EP1318304B1 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
EP1318304B1
EP1318304B1 EP20020026051 EP02026051A EP1318304B1 EP 1318304 B1 EP1318304 B1 EP 1318304B1 EP 20020026051 EP20020026051 EP 20020026051 EP 02026051 A EP02026051 A EP 02026051A EP 1318304 B1 EP1318304 B1 EP 1318304B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
vane
medium flow
valve
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
EP20020026051
Other languages
German (de)
English (en)
Other versions
EP1318304A2 (fr
EP1318304A3 (fr
Inventor
Johann Merz
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 Automotive Steering GmbH
Original Assignee
ZF Lenksysteme 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 ZF Lenksysteme GmbH filed Critical ZF Lenksysteme GmbH
Publication of EP1318304A2 publication Critical patent/EP1318304A2/fr
Publication of EP1318304A3 publication Critical patent/EP1318304A3/fr
Application granted granted Critical
Publication of EP1318304B1 publication Critical patent/EP1318304B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • 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
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the 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
    • 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

Definitions

  • the invention relates to a vane pump for generating a pressure medium flow to a consumer according to the preamble of claim 1.
  • a generic vane pump is out of the DE 41 36 150 A1 known.
  • the generic vane pump has a rotatably mounted cam ring in a pump housing. Inside the cam ring, a rotor is arranged, which has a plurality of slots, which are directed substantially radially outwards. In the slots wings are movably guided whose movement is controlled by the inner contour of the cam ring upon rotation of the rotor. Between the cam ring, the rotor and the end faces of laterally adjacent housing parts working chambers are formed. The working chambers each have a suction and pressure zone. In each of the two suction zones is an inlet chamber and in each of the two pressure chambers an outlet chamber arranged. By a, equipped with three control edge pairs flow control valve, the two pressure medium flows from the two outlet chambers at low pump speeds are connected in parallel and at higher pump speeds in series.
  • the from the DE 41 36 150 A1 known pump is used for example for a power steering system of a motor vehicle.
  • vane pumps are equipped with a flow control valve. This is to ensure that the liquid flow to the auxiliary power plant at a high pump speed corresponds to the liquid flow at a low pump speed.
  • an adjustable vane pump comprising a housing, a cam ring, a rotor with slots in which wings are guided displaceably, and a rear wing channel, which is connected via bores and grooves with the pump pressure side.
  • working chambers are provided, each having a suction zone with inlet chamber and a pressure zone with outlet chamber, wherein the pressure medium flows from the working chambers can be fed into a pressure collecting space.
  • the generic document describes this purpose a vane pump in which the pressure medium flows from the two outlet chambers at high speeds in series GE are switched.
  • the structure of the vane pump with the special flow control valve is relatively expensive.
  • an actuation of the flow control valve is only reached when a corresponding resistance is applied to the throttle point.
  • a high volume flow must be promoted, which requires corresponding power and causes undesirable heat development.
  • the known vane pumps usually promote a high volume, which is guided against a throttle or against a resistor and optionally traceable by a flow control valve and a bypass line.
  • the losses go directly into temperature and heat the pressure medium circulation clearly. This requires the use of appropriate coolers whose size increases proportionally with the pressures. Since more and more hydraulic power is required, especially in the automotive sector, the power losses resulting from the previously known vane-cell pumps, which are reflected directly in fuel consumption, increase significantly.
  • the present invention is based on the object To provide a vane pump, which solves the aforementioned disadvantages of the prior art, in particular the Wirkunsgrad significantly improved at higher speeds and allows for a cost-effective, compact design independent power control and accurate flow control to a consumer.
  • the shut-off valve optimizes the efficiency of the vane pump and enables a compact and cost-effective design.
  • a piston of the shut-off valve is controllable in dependence on the pump speed, wherein the piston of the shut-off valve is connected on a first piston side to the pump pressure side and on the opposite, second piston side to the rear vane oil passage.
  • the pressure-independent switching is achieved by the two-sided pressurization of the piston.
  • the speed dependence is achieved in that the second piston side is connected to the Schuerielölkanal.
  • the pressure means has both the operating pressure, i. the pressure on the pump pressure side and, with increasing pump speed, a superimposed back pressure.
  • the operating pressure of the Schuerielölkanal results in a known manner from the connection of the Schuerielölkanals via holes and grooves with the pump pressure side.
