EP1861623B1 - Machine rotative à palettes, notamment pompe rotative à palettes - Google Patents

Machine rotative à palettes, notamment pompe rotative à palettes Download PDF

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Publication number
EP1861623B1
EP1861623B1 EP06806142A EP06806142A EP1861623B1 EP 1861623 B1 EP1861623 B1 EP 1861623B1 EP 06806142 A EP06806142 A EP 06806142A EP 06806142 A EP06806142 A EP 06806142A EP 1861623 B1 EP1861623 B1 EP 1861623B1
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EP
European Patent Office
Prior art keywords
vane
radially
machine
shoes
rotor
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 - Fee Related
Application number
EP06806142A
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German (de)
English (en)
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EP1861623A1 (fr
Inventor
Willi Schneider
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Joma Polytec GmbH
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Joma Polytec GmbH
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Publication date
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Publication of EP1861623A1 publication Critical patent/EP1861623A1/fr
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Publication of EP1861623B1 publication Critical patent/EP1861623B1/fr
Expired - Fee Related 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
    • 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
    • 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
    • F04C2/3445—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 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis

Definitions

  • the invention relates to a vane machine, in particular a vane pump, according to the preamble of claim 1.
  • a vane pump with an annular inner rotor known, in which a plurality of radially outwardly extending wing elements are received radially displaceable.
  • the radially inner end portions of the wing elements are supported on a non-rotatable central part, the radially outer end portions of a non-rotatable outer ring.
  • the rotor can be rotated about a rotation axis that is offset from the central axis of the central part and the outer ring. In this way, at a rotational movement of the rotor between the wing elements initially larger and then smaller again conveying cells. Due to the change in volume of the delivery cells fluid is first sucked into the delivery cells and then ejected again. The end regions of the wing elements slide on the central part or the outer ring.
  • Such a vane pump can be made simple and inexpensive.
  • the WO 2007/039136 A1 which is considered to be state of the art in accordance with Article 54 (3) EPC, shows a vane pump of similar construction, but without a pivotable outer ring.
  • the BE-393530 which is considered to be the closest prior art, discloses the features of the preamble of claim 1.
  • Object of the present invention is to provide a vane machine, which has a high efficiency and at the same time is easy and inexpensive to produce.
  • the production of the vane cell machine according to the invention is simplified by eliminating the pivoting required in a pendulum slide machine in this area, which in turn lowers their production costs.
  • the outer rotor comprises individual and separate for each wing element shoes, with which the wing members are pivotally connected, a good seal between the outer rotor and wing member is achieved in this area, which further improves the efficiency of the vane cell machine according to the invention.
  • an additional variable volume which also has an increased efficiency result.
  • An advantage is the simple adjustment of the eccentricity by acting on a pressure chamber with a fluid. In particular against the force of a return spring.
  • the vane machine is the radially outer region of a Wing element mounted pivotally on his shoe during operation and forcibly guided in the circumferential direction of the shoe.
  • a radially inner central element which further simplifies the structure of the vane cell machine according to the invention.
  • the vane pump contributes, if it includes a radially outside of the shoes arranged and non-rotatable housing portion, on which the shoes rest during operation slidably. Such sliding interaction between the shoes and the rotationally fixed housing portion allows a good seal and is still inexpensive to implement.
