparatus includes an engine 44, two main pumps 45, 46, 47 driven by the engine 44, and the engine 44 in conjunction with the main pumps 45, 46, 47.
- the working machine provided with the crawler type traveling device is, for example, a hydraulic mini excavator
- the actuator 5 is a swing motor of the hydraulic excavator
- the actuators 6 and 8 are left and right traveling motors
- the actuator 7 is a blade.
- the actuator 9 is a swing cylinder
- the actuators 10, 11, and 12 are a boom cylinder, an arm cylinder, and a bucket cylinder, respectively.
- the control valve 49 is connected to the pressure oil supply oil passages 45a, 46a, 47a of the main pumps 45, 46, 47, and controls the direction and flow rate of the pressure oil supplied from the main pumps 45, 46, 47 to each actuator.
- a plurality of flow control valves are provided.
- the flow rate control valves 50a to 50h control the direction and flow rate of the pressure oil supplied from the main pumps 45, 46, and 47 to the actuators 5 to 12, respectively.
- the pressure oil discharged from the discharge ports of the two hydraulic pumps 45 and 46 is meter-in channels (inflow channels) 50b1 or 50b2 of the flow control valves 50b and 50d;
- the return oil from the traveling motors 6 and 8 is guided to the respective traveling motors 6 and 8 through 50d1 or 50d2, and the meter-out flow paths (outflow side flow paths) 50b3, 50b4 or 50d3 of the flow control valves 50b and 50d. It is returned to tank 0 via 50d4.
- the hydraulic pumps 45 and 46 are variable displacement types, and the displacement (displacement volume) is changed and the discharge flow rate is increased or decreased by controlling the tilt position.
- a horsepower control actuator 51 is usually provided, and the tilt position is controlled so as to reduce the flow rate accordingly when the discharge pressure of the hydraulic pumps 45 and 46 rises.
- the flow control valves 50b and 50d are of an open center type (center bypass type) and have center bypass flow paths 50b5 and 50d5 connected to the center bypass lines 52 and 53.
- the center bypass flow paths 50b5, 50d5 are fully opened
- the meter-in flow paths 50b1, 50b2; 50d1, 50d2 are fully closed
- the hydraulic pumps 45, 46 Is discharged from the hydraulic oil supply passages 45a and 46a connected to the discharge ports of the hydraulic pumps 45 and 46, the center bypass lines 52 and 53, and the center bypass passages 50b5 and 50d5 to the tank via the tank lines 54 and 55. Returned.
- the center bypass passages 50b5 and 50d5 reduce the opening area according to the amount of operation, and the maximum switching position (full) of the flow control valves 50b and 50d. Fully closed immediately before the stroke position.
- the meter-in flow paths 50b1, 50b2; 50d1, 50d2 of the flow control valves 50b, 50d increase the opening area according to the operation amount of the flow control valves 50b, 50d, and the maximum switching position (full stroke) of the flow control valves 50b, 50d. Fully open immediately before (position).
- the pressure oil supply oil passages 45a and 46a are provided with main relief valves (not shown) as safety means for regulating the maximum discharge pressure of the hydraulic pumps 45 and 46.
- the flow control valves 50b and 50d are hydraulic switching valves having hydraulic pilot portions 50b6, 50b7 and 50d6, 50d7, which are operated by the control pilot pressure generated by the remote control valve of the operating lever devices 34b, 34d for traveling.
- the discharge pressure of the pilot pump 48 is guided as a primary pressure to the remote control valves of the operation lever devices 34b and 34d.
- the hydraulic pumps 45 and 46 and the pilot pump 48 are driven by the engine 44.
- the discharge pressure of the pilot pump 48 is kept at a certain pressure by the pilot relief valve 56.
- This embodiment includes the same flow rate correction device 79 (pressure control valve unit 142) as that of the fifth embodiment.
- the pressure control valve unit 142 has a pipe 81 in which the pressure control valve 42 is arranged, and the upstream side of the pipe 81 is connected to a remote control valve of the left travel operation lever device 34b that outputs a forward control pilot pressure d.
- the downstream side is connected to the tank line.
- the pressure control valve 42 is a variable relief valve, and has an adjustment mechanism 83 that adjusts the urging force of the spring 82 that sets the relief pressure, as an adjustment device for adjusting the maximum flow rate of the flow control valve 50b.
- the adjustment mechanism 83 includes an adjustment pin and a lock nut (not shown) incorporated in the pressure control valve 42, like the plug 37 with an adjustment mechanism shown in FIG. 2B.
