EP2561230A2 - Pompe à palettes - Google Patents

Pompe à palettes

Info

Publication number
EP2561230A2
EP2561230A2 EP11715512A EP11715512A EP2561230A2 EP 2561230 A2 EP2561230 A2 EP 2561230A2 EP 11715512 A EP11715512 A EP 11715512A EP 11715512 A EP11715512 A EP 11715512A EP 2561230 A2 EP2561230 A2 EP 2561230A2
Authority
EP
European Patent Office
Prior art keywords
rotor
face
rotation
surface structure
pump 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.)
Withdrawn
Application number
EP11715512A
Other languages
German (de)
English (en)
Inventor
Andre Johanning
Hartmut Krueger
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.)
Robert Bosch GmbH
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 EP2561230A2 publication Critical patent/EP2561230A2/fr
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
    • 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
    • F04C15/0003—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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors
    • 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
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/17—Tolerance; Play; Gap

Definitions

  • the invention relates to a vane pump with a pump housing and a rotor which is arranged in a cavity of the pump housing along a rotation axis, wherein the pump housing comprises a first end face on which a second end face of the rotor is arranged opposite.
  • the vane pump includes a cylindrical pump housing defining an inner cylindrical cavity.
  • the pump housing includes an inlet port and an outlet port.
  • a rotor Arranged on an axis offset from the axis of the inner cylindrical cavity is a rotor.
  • the pump rotor is cylindrical and includes a plurality of axially extending and radially oriented narrow slots that freely slidably receive and retain a like plurality of vanes.
  • the vanes are held in close contact with the surface of the inner cylindrical cavity by a centrifugal force as the pump rotor rotates.
  • the rotor of the vane pump is axially supported by the fact that the end faces of the rotor abut against the opposite surfaces of the cavity of the pump housing.
  • an improved vane pump can be provided in that the vane pump comprises a device on a first end face of the pump housing and / or on a second end face, the pressure between the first end face of the pump housing by rotation of the rotor about an axis of rotation and the second end face of the rotor builds.
  • a friction of the rotor on an inner wall of the pump housing can be avoided, so that simply the efficiency of the vane pump is increased.
  • this reduces wear on the rotor and / or on the pump housing.
  • the device has at least one surface structure which is designed such that a distance between a surface of the surface structure and the opposite end surface decreases in the direction of rotation. In this way, simply a pressure between the end faces of the rotor and the pump housing can be constructed so that the two end faces of the pump housing and the rotor do not rub against each other.
  • the device comprises at least one compression groove, which is arranged obliquely to the rotational direction of the rotor. In this way, a pressure between the end faces of the rotor and the pump housing can also be generated, which prevents the rotor from grinding on an inner wall of the pump housing.
  • the rotor on a circumferential side to the rotation axis aligned slots, in each of which a wing is arranged, wherein arranged between the slots at least a first Verdichtungsnut and a second Verdichtungsnut.
  • the first compression groove extends in the direction of the axis of rotation of the rotor and the second compression groove in the direction of the slot. It is at one end of the second Verdichtungsnut arranged a wall which delimits the second compression groove of the slot.
  • the compression groove is formed spirally in the direction of the axis of rotation.
  • the helical formation allows the provision of a high pressure between the two end faces of the pump housing and the rotor.
  • the compression groove is bounded radially on the outside and / or inside by a further wall. In this way, the pressure generated by the compression groove can be reliably distributed over the end face of the rotor by limiting the compression groove.
  • the compression groove has a first region and a second region, wherein the second regions are helical and converge towards one another and meet in a third region. In this way, tilting of the rotor is avoided by a radially further outward pressure build-up.
  • the surface structure is convex in the direction of rotation. In this way, the pressure between the end face of the rotor and the end face of the pump housing is aerodynamically increased.
  • the surface structure comprises at least a first and a second stage, wherein the first stage and the second stage are arranged so that the distance between the first stage and the opposite end face and the second stage and the opposite end face in Direction of the rotational direction of the rotor decreases.
  • the step-shaped design allows for easy manufacturing of the vane pump.
  • the surface structure has at least one groove, which is aligned approximately in the direction of the axis of rotation of the rotor. In this way, air or another flow medium is reliably tracked into the surface structure.
  • the surface structure has at least one boundary web which delimits a region of the end surface without a surface structure and / or the surface structure with respect to a radially outer circumferential surface. In this way, the pressure generated in the surface structure can be reliably maintained in the region of the surface structure.
  • FIG. 1 is a perspective view of a vane pump with a first rotor.
  • Fig. 2 is a plan view of the first rotor
  • Fig. 3 is a plan view of a second rotor
