WO2008148472A1 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
WO2008148472A1
WO2008148472A1 PCT/EP2008/004150 EP2008004150W WO2008148472A1 WO 2008148472 A1 WO2008148472 A1 WO 2008148472A1 EP 2008004150 W EP2008004150 W EP 2008004150W WO 2008148472 A1 WO2008148472 A1 WO 2008148472A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
vane pump
control opening
control
pump according
Prior art date
Application number
PCT/EP2008/004150
Other languages
German (de)
English (en)
Inventor
René Constantin SCHEERER
Stefan Merz
Martin Josef Zug
Steffen Reiblein
Gordon Ulrich Mohn
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 WO2008148472A1 publication Critical patent/WO2008148472A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor

Definitions

  • the invention relates to a vane pump with a rotor in which a plurality of vanes is slidably disposed.
  • a vane pump is known, the rotor is rotatably connected to a shaft which is mounted in a housing part.
  • the rotor is surrounded in the radial direction by a lifting ring.
  • Between the cam and the rotor are separated by adjacent wings from each other formed a plurality of chambers.
  • the chambers are alternately connected to one of the terminals when the rotor is rotated by the shaft.
  • In a control plate control openings are arranged.
  • the control plate limits the flow cross section, can flow through the pressure medium into the chamber.
  • a disc is provided, which is arranged between the housing part and the rotor.
  • the rotor has a substantially cylindrical shape, wherein the cylinder jacket surface has a chamfer both to the top surface and to the bottom surface of the rotor.
  • Inlet cross section of the control opening in the control plate is covered by a side surface of the rotor.
  • pressure medium flows against the end face of the rotor, whereby a back pressure in the region of the narrowest cross section the tax opening is increased.
  • the filling behavior deteriorates and the efficiency of the vane pump drops, especially at high speeds.
  • a vane pump is known in each case, are arranged in the two Ansaug Griffinnieren on opposite sides of the rotor. As a result, the flow cross-section for filling in the suction of pressure medium in an enlarged chamber increases.
  • the rotors of the vane pump are each made approximately cylindrical.
  • the vane pump according to the invention has a rotor in which a plurality of vanes is arranged displaceably. At least one first control opening is provided, via which pressure medium is sucked in during a rotation of the rotor. The pressure medium is sucked into a chamber formed between two adjacent vanes.
  • the rotor tapers starting from its largest diameter in the direction of one of the at least one first control opening for sucking pressure medium facing side surface. According to the invention, the radius of the side of the rotor facing the first control opening for the suction of pressure medium and a distance of the first of the control opening to the axis of rotation limiting wall of the axis of rotation of the rotor at the mouth of the control opening the same.
  • Control opening for sucking pressure medium-facing side can maximize the control opening cross-section without affecting the control time.
  • the dimension of the control opening in the radial direction can be increased by the extension of the chamber to the control surface facing the side surface of the rotor.
  • adjusting the diameter of the rotor at least on the at least one control port facing side and the position of the control port for the suction of pressure medium a possible stepless transition when entering pressure medium from the control port into the chamber realized.
  • This step-free design of the transition reduces the flow resistance and the filling process is improved. This overall improves the efficiency of the vane pump, it being possible in particular for the speed of the vane pump to be increased owing to the lower flow velocity at a larger flow cross section.
  • the outlet angle is the angle between a wall of the first control opening in the direction of the axis of rotation and a plane of rotation of the rotor.
  • a surface portion of the outer surface of the rotor which extends from the largest diameter of the rotor toward the control surface facing the side surface of the rotor extends curved.
  • the curvature is in particular oriented so that the center of the curvature lies radially outside the rotor.
  • the curved surface it is preferable for the curved surface to consist of at least two regions, wherein the region further respectively arranged in the direction of the control opening has a larger radius of curvature than the region arranged adjacent thereto in the direction of the largest diameter of the rotor.
  • Rotor is moved with a rotation of the rotor at a greater speed in the circumferential direction than in the region of the smaller diameter on the side surface of the rotor. This results in a larger static pressure in the small diameter portion of the rotor, creating a pressure gradient in the direction of the largest diameter of the rotor. This pressure gradient also provides for an improvement in the filling or to accelerate the filling process. Thus, higher speeds of the vane pump can be realized. Furthermore, it is preferred if the rotor tapers radially starting from its largest diameter toward both side surfaces. By such a bilateral radial taper starting from the region of the largest
