EP1642030A2 - Pompe - Google Patents

Pompe

Info

Publication number
EP1642030A2
EP1642030A2 EP04738734A EP04738734A EP1642030A2 EP 1642030 A2 EP1642030 A2 EP 1642030A2 EP 04738734 A EP04738734 A EP 04738734A EP 04738734 A EP04738734 A EP 04738734A EP 1642030 A2 EP1642030 A2 EP 1642030A2
Authority
EP
European Patent Office
Prior art keywords
pump
contour
area
vane
point
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04738734A
Other languages
German (de)
English (en)
Other versions
EP1642030B1 (fr
EP1642030B2 (fr
Inventor
Ivo Agner
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.)
Magna Powertrain Bad Homburg GmbH
Original Assignee
LuK Fahrzeug Hydraulik GmbH and Co KG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=33521180&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1642030(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by LuK Fahrzeug Hydraulik GmbH and Co KG, ixetic Bad Homburg GmbH filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Publication of EP1642030A2 publication Critical patent/EP1642030A2/fr
Publication of EP1642030B1 publication Critical patent/EP1642030B1/fr
Application granted granted Critical
Publication of EP1642030B2 publication Critical patent/EP1642030B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • 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
    • 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
    • F04C2/3447—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 the vanes having the form of rollers, slippers or the like
    • 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
    • F04C2250/30—Geometry of the stator

