EP3737862A1 - Machine hydraulique, unité hydraulique comportant la machine hydraulique et axe hydraulique comportant la machine hydraulique - Google Patents

Machine hydraulique, unité hydraulique comportant la machine hydraulique et axe hydraulique comportant la machine hydraulique

Info

Publication number
EP3737862A1
EP3737862A1 EP19700638.0A EP19700638A EP3737862A1 EP 3737862 A1 EP3737862 A1 EP 3737862A1 EP 19700638 A EP19700638 A EP 19700638A EP 3737862 A1 EP3737862 A1 EP 3737862A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
hydraulic machine
heat exchange
axis
rotation
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.)
Granted
Application number
EP19700638.0A
Other languages
German (de)
English (en)
Other versions
EP3737862B1 (fr
Inventor
Andreas Guender
Jan Lukas Bierod
Johannes Schwacke
Saskia Ryznar
Oleg Stefanjuk
Marco Scholz
Emil Hanauer
Rene HUETTL
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3737862A1 publication Critical patent/EP3737862A1/fr
Application granted granted Critical
Publication of EP3737862B1 publication Critical patent/EP3737862B1/fr
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
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • 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
    • 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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • 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
    • F04B1/2042—Valves

Definitions

  • Hydromachine hydraulic aggregate with hydromachine, and hydraulic axis with hydromachine
  • the invention relates to a hydraulic machine according to the preamble of patent claim 1, a hydraulic unit with the hydraulic machine according to claim 11, as well as a hydraulic axis with the hydraulic machine according to claim 12.
  • the heart of a hydraulic circuit is a hydraulic machine, in particular a hydraulic pump. It converts mechanical into hydraulic, in particular hydrostatic, energy of a pressure medium conveyed by it. In the case of operation as a hydraulic motor, the conversion takes place in the reverse direction. In energy conversion occur losses that lead in the case of the hydraulic circuit in particular to the heating of the pressure medium. In this case, the loss occurring in the hydraulic machine (s) is responsible for the majority of the heating of the pressure medium, a much smaller part is caused by flow losses in lines. The heating of the pressure medium in the hydraulic pump is particularly great.
  • the heat loss incurred in the hydraulic pump due to loss of thermal energy is carried off by the pumped pressure medium into the hydraulic circuit until it is removed by means of an external heat exchanger as heat to a coolant.
  • the thermal energy is distributed to a large volume of oil, whereby a large amount of pressure medium is to circulate to dissipate the heat. Due to the large amount of pressure medium but also a DT to the recooling coolant is relatively small, so that the efficiency of the external heat exchanger is small and its heat exchange surface must be large, which keeps investment and operating costs high.
  • Coolant is, for example, water.
  • Heat exchangers are at risk of water entering the hydraulic oil as the oil and cooling water sides are only separated by a gasket in the case of the shell and tube heat exchanger, and only a thin solder layer in the case of the plate heat exchanger. Both seals can fail due to operational wear and so the
  • discharged pressure medium is recooled in a separate heat exchanger with water. Again, the circulating pressure medium amount is large. In addition, the flushed out amount must be permanently refilled, which brings device complexity with it.
  • the document CN 106 224 228 shows a hydraulic pump whose housing is wrapped by a heat pipe. The final dissipation of the heat takes place by recooling the medium of the heat pipe via a water bath.
  • a disadvantage of this solution for example, that the heat pipe through its external exposure to the
  • Hydraulic pump is exposed to damage due to impact.
  • Cooling jacket construction can take up comparatively much space.
  • the object of the invention is to provide a hydraulic machine with more efficient cooling, a hydraulic unit with the hydraulic machine and a hydraulic axis with the hydraulic machine.
  • the first object is achieved by a hydraulic machine with the features of
  • Patent claim 1 the second by a hydraulic unit with the features of