  • a precise positive guidance with simultaneously low frictional resistance, ease of manufacture, and, above all, easy assembly can be realized if at least one lateral edge region of a shoe is slidably guided in a guideway.
  • This can be formed for example by a lateral groove or between an outer ring and an annular step of a lateral cover member.
  • the shoes extend in the circumferential direction so far that in that area of the vane machine in which the volume of the first conveyor cells is minimal, the gap between adjacent shoes is close to zero.
  • the vane cell machine comprises at least one second delivery cell which is formed between the radially inner end region of a vane element and the inner rotor.
  • This delivery cell is of the type that is available in conventional piston pumps. As a result, the efficiency is further improved because an overall larger delivery volume is available.
  • first and second conveying conveyor cells and / or first and second sucking conveyor cells are each connected by at least one channel.
  • This channel is also advantageously present as a groove in a side cover and extends at an angle to a radius line which is greater than 0 °, in particular greater than 45 °. This avoids interactions between a wing element and the channel.
  • a vane pump carries in the FIGS. 1 to 9 Overall, the reference numeral 10.
  • the reference numeral 10 comprises a cylindrical housing 12, which consists of a pot-like part 12a and a front cover 12b.
  • a pump module 14 is arranged in the housing 12.
  • FIG. 3 shows a section III-III of FIG. 2 through a portion of a bottom 16 of the pot-like portion 12a of the housing 12.
  • the bottom 16 there are an inlet port 18 and an outlet port 20 communicating with kidney-shaped recesses 22 and 24 provided on the inside of the bottom 16, respectively.
  • a drive shaft 26 is also mounted, which passes through the cover 12 b of the housing 12 at its opposite end and there can be connected via a coupling, not shown, with a corresponding drive means.
  • the drive shaft 26 is connected to a cylindrical inner rotor 28, in which distributed over the circumference a plurality of radially extending slots 30 are present, of which in the figures, for clarity, however, not all provided with reference numerals.
  • a portion of a generally rectangular, disc-like wing member 32 is displaceable in the radial direction, but received against the inner rotor 28 in a fixed angle.
  • the radially inner end portion 34 of a vane member 32 received in the corresponding slot 30 of the vane member 32 is straight, whereas the radially outer end portion of a vane member 32 is formed as an axis-like thickening 36 of circular outer contour.
  • the longitudinal axis of this thickening 36 extends parallel to the longitudinal axis of the drive shaft 26th
  • the circularly thickened end region 36 of a wing element 32 is accommodated in a complementary recess (without reference numeral) in a shoe 38.
  • wing element 32 and shoe 38 in the radial direction (arrow R in FIG. 7 ) and in the circumferential direction (arrow U in FIG. 7 ) firmly connected to each other, but by the positive connection, the wing member 32 can be pivoted within a certain angular range relative to the shoe 38.
  • the end-side thickening 36 on the wing element 32 forms in this respect a pivot axis.
  • the shoes 38 are the same as the wing members 32 constructed identical to each other as a ring-segment-like shell parts with a common center axis. They are located on a radially inner boundary wall of an outer ring 40, which, as will be explained below, is rotatably connected to the housing 12.
  • the shoes 38 are seen in the direction of the drive shaft 26 longer than the wing members 32. So they are available with lateral edge portions 42a and 42b on the lateral edges 44 of the wing members 32 via. This protrusion of the lateral edge regions 42a and 42b is used for forced guidance of the shoes 38 in a guide track 46a or 46b.
  • the latter is formed on the one hand by the outer ring 40, seen in the direction of the drive shaft 26 as long as the shoes 38, and an annular step 48 a and 48 b, which is present in lateral cover members 50 a and 50 b, fixed to the outer ring 40 are connected.
  • the two cover elements 50a and 50b thus form the frontal boundaries of the pump module 14 (see also FIG. 4 ).
  • the shoes 38 form an outer rotor 51.
  • Front cover 50a has a suction kidney 52 and a pressure kidney 54 and a lying radially outward at the radial height of the shoes 38 suction slot 56 and a corresponding pressure slot 58.
