EP2495441A1 - Hydraulische axialkolbendrehmaschine - Google Patents

Hydraulische axialkolbendrehmaschine Download PDF

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Publication number
EP2495441A1
EP2495441A1 EP10826644A EP10826644A EP2495441A1 EP 2495441 A1 EP2495441 A1 EP 2495441A1 EP 10826644 A EP10826644 A EP 10826644A EP 10826644 A EP10826644 A EP 10826644A EP 2495441 A1 EP2495441 A1 EP 2495441A1
Authority
EP
European Patent Office
Prior art keywords
land portion
static pressure
filler opening
pressure pocket
oil passing
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.)
Withdrawn
Application number
EP10826644A
Other languages
English (en)
French (fr)
Inventor
Makoto Hemmi
Hideki Akita
Motoshi Suzuki
Kenta Suzuki
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.)
Hitachi Construction Machinery Co Ltd
Original Assignee
Hitachi Construction Machinery Co Ltd
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 Hitachi Construction Machinery Co Ltd filed Critical Hitachi Construction Machinery Co Ltd
Publication of EP2495441A1 publication Critical patent/EP2495441A1/de
Withdrawn legal-status Critical Current

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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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0602—Component parts, details
    • F03C1/0605—Adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0602—Component parts, details
    • F03C1/0607—Driven means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0668—Swash or actuated plate
    • 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
    • F04B1/128—Driving means
    • 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
    • F04B1/2078—Swash plates
    • 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
    • F04B1/22—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 having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible

