EP3224484B1 - Dispositif de refroidissement pour un ensemble hydraulique et utilisation d'un dispositif de refroidissement - Google Patents

Dispositif de refroidissement pour un ensemble hydraulique et utilisation d'un dispositif de refroidissement Download PDF

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Publication number
EP3224484B1
EP3224484B1 EP15798064.0A EP15798064A EP3224484B1 EP 3224484 B1 EP3224484 B1 EP 3224484B1 EP 15798064 A EP15798064 A EP 15798064A EP 3224484 B1 EP3224484 B1 EP 3224484B1
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EP
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Prior art keywords
container
heat
cooling
heat pipes
cooling apparatus
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EP15798064.0A
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German (de)
English (en)
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EP3224484A1 (fr
Inventor
Andreas Guender
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26—Supply reservoir or sump assemblies
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0423—Cooling

Definitions

  • the invention is based on a cooling device for a hydraulic unit for cooling a container for hydraulic oil of the hydraulic unit.
  • the invention also relates to a use of the cooling device.
  • pressure medium or hydraulic oil is conveyed from a container via a hydraulic pump, such as an external gear pump, which can be driven by a variable-speed motor.
  • the pressure medium can be branched off via a throttle, which can also be used to set a minimum speed of the pump.
  • Pressure medium branched off via the throttle can emit heat to an environment via a radiator that is cooled by air from a fan.
  • a leak from the pump can be fed to the radiator.
  • the disadvantage here is that the throttle leads to hydraulic losses, which in turn lead to waste heat.
  • a size of a volume flow through the radiator is also disadvantageously dependent on a system pressure on the output side of the pump, which is why there is no constant cooling capacity of the pressure medium.
  • the pressure medium can only be cooled by the radiator while the pump is in operation.
  • the JP S61 116112 A a cooling device with a large number of parallel bundled heat pipes.
  • the heat pipes have a heat absorption section in a tank and a cooling section protruding from the tank. Ribs are provided on both sections to improve heat transfer.
  • the US 2011/0303389 A1 discloses a fluid tank with passively acting cooling fins which protrude inside and outside the tank from a side wall, the outer cooling fins being arranged to be cooled by an air flow of a fan of an active acting heat exchanger, wherein a fluid flow from the heat exchanger into the fluid tank leads.
  • the JP S52 119117 U discloses a fluid tank with a cooling device comprising a plurality of heat pipes which extend through a wall or a lid of the tank, with fins being installed on the heat pipes inside and outside the lid.
  • the JP H06 18608 U discloses a cooling device with hollow tubes connecting two container sections, through which heat pipes extend concentrically in order to be flowed around along a longitudinal axis. It further discloses providing a channel in a bottom area of a tank so that a fluid introduced into the tank washes around bottom sections of a plurality of heat pipes one after the other. It also discloses a tank with heat pipes arranged in it and a baffle plate through which the heat pipes reach at a distance, so that a laminar flow is created along the heat pipes.
  • the invention is based on the object of creating a cooling device for a hydraulic unit that can also cool pressure medium outside of operation of the hydraulic unit or while the hydraulic unit is at a standstill, has an improved degree of efficiency compared to the prior art and requires little space.
  • Another object of the invention is to provide an advantageous use of a cooling device according to the invention.
  • a cooling device for a hydraulic unit has a container or tank for a hydraulic oil of the hydraulic unit.
  • the container has an inlet and an outlet, which can be designed as a return line and suction line.
  • the cooling device has at least two heat pipes, preferably three heat pipes, each heat pipe being immersed with a pipe section in the container. It can thus dissipate heat from the hydraulic oil.
  • This solution has the advantage that such a cooling device can also cool hydraulic oil while the hydraulic unit is at a standstill, in that heat is dissipated via the at least one heat pipe.
  • the cooling device has an improved degree of efficiency compared to the prior art and requires less space.
  • the heat pipe is, for example, a heat pipe or a two-phase thermosiphon.
