WO2015115428A1 - 作業機の制御システム及び低圧選択回路 - Google Patents
作業機の制御システム及び低圧選択回路 Download PDFInfo
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- WO2015115428A1 WO2015115428A1 PCT/JP2015/052206 JP2015052206W WO2015115428A1 WO 2015115428 A1 WO2015115428 A1 WO 2015115428A1 JP 2015052206 W JP2015052206 W JP 2015052206W WO 2015115428 A1 WO2015115428 A1 WO 2015115428A1
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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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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
- F15B11/10—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor in which the servomotor position is a function of the pressure also pressure regulators as operating means for such systems, the device itself may be a position indicating system
-
- 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
- E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—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
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2282—Systems using center bypass type changeover valves
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2285—Pilot-operated systems
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2292—Systems with two or more pumps
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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
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
-
- 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
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the 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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
- F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
Definitions
- the present invention relates to a work machine control system and a low-pressure selection circuit.
- JP 10-088627A discloses an excavating and turning work machine that supplies hydraulic oil from a first pump, a second pump, and a third pump to each circuit system.
- a split flow pump in which discharge ports are arranged in two stages in a single cylinder block and can simultaneously discharge two systems of hydraulic oil. May be used.
- the discharge flow rate of hydraulic oil to the two circuit systems is the same. Therefore, it is necessary to detect whether or not the actuator is operating by switching the operation valve in each of the two circuit systems by using a pressure sensor or the like and adjusting the discharge flow rate of the split flow pump.
- the present invention aims to make it possible to adjust the discharge flow rate of a split flow pump with a simple configuration when a split flow pump is used in a working machine having a plurality of circuit systems.
- a work machine control system that controls a work machine having a first actuator and a second actuator is a split flow type that discharges a working fluid from a first discharge port and a second discharge port.
- the fluid pressure pump, the working fluid discharged from the first discharge port, the first operation valve for controlling the first actuator, and the first discharge port in a state where the first operation valve is in the normal position A first circuit system having a first neutral passage communicating with the tank, a second operation valve that is supplied with the working fluid discharged from the second discharge port and controls the second actuator, and the second operation valve
- a second circuit system having a second neutral passage for communicating the second discharge port with the tank in a state where the second discharge port is in a normal position, and under the first operation valve of the first neutral passage.
- a low-pressure selection circuit that communicates by selecting the lower of the pressure of the downstream of the working fluid of the second operating valve for the working fluid between said second neutral passage.
- the fluid pressure pump is adjusted so that the discharge flow rate increases as the pressure of the working fluid selected by the low pressure selection circuit decreases.
- FIG. 1 is a configuration diagram of a work machine to which a work machine control system according to an embodiment of the present invention is applied.
- FIG. 2 is a circuit diagram of the work machine control system according to the embodiment of the present invention.
- FIG. 3 is an enlarged view of the low voltage selection circuit in FIG.
- FIG. 4 is a diagram for explaining a modification of the low voltage selection circuit.
- control system 100 a working machine control system (hereinafter simply referred to as a “control system”) 100 according to an embodiment of the present invention will be described with reference to the drawings.
- a hydraulic excavator 1 as a working machine to which the control system 100 is applied will be described with reference to FIG.
- the working machine is the hydraulic excavator 1
- the control system 100 can also be applied to other working machines such as a wheel loader.
- the working oil is used as the working fluid, but other fluids such as working water may be used as the working fluid.
- the hydraulic excavator 1 includes a crawler-type traveling unit 2, a swivel unit 3 that can be pivoted on an upper part of the traveling unit 2, and an excavation unit 5 that is disposed at the front center of the swivel unit 3.
- the traveling unit 2 travels the excavator 1 by driving a pair of left and right crawlers 2a by a traveling motor (not shown).
- the turning unit 3 is driven by a turning motor (not shown) and turns in the left-right direction with respect to the traveling unit 2.
