WO2025093473A1 - Dispositif de pompe - Google Patents

Dispositif de pompe Download PDF

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Publication number
WO2025093473A1
WO2025093473A1 PCT/EP2024/080406 EP2024080406W WO2025093473A1 WO 2025093473 A1 WO2025093473 A1 WO 2025093473A1 EP 2024080406 W EP2024080406 W EP 2024080406W WO 2025093473 A1 WO2025093473 A1 WO 2025093473A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
control
pump device
pistons
centering
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.)
Pending
Application number
PCT/EP2024/080406
Other languages
German (de)
English (en)
Inventor
Michael Giera
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.)
Bieri Hydraulik AG
Original Assignee
Bieri Hydraulik AG
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 Bieri Hydraulik AG filed Critical Bieri Hydraulik AG
Publication of WO2025093473A1 publication Critical patent/WO2025093473A1/fr
Anticipated expiration legal-status Critical
Pending legal-status Critical Current

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
    • F04B1/122—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
    • 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
    • F04B1/14—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 stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/145—Housings
    • 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
    • F04B1/14—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 stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • F04B1/148—Bearings therefor
    • 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
    • F04B1/14—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 stationary cylinders
    • F04B1/16—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 stationary cylinders having two or more sets of cylinders or pistons

Definitions

  • the invention relates to a pump device with a plurality of individual pistons which are divided into two groups and which are arranged opposite one another and in rows one behind the other for an opposing piston movement, each of which is guided so as to be longitudinally displaceable in a piston receptacle, and with a drivable control means which, with a control surface in each case, controls the individual pistons of each group in succession from a suction stroke to a pressure stroke and vice versa.
  • DE 10 2013 008 679 A1 discloses an axial piston pump in a swash plate design, particularly for hydraulic systems, comprising a cylinder drum rotatably driven about an axis in a pump housing, in which pistons are arranged in a row one behind the other for axial movement, which pistons are supported at least indirectly with their actuating end accessible outside the cylinder drum on a swash plate, which is pivotable to the desired angle of inclination relative to the axis in order to adjust the stroke of the pistons and thus the fluid system pressure generated by them, wherein the swash plate is mounted on the pump housing for its pivoting movements via a swash plate bearing, and wherein a supply device is provided, by means of which fluid under system pressure reaches at least the swash plate bearing.
  • a pressure device can be provided to hold the swashplate in contact with the swashplate bearing. This ensures proper bearings and correspondingly high operational reliability, even during long-term operation with a large number of adjustment cycles and/or high-frequency pivoting movements of the swashplate.
  • DE 10 2013 008 676 A1 discloses a further axial piston pump, in particular for use in hydraulic systems, having a cylinder drum which can be driven to rotate about an axis in a pump housing and in which piston-cylinder units are arranged offset on a circle, wherein the pistons are supported at least indirectly on a swash plate with their actuating end accessible outside the cylinder drum, and wherein a control device is arranged between the displacement chambers of the piston-cylinder units and a stationary fluid inflow and a stationary fluid outflow of the connection plate, which control device has fluid channels for the targeted transfer of fluid from the fluid inflow into the displacement chambers and from the displacement chambers to the fluid outflow, wherein at least one pressure equalization channel is provided in the control device between the fluid channels for the targeted build-up or release of fluid pressure in the displacement chambers.
  • DE 10 2004 060 954 A1 discloses a generic hydraulic piston machine or pump device which is designed in the manner of a
  • a so-called double swash plate pump is designed with a plurality of pistons arranged one behind the other in a cylinder and displaceably guided, each of which defines a working chamber into which pressure medium can be fed via a suction valve arranged on the piston and from which pressure medium can be discharged via a pressure valve, wherein the piston is penetrated by a pressure-equalizing pressure medium flow path which is delimited at least in sections by a capillary tube inserted into the piston.
  • the invention is based on the object of improving the said state of the art.
  • a pump device having the features of patent claim 1 in its entirety solves this problem.
  • control surfaces of the control means are arranged between the two groups of pistons, the individual pistons or pump pistons act equally on the control means from both sides, so that the mutually acting piston forces cancel each other out. This also relieves the load on the bearing of a drive shaft, which drives the control means in rotation in the manner of a swash plate with the respective control surfaces.
  • the pump device according to the invention with the mentioned force compensation can be used in particular for pumping fluids at very high pressures, usually in the range of several 100 bar.
