WO2019065510A1 - 液圧システム - Google Patents

液圧システム Download PDF

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Publication number
WO2019065510A1
WO2019065510A1 PCT/JP2018/035102 JP2018035102W WO2019065510A1 WO 2019065510 A1 WO2019065510 A1 WO 2019065510A1 JP 2018035102 W JP2018035102 W JP 2018035102W WO 2019065510 A1 WO2019065510 A1 WO 2019065510A1
Authority
WO
WIPO (PCT)
Prior art keywords
supply line
pressure
pump
side supply
tank
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/035102
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
哲弘 近藤
広明 三井
敏久 豊田
治生 山田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kawasaki Heavy Industries Ltd
Kawasaki Motors Ltd
Original Assignee
Kawasaki Heavy Industries Ltd
Kawasaki Jukogyo KK
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kawasaki Heavy Industries Ltd, Kawasaki Jukogyo KK filed Critical Kawasaki Heavy Industries Ltd
Priority to US16/652,134 priority Critical patent/US10907659B2/en
Priority to CN201880062585.6A priority patent/CN111108292B/zh
Priority to GB2006245.1A priority patent/GB2581683B/en
Publication of WO2019065510A1 publication Critical patent/WO2019065510A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • 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
    • F15B2211/20515—Electric motor
    • 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
    • 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
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/27—Directional control by means of the pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member