  • Diameter is achieved that a bending load due to asymmetry is avoided. By far in the region of the largest diameter in the radial direction guided wings, the bending moments on the wing can still hold comparatively low.
  • At least one further control opening for sucking pressure medium is present.
  • This further control opening is arranged on the side facing away from the control port for the suction of pressure medium side of the rotor and connected to the control port for the suction of pressure medium.
  • This can be achieved via an overall flow cross-section, which is composed of two control openings, a filling of the chambers. This is particularly advantageous together with the bilateral radial taper.
  • the different diameters also lead to the emergence of a filling-promoting pressure gradient in the chamber.
  • the regions of the largest diameter of the rotor is arranged off-center.
  • the off-center arrangement is in particular at the two Be Schollanteile adapted when two control openings are provided. Even with only one control opening, an asymmetrical arrangement of the area with the largest diameter can be used advantageously.
  • the ratio of a first distance of the region of the largest diameter of the rotor from the first control opening facing side surface of the rotor and a second distance of the region of the largest diameter of the second side surface, which faces the further first control opening is preferably the ratio of Be colllanteile dependent on the first control opening and the further first control opening.
  • the ratio of the first distance to the second distance is equal to the ratio of the first Be spallanteils to the second Be spallanteil.
  • FIG. 1 shows an example of a vane pump as
  • FIG. 2 shows a plan view of a housing part of the vane cell pump according to the invention
  • FIG. 3 shows a side view of a unilaterally tapered rotor of the vane pump according to the invention
  • Fig. 4 shows a cross section through a one-sided tapered
  • FIG. 3 shows a schematic representation for explaining the advantages of the vane cell pump according to the invention
  • FIG. 6 shows an illustration of a cover of the vane pump with a further control opening for filling the chambers on both sides;
  • Fig. 7 is an illustration of a rotor of the vane pump according to the invention with double-sided taper.
  • a pump unit 1 is shown, which is arranged in a housing consisting of a cup-shaped first housing part 2 and a second housing part.
  • the second housing part is designed as a connection plate 3 and closes the cup-shaped housing part. 2
  • a main pump 4 is arranged in the cup-shaped housing part 2.
  • the main pump 4 is an axial piston machine in the illustrated embodiment.
  • an auxiliary pump in the form of a
  • Vane pump 5 is formed.
  • the main pump 4 and the vane pump 5 are driven by a common drive shaft 6.
  • the drive shaft 6 penetrates the bottom of the cup-shaped housing part 2.
  • a toothing 7 is formed. The toothing 7 makes it possible to connect the drive shaft 6 with a torque-generating device.
  • the main pump 4 has a cylinder drum 8 in which cylinder bores are arranged in the longitudinal direction.
  • the plurality of cylinder bores is arranged distributed over a circumferential circle in the cylinder drum.
  • a piston is arranged longitudinally displaceable.
  • the pistons 7 protrude at one end out of the cylinder drum 8 and are articulated there, each with a shoe 10 connected.
  • the shoe 10 is supported on a swash plate 11. Depending on the inclination angle between the swash plate 11 and the drive shaft 6 lead in a rotation of the
  • connection plate 3 an inlet channel 12 and an outlet channel 13 are formed. Via the inlet channel 12 4 pressure medium is sucked by the main pump. During one revolution of the cylinder drum 8, the cylinder bores on the side facing the connection plate 3 are in contact with the inlet channel 12. As a result, pressure medium is sucked into the cylinder bore and displaced into the outlet channel 13 during a pressure stroke by the piston 9 arranged in the cylinder bores.
  • the illustrated pump unit 1 is a unit of a charge pump formed by the vane pump 5 and the main pump 4.
  • the vane pump 5 is disposed in a recess 14 in the terminal plate 3 and is also driven by the drive shaft 6.
  • the drive shaft 6 protrudes into the recess 14 with a free shaft end 16.
  • the rotor 15 is disposed on the free shaft end 16 and rotatably connected to the free end of the shaft 16.
  • the recess 14 is introduced from the side facing away from the main pump 4 side in the connection plate 3.
  • the recess 14 receives a rotor 15 of the vane pump 5 and a cam ring 19.
  • the cam ring 19 surrounds the rotor 15 and is arranged eccentrically to this.
  • a pressure chamber between the recess 14 and the cam ring 19 is formed.
  • This pressure chamber is connected to the inlet channel 12 via a control pressure line 20.