Definitions

  • the present invention relates to an axial piston hydraulic rotating machine used for a hydraulic pump and a hydraulic motor of a construction machine, and more particularly, to a structure of a piston shoe that is attached to a piston end and pressed against a swash plate.
  • a sliding surface between a piston shoe attached to a piston end of an axial piston hydraulic rotating machine and a swash plate serves as a hydrostatic bearing provided with a static pressure pocket at the center and a filler opening communicated therewith.
  • the aforementioned structure allows a fluid pressure of a lubricant supplied from the filler opening to the piston shoe to be balanced with the pressing force applied from the piston so that an oil film with appropriate thickness is formed between the piston shoe and the swash plate.
  • the piston shoe is allowed to be smoothly slidable without being in contact with the swash plate.
  • change in a tilt angle of the swash plate may change both horizontal and vertical components of the pressing force from the piston, which will bring the piston shoe into contact with the swash plate. This is likely to cause abrasion in the piston shoe.
  • the structure which solves the aforementioned problem has been proposed by providing an annular inner peripheral land portion 22 within a region of forming a static pressure pocket of a piston shoe 9, dividing the circular region of forming the static pressure pocket into an internal static pressure pocket 23 inside the inner peripheral land portion 22 and an external static pressure pocket 24 outside the inner peripheral land portion 22, and forming an outer peripheral land portion 25 as an outer periphery of the external static pressure pocket 24 (see Patent Literature 1).
  • the aforementioned structure allows a pressure receiving area of the piston shoe 9 to be larger than the area of the structure without the inner peripheral land portion 22. This makes it possible to improve abrasion proof property of the piston shoe 9.
  • the inner peripheral land portion 22 is annularly formed around a filler opening 9A, and partially provided with an oil passing groove 27 which communicates the internal static pressure pocket 23 with the external static pressure pocket 24 so that both ends at the internal static pressure pocket 23 and the external static pressure pocket 24 are disposed on a straight line which passes through the center of the filler opening 9A.
  • the piston shoe 9 disclosed in Patent Literature 1 is formed such that the oil passing groove 27 is formed so as to have both ends at the internal static pressure pocket 23 and the external static pressure pocket 24 disposed on the straight line A-B that passes through the center of the filler opening 9A. If the piston shoe 9 slides with respect to a swash plate 10 in the state where the oil passing groove 27 is directed in accordance with the sliding direction of the piston shoe 9 with respect to the swash plate, the lubricant flows in an arrowed direction. Referring to Fig. 6 , the lubricant flows into wide static pressure pockets 23, 24 after passing through a very small clearance between the swash plate 10 and the piston shoe 9.
  • Patent Literature 1 causes imbalance between the pressure distributions in the static pressure pockets 23, 24, which makes the oil film between the piston shoe 9 and the swash plate 10 at one side of the piston shoe 9 considerably thin. This may bring the piston shoe 9 into contact with the swash plate 10, thus causing the risk of eccentric wear.
  • the present invention has been made in consideration of the aforementioned circumstances, and an object of the present invention is to provide a hydraulic rotating machine with high reliability which is capable of keeping the pressure distribution within the static pressure pocket equalized as well as preventing the eccentric wear of the piston shoe.
  • the present invention provides an axial piston hydraulic rotating machine which includes a rotary shaft, a rotor attached to the rotary shaft, a piston slidably provided in a cylinder hole formed in the rotor, a piston shoe swingably attached to the piston, and a swash plate with which the piston shoe is slidably in contact.
  • a sliding surface of the piston shoe with respect to the swash plate has an inner peripheral land portion, an external static pressure pocket, and an outer peripheral land portion formed in this sequence concentrically with respect to a filler opening communicated with the cylinder hole via an oil passing hole formed in the piston and an internal static pressure pocket communicated with the filler opening on an outer periphery thereof, and an oil passing groove through which the internal static pressure pocket communicates with the external static pressure pocket is formed in a part of the inner peripheral land portion on a straight line that passes through a center of the filler opening.
  • An inner wall surface and an outer wall surface of the outer peripheral land portion, and an inner wall surface and an outer wall surface of the other land portion except the outer peripheral land portion are disposed on a straight line that connects the center of the filler opening to the center of the oil passing groove.
