EP2286088B1 - Pompe - Google Patents

Pompe Download PDF

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Publication number
EP2286088B1
EP2286088B1 EP09741806A EP09741806A EP2286088B1 EP 2286088 B1 EP2286088 B1 EP 2286088B1 EP 09741806 A EP09741806 A EP 09741806A EP 09741806 A EP09741806 A EP 09741806A EP 2286088 B1 EP2286088 B1 EP 2286088B1
Authority
EP
European Patent Office
Prior art keywords
side plate
pump
outer ring
outer edge
housing
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.)
Not-in-force
Application number
EP09741806A
Other languages
German (de)
English (en)
Other versions
EP2286088A2 (fr
Inventor
Johannes Maas
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.)
ixetic Bad Homburg GmbH
Original Assignee
ixetic Bad Homburg 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 ixetic Bad Homburg GmbH filed Critical ixetic Bad Homburg GmbH
Publication of EP2286088A2 publication Critical patent/EP2286088A2/fr
Application granted granted Critical
Publication of EP2286088B1 publication Critical patent/EP2286088B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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
    • F04C2/3441—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 one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—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 one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution

Definitions

  • the invention relates to a pump, in particular vane pump with variable delivery volume, according to the preamble of claim 1.
  • Pumps of the type discussed here are, for example WO 2007/036189 A1 , out DE 18 02 021 A1 or off DE 100 27 811 A1 , considered as the closest prior art, known.
  • Such pumps such as vane pumps, roller-cell pumps or the like, serve to convey, for example, hydraulic oil and have a pump housing and a cam ring arranged therein, which surrounds a rotor cooperating with a shaft. They also have an outer ring and at least one cooperating with this side plate.
  • Pumps of the type discussed here have to change the delivery volume on an adjustable against the force of a spring cam ring, so that the delivery volume can be reduced or increased depending on the position of the cam ring accordingly.
  • the at least one side plate is arranged in the axial direction, ie in the direction of the axis of rotation of the shaft, next to the lifting ring and forms a lateral boundary of the enclosed between the wings, the rotor, the lifting ring and a second lateral boundary conveyor cells.
  • the side plate is supported on the outer ring, which in turn on the pump housing or supported on the housing cover of the pump.
  • the outer ring serves to ensure a defined distance between the side plate and the rotor or the lifting ring, namely the so-called design clearance. He thus serves in known pumps as a spacer between the side plate and the rotor or the cam ring and has a correspondingly small wall thickness.
  • the cam ring facing away from the back of the side plate is completely or only partially applied to the pump pressure. Due to the fact that the pressurized areas on the back of the side plate are larger than that on the cam ring side facing the side plate, this deforms under the load of the hydraulic oil such that within the inner diameter of the outer ring, the distance between the rotor or the cam ring and the side plate is smaller, at the same time the side plate in the area outside the inner diameter lifts with increasing distance from the inner diameter of the outer ring.
  • the side plate is pressed in a depressurized state of the pump, the side plate only by a biasing element, such as an elastic seal or a spring against the outer ring, so that the parts are in the pressureless state together and can start the pump.
  • a biasing element such as an elastic seal or a spring against the outer ring
  • These biasing forces are low compared to the compressive forces acting on the side plate during operation.
  • Pumps that allow a change in the delivery volume include an outer ring having a large inner diameter. Due to the large inner diameter, the diameter of the side plate increases, so that the deflection of the side plate can assume considerable values, which in turn a large interpretation game, so a large distance between the side plate and the cam ring, or the rotor is required.
  • the object of the invention is therefore to provide a pump which does not have the disadvantages mentioned above, which in particular has a small bearing distance and compact builds.
  • a pump which has the features of claim 1.
  • the pump is characterized in that the at least one side plate in the axial direction between the pump housing and the outer ring, at least in a radially outer edge region, ie in the region outside the inner diameter of the outer ring in the unpressurized and pressurized state of the pump is firmly clamped and fixed so that a lifting of the side plate under load in the outer edge region is substantially avoided, and that an edge surface of the at least one side plate in the outer edge region on the outer ring and arranged on the back, so opposite edge surface of the Side plate rests against a projection of the pump housing.
  • the side plate is fixed or clamped in the outer edge region in the axial direction between the outer ring and the pump housing.
  • An axial clamping of the side plate, the pump housing and the outer ring can be done by means of a screw.
  • the fixed axial fixation in the region of an outer edge of the side plate leads to the reduction of the deformation of the side plate under pressurization. Because the side plate is clamped or fixed in the outer edge region in the axial direction, that is to say in the direction of the axis of rotation of the shaft, lifting of the side plate on the outer edge of the outer ring is prevented, that is to say in the region outside the inner diameter of the outer ring. making the side plate more stable overall and avoiding excessive deformation of the side plate under load.
  • a pump which is characterized in that at least on the outer edge region, that is in the region outside the inner diameter of the outer ring, the at least one side plate in the axial direction a force is exerted that is so large that in the direction of Rotary axis of the shaft, the side plate is firmly fixed at least in the outer edge region in the axial direction, so that deformation of the side plate under pressure is substantially reduced.