  • a hydraulic machine has a housing interior and a group of hydrostatic working spaces mounted rotatably about a rotation axis. These are connected in rotation of the group alternately with a high pressure and a low pressure of the hydraulic pump, in particular a corresponding port. During operation of the hydraulic machine, the pressure medium heats up. The work spaces have a leakage volume flow into the interior of the housing. According to the invention for cooling in
  • Housing interior accommodated a heat exchange device. In particular, this comes in contact with the leakage volume or volume flow.
  • the arrangement of the heat exchange device so close to the place of warming of the pressure medium, the DT is particularly high. Also, a turbulent turbulence of existing due to the leakage in the housing interior pressure medium due to the rotating work spaces is high. Already one of the two factors mentioned leads to an improved heat transfer, both together make the heat transfer particularly efficient. Therefore, a small and simply constructed heat exchange surface in the housing interior is sufficient.
  • Housing interior is realized a particularly efficient arrangement of the required cooling component.
  • the hydrostatic working spaces are each bounded by a hydrostatic cylinder-piston unit of the hydraulic machine.
  • the hydraulic machine is an axial piston machine and the cylinders are formed by cylinder bores formed in a rotatable cylinder drum.
  • the pistons are arranged axially displaceable.
  • the axial piston machine is formed in a swash plate design, wherein the piston mounted on a housing fixed or pivotally mounted
  • Page 3 of 15 Sliding disc are slidably supported.
  • a Schrägachsenbauweise is possible, wherein the piston heads are rotatably connected to an employee employed to the axis of rotation drive shaft.
  • the heat exchange device takes at least partially an annular space, which extends radially and axially between a Gescouseinnenwandung and the group.
  • the annulus offers itself particularly because it is present anyway and does not need to be extended or only slightly to arrange the heat exchange device. So the hydraulic machine builds despite the arranged inside the housing
  • the annular space extends in the direction of the axis of rotation and at least partially cylindrical. He may alternatively or additionally have a conical or oval section, for example, to promote a turbulent turbulence of the leakage volume or leakage volume flow and so the
  • the axis of rotation of the heat exchange device is annular, in particular annular, or polygonal, in particular four- or six- or octagonal, embraced.
  • Said forms relate to a projection of a contour, in particular an outer and / or inner contour of the heat exchange device, in a plane whose normal is the axis of rotation.
  • a wall of the heat exchange device is formed by a tube.
  • a wall of the heat exchange device is formed by a tube.
  • Wall thickness and / or material designed at least depending on the intended purpose to be transferred heat and / or the intended temperature of the pressure medium.
  • a fluid is arranged in a single-phase or two-phase, in particular arranged in a flowing manner.
  • the heat exchange device extends at least in sections in an undulating manner around the axis of rotation and in the direction of the axis of rotation. In this case, sections which extend predominantly parallel to or in the direction of the axis of rotation alternate with sections which extend predominantly circumferentially around the axis of rotation.
  • the heat exchange device extends in the direction radially to the axis of rotation with at least two windings or layers.
  • a first winding or layer extends radially inward in a direction of the axis of rotation up to a vertex of the first winding or layer, where it is at least one pipe diameter by an amount
  • Heat exchange device guided radially outward and extends with a second winding or layer from the apex back in the opposite direction.
  • the heat exchange device may extend partially or fully around the axis of rotation, so that a space in the housing interior, in particular in the annulus claimed space of a component of the hydraulic machine is bypassed by the heat exchange device.
  • the housing interior is delimited by a housing which is penetrated on the same side by a drive shaft which is rotatable about the rotation axis and to which the cylinder-piston units are connected in a rotationally fixed manner, and by an inlet and / or a return of the heat exchange device.
  • the housing interior is delimited by a housing which has ports of high pressure and low pressure on the same side and is penetrated by an inlet and / or a return of the heat exchanger device.
