EP1461533B1 - Pumpe - Google Patents

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Publication number
EP1461533B1
EP1461533B1 EP02798289A EP02798289A EP1461533B1 EP 1461533 B1 EP1461533 B1 EP 1461533B1 EP 02798289 A EP02798289 A EP 02798289A EP 02798289 A EP02798289 A EP 02798289A EP 1461533 B1 EP1461533 B1 EP 1461533B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
vane
under
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02798289A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1461533A1 (de
Inventor
Ivo Agner
Kerstin Rosenkranz
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.)
ixetic Bad Homburg GmbH
Original Assignee
ixetic Bad Homburg 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 ixetic Bad Homburg GmbH filed Critical ixetic Bad Homburg GmbH
Publication of EP1461533A1 publication Critical patent/EP1461533A1/de
Application granted granted Critical
Publication of EP1461533B1 publication Critical patent/EP1461533B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • F04C15/066—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • 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 pump as defined in the preamble of claim 1.
  • a pump is eg from the WO 01/94791 known.
  • Such known vane pumps are used in particular for supplying power steering systems or similar hydraulic systems in motor vehicles.
  • the two pressure chambers of the vane cells are connected to one another via a pressure collecting space within the pump, which leads to the consumer in a common pressure line.
  • the two suction chambers of the vane cells are connected to each other and lead to the intake of the pump in which the oil flowing back from the steering or a tank of the pump is fed back.
  • the invention has for its object to provide a doppelhübige vane pump in which the associated suction and pressure areas each form a pump half and thus as two separately available feed pumps can be used.
  • An embodiment of the invention is characterized in that the undercut groove on the opposite pressure plate or optionally in the housing or housing cover the same pitch at the same point as the first pressure plate.
  • Another pump according to the invention is characterized in that the pressure plate and / or the counter plate has two pressure-tight delimited high-pressure fields, between which there is a suction pressure field.
  • the pressure fields are sealed by sealing means.
  • the respective Untererielnut or Untererielniere supplied with high pressure or circulation pressure, in particular via channels within the respective pressure field.
  • the Untererielnut is, as already mentioned, made in two parts.
  • the division has to be made at the same place on the opposite side plate, which may for example contain a total of 4 under wing kidneys, whereby only the underfoot kidneys of the same pump half may communicate.
  • FIG. 1 schematically the structure of a sauhübigen, double-vane vane pump is shown.
  • a rotor 3 with extendable wings 5 is shown within a doppelhübigen cam ring 1.
  • the rotor 3 is rotationally driven by a shaft 7.
  • the doppelhübige vane pump contains two pressure areas 9 and two suction areas 11, which are represented by corresponding pressure and suction kidneys and correspondingly enlarging or reducing cells within the cam ring.
  • the function of such vane pumps is known.
  • the direction of rotation is represented by an arrow 13.
  • the cells between two wings increase in the suction chamber 11 and thus suck fluid in the rotation group.
  • the pressure region 9 the cell volumes between two wings shrink and thus squeeze the fluid out of the pressure regions 9.
  • the two intake regions 11 are connected via suction lines 15 to a reservoir 17 and suck the fluid from this common reservoir.
  • the upper pressure region 9 leads to a pressure line 19, while the lower pressure region 9 leads to a pressure line 21.
  • the two pressure ranges are therefore hydraulically separated.
  • the upper pressure region 9 has a connection 23 to an underfloor groove 25 in which pressure medium from the pressure region presses the vanes from below out of the rotor 3 against the contoured ring 1.
  • the Untererielnut 25 in the suction area is connected to the lower wing groove 27 in the pressure region, which in this FIG. 1 not shown.
  • the upper pressure region 9 and the right suction region 11 represent one half of the double-vane vane pump.
  • the second half of the twin-vane vane pump is represented by the lower pressure region 9 and the left suction region 11.
  • the lower pressure region 9 is connected by a connection 29 to an underfloor groove 31 in the left suction region 11.
  • This Untererienut 31 is in turn connected to the Untererielnut 33 in the lower pressure region 9 of this pump half.
