EP4617490B1 - Kolbenpumpe mit variabler fördermengenregelung - Google Patents

Kolbenpumpe mit variabler fördermengenregelung

Info

Publication number
EP4617490B1
EP4617490B1 EP25161842.7A EP25161842A EP4617490B1 EP 4617490 B1 EP4617490 B1 EP 4617490B1 EP 25161842 A EP25161842 A EP 25161842A EP 4617490 B1 EP4617490 B1 EP 4617490B1
Authority
EP
European Patent Office
Prior art keywords
swash plate
stopper
spring
piston pump
piston
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.)
Active
Application number
EP25161842.7A
Other languages
English (en)
French (fr)
Other versions
EP4617490A1 (de
Inventor
Shinichi Ikeno
Takaya Yokota
Ryo Yamamoto
Shuhei MIYATA
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.)
Nachi Fujikoshi Corp
Original Assignee
Nachi Fujikoshi Corp
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 Nachi Fujikoshi Corp filed Critical Nachi Fujikoshi Corp
Publication of EP4617490A1 publication Critical patent/EP4617490A1/de
Application granted granted Critical
Publication of EP4617490B1 publication Critical patent/EP4617490B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate

Definitions

  • the present invention relates to a constant horsepower control-type variable volume control piston pump.
  • variable horsepower control-type variable volume control piston pumps are widely used to effectively utilize engine output in hydraulic pumps such as for construction equipment.
  • a variable volume piston pump performs constant horsepower control by balancing the moment due to spring load with the moment due to discharge pressure, so that when the discharge pressure increases, the swash plate inclines, and the discharge flow rate decreases.
  • a constant horsepower control piston pump in which the oscillation center of a swash plate and the central axis of oscillation thereof are disposed separated from the central axis of the resultant force that presses the swash plate in the axial direction during the operation of a piston (Patent Literature 1).
  • Patent Literature 1 when one end of the swash plate pushes a spring to reduce the inclination angle of the swash plate, the length of a resultant force lever arm from the piston relative to the oscillation center is reduced.
  • more ideal constant horsepower control properties can be obtained.
  • the control cylinder 31 has a small hollow piston 33 for pushing the swash plate in the direction for pushing a spring 11 of a constant torque control mechanism 10 by abutting to the swash plate 1, a hollow piston 34 fitting to the outer periphery of the small hollow piston 33 by mutually adjusting an opening part, and the hollow control cylinder 31 fitting to the outer periphery of the hollow piston 34, and having an oil passage 32 for introducing differential pressure of a throttle valve 49 to a bottom part of the hollow piston 31.
  • a small spring 35 is arranged between the small hollow piston 33 and the hollow piston 34, and a drain oil passage 36 for always communicating with a pump drain is arranged in a bottom part of the small hollow piston 32 for abutting to the swash plate 1.
  • Patent Document 3 discloses a variable displacement swash plate type piston pump includes first and second housing members fastened to each other by fastening members, a rotary shaft, a swash plate.
  • a section of the inner circumferential surface of the first housing member has a recess.
  • a bulging portion is arranged in a section of the outer circumferential wall of the first housing member.
  • a section of the outer circumferential wall of the second housing member has a closing portion that closes the opening of the recess.
  • the fastening members include first and second fastening members arranged at positions that are on the opposite sides of the recess, inside the width of the swash plate in a direction along the inclination axis of the swash plate, and closer to the rotary shaft than the distal ends of the bulging portion and the closing portion in the bulging direction.
  • Patent document 4 discloses another known variable displacement swash plate type piston pump.
  • FIGS. 5 and 6 illustrate a conventional piston pump 100, where FIG. 5 shows a swash plate 107 at its maximum angle in a state of maximum discharge volume, and FIG. 6 shows an inclination angle of the swash plate 107 reduced due to oscillation of the swash plate 107.
  • Rotation of the shaft 105 causes the cylinder barrel 109 to rotate, so that the piston 113 moves along the swash plate 107. Since the swash plate 107 is inclined when this happens, the pistons 113 reciprocate relative to the cylinders 111 according to the distance between the swash plate 107 and the cylinder barrel 109. This causes the suction and discharge of oil in conjunction with the reciprocating motion of the pistons 113.
  • the swash plate 107 receives a resultant force from all the pistons 113. A moment Mp due to a pressing force from all the pistons 113 is thus applied to the swash plate 107. That is, the swash plate 107 is held at an angle where the moment Ms due to the spring 121 mentioned above and the moment Mp due to the pistons 113 are balanced.
  • FIG. 7A is an enlarged view of the vicinity of a stopper 123 in FIG. 5 .
  • the swash plate 107 oscillates in an anticlockwise direction in FIGS. 5 and 6 due to the pressing force of the spring 121 and is maintained in contact with the stopper 123. That is, the stopper 123 is fixed to a housing and regulates the maximum inclination angle of the swash plate 107.
  • Mp gradually increases from this state and surpasses Ms
  • FIG. 7B illustrates a state immediately after the swash plate 107 has started to oscillate and is separated from the stopper 123.
  • the inner pressure of the plurality of cylinders 111 repeats being a suction pressure and a discharge pressure during a single rotation of the shaft 105, so that the piston resultant force that acts on the swash plate 107 varies and vibrations that cause the swash plate 107 to oscillate are generated.
  • These vibrations can generate so-called knocking sounds caused by the contact and separation between the stopper 123 and the swash plate 107 in the vicinity of a cut point where the swash plate starts to oscillate from its maximum inclination angle. That is, when the difference between Mp and Ms is small, a slight gap may be formed between the swash plate 107 and the stopper 123 (portion X in the figure), so that the states illustrated in FIGS. 7A and 7B are repeated due to the pulsations, thereby generating the so-called knocking sounds.
  • the present invention has been made in view of such problem, and aims to provide a variable volume control piston pump with low noise.