  • the heat pipe has a refrigerant that evaporates at a point to be cooled, whereby heat is dissipated as heat of vaporization.
  • the gaseous coolant can then distribute itself in the heat pipe and precipitate on a cooled section (heat sink) on an inner wall of the pipe. Due to the force of gravity or a capillary effect, the coolant can then flow back to the cooling point.
  • the heat pipes each protrude with a further pipe section from the container in order to dissipate the heat to the outside.
  • the heat pipes are arranged in the flow path of the hydraulic oil between the inlet and the outlet.
  • the inlet, outlet and heat pipes are arranged approximately in a row.
  • the flow path can preferably extend approximately in one direction between the inlet and the outlet, whereby no or no major changes in direction of the flow path are provided and thus a simple geometric design, in particular of the container, is made possible and flow losses are minimized.
  • the heat pipes are arranged in such a way that, viewed in the direction of the flow path, they are not arranged one behind the other in series. Thus, the heat pipes do not shade each other, causing more heat from the hydraulic oil to the heat pipes can be performed.
  • the two or more heat pipes are preferably arranged approximately transversely to the flow path, viewed in the direction of the flow path, or are provided in a common plane which is angled to the direction of the flow path.
  • the heat pipes can preferably extend approximately parallel to one another.
  • the heat pipes protruding from the container can also extend essentially in the same direction, this being about a vertical direction.
  • a cooling structure can be provided on the heat pipes for improved heat supply and / or heat dissipation.
  • the cooling structure is preferably at least thermally connected to the heat pipe. It is conceivable that the cooling structure is also mechanically connected to the heat pipes or is designed in one piece with them. It is conceivable to provide a cooling structure inside the container and a cooling structure outside the container.
  • the cooling structure has, for example, a plurality or multiplicity of lamellae which can be designed as a lamellae pack.
  • the fins extend approximately perpendicular to the at least one heat pipe. These can be arranged approximately parallel to one another. Two or more heat pipes can share a respective cooling structure.
  • a size of the cooling structure in the container corresponds approximately to a flow cross section of the flow path of the container or the cross section of the container in the flow direction.
  • fins of the heat pipe or the heat pipes within the container can penetrate approximately the full cross section of the container. Due to the geometric arrangement of the inlet on one side of the plate pack and the outlet on the other side of the plate pack, a volume flow can be guided through the plate pack. This increases heat transfer from the hydraulic oil to the fins and thus in turn to the heat pipe or pipes.
  • the cooling structure can be provided on the tube section of the heat pipes provided inside the container. Additionally or alternatively, the cooling structure can be provided on the tube section of the heat pipes provided outside the container.
  • the cooling structure can be designed in such a way that it promotes a degassing process for the hydraulic oil.
  • the heat pipes and / or the cooling structure can be cooled outside the container by forced convection, in particular by a fan.
  • the heat pipes and / or the cooling structure outside the container can be cooled by a heat exchanger.
  • a material flow (cooling water) can then flow through the heat exchanger, for example.
  • the heat exchanger can thus have a cooling water circuit.
  • the heat exchanger can also be thermally and / or mechanically (in particular directly) connected to a housing, in particular a machine housing, in particular the hydraulic unit, in order to give off heat to the housing.
  • a flow cross section of the flow path is advantageously reduced like a throttle in the area of the heat pipes and / or in the area of the cooling structure. This is advantageous if the heat pipes and / or the cooling structure (lamellar pack) do not completely penetrate the cross section of the container, so that the hydraulic oil can then be forced to the heat pipes and / or to the cooling structure.
  • the throttle-like reduction in size can increase a flow rate of the hydraulic oil, which enables an improved flow around the heat pipes and / or the cooling structure.
  • At least the heat pipes and / or the cooling structure can be arranged approximately in the region of the narrowest cross section of the container.
  • the flow cross-section is reduced, for example, by a flow guide.