  • the respective pressure area supplies the underflute grooves with pressure and thus presses the wings hydraulically against the contour ring 1.
  • FIG. 2 shows the inventive construction of the rotation group of a double-vane vane pump. Same parts as in FIG. 1 are provided with the same reference numerals and will not be explained separately again here. It is important that the lower vane groove 25 in the suction region 11 and the lower vane groove 27 in the pressure region 9 are connected to one another for the upper vane pump half. It can also be seen that the underflute groove 27 is extended by a region 35. This area 35 extends essentially over a complete cell width between the wings 37 and 39. It can be seen that the wing 37 just leaves the printing area 9, ie the upper pressure kidney, when the leading wing 39 leaves the lower wing groove 35.
  • the wing 39 has to be supplied up to here with high pressure from the Untererielnut 35 and 27, as well as in the cell between the wings 37 and 39 still high pressure prevails, which acts from above on the wing head of the wing 39, which is not may lead to a depression of the wing.
  • the lower wing area of this wing may be depressurized when the lower vane pump area is switched to non-pressurized circulation in this twin-flow pump.
  • a leading cell between the wings 43 and 45 is supplied in this unpressurized part of the vane pump by an extension 47 of the lower wing groove with unpressurized under wing medium, so that the wings 43 and 45 are also in pressure equilibrium. Upon further rotation of the vane pump, this cell will then dive back into the pressurized part of the double-vane vane pump and supplied from the Unterhofflnut 25 again with pressure.
  • FIG. 3 shows a slightly different extender extension of the undercut groove 35.
  • the wing 37 just leaves the upper pressure kidney 9
  • the wing 39 is one half of its wing thickness in the subsequent Unterhofflnut 51 of the unpressurized vane pump half.
  • the groove 35 terminates at a distance 49 in front of the wing 39 of the vorrauseilenden wing cell.
  • FIG. 4 the inside of a pressure plate 57 is shown. Also visible in the pressure plate is the high-pressure kidney 9 and the suction kidney 11. Further, the underwing groove of the upper pump half is represented by the under-wing groove part 25 in the suction region, by the under-wing groove part 27 in the pressure region and by the inventive extension of the under-wing groove 35 in the pressure region. Clearly visible are the invention essential separation areas 53 and 55 to the lower undercut groove, which thus separate the under wing supply of the two pump halves from each other.
  • FIG. 5 is the counter-plate 59, which covers the rotation group on the other side of the vane pump shown.
  • the Untererielnuten Scheme 25 which is here but separated by a separation point 63 from the lower wing region 27 of the pressure region 9.
  • the extension of the Untererielnut 27 to the part 35 is here a mirror image of the plate FIG. 4 arranged.
  • separation areas 53 and 55 are again essential to the invention separation areas 53 and 55 in this position for the twin-flow pump.
  • the lower under wing area is divided by the separation point 61 into two Untererielnuten Schemee. This separation point is provided for corresponding cold start behavior and for squeezing the wings during cold start by forming certain resistances and pumping operations in the Untererielnuten.
  • Plate breakthroughs 65 and 67 are shown, which can conduct from the outside of the pressure range high pressure oil or low pressure oil, depending on the pump circuit, in this underwing area.
  • FIG. 6 These breakthroughs 65 and 67 are also recognizable.
  • the pressure plate 59 is now shown from the outside. It can be seen two pressure fields 69 and 71, in each of which the pressure kidneys 9 bring the expelled from the pump pressure oil and thus press this pressure plate by means of these pressure fields 69 and 71 from the outside with pressure against the contour ring and the rotation group.
  • the pressure fields 69 and 71 are sealed at their boundaries by seals against the rest of the pressure plate surface 73, which is acted upon by suction pressure.
  • the oil expressed from the pressure kidneys 9 of the vane pump becomes loud FIG.
  • the two pressure plates 59 and 57 and the contour ring 1 are rotatably connected to each other by means of through holes 79 and 81 and located therein positioning bolts and fixed in their orientation.
  • FIG. 7 shows a circuit diagram in which the function of a double-vane vane pump is shown schematically.
  • the two pump halves of the twin-vane vane pump are symbolically represented here by the pump symbols 101 and 103, which collect from the intake lines 15 together from a reservoir 17, the corresponding fluid.