  • In the pressure chamber thus acts a hydraulic force that tries to adjust the cam ring 19 in Fig. 1 down as a restoring force.
  • In the opposite direction acts in Fig. 1 not recognizable return device on the cam ring 19th
  • a plurality of grooves 17 formed in the radial direction are arranged as vane slots.
  • a wing 18 is guided in each of these grooves 17, a wing 18 is guided.
  • the wing 18 is slidably disposed in the radial direction in the groove 17 and sealingly cooperates with a raceway of the cam ring 19.
  • connection plate 3 The recess 14 of the connection plate 3 is closed by a lid 21 which is simply formed in FIG.
  • a lid 21 which is simply formed in FIG.
  • an O-ring is arranged in a groove of the lid 21.
  • connection plate 3 shows an end view of the connection plate 3.
  • the recess 14 is arranged, which is longer in one direction than the diameter of the cam ring 19. This allows the cam ring 19 in the recess 14 move and so its eccentricity with regard to the rotor 15.
  • a first control kidney 22 is formed in a base of the recess 14 as a first control port for sucking pressure medium.
  • the control kidney 22 extends along a circular arc section.
  • the first control kidney 22 is connected to an intake passage 23.
  • the intake passage 23 is formed in a connection bend 24 of the connection plate 3.
  • Intake passage 23 connected to a tank volume, not shown.
  • the centers are offset along the adjustment direction to each other.
  • the control kidney then has a straight connecting section which is rounded at the transition to the circular sections.
  • the pressure medium conveyed by the vane pump 5 is displaced from the chambers into a second control opening formed as a second control kidney 25.
  • the second control kidney 25 is also formed at the bottom of the recess 14 and connected to an exhaust passage 26.
  • the first control kidney 22 and the second control kidney 25 are arranged symmetrically with each other at the bottom of the recess 14. It may also be intended a slight twist of the control kidneys 22 and 25.
  • control notches may be formed in a known manner on the control kidneys 22, 25.
  • the center line between the first control kidney 22 and the second control kidney 25 simultaneously indicates the direction in which, in an adjustment of the delivery volume of the vane pump 5 of the cam ring 19 is moved.
  • a return device which is not shown in FIG. 2 and is inserted into a bore 27.
  • the restoring device can in the simplest case consist of a voltage applied to the cam ring 19 coil spring, which is supported at the opposite end to a screwed into the bore 20 plug.
  • FIGS Grooves 17 which in the illustrated embodiment extend in the radial direction for a rotor 15 'The grooves 17 extend from the outer surface 37 to a common circumferential circle, at which the grooves 17 end towards the center of the rotor 15' Ends of the grooves 17, the cross-section of the grooves 17 is slightly increased
  • the catch storage acts as
  • FIG. 4 shows a cross section through the rotor 15 '.
  • the rotor 15 ' has a first side surface 29 and a second side surface 30.
  • the surface normals of the side surfaces 29 and 30 are parallel to the center line 34 of FIG. 4
  • the outer surface 37 of the rotor 15 ' is formed by the region with the largest diameter 31 and a subsequent surface portion 33.
  • the surface portion 33 extends curved up to the smaller diameter 32 at the transition of the surface portion 33 to the first side surface 29.
  • the surface portion 33 is concavely curved, wherein the
  • the radius of curvature in the region adjacent to the region of greatest diameter 31 of the rotor 15 ' is smaller than the radius of curvature of the end formed in the region of the smaller diameter 32 of the surface portion 33.
  • the radius of curvature to the larger radius of curvature on the side of the surface portion 33 oriented toward the first side surface 29 may either be continuous or may be generated by a plurality of successively formed regions.
  • the regions each have a radius of curvature, wherein the radius of curvature of the regions in the direction of the first side surface 29 becomes larger and larger.
  • Vane pump 5 is shown in FIG. 5. It can be seen in particular that the smaller diameter 32 at the transition from the surface portion 33 in the first side surface 29 is the same size as the minimum distance of the first control port 22 toward the
  • Rotation axis 34 towards limiting wall 35 of the rotation axis an orifice angle between the first control kidney 22 to the rotation axis limiting wall 35 and the plane of rotation of the rotor 15 'is a right angle.
  • At the Transition between the first side surface 29 and the surface portion 33 is formed between the surface portion 33 and the plane of rotation of the rotor 19 'also a right angle.
  • the two right angles thus complement each other to 180 °.
  • the peripheral speed of the pressure medium in the chamber is greater than in the region of the minimum distance of the wall 35 from the axis of rotation 34.
  • a difference therefore forms between the static pressure in the region of the surface portion 33 at the transition to the first side surface 29 and in the region of the largest diameter 31 of the rotor 15.