Definitions

  • the present invention relates to a hydraulic system in which a single-rod hydraulic cylinder and a pump are connected to form a closed circuit.
  • Patent Document 1 discloses a hydraulic system 100 as shown in FIGS. 5A and 5B.
  • a single rod hydraulic cylinder 120 and a pump 110 are connected by a rod side supply line 131 and a head side supply line 132 so as to form a closed circuit.
  • a first tank line 141 is branched from the rod side supply line 131, and a second tank line 151 is branched from the head side supply line 132. Pilot check valves 142 and 152 are provided in the first tank line 141 and the second tank line 151, respectively.
  • the pilot check valve 142 provided in the first tank line 141 releases the backflow prevention function when the pressure in the head side supply line 132 increases, and the pilot check valve 152 provided in the second tank line 151 When the pressure in the rod side supply line 131 becomes high, the backflow prevention function is released.
  • the pump suction flow rate (theoretical flow rate) is insufficient with respect to the flow rate discharged from the rod, so no force opposing load is generated.
  • the speed of the pressure cylinder 120 is accelerated by the load.
  • a shock occurs at the moment when the force opposing the load (external force) acting on the cylinder disappears, and at the moment when the flow rate flowing into the pump 110 matches the pump suction flow rate.
  • Such a change in the velocity of the hydraulic cylinder due to the reversal of the direction of the load also occurs when the direction of the load reverses from the extension direction to the reduction direction.
  • the direction of the load is the extension direction as shown in FIG. 6A at the time of the shortening operation of the hydraulic cylinder 120
  • the pressure of the rod side supply line 131 becomes high against the load and the speed of the hydraulic cylinder 120 Is controlled by the discharge flow rate of the pump 110.
  • the pilot check valve 152 of the second tank line 151 is opened, and the hydraulic fluid at a flow rate difference between the pressure receiving area of the head side chamber and the rod side chamber of the hydraulic cylinder 120 flows into the tank 160 through the second tank line 151.
  • the pilot check valve 142 of the first tank line 141 is opened by the pressure of the head side supply line 132, and the hydraulic fluid of the flow rate difference between the head side chamber and the rod side chamber of the hydraulic cylinder 120 is the first tank line 141 Flow into the tank 160 through the That is, when the direction of the load reverses from the extension direction to the shortening direction at the time of the shortening operation of the hydraulic cylinder 120, not only the mechanical shock occurs but also the speed of the hydraulic cylinder 120 changes. More specifically, the flow rate flowing into the pump 110 rapidly increases, and the pressure on the suction side rapidly increases by the amount exceeding the theoretical discharge (suction) flow rate of the pump 110 and the speed of the hydraulic cylinder 120 rapidly decelerates.
  • the rotational speed of the rotary machine driving the pump 110 is instantaneously It is possible to change.
  • the rotating machine is an engine.
  • the rotary machine is a servomotor, a device for detecting the stroke speed of the cylinder and a sensor for detecting the pressure at both ports of the pump are required, and the configuration of the hydraulic system becomes complicated.
  • the hydraulic system of the present invention is a single-rod hydraulic cylinder including a rod side chamber and a head side chamber, and a variable displacement having a first port and a second port driven by a rotary machine.
  • Type pump a flow control device for switching the displacement per rotation of the pump between a first set value and a second set value smaller than the first set value, and the rod side chamber of the first port
  • a rod side supply line connecting to the head side, a head side supply line connecting the second port to the head side chamber so as to form a closed circuit together with the pump, the rod side supply line and the hydraulic cylinder;
  • a first tank line branched from the side supply line and connected to the tank, and a direction from the tank to the rod side supply line provided in the first tank line
  • a first pilot check valve which permits flow but prohibits reverse flow, and which releases the backflow prevention function when the pressure on the head side supply line becomes higher than a first set pressure, and the head
  • the second tank line branched from the side supply line and connected to the tank,
  • the pressure and the pressure of the head side supply line are derived, and the flow rate adjustment device is configured to perform the pressure when the pressure of the head side supply line is higher than the pressure of the rod side supply line.
  • the displacement of the pump is switched to the first set value, and the displacement of the pump is switched to the second set value when the pressure of the rod side supply line is higher than the pressure of the head side supply line.
  • the pump suction flow rate can be matched with the discharge flow rate from the rod side by reducing the discharge (suction) volume of the pump and reducing the discharge (suction) flow rate of the pump.
  • the passage of the hydraulic fluid drawn from the tank is switched from the first tank line to the second tank line. In this way, it is possible to suppress the change in the speed of the hydraulic cylinder (acceleration) without instantaneously changing the rotational speed of the rotary machine.
  • the pressure on the head side supply line increases against the load, and the cylinder speed is discharged from the rod side
  • the control by the flow rate changes to the control by the supply flow rate to the head side.
  • the pump discharge flow rate can be made to coincide with the supply flow rate to the head side by increasing the discharge (suction) volume of the pump and thus increasing the discharge (suction) flow rate.
  • the passage of the hydraulic fluid drawn from the tank is switched from the second tank line to the first tank line. In this way, it is possible to suppress the change (deceleration) of the speed of the hydraulic cylinder without instantaneously changing the rotational speed of the rotary machine.
  • the ratio of the first set value to the second set value may be equal to the pressure receiving area ratio of the head side chamber to the rod side chamber of the hydraulic cylinder. According to this configuration, it is possible to significantly suppress the change in the speed of the hydraulic cylinder.
  • the rotary machine is a servomotor
  • the first port and the second port of the pump may be switched between the discharge side and the suction side according to the rotation direction of the rotary machine.
  • the first and second ports of the pump may be switched between the discharge side and the suction side by tilting the swash plate or the slant axis of the pump in both directions beyond the reference line.
  • the present invention it is possible to suppress the change in the speed of the hydraulic cylinder without instantaneously changing the rotational speed of the rotary machine even if the direction of the load is reversed during the expansion operation and the contraction operation of the hydraulic cylinder. it can.
  • FIGS. 2A and 2B show the flow of hydraulic fluid during extension operation of a hydraulic cylinder
  • FIG. 2A shows the case where the load direction is the shortening direction
  • FIG. 2B shows the case where the load direction is the extension direction
  • FIGS. 3A and 3B show the flow of hydraulic fluid during the shortening operation of the hydraulic cylinder
  • FIG. 3A shows the case where the load direction is the extension direction
  • FIG. 3B shows the case where the load direction is the shortening direction.
  • 5A and 5B are schematic views of a conventional hydraulic system, showing the flow of hydraulic fluid during extension operation of the hydraulic cylinder.
  • 6A and 6B are schematic views of a conventional hydraulic system, showing the flow of hydraulic fluid during the shortening operation of the hydraulic cylinder.
  • FIG. 1 shows a hydraulic system 1 according to an embodiment of the present invention.
  • the hydraulic system 1 includes a single-rod hydraulic cylinder 4, a pump 2 connected to the hydraulic cylinder 4 to form a closed circuit, and a rotary machine 3 for driving the pump 2.
  • the hydraulic fluid flowing through the closed circuit is typically oil, but may be liquid other than oil.
  • the hydraulic cylinder 4 includes a rod side chamber 41 and a head side chamber 42 separated from each other by a piston.
