EP1642030B1 - Pompe - Google Patents

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Publication number
EP1642030B1
EP1642030B1 EP04738734.5A EP04738734A EP1642030B1 EP 1642030 B1 EP1642030 B1 EP 1642030B1 EP 04738734 A EP04738734 A EP 04738734A EP 1642030 B1 EP1642030 B1 EP 1642030B1
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EP
European Patent Office
Prior art keywords
region
contour
pump
point
wing
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.)
Expired - Lifetime
Application number
EP04738734.5A
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German (de)
English (en)
Other versions
EP1642030A2 (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
Magna Powertrain Bad Homburg GmbH
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Publication of EP1642030B1 publication Critical patent/EP1642030B1/fr
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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
    • 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 gear pump, with doppelhubiger conveying contour, wherein the conveying contour has at least one rising area, at least one great circle area, at least one descent region and at least one small circle region and the pump within the delivery contour 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 gear pump, with doppelhubiger conveying contour
  • the conveying contour has at least one rising area, at least one great circle area, at least one descent region and at least one small circle region and the pump within the delivery contour a rotor with radially displaceable Has wings or rollers in radial rotor slots.
  • the cell volume is nearly constant (apart from the case, which is a slight reduction of the blade stroke radially inward depending on the angle of rotation), and it can via pressure equalizing notches or intermediate capacities (see DE 100 27 990 A1 ) the pressure reversal can be realized soft with low pressure gradient.
  • these measures are not sufficient for use with foamed gear oil.
  • US 2,588,430 shows a vane pump with 12 wings and with an annular contour in which the small circle area is 40 °, the great circle area is 40 ° and both the rise area (suction) and the descent area (pressure range) 50 °. So the great circle area with 40 ° is smaller than the descent area with 50 ° and the rise area with 50 ° the same size as the descent area with 50 °.
  • the application describes that thereby higher pressures and better efficiencies can be achieved. We proposed no solution to the problem of "foamed oil” or "air in oil”.
  • a vane cell pump or roller cell pump having a double-stroke conveying contour, wherein the conveying contour comprises at least one rising region, which represents a suction region, at least one great circle region, which represents a first separating region, at least one descent region, which represents a pressure region, and at least one small-circle region, which represents a further separation region, and the pump within the delivery contour has a rotor with radially displaceable vanes or rollers in radial slots, wherein the angular range of the great circle of the delivery contour is greater than the angular range of the descent region, and in that the angular range of the increase region so-called suction area, larger than the angle range of the descent area.
  • a pump according to the invention is characterized in that in a 10-blade pump the great circle region of the conveying contour by at least 10 ° -15 °, preferably 13 ° greater than the angular pitch of the blade positions in the rotor (36 °) of a 10-wing standard pump and in a 12-blade pump, the great circle region of the delivery contour is at least 16 ° -25 °, preferably 22 ° greater than the angular pitch of the blade positions in the rotor (30 °) of a 12-wing standard pump.
  • the compression area is shortened compared to the standard pumps, and the area which is available for the pressure compensation process (pressure equalizing notches or intermediate capacities) advantageously extends by the corresponding angle or angles.
  • a further pump according to the invention is characterized in that the length of the suction region remains essentially the same with respect to a standard pump. This has the advantage that no losses must be accepted by the same large suction area with respect to reaching the maximum speed.
  • a pump is preferred in which, in the case of a 10-blade pump, the turning points of the Hubkonturfunktion are shifted relative to a 10-wing standard contour by about 3 ° in the direction of rotation.