  • the dynamic pressure occurring with increasing speed results from the movement of the vanes in the slots of the rotor.
  • a kind of rear wing pump is formed, wherein the dynamic pressure increases proportionally with increasing pump speed.
  • the rear wing pump is created by the fact that the wings in the region of the inlet chambers from the view of Schuflüglölkanals migrate to the outside and thus sucking pressure medium from the pressure accumulation chamber or the pump pressure side. This pressure medium is pushed out of the slots again in the area of the outlet chambers.
  • the flow rate is defined with wing face times Hub and is speed-proportional. It is a small amount of oil.
  • the inventor has recognized that the speed dependence of the back pressure in the rear wing area can be used to control the shut-off valve and thus a particularly advantageous power control and accurate flow control to a consumer is possible.
  • start-up valve has a spring which counteracts the pressure of the rear wing oil channel.
  • the spring By the spring, a first switching position of the shut-off valve is advantageously ensured, in which the pressure medium flow from the first outlet chamber via a check valve to the pressure accumulation chamber can be fed.
  • the first switching position of the shut-off valve is at low pump speeds.
  • the spring is designed as a compression spring and arranged on the connected to the pump pressure side of the first piston side.
  • the shut-off valve thus has essentially two switching positions.
  • the first switching position in which the spring is stretched, the pressure medium flow from the first outlet chamber to the pump pressure side or in the pressure accumulation chamber is promoted.
  • the spring opposite, second piston side which is connected to the Schuerielölkanal, acted upon by the speed-dependent proportional increasing pressure.
  • This pressure moves the piston with increasing speed in the spring direction and thus opens a Ablbelberichtkante that allows a non-pressurized flow of the pressure medium of the first outlet chamber to the pump suction.
  • the pressure medium flow is thus returned to the shortest route to the pump suction.
  • the short-circuited pressure medium flow from the first outlet chamber can be injected into the pressure medium flow of the suction connection by means of an intersection formed as an injector.
  • the energy that brings the short-circuited or recycled pressure medium flow with it, can thus be used to charge the coming from the suction port fluid flow.
  • the injector formed from the suction port and the intersection thus causes the recirculated pressure medium flow is optimally fed to the pump suction without the Druckstoffzufluß is hindered from the outside. This results in further, energetic advantages for the vane pump.
  • shut-off valve is integrated in a pump cover.
  • the structure of a vane pump is basically, for example, from DE 41 36 150 A1 , known. Therefore, only the features necessary for the invention will be described in more detail below.
  • the vane pump has a pump suction side 1 with a suction port 2 and a pump pressure side 3, which leads to a consumer, not shown, on.
  • the vane pump is suitable for supplying a power steering system of a motor vehicle.
  • a pump housing 4 a drive shaft 5 is mounted, which is connected to a rotor 6 located on it.
  • the rotor 6 has radially arranged slots 7, in which wings 8 are guided displaceably.
  • ten wings 8 may be provided.
  • the wings 8 and the rotor 6 are surrounded by a cam ring 9, which is secured against rotation with the pump housing 4. Between the cylindrical peripheral surface of the rotor 6 and the elliptical bore of the cam ring 9 are the two working chambers 10.
  • the working chambers 10 are configured generally sickle-shaped. The delivery volume results from the largest possible sickle segment between two wings 8 and the width of the rotor 6 or the wing. 8
  • FIG Fig. 2 A schematic representation of the working chambers 10 is shown in FIG Fig. 2 shown. It follows that each working chamber 10 each have a suction zone with an inlet chamber 11 and 12 and a pressure zone with an outlet chamber 13 and 14 respectively. The pressure medium flows from the outlet chambers 13, 14 are in a pressure collection chamber 15 feasible.
  • FIG. 1 shows, the vane pump on a Händlölkanal 16 which is connected via not shown holes and grooves, with the pump pressure side 3 and the pressure accumulator 15.
  • the rear wing oil channel 16 is also connected to a so-called Kaltstartnut 17.
  • the rotation of the drive shaft 5 and thus also the rotor. 6 causes the guided in the rotor 6 wings 8 are pressed by the resulting centrifugal force in the radial direction of the track of the fixed cam ring 9. This is supported by the pressure medium, which passes from the pressure accumulator 15 in the Schuerielölkanal 16 and thus to the inner end faces of the wings 8.
  • the pressure medium flow from the first outlet chamber 13 by means of a shut-off valve 18 which is integrated in the pump cover 19, controllable.
  • the pressure medium flow is short-circuited at low pump speeds to the pressure accumulator 15 and at higher pump speeds or fed directly to the pump suction side 1.
  • the shut-off valve 18, a piston 20 which is controllable in dependence on the pump speed.