  • the pump device can be used to To pump a fluid medium into a central tank filled with hydrogen in order to displace the hydrogen so that the displaced hydrogen can be removed from the tank for further use, for example, during a vehicle refueling process.
  • the pumping device can also be used for other technical applications, particularly in the low-pressure range.
  • the two control surfaces of the control means are part of a control disk mounted on a drive shaft and rotatably driven by the drive shaft, and the control surfaces are inclined toward each other relative to the drive shaft.
  • the control disk is mounted on the drive shaft in a rotationally fixed manner by means of a driver and is guided axially displaceably on the drive shaft by means of a centering device using at least one energy storage device, in particular in the form of two compression springs, in a central position between the two groups of pistons.
  • Connections between the drive shaft and the control disk such as a connection by means of a key or a splined shaft, are used as drivers.
  • a self-centering system is created which can compensate for any unevenness in the material pairing between the control disk and the pump piston by means of the centering device, thus ensuring low-friction, long-term operation of the pump device.
  • the central arrangement in the middle and inside the pump device means that the interior of the device housing of the pump device with its movable components is can be better sealed from the environment, for example by using well-sealed housing end covers.
  • the centering device comprises two opposing centering sleeves, preferably of the same design, each of which is supported with one free end on the control disc and with the other free end on the respectively associated compression spring, preferably with the same spring force. This achieves particularly low-vibration operation for the pump device.
  • the respective compression spring of the centering device is supported with its one free end on an inner flange widening on the centering sleeve and with its other free end on a fixed bearing point in the form of a fixing ring and that both the centering sleeves and the compression springs as well as the fixing rings extend coaxially along the longitudinal axis of the device and thereby encompass the drive shaft.
  • all pistons are guided with one piston end in an associated sliding guide, which is supported by means of a pretensioning device with a predeterminable pretension in each position of the control disc on the adjacent control surface.
  • a shoe part of the respective sliding guide consisting of two shoe parts, has an annular, flange-like widening, which in each travel state of a piston, due to the movement of the control disc, is in contact with a control ring, which is supported on a contact cone of the pretensioning device, which in this respect is supported by an energy storage in the form of a further compression spring is preloaded, which is supported stationary with one free end on parts of the device housing and with its other free end is in movable contact with the contact cone.
  • the respective preloading device with its compression spring ensures that one shoe part with its flange-like widening can be tilted or pivoted around a rod end of a piston in such a way that the free end face of the other shoe part of the sliding guide or sliding shoe, which is thus carried along in the movement, remains in contact with the associated, adjacent control surface of the control disc.
  • the control disc can directly transmit the resulting force to the respective piston for a pump delivery movement without hindrance during its rotating movement.
  • the pistons of each group are of identical construction and accommodated in pairs opposite each other in their respective piston chambers on the control disc. Accordingly, the pistons of each group act in pairs in a common actuation plane on the control surfaces of the control disc, which are provided with the same inclination in this pump operating range, thus achieving complete, mutual force balance, which benefits smooth and wear-free operation.
  • control surfaces with the same inclination, define a control cone in a fictitious extension, whose cone angle is less than 30°, preferably less than or equal to 20°.
  • the displacement volume per stroke for the pump device can be specified accordingly and kept constant during operation.
  • the pump performance is determined by the volume flow and pressure.
  • the pretensioning device at least partially encompasses the centering device, which are arranged coaxially with each other. This also benefits compactness, and the pump device as a whole is extremely compact while maintaining high performance.
  • the respective contact cone has a conical or spherical control surface on its outer circumference for engagement with the control ring and a hollow cylindrical central recess with which it is guided along the centering sleeve for movement thereon. This achieves gentle control or centering for the respective sliding guide.
  • the valve device advantageously has two check valves assigned to each fluid chamber, which separate the suction side from the pressure side in each travel position of a piston during piston operation.
  • the control disc is rotatably guided in a control chamber within a pump housing, which is provided with connection points in the pump housing, allowing the drainage of leakage oil resulting from pump operation with the pistons.
  • the suction side and the pressure side each open into an annular chamber in the pump housing, to which the fluid chambers of all pistons are connected.
  • the two annular chambers are therefore designed to have the same volume to ensure a constant pressure distribution, which helps simplify manufacturing.
  • FIG 2 shows an enlarged view of a single pump piston with sliding thrust guide, as used in the pump device according to Figure 1.