  • Separate pressure outputs 19 and 21 can supply the pressure oil from the respective pump half, depending on the circuit of the respective consumer.
  • a switching valve 105 connects the pressure outlet 19 of the pump half 101 with a connection 107, which is connected via a check valve 109 to a connection point 111. In the connection point 111 also opens the pressure line 21 of the second pump half 103.
  • valve 105 In the switching position of the valve 105 shown here so a consumer can be supplied to the consumer port 113 with the oil flow of both pump halves 101 and 103.
  • a pressure limiting valve 115 is still provided which opens when the maximum pressure is exceeded and allows excess oil flow to flow back into the reservoir 17 via a connection 117, so that the pressure can not increase any further. If the total oil flow of the pump halves 101 and 103 is not necessary for the supply of the consumer at the consumer connection 113, the oil flow of the pump half 101 can be fed back to the reservoir 17 or the suction regions 15 of the pump via a line 119 by switching over the valve 105.
  • the pump half 101 is thus in the pressureless circulation at a circulation pressure of about 1 to 3 bar, depending on the resistances of the partial circuit.
  • FIG. 8 shows the outside view of a pump according to the invention. From a pump housing 200, the end of a shaft 202 protrudes.
  • FIG. 8 serves for the orientation of two sections, of which the section KK through the rotation group in FIG. 9 is shown and the section LL in FIG. 10 through adjacent pressure channels with integrated non-return valves.
  • the pump itself must not idle when the vehicle is parked, even if the pressure side loses oil through valve spool leaks of the transmission control and thus the idling channel runs empty due to the principle of the communicating tubes. Therefore, the internal channels of the pump are arranged so that even under these conditions, the rotation group remains filled at least over the shaft center with oil.
  • An illustration of this internal oil channel guide is in FIG. 9 to see.
  • the rotation group consists, as already in FIG. 1 described, inter alia, from the contour ring 1, from the rotor 3, from the wings 5, from the shaft 7 and contains the two pressure areas 9 and the two suction regions 11.
  • An intake passage 206 is formed by forming an intermediate wall 208 such that its inlet region 210 is disposed above the center of the shaft 7 and thus the rotation group remains filled up to the height of the intermediate wall 208 with oil, even if the intake passage 206 should otherwise idle. Via an arcuate extension 212 of the inner pump housing and the suction region 11 of the right side with the suction side 210 and thus to the intake passage 206 is connected.
  • FIG. 10 is on average LL from the FIG. 8 the formation of the pressure channels shown in the pump according to the invention.
  • a first pressure channel 214 and a second pressure channel 216 is formed in the pump housing 200.
  • the first pressure channel 214 is associated with the upper pressure range and closed by a check valve 218, whose function will be explained later.
  • the lower pressure range of the vane pump is closed by a check valve 220. While the upper pressure range with the check valve 218 over the shaft center 7 is the lower pressure range with the check valve 220 by a siphon-like design of the pressure channel 216 designed such that the oil in any case remains above the shaft center within this oil passage, when the right part of the pressure channel 216 should idle. This is made possible by the raised channel wall 224.
  • FIG. 11 the pump according to the invention is shown in a further cross-section so that the check valves 218 and 220 can be seen in cross section. They partially protrude into the pressure plate 59 FIG. 6 in so that they the upper pressure field 69 and the lower pressure field 71 against the pressure outputs 214 from FIG. 10 and 216 off FIG. 10 close.
  • the upper check valve consists of a valve seat 224 into which the sealing body 226 is pressed by means of a spring 228. Opposite the housing, the valve seat 224 is additionally sealed by a seal 230. Likewise, the seals of the pressure fields through the seal 232 can be seen.
  • the lower check valve 220 is constructed identically and will not be described again here.
  • the function of the check valves is such that when the pump is stopped, the pressure areas are closed and thus the respective pressure ranges only with their Untererielnuten, as in the FIGS. 2 to 6 are described connected.
  • pressure builds up within the rotation group, which can lift the check valve body 226 from their seats, thus allowing a promotion of the pressure oil outward into the two pressure channels 214 and 216 and thus to corresponding consumers.