Definitions

  • the invention relates to a pump, such as a vane pump or roller cell pump, in particular a gear pump, with a double-stroke delivery contour, the delivery contour having at least one rise area, at least one large circle area, at least one descent area and at least one small circle area, and the pump within the delivery contour has a rotor with radially displaceable Has wings or rollers in radial rotor slots.
  • a pump such as a vane pump or roller cell pump, in particular a gear pump, with a double-stroke delivery contour
  • the delivery contour having at least one rise area, at least one large circle area, at least one descent area and at least one small circle area
  • the pump within the delivery contour has a rotor with radially displaceable Has wings or rollers in radial rotor slots.
  • a pump such as a vane pump or roller cell pump, in particular a gear pump, with a double-stroke conveying contour, the conveying contour having at least one rising area, at least one large circle area, at least one descending area and at least one small circle area and the pump within the conveying contour with a rotor has radially displaceable vanes or rollers in radial rotor slots and the angular range of the large circle area of the delivery contour is extended compared to a standard pump.
  • a pump according to the invention is characterized in that, in the case of a 10-vane pump, the large circle area of the delivery contour is at least 10 ° -15 °, preferably 13 °, larger than the angular division of the vane positions in the rotor (36 °) of a 10-vane standard pump and in the case of a 12-vane pump, the large circle area of the delivery contour is at least 16 ° -25 °, preferably 22 °, larger than the angular division of the vane positions in the rotor (30 °) of a 12-vane standard pump.
  • Another pump according to the invention is characterized in that the length of the suction area remains essentially the same as that of a standard pump. This has the advantage that the suction area of the same size means that no losses have to be accepted when reaching the maximum speed.
  • blade pitch 30 °
  • the turning points in the direction from the pressure area to the suction area have a distance of 2.5 x wing pitch.
  • a pump is preferred in which, in the case of a 10-vane pump, the turning points of the stroke contour function are shifted by approximately 3 ° in the direction of rotation compared to a 10-vane standard contour.
  • This has the advantage that the superimposition of the kinematic volume flow pulsation of the upper wing and lower wing pumps complements each other optimally. Otherwise, the turning points have a distance of approx.2.5 x blade pitch (the blade pitch for the 10-blade pump is 36 °).
  • Figure 1 shows the delivery contour of a 10-vane standard pump.
  • Figure 2 shows the delivery contour of a 10-vane pump according to the invention.
  • Figure 3 shows the delivery contour of a 12-vane pump according to the invention.
  • Figure 4 shows the function of the stroke of a 12-wing conveyor contour according to the invention over the angle of rotation.
  • Figure 5 shows the function of deriving the stroke according to the angle of rotation of a 12-wing conveyor contour according to the invention over the angle of rotation.
  • FIG. 6 shows the function of deriving the cell volume according to the angle of rotation, plotted over the angle of rotation, of a 12-wing conveyor contour according to the invention.
  • FIG. 1 the delivery contour of a 10-vane standard pump with the corresponding rotation angle points is shown schematically.
  • the conveying contour 1 is shown in principle in the center of the picture and is now explained schematically on the basis of the angle points, these angles not being shown exactly in terms of angle, but only their positions being explained schematically.
  • the description of the conveyor contour begins with the angle 0 °, which is located in the middle of the small circle area.
  • the small circle area merges at angle point 5, ie at 15 °, into the rise area (contour is enlarged radially outwards), in which the stroke volume between two wings increases and thus forms the suction area.
  • the rise range has an inflection point in the stroke contour function at angle point 7 at 45 ° (change in radius as a function of the angle of rotation) and finally ends at 69 ° in angle point 9.
  • the position of the inflection points of the stroke contour function can be determined by the position of the maxima and minima of the first derivative determine the stroke contour function via the angle of rotation (exactly).
  • the so-called great circle area extends from the angular point 9, that is from 69 °, to the angular point 11, that is to say 111 °, which, however, ensures this by the so-called case, ie a slight reduction of the stroke radially inward depending on the angle of rotation that the wing heads always remain pressed against the contour.
  • the great circle area with the case can also be defined so that its beginning is the maximum of Stroke contour function forms and its end is given as soon as there is no tangent continuity in the first and / or second derivative of the stroke contour function.
  • the actual descent area begins from point 11, that is at 111 °, which extends to 165 °, that is to the angle point 15, and thus represents the pressure range of the vane pump, since the stroke volume is now reduced.
  • the descent area again has a turning point in the stroke contour function at the angle point 13, ie at 135 °.
  • the point of inflection at point 7, ie in the area of ascent, and the point of inflection at point 13, ie in the area of descent, are spaced apart by approximately 90 °.
  • the 10-vane pump has a vane pitch of 36 °, this corresponds to 2.5 times the vane pitch.
  • the inflection point in the descent area and the inflection point in the next ascent area are thus also spaced apart by 2.5 times the wing pitch.
  • the position of the turning points is symmetrical to the main axis of the contour.
  • Half of the next small circle area extends from 165 °, ie from angle point 15, to 180 °, ie to angle point 17. From 180 ° to 360 °, ie from angle point 17 to back to angle point 3, the conveyor contour repeats itself symmetrically to the previously described conveyor contour half.
  • FIG. 2 shows a conveyor contour according to the invention for use in gear pumps, which has an extended large circle area.
  • the description of the conveyor contour 1 begins again at the angle point 3, i.e. at 0 ° in the middle of