  • a flow guide This is preferably a ramp or a partition that reduces the flow cross-section. If a ramp is provided, it can be angled starting from a container bottom, in particular extending away in the direction of flow.
  • the reduction in the flow cross section is preferably carried out continuously, as a result of which the flow properties of the hydraulic oil are improved.
  • the hydraulic oil can be conveyed from the outlet via a hydraulic machine which can be driven by a drive unit.
  • the drive unit can have its own cooling device, which is also simple in terms of device technology is used to cool the heat pipes and / or the cooling structure.
  • the cooling device of the drive unit is preferably a fan, the air flow of which is used for cooling.
  • the drive unit and the hydraulic machine can then advantageously form a motor-pump unit or a motor-pump group.
  • An arrangement with the cooling device according to the invention and the motor-pump unit can then preferably be provided.
  • the motor-pump unit is preferably arranged directly or adjacent to the at least one outer heat pipe and / or its outer cooling structure.
  • a further heat pipe can advantageously be provided for a further component of the hydraulic unit.
  • the further heat pipe can then be arranged with at least one pipe section adjacent to the pipe section of the at least one heat pipe of the container.
  • the heat pipes can then bundle both the heat of the container and the heat of a further component or further components, such as the drive unit or other “hotspots”.
  • a temperature of the entire hydraulic unit can be kept constant and / or heat can be dissipated together. With this concept, the thermal energy can be bundled and used alternatively for further processes.
  • the heat pipes of the container and at least one further component are preferably cooled together.
  • the waste heat of at least one heat pipe of the container and / or the component can be provided for at least one further process.
  • the heat pipes for the container together with the cooling structure are preferably designed in such a way that an approximately constant temperature is provided on both heat absorption surfaces and heat emission surfaces.
  • a temperature difference to the hydraulic oil or to the environment can be approximately the same over an entire area be great.
  • the heat dissipation capacity is comparatively high for the same area, and the cooling device can be designed more compact.
  • the cooling device it is provided that it is used for a hydraulic unit which has a comparatively low cooling requirement and can be a so-called "small unit".
  • the hydraulic unit or the container of the hydraulic unit preferably has a cooling capacity of max. 1000 watts, preferably of max. 300 to 500 watts.
  • the cooling device for small units, it is therefore advantageously possible to use products from the computer industry, since modern graphics cards, for example, have a similar cooling capacity. For example, heat pipes from the computer industry are technically well developed and usually inexpensive.
  • the cooling device 1 has a container 2 for hydraulic oil. Hydraulic oil 6 is fed to the container 2 from a hydraulic unit via an inlet 4 in the form of an inlet line. Hydraulic oil 10 is then led out of the container 2 via a drain 8 in the form of a drain line.
  • the Inlet 4 and outlet 8 are arranged approximately parallel to one another.
  • the container 2 has an approximately cuboid design. Between the inlet 4 and the outlet 8, three heat pipes 12, 14 and 16 are provided. These are approximately rod-shaped and immersed into the container 2 with a pipe section 18 and protrude from the container 2 with a further pipe section 20.
  • the heat pipes 12 to 16 extend approximately in a vertical direction and are arranged parallel to one another.
  • the heat pipes 12 to 16 here extend approximately in a common plane.
  • a cooling structure in the form of a laminated core 22 is arranged on the inner pipe sections 18 of the heat pipes 12 to 16. This is arranged together with the heat pipes 12 to 16 in the plane.
  • the plate pack 22 has a plurality of plates extending approximately parallel to one another. The slats extend approximately in the horizontal direction.
  • a flow path 24 within the container 2 leads from the inlet 4 to the outlet 8 approximately in a single direction.
  • the disk pack 22 is then arranged within the flow path 24.
  • the plane in which the lamella pack 22 and the heat pipes 12 to 16 are arranged extends approximately transversely to the flow path 24.
  • the lamella pack 22 extends approximately over an entire cross section of the container 2, which means that it extends approximately from the entire from the inlet 4 to the outlet 8 flowing hydraulic oil flows through or around it.
