EP0758716A2 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
EP0758716A2
EP0758716A2 EP96112844A EP96112844A EP0758716A2 EP 0758716 A2 EP0758716 A2 EP 0758716A2 EP 96112844 A EP96112844 A EP 96112844A EP 96112844 A EP96112844 A EP 96112844A EP 0758716 A2 EP0758716 A2 EP 0758716A2
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
plate
area
fluid
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
EP96112844A
Other languages
German (de)
English (en)
Other versions
EP0758716A3 (fr
EP0758716B1 (fr
Inventor
Ivo Agner
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.)
LuK Fahrzeug Hydraulik GmbH and Co KG
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
Priority claimed from DE19531701A external-priority patent/DE19531701C1/de
Priority claimed from DE1996129336 external-priority patent/DE19629336C2/de
Application filed by LuK Fahrzeug Hydraulik GmbH and Co KG filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Publication of EP0758716A2 publication Critical patent/EP0758716A2/fr
Publication of EP0758716A3 publication Critical patent/EP0758716A3/fr
Application granted granted Critical
Publication of EP0758716B1 publication Critical patent/EP0758716B1/fr
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
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • 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

Definitions

  • the invention relates to a pump, in particular a vane pump, according to the preamble of claim 1.
  • Pumps, in particular roller cell and vane pumps of the type mentioned here are known.
  • DE 28 35 816 A1 shows a pump with a rotor, in the peripheral wall of which vanes-receiving slots are made.
  • the rotor rotates within a contour ring, which forms at least one, here two crescent-shaped conveying spaces through which the blades pass.
  • the rotor rotates, there are larger and smaller spaces, and thus suction and pressure areas.
  • the fluid delivered by the vane pump for example hydraulic oil
  • its viscosity increases so that the mobility of the vanes decreases. If the pump is now put into operation, a cold start due to the short circuit in a pump section may result in a greatly reduced delivery rate.
  • a sealing element as a hydraulic resistance element is particularly advantageous. Since the sealing element completely seals off a fluid path, it is therefore a resistance element with an infinite resistance. Because the sealing element in particular interrupts the connection of the two pressure areas to one another, here also the fluid path from the pressure side of the pump to a consumer, the hydraulic oil delivered during the start of the pump is used exclusively for the lower wing area, i.e. exclusively for the wings ( for a roller cell pump Rollers) in their functional position.
  • An embodiment of a vane pump is preferred in which a fluid connection is first established to a lower vane area leading the delivery opening. Pressure is thus applied to the lower wing area of those wings which are currently passing through the suction area.
  • the function of the pump section, which otherwise does not deliver hydraulic oil during a cold start, is supported here.
  • An embodiment of a vane pump is also preferred, in which the hydraulic resistance element has a finite resistance, an adjustment of the resistance value being achievable by appropriately designing channel or groove cross sections.
  • the invention described below relates to both vane pumps and roller cell pumps.
  • the following description is based purely on vane pumps.
  • a first embodiment of a pump designed as a vane pump 1 is shown highly schematically in longitudinal section. It has a basic housing 3 which is penetrated by a drive shaft 5 which engages in a rotor 7.
  • the rotor 7 is provided on its circumferential surface with radially extending slots in which blades are movably arranged.
  • the rotor 7 is surrounded by a contour ring 9, the inner surface of which is designed such that at least one, preferably two crescent-shaped delivery spaces are formed. These are traversed by the blades, with two pump sections, each with a suction and a pressure area.
  • the rotor 7 and the contour ring 9 lie sealingly on a sealing surface of the basic housing 3.
  • a pressure plate 11 is provided, through which the fluid delivered by the vane pump 1 is guided from the pressure side of the pump into a pressure chamber 13, which is part of a fluid path leading from the pressure side to a consumer.
  • the pressure plate 11 is traversed with pressure channels 15 which on the one hand open to the pressure area of the pump sections and on the other hand to the pressure chamber 13.
  • the delivery openings of the pressure channels 15 opening into the pressure chamber 13 are designated and designed by a cold start plate 17 here Sealed sealing element, which is pressed by a pressure spring 19, for example, a plate spring with a biasing force on the pressure plate 11.
  • the fluid, preferably oil, delivered by the vane pump 1 reaches a consumer, for example a power steering device or a transmission.
  • FIG. 2 shows a greatly enlarged surface 33 of the pressure plate 11 which faces the cold start plate 17 (not shown in FIG. 2).
  • Two kidney-shaped delivery openings 21 and 23 can be seen here, which lead via the pressure channels 15 to the pressure areas of the pump sections.
  • the pressure channels 15 preferably have a passage area which is at most 1/3 of the passage area of the delivery openings 21, 23.
  • a suction area 25 of the first pump section indicated here belongs to the pressure area assigned to the delivery opening 21.