  • Fig. 4 is a plan view of a third rotor
  • Fig. 5 is a plan view of a fourth rotor
  • Fig. 6 is a plan view of a fifth rotor
  • FIG. 7 shows a perspective view of the vane pump with a first surface structure of a sixth rotor
  • FIG. 8 shows a section along a direction of rotation of a seventh rotor through a second surface structure
  • FIG. 9 shows a section along the direction of rotation of an eighth rotor through a third surface structure
  • FIG. 10 shows a section along the direction of rotation of a ninth rotor through a fourth surface structure
  • 1 1 is a perspective view of a section of a tenth rotor with a fifth surface structure.
  • the vane pump 1 shows a perspective view of a vane pump 1.
  • the vane pump 1 comprises a drive 28, a pump housing 26 and a first rotor 10 arranged in the pump housing 26.
  • the pump housing 26 comprises a cavity 27 which is rotationally symmetrical about a cylinder axis 48 and in which the first one Rotor 10 is arranged.
  • the pump housing 26 comprises an inlet opening 52 and an outlet opening 53.
  • the first rotor 10 has an axis of rotation 21 which is offset from a cylinder axis 48 of the cavity 27.
  • the first rotor 10 is cylindrical, arranged on a rotor shaft 59 and comprises a plurality of slots 22 which extend parallel to the axis of rotation 21. In the slots 22, a respective wing 23 is arranged.
  • the cavity 27 of the pump housing 26 has a first end face 30, which is arranged opposite to a second end face 31 of the first rotor 10.
  • a plurality of compression grooves 24, 25 are arranged at the second end face 31 of the first rotor 10.
  • the compression grooves 24, 25 are disposed between the slots 22 for the wings 23 and opened to the first end face 30 of the pump housing 26 out.
  • a cross section of the compression grooves 24, 25 reduces along the course of the compression groove 24, 25 radially from the outside to the axis of rotation 21 out.
  • a first compression groove 24 is guided spirally in the direction of the rotation axis 21 as far as into a radially inner region of the second end face 31.
  • a second compression groove 25, like the first compression groove 24, is helically formed, extending in the direction of the slot 22 and terminating at a distance therefrom.
  • the first compression groove 24 is delimited from a rotor shaft 59 by a first wall 45.
  • the second compression groove 25 is separated from the slot 22 by a second wall 46.
  • the wings 23 are pressed by the centrifugal force to the outside until they abut against the pump housing 26.
  • the wings Gel 23 are adapted to slide along a pump housing inner wall 51 and to promote a fluid from the inlet port 52 to the outlet port 53.
  • the conveying medium is guided radially outwards into the compression grooves 24, 25, the compression grooves 24, 25, by their course, conveying the conveying medium radially inwards from the first rotor 10. In this case, a pressure builds up along the compression grooves 24, 25.
  • the fluid is due to the end of the compression grooves 24, 25 forced to leave the compression grooves 24, 25 and exit in the direction of the first end face 30 of the pump housing.
  • the conveying medium in the compression grooves 24, 25 is subjected to a pressure which acts as a force relative to the first end face 30 of the pump housing 26. In this way, it is ensured that the first rotor 10 is mounted axially spaced from the first end face 30 of the pump housing 26. This has the advantage that a sliding of the first rotor
  • FIGS. 2 to 7 show various principal embodiments of compression grooves in a rotor 10, 12, 13, 14, 15, 16. The direction of rotation of the
  • Rotors 10, 12, 13, 14, 15, 16 are each clockwise.
  • FIG. 2 shows a top view of the first rotor 10, which comprises a plurality of compression grooves 24, 25 on the second end face 31.
  • the first rotor 10 has a driver 61 for transmitting the torque from the rotor shaft 59 to the first rotor 10.
  • the compression grooves 24, 25 are formed spirally and promote a fluid from the radially outer peripheral surface 34 inwardly. At the end of the compression grooves 24, 25, the volume flow of the pumped medium through the end of the compression groove 24, 25 in the direction of the first end face 30 of the pump housing 26 is derived.
  • FIG. 3 shows a plan view of a second rotor 13.
  • the second rotor 13 comprises a plurality of compression grooves 54 which are shortened in comparison to the first compression grooves 24 shown in FIG. 2 and terminate in the diameter of the radially inward end of the slots 22.
  • the second rotor 13 has the first radially inner, arranged to the third compression grooves 54
  • the first wall 45 delimits the third compression grooves 54 from the rotor shaft 59.
  • the second rotor 13 has the second wall 46, which delimits the third compression grooves 54 from the slots 22.
  • the pressure 10 generated by the third compression grooves 54 is radially outwardly as shown in Fig. 2, derived in the direction of the first end face 30 of the pump housing 26, so that the second rotor 13 is tiltably mounted axially relative to the first rotor 10.
  • FIG. 4 shows a plan view of a third rotor 14, which comprises a plurality of fourth sealing grooves 55.
  • the conveying medium is conveyed radially from the inside to the outside, the third rotor 14 having no walls 45, 46, as shown in FIGS. 1 to 3. having.
  • the fourth compression grooves 55 are oriented in opposite directions to the direction of compression opposite the compression grooves 20 24, 25, 54 shown in FIGS. 2 to 3.
  • a promotion of the conveying medium radially from the inside out provides a tilt-stable axial bearing of the third rotor 14.
  • FIG. 5 shows a plan view of a fourth rotor 15, which is similar to the one shown in FIG.
  • 4 fourth rotor 14 has fifth compression grooves 56, which are executed compared to the fourth compression grooves 55 shortened.