  • variable volume control piston pump as defined by claim 1.
  • the pressing means is a hydraulic piston, and the hydraulic piston is pressed against the swash plate with a constant force.
  • a spring may be disposed at a back portion of the hydraulic piston, and the spring may press the hydraulic piston in a pressing direction of the hydraulic piston.
  • the stopper may be disposed in a position facing the spring across the swash plate.
  • the stopper may be disposed on a side opposite the spring across the support portion.
  • the pressing means capable of pressing the stopper against the swash plate is disposed behind the stopper, and when the angle of the swash plate changes, the stopper follows the swash plate and is maintained pressed against the swash plate with a constant force.
  • the stopper does not separate from the swash plate and the generation of knocking sounds can be suppressed.
  • the stopper can always be pressed against the swash plate with a constant force relative to a stroke length of the hydraulic piston.
  • the stopper can be reliably pressed against the swash plate regardless of the inclination angle of the swash plate.
  • disposing the spring at the back portion of the hydraulic piston and pressing the hydraulic piston with the spring in the pressing direction of the hydraulic piston makes it possible to smoothly push out the hydraulic piston immediately after the start of oscillation of the swash plate. That is, immediately after the swash plate starts to oscillate from the state of maximum discharge volume, the initial movement of the piston may be unstable due to friction between the hydraulic piston and the cylinder, etc. However, such delay in the movement of the hydraulic piston can be suppressed, and the piston can be more reliably pressed against the swash plate.
  • Such pressing means may be disposed in a position facing the spring across the swash plate, or may be disposed on a side opposite the spring across the support portion of the swash plate. In both cases, the stopper can regulate the maximum inclination angle of the swash plate and suppress the generation of knocking sounds during the oscillation of the swash plate.
  • the present invention is capable of providing a variable volume control piston pump with low noise.
  • FIG. 1 illustrates a piston pump 1 in a state of maximum discharge volume
  • FIG. 2 illustrates the piston pump 1 in a state in which a swash plate 7 has oscillated.
  • the piston pump of this embodiment is a constant horsepower variable volume control-type piston pump.
  • the piston pump 1 is composed mainly of a shaft 5, the swash plate 7, a cylinder barrel 9, a valve plate 15, a spring 21, etc.
  • the shaft 5, the swash plate 7, the cylinder barrel 9, the valve plate 15, the spring 21, etc., are accommodated inside a housing 3.
  • the shaft 5 is rotatably attached to the housing 3.
  • the cylinder barrel 9 is connected to the shaft 5. That is, the cylinder barrel 9 is rotatable together with the shaft 5 about the shaft 5 as its axis.
  • a plurality of cylinders 11 are disposed in the cylinder barrel 9 at predetermined intervals in a circumferential direction about the shaft 5.
  • a piston 13 that is capable of reciprocating in an axial direction of the shaft 5 is disposed in each of the cylinders 11.
  • each piston 13 abuts the swash plate 7 via a shoe 17.
  • the shoe 17 is slidable along the surface of the swash plate 7. That is, the end portion of the piston 13 moves in the circumferential direction about the shaft 5 along the surface of the swash plate 7.
  • the swash plate 7 is capable of oscillating about a support portion (an oscillation center 19) with a direction perpendicular to the axial direction of the shaft 5 (direction perpendicular to the paper surface) as the axis of rotation. That is, the angle of the swash plate 7 is variable relative to the shaft 5. It should be noted that unlike the cylinder barrel 9, the swash plate 7 does not rotate about the shaft 5 as its axis of rotation.
  • the swash plate 7 is provided with an arm portion at one end portion (upper side in the figure). At the arm portion, a tip end of the spring 21 is in contact with the swash plate 7 via a spring holder 22, and the swash plate 7 is pressed by the spring 21 so that an inclination angle relative to the shaft 5 increases. That is, the moment Ms (see FIG. 5 ) due to the pressing force from the spring 21 is applied to the swash plate 7 relative to the oscillation center 19.
  • the swash plate 7 inclines in an anticlockwise direction in the figure starting from the oscillation center 19 by the moment Ms due to the force from the spring 21.
  • a stopper 23 is disposed at the rear of a direction of oscillation of the swash plate 7 caused by the spring 21. That is, the stopper 23 is disposed in a position facing the spring 21 across the swash plate 7.
  • the swash plate 7 is at its maximum inclination angle, where further oscillation of the swash plate 7 is regulated by the stopper 23. That is, the maximum inclination angle of the swash plate 7 can be regulated by the stopper 23.
  • the function of the stopper 23 will be described in detail further below.
  • the rotation of the shaft 5 causes the cylinder barrel 9 to rotate together with the shaft 5.
  • the cylinders 11 and the pistons 13 provided in the cylinder barrel 9 thus move about the shaft 5.
  • the end portions of the pistons 13 are movable along the surface of the swash plate 7.
  • a hole is formed in a predetermined position of the valve plate 15.
  • the swash plate 7 receives the resultant force from all the pistons 13. That is, the moment Mp (see FIG. 5 ) due to the pressing force from all the pistons 13 is applied to the swash plate 7.
  • the swash plate 7 inclines in a direction in which the inclination angle increases (anticlockwise direction in the figure)
  • Ms ⁇ Mp the swash plate 7 inclines in a direction in which the inclination angle decreases (clockwise direction in the figure) against the moment Ms by the spring 21.
  • FIG. 3A is an enlarged view of the vicinity of the stopper 23 in FIG. 1 .
  • FIG. 3B is an enlarged view of the vicinity of the stopper 23 in FIG. 2 , and illustrates a state in which the swash plate 7 has oscillated from the state shown in FIG. 3A in the direction in which the inclination angle of the swash plate 7 decreases.
  • the stopper 23 of the piston pump 1 is accommodated in a cylinder portion 29 formed in the housing 3.
