EP1461533B1 - Pump - Google Patents

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Publication number
EP1461533B1
EP1461533B1 EP20020798289 EP02798289A EP1461533B1 EP 1461533 B1 EP1461533 B1 EP 1461533B1 EP 20020798289 EP20020798289 EP 20020798289 EP 02798289 A EP02798289 A EP 02798289A EP 1461533 B1 EP1461533 B1 EP 1461533B1
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EP
European Patent Office
Prior art keywords
pressure
pump
vane
under
characterised
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.)
Active
Application number
EP20020798289
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German (de)
French (fr)
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EP1461533A1 (en
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
Priority to DE10164250 priority Critical
Priority to DE10164250 priority
Application filed by ixetic Bad Homburg GmbH filed Critical ixetic Bad Homburg GmbH
Priority to PCT/DE2002/004678 priority patent/WO2003056180A1/en
Publication of EP1461533A1 publication Critical patent/EP1461533A1/en
Application granted granted Critical
Publication of EP1461533B1 publication Critical patent/EP1461533B1/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064Arrangements 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
    • F04C15/066Arrangements 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08Rotary pistons
    • F01C21/0809Construction of vanes or vane holders
    • F01C21/0818Vane tracking; control therefor
    • F01C21/0854Vane tracking; control therefor by fluid means
    • F01C21/0863Vane tracking; control therefor by fluid means the fluid being the working fluid
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023Axial sealings for working fluid
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/30Rotary-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
    • F04C2/34Rotary-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
    • F04C2/344Rotary-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
    • F04C2/3446Rotary-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

Abstract

The invention relates to a pump, particularly a vane pump or roller cell pump, provided with a two-stroke contour ring, a rotor, vanes, side plates, a casing, a casing cover and with lower vane grooves for supplying the lower vane surfaces with pressure, whereby the vanes, which are mounted inside the rotor in a manner that enables them to be radially displaced, are pressed outward against the contour ring by this pressure.