  • This has the advantage that the superposition of the kinematic volumetric flow pulsation of the wing and underfloor pump complement each other optimally. Otherwise, the turning points have a distance of about 2.5 x wing pitch (the wing pitch in the 10-wing pump is 36 °).
  • FIG. 1 the delivery contour of a 10-wing standard pump with the corresponding rotation angle points is shown schematically.
  • the conveyor contour 1 is shown in principle in the center of the picture and will now be explained schematically with reference to the angular points, these angles are not shown angularly accurate, but only their positions are explained schematically.
  • the conveyor contour description begins with the angle 0 °, which is located in the middle of the small circle area.
  • the small circle region goes in the angular point 5, ie at 15 °, in the rising area (contour is enlarged radially outward), in which increases the displacement between two wings and thus forms the suction area.
  • the rise area has an inflection point in the Hubkonturfunktion (radius change as a function of the angle of rotation) at angle point 7 at 45 ° and finally ends at 69 ° at the angle 9.
  • the position of the inflection points Hubkonturfunktion can be determined by the position of the maxima and the minima of the first derivative determine the stroke contour function above the angle of rotation (exactly). From the angle point 9, that is from 69 °, to the angle point 11, that is to say to 111 °, the so-called great circle region extends, which, however, is defined by the so-called case, i. a slight reduction of the stroke radially inwards depending on the angle of rotation, ensures that the wing heads always remain pressed against the contour.
  • the great circle region with the case can also be defined such that its beginning forms the maximum of the stroke contour function and is given its end as soon as there is no tangent continuity in the first and / or second derivative of the stroke contour function.
  • the actual descent region begins, which runs up to 165 °, that is to say up to the angle 15, and thus represents the pressure range of the vane pump, since the stroke volume now decreases.
  • the descent region has at angular point 13, i. at 135 °, again a turning point in the Hubkonturfunktion.
  • the inflection point at point 7, i. in the rise area, and the inflection point at point 13, i. in the descent, are spaced by about 90 ° from each other.
  • the 10-wing pump has a wing pitch of 36 °, this corresponds to 2.5 times the wing pitch.
  • the turning point in the descent area and the turning point in the next rise area are therefore also spaced by 2.5 times the wing pitch to each other.
  • the location of the turning points is symmetrical to the main axis of the contour. From 165 °, i. from the angle 15, up to 180 °, i. until the angle 17, in turn, one half of the next small circle area extends. From 180 ° to 360 °, i. from the angle 17 to back to the angle 3, the conveyor contour is repeated symmetrically to the previously described votingkonturhgan.
  • FIG. 2 a conveyor contour according to the invention for use in gear pumps is shown, which has a prolonged great circle area.
  • the description of the conveyor contour 1 begins again at the angle 3, ie at 0 ° in the middle of the small circle area.
  • the increase in the conveying contour begins and ends at the angle point 9 again at 69 °.
  • the turning point of the conveyor contour function within the rise range is opposite to the FIG. 1 from 45 to 47.7 °, ie offset to about 48 ° or 3 ° in the direction of rotation and is thus at the new angular point 20.
  • the great circle region of the new contour now extends from the angle point 9, ie from 69 °, to the angle point 22 at 118 °, which means that the great circle area with respect to the great circle area FIG. 1 extended by about 7 ° and this extension is now available for longer pressure equalization operations to compress unresolved air in the oil.
  • the descent region of the conveying contour begins at angle point 22 at 118 ° and ends again at angle point 15 at 165 °, which means that the pressure range now by the corresponding 7 ° relative to the pressure range in FIG. 1 is shortened. It is important that the length of the suction region is maintained from the angular point 5 to the angle point 9, which is advantageous in terms of reaching the maximum speed.
  • the inflection point 24 in the descent area is at 137.7 °, ie about 138 °, opposite to the inflection point off FIG. 1 advanced by 3 ° in the direction of rotation, which in turn means that both inflection points maintain their spacing of 90 ° or 2.5 x the pitch of the 10-blade pump (36 °).
  • this new, inventive stroke contour is repeated symmetrically to the upper half.