  • a hydraulic circuit 27 is connected to the cylinder portion 29 and a constant hydraulic pressure (P in the figure) is applied to the cylinder portion 29. It should be noted that the flow paths and various valves that form the hydraulic circuit 27 may be disposed outside the housing 3 or may be accommodated inside the housing 3.
  • the stopper 23 receives a force in a direction in which the stopper 23 is pushed out from the cylinder portion 29 by the hydraulic pressure.
  • the stopper 23 can thus press the swash plate 7 with a constant force. That is, the stopper 23 is a hydraulic piston and functions as a pressing means for pressing the stopper 23 against the swash plate 7 with a predetermined force.
  • a spring force of the spring 21 is set in advance taking into account a pressing force of the stopper 23.
  • the pressing force of the stopper 23 is sufficiently smaller than the pressing force of the spring 21, and when the moment Ms due to the spring 21 is greater than the moment Mp due to the hydraulic pressure from the pistons 13, the stopper 23 is retracted into the cylinder portion 29 to the limit of retraction by the pressing force of the spring 21 via the swash plate 7, as illustrated in FIG. 1 .
  • the fully retracted state of the stopper 23 in the cylinder portion 29 means that the stopper 23 cannot move backward any further.
  • the stopper 23 thus has the function of regulating the maximum inclination angle of the swash plate 7.
  • a stroke length of the stopper 23 is set to be greater than or equal to a displacement amount in an oscillating range of the swash plate 7 (maximum displacement amount of the spring 21). That is, the stopper 23 has a movable range that can follow the total oscillating range of the swash plate 7 set for the piston pump 1 (i.e., the range from the state illustrated in FIG. 1 to the state in which the spring 21 is most compressed in the range of use).
  • the stopper 23 is maintained pressing the swash plate 7 with a predetermined pressing force. That is, the stopper 23 is always maintained pressed against and in contact with the swash plate 7 with a constant pressing force.
  • the stopper 23 will follow these vibrations and always be maintained in contact with the swash plate 7. Consequently, the generation of the so-called knocking sounds can be suppressed.
  • a pin 31 having a diameter smaller than that of the body of the stopper 23 is provided behind the stopper 23. Additionally, the housing 3 is provided with a hole 33 behind the cylinder portion 29, and the pin 31 is accommodated in the hole 33. Additionally, a disc spring 25 having a diameter greater than that of the hole 33 is disposed at a back portion of the stopper 23 in the cylinder portion 29. The disc spring 25 is capable of pressing the stopper 23 from behind in a direction toward the swash plate 7. A hole is formed in the disc spring 25, and the pin 31 is inserted into the hole in the disc spring 25. Additionally, as described above, in the fully retracted state of the stopper 23 in the cylinder portion 29, the disc spring 25 is compressed.
  • the operation of the stopper 23 may be unstable from the state in which the swash plate 7 is pressed by the spring 21 at its maximum inclination angle to immediately after the start of oscillation of the swash plate 7, as illustrated in FIG. 3A .
  • the disc spring 25 helps the operation of the stopper 23 immediately after the swash plate 7 starts to move.
  • the stopper 23 can thus stably maintain the pressing state of the swash plate 7 from the start of operation.
  • the length of the pin 31 is set to the stroke length of the stopper 23 or more.
  • the pin 31 thus does not fall out of the hole 33 in the movable range of the stopper 23. Consequently, the disc spring 25 does not come off the pin 31, and is always held on the outer circumference of the pin 31 (behind the stopper 23).
  • FIG. 4 illustrates a piston pump 1a according to another embodiment. It should be noted that in the mechanism of the piston pump 1a, same reference signs as those in FIG. 1 , etc., are given to the configurations that exhibit similar functions as those of the piston pump 1, and redundant description will be omitted.
  • the piston pump 1a has a substantially similar structure to the piston pump 1, except for the placement of the stopper 23.
  • the stopper 23 is disposed on a side opposite the spring 21 across the support portion (oscillation center 19) of the swash plate 7. That is, the pressing direction of the spring 21 toward the swash plate 7 is the same as the pressing direction of the stopper 23 toward the swash plate 7 (left direction in the figure).
  • the stopper 23 is also a hydraulic piston, and has a stroke length that is capable of following the oscillating range of the swash plate 7. That is, the stopper 23 follows the oscillation of the swash plate 7 and is always maintained in contact with the swash plate 7. Additionally, since there is a limit of retraction into the cylinder portion 29, the stopper 23 can also exhibit the function as a stopper that regulates further inclination of the swash plate 7.
  • the stopper 23 that regulates the maximum inclination angle of the swash plate 7 is capable of moving by following the oscillation of the swash plate 7. Additionally, since the stroke length of the stopper 23 can cover the oscillating range of the swash plate 7, the tip end of the stopper 23 does not separate from the swash plate 7. Thus, the generation of the so-called knocking sounds caused by the swash plate 7 and the stopper 23 can be suppressed.
  • the stopper 23 even if the stopper 23 is movable and is capable of following the oscillation of the swash plate 7, if the stroke length is not sufficient, the stopper 23 and the swash plate 7 may separate at certain inclination angles of the swash plate 7, thereby causing knocking sounds.
  • the stroke length of the stopper 23 can sufficiently cover the oscillating range of the swash plate 7, so that the generation of knocking sounds can always be suppressed regardless of pressure (regardless of the inclination angle of the swash plate 7).
  • stopper 23 being a hydraulic piston enables the stopper 23 to always be continuously pressed against the swash plate 7 with a constant force.
  • the placement of the stopper 23 is not limited to the embodiments described above. Additionally, the pressing means for pressing the stopper 23 from behind is not limited, and may involve other methods besides hydraulics. Furthermore, the disc spring 25 is not a necessarily essential element to be disposed behind the stopper 23, and other elastic members are also acceptable instead of the disc spring 25.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (5)