  • This pressure difference leads to an improvement in the filling of the chamber.
  • a particularly good utilization of this pressure difference results from the curved design of the surface portion 33.
  • the center of the curvature is in the section through the rotor 15 'in the radial direction outside of the rotor 15'.
  • the radius of curvature becomes larger starting from the region of the largest diameter 31 in the direction of the first side surface 29, wherein either a continuous increase in the radius of curvature or a section-wise enlargement of the radius of curvature can be used. This results in a plurality of successive in the axial direction of portions of the surface portion 33, wherein each further to the first side surface 29 formed toward area has a larger radius of curvature than that in the direction the area of greatest diameter 31 adjacent area.
  • Fig. 5 shows one only in one direction to the first
  • the region of the largest diameter 31 may also be displaced, for example, in the direction of the center plane of the rotor 15 '. In particular, it decreases then, the free length of the wing 18 of the guided area in the region of the largest diameter 31.
  • Such a two-sided taper of the rotor 15 'in the direction of the first side surface 29 back and on the second side surface 30 out, can therefore also in one-sided
  • FIG. 6 shows a plan view of the cover 121 from the side of the connection plate 3.
  • the cover 121 together with the rotor 115 is shown. Good to see are formed in the rotor 115 grooves 117.
  • a groove 117 is provided with a reference numeral. In the grooves 117, a respective wing 18 is arranged.
  • a chamber 135 is formed, which is bounded outwardly by a raceway 134 of the cam ring 119 and in the direction of the axis of rotation of the vane pump 5 through an outer surface 129 of the rotor 115.
  • control openings are also provided in the cover 121.
  • a further control kidney 122 is provided, which is opposite to the first control kidney 22.
  • pressure medium is sucked in both via the first control kidney 22 and also via the further first control kidney 22.
  • a further second control kidney 125 is formed in the cover 121.
  • the further first control kidney 122 is connected via an overflow 133 with the intake passage 23 in Connection.
  • an overflow of pressure medium from the intake passage 23 for example, a recess in the cam ring 119, a chamfering of the cam ring 119 or corresponding holes or a groove in the terminal plate 3 may be arranged.
  • a guide ring 135 is provided.
  • the guide ring 135 is disposed in a recessed area of the rotor 115.
  • Such a guide ring can also be arranged on both sides of the rotor 115.
  • the wings 18 abut with their oriented in the direction of the axis of rotation towards the end face on the outer circumference of the guide ring 135. This ensures even at low speeds or highly viscous pressure medium that the wings 18 sealingly cooperate with the cam ring 19.
  • the extension / retraction of the wings is ensured by the ring in all operating conditions.
  • FIG. 7 shows a further preferred exemplary embodiment of a rotor 115 in an end view.
  • the rotor 115 has its raised portion 131 in the center. This is particularly preferred when the Be Schollanteile on the first control kidney 22 and the other first control kidney 122 are the same for sucking pressure medium.
  • a first distance di from the first side surface 129 to the beginning of the largest diameter portion 131 and the second distance d 2 from the second side surface 130 to the largest diameter portion 131 are equal.
  • the bilateral radial taper can be achieved with the resulting central location of the raised area 131 contribute to the prevention of bending stress due to asymmetry even when filling on one side.
  • a transition region 136 or 136' is formed in each case.
  • This transition region 136 or 136 ' can be formed, for example, with a curvature of the surface sections 133 or 133' running in the opposite direction to the curvature. Because of the symmetry of the rotor 115 shown in FIG. 7, the corresponding features are provided with the corresponding, primed reference numerals. An alternative embodiment of the rotor 115 without transition region is also conceivable.
  • the region of the largest diameter 131 may be arranged in an embodiment of the rotor 115, not shown, outside the center plane of the rotor 115.
  • the ratio di to U 2 is then preferably equal to the ratio of the filling proportions via the first control opening 22 and the further first control opening 122.
  • the area of the largest diameter 131 is formed so that the median plane between the first side face 129 and the second side face 130 lies within the area 131.
  • the asymmetrical displacement corresponding to the Be Stirllan turnover can then be done by displacement in the direction of the first side surface 129 or the second side surface 130 through the transition regions 136 or 136 '.
  • the invention is not limited to the illustrated embodiment. In particular, advantageous combinations of individual features of the individual embodiments are possible with each other.

