EP1461533A1 - Pompe - Google Patents

Pompe

Info

Publication number
EP1461533A1
EP1461533A1 EP02798289A EP02798289A EP1461533A1 EP 1461533 A1 EP1461533 A1 EP 1461533A1 EP 02798289 A EP02798289 A EP 02798289A EP 02798289 A EP02798289 A EP 02798289A EP 1461533 A1 EP1461533 A1 EP 1461533A1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
lower wing
particular according
wing
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.)
Granted
Application number
EP02798289A
Other languages
German (de)
English (en)
Other versions
EP1461533B1 (fr
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
LuK Fahrzeug Hydraulik GmbH and Co KG
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 LuK Fahrzeug Hydraulik GmbH and Co KG filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Publication of EP1461533A1 publication Critical patent/EP1461533A1/fr
Application granted granted Critical
Publication of EP1461533B1 publication Critical patent/EP1461533B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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, in particular a vane cell pump or roller cell pump, with a two-stroke contour ring, with a rotor, with vanes, with side plates, with a housing and a housing cover, with underfloor grooves for supplying the lower wing surfaces with pressure, the vanes being radially displaceable are arranged in the rotor and are extended by the pressure under the wings and pressed against the contour ring.
  • Vane pumps of this type are known and 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 each other via a pressure accumulator inside 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 suction area of the pump, in which the oil flowing back from the steering or a tank is fed back to the pump.
  • the invention has for its object to provide a double-stroke vane cell pump in which the associated suction and pressure areas each form a pump half and can thus be used as two separately available feed pumps.
  • the task is performed by a pump, in particular a vane cell pump or a roller cell pump, with a two-stroke contour ring, with a rotor with vanes, with side plates and a housing and a housing cover, with under-wing grooves for supplying the lower wing surfaces with pressure, with the vanes which can be displaced radially in the rotor the pressure in the lower wing groove is pressed against the contour ring, solved in that the lower wing groove is divided into two parts and one part, viewed in the direction of rotation, extends under a suction grille and at least one subsequent pressure grille, so that the lower wing groove corresponds to the suction area of one half of the pump is associated with the associated lower wing groove, which is assigned to the pressure range of the same pump half, is connected and there is no connection to the lower wing grooves of the other pump half.
  • the under-wing supply is designed in such a way that there are no direct channels via the channels in the side plates Short circuits occur and the wings are always pressed
  • a preferred embodiment of the invention is characterized in that the part of the lower wing groove lying under the pressure kidney, viewed in the direction of rotation, is essentially extended by the angular amount of a leading cell.
  • a pump is preferred in which the extension of the lower wing groove is designed such that the leading wing of the leading cell is only a maximum of one wing thickness in the next, possibly unpressurized lower wing groove, if the trailing wing of the leading cell is just connecting to the one above has left the under wing groove positioned pressure kidney. This means that the leading wing leaves the lower wing groove when the trailing wing leaves the pressure kidney positioned above.
  • a further embodiment according to the invention is characterized in that the lower wing groove on the opposite pressure plate or possibly in the housing or housing cover has the same division 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 counterplate has two pressure-tightly delimited high-pressure fields, between which there is a suction pressure field.
  • the pressure fields are sealed off by sealing devices.
  • the respective under-wing groove or under-wing kidney is preferably supplied with high pressure or circulating pressure, in particular via channels within the respective pressure field.
  • the under-wing groove is made in two parts.
  • the division must be made on the opposite side plate, which may contain a total of 4 lower wing kidneys, at the same point, whereby only the lower wing kidneys of the same pump half may be connected.
  • the leading wing of the cell which is currently finishing the pushing-out process, may only leave the lower wing kidney, which is assigned to the corresponding pressure range of the associated pump half, with its slotted surface under the wing when the trailing wing no longer has a connection to the pressure kidney. This is the only way to ensure that the leading wing is always pressed against the contour with sufficient pressure and that there is no wing lift-off or short circuits.
  • Figure 1 shows schematically the structure of a two-stroke double-flow
  • FIG. 2 shows a rotation group according to the invention with the inventive