  1. Kolbenpumpe (1) mit variabler Fördermengenregelung, umfassend ein Gehäuse (3), in dem untergebracht sind:
    ein Zylindergehäuse (9), das zusammen mit einer Welle (5) um eine Achse der Welle drehbar ist;
    eine Vielzahl von Zylindern (11), die in dem Zylindergehäuse (9) in vorbestimmten Abständen in einer Umfangsrichtung um die Welle (5) angeordnet sind;
    eine Vielzahl von Kolben (13), die in einer axialen Richtung der Welle (5) relativ zu einem jeweiligen Zylinder der Zylinder (11) hin- und herbewegbar sind;
    eine Schwenkplatte (7), die um einen Stützabschnitt herum schwingbar ist, um einen Winkel relativ zu den Kolben (13) variabel zu machen;
    eine Feder (21), die einen Abschnitt der Schwenkplatte (7) drücken kann, um einen Neigungswinkel der Schwenkplatte (7) zu vergrößern; und
    ein Anschlag (23), der so konfiguriert ist, dass er einen maximalen Neigungswinkel der Schwenkplatte (7) reguliert,
    wobei ein Endabschnitt des Kolbens (13) entlang einer Oberfläche der Schwenkplatte (7) beweglich ist,
    wobei der Anschlag (23) ein Druckmittel ist, um mit einer vorbestimmten Kraft gegen die Schwenkplatte (7) zu drücken,
    dadurch gekennzeichnet, dass
    der Anschlag (23) so konfiguriert ist, dass er mit einer konstanten Kraft über einen gesamten Schwingbereich der Schwenkplatte (7) gegen die Schwenkplatte (7) gedrückt gehalten wird, und
    ein Moment zum Ändern eines Neigungswinkels der Schwenkplatte (7) aufgrund einer Druckkraft des Anschlags (23) kleiner ist als ein Moment zum Ändern eines Neigungswinkels der Schwenkplatte (7) aufgrund einer Druckkraft der Feder (21).
  2. Kolbenpumpe (1) mit variabler Fördermengenregelung nach Anspruch 1,
    wobei das Druckmittel ein Hydraulikkolben (23) ist, und
    wobei der Hydraulikkolben (23) mit einer konstanten Kraft gegen die Schwenkplatte (7) gedrückt wird.
  3. Kolbenpumpe (1) mit variabler Fördermengenregelung nach Anspruch 2,
    wobei eine Feder (25) an einem hinteren Abschnitt des Hydraulikkolbens (23) angeordnet ist, und
    wobei die Feder (25) den Hydraulikkolben (23) in einer Druckrichtung des Hydraulikkolbens (23) drückt.
  4. Kolbenpumpe (1) mit variabler Fördermengenregelung nach Anspruch 1, wobei der Anschlag (23) in einer der Feder (21) zugewandten Position auf der anderen Seite der Schwenkplatte (7) angeordnet ist.
  5. Kolbenpumpe (1) mit variabler Fördermengenregelung nach Anspruch 1, wobei der Anschlag (23) auf einer der Feder (21) gegenüberliegenden Seite auf der anderen Seite des Stützabschnitts angeordnet ist.
EP25161842.7A 2024-03-15 2025-03-05 Kolbenpumpe mit variabler fördermengenregelung Active EP4617490B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2024040837A JP7590682B1 (ja) 2024-03-15 2024-03-15 可変容量制御ピストンポンプ