- the excavation unit 5 includes a boom 6 that is rotatably supported around a horizontal axis that extends in the left-right direction of the swivel unit 3, an arm 7 that is rotatably supported on the tip of the boom 6, and a pivot that rotates around the tip of the arm 7. And a bucket 8 that is movably supported and excavates earth and sand. Further, the excavation unit 5 includes a boom cylinder 6 a that rotates the boom 6 up and down, an arm cylinder 7 a that rotates the arm 7 up and down, and a bucket cylinder 8 a that rotates the bucket 8.
- the control system 100 is discharged from a hydraulic pump 10 as a fluid pressure pump that discharges hydraulic oil, a first circuit system 20 to which hydraulic oil discharged from the first discharge port 12 is supplied, and a second discharge port 13.
- the second circuit system 30 to which the operating oil is supplied, the operating oil downstream of the operation valves 21 to 23 of the first neutral passage 25 in the first circuit system 20, and the operation of the second neutral passage 35 in the second circuit system 30.
- a low-pressure selection circuit 40 that selects and communicates the lower one of the hydraulic oils downstream of the valves 31 to 34.
- the control system 100 controls the operation of a plurality of actuators of the excavator 1.
- the control system 100 includes another pump (not shown) that supplies hydraulic oil to a third circuit system (not shown) having another actuator such as a swing motor.
- the hydraulic pump 10 is driven by an engine (not shown).
- the hydraulic pump 10 has a split flow in which a first discharge port 12 and a second discharge port 13 are arranged in two stages in a single cylinder block (not shown) and can simultaneously discharge two systems of hydraulic oil.
- the hydraulic pump 10 distributes hydraulic oil equally from the first discharge port 12 and the second discharge port 13.
- the hydraulic pump 10 is a variable displacement pump that includes a swash plate (not shown) whose tilt angle is adjusted by a regulator 11 controlled by pilot pressure, and whose discharge flow rate is adjusted by the tilt angle of the swash plate.
- the hydraulic pump 10 uses the hydraulic oil pressure selected by the low pressure selection circuit 40 as a pilot pressure, and the tilt angle of the swash plate is adjusted so that the discharge flow rate increases as the pilot pressure decreases.
- the discharge flow rate of the hydraulic oil discharged from the first discharge port 12 and the second discharge port 13 is adjusted by a single regulator 11.
- the hydraulic fluid discharged from the hydraulic pump 10 passes through the first discharge passage 15 connected to the first discharge port 12 and the second discharge passage 16 connected to the second discharge port 13, and the first circuit system 20. And the second circuit system 30 respectively.
- a main relief valve 18 is provided downstream of the first discharge passage 15 and the second discharge passage 16 so as to open when a predetermined main relief pressure is exceeded and keep the operating hydraulic pressure below the main relief pressure.
- the first discharge passage 15 and the second discharge passage 16 are respectively provided with check valves 15a and 16a that allow only the flow of hydraulic oil to the main relief valve 18.
- the predetermined main relief pressure is set high enough to ensure a minimum operating pressure for each of the operation valves 21 to 23 and 31 to 34 described later.
- the first circuit system 20 includes, in order from the upstream side, an operation valve 21 that controls the travel motor of the left crawler 2a, an operation valve 22 that controls the boom cylinder 6a, and an operation valve 23 that controls the bucket cylinder 8a. Prepare. These operation valves 21 to 23 correspond to the first operation valve, and the traveling motor, the boom cylinder 6a, and the bucket cylinder 8a correspond to the first actuator.
- the first circuit system 20 includes a first neutral passage 25 that allows the first discharge passage 15 to communicate with the tank 19 in a state where the operation valves 21 to 23 are all in the normal position, and a parallel passage that is provided in parallel with the first neutral passage 25. 26.
- a throttle 27 for generating a pilot pressure as a negative control pressure is provided downstream of the operation valve 23 in the first neutral passage 25.
- the throttle 27 is provided in parallel with a pilot relief valve 28 that opens when the pilot pressure generated upstream of the throttle 27 exceeds a predetermined pilot relief pressure and keeps the pilot pressure below the pilot relief pressure.
- the predetermined pilot relief pressure is set lower than the main relief pressure of the main relief valve 18 so that no abnormal pressure is generated in the throttle 27.
- a first pilot passage 29 is connected to the upstream side of the throttle 27.
- the pilot pressure generated by the throttle 27 is guided to the first pilot passage 29.