  • the check valves are thus arranged at the transition between the pressure field volumes of the plate 59 and the pressure channels. These check valves are intended to be primarily resistance elements that may not necessarily be 100% tight. About the check valves so the volume of the pressure fields of the plate 59 is connected to the pressure supplying channels to the consumer.
  • the check valves are designed as simple plate valves. Other variants are possible.
  • the seat of this spring-loaded plate 226 is an automatic rotating part, which, sealed with an O-ring, is mounted in the pump housing and is positively fixed by shoulders in the pump housing and corresponding design of the printing plates. Of course, it is also possible to omit the O-ring and press the seat with transitional or interference fit. Because the rotation group itself may not idle, the shaft is sealed with a shaft seal 234 to the outside. If the internal pump leakage collects in the middle of the shaft, the shaft seal can open at a certain pressure and the leak oil can escape into the gear compartment. The exact function of this special shaft seal, which can work as a check valve, is already described in detail in another application.
  • a check valve is enlarged in the open state and in Figure 12.2 shown in the closed state. It can be seen that the plate valve body 226 in Figure 12.1 from the valve seat 224 is opened by the opening stroke X, so that the pressure oil can flow into the corresponding pressure channel. In Figure 12.2 the plate valve body 226, pressed by the force of the spring 228, abuts on the valve seat 224.
  • the suction of the pump according to the invention now works as follows: In the worst case, z. B. after a canceled cold start when stopping a back-rotating diesel engine, all wings are in the slot bottom of the rotor near the small circle diameter of the cam ring. If the rotor now rotates when starting, the blades are minimally driven by the centrifugal force. This way, the wings on the pressure side of the stroke contour also drive back into the rotor. However, the volume which the wing feeds into the underflute groove when it is driven in is pushed almost without loss under a wing which projects out on the suction side. This wing now comes out at least by the amount that the retracting wing is retracted. In addition, the centrifugal forces act on the wing.
  • FIG. 13 shows a special embodiment of the rotation group, in which asymmetric pump divisions can be realized by different contour strokes.
  • the known components contour ring 1, rotor 3, wings 5 and the shaft 7 and the two pressure areas 9 and the two suction regions 11 have already been described in their function.
  • the two great circle regions 240 above the rotor 3 and 242 below the rotor 3 within the cam ring 1 should be the same size in this example.
  • the following function is conceivable that is driven by a small circle radius 236 to a large circle radius 242, which corresponds for example to a 60% suction, based on the total delivery volume of the pump.
  • a large circle radius 242 which corresponds for example to a 60% suction, based on the total delivery volume of the pump.
  • the large-circle region 242 moves back to a larger minor circle radius 238, only 40% of the stroke volume, based on the total pump delivery rate, is expressed by the cell volume reduction. If this large minor circle radius 238 is used to drive the radius of the circle 240, then this again likewise means only a 40% suction, based on the total delivery rate of the pump.
  • this large circle radius 240 then moves back to the smaller small circle radius 236, this means a 60% expressions of the oil.
  • the aspirated cell volumes differ from the expressed cell volumes.
  • This solution can have advantages if, for reasons of space, less installation space is available on one side than on the other for suction or pressure ducts.
  • the small circle remains at the same level and the great circles are of different sizes. It is important that both the small circle radius and the great circle radius or both radii together can be varied independently of each other.
  • the pump halves are internally hydraulically separated. That is, the correspondingly associated lower wing areas and upper wing areas are separated. There is a common suction line and two separate pressure lines. Each rotation group pressure output is assigned a pressure field, which is required for the realization of the pressure plate compensation. Within this pressure field channels are realized, which serve the Untererielski the respective pump half.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP02798289A 2001-12-27 2002-12-20 Pumpe Expired - Lifetime EP1461533B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10164250 2001-12-27
DE10164250 2001-12-27
PCT/DE2002/004678 WO2003056180A1 (de) 2001-12-27 2002-12-20 Pumpe