  • the pump device shown in Figure 1 has a plurality of individual pistons 10 of the same design, which are arranged concentrically around a longitudinal axis 12 of the pump device in a multiple arrangement.
  • the pistons 10 can be divided into two groups 14, 16, with each group 14 or 16 in the multiple arrangement preferably at least five individual pistons 10 or preferably more are associated with each group. However, for the solution according to the invention, just one piston 10 per group 14 or 16 is sufficient.
  • the number of pistons 10 used ultimately depends on the desired pumping performance with the device.
  • the individual pistons 10 are arranged in pairs opposite one another on a common axis 18 that runs parallel to the longitudinal axis 12.
  • pistons 10 of each group 14, 16 are arranged in rows one behind the other transversely to the longitudinal axis 12, with one row, for example, comprising the five aforementioned pistons 10 of a group 14 or 16.
  • the pistons 10 are each precisely guided in a piston receptacle 20 in the device housing 22, and the direction of travel of each piston 10 in the piston receptacle 20 is parallel to the aforementioned longitudinal axis 12.
  • Figure 1 shows a drivable, rotating control means 24 which, with a control surface 26, controls the individual pistons 10 of each group 14, 16 in succession from a suction stroke to a pressure stroke and vice versa.
  • the two control surfaces 26 of the control means 24 are arranged between the two groups 14, 16 of pistons 10.
  • the piston pair 10 arranged at the bottom in a plane is, due to the position of the control means 24, in the maximum deflected front position for a suction stroke, and the piston pair 10 shown at the top is, due to the control means 24, in its rearmost retracted position, in which a pressure stroke has already been completed.
  • the pistons 10 located in a row between each other assume an intermediate piston position (not shown) for each row of a group 14, 16.
  • the two opposing control surfaces 26 of the control means 24 are part of a control disc 28 which is mounted on a drive shaft 30 and can be driven in rotation by means of the latter, the control surfaces 26 being arranged opposite the drive shaft 30, which extends coaxially to the longitudinal axis 12, are inclined towards one another.
  • the drive shaft 30 is led out of the device housing 22 on its right-hand side, as viewed in the direction of Figure 1, and is provided with a tongue and groove connection 32 for the engagement of a drive device, such as a pump motor.
  • Each piston 10 of each group 14, 16 is accommodated in pairs opposite one another in relation to the control disk 28, each in an identically designed piston chamber 34, so that all piston chambers 34 have the same volume.
  • the control disk 28 is designed as a wedge in the longitudinal sectional view according to Figure 1, wherein the control surfaces 26, with the same inclination relative to the longitudinal axis 12, delimit a control cone in a fictitious extension, the cone angle of which is less than 30°, preferably less than or equal to 20°. It is understood that, viewed in the direction of Figure 1, when the control disk 28 rotates around the longitudinal axis 12 by 180° by means of the drive shaft 30, the narrowest point of the control disk 28 with the fictitious control cone is then at the top and the widest point is at the bottom. Because the control disk 28 is driven in rotation by the drive shaft 30, all pistons 10 of each group 14, 16 are switched one after the other from a maximum suction stroke to a maximum pressure stroke and from there back again to a maximum suction stroke.
  • Both the centering sleeves 40 and the compression springs 42 as well as the locking rings 44 extend coaxially along the longitudinal axis 12 and thereby encompass the drive shaft 30.
  • the respective compression spring 42 is mounted in a ring shape on the outer circumference of the drive shaft 30 and is outwardly encompassed by the respective centering sleeve 40, which engages in a guide drive 46 in the control disk 28 adjacent to the other centering sleeve 40 on its free end face.
  • the two compression springs 42 are mounted directly on the drive shaft 30 and encompass it.
  • the respective locking ring 44 represents a sliding and rolling bearing and therefore consists of two parts.
  • That part of the respective locking ring 44 which is installed in the direction of the device housing and to which the position line 44 leads is stationary and is firmly installed with the housing, whereas the second part, which is installed in the direction of the assignable centering sleeve 40, rotates with the drive shaft 30 and thus together with the adjacent associated spring 42 including the centering sleeve 40.
  • the drive shaft 30 is mounted within the device housing 22 by means of several plain bearings 48 and, within the scope of the passage to the outside, is guided in a receiving bushing 52 in a sealed manner within a housing plate 50 on the free end face of the device housing 22.
  • All pistons 10 are guided with a free, front piston end in an associated sliding guide, which is also technically referred to as a sliding shoe 54.
  • the respective sliding guide is supported by means of a pretensioning device 56 with a predeterminable preload in every position of the control disk 28 on the associated adjacent control surface 26.
  • the details of such a piston-sliding shoe pairing 10, 54 for the axial piston machine shown in Figure 1, in particular in the form of a Swashplate machine, is shown in more detail in Figure 2.
  • the mentioned pairing 10, 54 each has the piston 10, which has a spherical joint head 60 at the end of a piston shaft 58, which is at least partially received by a ball socket 62 of the sliding block 54.