Description

  • The invention relates to a pump as defined in the preamble of claim 1. Such 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. In this case, 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. Likewise, 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.
  • The task is solved by a pump according to the features of claim 1. This has the consequence that the underflügelversorgung is designed such that on the channels in the side plates no direct Short circuits occur and the wings are always pressed with the necessary pressure to the contour to prevent unwanted lifting and resulting short circuits.
  • 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. In a pump according to the invention, the pressure fields are sealed by sealing means.
  • Preferably, in a pump from each pressure field, the respective Unterflügelnut or Unterflügelniere supplied with high pressure or circulation pressure, in particular via channels within the respective pressure field.
  • This means that the pump halves are internally hydraulically separated. The correspondingly assigned lower wing areas and upper wing areas are separated. There is a common suction line and two separate pressure lines. Each vane pressure output is assigned a pressure field required for the realization of the pressure plate compensation. Within this pressure field channels are realized, which serve to Unterflügelversorgung the respective pump half.
  • The Unterflügelnut 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.
  • The leading wing of the cell, which just finishes the Ausdrückvorgang must only with its slot area under the wing, the Unterflügelniere, which is assigned to the corresponding pressure range of the associated pump half leave when the trailing wing has no connection to the pressure kidney. Only thereby can be made possible that the leading wing is always pressed with a sufficiently large pressure against the contour and there is no wing lifting or short circuits.
  • The invention will now be described with reference to the figures.
  • FIG. 1
    shows schematically the construction of a zwehübigen double-vane vane pump.
    FIG. 2
    shows a rotation group according to the invention with undercut groove according to the invention.
    FIG. 3
    also shows a rotation group with a Unterflügelnut invention.
    FIG. 4
    shows a side plate.
    FIG. 5
    shows an opposite side plate.
    FIG. 6
    shows the outside of a side plate with two separate pressure fields.
    FIG. 7
    shows the hydraulic circuit diagram of a double-flow pump.
    FIG. 8
    shows the outside view of a pump according to the invention.
    FIG. 9
    shows the cross section KK of FIG. 8 ,
    FIG. 10
    shows the cross section LL of FIG. 8 ,
    FIG. 11
    shows a further cross section of FIG. 8 ,
    FIG. 12
    shows check valves in cross section.
    FIG. 13
    shows different contour strokes.
  • In FIG. 1 schematically the structure of a zweihübigen, double-vane vane pump is shown. Within a doppelhübigen cam ring 1, a rotor 3 with extendable wings 5 is shown. 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. Upon rotation of the rotor 3, the cells between two wings increase in the suction chamber 11 and thus suck fluid in the rotation group. In the pressure region 9, the cell volumes between two wings shrink and thus squeeze the fluid out of the pressure regions 9.
  • In the following, we will now discuss the special circuit of a double-flow pump. 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. Furthermore, 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 Unterflügelnut 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 Unterflügenut 31 is in turn connected to the Unterflügelnut 33 in the lower pressure region 9 of this pump half. This means that for each half of the twin-vane vane pump, the respective pressure area supplies the underflute grooves with pressure and thus presses the wings hydraulically against the contour ring 1. Now, if one of the two vane pump halves is depressurized, because a corresponding consumer does not need the pressure, so that the lower wing area is depressurized, so that the wings can continue to move substantially pressure balanced in each pump area. In the depressurized state, a minimum circulating pressure of up to 3 bar is present, which, in addition to the centrifugal force, also helps to move the blades out.
  • 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. This means that the wing 39 has to be supplied up to here with high pressure from the Unterflügelnut 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. When moving on into the suction region 41 of the next vane pump half of the wing head from above is depressurized, and thus 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. Likewise, 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 Unterflügelnut 25 again with pressure.
  • FIG. 3 shows a slightly different extender extension of the undercut groove 35. When the wing 37 just leaves the upper pressure kidney 9, the wing 39 is one half of its wing thickness in the subsequent Unterflügelnut 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.
  • In 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.
  • In FIG. 5 is the counter-plate 59, which covers the rotation group on the other side of the vane pump shown. Below the suction kidney 11 is the Unterflügelnutenbereich 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 Unterflügelnut 27 to the part 35 is here a mirror image of the plate FIG. 4 arranged. To recognize 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 Unterflügelnutenbereiche. 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 Unterflügelnuten. Furthermore, in FIG. 5 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.
  • In FIG. 6 These breakthroughs 65 and 67 are also recognizable. In FIG. 6 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. Thus, the oil expressed from the pressure kidneys 9 of the vane pump becomes loud FIG. 1 is forwarded into the pressure lines 19 or 21, supplied via here embedded in the pressure plate channels 75 and 77 and the openings 65 and 67 to the corresponding Unterflügelnuthälften. 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. In this diagram, only one consumer port 113 and a non-pressurized circulation circuit for the pump half 101 is provided. 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. 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. To protect the hydraulic circuit, 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.
  • In FIG. 10 is on average LL from the FIG. 8 the formation of the pressure channels shown in the pump according to the invention. In the pump housing 200, a first pressure channel 214 and a second pressure channel 216 is formed. 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. Likewise, 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.
  • In 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 Unterflügelnuten, as in the FIGS. 2 to 6 are described connected. After the start of the promotion 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.
  • In Figure 12.1 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. With more and more outgoing wings creates a kind of centrifugal pump action. The resulting flow and delivery pressure is due to the check valve elements, completely brought to the underfloor supply of the associated pump half. The special design of the underfloor channels and the non-return elements creates a self-reinforcing effect, which leads to safe suction of the pump. For this initial kick oil is needed, which is provided by the formation of the siphon-like channels. If the pump is now pumping oil, opening the check valves, and the pump is idling, it will remain in operation, even if it is now delivering air due to an empty suction pipe. The pressure built up by the check valves is sufficient to maintain the function of the pump hold. Now the pump sucks so long, until oil from z. B. is sucked in a filter. The oil in the siphons is needed for the initial kick to break open the wings sticking strongly in the slots and start the self-energizing mechanism.
  • 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. Different is in FIG. 13 now the representation of the small circle portions 236 and 238 of Hubringkontur. While the right small circle region 236, as normally designed for vane pumps, approximately corresponds to the outer diameter of the rotor 3, the small circle portion 238 is provided on the left side with a larger radius than the outer radius of the rotor 3, so that here a considerable gap is formed. 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. When 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. If this large circle radius 240 then moves back to the smaller small circle radius 236, this means a 60% expressions of the oil. In this variant, therefore, 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. In the simplest case, 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.
  • All solutions described in this application can be used in vane pumps with a doppelhübigen contour ring, in which each pump half can promote oil separately at different pressure levels and either different pressure circuits are supplied with oil or in which a pump half is switched without pressure in the circulation for energy saving reasons.
  • 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 Unterflügelversorgung the respective pump half.