  • the inner and outer wall surfaces of the outer peripheral land portion, and the inner and outer wall surfaces of the other land portion except the outer peripheral land portion are disposed on a straight line which connects centers of the filler opening and the oil passing groove. Even if the piston shoe slides with respect to the swash plate in the state where the direction of the straight line which connects the centers of the filler opening and the oil passing groove is consistent with the sliding direction of the piston shoe with respect to the swash plate, the pressure distribution is equalized at the inflow and outflow sides of the lubricant that forms the oil film interposed between the piston shoe and the swash plate. This may suppress the eccentric wear in the piston shoe, thus enhancing durability of the axial piston hydraulic rotating machine.
  • a direction of forming the oil passing groove is inclined with respect to the straight line that connects the center of the filler opening to the center of the oil passing groove, and the inner wall surface and outer wall surface of the inner peripheral land portion are disposed on the straight line that connects the center of the filler opening to the center of the oil passing groove.
  • the inner and outer wall surfaces of the inner peripheral land portion are disposed on the straight line which connects the centers of the filler opening and the oil passing groove. This makes it possible to equalize the pressure distribution at the inflow and outflow sides of the lubricant that forms the oil film interposed between the piston shoe and the swash plate when the piston shoe slides with respect to the swash plate.
  • a shielding land portion that is larger than an interval between the oil passing grooves is formed in at least one of the internal static pressure pocket and the external static pressure pocket opposite an open end of the oil passing groove.
  • a shielding land that is larger than an interval between the oil passing grooves is formed opposite an open end of the oil passing groove in at least one of the internal and external static pressure pockets.
  • the inner and outer wall surfaces of the outer peripheral land portion, and the inner and outer wall surfaces of the other land portion except the outer peripheral land portion are disposed on the straight line that connects the centers of the filler opening and the oil passing groove. Even if the piston shoe slides with respect to the swash plate in the state where the sliding direction of the piston shoe with respect to the swash plate is consistent with the direction of the straight line that connects the centers of the filler opening and the oil passing groove, the pressure distribution may be equalized at the inflow and outflow sides of the lubricant that forms the oil film interposed between the piston shoe and the swash plate. This makes it possible to prevent the eccentric wear of the piston shoe as well as enhance durability of the axial piston hydraulic rotating machine.
  • the axial piston hydraulic rotating machine 1 is configured to have a rotary shaft 4 integrally linked with a rotor 5, and rotatably stored in a casing formed of a front casing 2 and a rear casing 3.
  • a plurality of cylinder holes 6 are formed in the rotor 5 in a circumferential direction.
  • a piston 8 is provided in each of the cylinder holes 6.
  • An end portion of the piston 8 is swingably connected to a piston shoe 9 via a spherical bearing.
  • One surface of the piston shoe 9 is slidably in contact with a surface of a swash plate 10 tiltably held at the front casing 2.
  • the swash plate 10 is configured to have the tilt angle changeable by a not shown servo piston.
  • the stroke of the piston 8 is changed by adjusting the tilt angle of the swash plate 10.
  • a valve plate 7 with which the rotor 5 is slidably in contact is fixed to the rear casing 3.
  • the valve plate 7 is provided with a suction port and a discharge port which are not shown.
  • the piston 8 has an oil passing hole 8A communicated with the suction port or the discharge port of the valve plate 7 via the cylinder hole 6, and the piston shoe 9 has a filler opening 9A at the center, which is communicated with the oil passing hole 8A formed in the piston 8.
  • the hydraulic fluid supplied from the suction port is compressed by the piston 8, and discharged from the discharge port so that the axial piston hydraulic rotating machine according to the embodiment functions as a hydraulic pump.
  • the piston 8 is driven under the pressure of the pressurized oil, and the rotary shaft 4 and the rotor 5 are driven and rotated accompanied therewith so that the axial piston hydraulic rotating machine functions as a hydraulic motor.
  • the piston shoe 9 has a circular internal static pressure pocket 23 communicated with the filler opening 9A, an inner peripheral land portion 22 formed on the outer periphery of the internal static pressure pocket 23, an external static pressure pocket 24 formed on the outer periphery of the inner peripheral land portion 22, and an outer peripheral land portion 25 formed on the outer periphery of the external static pressure pocket 24 on the sliding surface in contact with the swash palate 10.
  • the inner peripheral land portion 22 is annularly formed around the filler opening 9A.
  • Two oil passing grooves 27 through which the internal static pressure pocket 23 communicates with the external static pressure pocket 24 are formed in parts of the inner peripheral land portion 22 on straight lines, passing through the center of the filler opening 9A.
  • the oil passing grooves 27 are inclined with respect to the straight line A-B passing through the center of the filler opening 9A.
  • An inner wall surface and an outer wall surface of the inner peripheral land portion 22 are disposed on the straight lines that connect the center of the filler opening 9A to the center of the oil passing groove 27.