  • the mentioned joint head 60 has a diameter along its largest outer circumference that is larger than the diameter of the piston shaft 58 along its largest outer circumference, wherein the respective diameter is determined transversely to the displacement movement of the piston 10.
  • constriction 64 which is reduced in diameter compared to the adjacent joint head 60 and the piston shaft 58, the constriction 64 resulting in particular from the manufacture of the piston 10.
  • the constriction 64 also has the task of limiting the free pivoting movement of the sliding block 54 on the joint head 60 in the manner of a stop.
  • the piston 10 further has a longitudinal channel 66 which extends continuously through the piston 10 with essentially the same inner diameter, the longitudinal channel 66 exiting into the environment at the end of the piston 10 via funnel-shaped extensions 68.
  • the sliding block 54 has two shoe parts 70, 72, which, in cooperation with the joint head 60, form the ball socket 62, whereby each shoe part 70, 72 forms a bearing support for parts of the joint head 60 of the piston 10.
  • One shoe part 70 with a diameter reduction 74, surrounds the joint head 60 of the piston 10 in such a way as to be press-fitted, that only rotational movements are possible for the piston 10 and/or the sliding block 54, namely around all axes.
  • the one shoe part 70 with its support forms a kind of linear, circumferential contact point 76 for the outer circumference of the joint head 60.
  • the other shoe part 72 supports the joint head 60 axially with its support as shown in Figure 2 and thus forms a shell-shaped bearing point 78 with it.
  • one shell part 70 has a central recess 80 through which the joint head 60 with its free end face and the other shoe part 72 each at least partially pass, wherein the central recess 80 with an inner cylindrical guide surface 82 forms a longitudinal guide for the cylindrical outer circumference of the other shoe part 72.
  • the piston 10 is guided, viewed in the longitudinal direction, back and forth in an associated piston receptacle 20 in the device housing 22, and its joint head 60 enables pivoting of the sliding shoe 54 with its two shoe parts 70, 72, with one shoe part 70 driving the other shoe part 72 via its internal guide surface 82, and vice versa.
  • the other shoe part 72 has a type of nozzle channel 84 extending through it from its free end face, which opens into a fluid chamber 86 between the shoe part 72 and the piston head 60, with the fluid chamber 86 in turn being fluid-conductingly connected to the longitudinal channel 66 of the piston 10.
  • the fluid to be pumped by the pump device can be conveyed as lubricant via the respective piston chamber 34 and the longitudinal channel 66 with the funnel-shaped extensions 68 into the fluid chamber 86, and from there, a supply to the front, free end face 88 of the shoe part 72 is ensured via the nozzle channel 84.
  • a circular-cylindrical recess 90 is introduced into the free end face 88 of the shoe part 72, which is in direct media-carrying connection with the fluid supply above the nozzle channel 84. In this way, an unobstructed, low-wear operation is achieved by the aforementioned internal lubricant supply with the fluid or medium to be pumped.
  • one shoe part 70 of a shoe part 54 has an annular, flange-like widening 92 which, in every travel state of a piston 10, due to the control disk 28, is in contact with a control ring 94 which is supported on a contact cone 96 of the pretensioning device 56, which is pretensioned in this respect by an energy store in the form of a further compression spring 98 which is supported stationary with one free end on parts of the device housing 22 and is in movable contact with the contact cone 96 with its other free end (control ring 94, contact cone 96 and compression spring 98 are only shown once in Figure 1).
  • the corresponding pretensioning device 56 is constructed identically for both groups 14, 16.
  • the respective pretensioning device 56 ensures that the control ring 94, which is thereby driven, is adjusted via the compression spring 98 acting on the contact cone 96 in such a way that the one shoe part 70 with its widened portion 92 is tilted or pivoted around the joint head 60 in such a way that the free end face 88 of the further shoe part 72, which is thus driven in the movement, remains in contact with the adjacent control surface 26 of the control disk 28.
  • the opposing surfaces of the respective control ring 94 are in contact with the flange-like widened portion 92, and to this extent the control ring 94 encompasses the one shoe part 70 and is guided longitudinally thereon.
  • each piston shaft 58 defines the piston chamber 34 with variable volume.
  • the respective piston chamber 34 is coaxially enclosed by the compression spring 98 via an adjacent underlying contact cone 96 and is connected by a branch channel 100 to a circumferential channel-like annular space 102 in the device housing 22.
  • FIG. 1 shows, in a highly simplified form, two check valves 106, 108, one on the suction side of the pump device and one on the pressure side.
  • control disk 28 rotates radially during fluid delivery, and the pistons 10, held stationary in their piston receptacles 20 in the receiving cylinder, are only moved back and forth in directions parallel to the longitudinal axis 12.
  • the control disk 28 is rotatably guided in a so-called control chamber within the device housing 22, which is provided with opposite connection points 116, 118 in the device housing 22.
  • the purpose of the two bores 116, 118 is to drain leakage oil and to actively flush it through for a cooling effect. Fluid can flow from connection 116 to 118 or vice versa.
  • the pressure in the housing can be either greater or less than the ambient pressure.