Claims (13)

  1. Pump, more particularly a vane cell pump or roller cell pump, with a two-stroke contour ring (1), with a rotor (3), with vanes (5), with side plates (57, 59), with a housing (200) and with a housing cover, with under-vane grooves for supplying the lower vane faces with pressure, wherein the vanes (5) mounted displaceable radially in the rotor (3) are pressed outwards against the contour ring (1) by the pressure wherein the under-vane groove is divided into two and each one part, seen in the direction of rotation, extends under a suction kidney (11) and at least one successive pressure kidney (9) and wherein the under-vane groove is divided into two so that the under-vane groove (25) which is associated with the suction area of the one pump half is in communication with the associated under-vane groove (27) which is associated with the pressure area of the same pump half, and there are no connections to the under-vane grooves of the other pump half, and wherein the part of the under-vane groove (27) lying underneath the pressure kidney (9), seen in the direction of rotation, is extended substantially by the angular amount (35) of a leading cell, characterised in that the extension (35) of the under-vane groove is configured so that the leading vane (39) of the leading cell stands by only a maximum of one half of a vane thickness in the next, possibly pressureless, under-vane groove (51) when the trailing vane (37) of the leading cell has just left the pressure kidney (9) positioned above the under-vane groove.
  2. Pump according to claim 1 characterised in that the under-vane groove on the opposite side of the rotation group, i.e. on the other plate (39) or where applicable in the housing or in the housing cover, has the same division (53, 55) at the same place as the first plate.
  3. Pump according to one of the preceding claims characterised in that the pressure plate (57) and/or the counter plate (29) has two high pressure fields (69, 71) with pressure-tight borders between which is located a suction pressure field.
  4. Pump according to claim 3 characterised in that the high pressure fields (69, 71) are sealed by sealing devices (232).
  5. Pump according to one of the preceding claims characterised in that each relevant under-vane groove or under-vane kidney is supplied with high pressure or circumferential pressure from each high pressure field (69, 71), more particularly via channels (75, 77) inside the relevant pressure field (69, 71).
  6. Pump according to one of the preceding claims characterised in that the internal suction intake and pressure channels (206, 214, 216) of the pump are arranged so that the rotation group when stationary at least over the shaft centre remains full of oil.
  7. Pump according to one of the preceding claims characterised in that the two pressure channels (214, 216) are each closed by a non-return valve (218, 220).
  8. Pump according to one of the preceding claims characterised in that the non-return valves (218, 220) when the pump is stationary close the pressure areas from the outside and thus the relevant pressure areas are each only connected to their under-vane grooves.
  9. Pump according to one of the preceding claims characterised in that the shaft (7) is sealed from the outside by a shaft sealing ring (234) which from a specific pressure functions as a non-return valve and lets leakage oil escape into the gearbox chamber.
  10. Pump according to one of the preceding claims characterised in that non-symmetrical pump divisions can be achieved through different contour strokes.
  11. Pump according to one of the preceding claims characterised in that a small circular area (238) is provided with a larger radius than the outer radius of the rotor (3).
  12. Pump according to one of the preceding claims characterised in that the two large circular areas (240, 242) are of different size.
  13. Pump according to one of the preceding claims characterised in that both the small circular radii (236, 238) and the large circular radii (240, 242) as well as the two radii together can be altered in any way independently of one another.
EP20020798289 2001-12-27 2002-12-20 Pump Active EP1461533B1 (en)

Priority Applications (3)

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

Publications (2)

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EP1461533A1 EP1461533A1 (en) 2004-09-29
EP1461533B1 true EP1461533B1 (en) 2012-06-20

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EP20020798289 Active EP1461533B1 (en) 2001-12-27 2002-12-20 Pump

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

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011042105A2 (en) * 2009-10-07 2011-04-14 Ixetic Bad Homburg Gmbh Vane pump
GB2486007B (en) 2010-12-01 2017-05-10 Itt Mfg Enterprises Inc Sliding vane pump
DE102013108697A1 (en) * 2013-08-12 2015-02-12 Zf Lenksysteme Gmbh Displacement pump, especially adjustable wing cell pump
WO2015193170A1 (en) 2014-06-16 2015-12-23 Magna Powertrain Bad Homburg GmbH Pump device
DE102014222321B3 (en) * 2014-10-31 2015-12-10 Magna Powertrain Bad Homburg GmbH Vane pump with improved starting behavior
DE102014222322B3 (en) 2014-10-31 2016-02-04 Magna Powertrain Bad Homburg GmbH Vane pump with improved starting behavior
FR3033609A1 (en) * 2015-03-09 2016-09-16 Yves Gringoz Hydrostatic guidance with pressure shift
DE102015105933B4 (en) * 2015-04-17 2018-04-26 Schwäbische Hüttenwerke Automotive GmbH Pump
DE102015215982B4 (en) * 2015-08-21 2017-03-16 Magna Powertrain Bad Homburg GmbH Pump and system for supplying a consumer
DE102016216681A1 (en) 2015-09-11 2017-04-13 Magna Powertrain Bad Homburg GmbH Variable displacement pump with underfloor supply and procedure
DE102018200225B3 (en) * 2018-01-09 2019-03-07 Magna Powertrain Bad Homburg GmbH Pump assembly for a vehicle, and control for a pump assembly and method

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 (en) * 1992-03-16 2000-02-28 株式会社デンソー Fluid machinery

Also Published As

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

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