  • the piston 20 of the shut-off valve 18 is connected at a first piston side 21 to the pump pressure side 3 and the pressure collecting space 15.
  • the shut-off valve 18 also has a spring 23, which counteracts the pressure of the pressure medium from the Schuhofflölkanal 16.
  • the spring 23 is arranged on the first piston side 21 and formed in the illustrated embodiment as a compression spring.
  • the vane pump has a check valve 24, via which the pressure medium flow from the first outlet chamber 13 can enter the pressure collecting space 15.
  • the check valve 24 may be formed in an advantageous manner as a diaphragm valve.
  • the short-circuited pressure medium flow from the first outlet chamber 13, as shown Fig. 1 can be seen, injected by means of an intersection 25 in the pressure medium flow of the suction port 2.
  • the intersection is designed as an injector 25.
  • Fig. 1 Like also out Fig. 1 can be seen, the vane pump on a flow control piston 26, whose function for the inventive device in Fig. 2 is shown in more detail.
  • Fig. 2 shows an already described cam ring 9 which limits the rotor 6 with the wings 8.
  • the rotor 6 rotates in the arrow direction whereby in a conventional manner two working chambers 10 each having an inlet chamber 11 and 12 and an outlet chamber 13 and 14 are formed.
  • the inlet chambers 11 and 12 are supplied by two inlet chamber lines 27 with a pressure medium flow.
  • this pressure medium from the inlet chambers 11 and 12 conveyed to the outlet chambers 13 and 14, respectively.
  • the pressure medium is discharged into an uncontrolled outlet line 28 in the direction of a main pressure line 29.
  • the pressure medium flow from the first outlet chamber 13 is discharged into a controlled outlet conduit 30 which branches in the direction of the shut-off valve 18 and the check valve 24.
  • the shut-off valve 18 is closed (as in FIG Fig. 2 shown), so that the pressure medium flow from the controlled outlet conduit 30 through the check valve 24 flows into the main pressure line 29.
  • the piston 20 of the shut-off valve 18 is moved in the direction of the spring 23 so that a Abschalt deviskante 31 opens, which is a flow of the pressure medium flow from the first outlet chamber 13 and controlled outlet conduit 30 to the pump suction side 1 allows.
  • the non-return valve 24 prevents the pressure medium flow from flowing out of the second outlet chamber 14 or out of the main pressure channel 29 via the shut-off control edge 31 back to the pump suction side 1.
  • the pressure medium flow of the first outlet chamber 13 is injected into a pressure medium flow from an oil reservoir pipe 33 of an oil tank 34.
  • the actuation of the piston 20 takes place through the rear wing oil channel 16 which is connected to the second piston side 22 by a rear wing oil line 35.
  • the speed-dependent actuation of the piston 20 is effected by the already mentioned "rear wing pump", which generates by the radial movement of the wings 8 a proportional to the speed increasing, superimposed back pressure.
  • the rear wing oil channel 16 also has throttle points 36 to increase the pressure with increasing speed. In the in Fig. 2 illustrated embodiment, four throttle bodies 36 are provided. Of course, embodiments are also feasible that allow a non-proportional increase of backpressure.
  • the pressure acting on the second piston side 22 (operating pressure + back pressure) of the rear wing oil channel 16 counteracts the spring 23 together with the voltage applied in the main pressure channel 29 operating pressure.
  • the main pressure channel 29 is connected by a branch channel 37 with the first piston side 21.
  • a control panel 38 is arranged, the, to control a bypass line 39, with the flow control piston 26 corresponds.
  • the bypass line 39 is intended to conduct an excess pressure medium flow back to the pump suction side 1. This ensures that a constantly controlled flow of pressure medium reaches the consumer. It is particularly advantageous if a straight or falling course of the pressure medium flow to the consumer can be realized by the shut-off valve 18 and the flow control piston 26 with increasing pump speed.
  • the flow control piston 26 is configured such that the flow control piston 26 opens the bypass line 39 only from a certain, predetermined pressure.
  • the pressure of the flow control piston 26 is kept closed, it is constructed by a flow control piston spring 40 and a flow control line 41. '
  • the power control line 41 is acted upon by the pressure of the pressure medium to the consumer.
  • the pressure that opens the flow control piston 26 is applied by the main pressure line 29 or a differential pressure is generated when flowing through the control orifice 38, wherein the reduced pressure acts on the side with the flow control spring. As the volume flow increases, the differential pressure increases and opens the bypass 39.
  • the bypass line 39 forms a bypass injector 43 with a suction line 42 into which the pressure medium from the return line 32 has possibly already been injected beforehand.
  • the bypass line 39 can be introduced into the suction line 42 as an intersection, for example.
  • pump suction 1 is formed for both working chambers 10, but may optionally be designed only for a single working chamber 10, so that in this embodiment, two pump suction 1 are necessary.