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

Abstract

L'invention concerne un dispositif de pompe comprenant : de multiples pistons individuels (10) qui sont subdivisés en deux groupes (14, 16) et qui sont chacun, en étant situés en face les uns des autres et les uns derrière les autres en rangées à des fins de mouvements de piston dans des directions opposées, guidés longitudinalement de manière mobile dans un réceptacle de piston (20) ; et des moyens de commande apte à être entraînés (24) qui chacun, par l'intermédiaire d'une face de commande (26), commande les pistons individuels (10) de chaque groupe (14, 16) dans une séquence d'une course d'aspiration et d'une course de distribution et inversement, les faces de commande (26) des moyens de commande (24) étant situées entre les deux groupes (14, 16) de pistons (10).
PCT/EP2024/080406 2023-10-31 2024-10-28 Dispositif de pompe Pending WO2025093473A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102023004369.9 2023-10-31
DE102023004369.9A DE102023004369A1 (de) 2023-10-31 2023-10-31 Pumpenvorrichtung

Publications (1)

Publication Number Publication Date
WO2025093473A1 true WO2025093473A1 (fr) 2025-05-08

Family

ID=93291875

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2024/080406 Pending WO2025093473A1 (fr) 2023-10-31 2024-10-28 Dispositif de pompe

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DE (1) DE102023004369A1 (fr)
WO (1) WO2025093473A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023004370A1 (de) 2023-10-31 2025-04-30 Bieri Hydraulik Ag Kolben-Gleitschuh-Paarung

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1058195A (fr) * 1952-06-10 1954-03-15 Pompe pour fluide incompressible à commande rotative
US2880042A (en) * 1957-06-20 1959-03-31 New York Air Brake Co Piston
GB1254877A (en) * 1968-10-19 1971-11-24 Pressure Dynamics Ltd Hydraulic piston and cylinder devices
WO1995034756A1 (fr) * 1994-06-15 1995-12-21 Fmc Corporation Pompe volumetrique a cylindres en tandem
DE60205467T2 (de) * 2001-03-12 2006-06-01 Haldex Brake Corp. Axialkolbenverdichter mit taumelscheibenaktuator
DE102004060954A1 (de) 2004-12-17 2006-06-29 Bosch Rexroth Ag Hydraulische Kolbenmaschine
DE102013008679A1 (de) 2013-05-22 2014-11-27 Hydac Drive Center Gmbh Axialkolbenpumpe
DE102013008676A1 (de) 2013-05-22 2014-12-11 Hydac Drive Center Gmbh Axialkolbenpumpe
CN115523115A (zh) * 2022-09-29 2022-12-27 燕山大学 对顶式超高压轴向柱塞泵

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1058195A (fr) * 1952-06-10 1954-03-15 Pompe pour fluide incompressible à commande rotative
US2880042A (en) * 1957-06-20 1959-03-31 New York Air Brake Co Piston
GB1254877A (en) * 1968-10-19 1971-11-24 Pressure Dynamics Ltd Hydraulic piston and cylinder devices
WO1995034756A1 (fr) * 1994-06-15 1995-12-21 Fmc Corporation Pompe volumetrique a cylindres en tandem
DE60205467T2 (de) * 2001-03-12 2006-06-01 Haldex Brake Corp. Axialkolbenverdichter mit taumelscheibenaktuator
DE102004060954A1 (de) 2004-12-17 2006-06-29 Bosch Rexroth Ag Hydraulische Kolbenmaschine
DE102013008679A1 (de) 2013-05-22 2014-11-27 Hydac Drive Center Gmbh Axialkolbenpumpe
DE102013008676A1 (de) 2013-05-22 2014-12-11 Hydac Drive Center Gmbh Axialkolbenpumpe
CN115523115A (zh) * 2022-09-29 2022-12-27 燕山大学 对顶式超高压轴向柱塞泵

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