  • Wie aus FIG. 5 5 additional groove-like and kidney-shaped recesses 60 and 62 are located on the inner side of the cover element 50a facing the wing elements 32, which are arranged radially inwardly of the suction kidney 52 or pressure kidney 54 approximately at the level of the radially inner region of the slots 30.
  • the kidney-shaped recess 60 arranged in the region of the suction kidney 52 extends over a smaller area in the circumferential direction U than the kidney-shaped recess 62 arranged in the region of the pressure kidney 54.
  • the inner kidney-shaped recess 60, the suction kidney 52, and the suction slot 56 are fluidly interconnected by groove-like and 64 also on the inside of the cover 50a facing the wing members 32 existing channels. Analogous to this are the kidney-shaped recess 62, the pressure kidney 54 and the pressure slot 58 connected by corresponding groove-like channels 66.
  • the channels 64 and 66 extend at an angle of approximately 45 ° with respect to the radius line R.
  • the unit formed by outer ring 40 and lateral cover elements 50a and 50b which is denoted by 68 and to which the shoes 38 and the wing elements 32 belong due to the forced guidance in the guide track 46, can be pivoted about an axis 70.
  • the outer ring 40 is connected to a bracket member 72, which by a spring 74 in the in FIG. 7 shown position is applied.
  • the central axis of the unit 68 is not on the central axis of the drive shaft 26, but is offset relative to this parallel.
  • the stirrup element 72 and with it the unit 68 can be pivoted against the force of the spring 74 about the axis 70 until, if appropriate, the central axis of the unit 68 and the longitudinal axis of the drive shaft 26 are concentric.
  • the stirrup element 72 has sealing surfaces 78a and 78b which cooperate slidably with the housing 12.
  • the vane pump 10 operates as follows, wherein first in FIG. 7 When the drive shaft 26 is rotated in the direction of the arrow 79, the inner rotor 28 is also rotated. As a result, the wing elements 32 are taken, and on this turn, the shoes 38, which form the outer rotor 51. Since at the in FIG. 7 shown position of the unit 68 whose central axis is offset from the axis of rotation of the drive shaft 26, resulting between outer ring 40, shoes 38, wing members 32, and inner rotor 28 first feed cells 80, the volume on a Suction side 81 initially increases and then decreases again on a pressure side 83.
  • a slot 30 between the radially inner end region 34 and the inner rotor 28 forms a second delivery cell 84, the volume of which also increases on the suction side 81 and decreases on the pressure side 83.
  • These delivery cells 84 are also filled on the suction side via the radially inner kidney-shaped recess 60, the channels 64, the suction kidney 52, and the kidney-shaped recess 22 with fluid.
  • the volume of the first delivery cells 80 and the second delivery cells 84 shrinking again on the pressure side 83, the fluid received there is forced through the pressure kidney 54 or the kidney-shaped recess 62 and the channels 66 to the kidney-shaped recess 24 and from there to the outlet 20.
  • the fluid volume 82 present between adjacent shoes 38 can escape through the pressure slot 58 to the outlet opening 20. It is how very good also from the FIGS. 6 and 7 it can be seen, the extension of the shoes 38 in Circumferential direction U selected so that in that area (reference numeral 86) of the vane pump 10, in which the volume of the first delivery cells 80 is minimal, the gap between adjacent shoes 38 is close to zero.
  • the shoes 38 cooperate with their radial outer side in a sliding manner with the inner wall of the outer ring 40. Due to the comparatively large sealing surface, a good seal is obtained between adjacent first delivery cells 80, without the need for additional sealing means, in particular no lubricants. A reduction of the sliding friction between the shoes 38 and the outer ring 40 can be achieved by an appropriate choice of material.
  • FIG. 9 the vane pump 10 is shown in a state in which the bracket member 72 is pivoted against the force of the spring 74 so that the central axis of the unit 68 and the axis of rotation of the drive shaft 26 are concentric. It can be seen that in this case the first delivery cells 80 and the second delivery cells 84 do not change the volume even with a rotation of the drive shaft 26, so that the vane pump 10 does not deliver fluid in this operating position.