  • a rod extends from the piston so as to penetrate the rod side chamber 41.
  • the pump 2 has a first port 21 and a second port 22.
  • the first port 21 is connected to the rod side chamber 41 of the hydraulic cylinder 4 by the rod side supply line 51
  • the second port 22 is connected to the head side chamber 42 of the hydraulic cylinder 4 by the head side supply line 52.
  • the rod side supply line 51 and the head side supply line 52 form the above-described closed circuit between the pump 2 and the hydraulic cylinder 4.
  • the pump 2 is a variable displacement swash plate pump having a swash plate 23, and the rotary machine 3 is a servomotor.
  • the first port 21 and the second port 22 of the pump 2 are switched between the discharge side and the suction side depending on the rotation direction of the rotary machine 3.
  • the speed and position of the hydraulic cylinder 4 are controlled by controlling the rotational speed and the rotational angle of the servomotor.
  • the pump 2 may be an oblique shaft pump.
  • the pump 2 may be a reference line (a line perpendicular to the pump center line in the case of the swash plate pump, a center line of the pump 2 in the case of the oblique axis pump) It may be a dual-tilt pump capable of switching between the discharge side and the suction side of the first port 21 and the second port 22 by tilting in both directions beyond.
  • the rotary machine 3 may be an engine.
  • the drain line 24 extends from the pump 2 to the tank 11. When the pump 2 is driven, a small amount of hydraulic fluid flows from the pump 2 to the tank 11 through the drain line 24.
  • the discharge capacity per one rotation of the pump 2 is adjusted by the flow rate adjusting device 8.
  • the flow rate adjusting device 8 will be described in detail later.
  • the first tank line 6 is branched from the rod side supply line 51, and the second tank line 7 is branched from the head side supply line 52.
  • the first tank line 6 and the second tank line 7 are connected to the tank 11.
  • a first pilot check valve 61 is provided in the first tank line 6.
  • the first pilot check valve 61 allows the flow from the tank 11 to the rod-side supply line 51 but prohibits the reverse flow. Further, the pressure of the head side supply line 52 is led to the first pilot check valve 61 through the pilot line 62, and the pressure of the head side supply line 52 in the first pilot check valve 61 becomes higher than the first set pressure P1. Release the backflow prevention function.
  • a second pilot check valve 71 is provided in the second tank line 7.
  • the second pilot check valve 71 allows the flow from the tank 11 to the head-side supply line 52 but prohibits the reverse flow. Further, the pressure of the rod side supply line 51 is led to the second pilot check valve 71 through the pilot line 72, and the pressure of the rod side supply line 51 in the second pilot check valve 71 becomes higher than the second set pressure P2. Release the backflow prevention function.
  • the second set pressure P2 of the second pilot check valve 71 may be equal to or different from the first set pressure P1 of the first pilot check valve 61.
  • the above-described flow rate adjusting device 8 switches the displacement of the pump 2 between the first set value q1 and the second set value q2 smaller than the first set value q1.
  • the ratio of the first set value q1 to the second set value q2 is equal to the pressure receiving area ratio of the head side chamber 42 and the rod side chamber 41 of the hydraulic cylinder 4.
  • the pressure of the rod side supply line 51 and the pressure of the head side supply line 52 are led to the flow rate adjusting device 8 through the pilot lines 8e and 8f. Then, when the pressure of the head side supply line 52 is higher than the pressure of the rod side supply line 51, the flow rate adjusting device 8 switches the displacement of the pump 2 to the first set value q1, and the pressure of the rod side supply line 51 When the pressure is higher than the pressure of the head side supply line 52, the displacement of the pump 2 is switched to the second set value q2.
  • the flow control device 8 includes an axially slidable servo piston 81 connected to the swash plate 23 of the pump 2.
  • a first pressure receiving chamber 82 to which the small diameter end of the servo piston 81 is exposed and a second pressure receiving chamber 83 to which the large diameter end of the servo piston 81 is exposed are formed.
  • the first pressure receiving chamber 82 is connected to the output port of the high pressure selection valve 84 by the output line 8 c.
  • the two input ports of the high pressure selection valve 84 are connected to the rod side supply line 51 and the head side supply line 52 by input lines 8a and 8b, respectively. That is, the high pressure selection valve 84 selects and outputs the higher one of the pressure of the rod side supply line 51 and the pressure of the head side supply line 52.
  • the second pressure receiving chamber 83 is connected to the switching valve 85 by a relay line 8g.
  • the switching valve 85 is connected to the output port of the high pressure selection valve 84 by the output line 8d, and is connected to the tank 11 by the tank line 8h.
  • the switching valve 85 has a pair of pilot ports, and these pilot ports are connected to the rod side supply line 51 and the head side supply line 52, respectively, by the above-described pilot lines 8e and 8f.
  • the switching valve 85 causes the second pressure receiving chamber 83 to communicate with the tank 11 when the pressure of the head side supply line 52 led through the pilot line 8 f is higher than the pressure of the rod side supply line 51 led through the pilot line 8 e.
  • Position 1 (left position in FIG. 1).
  • the servo piston 81 most moves to the second pressure receiving chamber 83 side, and the tilt angle of the pump 2 becomes maximum, and the displacement of the pump 2 becomes the first set value q1.
  • the switching valve 85 causes the second pressure receiving chamber 83 to be a high pressure selective valve. It is located in a second position (right side position in FIG. 1) in communication with the output port 84. As a result, the servo piston 81 most moves to the first pressure receiving chamber 82 side, and the tilting angle of the pump 2 is minimized, and the displacement of the pump 2 becomes the second set value q2.
  • the spring of the switching valve 85 is disposed on the side of the pilot line 8f in the illustrated example, the spring may be disposed on the side of the pilot line 8e.
  • the second pilot check valve 71 of the second tank line 7 is opened by the pressure of the rod side supply line 51, and the hydraulic fluid at the flow rate difference between the head side chamber 42 of the hydraulic cylinder 4 and the rod side chamber 41 It flows into the tank 11 through the second tank line 7.
  • the rotational speed of the rotary machine 3 is not instantaneously changed even if the direction of the load is reversed during the extension operation and the shortening operation of the hydraulic cylinder 4.
  • a change in speed of the hydraulic cylinder 4 can be suppressed.
  • the pressure of the rod side supply line 51 and the pressure of the head side supply line 52 are led to the flow rate adjusting device 8, and the operation of the flow rate adjusting device 8 is controlled by these pressures. There is no need to control electrically.
  • the ratio of the first set value q1 to the second set value q2 is equal to the pressure receiving area ratio of the head side chamber 42 and the rod side chamber 41 of the hydraulic cylinder 4, the change of the speed of the hydraulic cylinder 4 It can be significantly suppressed.
  • the flow rate adjusting device 8 is not limited to the one having the configuration shown in FIG. 1, and may have the configuration as shown in FIG. 4.
  • the high pressure selection valve 84 (see FIG. 1) is not employed, and the first pressure receiving chamber 82 is connected to the head side supply line 52 by the first pressure introduction line 8j.
  • the switching valve 85 is connected to the rod side supply line 51 by the second pressure introduction line 8k. That is, the switching valve 85 switches whether the second pressure receiving chamber 83 is in communication with the tank 11 or in communication with the rod side supply line 51.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
PCT/JP2018/035102 2017-09-29 2018-09-21 液圧システム Ceased WO2019065510A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US16/652,134 US10907659B2 (en) 2017-09-29 2018-09-21 Hydraulic system
CN201880062585.6A CN111108292B (zh) 2017-09-29 2018-09-21 液压系统
GB2006245.1A GB2581683B (en) 2017-09-29 2018-09-21 Hydraulic system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-190723 2017-09-29
JP2017190723A JP6886381B2 (ja) 2017-09-29 2017-09-29 液圧システム