Publications (2)

Publication Number Publication Date
EP1461533A1 EP1461533A1 (de) 2004-09-29
EP1461533B1 true EP1461533B1 (de) 2012-06-20

Family

ID=7711042

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02798289A Expired - Lifetime EP1461533B1 (de) 2001-12-27 2002-12-20 Pumpe

Country Status (6)

Country Link
EP (1) EP1461533B1 (it)
AU (1) AU2002363838A1 (it)
DE (2) DE10297707D2 (it)
FR (1) FR2834317B1 (it)
IT (1) ITMI20022764A1 (it)
WO (1) WO2003056180A1 (it)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2486280B8 (de) 2009-10-07 2014-07-09 Magna Powertrain Bad Homburg GmbH Flügelzellenpumpe
GB2486007B (en) * 2010-12-01 2017-05-10 Itt Mfg Enterprises Inc Sliding vane pump
DE102013108697A1 (de) * 2013-08-12 2015-02-12 Zf Lenksysteme Gmbh Verdrängerpumpe, insbesondere verstellbare flügelzellenpumpe
WO2015193170A1 (de) 2014-06-16 2015-12-23 Magna Powertrain Bad Homburg GmbH Pumpvorrichtung
DE102014222322B3 (de) * 2014-10-31 2016-02-04 Magna Powertrain Bad Homburg GmbH Flügelzellenpumpe mit verbessertem Startverhalten
DE102014222321B3 (de) * 2014-10-31 2015-12-10 Magna Powertrain Bad Homburg GmbH Flügelzellenpumpe mit verbessertem Startverhalten
FR3033609A1 (fr) * 2015-03-09 2016-09-16 Yves Gringoz Guidage hydrostatique a report de pression
DE102015105933B4 (de) * 2015-04-17 2018-04-26 Schwäbische Hüttenwerke Automotive GmbH Pumpe
DE112016002466B4 (de) * 2015-06-02 2023-10-26 Hanon Systems Efp Deutschland Gmbh Flügelzellenpumpe und Verfahren zu deren Betrieb
DE102015215982B4 (de) 2015-08-21 2017-03-16 Magna Powertrain Bad Homburg GmbH Pumpe sowie System zur Versorgung eines Verbrauchers
DE102016216681A1 (de) 2015-09-11 2017-04-13 Magna Powertrain Bad Homburg GmbH Verstellpumpe mit Unterflügelversorgung und Verfahren
DE102018200225B3 (de) * 2018-01-09 2019-03-07 Magna Powertrain Bad Homburg GmbH Pumpenanordnung für ein Fahrzeug, sowie Steuerung für eine Pumpenanordnung und Verfahren
DE102019113395A1 (de) * 2019-05-20 2020-11-26 Schwäbische Hüttenwerke Automotive GmbH Flügelzellenpumpe mit Flügelabstützung
DE102019121958A1 (de) * 2019-08-14 2021-02-18 Schwäbische Hüttenwerke Automotive GmbH Flügelzellenpumpe mit Druckausgleichsverbindung
DE102019127389A1 (de) * 2019-10-10 2021-04-15 Schwäbische Hüttenwerke Automotive GmbH Flügelzellenpumpe
DE102019132711A1 (de) 2019-12-02 2021-06-02 Fte Automotive Gmbh Flüssigkeitspumpe, insbesondere zur Versorgung eines Getriebes oder einer Kupplung im Antriebsstrang eines Kraftfahrzeugs
DE102020105173A1 (de) * 2020-02-27 2021-09-02 Fte Automotive Gmbh Pumpenaggregat für einen Antriebsstrang eines Kraftfahrzeugs

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3790314A (en) * 1972-05-22 1974-02-05 Abex Corp Vane pump having extended undervane suction ports
JPS51130904A (en) * 1975-04-30 1976-11-13 Sundstrand Corp Fluid pumps
US4505654A (en) * 1983-09-01 1985-03-19 Vickers Incorporated Rotary vane device with two pressure chambers for each vane
JP3014204B2 (ja) * 1992-03-16 2000-02-28 株式会社日本自動車部品総合研究所 流体機械

Also Published As

Publication number Publication date
WO2003056180A1 (de) 2003-07-10
FR2834317A1 (fr) 2003-07-04
EP1461533A1 (de) 2004-09-29
FR2834317B1 (fr) 2006-06-09
ITMI20022764A1 (it) 2003-06-28
DE10259894A1 (de) 2003-07-17
AU2002363838A1 (en) 2003-07-15
DE10297707D2 (de) 2005-02-17

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