  • a heat 26 can thus be supplied to the heat pipes 12 to 16 directly or via the lamella pack 22 from the pressure medium in the container 2.
  • a cooling structure in the form of a lamella pack 28 is also assigned to the pipe sections 20 outside the container 2. This is according to Figure 1 designed in accordance with the disk pack 22. Heat 30 can then be given off from the pipe sections 20 of the heat pipes 12 to 16 directly via the lamella pack 28 to an environment. In addition, a fan 32 is provided, which increases the flow of air through the lamella set 28.
  • the container 2 is thus shown, the cross section of which is penetrated by the lamella pack 22.
  • the plate pack 22 is thermally connected to several heat pipes 12 to 16.
  • the outlet 8 is here on one side of the lamella set 22 and the inlet 4 on the other side. This means that during the During operation, the resulting volume flow of hydraulic oil in container 2 increases the heat transfer from the hydraulic oil to the inner disk pack 22.
  • the heat pipes 12 to 16 then transport the thermal energy to the outer lamella pack 28, the heat transfer to the ambient air being increased here by means of the fan 32.
  • a cooling device 34 is shown.
  • this has no fan 32 and no outer disk pack 28.
  • a heat exchanger 36 is provided. This is arranged at the end of the heat pipes 12 to 16.
  • the thermal energy can be given off, for example, via a cooling water circuit or to a thermally inert mass of a machine housing.
  • the thermal energy of the hydraulic unit is bundled in one area and can be made available for further processes if necessary, especially when using several hydraulic units.
  • FIG. 3 has a cooling device 38 compared to the embodiment in FIG Figure 1 a reduced inner lamella pack 40. Furthermore, the heat pipes 12 to 16 in the container 2 are shortened. The lamellar pack 40 with the heat pipes 12 to 16 therefore has a smaller cross section within the container 2 and thus does not penetrate the entire cross section of the container 2.
  • a flow guide 42 is provided here to increase the heat transfer. This prevents the hydraulic oil from flowing past the plate pack 40 or the heat pipes 12 to 16. Furthermore, the heat transfer is increased by a higher flow rate of the hydraulic oil.
  • the flow guide 42 is designed as a ramp which extends from the container bottom 44 to the lamella pack 40 or the heat pipes 12 to 16. The lamella pack 40 with the heat pipes 12 to 16 is then arranged in the narrowest cross section of the container 2.
  • FIG 4 has the cooling device 46 in contrast to Figure 1 no fan 32. Instead, a motor fan 48 of a motor 50 is used.
  • the motor fan 48 thus serves to cool the motor 50 and to cool the outer lamella set 28 with the heat pipes 12 to 16.
  • a pump 52 is driven by the motor 50. This conveys hydraulic oil via the outlet 8 from the container 2 Figure 4
  • the motor 50 with the pump 52 which form a motor-pump unit, is arranged or mounted directly next to the outer disk pack 28, and one of the motor fan 48 The volume flow generated can then increase the heat transfer to the plate pack 28 or to the heat pipes 12 to 16.
  • a cooling device 54 in Figure 5 has in addition to the heat exchanger 36, see Figure 2 , further heat pipes 56 and 58.
  • the heat pipe 56 is used to cool the motor 50 and the heat pipe 58 is used to cool the pump 52.
  • further heat pipes can be provided for further sections or components of a hydraulic unit to be cooled.
  • the heat pipes 56, 58 and 12 to 16 are bundled together in the heat exchanger 36 and can be cooled in a targeted manner by a cooling water circuit or can give off heat to the thermally inert mass of the machine housing. The thermal energy is thus bundled and can be used for further processes if required.
  • the heat pipes 12 to 16 and / or 56, 58 and / or the cooling structure can be components from the computer industry.
  • the heat pipes 12 to 16 with their cooling structure are designed for cooling capacities between 300 and 500 watts, for example.
  • a temperature distribution of a lamellar core 60 with heat pipes is shown as an example. It can be seen that a temperature of the lamella set 60 lies in approximately the same temperature range. Heat can thus be given off and / or absorbed over the entire plate pack 60 with approximately the same temperature gradient.
  • a cooling device for a hydraulic unit which has a container for hydraulic oil. Two heat pipes are provided for cooling the container. Hydraulic oil in the container flows approximately in a straight line from an inlet to an outlet. The at least two heat pipes are then arranged between the inlet and the outlet.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Claims (14)