  • a further preferred pump is provided that two side plates are provided, which, viewed in the axial direction, are arranged on opposite sides of the outer ring.
  • An axial tension or fixation can thus also be provided in the case of an adjustable vane-cell pump pressure-compensated on both sides.
  • the side plate is clamped in an outer edge region on the outer ring so that a lifting of the side plate is avoided at the outer edge.
  • a screw connection of the pump housing, the two side plates, the outer ring and the housing cover an axial clamping.
  • one of the two side plates in the outer edge region on the pump housing is applied and the other side plate for generating an axial force in the outer edge region cooperates with at least one elastic element, for example with a plate spring.
  • at least one elastic element for example with a plate spring.
  • a pump is preferred, which is characterized in that a side plate is at least partially disposed on the pump housing and the respective other side plate on the housing cover.
  • a side plate is at least partially disposed on the pump housing and the respective other side plate on the housing cover.
  • the pump can be dispensed with the elastic elements.
  • a pump is preferred, which is characterized in that the ratio of an outer radial section to an inner radial section of the side plate is ⁇ 0.2.
  • a particularly secure axial fixation in the outer region of the side plate is possible, whereby a deformation of the side plate under pressure is substantially reduced.
  • FIG. 1 shows a schematic sectional view of a known from the prior art pump 1.
  • the pump 1 shown here is purely by way of example a vane pump with variable delivery volume, as for example in WO 2007/036189 A1 is described.
  • Such pumps are used in particular for consumers with, depending on the operating state, greatly changing volumetric flow requirements, such as, for example, in power steering devices for motor vehicles.
  • the pump 1 has a pump housing 3 and a housing cover 5. Further, a shaft 7 and a rotatably connected thereto rotor 9 are provided.
  • the shaft 7 is mounted in the pump housing 3 by means of two radial bearings 11 and 11 ', which have a bearing distance a to each other.
  • shaft seals 13 and 13 ' provided on the shaft 7, which prevent leakage of fluid, in particular leakage oil from the pump 1.
  • At least one radial slot is provided, in which a radially displaceable wing 15 is arranged.
  • the vane 15 is displaced out of the slot so that it slides along the inner surface of a cam ring 17 surrounding the rotor 9.
  • an outer ring 19 is provided, on which a side plate 21 is supported, which has an opening 22 for the passage of the shaft 7.
  • the cam ring 17 is freely displaceable in the outer ring 19. On the side facing away from the side plate 21 of the outer ring 19, this is supported on the housing cover 5 from.
  • the outer ring 19 serves to ensure a defined distance b and b 'between the side plate 21 and the housing cover 5 and the rotor 9 and the cam ring 17, wherein the distances b and b' together give the interpretation game.
  • the side plate 21 In the pressureless state of the pump 1, the side plate 21 is pressed by a biasing element, here in the form of the elastic seals 25 or even by a spring, not shown here, against the outer ring 19. In this case, the side plate rests against the end face of the outer ring. In the pressurized state of the pump 1, however, the back 23 of the side plate 21 is fully or partially applied to the pump pressure.
  • the vane pump shown here is thus a one-sided pressure compensated pump 1.
  • a gap S is provided, which should also ensure that the housing cover 5 cooperates with a defined stop 26 of the pump housing 3.
  • FIG. 2 shows a schematic sectional view of the pump 1 according to FIG. 1 under load.
  • the same parts are provided with the same reference numerals, so far as the description to FIG. 1 is referenced.
  • FIG. 2 makes it clear that the forces resulting from a pressurization of the rear side 23 on the side plate 21 outweigh the forces exerted on the side plate 21 from the side facing the rotor 9.
  • FIG. 2 also shows that the side plate 21 is deformed by the pressurization on the back of the side plate 21 within the inner edge K of the outer ring 19 in the direction of the rotor 9, wherein At the same time it lifts off the outer ring 19 outside the inner edge K of the outer ring 19 at the outer edge.
  • the contact surface between the side plate 21 and the end face of the outer ring 19 reduces under load up to a "contact line", which is defined on the end face of the outer ring by the inner edge K.
  • the distance b must therefore be so great that a contact of the side plate 21 and the rotor 9 is avoided even with a large deformation of the side plate 21, that is at maximum pump pressure and maximum swung-out cam ring. It is also possible to form the side plate 21 thicker, so that the deformation is reduced under pressure.
  • both solutions have the disadvantage that the bearing distance a would increase, which in addition an enlargement of the shaft diameter would be required to prevent bending of the shaft 7. As a result, the axial and radial length and the weight of the pump 1 would increase.
  • FIG. 3 shows a schematic sectional view of a pump 1 of a first embodiment of the invention. Same parts are with provided with the same reference numerals, so that reference is made to the description of the preceding figures.
  • the pump 1 shown here has at least one pressure-compensated side plate 21, preferably with an enlarged diameter.
  • the outer ring 19 has a larger diameter than the known from the prior art outer rings.
  • the side plate 21 and the outer ring 19 extend further in the radial direction beyond the inner edge K on the end face of the outer ring 19 also, ie perpendicular to the axis of rotation D, as in the in the Figures 1 and 2 shown pumps 1.
  • FIG. 3 makes it clear that the side plate 21 is supported on the outer ring 19 here as well.
  • the at least one side plate 21 has a, seen in the radial direction, outer edge region 27, in which the side plate 21 is supported with a first edge surface 29 on the outer ring 19. On the side opposite the first edge surface 29, the side plate 21 is supported with a second edge surface 31 on a projection 33 of the pump housing 3. By the projection 33, the gap S between the side plate 21 and the pump housing 3 is formed.