  • the inlet and / or the return is sealed on the outside of the housing against this. This makes the sealing point easily accessible, controllable and maintainable.
  • Page 5 of 15 A hydraulic unit has a hydraulic machine formed according to at least one aspect of the foregoing description.
  • the hydraulic machine in particular with its housing, connected at least: a drive machine, in particular an electric machine, via which a torque to the hydraulic machine is transferable, and a pressure medium container, which is connectable to the low pressure and / or high pressure of the hydraulic machine.
  • the pressure medium container can be designed as an open tank (open circuit) or pressure equalization tank (closed circuit).
  • Such an aggregate is provided, for example, for supplying pressure medium to a hydraulic cylinder.
  • a hydraulic axle accordingly has a hydraulic machine, which according to at least one aspect of the preceding description. It is firmly connected to the hydraulic machine, in particular with its housing, at least: a prime mover, in particular electric machine, via which a torque to the hydraulic machine is transferable, one of the hydraulic machine with pressure medium supplyable hydraulic cylinder and a
  • Control block in particular valve control block, for controlling the pressure medium supply.
  • a tank or a pressure medium container which can be connected to the low pressure and / or high pressure of the hydraulic machine can be provided.
  • FIG. 1 shows a hydrostatic axial piston pump in swash plate construction according to a first embodiment, in a longitudinal section,
  • FIG. 2 shows a hydrostatic axial piston pump in swash plate construction according to a second embodiment, in a longitudinal section
  • Figure 3 shows a second embodiment of a heat exchange device of
  • FIG. 4 shows the heat exchanger device according to FIG. 3 in a side view
  • FIG. 5 shows the heat exchanger device according to FIGS. 3 and 4 in a view in the direction of the longitudinal axis
  • Figure 6 shows a third embodiment of a heat exchange device in one
  • FIG. 7 shows a hydrostatic axial piston pump according to a third exemplary embodiment with the heat exchange device according to FIG. 6,
  • FIG. 8 shows a hydrostatic axial piston pump according to a fourth exemplary embodiment in a longitudinal section
  • Figure 9 shows a heat exchange device according to a fifth embodiment in a side view and a plan view
  • FIG. 10 shows a heat exchange device according to a sixth embodiment in a side view and in a plan view.
  • a first exemplary embodiment of a hydrostatic axial piston pump 1 has a housing 2 with an annular housing jacket 4, which is closed on the end, on the one hand, by a drive-through cover 6 and, on the other hand, by a connection cover 8.
  • a drive shaft 14 is rotatably supported via roller bearings 10, 12.
  • a cylinder drum 16 Rotatably connected to the drive shaft 14 is a cylinder drum 16, in which along a concentric with the axis of rotation 18 arranged pitch circle a plurality of cylinder bores is parallel to the axis of rotation 18 is introduced.
  • a hydrostatic working piston 20 is axially displaceably guided and slidably supported by the housing cover 6 on a swash plate 22 fixedly arranged in the housing 2.
  • a control disk 24 which is penetrated by passage openings (not shown), is arranged between the cylinder drum 16 and the connection cover 8.
  • the through-hole pressure kidney are in pressure medium connection with a high pressure port 26 and a low pressure port 28 of the
  • the hydrostatic working chambers Upon rotation of the drive shaft 14, and thus the cylinder drum 16, the hydrostatic working chambers are connected via their to the terminals 26, 28 facing outlets alternately with high and low pressure.
  • a housing interior 30 is formed. Radial between the
  • Page 7 of 15 this and about the axis of rotation 18 extends a helical
  • Heat exchange device 36 for removing thermal energy from the housing 2.
  • the thermal energy is exactly at this point to one in the coil flowing coolant, such as water, transferred.
  • a DT at this point is very high and the heat transfer coefficient a also. This can be transferred to a small heat exchange surface, a large amount of heat.
  • a significantly larger heat exchanger which would have to be made available externally, is eliminated. In this way, both the investment costs and the operating costs savings can be achieved.
  • direct temperature-related wear on the hydrostatic axial piston pump can be minimized since it can always be operated in the optimum temperature range.
  • a secondary hot water supply can be supplied with heat.