  1. Dispositif de refroidissement pour un ensemble hydraulique, le dispositif de refroidissement comportant un conteneur (2) d'huile hydraulique comprenant une amenée (4) et une évacuation (8), au moins deux tubes de conduction de chaleur (12, 14, 16) étant disposés dans le chemin d'écoulement (24) de l'huile hydraulique entre l'amenée (4) et l'évacuation (8), chaque tube de conduction de chaleur (12, 14, 16) comportant un moyen de refroidissement et chaque tube de conduction de chaleur (12, 14, 16) étant plongé dans le conteneur (2) avec une section de tube (20), pour évacuer la chaleur hors de l'huile hydraulique sous la forme de chaleur d'évaporation, en ce que le moyen de refroidissement s'évapore au niveau d'un point à refroidir, les tubes de conduction de chaleur (12, 14, 16) n'étant pas disposés en ligne dans la direction du chemin d'écoulement (24).
  2. Dispositif de refroidissement selon la revendication 1, le chemin d'écoulement (24) s'étendant approximativement dans une direction entre l'amenée (4) et l'évacuation (8).
  3. Dispositif de refroidissement selon l'une quelconque des revendications précédentes, au moins une structure de refroidissement (22, 28) étant prévue au niveau des au moins deux tubes de conduction de chaleur (12, 14, 16).
  4. Dispositif de refroidissement selon la revendication 3, les au moins deux tubes de conduction de chaleur (12, 14, 16) divisant la structure de refroidissement (22, 28) respective.
  5. Dispositif de refroidissement selon l'une quelconque des revendications 3 à 4, l'au moins une structure de refroidissement (22, 28) comportant une pluralité de lamelles réalisées sous la forme de paquets de lamelles (22, 28) et disposés approximativement à distance parallèle les uns par rapport aux autres.
  6. Dispositif de refroidissement selon l'une quelconque des revendications 3 à 5, un ordre de grandeur de l'au moins une structure de refroidissement (22) dans le conteneur (2) correspondant approximativement à une section transversale d'écoulement du conteneur (2).
  7. Dispositif de refroidissement selon l'une quelconque des revendications 3 à 6, l'au moins une structure de refroidissement (22) étant prévue au niveau des sections de tube (18) prévues à l'intérieur du conteneur (2) des au moins deux tubes de conduction de chaleur (12, 14, 16) et/ou l'au moins une structure de refroidissement (28) étant prévue au niveau des sections de tube (20) prévues à l'extérieur du conteneur (2) des au moins deux tubes de conduction de chaleur (12, 14, 16) .
  8. Dispositif de refroidissement selon l'une quelconque des revendications précédentes, les au moins deux tubes de conduction de chaleur (12, 14, 16) étant refroidis à l'extérieur du conteneur (2) par convexion forcée.
  9. Dispositif de refroidissement selon l'une quelconque des revendications précédentes, les au moins deux tubes de conduction de chaleur (12, 14, 16) étant refroidis à l'extérieur du conteneur (2) par le biais d'un échangeur thermique (36).
  10. Dispositif de refroidissement selon l'une quelconque des revendications précédentes, une section transversale d'écoulement du conteneur (2) étant réduite en forme d'étranglement dans la zone des au moins deux tubes de conduction de chaleur (12, 14, 16).
  11. Dispositif de refroidissement selon l'une quelconque des revendications précédentes avec une machine hydraulique et une unité d'entraînement comportant un dispositif de refroidissement de l'huile hydraulique pouvant être transportée depuis l'évacuation (8), via la machine hydraulique (52) entraînée par l'unité d'entraînement (50), le dispositif de refroidissement de l'unité d'entraînement (50) servant en outre pour le refroidissement des au moins deux tubes de conduction de chaleur (12, 14, 16).
  12. Dispositif de refroidissement selon l'une quelconque des revendications précédentes, le dispositif de refroidissement comportant au moins un tube de conduction de chaleur (56, 58) supplémentaire pour un composant (50, 52) supplémentaire de l'ensemble hydraulique, l'au moins un tube de conduction de chaleur (56, 58) supplémentaire étant disposé, avec une section de tube, à proximité de la section de tube extérieure (20) des au moins deux tubes de conduction de chaleur (12, 14, 16) du conteneur (2).
  13. Dispositif de refroidissement selon l'une quelconque des revendications précédentes, la chaleur d'échappement d'au moins un tube de conduction de chaleur (12, 14, 16, 56, 58) étant prévue pour au moins un processus supplémentaire.
  14. Utilisation du dispositif de refroidissement selon l'une quelconque des revendications précédentes pour un ensemble hydraulique qui est configuré de telle sorte qu'au moins le conteneur présente une puissance de refroidissement d'environ 1000 Watt maximum, de préférence de 300 à 500 Watt maximum.
EP15798064.0A 2014-11-25 2015-11-20 Dispositif de refroidissement pour un ensemble hydraulique et utilisation d'un dispositif de refroidissement Active EP3224484B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014223947.8A DE102014223947A1 (de) 2014-11-25 2014-11-25 Kühlvorrichtung für ein Hydraulikaggregat und Verwendung einer Kühlvorrichtung
PCT/EP2015/077176 WO2016083249A1 (fr) 2014-11-25 2015-11-20 Dispositif de refroidissement pour groupe hydraulique et utilisation d'un dispositif de refroidissement

