EP2633194A2 - Pompe à palettes - Google Patents

Pompe à palettes

Info

Publication number
EP2633194A2
EP2633194A2 EP11782528.1A EP11782528A EP2633194A2 EP 2633194 A2 EP2633194 A2 EP 2633194A2 EP 11782528 A EP11782528 A EP 11782528A EP 2633194 A2 EP2633194 A2 EP 2633194A2
Authority
EP
European Patent Office
Prior art keywords
vane
pump
pump housing
rotor shaft
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.)
Withdrawn
Application number
EP11782528.1A
Other languages
German (de)
English (en)
Inventor
Franz Pawellek
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.)
Nidec GPM GmbH
Original Assignee
Geraete und Pumpenbau GmbH Dr Eugen Schmidt
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 Geraete und Pumpenbau GmbH Dr Eugen Schmidt filed Critical Geraete und Pumpenbau GmbH Dr Eugen Schmidt
Publication of EP2633194A2 publication Critical patent/EP2633194A2/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Withdrawn legal-status Critical Current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
    • 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
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
    • 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
    • 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
    • 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
    • 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

Definitions

  • the invention relates to a vane pump with a mounted in a pump housing, driven by a shaft rotor, a plurality of radially displaceably mounted in this rotor wing plates and a surrounding the rotor and the wing plates outer ring, this either directly in the pump housing, or in a predetermined in the pump housing along Lanes moveable collar is arranged.
  • a suction kidney and on the other hand arranged a pressure kidney offset by 180 ° to this.
  • EP 1 043 503 A2 now describes a further design of an adjustable vane pump with a pivotally mounted adjusting ring. Also in this design, the wing plates are pressed solely by, in the rotation of the rotor acting on the radially slidable in the bearing slots of the rotor wing plates acting centrifugal force against the outer ring, which in turn has the disadvantages already described result.
  • the seal on the outer ring is increased due to the use of synchronizing rings, especially in the lower speed range.
  • This embodiment is very production intensive, costly, susceptible to wear and also very “sensitive”, that is susceptible to interference with the particles carried by the pumped medium.
  • the respective vane pump then pumps the delivery volume flow as a positive displacement pump from the suction kidney into the pressure kidney.
  • Another design of a positive displacement pump, with such enlarged displacement chambers has also been described by the applicant in DE 10 2005 017 834 A1.
  • a major disadvantage of these aforementioned types of vane pumps of the current state of the art is that at drive speeds in the range of 4500 U / min to over 6000 U / min (eg when using these vane pumps as directly driven by the crankshaft of an automotive engine oil pumps) Filling the Flugungsellen (pump chambers) incomplete, with all the resulting disadvantages, including high power losses, increased noise, increased wear and the like more.
  • the object of the invention is therefore to develop a novel vane pump, which eliminates the aforementioned disadvantages of the prior art, which reduces friction and leakage losses, with minimal outer diameter optimal flow filling and emptying of Pumpenkammem, in the lower and in the upper Guaranteed speed range, while significantly reducing power losses, especially minimized friction losses, also manufacturing technology is easy to manufacture and assemble and significantly reduces manufacturing costs, at the same "particle insensitive", minimizes wear of the assemblies, increases reliability and durability and is characterized by a low noise Even at high speeds, it offers a high specific volume flow with high volumetric efficiency both at low and at high speeds.
  • a vane pump with a pump housing (1) and a rotor shaft (12), wherein the rotor shaft (12) consists of a drive shaft (2) mounted in the pump housing (1) and a rotor hollow shaft (24) connected to the drive shaft (2) ), wherein radially in the wall of the hollow rotor shaft (24) radial bearing grooves (4) are arranged in which radially by the hollow rotor shaft (24) protruding wing plates (5) are mounted radially displaceable, wherein the hollow rotor shaft (24) with the wing plates ( 5) is enclosed by the cylinder jacket of an inner cylinder (6), which is arranged in a control slide (7) which is displaceably or pivotally mounted in the pump housing (1) along predetermined paths, with an inlet channel (8) arranged in the pump housing (1) the Einströmniere / n (9) arranged on one or both sides of the adjusting slide (7) in the / the side walls of the pump housing (1) opens / lead, with a eben