- the pressure control valve 42 limits the maximum pressure of the forward control pilot pressure d generated by the remote control valve of the left travel operation lever device 34b to a pressure corresponding to the setting of the spring 82, and the stroke of the flow control valve 50b. Regulate and control flow rate.
- the flow rates guided to the left and right traveling motors 6 and 8 at this time are the same, but in rare cases they are not equal due to manufacturing errors of the main pumps 45 and 46 and the traveling motor, and the speed difference between the left and right traveling motors 6 and 8 (rotational speed difference). ) May occur and traveling meandering may occur.
- the control pilot pressure d (or h) for operating the flow control valve having the higher rotation speed is set to the flow control valve 50b (or The pressure control valve unit 142 is connected between the pipeline leading to 50d) and the tank line. Then, the control pin pressure d (or h) is reduced by operating the adjustment pin of the adjustment mechanism 83 of the pressure control valve 42 to weaken the biasing force of the spring 82, and the stroke of the flow control valve 50b (or 50d) is reduced.
- straight running correction of the traveling meander can be performed.
- FIG. 10 shows a hydraulic drive device for a working machine according to an eighth embodiment of the present invention.
- This embodiment includes the same flow rate correction device 89 (pressure reducing valve unit 143) as that of the sixth embodiment.
- the hydraulic drive device shown in FIG. 10 rotates the left traveling motor 6 when the operating levers of the operating lever devices 34b and 34d for traveling are operated in the full right direction in the drawing with the intention of straight traveling operation. Is higher than the rotational speed of the right travel motor 8, and the forward control pilot pressure d is selected from the control pilot pressure cd generated by the remote control valve of the left travel operation lever device 34b.
- a pressure reducing valve unit 143 having a pressure reducing valve 43 for reducing the forward control pilot pressure d is connected to the pipe leading to the pipe.
- the pressure reducing valve unit 143 has a pipe 91 in which the pressure reducing valve 43 is arranged, and the upstream side of the pipe 91 is connected to a remote control valve of a left traveling operation lever device 34b that outputs a forward control pilot pressure d.
- the downstream side is connected to a conduit that guides the forward control pilot pressure d to the flow control valve 26b.
- the pressure reducing valve 43 has an adjusting mechanism 93 that adjusts the urging force of the spring 92 that sets the pressure reducing valve output pressure as an adjusting device for adjusting the maximum flow rate of the flow control valve 50b for left travel.
- the adjustment mechanism 93 includes an adjustment pin and a lock nut (not shown) incorporated in the pressure reducing valve 43, like the plug 37 with an adjustment mechanism shown in FIG. 2B.
- the pressure reducing valve 43 reduces the maximum pressure of the forward control pilot pressure d generated by the remote control valve of the left travel operation lever device 34b to a pressure corresponding to the setting of the spring 92, and regulates the stroke of the flow control valve 50b. The flow rate is controlled.
- the flow rates guided to the left and right traveling motors 6 and 8 at this time are the same, but in rare cases they are not equal due to manufacturing errors of the main pumps 45 and 46 and the traveling motor, and the speed difference between the left and right traveling motors 6 and 8 (rotational speed difference). ) May occur and traveling meandering may occur.
- the control pilot pressure d (or h) for operating the flow control valve having the higher rotation speed is set to the flow control valve 50b (or 50 d) is connected to the pressure reducing valve unit 143. Then, the control pin pressure d (or h) is reduced by operating the adjustment pin of the adjustment mechanism 93 of the pressure reducing valve 43 to weaken the biasing force of the spring 92, and the stroke of the flow control valve 50b (or 50d) is regulated. Then, by adjusting the output flow rate of the flow rate control valve 50b (or 50d), straight running correction of the traveling meander can be performed.
- the present embodiment can provide the same effects as those of the first embodiment. ⁇ Others>
- some embodiments when the present invention is applied to a hydraulic excavator have been described.
- the present invention is not limited to these embodiments.
- a description will be given of the case where the flow rate correction device is adjusted by attaching the flow rate correction device when it is found that there is a problem of traveling meandering when checking the flow rate correction device before product shipment.
- a flow rate correction device is attached in advance to the hydraulic drive device of the work implement, and then adjustment is performed when it is found that there is a problem of traveling meandering. May be.
- the present invention can be applied to work machines other than the hydraulic excavator (for example, a hydraulic crane, a bulldozer, etc.) as long as the work machine includes a crawler type traveling device. Can be applied to achieve the same effect.