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

Abstract

L'invention concerne une pompe à palettes dotée d'un rotor (15') comprenant plusieurs ailettes (18) disposées en forme de coulissement radial. La pompe à palettes présente au moins une première vanne de commande (22) pour aspirer le fluide sous pression dans une chambre formée entre deux ailettes (18) adjacentes. Le rotor (15') se rétrécit, partant de la zone du plus grand diamètre (31) vers une première face latérale (29) orientée sur la première vanne de commande (22) pour l'aspiration du fluide sous pression. Le petit rayon (32) du côté du rotor (15') tourné vers la première vanne de commande (22) pour l'aspiration du fluide sous pression est identique à la distance minimale entre la paroi (35) de la première vanne de commande (22) et l'axe de rotation du rotor (15').
PCT/EP2008/004150 2007-06-05 2008-05-23 Pompe à palettes WO2008148472A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102007026180 2007-06-05
DE102007026180.4 2007-06-05
DE102007039172.4A DE102007039172B4 (de) 2007-06-05 2007-08-20 Flügelzellenpumpe
DE102007039172.4 2007-08-20

Publications (1)

Publication Number Publication Date
WO2008148472A1 true WO2008148472A1 (fr) 2008-12-11

Family

ID=39942242

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/004150 WO2008148472A1 (fr) 2007-06-05 2008-05-23 Pompe à palettes

Country Status (2)

Country Link
DE (1) DE102007039172B4 (fr)
WO (1) WO2008148472A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022111278A1 (de) 2022-05-06 2023-11-09 Valeo Powertrain Gmbh Drehschieberpumpe