Publications (2)

Publication Number Publication Date
EP4617490A1 EP4617490A1 (de) 2025-09-17
EP4617490B1 true EP4617490B1 (de) 2026-02-11

Family

ID=93588037

Family Applications (1)

Application Number Title Priority Date Filing Date
EP25161842.7A Active EP4617490B1 (de) 2024-03-15 2025-03-05 Kolbenpumpe mit variabler fördermengenregelung

Country Status (2)

Country Link
EP (1) EP4617490B1 (de)
JP (1) JP7590682B1 (de)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH046775U (de) 1990-04-28 1992-01-22
JPH07158558A (ja) * 1993-12-10 1995-06-20 Kayaba Ind Co Ltd ピストンポンプ
JP3681258B2 (ja) * 1997-06-13 2005-08-10 カヤバ工業株式会社 可変容量型斜板ピストンポンプ
JP3816786B2 (ja) 2001-11-15 2006-08-30 株式会社不二越 可変容量形ピストンポンプの容量制御装置
JP6450629B2 (ja) * 2015-04-02 2019-01-09 株式会社日立建機ティエラ 作業機械の油圧駆動装置
JP6206513B2 (ja) * 2016-01-14 2017-10-04 株式会社豊田自動織機 可変容量型斜板式ピストンポンプ
JP2019199847A (ja) * 2018-05-17 2019-11-21 ナブテスコ株式会社 油圧ポンプ

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JP7590682B1 (ja) 2024-11-27
JP2025141083A (ja) 2025-09-29
EP4617490A1 (de) 2025-09-17

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