Publications (2)

Publication Number Publication Date
EP3224484A1 EP3224484A1 (fr) 2017-10-04
EP3224484B1 true EP3224484B1 (fr) 2020-09-02

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EP (1) EP3224484B1 (fr)
JP (1) JP6570635B2 (fr)
CN (1) CN107002712A (fr)
DE (1) DE102014223947A1 (fr)
WO (1) WO2016083249A1 (fr)

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CN110230477A (zh) * 2019-06-25 2019-09-13 临沂矿业集团菏泽煤电有限公司 煤矿液压钻车用除尘装置
CN110529440B (zh) * 2019-09-24 2020-09-15 哈尔滨工业大学 一种回油动力驱动带石墨烯导热风扇的液压油箱
CN110617253B (zh) * 2019-10-10 2024-04-12 中车资阳机车有限公司 一种液力传动机车用集成化冷却装置
CN113294410A (zh) * 2021-05-25 2021-08-24 珠海格力智能装备有限公司 液压站及数控机床
DE102022131113B4 (de) 2022-11-24 2024-07-18 Ammann Schweiz Ag Kühler-Tank-Kombination
CN115807793B (zh) * 2023-02-09 2023-05-05 泰州海陵液压机械股份有限公司 一种可调整恒压的液压机构及工作方法
CN117847026A (zh) * 2024-03-07 2024-04-09 徐州徐工矿业机械有限公司 一种散热液压油箱

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CN107002712A (zh) 2017-08-01
EP3224484A1 (fr) 2017-10-04
WO2016083249A1 (fr) 2016-06-02
DE102014223947A1 (de) 2016-05-25
JP2017538899A (ja) 2017-12-28
JP6570635B2 (ja) 2019-09-04

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