  • the vane rotor (3) formed by the inventive arrangement of the copegelplatten Operationssstege (14) on the hollow rotor shaft (24) causes on the one hand, due to the leadership of the wing plates in accordance with the invention very "long" bearing grooves of the copegelplatten Operationssstege (14) a high mechanical stability even “thinner “and thus low-friction revolving wing panels.
  • the arrangement according to the invention also causes the vane pumps according to the invention with a much smaller inner cylinder diameter (diameter of the inner cylinder (6)) and much wider wing plates (5), ie larger chamber length can be built so that with minimal outer diameter always a fluidically optimal filling and emptying the pump chambers, is ensured both in the lower and in the upper speed range.
  • the seal in the wing guides is substantially increased by the "long" wing guide in the bearing grooves (4), and thereby at the same time significantly reduces the leakage losses occurring there.
  • the cylindrical rollers according to the invention can be manufactured with a significantly higher production accuracy at a significantly lower cost, since such synchronizing cylinders (15) are used, for example, as can be produced by centerless grinding with the highest manufacturing accuracy.
  • the sealing gap between the wing plates (5) and the inner cylinder (6) can be lowered very clearly to less than one tenth of a millimeter by means of the synchronizing cylinder (15).
  • the entire arrangement is at the same time sturdy and "particle-insensitive", whereby the wear of the assemblies is minimized and the reliability and service life of the vane pump according to the invention is markedly increased, whereby the vane pump according to the invention is characterized in particular by the exact guidance by a low-noise operation even at high rotational speeds.
  • the invention is also a special embodiment of the invention in which the diegelplatten Operationssstege (14) at its outer periphery by means of bearing grooves (4) provided with outer ring (17) are interconnected, wherein in, with the Einströmniere (9) provided inflow, on or On both sides of the adjusting slide (7) in the region of the outer ring (17), ie in the / the sowandung / s of the pump housing (1), the outer ring (17) surrounding overflow (16) are arranged, which is an inflow of the fluid through the overflow ( 16) from the inner chamber (s) around the outer ring (17) into the outer displacement cell (s).
  • This invention here from the diegelplatten Operationssstegen (14) and the outer ring (17) formed inner chambers of a "closed" wing rotor (3) cause in circulating wing rotor (3) even with this design of the solution according to the invention occurring in the inner chambers centrifugal pump effect, which an inflow of the conveyed medium from the inner chambers via the overflow kidneys (16) according to the invention, ie around the outer ring (17), into the outer displacement cell (s) which in the region of the outer edge of the inner chambers, the outer ring (17) in the peripheral side of the pump housing (1) arranged adjacent circumferential guide groove (27), which merges into the overflow (16),
  • a highly effective inflow of the delivery medium from the inner chambers via the circumferential guide groove (27) into the overflow kidney (16) and from there into the outer displacement cell (s) is ensured.
  • FIG. 1 the vane pump according to the invention as
  • FIG. 2 the vane pump according to the invention as
  • FIG. 3 the vane pump according to the invention as
  • Free-chamber pump with a linearly movable adjusting slide 7 in radial section at D-D according to Figure 4;
  • FIG. 4 the vane pump according to the invention as
  • FIG. 5 the vane pump according to the invention as
  • FIG. 6 the vane pump according to the invention as
  • Free-chamber pump with a pivotable lock slider 7 in radial section Free-chamber pump with a pivotable lock slider 7 in radial section.
  • the rotor shaft 12 consists of a drive shaft 2 mounted in the pump housing 1 and a rotor hollow shaft 24 connected to the drive shaft 2.
  • a cylinder guide 13 is arranged, in which a freely rotating, with the adjacent modules not rigidly connected synchronizing cylinder 15 is guided,