  • the descending area of the conveyor contour begins at angle point 22 at 118 ° and ends again at angle point 15 at 165 °, which means that the pressure area is now shortened by the corresponding 7 ° compared to the pressure area in FIG. 1. It is important that the length of the suction area from the angle point 5 to the angle point 9 is maintained, which is advantageous in terms of reaching the maximum speed.
  • the inflection point 24 in the descent area is at 137.7 °, that is approximately at 138 °, in relation to the inflection point from FIG. 1 by 3 ° in the direction of rotation brought forward, which in turn means that both turning points maintain their distance of 90 ° or 2.5 x the blade pitch of the 10-blade pump (36 °). At 180 ° at angle 17, this new stroke contour according to the invention repeats itself symmetrically to the upper half.
  • a delivery contour of a 12-vane pump according to the invention is shown in FIG.
  • the description of the delivery contour 1 starts again at 0 degrees at the angle point 3. Since the 12-vane pump has a vane division of 30 ° instead of 36 °, the small circle area, which was 30 ° for the 10-vane pump, can be around these are reduced by 6 ° to 24 °, as a result of which the rise range of the conveyor contour begins after half a small circle range at 12 ° at angle point 30.
  • the rise range of the conveyor contour i.e. the suction area, as with the contours from FIG. 1 and FIG. 2, is maintained at 54 ° and thus ends at 66 ° at angle 32, again 3 ° earlier than with the 10-vane pumps.
  • the length of the suction area remains advantageously usable with regard to reaching the maximum speed.
  • the inflection point of the stroke contour function in the rise area should advantageously be in the middle of the rise area and is therefore arranged at angle point 34 at approximately 37.5 °.
  • the great circle area of this conveyor contour now extends from the angle point 32 at 66 ° to the angle point 36 at 118 ° and is thus once again extended by 3 ° compared to the conveyor contour from FIG. 2 or by 10 ° compared to the conveyor contour from FIG. 1, which in turn represents a gain for improved pressure equalization processes with foamed gear oil.
  • the descent area that is to say the pressure area of this conveyor contour, extends from the angle point 36 at 118 ° to the angle point 38 at 168 °, at which the conveyor contour then in turn merges into the next small circle area.
  • the inflection point of the stroke contour function in the descent area is arranged at angle point 40 at 141.7 ° and is thus spaced from the inflection point at angle point 34 by 104 °, that is to say about 3.5 times the blade pitch of 30 ° for the 12-blade pump ,
  • the turning point 40 in the descent area that is to say in the pressure area, is opposite to the next in the direction of rotation
  • the difference between the great circle length and the blade pitch is now 22 ° compared to 6 ° with the standard 10-wing contour and 13 ° compared to the improved 10-wing contour from FIG. 2.
  • the compression range can even be extended by 3 ° compared to the shortened compression range from FIG.
  • the turning points in the transition functions of the stroke contour therefore have a factor x.5 of the wing pitch, which is the basis for a good superimposition of the lower wing and upper wing pressure pulsation.
  • the aim of the invention is to make the available angle in the large circle area as long as possible, since the noise in foamed gear oil is mainly dominated by the pressure compensation processes and not by the geometrically caused volume flow pulsation. With this contour, too, the compression range is somewhat shorter than the intake range, and the turning points are rotated slightly further as a pair.
  • FIG. 4 shows the stroke contour function of the 12-wing contour from FIG. 3 with an extended case over the angle of rotation.
  • the contour increase begins at point 50 (corresponds to point 30 in FIG. 3) and continues to point 54.
  • the great circle area 56 begins at point 54 (point 32 in FIG. 3) at approximately 66 °.
  • the great circle area 56 constantly reduces the wing stroke with the so-called case to point 58 (point 36 in FIG. 3), in which the contour drop 60 then occurs extends to point 62 (point 38 in Figure 3).
  • the small circle area 64 then begins at point 62 and extends to point 66. Then the contour starts again in the same way as from point 50.
  • FIG. 5 shows the function of deriving the wing stroke according to the angle of rotation of the contour from FIG. 3 over the angle of rotation.
  • the contour increase begins with increasing amount of derivative of the wing stroke according to the angle of rotation and has its maximum at point 72 (point 34 in FIG. 3), whereupon the amount of derivative of the wing stroke according to the angle of rotation up to Point 74 (point 32 in
  • FIG. 3 decreases again steadily.
  • point 74 there is then the transition to the great circle area, the derivation of which is shown by the course of line 76.
  • the large circle area 76 passes at point 78 (point 36 in FIG. 3) to the transition function in the direction of a small circle, which initially begins with a decreasing amount of the derivative of the wing stroke according to the angle of rotation, which is represented by the function curve 80 is started until, from the minimum 82 (point 40 in FIG. 3), the amount of the derivative of the wing stroke according to the angle of rotation increases again, as represented by the functional area 84.
  • point 86 point 38 in FIG. 3
  • the small circle area 90 is then reached, which extends to point 92. From point 92, the function sequence is repeated as from point 70.
  • FIG. 6 shows the derivation of the cell volume according to the angle of rotation of the contour from FIG. 3 over the angle of rotation.
  • a progressive increase in cell volume up to point 100 and then a degressive increase in cell volume up to point 102 characterize the suction process.
  • the volume is then gradually and gradually reduced in the great circle area until the actual compression process takes place from point 104 with a progressive decrease in volume to point 106 and then with a degressive decrease in volume to point 108.
  • This function of deriving the cell volume according to the angle also shows, for example, between points 100 and 106 the distance of the turning points of the stroke contour function from 3.5 times the wing pitch and from point 106 to point 110 from 2.5 times the wing pitch.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