- the first pilot passage 29 is connected to the low pressure selection circuit 40.
- the operation valves 21 to 23 control the operation of each actuator by controlling the flow rate of hydraulic oil guided from the hydraulic pump 10 to each actuator.
- the operation valves 21 to 23 are operated by pilot pressure supplied when the operator of the excavator 1 manually operates the operation lever.
- the operation valve 21 is normally in the normal position by the biasing force of the pair of centering springs, and is switched to the first switching position and the second switching position by the pilot pressure supplied from the pilot passages 21a and 21b.
- the operation valve 22 is normally in the normal position by the biasing force of the pair of return springs, and is switched to the first switching position and the second switching position by the pilot pressure supplied from the pilot passages 22a and 22b.
- the operation valve 23 is normally in the normal position by the urging force of the pair of return springs, and is switched to the first switching position and the second switching position by the pilot pressure supplied from the pilot passages 23a and 23b.
- the second circuit system 30 includes, in order from the upstream side, an operation valve 31 that controls the traveling motor of the right crawler 2a, an operation valve 32 that controls the spare actuator, and an operation valve 33 that also controls the spare actuator, And an operation valve 34 for controlling the arm cylinder 7a.
- These operation valves 31 to 34 correspond to the second operation valve, and the traveling motor, the spare actuator, and the arm cylinder 7a correspond to the second actuator.
- the second circuit system 30 includes a second neutral passage 35 that allows the second discharge passage 16 to communicate with the tank 19 in a state where the operation valves 31 to 34 are all in the normal position, and a parallel passage that is provided in parallel with the second neutral passage 35. 36.
- a throttle 37 for generating a pilot pressure as a negative control pressure is provided on the downstream side of the operation valve 34 in the second neutral passage 35.
- the throttle 37 is provided in parallel with a pilot relief valve 38 that opens when the pilot pressure generated upstream of the throttle 37 exceeds a predetermined pilot relief pressure and keeps the pilot pressure below the pilot relief pressure.
- the predetermined pilot relief pressure is set lower than the main relief pressure of the main relief valve 18 to such an extent that no abnormal pressure is generated in the throttle 37.
- a second pilot passage 39 is connected to the upstream side of the throttle 37.
- the pilot pressure generated by the throttle 37 is guided to the second pilot passage 39.
- the second pilot passage 39 is connected to the low pressure selection circuit 40.
- the operation valves 31 to 34 control the operation of each actuator by controlling the flow rate of hydraulic oil guided from the hydraulic pump 10 to each actuator.
- Each of the operation valves 31 to 34 is operated by a pilot pressure supplied when the operator of the excavator 1 manually operates the operation lever.
- the operation valve 31 is normally in the normal position by the biasing force of the pair of centering springs, and is switched to the first switching position and the second switching position by the pilot pressure supplied from the pilot passages 31a and 31b.
- the operation valve 32 is normally in the normal position by the urging force of the pair of return springs, and is switched to the first switching position and the second switching position by the pilot pressure supplied from the pilot passages 32a and 32b.
- the operation valve 33 is normally in the normal position by the urging force of the pair of return springs, and is switched to the first switching position and the second switching position by the pilot pressure supplied from the pilot passages 33a and 33b.
- the operation valve 34 is normally in the normal position by the urging force of the pair of return springs, and is switched to the first switching position and the second switching position by the pilot pressure supplied from the pilot passages 34a and 34b.
- the low pressure selection circuit 40 selects a high pressure side hydraulic oil from a first neutral passage 25 as a first fluid passage and a second neutral passage 35 as a second fluid passage. Are switched according to the pressure of the hydraulic fluid selected by the shuttle valve 41 and the hydraulic pressure selected by the shuttle valve 41, and the hydraulic fluid on the high pressure side of the first neutral passage 25 and the second neutral passage 35 is shut off, and the hydraulic fluid on the low pressure side Is provided with a first switching valve 45 and a second switching valve 46 serving as switching valves that lead the pilot pressure to the regulator 11 through the pilot passage 11a.