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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 (13)

  1. Pompe à palettes pour générer un courant de fluide sous pression vers un dispositif consommateur, en particulier une direction assistée d'un véhicule automobile, comprenant les caractéristiques suivantes :
    - un côté d'aspiration (1) de la pompe qui peut être alimenté par un raccord d'aspiration (2) à un fluide sous pression et un côté de pression (3) de la pompe, qui peut être connecté au dispositif consommateur au moyen d'une conduite de pression principale (29) ;
    - un boîtier (4) de pompe dans lequel est maintenu un anneau à came (9) et dans lequel est monté un arbre d'entraînement (5) avec un rotor (6), le rotor (6) présentant des fentes (7) dans lesquelles des palettes (8) sont guidées de manière déplaçable ;
    - un canal d'huile (16) derrière les palettes, qui est connecté par le biais d'alésages et de rainures au côté de pression (3) de la pompe et qui sollicite avec une pression de travail les surfaces frontales intérieures des palettes (8) ; et
    - des chambres de travail (10), qui présentent chacune une zone d'aspiration avec une chambre d'entrée (11 ; 12) et une zone de pression avec une chambre de sortie (13 ; 14), les courants de fluide sous pression pouvant être guidés hors des chambres de travail (10) dans un espace de collecte sous pression (15),
    - un piston (20) d'une soupape de coupure (18) pouvant être commandé en fonction de la vitesse de rotation de la pompe,
    - le piston (20) de la soupape de coupure (18) étant raccordé au niveau d'un premier côté de piston (21) au côté de pression (3) de la pompe et au niveau du deuxième côté opposé du piston (22) au canal d'huile (16) derrière les palettes,
    caractérisée par les caractéristiques suivantes :
    - le courant de fluide sous pression sortant d'une première chambre de sortie (13) peut être commandé au moyen de la soupape de coupure (18) de telle sorte que le courant de fluide sous pression, lorsque les vitesses de rotation de la pompe sont petites, soit acheminé par le biais d'un clapet anti-retour (24) à l'espace de collecte sous pression (15), et lorsque les vitesses de rotation de la pompe sont plus élevées, soit acheminé de manière court-circuitée ou directement au côté d'aspiration (1) de la pompe,
    - le clapet anti-retour (24) empêche une décharge du courant de fluide sous pression hors de la deuxième chambre de sortie (14), ou hors du canal de pression principal (29) vers le côté d'aspiration (1) de la pompe.
  2. Pompe à palettes selon la revendication 1,
    caractérisée en ce que
    la soupape de coupure (18) présente un ressort (23) qui agit à l'encontre de la pression du canal d'huile (16) derrière les palettes.
  3. Pompe à palettes selon la revendication 1 ou 2,
    caractérisée en ce que
    le ressort (23) est réalisé sous forme de ressort de pression et est disposé au niveau du premier côté (21) du piston, connecté au côté de pression (3) de la pompe.
  4. Pompe à palettes selon l'une quelconque des revendications 1 à 3,
    caractérisée en ce que
    le courant de fluide sous pression sortant de la première chambre de sortie (13) dans une première position de commutation de la soupape de coupure (18), qui correspond aux vitesses de rotation inférieures de la pompe, peut être acheminé par le biais d'un clapet anti-retour (24) à l'espace de collecte sous pression (15) ou à la conduite de pression principale (29).
  5. Pompe à palettes selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce qu'une pompe à palettes arrière est formée par le déplacement des palettes dans les fentes (7) du rotor (6), laquelle produit une pression de compression superposée dans le canal d'huile (16) derrière les palettes, la pression de compression augmentant de manière proportionnelle à l'augmentation de la vitesse de rotation de la pompe.
  6. Pompe à palettes selon la revendication 5,
    caractérisée en ce que le canal d'huile (16) derrière les palettes présente des points d'étranglement (36) pour augmenter la pression lorsque la vitesse de rotation de la pompe augmente.
  7. Pompe à palettes selon l'une quelconque des revendications 2 à 6,
    caractérisée en ce que
    le piston (20), lorsque la vitesse de rotation de la pompe augmente, se déplace sous l'effet de l'augmentation de la pression du canal d'huile (16) derrière les palettes dans la direction du ressort (23) de telle sorte qu'une arête de commande de coupure (31) s'ouvre, laquelle permet un écoulement du courant de fluide sous pression hors de la première chambre de sortie commandable (13) vers le côté d'aspiration (1) de la pompe ou vers le raccord d'aspiration (2).
  8. Pompe à palettes selon l'une quelconque des revendications 2 à 7,
    caractérisée en ce que
    le clapet anti-retour (24) empêche une évacuation du courant de fluide sous pression hors de la deuxième chambre de sortie (14) ou hors de l'espace de collecte sous pression (15).
  9. Pompe à palettes selon l'une quelconque des revendications 1 à 8,
    caractérisée en ce que
    le courant de fluide sous pression court-circuité hors de la première chambre de sortie (13) peut être injecté dans le courant de fluide sous pression du raccord d'aspiration (2) au moyen d'une intersection (25).
  10. Pompe à palettes selon la revendication 9,
    caractérisée en ce que
    l'intersection est réalisée sous forme d'injecteur (25).
  11. Pompe à palettes selon l'une quelconque des revendications 1 à 10,
    caractérisée en ce que
    l'on dispose dans la conduite sous pression principale (29) conduisant au dispositif consommateur un diaphragme de régulation (38) qui coopère avec un piston de régulation de courant (26) pour la commande d'une conduite de dérivation (39).
  12. Pompe à palettes selon la revendication 11,
    caractérisée en ce
    qu'un courant de fluide sous pression de dérivation peut être acheminé par une deuxième intersection réalisée sous forme d'injecteur de dérivation (43), au courant de fluide sous pression jusqu'aux chambres d'entrée (11, 12).
  13. Pompe à palettes selon l'une quelconque des revendications 1 à 12, caractérisée en ce que
    la soupape de coupure (18) est intégrée dans un couvercle de pompe (19).
EP20020026051 2001-12-07 2002-11-22 Pompe à palettes Expired - Fee Related EP1318304B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10160286 2001-12-07
DE2001160286 DE10160286A1 (de) 2001-12-07 2001-12-07 Flügelzellenpumpen