  • Figure 3 also shows a rotating group with an inventive
  • Figure 4 shows a side plate.
  • Figure 5 shows an opposite side plate.
  • Figure 6 shows the outside of a side plate with two separate pressure fields.
  • Figure 7 shows the hydraulic circuit diagram of a double-flow pump.
  • Figure 8 shows the external view of a pump according to the invention.
  • FIG. 9 shows the cross section KK from FIG. 8.
  • FIG. 10 shows the cross section LL from FIG. 8.
  • FIG. 11 shows a further cross section from FIG. 8.
  • Figure 12 shows check valves in cross section.
  • Figure 13 shows different contour strokes.
  • FIG. 1 the structure of a two-stroke, two-flow vane cell pump is shown schematically.
  • a rotor 3 with wings 5 that can be pulled out is shown within a double-stroke cam ring 1.
  • the rotor 3 is driven in rotation by a shaft 7.
  • the double-pretty vane cell 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 lifting ring.
  • the function of such vane pumps is known.
  • the direction of rotation is represented by an arrow 13.
  • the special circuit of a double-flow pump will now be discussed below.
  • the two suction areas 11 are connected to a reservoir 17 via suction lines 15 and suck in the fluid from this common reservoir.
  • the upper pressure area 9 leads to a pressure line 19, while the lower pressure area 9 leads to a pressure line 21.
  • the two pressure ranges are therefore hydraulically separated.
  • the upper pressure area 9 has a connection 23 to a lower wing groove 25, in which pressure medium from the pressure area presses the wings from below out of the rotor 3 against the contour ring 1.
  • the lower wing groove 25 in the suction area is connected to the lower wing groove 27 in the pressure area, which is not shown in this figure 1.
  • the upper pressure area 9 and the right suction area 11 represent one half of the double-flow wing cell pump.
  • the second half of the double-flow vane cell pump is represented by the lower pressure area 9 and the left suction area 11.
  • the lower pressure area 9 is connected by a connection 29 to a lower wing groove 31 in the left suction area 11.
  • This underfloor groove 31 is in turn connected to the underwing groove 33 in the lower pressure region 9 of this pump half.
  • the respective pressure range supplies the under-wing grooves with pressure and thus presses the blades hydraulically against the contour ring 1. If one of the two vane cell pump halves is now depressurized because a corresponding consumer does not need the pressure, the lower vane area is also depressurized, so that the vanes can continue to move essentially pressure-balanced in the respective pump area. In the depressurized state, there is a minimum circulating pressure of up to 3 bar, which, in addition to the centrifugal force, also supports the removal of the wings.
  • Figure 2 shows the inventive design of the rotation group of a double flow wing cell pump.
  • the same parts as in Figure 1 are provided with the same reference numerals and are not explained again separately here.
  • the lower wing groove 25 in the suction area 11 and the lower wing groove 27 in the pressure area 9 are connected to one another for the upper vane pump half.
  • the lower wing groove 27 is extended by an area 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 pressure area 9, ie the upper pressure kidney, when the leading wing 39 leaves the lower wing groove 35.
  • the wing 39 must be supplied with high pressure from the lower wing groove 35 or 27, since there is still high pressure in the cell between the wings 37 and 39 - which acts on the wing head of the wing 39 from above, which is what must not cause the wing to be pressed down.
  • the wing head is depressurized from above, and thus the lower vane area of this vane may also become depressurized if the lower vane pump area is switched to unpressurized circulation in this double-flow pump.
  • FIG. 3 shows a slightly different extension of the lower wing groove 35.
  • the wing 39 is with half its wing thickness in the subsequent lower wing groove 51 of the depressurized vane pump half.
  • the groove 35 ends at a distance 49 in front of the wing 39 of the leading wing cell.
  • FIG. 5 The inside of a pressure plate 57 is shown in FIG.
  • the high-pressure kidney 9 and the suction kidney 11 can be seen in the pressure plate.
  • the lower wing groove of the upper pump half is represented by the lower wing groove part 25 in the suction area, by the lower wing groove part 27 in the pressure area and by the inventive extension of the lower wing groove 35 in the pressure area.
  • the separating areas 53 and 55 to the lower under-wing groove, which are essential to the invention, can also be clearly seen and thus separate the under-wing supply of the two pump halves from one another.
  • FIG. 5 shows the counter plate 59, which covers the rotation group on the other side of the wing cell pump.
  • the lower wing groove area 25 which is separated here from the lower wing area 27 of the pressure area 9 by a separation point 63.
  • the extension of the lower wing groove 27 by the part 35 is arranged here as a mirror image of the plate in FIG. 4.
  • the separating areas 53 and 55 which are essential to the invention, can again be seen in this position for the double-flow pump.