- the shuttle valve 41 selects one of the hydraulic oils on the high pressure side from the first pilot passage 29 connected to the first neutral passage 25 and the second pilot passage 39 connected to the second neutral passage 35. It leads to the pilot passage 41a.
- the first switching valve 45 includes a blocking position 45 a that blocks hydraulic fluid from the first pilot passage 29 and a communication position 45 b that allows hydraulic fluid from the first pilot passage 29 to communicate.
- the first switching valve 45 is provided with a spool (not shown) on which the pilot pressure of the pilot passage 41a acts on one side and the urging force of the return spring 45c and the pilot pressure of the pilot passage 45d act on the other side. The hydraulic pressure of the first pilot passage 29 is guided to the pilot passage 45d.
- the second switching valve 46 includes a blocking position 46a for blocking hydraulic oil from the second pilot passage 39 and a communication position 46b for allowing hydraulic oil from the second pilot passage 39 to communicate.
- the second switching valve 46 includes a spool (not shown) on which the pilot pressure of the pilot passage 41a acts on one side and the urging force of the return spring 46c and the pilot pressure of the pilot passage 46d act on the other side. The hydraulic pressure of the second pilot passage 39 is guided to the pilot passage 46d.
- One of the first switching valve 45 and the second switching valve 46 is switched to the communication positions 45b and 46b by the pressure of the hydraulic oil selected by the shuttle valve 41, and the hydraulic fluid that has passed is guided to the regulator 11 as a pilot pressure. .
- the hydraulic oil discharged from the hydraulic pump 10 is distributed to the first neutral passage 25 and the second neutral passage 35 and guided to the low pressure selection circuit 40.
- a pilot pressure in the first pilot passage 29 connected to the first neutral passage 25 and a pilot pressure in the second pilot passage 39 connected to the second neutral passage 35 are guided to the low pressure selection circuit 40.
- the pilot pressure in the first pilot passage 29 and the pilot pressure in the second pilot passage 39 have different sizes depending on piping resistance and the like. Here, a case where the pilot pressure in the first pilot passage 29 is higher than the pilot pressure in the second pilot passage 39 will be described.
- the shuttle valve 41 guides the pilot pressure of the first pilot passage 29 on the high pressure side to the pilot passage 41a.
- the first switching valve 45 is switched to the cutoff position 45a by the urging force of the return spring 45c because the pilot pressure in the pilot passage 45d and the pilot pressure in the pilot passage 41a are substantially the same.
- the differential pressure of the second switching valve 46 overcomes the urging force of the return spring 46c and is switched to the communication position 46b.
- the pilot pressure in the second pilot passage 39 that has passed through the second switching valve 46 is guided to the regulator 11 of the hydraulic pump 10 through the pilot passage 11a.
- the operation valves 21 to 23 of the first circuit system 20 and the operation valves 31 to 34 of the second circuit system 30 are all in the normal position. Therefore, hydraulic oil is not led to each actuator, and the pilot pressure led to the regulator 11 is relatively high. Therefore, the tilt angle of the swash plate of the hydraulic pump 10 is adjusted so that the discharge flow rate is reduced. Therefore, the hydraulic pump 10 is adjusted to the minimum discharge flow rate when the operation valves 21 to 23 and 31 to 34 are not operated.
- the operator When the boom 6 rotates, the operator operates the operation lever, whereby pilot pressure is supplied from the pilot passage 22a or the pilot passage 22b, and the operation valve 22 is switched to the first switching position or the second switching position. It is done. Thereby, a part of the hydraulic fluid guided from the first discharge port 12 of the hydraulic pump 10 to the first circuit system 20 is guided from the operation valve 22 to the boom cylinder 6a. Therefore, the hydraulic pressure in the first neutral passage 25 downstream from the operation valve 22 is reduced as compared with the case where the boom 6 is not rotating.
- the shuttle valve 41 guides the pilot pressure of the second pilot passage 39 on the high pressure side to the pilot passage 41a.
- the differential pressure of the first switching valve 45 overcomes the urging force of the return spring 45c and is switched to the communication position 45b.
- the second switching valve 46 is switched to the cutoff position 46a by the urging force of the return spring 46c.
- the pilot pressure in the first pilot passage 29 that has passed through the first switching valve 45 is guided to the regulator 11 of the hydraulic pump 10 through the pilot passage 11a.