  • Essential to the invention is that on the hollow rotor shaft 24 rigid wing-shaped, in the wall of the rotor hollow shaft 24 arranged bearing grooves 4 associated, in the region of the bearing grooves 4, the hollow shaft 24 to the approximately 0.75 to 1, 8 times the diameter of the synchronizing cylinder 15th radially superior wing plate guide webs 14 are arranged with bearing grooves 4 such that the rotor hollow shaft 24 forms a wing rotor 3 according to the invention with the diegelplatten Adjustsstegen 14.
  • the Lümuten 4 lie in the wall of the hollow rotor shaft 24 in the plane of the bearing grooves 4 of the respective associated rempligelplatten Operationssstege 14 and also pass directly into this, so that arranged in the bearing grooves 4 of the diegelplatten Resultssstege 14 of the wing rotor 3 wing plates. 5 extending into the cylinder guide 13, wherein the arranged in the bearing grooves 4 of the vane rotor 3 wing plates 5 both "inside” on the synchronizing cylinder 15 as well as “outside” rest on the inner cylinder 6 of the adjusting slide 7.
  • the very "long" wing plate guide webs 14 act simultaneously as a centrifugal pump in conjunction with the novel radially arranged in the inner cylinder 6 outflow openings 10.
  • the inventive use of 1 mm thick wing plates also has the advantage that the centrifugal force and thus simultaneously occurring on the inner cylinder 6 friction torque and thus at the same time the friction losses can be significantly reduced.
  • the arrangement according to the invention makes it possible to construct the vane pumps according to the invention with a substantially smaller inner cylinder diameter (diameter of the inner cylinder 6 and, at the same time, substantially laterally wider vane rotors 3, with vane plates 5 arranged in the vane guide webs 14, i.e. with a larger chamber length.
  • the friction losses can also be significantly reduced even by reducing the number of wing plates in the vane pumps according to the invention.
  • the seal in the wing guides is increased by the high wing guide and thereby also significantly reduces the volumetric losses occurring there.
  • the invention according to the invention in the cylinder guide 13 rotating synchronizing cylinder 15 takes over in the present invention, the task of the synchronizer rings (lifting rings).
  • Such cylindrical rollers can be manufactured with a much higher manufacturing accuracy at significantly lower cost.
  • Sealing gap between the wing plates 5 and the inner cylinder 6 to be significantly reduced to less than a tenth of a millimeter over the prior art. Since the leakage current behaves proportional to the 3rd power of the gap height, this substantial reduction of the sealing gap between the wing plates 5 and the inner cylinder 6 has very significant effects on the leakage flow at the sealing gap between the wing plates 5 and the inner cylinder 6 relative to those at these locations in the state the technology occurring leakage current.
  • the diegelplatten arrangementsstege 14 are connected to each other at its outer periphery by means of bearing grooves 4 outer ring 17, wherein in the Einströmniere 9 provided inflow, one or both sides of the lock slide 7 in Area of the outer ring 17, ie in the / the side wall / s of the pump housing 1, the outer ring 17 surrounding Matterströmnieren 16 are arranged, which is an inflow of the pumped medium via the overflow 16 from the / the inner chamber / n around the outer ring 17 around in the outer / n Verdrängerzel! e / n enable.
  • the inner chambers formed in this embodiment of the inventive solution of the rempligelplatten Operationssstegen 14 and the outer ring 17 cause, with rotating vane 3, occurring in these inner chambers centrifugal pumping effect, which is an inflow of the pumped medium from the / the inner chamber (s) via the invention overflow 16, ie around the outer ring 17, into the outer displacement cell (s).
  • a circumferential guide groove 27 is arranged, which merges into the overflow 16 and so a highly effective inflow of the fluid from the / the inner chamber / n on the circumferential guide groove 27 in the overflow kidney 16 and from there into the outer / n displacement cell / n causes.
  • the inventive solution causes by means of the combinatorial effect, which results from the superimposition of an internal centrifugal pump according to the invention and an external displacement pump, that the displacement cells in the entire speed range always optimally and completely, ie gas bubbles, are filled.
  • FIG. 2 shows the vane-cell pump according to the invention constructed as a double-chamber pump from FIG. 1, with a linearly movable adjusting slide 7 in a side view in section in A-A (according to FIG. 1).