  • the lower lower wing area is divided by the separating point 61 into two lower wing groove areas. This separation point is provided for corresponding cold start behavior and for pressing out the wing during cold start by forming certain resistances and pumping processes in the under wing grooves.
  • plate openings 65 and 67 are shown in FIG. 5, which can lead from the outside of the high-pressure oil or low-pressure oil pressure area, depending on the pump circuit, into this lower wing area.
  • FIG. 6 the pressure plate 59 is now shown from the outside.
  • Two pressure fields 69 and 71 can be seen, into each of which the pressure kidneys 9 introduce the pressure oil expelled from the pump and press this pressure plate from the outside with pressure against the contour ring and the rotating group by means of these pressure fields 69 and 71.
  • 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 cell pump which according to FIG.
  • the two pressure plates 59 and 57 and the contour ring 1 are connected to one another in a rotationally fixed manner by means of through openings 79 and 81 and positioning bolts located therein and are fixed in their alignment.
  • FIG. 7 shows a circuit diagram in which the function of a double-flow vane cell pump is shown schematically.
  • the two pump halves of the double-flow vane cell pump are symbolically represented here by the pump symbols 101 and 103, which draw the corresponding fluid from the reservoir 15 together from a reservoir 17.
  • 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 changeover valve 105 connects the pressure outlet 19 of the pump half 101 to a connection 107, which is connected to a connection point 111 via a check valve 109.
  • the pressure line 21 of the second pump half 103 also opens into the connection point 111.
  • a consumer at the consumer connection 113 can thus be supplied with the oil flow from both pump halves 101 and 103.
  • a pressure limiting valve 115 is also 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 cannot rise further. If the total oil flow of the pump halves 101 and 103 is now not necessary for supplying the consumer at the consumer connection 113, the oil flow of the pump half 101 can be returned to the reservoir 17 or the suction areas 15 of the pump by switching the valve 105.
  • the pump half 101 is therefore in the unpressurized circulation at a circulation pressure of approx. 1 to 3 bar, depending on the resistances of the partial circuit.
  • Figure 8 shows the external view of a pump according to the invention.
  • the end of a shaft 202 protrudes from a pump housing 200.
  • Figure 8 is used to orient two cuts, of which the section K-K through the rotating group in Figure 9 is shown and the section L-L in Figure 10 through adjacent pressure channels with integrated check valves.
  • the pump itself must not run empty when the vehicle is parked, even if the pressure side loses oil due to valve spool leakages in the transmission control and the suction channel therefore also runs empty due to the principle of communicating tubes.
  • the internal channels of the pump are therefore arranged in such a way that even under these conditions the rotating group remains filled with oil at least over the middle of the shaft.
  • a representation of this internal oil channel guide can be seen in FIG. 9.
  • the rotation group consists, among other things, of the contour ring 1, of the rotor 3, of the vanes 5, of the shaft 7 and contains the two pressure areas 9 and the two suction areas 11.
  • a suction channel 206 is formed of an intermediate wall 208 in such a way that its inlet area 210 is arranged above the center of the shaft 7 and thus the rotation group remains filled with oil up to the height of the intermediate wall 208, even if the intake duct 206 should otherwise run empty.
  • the suction area 11 on the right side is also connected to the suction side 210 and thus to the suction channel 206.
  • FIG. 10 shows in section L-L from FIG. 8 the formation of the pressure channels in the pump according to the invention.
  • a first pressure channel 214 and a second pressure channel 216 are formed in the pump housing 200.
  • the first pressure channel 214 is assigned to the upper pressure range and closed by a check valve 218, the function of which will be explained later.
  • the lower pressure range of the wing cell pump is also closed by a check valve 220.
  • the lower pressure range with the check valve 220 is designed by a siphon-like design of the pressure channel 216 such that the oil definitely remains above the shaft center within this oil channel if the right part of the pressure channel 216 should run empty. This is made possible by the raised duct wall 224.
  • FIG. 11 shows the pump according to the invention in a further cross section such that the check valves 218 and 220 can be seen in cross section. They partially protrude into the pressure plate 59 from FIG. 6 in such a way that they close the upper pressure field 69 and the lower pressure field 71 against the pressure outlets 214 from FIGS. 10 and 216 from FIG.
  • the upper check valve consists of a valve seat 224, into which the sealing body 226 is pressed by means of a spring 228.