- the operation valve 22 of the first circuit system 20 is switched to the first switching position or the second switching position. Therefore, the pilot pressure guided to the regulator 11 is lower than when the operation valve 22 is in the normal position. Therefore, in the hydraulic pump 10, the tilt angle of the swash plate is adjusted so that the discharge flow rate increases.
- the operation valve 22 of the first circuit system 20 when the operation valve 22 of the first circuit system 20 is operated and the boom cylinder 6a operates, the pressure of the hydraulic oil downstream of the first neutral passage 25 of the first circuit system 20 decreases. Therefore, the pilot pressure of the first pilot passage 29 on the lowered side is selected by the low pressure selection circuit 40, and the discharge flow rate of the hydraulic pump 10 is adjusted to be increased by the selected pilot pressure. Therefore, when the operation valve 22 is operated, the discharge flow rate is adjusted to be necessary for the operation of the boom cylinder 6a.
- the discharge flow rate of the hydraulic pump 10 can be adjusted with a simple configuration without using a pressure sensor or a controller.
- the pressure of the hydraulic oil downstream of the first neutral passage 25 of the first circuit system 20 decreases. Therefore, the pilot pressure in the first pilot passage 29 is selected by the low pressure selection circuit 40 and is adjusted so that the discharge flow rate of the hydraulic pump 10 is increased.
- the pilot pressure in the second pilot passage 39 is selected by the low pressure selection circuit 40 and is adjusted so that the discharge flow rate of the hydraulic pump 10 is increased.
- the hydraulic pump 10 is adjusted to the minimum discharge flow rate, and any one of the operation valves 21 to 23 and 31 to 34 is operated.
- the discharge flow rate is adjusted to be necessary for the operation of the actuator. Therefore, the discharge flow rate of the hydraulic pump 10 can be adjusted with a simple configuration without using a pressure sensor or a controller.
- the low pressure selection circuit 50 is different from the low pressure selection circuit 40 in that it includes a single switching valve 55.
- the low pressure selection circuit 50 is based on a shuttle valve 41 as a high pressure selection valve for selecting hydraulic oil on the high pressure side of the first neutral passage 25 and the second neutral passage 35, and the pressure of the hydraulic oil selected by the shuttle valve 41.
- a switching valve 55 that is switched and shuts off the high-pressure side hydraulic oil in the first neutral passage 25 and the second neutral passage 35 and guides the low-pressure side hydraulic oil to the regulator 11 through the pilot passage 11a as a pilot pressure. .
- the switching valve 55 shuts off the hydraulic oil from the first pilot passage 29 and the second pilot passage 39 and communicates only the hydraulic oil from the pilot passage 41 a and the operation from the second pilot passage 39.
- a second switching position 55b for communicating only oil and a third switching position 55c for communicating only hydraulic oil from the first pilot passage 29 are provided.
- the switching valve 55 has a spool (not shown) on which the urging force of the centering spring 55d and the pilot pressure of the pilot passage 55f act on one side, and the urging force of the centering spring 55e and the pilot pressure on the pilot passage 55g on the other side. Prepare.
- the hydraulic pressure of the first pilot passage 29 is led to the pilot passage 55f
- the hydraulic pressure of the second pilot passage 39 is led to the pilot passage 55g.
- the switching valve 55 When there is almost no difference in pilot pressure between the first pilot passage 29 and the second pilot passage 39, the switching valve 55 is switched to the first switching position 55a by the urging force of the centering springs 55d and 55e.
- the switching valve 55 When the pilot pressure in the first pilot passage 29 is higher than the pilot pressure in the second pilot passage 39, the switching valve 55 is switched to the second switching position 55b by the pilot pressure in the pilot passage 55f. Thereby, the pilot pressure of the second pilot passage 39 whose pressure is lower than that of the first pilot passage 29 is guided to the regulator 11 of the hydraulic pump 10 through the pilot passage 11a.
- the switching valve 55 is switched to the third switching position 55c by the pilot pressure in the pilot passage 55g.