  • the pump housing 1 is constructed in several parts, and consists of a spacer 18, a side plate 19 with an axle bearing 20 and a cover plate 21 with a shaft bearing 22nd
  • the bearing in the pump housing 1, provided outside the pump housing 1 with a drive wheel 23 rotor shaft 12 is formed in several pieces, the rotor hollow shaft 24 in the middle n Suite of the vane rotor 3 has an inner diameter corresponding to the inner diameter of the cylinder guide 13.
  • the number of wing plates 5 on the vane rotor 3 can be significantly reduced by the inventive solution at the same time, whereby the friction losses drop significantly.
  • the large inflow openings, the large chambers, as well as the large outflow openings 10 thereby ensure that the vane pump according to the invention "particle insensitive" works.
  • the vane pump according to the invention is also easy to manufacture and assemble in terms of manufacturing technology, the manufacturing costs have been significantly reduced compared to the designs of the prior art.
  • the present solution is characterized not only by a very low wear, high reliability and a long life, but also by a low-noise operation both at low, as well as at high speeds, while ensuring at the same time a high specific volume flow with high volumetric efficiency both at low and at high speeds (in the range of 4,500 rev / min to over 6,000 rev / min).
  • FIG. 3 now shows a further embodiment of the vane cell pump according to the invention, here as a free-chamber pump, in a radial section in D-D according to FIG. 4, again with a linearly movable adjusting slide 7.
  • a rotatably connected to the drive shaft 2 vane rotor 3 is arranged in a pump housing 1 on a drive shaft 2.
  • the drive shaft 2 is constructed in one piece with the aircraft rotor 3 as a rotor shaft 12.
  • the rotor shaft 12, in the region of the vane rotor 3 completely or partially as a hollow rotor shaft 24, with a in the Rotor hollow shaft 24 arranged cylinder guide 13 is formed, wherein the vane rotor 3 has wing-shaped, radially extending wing plate guide webs 14 with bearing grooves 4, which extend into the cylinder guide 13. In these bearing grooves 4 of the vane rotor 3 radially displaceable wing plates 5 are mounted.
  • the vane rotor 3 and the wing plates 5 are surrounded by a cylindrical inner cylinder 6 of a locking slide 7, this lock slide 7 is mounted linearly displaceable in the present embodiment along predetermined paths in the pump housing 1, wherein one or both sides of the adjusting slide 7 in the side walls of the pump housing. 1 is arranged in a arranged in the pump housing inlet channel 8 opening Einströmniere / n 9 is / are.
  • Essential to the invention is that in the cylinder guide 13, a synchronizing cylinder 15 is arranged, and arranged in the bearing grooves 4 wing plates 5 abut both the synchronizing cylinder 15 as well as on the inner cylinder 6 of the adjusting slide 7, wherein the pump working side opposite Einströmniere 9, i. offset by 180 °, arranged / n outflow / en 10 is disposed in the inner cylinder 6 of the control slide 7 is / are.
  • the diegelplatten Operationssstege 14 on its outer circumference not by means of an outer ring 17 are interconnected, and the side of the lock slider 7, i. in the side wall of the pump housing 1, no overflow 16 are arranged.
  • FIG. 4 the vane-cell pump according to the invention, constructed as a free-chamber pump, is shown in side view in section at C-C according to FIG.
  • the pump housing 1 is constructed in several parts in this embodiment of the invention, and consists of a spacer 18, a side plate 19 with an axle bearing 20 and a cover plate 21 with a shaft bearing 22nd
  • the rotor shaft 12 provided outside the pump housing 1 with a sprocket drive wheel 23 is formed in several pieces and on the one hand consists of a rotor hollow shaft 24 mounted in the pump housing 1, whose inner diameter in the center region of the vane rotor 3 corresponds to the inner diameter of the cylinder guide 13.
  • the cylinder guide 13 is structurally formed in this design, that in the free end of the hollow rotor shaft 24 with the inner diameter of the cylinder guide 13 rotatably a bearing ring 25 is arranged.
  • FIG. 6 now shows a vane pump according to the invention in FIG.
  • the friction and thus the wear of the modules could be minimized, and thereby the reliability and life of the vane pump according to the invention can be significantly increased.
  • the present solution is also characterized by a very quiet running both at low, as well as at high speeds and at the same time ensures a high specific flow rate high volumetric efficiency at both low and high speeds (ranging from 4,500 rpm to over 6,000 rpm).