  • FIG. 3 a conveyor contour according to the invention of a 12-blade pump is shown.
  • the description of the conveyor contour 1 begins again at 0 degrees in the angular point 3.
  • the 12-wing pump has a wing pitch of 30 ° instead of 36 °
  • the small circle area which has been 30 ° in the 10-wing pump to be reduced to 24 ° 6 °, whereby the rise range of the conveying contour begins after half a small circle at 12 ° in the angular point 30.
  • the rising area of the conveying contour ie the suction area, is like the contours FIG. 1 and FIG. 2 maintained at 54 ° and thus ends at 66 ° at the angle of 32, so again 3 ° earlier than the 10-wing pumps.
  • the inflection point of the Hubkonturfunktion in the rise area should be located advantageously in the middle of the rise range and is therefore arranged at an angle 34 at about 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 with respect to the conveyor contour FIG. 2 by 3 ° or with respect to the conveyor contour FIG. 1 extended by 10 °, which in turn represents a gain for improved pressure compensation with foamed gear oil.
  • the descent region ie the pressure range of this conveying contour, extends from the angular point 36 at 118 ° to the angular point 38 at 168 °, in which the conveying contour in turn in the passes next small circle area.
  • the inflection point of the Hubkonturfunktion in the descent area is arranged at angle point 40 at 141.7 ° and is thus from the inflection point at the angle 34 by 104 °, which is about 3.5 times the wing pitch of 30 ° in the 12-wing pump, spaced .
  • the turning point 40 in the descent region, ie in the pressure range is spaced in the direction of rotation with respect to the next turning point at the angular point 42 by about 2.5 times the wing pitch of 30 °.
  • the difference in great circle length to wing pitch is now 22 ° to 6 ° for the standard 10 wing contour and 13 ° to the improved 10 wing contour FIG. 2 ,
  • the compression area may be opposite to the shortened compression area FIG. 2 even be extended by 3 °.
  • the inflection points in the transition functions of the stroke contour thus have a factor x.5 of the wing pitch, which is the basis of a good overlap of under wing and wing pressure pulsation.
  • the aim of the invention is to make the available angle in the great circle area as long as possible, since the noise in foamed gear oil is dominated mainly by the pressure compensation operations and not by the geometrically caused volumetric flow pulsation.
  • the compression area is slightly shorter than the intake area, and the turning points are minimally a little further rotated as a pair.
  • FIG. 4 is the stroke contour function of the 12-wing contour FIG. 3 shown with extended case over the rotation angle.
  • point 50 corresponds to point 30 in FIG. 3
  • point 54 at about 66 ° begins the great circle area 56.
  • the great circle area 56 reduces the wing stroke constant with the so-called case to the point 58 (point 36 in FIG. 3 ), in which then the contour drop 60 to the point 62 (point 38 in FIG. 3 ).
  • point 62 then begins the small circle region 64, which extends to point 66. Thereafter, the contour increase begins again in the same manner as from point 50.
  • the great circle region 56 could be decidedly extended compared to the small circle region 64, which here now has an area in the case of the 12-wing pump extending from 30 ° minus 6 °.
  • FIG. 5 is the function of deriving the wing lift according to the angle of rotation of the contour FIG. 3 shown above the angle of rotation.
  • the increase in contour 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 lift after the angle of rotation to the point 74 (point 32 in FIG. 3 ) decreases steadily again.
  • the transition to the great circle region, the derivative of which is represented by the course of line 76 then takes place.
  • the great circle area 76 goes to point 78 (point 36 in FIG FIG.
  • FIG. 6 is the derivative of the cell volume according to the angle of rotation of the contour FIG. 3 shown above the angle of rotation.
  • a progressive increase in cell volume to point 100 and then a degressive increase in cell volume to point 102 characterize the aspiration process. Thereafter, the volume is then reduced slightly steadily in the great circle area by the case, until then from the point 104 of the actual compression process with progressive volume decrease to point 106 and then with degressive volume decrease takes place to the point 108. Thereafter, when passing through the petty rice region, an increase in volume of a progressive nature up to the point 110 occurs again, the process described here repeating itself for the second time.