Publications (3)

Publication Number Publication Date
EP1318304A2 EP1318304A2 (fr) 2003-06-11
EP1318304A3 EP1318304A3 (fr) 2003-09-10
EP1318304B1 true EP1318304B1 (fr) 2009-02-18

Family

ID=7708468

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020026051 Expired - Fee Related EP1318304B1 (fr) 2001-12-07 2002-11-22 Pompe à palettes

Country Status (2)

Country Link
EP (1) EP1318304B1 (fr)
DE (2) DE10160286A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10229809A1 (de) * 2002-07-03 2004-01-15 Zf Lenksysteme Gmbh Flügelzellenpumpe
DE10354577A1 (de) * 2003-11-21 2005-06-16 Zf Friedrichshafen Ag Pumpeneinrichtung, insbesondere zur Förderung von Getriebeöl
US8454335B2 (en) * 2011-01-13 2013-06-04 Hamilton Sundstrand Corporation Valveless vane compressor
DE102020105173A1 (de) 2020-02-27 2021-09-02 Fte Automotive Gmbh Pumpenaggregat für einen Antriebsstrang eines Kraftfahrzeugs

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB559108A (en) * 1940-11-15 1944-02-04 Cyril Alphonso Pugh Improvements in or relating to fuel supply systems for internal-combustion engines
JPS61119472A (ja) * 1984-11-15 1986-06-06 Toyoda Mach Works Ltd ベ−ンポンプの容量切替装置
EP0522505A3 (en) * 1991-07-09 1993-07-14 Toyoda Koki Kabushiki Kaisha Variable-displacement vane pump
DE4136151C2 (de) * 1991-11-02 2000-03-30 Zahnradfabrik Friedrichshafen Flügelzellenpumpe
DE4136150A1 (de) 1991-11-02 1993-05-06 Zf Friedrichshafen Ag, 7990 Friedrichshafen, De Fluegelzellenpumpe
JPH0655946U (ja) * 1993-01-12 1994-08-02 株式会社ユニシアジェックス ベーンポンプの流量制御機構

Also Published As

Publication number Publication date
DE10160286A1 (de) 2003-06-18
EP1318304A2 (fr) 2003-06-11
EP1318304A3 (fr) 2003-09-10
DE50213284D1 (de) 2009-04-02

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