Landscapes

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

Abstract

L'invention concerne une pompe à palettes présentant un rotor monté dans un carter de pompe et entraîné par un arbre, plusieurs plaques de palette montées dans ce rotor de façon à pouvoir coulisser radialement et une bague extérieure entourant le rotor et les plaques de palette, cette bague étant disposée soit directement dans le carter de pompe soit dans une bague de réglage pouvant être déplacée dans le carter de pompe le long de bandes prédéfinies. L'invention a pour but de développer une pompe à palettes qui réduit entre autres les pertes par frottement et pertes par fuite, qui garantit, avec un diamètre externe minimal, un remplissage et un vidage optimaux au niveau de l'écoulement des chambres de pompe, dans la plage de régimes supérieure comme dans la plage de régimes inférieure, qui réduit alors sensiblement les puissances de perte, qui peut en plus être fabriquée et montée facilement au niveau de la technique de fabrication et qui réduit sensiblement les coûts de production, qui est en même temps "insensible aux particules", qui rend minimale l'usure des ensembles, qui garantit la fiabilité et la durée de vie, ainsi qu'un débit volumique de transport spécifique élevé avec un grand rendement volumétrique aussi bien à des régimes faibles qu'à des régimes élevés. La pompe à palettes selon l'invention se caractérise en particulier en ce que, dans l'arbre creux de rotor (24), est disposé un guide-cylindre (13), dans lequel est guidé un cylindre de synchronisation (15) tournant librement, relié de façon non rigide aux ensembles voisins, des nervures de guidage de plaque de palette (14) en forme d'ailette, attribuées aux rainures de palier (4) disposées dans la paroi de l'arbre creux de rotor (24) et dépassant radialement dans la zone de ces rainures de palier (4) de l'arbre creux de rotor (24) d'environ 0,75 jusqu'à 1,8 fois le diamètre du cylindre de synchronisation (15), étant disposées avec des rainures de palier (4) de façon rigide sur l'arbre creux de rotor (24), de telle sorte que l'arbre creux de rotor (24) forme un rotor de palette (3) avec les nervures de guidage de plaque de palette (14), et en ce qu'un orifice/des orifices (10) continu(s) et agencé(s) radialement par rapport au cylindre intérieur (6) est/sont disposé(s) dans le coulisseau de réglage (7), lesquels orifices font face côté pompe au(x) dispositif(s) d'admission (9) disposé(s) dans la/les paroi(s) latérale(s) du carter de pompe (1).
EP11782528.1A 2010-06-04 2011-05-31 Pompe à palettes Withdrawn EP2633194A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010022677.7A DE102010022677B4 (de) 2010-06-04 2010-06-04 Flügelzellenpumpe
PCT/DE2011/001140 WO2011150917A2 (fr) 2010-06-04 2011-05-31 Pompe à palettes

Publications (1)

Publication Number Publication Date
EP2633194A2 true EP2633194A2 (fr) 2013-09-04

Family

ID=44973713

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11782528.1A Withdrawn EP2633194A2 (fr) 2010-06-04 2011-05-31 Pompe à palettes

Country Status (6)

Country Link
US (1) US8998594B2 (fr)
EP (1) EP2633194A2 (fr)
CN (1) CN103221690B (fr)
BR (1) BR112012030739A2 (fr)
DE (1) DE102010022677B4 (fr)
WO (1) WO2011150917A2 (fr)

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CN105822889B (zh) * 2015-01-26 2021-01-29 吴小平 一种圆缺转子变容油泵
EP3350447B1 (fr) * 2015-09-14 2020-03-25 Torad Engineering, LLC Dispositif d'hélice à aubes multiples
DE102015222577A1 (de) * 2015-11-16 2017-05-18 Mahle International Gmbh Innenrotor und Pendelschieberpumpe
DE202015008501U1 (de) * 2015-12-10 2017-03-13 GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) Flügelzellenpumpe
SE1630113A1 (sv) * 2016-07-20 2018-01-21 Norlin Petrus Pumpenhet samt kompressor utan ventil
CN108302036B (zh) * 2017-01-12 2021-08-03 罗伯特·博世有限公司 叶片泵以及高压燃油泵
CN113994095A (zh) 2019-05-23 2022-01-28 皮尔伯格泵技术有限责任公司 可变排量润滑剂泵
WO2020239216A1 (fr) * 2019-05-29 2020-12-03 Pierburg Pump Technology Gmbh Pompe à lubrifiant à cylindrée variable

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Also Published As

Publication number Publication date
US8998594B2 (en) 2015-04-07
CN103221690A (zh) 2013-07-24
WO2011150917A3 (fr) 2013-08-01
WO2011150917A2 (fr) 2011-12-08
CN103221690B (zh) 2015-11-25
US20130078127A1 (en) 2013-03-28
DE102010022677B4 (de) 2016-06-30
BR112012030739A2 (pt) 2016-11-01
DE102010022677A1 (de) 2011-12-08

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