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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)

Abstract

L'invention concerne une machine rotative à palettes qui comprend un rotor interne (28) et un rotor externe (51). Une pluralité d'éléments palettes (32) s'étendant radialement sépare des premières cellules transporteuses (80) les unes des autres. Les éléments palettes (32) ont une zone terminale radiale interne (34) logée de manière mobile dans la direction radiale dans le rotor interne (28) et une zone terminale radiale externe (36) logée de manière pivotante dans le rotor externe (51). Conformément à l'invention, les zones terminales radiales internes (34) des éléments palettes (32) sont logées dans le rotor interne (28) en position angulaire fixe et le rotor externe (51) comprend des sabots (38) individuels et séparés pour chaque élément palette (32), dans lesquels les éléments palettes (32) sont logés pivotants.

Claims (10)

  1. Machine rotative à palettes (10), en particulier pompe à palettes, comportant au moins un rotor intérieur (28), monté dans un carter (12), au moins un rotor extérieur (51) et une pluralité de palettes (32) s'étendant au moins sensiblement dans le sens radial, par lesquelles des premières cellules de refoulement (80) sont séparées les unes des autres et lesquelles sont reçues avec une zone d'extrémité (34) radialement intérieure dans le rotor intérieur (28) de manière mobile en translation dans la direction radiale et avec une zone d'extrémité (36) radialement extérieure dans le rotor extérieur (51) de manière pivotante, les zones d'extrémité (34) radialement intérieures des palettes (32) étant reçues dans le rotor intérieur (28) de manière au moins sensiblement fixe en position angulaire, et le rotor extérieur (51) comporte pour chaque palette (32) au moins un coussinet (38) séparé, par lequel la palette (32) est assemblée de manière pivotante, au moins une zone de bordure (42) latérale d'un coussinet (38) étant logée de manière à pouvoir glisser dans une voie de guidage (46), caractérisée en ce que ledit au moins un coussinet (38) est en appui contre la surface périphérique intérieure d'une bague extérieure (40), et en ce que la bague extérieure (40) est reliée à un élément en étrier (72) et est montée de manière à pouvoir pivoter autour d'un axe (70), une chambre de pression (76) étant prévue entre l'élément en étrier (72) et le carter (12), et l'élément en étrier (72) pouvant pivoter autour de l'axe (70) lorsque la chambre de pression (76) est sollicitée par la pression d'un fluide.
  2. Machine rotative à palettes selon la revendication 1, caractérisée en ce que l'élément en étrier (72) est sollicité par un ressort (74) dans une position dans laquelle l'axe médian de la bague extérieure (40) est décalé parallèlement à l'axe médian d'un arbre d'entraînement (26).
  3. Machine rotative à palettes selon la revendication 1 ou 2, caractérisée en ce que la zone d'extrémité (34) radialement extérieure d'une palette (32) est fixée à son coussinet (38) de manière à pouvoir pivoter en cours de service et le coussinet (38) subit un guidage forcé (46) dans la direction circonférentielle (U).
  4. Machine rotative à palettes selon l'une quelconque des revendications précédentes, caractérisée en ce qu'elle comporte une partie de carter (40), immobile en rotation et disposée radialement en dehors des coussinets (38), sur laquelle les coussinets (38) sont en appui de manière à pouvoir glisser en cours de service.
  5. Machine rotative à palettes selon l'une quelconque des revendications précédentes, caractérisée en ce que la voie de guidage (46) est formée entre une bague extérieure (40) et un épaulement (48) annulaire d'un élément de recouvrement (50) latéral.
  6. Machine rotative à palettes selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un palier de glissement des coussinets (38) fonctionne à sec.
  7. Machine rotative à palettes selon l'une quelconque des revendications précédentes, caractérisée en ce que les coussinets (38) s'étendent dans la direction circonférentielle (U) sur une distance telle que, dans la zone (86) de la machine rotative à palettes (10), dans laquelle le volume des premières cellules de refoulement (80) est minime, il se forme une fente pratiquement nulle entre des coussinets (38) adjacents.
  8. Machine rotative à palettes selon l'une quelconque des revendications précédentes, caractérisée en ce qu'elle comporte au moins une deuxième cellule de refoulement (84), qui est formée entre la zone d'extrémité (34) radialement intérieure d'une palette (32) et le rotor intérieur (28).
  9. Machine rotative à palettes selon la revendication 8, caractérisée en ce que des premières et deuxièmes cellules de refoulement (80, 84) assurant le transport et/ou des premières et deuxièmes cellules de refoulement (80, 84) assurant l'aspiration sont reliées entre elles respectivement par au moins un conduit (64, 66).
  10. Machine rotative à palettes selon la revendication 9, caractérisée en ce que le conduit (64, 66) est réalisé sous forme de rainure dans un élément de recouvrement (50a) latéral, le conduit (64, 66) s'étendant en formant avec une ligne de rayon (R) un angle supérieur à 0°, en particulier supérieur à 45°.
EP06806142A 2006-10-10 2006-10-10 Machine rotative à palettes, notamment pompe rotative à palettes Expired - Fee Related EP1861623B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2006/009765 WO2007101457A1 (fr) 2006-10-10 2006-10-10 Machine rotative à palettes, notamment pompe rotative à palettes