  • This can be implemented, for example, by a 3-way circuit in which the cooling water in the
  • Heat exchange device 36 circulates until a sufficient DT is reached.
  • FIG. 2 shows a hydrostatic axial piston pump 101 according to a second embodiment
  • Embodiment A difference from the first embodiment according to FIG. 1 is
  • Page 8 of 15 in that the heat exchange device 136 differs from that according to FIG. Although it is also designed as a helix, but are the individual turns of the helix in the axial direction to each other.
  • an inlet 38 and a return 40 of the heat exchanger device 136 are shown in FIG. Both 38, 40 pass through the housing cover 6 and are sealed on the outside (not shown) against the housing 2. Through the inlet 38 flows in the helix of the
  • Heat exchange device 136 cooling water and takes on its way through the coil to the return 40 of the turbulence in the housing interior 134 turbulent
  • the turbulence generated by the cylinder drum 16 in the oil bath of the housing interior 30 proves to be advantageous for the
  • Heat transfer coefficient of the heat exchange device 136 Due to the closer arrangement of the helices of the heat exchange device 136 is a heat flux density, compared with the first embodiment of Figure 1, increased.
  • FIGS. 3 to 5 show the heat exchanger device 136 according to FIG. 2 in a perspective view, a side view and a plan view.
  • the comparatively short inlet 38 extends parallel to the axis of rotation 18 and is at right angles, with respect to the
  • Rotary axis 18 in the circumferential direction angled.
  • the helix extends with mutually adjacent turns in the direction of the axis of rotation 18 and circumferentially around it, until at apex of the heat exchange device 136, the helix tube tangentially expires and again at right angles, parallel to the axis of rotation 18 and is returned as return 40.
  • FIG. 6 shows a third exemplary embodiment of a heat exchange device 236 which is based on the helical heat exchange device 36 according to FIG. In contrast to this, the heat exchange device 236 in the radial direction two layers or
  • Windings rather than just one, up.
  • the individual turns in the direction of the axis of rotation 18 at a distance from each other.
  • the turbulent oil bath in the housing interior 30 can also reach the spaces between the turns.
  • internal turns extend circumferentially and in the direction of the axis 18 with a constant coil diameter up to a vertex of the heat exchanger device 36
  • Page 9 of 15 the diameter of the winding is extended to a larger radius and the turns are circumferentially returned in the reverse direction along the axis of rotation 18 around this. This results in two windings or layers.
  • the outer winding runs as return 40 again on the side of the inlet 38, parallel to this, from.
  • FIG. 7 shows a third exemplary embodiment of a hydrostatic axial piston pump 201, which differs from the second exemplary embodiment according to FIG. 2 essentially by the changed heat exchanger device 236 according to FIG.
  • Axial piston pump 301 is shown in FIG. 8. It differs from the exemplary embodiment according to FIG. 7 because of the modified heat exchange device 336. This is now designed to be undulating instead of helical. In this case, a ring of alternately parallel to the axis of rotation 18 extending and circumferentially angled sections are lined up so that the tube of the heat exchange device 336 alternately in
  • Circumferential direction extends about the axis of rotation 18. In this way, a temperature profile of the temperature difference DT deviating from the exemplary embodiments shown so far can be realized.
  • FIG. 9 A quite similarly constructed embodiment of a heat exchange device 436 is shown in FIG. 9. The embodiment differs from FIG. 8
  • Heat exchange device 436 in that comparatively few undulating
  • a last exemplary embodiment of a heat exchange device 536 is shown in FIG. 10. It extends in a helical stepwise manner and also has a rectangular cross section of the helices. These extend in sections horizontally, that is, in a plane whose normal is the axis of rotation 18, and are connected to each other by sections against the planes respectively. In this way, results in a basically stepped and helically wound heat exchange device.
  • a hydraulic machine with a housing interior, in which an engine is arranged, via the mechanical energy in hydraulic energy, and / or vice versa, leakage-related is changed. It is in the housing interior a
  • Page 10 of 15 Heat exchange device arranged to dissipate a heat flow of the leakage at least in sections.