  • the fourth rotor 15 has a radially outer third wall 47. This ensures a reliable pressure buildup with respect to the first end face 30 of the pump housing 26 and prevents
  • FIG. 6 shows a plan view of a fifth rotor 16, which has a plurality of sixth compression grooves 57, which comprise a radially outer first region 42 and a radially inner second region 43.
  • the two areas 42, 43 are spirally formed, wherein the two areas 42, 43 run towards each other and meet in a third area 44.
  • the sixth compression grooves 57 are bounded by the second wall 46 in the region of the slots 22, so that the first and second regions 42, 43 do not form a third region 44 on the third slots 22.
  • the delivery of the pumped medium takes place both radially from the inside to the outside and radially from outside to inside. In this case, the resulting pressure in the direction of the first end face 30 of the pump housing 26 in the third region 44 is deflected.
  • the sixth compression grooves 57 have only one of the two regions 42, 43, the pressure generated in the sixth compression grooves 57 is deflected on the second wall 46 in the direction of the first end face 30 of the pump housing 26.
  • the embodiment of the sixth compression grooves 57 of the fifth rotor 16 has the advantage that a higher pressure than an inward-outward conveyance, as shown in FIGS. 4 to 5, can be provided, while simultaneously the tilting stability of the fifth rotor 16 is increased compared to the embodiment shown in Fig. 2 to Fig. 3.
  • FIG. 7 shows a perspective view of a sixth rotor 12.
  • the sixth rotor 12 has a first surface structure 33 on its second end face 31.
  • the first surface structure 33 contains individual segments 58, which are separated from each other by a respective groove 32.
  • the groove 32 is aligned approximately in the direction of the axis of rotation 21 of the sixth rotor 12, and the first surface structure 33 is disposed radially outward on the second end face 31.
  • the first surface structure 33 is interrupted by the slots 22.
  • the first end face 30 of the pump housing 26 is arranged.
  • a surface of the first surface structure 33 is wedge-shaped, wherein the distance decreases in the direction of rotation to the first end face 30.
  • FIG. 8 shows a section along the direction of rotation of a seventh rotor 18 through a second surface structure 37, the segments 58 of which are separated from one another by the groove 32.
  • the second surface structure 37 is concave and symmetrical to the grooves 32.
  • the symmetrical design of the second surface structure 37 allows rotation of the rotor in both rotational directions, wherein the distance of the surface of the second surface structure 37 decreases in the rotational direction between the first end face 30 of the pump housing 26 and the second end face 31 with the second surface structure 37.
  • FIG. 9 shows a section along the direction of rotation of an eighth rotor 19 through a third surface structure 38.
  • the third surface structure 38 comprises individual segments 58, which are separated by the groove 32, respectively.
  • a surface of the surface structure 38 is concave, wherein a single segment 58 of the surface structure 38 has an approximately wedge-shaped basic shape.
  • the direction of rotation is fixed with respect to the second surface structure 37 in the case of the third surface structure 38, but more segments 58 of the surface structure 38 can be arranged on the second end surface 31 on the eighth rotor 19 due to the narrower design of the individual segments 58. In this case, the distance between the surface of the third surface structure 38 along the direction of rotation of the eighth rotor 19 with respect to the first end face 30 of the pump housing 26 decreases.
  • the fourth surface structure 39 comprises a first stage 40 and a second stage 41.
  • the first stage 40 and the second stage 41 are thus at the end face 31 of the ninth rotor 20 is arranged such that a distance of the first step 40 to the first end face 30 and the distance of the second step 40 to the first end face 30 decreases in the direction of rotation.
  • the formation of the fourth surface structure 39 by means of steps 40, 41 enables a simple and cost-effective production of the fourth surface structure.
  • Structure 39 of the ninth rotor 20 Individual segments 58 of the fourth surface structure 39, each comprising a first and a second step 40, 41, are separated by the groove 32.
  • FIG. 11 shows a perspective view of a section of a tenth rotor 17.
  • the tenth rotor 17 comprises a fifth surface structure 49.
  • the fifth surface structure 49 is similar to the first surface structure 33 shown in FIG.
  • the fifth surface structure 49 in this case comprises individual segments 58, which are separated from one another by the grooves 32.
  • the fifth surface structure 49 is wedge-shaped, wherein a wedge-shaped region 50 is separated by an inner first boundary web 35 and by a radially outer second boundary web 36 from a region 60 of the end face 31, in which no surface structure is arranged. Furthermore, the second radially outer boundary web 36 separates the wedge-shaped region 50 from a peripheral surface 34 of the tenth rotor 17.
  • the boundary webs 35, 36 prevent the discharge of the fluid from the wedge-shaped region 50, so as to increase the pressure between the fifth surface structure 49 and the first end face 30 of the pump housing 26 build.
  • the wedge-shaped region 50 is aligned so that decreases in the rotational direction of the distance of the surface of the wedge-shaped region 50 to the opposite first end face 30 of the pump housing 26.
  • the compression grooves and the surface structures are each disposed on the rotor.
  • the compression grooves or the surface structure are on the first end face of the pump housing.