  • the axial piston hydraulic rotating machine is configured to form the oil passing groove 27 that is directed to incline with respect to the straight line A-B passing through the center of the filler opening 9A, and to dispose the inner wall surface and outer wall surface of the inner peripheral land portion 22 on the straight line that connects the center of the filler opening 9A to the center of the oil passing groove 27.
  • the structure allows the pressure distribution to be equalized at the inflow side A and the outflow side B of the lubricant that forms the oil film interposed between the piston shoe 9 and the swash plate 10 even if the straight line A-B that passes through the center of the filler opening 9A is consistent with the sliding direction of the piston shoe 9 with respect to the swash plate 10.
  • each pressure of the filler opening 9A communicated with the cylinder hole 6 is opened in the center of the sliding surface of the piston shoe 9, each pressure of the filler opening 9A, the internal static pressure pocket 23, the external static pressure pocket 24 which are communicated with the filler opening 9A, and the oil passing grooves 27 becomes substantially the same as the pressure inside the cylinder hole 6.
  • the pressure at the inner periphery of the outer peripheral land portion 25 becomes the same as that in the cylinder hole 6: however, the pressure is decreased toward the outer peripheral side.
  • the pressure at the outer periphery becomes the same as that of the hydraulic fluid which is accumulated inside the casing 1.
  • the pressure distributions on the section taken along straight line A-B shown in Fig. 1 are indicated by dashed straight lines in Fig.
  • FIG. 2 when there is no relative motion between the piston shoe 9 and the swash plate 10.
  • Solid straight line in Fig. 2 shows the pressure distribution at the same positions when there is the relative motion of the swash plate 10 with respect to the piston shoe 9 in the arrowed direction as shown in Fig. 1 .
  • the pressure drops at an inlet (X) of the external static pressure pocket 24 and an inlet (X") of the internal static pressure pocket 23 at upstream side of the pad center of the hydraulic fluid flow, and the pressure rises at an outlet (Y) of the external static pressure pocket 24 and an outlet (Y") of the internal static pressure pocket 23 at downstream side.
  • the former pressure drop is caused by rapid enlargement of the flow passage, and the latter pressure rise is caused by rapid shrinkage of the flow passage.
  • the flow passage is rapidly enlarged at a time point (X) of the inflow into the external static pressure pocket 24.
  • the shrinkage (X') of the flow passage is caused by the inner peripheral land portion 22 immediately so as to suppress the pressure drop to be kept low.
  • shrinkage occurs in the flow passage to raise the pressure at the outlet (Y) of the external static pressure pocket 24.
  • the pressure rise may be suppressed to be kept low because of enlargement of the flow passage at the inlet (Y') of the external static pressure pocket 24 just before the outlet.
  • the inner peripheral land portion 22 is provided to cover the direction that passes through the center of the filler opening 9A. This makes it possible to provide similar effects regardless of the direction of the relative motion.
  • the pressure distribution on the sliding surface is brought into substantially equalized entirely on the sliding surface. This makes it possible to stabilize the posture of the piston shoe 9, prevent the eccentric wear, and reduce the risk of damage. Then highly reliable hydraulic rotating machine with high efficiency may be realized.
  • Figs. 4(a), 4(b) and 4(c) show another embodiments of the present invention.
  • a shielding land portion 28 that is larger than a groove interval of the oil passing groove 27 is formed in the external static pressure pocket 24 opposite the oil passing groove 27.
  • the shielding land portion 28 that is larger than the groove interval of the oil passing groove 27 is formed in the internal static pressure pocket 23 opposite the oil passing groove 27.
  • the shielding land portions 28 each larger than the groove interval of the oil passing groove 27 are formed both in the external static pressure pocket 24 opposite the oil passing groove 27 and the internal static pressure pocket 23 opposite the oil passing groove 27.
  • the shielding land portion 28 may be formed only in the internal static pressure pocket 23, or may be formed in both the internal static pressure pocket 23 and the external static pressure pocket 24.
  • the axial piston hydraulic rotating machine according to the present invention may allow the construction machine to have a quick response because of small friction inside the hydraulic rotating machine.
  • the change in the rotating speed with respect to time from activation is expressed by a curve 31 as shown in Fig. 7 .
  • the change in the rotating speed resulting from application of the present invention may be expressed by a curve 32.
  • the rotating speed of the axial piston hydraulic rotating machine at a time T 1 elapsing from activation becomes N 1 for the related art, and N 2 for the present invention.
  • the present invention is capable of providing the response quicker than related art.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
EP10826644A 2009-10-27 2010-10-22 Hydraulische axialkolbendrehmaschine Withdrawn EP2495441A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009246508A JP2011094490A (ja) 2009-10-27 2009-10-27 アキシャルピストン型液圧回転機械
PCT/JP2010/068736 WO2011052512A1 (ja) 2009-10-27 2010-10-22 アキシャルピストン型液圧回転機械