Publications (1)

Publication Number Publication Date
WO2019065510A1 true WO2019065510A1 (ja) 2019-04-04

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Application Number Title Priority Date Filing Date
PCT/JP2018/035102 Ceased WO2019065510A1 (ja) 2017-09-29 2018-09-21 液圧システム

Country Status (5)

Country Link
US (1) US10907659B2 (enExample)
JP (1) JP6886381B2 (enExample)
CN (1) CN111108292B (enExample)
GB (1) GB2581683B (enExample)
WO (1) WO2019065510A1 (enExample)

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Publication number Priority date Publication date Assignee Title
JP7489766B2 (ja) * 2019-10-31 2024-05-24 川崎重工業株式会社 液圧駆動システム、それを備える電液アクチュエータユニット、及び制御装置
KR102660886B1 (ko) * 2021-07-07 2024-04-26 울산대학교 산학협력단 전기 유압 액추에이터를 이용한 상체 근육 강화 운동 기구
KR102689389B1 (ko) * 2022-09-14 2024-07-30 울산대학교 산학협력단 전기유압을 이용한 근력운동기구용 중량구현장치 및 이를 이용한 근력운동기구

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JP2005036870A (ja) * 2003-07-14 2005-02-10 Nachi Fujikoshi Corp 両回転形液圧ポンプ装置

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