Landscapes

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

Abstract

L'invention concerne une pompe à palettes (1) comprenant un carter de pompe (26) et un rotor (10) disposé dans une cavité (27) du carter de pompe (26) le long d'un axe de rotation (21), le carter de pompe (26) comprenant une première face frontale (30) en vis-à-vis de laquelle est disposée une deuxième face frontale (31) du rotor (10). Selon l'invention, un dispositif (24, 25) est disposé sur la première face frontale (30) du carter de pompe (26) et/ou sur la deuxième face frontale (31) du rotor (10), ce dispositif (24, 25) établissant une pression entre la première face frontale (30) du carter de pompe (26) et la deuxième face frontale (31) du rotor sous l'effet d'une rotation du rotor (10) autour de l'axe de rotation (21).
EP11715512A 2010-04-22 2011-04-18 Pompe à palettes Withdrawn EP2561230A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010028061 DE102010028061A1 (de) 2010-04-22 2010-04-22 Flügelzellenpumpe
PCT/EP2011/056085 WO2011131598A2 (fr) 2010-04-22 2011-04-18 Pompe à palettes

Publications (1)

Publication Number Publication Date
EP2561230A2 true EP2561230A2 (fr) 2013-02-27

Family

ID=44625926

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11715512A Withdrawn EP2561230A2 (fr) 2010-04-22 2011-04-18 Pompe à palettes

Country Status (4)

Country Link
EP (1) EP2561230A2 (fr)
CN (1) CN103038452A (fr)
DE (1) DE102010028061A1 (fr)
WO (1) WO2011131598A2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2498816A (en) 2012-01-27 2013-07-31 Edwards Ltd Vacuum pump
JP6382877B2 (ja) * 2016-03-24 2018-08-29 大豊工業株式会社 ベーンポンプ
EP3957822B1 (fr) * 2020-08-20 2023-12-13 GKN Sinter Metals Engineering GmbH Agencement de pompe
EP3957823B1 (fr) * 2020-08-20 2023-11-08 GKN Sinter Metals Engineering GmbH Agencement de pompe
CN114941623A (zh) * 2022-05-28 2022-08-26 江苏大学 一种罗茨真空泵

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2012874A (en) * 1977-12-07 1979-08-01 Seiko Instr & Electronics Rotary Positive-displacement Fluid-machines
DE2938276A1 (de) * 1979-09-21 1981-04-09 Robert Bosch Gmbh, 7000 Stuttgart Fluegelzellenverdichter
JPS56106088A (en) * 1980-01-29 1981-08-24 Matsushita Electric Ind Co Ltd Rotary type fluid equipment
DE3014519A1 (de) * 1980-04-16 1981-10-22 Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt Drehkolbenmaschine, insbesondere zellenpumpe
DE10158146A1 (de) * 2001-11-28 2003-06-18 Horn Gmbh & Co Kg Selbstansaugende Hybridpumpe
US7946833B2 (en) 2007-12-05 2011-05-24 GM Global Technology Operations LLC Variable displacement vane pump
EP2075469A2 (fr) * 2007-12-25 2009-07-01 Panasonic Electric Works Co., Ltd. Pompe à palettes
DE102008036273B4 (de) * 2008-08-04 2013-09-26 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Rotationskolbenpumpe mit Taschen für Schmiermittel

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2011131598A2 *

Also Published As

Publication number Publication date
WO2011131598A2 (fr) 2011-10-27
CN103038452A (zh) 2013-04-10
WO2011131598A3 (fr) 2013-01-31
DE102010028061A1 (de) 2011-10-27

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