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)

Abstract

L'invention concerne une machine hydraulique (1) comprenant un espace intérieur de boîtier (30) et un groupe (16) d'espaces de travail hydrostatiques, monté à l'intérieur de manière rotative sur un axe de rotation (18), qui peuvent être reliés alternativement à une haute pression et à une basse pression de la machine hydraulique lors de la rotation du groupe et présentent une fuite vers l'espace intérieur de boîtier. Un dispositif d'échange de chaleur (36) est reçu dans l'espace intérieur de boîtier (30). L'invention concerne également une unité hydraulique et un axe hydraulique, chacun comportant une telle machine hydraulique.
EP19700638.0A 2018-01-11 2019-01-07 Machine hydraulique, unité hydraulique comportant la machine hydraulique et axe hydraulique comportant la machine hydraulique Active EP3737862B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018200345.9A DE102018200345A1 (de) 2018-01-11 2018-01-11 Hydromaschine, hydraulisches Aggregat mit der Hydromaschine, und hydraulische Achse mit der Hydromaschine
PCT/EP2019/050202 WO2019137862A1 (fr) 2018-01-11 2019-01-07 Machine hydraulique, unité hydraulique comportant la machine hydraulique et axe hydraulique comportant la machine hydraulique

Publications (2)

Publication Number Publication Date
EP3737862A1 true EP3737862A1 (fr) 2020-11-18
EP3737862B1 EP3737862B1 (fr) 2022-06-22

Family

ID=65031028

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19700638.0A Active EP3737862B1 (fr) 2018-01-11 2019-01-07 Machine hydraulique, unité hydraulique comportant la machine hydraulique et axe hydraulique comportant la machine hydraulique

Country Status (5)

Country Link
US (1) US11619214B2 (fr)
EP (1) EP3737862B1 (fr)
CN (1) CN111566346B (fr)
DE (1) DE102018200345A1 (fr)
WO (1) WO2019137862A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021202489A1 (de) 2021-03-15 2022-09-15 Robert Bosch Gesellschaft mit beschränkter Haftung Kühlmodul für eine Hydromaschine, Hydromaschine damit, und hydraulisches Aggregat

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US1764753A (en) * 1926-09-30 1930-06-17 Fairbanks Morse & Co Fluid-compressing means
DE2703686A1 (de) 1977-01-29 1978-08-10 Bosch Gmbh Robert Verdraengerpumpe
DE9411163U1 (de) 1994-07-09 1995-12-21 O & K Orenstein & Koppel Ag, 13581 Berlin Einrichtung zur Kühlung mindestens einer Fahrpumpe und/oder mindestens eines Fahrmotors eines hydrostatischen Fahrantriebes
JP3626236B2 (ja) 1995-02-22 2005-03-02 株式会社竹内製作所 モータ用油圧回路
TW504546B (en) * 2000-10-17 2002-10-01 Fisher & Amp Paykel Ltd A linear compressor
US7799221B1 (en) * 2008-01-15 2010-09-21 Macharg John P Combined axial piston liquid pump and energy recovery pressure exchanger
CN101684783A (zh) * 2008-09-28 2010-03-31 海特克液压有限公司 柱塞泵
CN102128186A (zh) * 2011-03-24 2011-07-20 莱芜钢铁股份有限公司 水气双冷液压缸
DE102011054623A1 (de) * 2011-10-11 2013-04-11 Linde Material Handling Gmbh Hydrostatische Axialkolbenmaschine mit einer Kühlung
DE102012000986B3 (de) 2012-01-22 2013-05-23 Arburg Gmbh + Co Kg Hydraulikeinrichtung mit einer Temperiereinrichtung
CN103939414A (zh) * 2014-05-08 2014-07-23 无锡市长江液压缸厂 一种快速水冷隔水套油缸
JP2016017430A (ja) 2014-07-07 2016-02-01 Ｋｙｂ株式会社 水圧回転機
CN105201816B (zh) * 2015-09-07 2017-03-22 福州大学 一种斜盘式柱塞泵的缸体自冷却结构
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CN106678117B (zh) * 2016-12-30 2018-10-19 天津市双象工程液压件有限责任公司 一种缓冲液压缸

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021202489A1 (de) 2021-03-15 2022-09-15 Robert Bosch Gesellschaft mit beschränkter Haftung Kühlmodul für eine Hydromaschine, Hydromaschine damit, und hydraulisches Aggregat
EP4060185A1 (fr) 2021-03-15 2022-09-21 Robert Bosch GmbH Module de refroidissement pour une machine hydraulique, machine hydraulique correspondante et groupe hydraulique

Also Published As

Publication number Publication date
WO2019137862A1 (fr) 2019-07-18
US20200340460A1 (en) 2020-10-29
CN111566346B (zh) 2023-05-30
DE102018200345A1 (de) 2019-07-11
US11619214B2 (en) 2023-04-04
EP3737862B1 (fr) 2022-06-22
CN111566346A (zh) 2020-08-21

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