- the pilot pressure of the first pilot passage 29 having a lower pressure than that of the second pilot passage 39 is guided to the regulator 11 of the hydraulic pump 10 through the pilot passage 11a.
- the hydraulic pump 10 performs the minimum discharge.
- the flow rate is adjusted and any of the operation valves 21 to 23 and 31 to 34 is operated, the flow rate is adjusted to the discharge flow rate necessary for the operation of the actuator. Therefore, the discharge flow rate of the hydraulic pump 10 can be adjusted with a simple configuration without using a pressure sensor or a controller.
- the cost can be reduced compared to the low pressure selection circuit 40 in which the first switching valve 45, the second switching valve and 46 are used as switching valves. Is possible.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
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- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims (5)
- 第一アクチュエータと第二アクチュエータとを有する作業機を制御する作業機の制御システムであって、
作動流体を第一吐出ポートと第二吐出ポートとから吐出するスプリットフロー型の流体圧ポンプと、
前記第一吐出ポートから吐出された作動流体が供給され、前記第一アクチュエータを制御する第一操作弁と当該第一操作弁がノーマル位置にある状態で前記第一吐出ポートをタンクに連通させる第一中立通路とを有する第一回路系統と、
前記第二吐出ポートから吐出された作動流体が供給され、前記第二アクチュエータを制御する第二操作弁と当該第二操作弁がノーマル位置にある状態で前記第二吐出ポートをタンクに連通させる第二中立通路とを有する第二回路系統と、
前記第一中立通路の前記第一操作弁の下流の作動流体と前記第二中立通路の前記第二操作弁の下流の作動流体とのうち圧力の低い方を選択して連通させる低圧選択回路と、を備え、
前記流体圧ポンプは、前記低圧選択回路によって選択された作動流体の圧力が低いほど吐出流量が多くなるように調整される作業機の制御システム。 - 請求項1に記載の作業機の制御システムであって、
前記流体圧ポンプは、前記低圧選択回路によって選択された作動流体の圧力をパイロット圧として制御される単一のレギュレータによって傾転角が調整される斜板を備え、前記レギュレータによって吐出流量が調整される作業機の制御システム。 - 請求項2に記載の作業機の制御システムであって、
前記低圧選択回路は、
前記第一中立通路と前記第二中立通路のうち高圧側の作動流体を選択する高圧選択弁と、
前記高圧選択弁で選択された作動流体の圧力によって切り換えられ、前記第一中立通路と前記第二中立通路とのうち高圧側の作動流体を遮断し、低圧側の作動流体を前記パイロット圧として前記レギュレータに導く切換弁と、を備える作業機の制御システム。 - 請求項3に記載の作業機の制御システムであって、
前記切換弁は、
前記第一中立通路からの作動流体を遮断可能な第一切換弁と、
前記第二中立通路からの作動流体を遮断可能な第二切換弁と、を備え、
前記第一切換弁と前記第二切換弁との一方は、前記高圧選択弁で選択された作動流体の圧力によって連通状態に切り換えられ、通過した作動流体が前記パイロット圧として前記レギュレータに導かれる作業機の制御システム。 - 第一流体通路と第二流体通路のうち高圧側の作動流体を選択する高圧選択弁と、
前記高圧選択弁で選択された作動流体の圧力によって切り換えられ、前記第一流体通路と前記第二流体通路とのうち高圧側の作動流体を遮断し、低圧側の作動流体を連通させる切換弁と、を備える低圧選択回路。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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DE112015000185.9T DE112015000185T5 (de) | 2014-01-31 | 2015-01-27 | Arbeitsmaschinen-Steuerungssystem und Auswahlkreislauf für niedrigeren Druck |
CN201580002576.4A CN105723100B (zh) | 2014-01-31 | 2015-01-27 | 工程机械的控制***和低压选择回路 |
US15/032,908 US10273983B2 (en) | 2014-01-31 | 2015-01-27 | Working machine control system and lower pressure selection circuit |
KR1020167011103A KR101807980B1 (ko) | 2014-01-31 | 2015-01-27 | 작업기의 제어 시스템 및 저압 선택 회로 |
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JP2014016473A JP6286216B2 (ja) | 2014-01-31 | 2014-01-31 | 作業機の制御システム及び低圧選択回路 |
JP2014-016473 | 2014-01-31 |