  • the side plate 21 is arranged between the projection 33 of the pump housing 3 and the outer ring 19.
  • An axial clamping of the side plate 21 with the pump housing 3 and the outer ring 19 is here purely by way of example in FIG 3 merely indicated screw 35, which passes through the housing cover 5, the outer ring 19, the side plate 21 and the pump housing 3.
  • screw 35 By means of the screw 35, an axial force is exerted on all the above-mentioned components, ie also on the side plate 21, so that it is clamped between the outer ring 19 and the projection 33.
  • the side plate 21 between the pump housing 3 and the outer ring 19 axially, ie in the direction of the rotation axis D, fixed.
  • the side plate 21 is firmly clamped at least in the outer edge region 27 in the unpressurized and pressurized state of the pump 1, in the axial direction, ie in the direction of the axis of rotation D of the shaft 7.
  • An in FIG. 2 shown lifting the side plate 21 from the outer edge of the outer ring 19 is thus avoided.
  • the deformation of the side plate 21 under load so when pressurizing the back 23 with hydraulic oil, significantly reduced, so that can be dispensed with an increase in the interpretation game and a thicker design of the side plate 21 to prevent excessive bending , Rather, even thinner side plates 21 can be used, which allow a shortening of the bearing distance a and thereby a reduction in the weight and the installation space of the pump 1.
  • the projection 33 seen in the radial direction, is formed as wide as the outer ring 19, so that the edge surfaces 29 and 31 are the same size.
  • FIG. 4 shows a schematic sectional view of a second embodiment of a pump 1 under load. Same parts are provided with the same reference numerals, so that reference is made to the description of the preceding figures.
  • the embodiment according to FIG. 4 shows a double-sided pressure compensated pump 1, in which therefore two side plates 21 and 21 'are provided.
  • the arrangement of the side plate 21 corresponds to the in FIG. 3 shown, so reference is made in this regard to the preceding description.
  • the second side plate 21 ' is disposed through the outer ring 19 at a distance b', the so-called interpretation game, from the rotor 9 and the cam ring 17.
  • the side plate 21 ' has the same radius R as the side plate 21 measured from the rotation axis D of the shaft 7 to the outer edge c of the side plates 21, 21'.
  • FIG. 4 makes it clear that the side plate 21 'is arranged by the preferably integrally formed with the housing cover 5 projection 37 at a distance from the housing cover 5, so that between this and the side plate 21', a gap S 'is formed for receiving hydraulic oil, in the
  • elastic sealing elements 25 'and / or a non-illustrated spring element can be arranged.
  • the wall 43 of the pump housing 3 can be substantially thinner.
  • FIG. 5 shows a schematic sectional view of a third embodiment of a pump 1.
  • the same parts are the same Reference numerals provided so that reference is made to the description of the preceding figures.
  • FIG. 5 shows a double-sided pressure compensated vane pump under load. Accordingly, according to the in FIG. 4 shown embodiment, two side plates 21, 21 'is provided. The arrangement of the side plate 21 corresponds to that in the Figures 3 and 4 shown, so here is not further discussed.
  • an elastic element 45 is provided, which is formed here purely by way of example as a plate spring.
  • the elastic element 45 is supported on the one hand on the housing cover 5 and on the other hand on the outer edge region 27 'on the side plate 21' from.
  • the housing cover 5 is screwed to the pump housing 3 by means of a screw 47 only indicated here.
  • Other types of cover and housing are also possible.
  • the wall portion 43 of the pump housing 3 is thicker here in the radial direction.
  • the elastic element 45 is supported on the one hand on the housing cover 5 and on the other hand in the outer edge region 27 'on the side plate 21' from. As a result, an axial force is exerted on the side plates 21 and 21 '.
  • the elastic member 45 is different from the elastic members 25 and 25 '(FIG. FIG. 1 ) in that it exerts a significantly greater force on the side plates 21 and 21 '. This force is according to the invention so great that the lifting the side plates 21, 21 'in the outer edge regions 27, 27' is prevented from the outer ring 19, that is, in this embodiment, the side plates 21 and 21 'are axially clamped in the pump. It can also be provided that the elastic element 45 is supported on the side plate 21 and on the pump housing 3.
  • the pump 1 according to the present invention is in the FIGS. 3 to 5 each shown under load; the side plates 21, 21 'are thus subjected to a pressure. It can be clearly seen that different than in the FIG. 2 shown conventional pump 1 in the pressurized state, the side plates 21, 21 'does not lift off at the outer edge of the outer ring 19 and the distance b, b' between the rotor 9 and the side plates 21, 21 ', although smaller, excessive bending but through the solid axial clamping of the side plates 21, 21 'is prevented.
  • the pump 1 proposed here has at least one pressure-compensated side plate 21, which has a larger radius R than conventional side plates.
  • the pump 1 according to the invention also preferably has an outer ring 19 with a larger diameter.
  • the side plates 21, 21 ' are axially fixed in an outer edge region 27, 27' between the outer ring 19 and the pump housing 3, or the housing cover 5 or an elastic element 45, for example by means of a screw.
  • the pump 1 proposed here can also be used with adjustable vane pumps, which are operated without pressure or at low pressures. In these operating conditions, there is a risk that the side plates 21, 21 'stand out from the outer ring 19 due to pressure peaks in the work chambers of the pump 1, not shown here, and thus are damaged. In the embodiments of the invention described herein, the pressing force of the side plates 21, 21 'can be increased without increasing the deformation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Fluid-Driven Valves (AREA)
  • Eye Examination Apparatus (AREA)