La présente invention concerne une pompe telle qu'une pompe à cellules à ailettes ou une pompe à cellules à rouleaux par exemple, en particulier une pompe à engrenages, présentant un contour d'acheminement à double course qui présente au moins une zone de montée, au moins une zone de grand cercle, au moins une zone de descente et au moins une zone de petit cercle, la pompe présentant à l'intérieur du contour d'acheminement, un rotor comprenant des rouleaux ou des ailettes à mouvement axial, disposé(e)s dans des fentes radiales.
EP04738734.5A 2003-06-30 2004-06-19 Pompe Expired - Lifetime EP1642030B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10329284 2003-06-30
PCT/DE2004/001284 WO2005001289A2 (fr) 2003-06-30 2004-06-19 Pompe

Publications (3)

Publication Number Publication Date
EP1642030A2 true EP1642030A2 (fr) 2006-04-05
EP1642030B1 EP1642030B1 (fr) 2016-04-13
EP1642030B2 EP1642030B2 (fr) 2019-12-04

Family

ID=33521180

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04738734.5A Expired - Lifetime EP1642030B2 (fr) 2003-06-30 2004-06-19 Pompe

Country Status (7)

Country Link
US (1) US7922469B2 (fr)
EP (1) EP1642030B2 (fr)
JP (1) JP4653739B2 (fr)
KR (1) KR101162780B1 (fr)
CN (1) CN101052806B (fr)
DE (1) DE102004030478A1 (fr)
WO (1) WO2005001289A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5762202B2 (ja) * 2011-08-02 2015-08-12 日立オートモティブシステムズ株式会社 可変容量型ベーンポンプ
US10227979B2 (en) * 2016-10-19 2019-03-12 Ford Global Technologies, Llc Vane spacing for a variable displacement oil pump

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Publication number Priority date Publication date Assignee Title
US2731919A (en) * 1956-01-24 Prendergast
US2588430A (en) 1945-10-15 1952-03-11 Odin Corp Rotary blade pump
DE1011284B (de) 1951-10-23 1957-06-27 Charles Scott Prendergast Pumpe oder Motor
US2831631A (en) 1953-07-27 1958-04-22 Petersen Entpr Rotary compressor
US3869231A (en) 1973-10-03 1975-03-04 Abex Corp Vane type fluid energy translating device
JPH0674790B2 (ja) * 1983-03-08 1994-09-21 株式会社豊田中央研究所 流体圧ベ−ンポンプ
CN86206061U (zh) * 1986-08-15 1987-06-10 杨斌 用于双作用叶片油泵的定子
US4913636A (en) 1988-10-05 1990-04-03 Vickers, Incorporated Rotary vane device with fluid pressure biased vanes
JPH0378987U (fr) * 1989-12-04 1991-08-12
JP3080185B2 (ja) * 1991-07-10 2000-08-21 カヤバ工業株式会社 ベーンポンプ装置
DE4327106A1 (de) 1993-08-12 1995-02-16 Salzkotten Tankanlagen Flügelzellenpumpe
DE19626211C2 (de) * 1996-06-29 2002-03-14 Luk Fahrzeug Hydraulik Flügelzellenpumpe
DE19710378C1 (de) 1996-12-23 1998-03-12 Luk Fahrzeug Hydraulik Flügelzellenmaschine, insbesondere Flügelzellenpumpe
EP0851123B1 (fr) * 1996-12-23 2003-07-09 LuK Fahrzeug-Hydraulik GmbH & Co. KG Pompe à palettes
DE19900926B4 (de) 1998-01-28 2015-01-22 Magna Powertrain Bad Homburg GmbH Pumpe
DE10027990A1 (de) 2000-06-08 2001-12-20 Luk Fahrzeug Hydraulik Pumpe
JP2003097453A (ja) * 2001-09-25 2003-04-03 Hitachi Unisia Automotive Ltd 可変容量型ベーンポンプ
JP2003097454A (ja) * 2001-09-26 2003-04-03 Hitachi Unisia Automotive Ltd ベーンポンプ

Non-Patent Citations (1)

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Title
See references of WO2005001289A2 *

Also Published As

Publication number Publication date
DE102004030478A1 (de) 2005-01-20
EP1642030B1 (fr) 2016-04-13
WO2005001289A2 (fr) 2005-01-06
WO2005001289A3 (fr) 2007-03-22
KR101162780B1 (ko) 2012-07-04
CN101052806A (zh) 2007-10-10
US7922469B2 (en) 2011-04-12
KR20060032597A (ko) 2006-04-17
US20070128065A1 (en) 2007-06-07
CN101052806B (zh) 2010-12-08
JP4653739B2 (ja) 2011-03-16
JP2007524027A (ja) 2007-08-23
EP1642030B2 (fr) 2019-12-04

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