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010123556A2 (fr) * 2009-04-21 2010-10-28 Slw Automotive Inc. Pompe à palettes avec rotor et bague d'extension à palettes améliorés
DE102010039344A1 (de) * 2010-08-16 2012-02-16 Joma-Polytec Gmbh Flügelzellenpumpe
DE102015107519A1 (de) * 2015-05-13 2016-11-17 Robert Bosch Automotive Steering Gmbh Verdrängerpumpe, Verfahren zum Betreiben einer Verdrängerpumpe, Lenksystem und Getriebe
DE102015120798A1 (de) * 2015-12-01 2017-06-01 Robert Bosch Automotive Steering Gmbh Verdrängerpumpe
DE102016226117A1 (de) 2016-12-22 2018-06-28 Volkswagen Aktiengesellschaft Flügelzellenpumpe, Fluidsystem und Brennkraftmaschine
DE102017201213A1 (de) 2017-01-26 2018-07-26 Volkswagen Aktiengesellschaft Flügelzellenpumpe
DE102017219849A1 (de) * 2017-11-08 2019-05-09 Robert Bosch Gmbh Verdrängermaschine mit einer Axialkolbenmaschine und einer Flügelzellenmaschine

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2636481A (en) * 1949-05-28 1953-04-28 New York Air Brake Co Vane type hydraulic motor
US2853023A (en) * 1955-08-12 1958-09-23 American Brake Shoe Co Fluid energy translating apparatuses
US3175506A (en) * 1960-10-06 1965-03-30 Erdmann Hans Rotating vane type pump
DE2443720A1 (de) * 1973-09-24 1975-04-03 Parker Hannifin Corp Drehkolbenpumpe fuer fluessigkeiten
US4080123A (en) * 1975-06-13 1978-03-21 Daimler-Benz Aktiengesellschaft Rotary liquid pump with spaced drive shaft connection means
EP0068035A1 (fr) * 1981-06-26 1983-01-05 Vickers Systems GmbH Pompe à palettes en particulier pour direction assistée
DE4109149A1 (de) * 1991-03-20 1992-09-24 Rexroth Mannesmann Gmbh Steuerscheibe fuer fluegelzellenpumpe
DE20022423U1 (de) * 2000-07-27 2001-08-30 Luk Fahrzeug-Hydraulik Gmbh & Co Kg, 61352 Bad Homburg Pumpe
EP1178211A2 (fr) * 2000-08-01 2002-02-06 Siemens Aktiengesellschaft Plaque de réglage, notamment pour pompe à palettes
US20050019175A1 (en) * 2003-07-25 2005-01-27 Unisia Jkc Steering Systems Co., Ltd. Variable displacement pump

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2642802A (en) 1948-12-14 1953-06-23 Vickers Inc Dual rotary pump for power transmissions

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2636481A (en) * 1949-05-28 1953-04-28 New York Air Brake Co Vane type hydraulic motor
US2853023A (en) * 1955-08-12 1958-09-23 American Brake Shoe Co Fluid energy translating apparatuses
US3175506A (en) * 1960-10-06 1965-03-30 Erdmann Hans Rotating vane type pump
DE2443720A1 (de) * 1973-09-24 1975-04-03 Parker Hannifin Corp Drehkolbenpumpe fuer fluessigkeiten
US4080123A (en) * 1975-06-13 1978-03-21 Daimler-Benz Aktiengesellschaft Rotary liquid pump with spaced drive shaft connection means
EP0068035A1 (fr) * 1981-06-26 1983-01-05 Vickers Systems GmbH Pompe à palettes en particulier pour direction assistée
DE4109149A1 (de) * 1991-03-20 1992-09-24 Rexroth Mannesmann Gmbh Steuerscheibe fuer fluegelzellenpumpe
DE20022423U1 (de) * 2000-07-27 2001-08-30 Luk Fahrzeug-Hydraulik Gmbh & Co Kg, 61352 Bad Homburg Pumpe
EP1178211A2 (fr) * 2000-08-01 2002-02-06 Siemens Aktiengesellschaft Plaque de réglage, notamment pour pompe à palettes
US20050019175A1 (en) * 2003-07-25 2005-01-27 Unisia Jkc Steering Systems Co., Ltd. Variable displacement pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022111278A1 (de) 2022-05-06 2023-11-09 Valeo Powertrain Gmbh Drehschieberpumpe

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Publication number Publication date
DE102007039172A1 (de) 2008-12-11
DE102007039172B4 (de) 2024-02-15

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