Publications (1)

Publication Number Publication Date
EP2495441A1 true EP2495441A1 (de) 2012-09-05

Family

ID=43921934

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10826644A Withdrawn EP2495441A1 (de) 2009-10-27 2010-10-22 Hydraulische axialkolbendrehmaschine

Country Status (6)

Country Link
US (1) US20120213656A1 (de)
EP (1) EP2495441A1 (de)
JP (1) JP2011094490A (de)
KR (1) KR20120106726A (de)
CN (1) CN102713285A (de)
WO (1) WO2011052512A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3109468A1 (de) * 2015-06-26 2016-12-28 Danfoss A/S Hydraulische maschine
US10288051B2 (en) 2015-06-26 2019-05-14 Danfoss A/S Hydraulic machine arrangement
US10352322B2 (en) 2015-06-26 2019-07-16 Danfoss A/S Vane cell machine with centric bore in ring insert in side wall
CN113586382A (zh) * 2021-08-23 2021-11-02 力源液压（苏州）有限公司 一种用于高压柱塞变量泵的配油盘偏磨消除方法

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6246582B2 (ja) * 2013-12-16 2017-12-13 日立建機株式会社 液圧回転機械
JP6275502B2 (ja) * 2014-02-12 2018-02-07 川崎重工業株式会社 液圧回転装置のシューおよび液圧回転装置
DE102020203679A1 (de) 2020-03-23 2021-09-23 Robert Bosch Gesellschaft mit beschränkter Haftung Gleitschuh für einen Kolben einer Axialkolbenmaschine

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB983310A (en) * 1962-01-29 1965-02-17 Hans Thoma Improvements in or relating to swash plate or like pumps or motors
JPS4842103U (de) * 1971-09-20 1973-05-30
JPS5842103U (ja) * 1981-09-17 1983-03-19 中国文化実業株式会社 和装用ｔシヨ−ツ
JPS648366A (en) * 1987-06-29 1989-01-12 Mitsubishi Heavy Ind Ltd Piston pump-motor
JPH01105095A (ja) 1987-10-15 1989-04-21 Mitsubishi Heavy Ind Ltd 漏洩流体感知保温材及びその製造方法
JPH021476U (de) * 1988-06-13 1990-01-08
JP3703610B2 (ja) * 1997-08-06 2005-10-05 カヤバ工業株式会社 アキシャルピストンポンプまたはモータ
JP2000018151A (ja) * 1998-07-02 2000-01-18 Honda Motor Co Ltd アキシャルプランジャ型油圧機器
JP2001263218A (ja) * 2000-03-14 2001-09-26 Hitachi Constr Mach Co Ltd 液圧回転機
JP4427211B2 (ja) * 2001-05-16 2010-03-03 ヤンマー株式会社 バルブプレートの仕組構造

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2011052512A1 *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3109468A1 (de) * 2015-06-26 2016-12-28 Danfoss A/S Hydraulische maschine
US10288051B2 (en) 2015-06-26 2019-05-14 Danfoss A/S Hydraulic machine arrangement
US10352322B2 (en) 2015-06-26 2019-07-16 Danfoss A/S Vane cell machine with centric bore in ring insert in side wall
US10711780B2 (en) 2015-06-26 2020-07-14 Danfoss A/S Hydraulic machine
CN113586382A (zh) * 2021-08-23 2021-11-02 力源液压（苏州）有限公司 一种用于高压柱塞变量泵的配油盘偏磨消除方法
CN113586382B (zh) * 2021-08-23 2022-11-08 苏州力源液压有限公司 一种用于高压柱塞变量泵的配油盘偏磨消除方法

Also Published As

Publication number Publication date
JP2011094490A (ja) 2011-05-12
CN102713285A (zh) 2012-10-03
US20120213656A1 (en) 2012-08-23
WO2011052512A1 (ja) 2011-05-05
KR20120106726A (ko) 2012-09-26

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