Publications (2)

Publication Number Publication Date
EP1861623A1 EP1861623A1 (fr) 2007-12-05
EP1861623B1 true EP1861623B1 (fr) 2010-12-08

Family

ID=38110673

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06806142A Expired - Fee Related EP1861623B1 (fr) 2006-10-10 2006-10-10 Machine rotative à palettes, notamment pompe rotative à palettes

Country Status (7)

Country Link
US (1) US7736134B2 (fr)
EP (1) EP1861623B1 (fr)
JP (1) JP5021749B2 (fr)
KR (1) KR100999214B1 (fr)
CN (1) CN101163883B (fr)
DE (1) DE502006008468D1 (fr)
WO (1) WO2007101457A1 (fr)

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WO2007039012A1 (fr) * 2005-10-06 2007-04-12 Joma-Hydromechanic Gmbh Pompe a palettes coulissantes
WO2008124174A1 (fr) * 2007-04-10 2008-10-16 Borgwarner Inc. Pompe à double aube à déplacement variable
WO2012004992A1 (fr) * 2010-07-08 2012-01-12 パナソニック株式会社 Compresseur rotatif et dispositif de cycle de refroidissement
WO2012004993A1 (fr) 2010-07-08 2012-01-12 パナソニック株式会社 Compresseur rotatif et dispositif à cycle frigorifique
US8961148B2 (en) * 2011-07-19 2015-02-24 Douglas G. Hunter Unified variable displacement oil pump and vacuum pump
CN102410214A (zh) * 2011-11-03 2012-04-11 湖南机油泵股份有限公司 中段变量高速限压的三段式压力反馈变排量叶片泵及变排量方法
EP3051134B1 (fr) 2013-09-24 2018-05-30 Aisin Seiki Kabushiki Kaisha Pompe à huile
DE102014102643A1 (de) * 2014-02-27 2015-08-27 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit Kunststoffverbundstruktur
CN104265626A (zh) * 2014-09-03 2015-01-07 上海大学 内外转子共转式叶片泵
JP6295923B2 (ja) * 2014-11-12 2018-03-20 アイシン精機株式会社 オイルポンプ
CN105351028B (zh) * 2015-11-04 2017-08-25 湖南机油泵股份有限公司 一种一级变排量叶片泵
DE102016211913A1 (de) * 2016-06-30 2018-01-18 Schwäbische Hüttenwerke Automotive GmbH Flügelzellenpumpe mit druckbeaufschlagbarem Unterflügelbereich
US10316840B2 (en) * 2016-08-29 2019-06-11 Windtrans Systems Ltd Rotary device having a circular guide ring
CN109812298A (zh) * 2019-02-19 2019-05-28 东南大学 一种气缸随转的滑片式膨胀机

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EP1931879B1 (fr) * 2005-10-06 2009-11-04 Joma-Polytec Kunststofftechnik GmbH Pompe a palettes coulissantes
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WO2007039012A1 (fr) * 2005-10-06 2007-04-12 Joma-Hydromechanic Gmbh Pompe a palettes coulissantes

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Publication number Publication date
WO2007101457A1 (fr) 2007-09-13
US7736134B2 (en) 2010-06-15
KR100999214B1 (ko) 2010-12-07
JP5021749B2 (ja) 2012-09-12
KR20080011388A (ko) 2008-02-04
CN101163883B (zh) 2014-01-08
CN101163883A (zh) 2008-04-16
EP1861623A1 (fr) 2007-12-05
US20090169409A1 (en) 2009-07-02
JP2010506074A (ja) 2010-02-25
DE502006008468D1 (de) 2011-01-20

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