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

Claims (5)

  1. Pompe à palettes ou pompe cellulaire à rouleaux comprenant un contour de refoulement à double course, le contour de refoulement présentant au moins une région croissante qui constitue une région d'aspiration, au moins une région de grand cercle qui constitue une première région de séparation, au moins une région décroissante qui constitue une région de pression et au moins une région de petit cercle qui constitue une autre région de séparation, et la pompe présentant à l'intérieur du contour de refoulement un rotor avec des palettes déplaçables radialement ou des rouleaux dans des fentes radiales, caractérisée en ce que la plage angulaire du grand cercle du contour de refoulement est supérieure à la plage angulaire de la région décroissante et en ce que la plage angulaire de la région croissante, appelée région d'aspiration, est supérieure à la plage angulaire de la région décroissante.
  2. Pompe selon la revendication 1, caractérisée
    en ce que
    - pour une pompe avec 10 palettes, la région de grand cercle vaut essentiellement 49°, la région croissante vaut essentiellement 54°, la région décroissante vaut essentiellement 47° et la région de petit cercle vaut essentiellement 30°,
    - pour une pompe avec 12 palettes, la région de grand cercle vaut essentiellement 52°, la région croissante vaut essentiellement 54°, la région décroissante vaut essentiellement 50° et la région de petit cercle vaut essentiellement 24°.
  3. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que la région de grand cercle est supérieure à la région de petit cercle.
  4. Pompe selon la revendication 2 ou 3, caractérisée en ce que dans le cas de la pompe à 12 palettes, les points d'inflexion de la fonction du contour de course dans la direction de la région croissante vers la région décroissante présentent approximativement une distance angulaire de 3,5 x la division des palettes (division des palettes = 30°) et les points d'inflexion de la fonction de contour de course dans la direction de la région décroissante vers la région croissante présentent approximativement une distance angulaire de 2,5 x la division des palettes.
  5. Pompe selon la revendication 2 ou 3, caractérisée en ce que dans le cas de la pompe à 10 palettes, les points d'inflexion de la fonction de contour de course sont décalés par rapport à un contour dit de refoulement standard pour 10 palettes selon la figure 1, d'environ 3° dans le sens de rotation.
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 EP1642030A2 (fr) 2006-04-05
EP1642030B1 true EP1642030B1 (fr) 2016-04-13
EP1642030B2 EP1642030B2 (fr) 2019-12-04

Family

ID=33521180

Family Applications (1)

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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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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
DE2438707A1 (de) 1973-10-03 1975-04-10 Abex Corp Drehschieberstroemungsmaschine
DE68905742T2 (de) 1988-10-05 1993-10-21 Vickers Inc Leistungsantriebselement.
DE4327106A1 (de) 1993-08-12 1995-02-16 Salzkotten Tankanlagen Flügelzellenpumpe

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US2731919A (en) * 1956-01-24 Prendergast
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
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
DE19626211C2 (de) * 1996-06-29 2002-03-14 Luk Fahrzeug Hydraulik Flügelzellenpumpe
EP0851123B1 (fr) * 1996-12-23 2003-07-09 LuK Fahrzeug-Hydraulik GmbH & Co. KG Pompe à palettes
DE19710378C1 (de) 1996-12-23 1998-03-12 Luk Fahrzeug Hydraulik Flügelzellenmaschine, insbesondere Flügelzellenpumpe
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

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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
DE2438707A1 (de) 1973-10-03 1975-04-10 Abex Corp Drehschieberstroemungsmaschine
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CN101052806B (zh) 2010-12-08
US7922469B2 (en) 2011-04-12
DE102004030478A1 (de) 2005-01-20
EP1642030A2 (fr) 2006-04-05
US20070128065A1 (en) 2007-06-07
JP2007524027A (ja) 2007-08-23
WO2005001289A2 (fr) 2005-01-06
KR20060032597A (ko) 2006-04-17
CN101052806A (zh) 2007-10-10
JP4653739B2 (ja) 2011-03-16
KR101162780B1 (ko) 2012-07-04
EP1642030B2 (fr) 2019-12-04
WO2005001289A3 (fr) 2007-03-22

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