Abstract
Description
図3に油圧ショベルの外観を示す。
<第1の実施形態>
図1A及び図2Bに本発明の第1の実施形態に係わる作業機の油圧駆動装置を示す。
<第2の実施形態>
図4A及び図4Bに本発明の第2の実施形態に係わる作業機の油圧駆動装置を示す。
<第3の実施形態>
図5A及び図5Bに本発明の第3の実施形態に係わる作業機の油圧駆動装置を示す。
<第4の実施形態>
図6A及び図6Bに本発明の第4の実施形態に係わる作業機の油圧駆動装置を示す。
<第5の実施形態>
図7A及び図7Bに本発明の第5の実施形態に係わる作業機の油圧駆動装置を示す。
<第6の実施形態>
図8A及び図8Bに本発明の第6の実施形態に係わる作業機の油圧駆動装置を示す。
<第7の実施形態>
図9に本発明の第7の実施形態に係わる作業機の油圧駆動装置を示す。
<第8の実施形態>
図10に本発明の第8の実施形態に係わる作業機の油圧駆動装置を示す。
<その他>
以上において、本発明を油圧ショベルに適用した場合の幾つかの実施形態を説明したが、本発明はこれらの実施形態に限られるものではない。例えば、第5~第8の実施形態では、流量補正装置を作業機の製品出荷前のチェック時に、走行蛇行の不具合があることが分かった時点で流量補正装置を取り付けて調整を行う場合について説明したが、第2及び第4の実施の形態と同様、作業機の油圧駆動装置に予め流量補正装置を取り付けておき、その後、走行蛇行の不具合があることが分かった時点で調整を行うようにしてもよい。
2 メインポンプ
3 パイロットポンプ
4 コントロールバルブ
5,6,7,8,9,10,11,12 アクチュエータ
(6,8 左右の走行モータ)
13,14,15,16,17,18,19,20 バルブセクション
25 アンロード弁
26a~26h 流量制御弁
27a~27h 圧力補償弁
28a~28h 受圧部
30 エンジン回転数検出弁装置
34a~34h 操作レバー装置
34b 操作レバー装置(走行用操作装置)
34d 操作レバー装置(走行用操作装置)
35 ポンプ制御装置
36b,36d 目標補償差圧調整バネ
37 調整機構付プラグ
37A,37B 調整機構付プラグ
37a プラグ本体
37b 調整ピン
37c ロックナット
38 ハウジング
39 流量補正装置(目標補償差圧調整装置)
39A,39B 流量補正装置(目標補償差圧調整装置)
40 減圧弁
40b,40d 減圧弁
42 圧力制御弁
43 減圧弁
44 エンジン
45,46,47 メインポンプ
49 コントロールバルブ
50a~50h 流量制御弁
61b,61b 弁体
65b,65b プラグ
66b,66d 補正受圧部
69 流量補正装置(目標補償差圧調整装置)
69A,69B 流量補正装置(目標補償差圧調整装置)
71 配管
71b,71d 配管
72 バネ
72b,72d バネ
73 調整機構付プラグ
73b,73d 調整機構付プラグ
79 流量補正装置
81 配管
82 バネ
83 調整機構付プラグ
89 流量補正装置
91 配管
92 バネ
93 調整機構付プラグ
140 減圧弁ユニット
140A,140B 減圧弁ユニット
142 圧力制御弁ユニット
143 減圧弁ユニット
Claims (6)
- エンジン(1)と、このエンジンにより駆動される可変容量型のメインポンプ(2)と、このメインポンプから吐出された圧油により駆動される走行用の第1及び第2油圧モータ(5,8)を含む複数のアクチュエータ(5~12)と、前記メインポンプから前記複数のアクチュエータに供給される圧油の流量を制御する第1及び第2走行用流量制御弁(14,16)を含む複数の流量制御弁(13~20)と、前記第1及び第2走行用油圧モータの回転によってそれぞれ駆動される左右の履帯(310,311)とを備えた履帯式走行装置(315)を備えた作業機の油圧駆動装置において、
前記第1及び第2走行用流量制御弁(14,16)の少なくともどちらか一方の走行用流量制御弁(14)から出力される最大流量を予め設定した流量に制限する流量補正装置(39)を備えることを特徴とする履帯式走行装置を備えた作業機の油圧駆動装置。 - 前記複数の流量制御弁(13~20)の前後差圧をそれぞれ制御する第1及び第2走行用圧力補償弁(27b,27d)を含む複数の圧力補償弁(27a~27h)と、前記メインポンプ(2)の吐出圧が前記複数のアクチュエータ(5~12)の最高負荷圧より目標差圧だけ高くなるようメインポンプの押しのけ容積をロードセンシング制御するポンプ制御装置(35)とを備え、前記複数の圧力補償弁は、前記流量制御弁の前後差圧が前記メインポンプの吐出圧と前記複数のアクチュエータの最高負荷圧との差圧に保持されるようにそれぞれの流量制御弁の前後差圧を制御する請求項1記載の履帯式走行装置(315)を備えた作業機の油圧駆動装置において、
前記流量補正装置(39)は、前記第1及び第走行用圧力補償弁(27b,27d)のうち前記走行用流量制御弁(14)に対応する走行用圧力補償弁(27b)の目標補償差圧を補正する目標補償差圧調整装置(39)であることを特徴とする履帯式走行装置を備えた作業機の油圧駆動装置。 - 請求項2記載の履帯式走行装置(315)を備えた作業機の油圧駆動装置において、
前記目標補償差圧調整装置(39)は、前記走行用圧力補償弁の目標補償差圧を設定するバネ(36b)の付勢力を調整する調整ピン(37b)を有する調整機構付プラグ(37)であることを特徴とする履帯式走行装置を備えた作業機の油圧駆動装置。 - 請求項2記載の履帯式走行装置(315)を備えた作業機の油圧駆動装置において、