  • the valve seat 224 is additionally sealed off from the housing by a seal 230.
  • the seals of the pressure fields can also be recognized by the seal 232.
  • the lower check valve 220 is constructed identically and will not be described again here.
  • the function of the check valves is that the pressure areas are closed when the pump is at a standstill and the respective pressure areas are therefore only connected to their under-wing grooves, as described in FIGS. 2 to 6.
  • a pressure builds up within the rotation group, which causes the check valve body 226 to lift off its seats and thus enables the delivery of the pressure oil to the outside into the two pressure channels 214 and 216 and thus to the 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 primarily intended to be resistance elements, which do not necessarily have to be 100% tight.
  • the volume of the pressure fields of the plate 59 is thus connected to the pressure channels leading to the consumer via the check valves.
  • the check valves are designed as simple plate valves. Any other variants are possible.
  • the seat of this spring-loaded plate 226 is an automatic turned part, which, sealed with an O-ring, is installed in the pump housing and is positively fixed by shoulders in the pump housing and corresponding design of the pressure plates. Of course, it is also possible to omit the O-ring and press fit the seat with a transition or press fit. Because the rotating group itself must not run idle, the shaft is sealed to the outside with a shaft sealing ring 234. If the internal pump leakage collects in the shaft middle, the shaft sealing ring can open at a certain pressure and the leak oil can escape into the gear chamber. The exact function of this special shaft sealing ring, which can work as a check valve, has already been described in detail in another application.
  • a check valve is shown enlarged in the open state in FIG. 12.1 and in the closed state in FIG. 12.2. It can be seen that the plate valve body 226 in FIG. 12.1 is opened by the valve seat 224 by the opening stroke X, so that the pressure oil can flow into the corresponding pressure channel. In FIG. 12.2, the plate valve body 226 is pressed against the valve seat 224 by the force of the spring 228.
  • the suction process of the pump according to the invention now works as follows: In the worst case, for. B. after an aborted cold start when turning off a rotating diesel engine, all blades are in the slot base of the rotor near the small circle diameter of the cam ring. If the rotor turns when starting, the wings extend minimally due to the centrifugal force. The blades on the pressure side of the stroke contour also drive this way back into the rotor. The volume that the wing feeds into the lower wing groove when moving in is pushed almost without loss under a wing moving out on the suction side. This wing now comes out at least by the amount that the retracting wing is retracted. The centrifugal forces also act on the wing.
  • FIG. 13 shows a special configuration of the rotation group, in which asymmetrical pump divisions can also be achieved by different contour strokes.
  • the known components contour ring 1, rotor 3, wing 5 and the shaft 7 and the two pressure areas 9 and the two suction areas 11 have already been described in their function.
  • the representation of the small circle areas 236 and 238 of the cam ring contour is different in FIG. While the right small circle area 236, as is normally designed for vane pumps, corresponds approximately to the outer diameter of the rotor 3, the small circle area 238 on the left side is provided with a larger radius than the outer radius of the rotor 3, so that a considerable gap is created here.
  • the two large circle areas 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 for moving from a small circle radius 236 to a large circle radius 242, which corresponds, for example, to 60% suction, based on the total delivery volume of the pump.
  • a small circle radius 236 corresponds, for example, to 60% suction, based on the total delivery volume of the pump.
  • a large circle radius 242 corresponds, for example, to 60% suction, based on the total delivery volume of the pump.
  • this large circle radius 240 is then used again for the smaller small circle radius 236, this means that the oil is squeezed out 60%.
  • the aspirated cell volumes differ from the expressed cell volumes.
  • This solution can have advantages if, for reasons of installation space, less installation space is available on one side than for suction or pressure ducts on the other.
  • the small circle remains at the same level and the large circles are of different sizes. It is important that both the small circle radius and the large circle radius or both radii can be varied independently of one another as desired.
  • the pump halves are hydraulically separated internally. This means that the correspondingly assigned lower wing areas and upper wing areas are separated. There is a common suction line and two separate pressure lines. A pressure field is assigned to each rotation group pressure output, which is required for the realization of the printing plate compensation. Channels are used within this pressure field, which serve to supply the underfloor of the respective pump half.