Claims (11)

  1. Pompe (1), notamment pompe à cellules semi-rotatives à volume déplacé variable, avec un carter de pompe (3) et un anneau de levage (17) disposé en son sein qui entoure un rotor (9) coopérant avec un arbre (7), ainsi qu'avec au moins une plaque latérale (21) qui coopère avec un anneau externe (19) prévu radialement en dehors de l'anneau de levage (17), caractérisée en ce que l'au moins une plaque latérale (21) est encastrée de manière fixe et ainsi fixée au moins dans une région de bordure extérieure (27) vue dans la direction radiale, à l'état sans pression et à l'état conducteur de pression de la pompe (1), en direction axiale entre le carter de pompe (3) et l'anneau externe (19) de telle sorte qu'un soulèvement de la plaque latérale (21) est essentiellement évité en charge dans la région de bordure extérieure (27), et qu'une surface de bordure (29) de l'au moins une plaque latérale (21) repose dans la région de bordure extérieure (27) sur l'anneau externe (19) et une surface de bordure opposée (31) de la plaque latérale (21) repose sur une saillie (33) du carter de pompe (3).
  2. Pompe selon la revendication 1, caractérisée en ce qu'une force est exercée en direction axiale au moins sur la région de bordure extérieure (27) de l'au moins une plaque latérale (21).
  3. Pompe selon la revendication 2, caractérisée en ce que l'au moins une plaque latérale (21) est vissée au carter de pompe (3) et à l'anneau externe (19) en vue de générer la force axiale.
  4. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que deux plaques latérales (21, 21') qui sont disposées sur des côtés opposés de l'anneau externe (19), vu en direction axiale, sont prévues.
  5. Pompe selon la revendication 4, caractérisée en ce que les deux plaques latérales (21, 21') reposent dans la région de bordure extérieure (27, 27') sur l'anneau externe (19).
  6. Pompe selon l'une quelconque des revendications précédentes 4 ou 5, caractérisée en ce qu'une plaque latérale (21) repose dans la région de bordure extérieure (27) sur le carter de pompe (3) et l'autre plaque latérale (21') coopère avec un élément élastique (45) en vue de générer une force axiale dans la région de bordure extérieure (27').
  7. Pompe selon la revendication 6, caractérisée en ce que l'élément élastique (45) est disposé entre la plaque latérale (21) et le carter de pompe (3).
  8. Pompe selon la revendication 6, caractérisée en ce que l'élément élastique (45) est disposé entre la plaque latérale (21') et un couvercle de carter (5).
  9. Pompe selon l'une quelconque des revendications précédentes 4 à 8, caractérisée en ce qu'une plaque latérale (21) s'appuie dans la région de bordure extérieure (27) sur une saillie (33) du carter de pompe (3) et l'autre plaque latérale respective (21') s'appuie sur une saillie (37) du couvercle de carter (5).
  10. Pompe selon la revendication 9, caractérisée en ce que les deux plaques latérales (21, 21'), le couvercle de carter (5), l'anneau externe (19) et le carter de pompe (3) sont vissés ensemble.
  11. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que le rapport entre un trajet partiel radial extérieur (I1) de la plaque latérale et un trajet partiel intérieur (I2) de la plaque latérale (21, 21') est ≥ 0,2.
EP09741806A 2008-05-08 2009-04-17 Pompe Not-in-force EP2286088B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008023830 2008-05-08
PCT/EP2009/002831 WO2009135587A2 (fr) 2008-05-08 2009-04-17 Pompe