前記目標補償差圧調整装置は、前記走行用圧力補償弁の目標補償差圧をパイロット油圧源(33)の圧力を減圧して補正する減圧弁(40)を備えた減圧弁ユニット(140)であることを特徴とする履帯式走行装置を備えた作業機の油圧駆動装置。 - 請求項1記載の履帯式走行装置(315)を備えた作業機の油圧駆動装置において、
前記走行用流量制御弁(14)を操作するための制御パイロット圧を生成するリモコン弁を備えた走行用操作装置(34b)を更に備え、
前記流量補正装置(79)は、前記走行用操作装置のリモコン弁と前記走行用流量制御弁(14)の間に配置され、前記リモコン弁の制御パイロット圧を減圧する圧力制御弁(42)を備えた圧力制御弁ユニット(142)であることを特徴とする履帯式走行装置を備えた作業機の油圧駆動装置。 - 請求項1記載の履帯式走行装置(315)を備えた作業機の油圧駆動装置において、
前記走行用流量制御弁(14)を操作するための制御パイロット圧を生成するリモコン弁を備えた走行用操作装置(34b)を更に備え、
前記流量補正装置(89)は、前記走行用操作装置のリモコン弁と前記走行用流量制御弁(14)の間に配置され、前記リモコン弁の制御パイロット圧を減圧する減圧弁(43)を備えた減圧弁ユニット(143)であることを特徴とする履帯式走行装置を備えた作業機の油圧駆動装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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US13/976,232 US20130287601A1 (en) | 2011-01-06 | 2012-01-05 | Hydraulic drive system for working machine including track device of crawler type |
JP2012551877A JP5750454B2 (ja) | 2011-01-06 | 2012-01-05 | 履帯式走行装置を備えた作業機の油圧駆動装置 |
EP12732178.4A EP2662576B1 (en) | 2011-01-06 | 2012-01-05 | Hydraulic drive of work machine equipped with crawler-type traveling device |
CN201280004518.1A CN103299087B (zh) | 2011-01-06 | 2012-01-05 | 具有履带式行驶装置的作业机的液压驱动装置 |
US15/262,500 US10287751B2 (en) | 2011-01-06 | 2016-09-12 | Hydraulic drive system for working machine including track device of crawler type |
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JP2011001422 | 2011-01-06 | ||
JP2011-001422 | 2011-01-06 |
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US13/976,232 A-371-Of-International US20130287601A1 (en) | 2011-01-06 | 2012-01-05 | Hydraulic drive system for working machine including track device of crawler type |
US15/262,500 Continuation US10287751B2 (en) | 2011-01-06 | 2016-09-12 | Hydraulic drive system for working machine including track device of crawler type |
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WO2012093703A1 true WO2012093703A1 (ja) | 2012-07-12 |
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EP (1) | EP2662576B1 (ja) |
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Also Published As
Publication number | Publication date |
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US10287751B2 (en) | 2019-05-14 |
US20160376769A1 (en) | 2016-12-29 |
EP2662576A4 (en) | 2018-01-10 |
US20130287601A1 (en) | 2013-10-31 |
JPWO2012093703A1 (ja) | 2014-06-09 |
CN103299087A (zh) | 2013-09-11 |
EP2662576A1 (en) | 2013-11-13 |
CN103299087B (zh) | 2016-07-06 |
EP2662576B1 (en) | 2021-06-02 |
JP5750454B2 (ja) | 2015-07-22 |
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