Abstract

L'invention concerne une pompe, notamment une pompe à cellules semi-rotative, qui comprend une bague de contour à levée double, un rotor, des pales, des plaques latérales, un carter et un couvercle de carter, ainsi que des rainures de pales inférieures pour alimenter les faces inférieures des pales en pression. Les pales montées déplaçables dans le sens radial sont comprimées vers l'extérieur contre la bague de contour, sous l'effet de la pression.
EP02798289A 2001-12-27 2002-12-20 Pompe Expired - Lifetime EP1461533B1 (fr)

Applications Claiming Priority (3)

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

Publications (2)

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

Family

ID=7711042

Family Applications (1)

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

Country Status (6)

Country Link
EP (1) EP1461533B1 (fr)
AU (1) AU2002363838A1 (fr)
DE (2) DE10259894A1 (fr)
FR (1) FR2834317B1 (fr)
IT (1) ITMI20022764A1 (fr)
WO (1) WO2003056180A1 (fr)

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EP3835585A1 (fr) * 2019-12-02 2021-06-16 FTE automotive GmbH Pompe à liquide, en particulier pour alimenter une transmission ou un embrayage dans le train d'entraînement d'un véhicule à moteur

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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 (fr) 2014-06-16 2015-12-23 Magna Powertrain Bad Homburg GmbH Dispositif de pompage
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
US11215177B2 (en) * 2015-06-02 2022-01-04 Hanon Systems Efp Deutschland Gmbh Vane pump and method for the operation thereof
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
DE102020105173A1 (de) * 2020-02-27 2021-09-02 Fte Automotive Gmbh Pumpenaggregat für einen Antriebsstrang eines Kraftfahrzeugs

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3835585A1 (fr) * 2019-12-02 2021-06-16 FTE automotive GmbH Pompe à liquide, en particulier pour alimenter une transmission ou un embrayage dans le train d'entraînement d'un véhicule à moteur
US11686306B2 (en) 2019-12-02 2023-06-27 Fte Automotive Gmbh Liquid pump, in particular for providing a supply to a transmission or to a clutch in the drive train of a motor vehicle

Also Published As

Publication number Publication date
DE10259894A1 (de) 2003-07-17
AU2002363838A1 (en) 2003-07-15
EP1461533B1 (fr) 2012-06-20
DE10297707D2 (de) 2005-02-17
FR2834317A1 (fr) 2003-07-04
WO2003056180A1 (fr) 2003-07-10
ITMI20022764A1 (it) 2003-06-28
FR2834317B1 (fr) 2006-06-09

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