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WO2015115428A1 true WO2015115428A1 (ja) | 2015-08-06 |
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US (1) | US10273983B2 (ja) |
JP (1) | JP6286216B2 (ja) |
KR (1) | KR101807980B1 (ja) |
CN (1) | CN105723100B (ja) |
DE (1) | DE112015000185T5 (ja) |
WO (1) | WO2015115428A1 (ja) |
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DE102015211704A1 (de) * | 2015-06-24 | 2016-12-29 | Robert Bosch Gmbh | Ventilbaugruppe mit zumindest zwei Pumpenleitungen für eine Pumpe |
JP7190933B2 (ja) * | 2019-02-15 | 2022-12-16 | 日立建機株式会社 | 建設機械 |
JP7471901B2 (ja) | 2020-04-28 | 2024-04-22 | ナブテスコ株式会社 | 流体圧駆動装置 |
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JPS5892554U (ja) * | 1981-12-17 | 1983-06-23 | 内田油圧機器工業株式会社 | 高低圧選択バルプ |
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JPS5569782A (en) * | 1978-11-20 | 1980-05-26 | Japan Steel Works Ltd:The | Output-power controller for pumps |
DE3733677A1 (de) * | 1987-10-05 | 1989-04-13 | Rexroth Mannesmann Gmbh | Lastunabhaengige steuereinrichtung fuer hydraulische verbraucher |
JP3681833B2 (ja) | 1996-09-19 | 2005-08-10 | ヤンマー株式会社 | 掘削旋回作業機の油圧回路 |
NL1025806C2 (nl) * | 2004-03-25 | 2005-09-27 | Demolition And Recycling Equip | Hydraulische cilinder bijvoorbeeld voor toepassing bij een hydraulisch gereedschap. |
US7302797B2 (en) * | 2005-05-31 | 2007-12-04 | Caterpillar Inc. | Hydraulic system having a post-pressure compensator |
CN201218255Y (zh) * | 2008-05-29 | 2009-04-08 | 广西柳工机械股份有限公司 | 平地机前轮驱动液压负荷传感装置 |
JP5480847B2 (ja) * | 2011-06-21 | 2014-04-23 | 株式会社クボタ | 作業機 |
-
2014
- 2014-01-31 JP JP2014016473A patent/JP6286216B2/ja active Active
-
2015
- 2015-01-27 KR KR1020167011103A patent/KR101807980B1/ko active IP Right Grant
- 2015-01-27 DE DE112015000185.9T patent/DE112015000185T5/de not_active Withdrawn
- 2015-01-27 CN CN201580002576.4A patent/CN105723100B/zh active Active
- 2015-01-27 WO PCT/JP2015/052206 patent/WO2015115428A1/ja active Application Filing
- 2015-01-27 US US15/032,908 patent/US10273983B2/en active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS5892554U (ja) * | 1981-12-17 | 1983-06-23 | 内田油圧機器工業株式会社 | 高低圧選択バルプ |
JPS6019803U (ja) * | 1983-07-19 | 1985-02-12 | 三菱重工業株式会社 | 低値選択油圧回路 |
JPS6047904U (ja) * | 1983-09-08 | 1985-04-04 | 三菱重工業株式会社 | 低値選択油圧回路 |
JP2000074233A (ja) * | 1998-08-27 | 2000-03-14 | Shin Caterpillar Mitsubishi Ltd | 流体圧切換弁 |
WO2009123047A1 (ja) * | 2008-03-31 | 2009-10-08 | 株式会社不二越 | 建設機械の油圧回路 |
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KR20160063376A (ko) | 2016-06-03 |
US20160265560A1 (en) | 2016-09-15 |
KR101807980B1 (ko) | 2017-12-11 |
CN105723100B (zh) | 2017-07-04 |
CN105723100A (zh) | 2016-06-29 |
US10273983B2 (en) | 2019-04-30 |
JP2015143531A (ja) | 2015-08-06 |
JP6286216B2 (ja) | 2018-02-28 |
DE112015000185T5 (de) | 2016-07-07 |
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