Publications (2)

Publication Number Publication Date
EP2286088A2 EP2286088A2 (fr) 2011-02-23
EP2286088B1 true EP2286088B1 (fr) 2011-11-23

Family

ID=41265067

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09741806A Not-in-force EP2286088B1 (fr) 2008-05-08 2009-04-17 Pompe

Country Status (4)

Country Link
EP (1) EP2286088B1 (fr)
AT (1) ATE534822T1 (fr)
DE (1) DE112009000601A5 (fr)
WO (1) WO2009135587A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3081741B1 (fr) 2015-04-17 2019-11-13 Schwäbische Hüttenwerke Automotive GmbH Pompe

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018091265A (ja) * 2016-12-06 2018-06-14 Ｋｙｂ株式会社 可変容量形ベーンポンプ

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL290789A (fr) *
DE1788270U (de) * 1956-09-06 1959-05-06 Bosch Gmbh Robert Zahnradfluessigkeitspumpe.
DE1802021A1 (de) * 1968-10-09 1970-06-18 Teves Gmbh Alfred Drehfluegelpumpe
DE9201060U1 (de) * 1992-01-29 1992-03-19 Voulgaris, Andres, 8164 Hausham Hydraulischer Motor
DE19703114C2 (de) * 1997-01-29 2002-11-21 Danfoss As Hydraulische Flügelzellenmaschine
DE19904339A1 (de) * 1999-02-03 2000-08-10 Mannesmann Rexroth Ag Hydrostatische Pumpe
DE10027811A1 (de) * 2000-06-05 2001-12-13 Luk Fahrzeug Hydraulik Pumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3081741B1 (fr) 2015-04-17 2019-11-13 Schwäbische Hüttenwerke Automotive GmbH Pompe

Also Published As

Publication number Publication date
WO2009135587A3 (fr) 2010-03-18
EP2286088A2 (fr) 2011-02-23
ATE534822T1 (de) 2011-12-15
WO2009135587A2 (fr) 2009-11-12
DE112009000601A5 (de) 2011-03-31

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