  • the suction area 27 of the second pump section is correspondingly assigned to the pressure area associated with the delivery opening 23.
  • the pressure plate 11 is here provided with supply channels running essentially perpendicular to the image plane, through which the pressurized fluid or hydraulic oil reaches the lower wing areas of the pump sections.
  • a first feed opening 29 can be seen here, in which the feed channel of the first lower wing section opens, and also a second feed opening 31, in which the one assigned to the second lower wing area Feed channel in the printing plate surface 33 opens.
  • FIG. 2 shows that grooves 35 and 37 serving as fluid connections are made in the pressure plate surface 33.
  • the first groove 35 runs from the delivery opening 21 to the feed opening 31
  • the second groove 37 extends from the delivery opening 23 to the feed opening 29.
  • the delivery openings of one pump section thus supply the lower wing area of the other, leading pump section.
  • the imaginary dividing line between the two pump sections is indicated by a dashed diagonal 39.
  • FIG. 3 in turn shows the printing plate surface 33 of a printing plate 11. Parts which correspond to those in FIG. 2 are provided with the same reference numerals, so that their description can be dispensed with here.
  • Fluid connections designed as grooves are also introduced into the pressure plate surface 33 here, but their course differs from that explained with reference to FIG. 2 insofar as the delivery opening 21 has no connection to any grooves.
  • two grooves 37a and 37b are provided on the conveyor opening 23, which lead to the feed openings 29 and 31. Both lower wing areas are therefore supplied with hydraulic oil from the delivery opening of a pump section.
  • the cold start plate has been removed in order to make the contours on the printing plate surface 33 more recognizable.
  • the contact area or contact area 41 between the pressure plate 11 and cold start plate 17 is shown in dashed lines. It can be seen that the contact area between the two plates is significantly smaller than their surface or overall cross section.
  • the outer contour 43 of the cold start plate 17 is also indicated in FIG. 4.
  • the printing plate surface 33 has conveying openings 21 and 23 and feed openings 29 and 31.
  • a fluid connection designed as a channel 37c extends from the conveying opening 23 to the feed opening 29.
  • the two feed openings 29 and 31 are connected to one another by an annular groove 45 which is in fluid communication with the channel 37c.
  • the annular groove 45 is therefore also connected to the delivery opening 23 via the channel 37c designed as a groove.
  • the channel 37c running between the conveying opening 23 and the supply opening 29 is formed deeper than the annular groove 45. It is also possible to make the channel 37c a mirror image and not to run to the feed opening 29 but to the feed opening 31.
  • the contact area 41 is placed in such a way that the pressure areas of the pump sections which open into the pressure plate surface 33 via the delivery openings 21 and 23 are covered to the outside.
  • the cold start properties of the pump are already significantly improved if only the delivery opening 23 of the lower pump section is closed by the cold start plate 17.
  • the contact area 41 completely surrounds the feed openings 29 and 31 and the delivery opening 23 and closes off the fluid path to the pressure chamber 13 or to the consumer which originates from the delivery opening 21.
  • the pressure areas of the vane pump 1 are separated from one another by the cold start plate 17, which rests on the pressure plate 11 and serves as sealing elements or as a hydraulic resistance element with infinite resistance.
  • no grooves are connected to the delivery opening 21. It is rather the case that the delivery opening 23 of the pump section located underneath supplies the lower wing regions of both pump sections with hydraulic oil. This takes place in that on the one hand hydraulic oil emerging from the delivery opening 23 reaches the supply opening 29 and on the other hand in that hydraulic oil emerging from the delivery opening 23 is led to the supply opening 31 through the groove 37b. With that thus the under-wing areas of both pump sections are acted upon by the hydraulic oil of a single delivery opening 23 with delivered oil and thus with pressure.
  • the hydraulic oil which is very viscous in the cold start, first reaches the feed opening 29 through the channel 37c, since the larger delivery cross section is given here. A significantly smaller proportion of the oil produced is conveyed through the annular groove 45 to the feed opening 31, since there is greater hydraulic resistance here due to the smaller depth of the annular groove 45.
  • hydraulic oil is supplied to the lower wing area of the suction area leading the delivery opening 23.
  • the cold start plate 17 lifts against the force of the pressure spring 19 from the pressure plate 11, so that the two delivery openings 21 and 23 are released and the oil delivered can reach the consumer via the pressure chamber 13.
  • the contact area 41 is chosen to be as small as possible so that the cold start plate 17 does not adhere to the pressure plate 11, moreover it is avoided that the hydrodynamic paradox comes into effect and the cold start plate 17 is attracted to the pressure plate 11 by escaping oil.
  • both centering and anti-rotation of the cold start plate 17 are required, for example by pins 47 and 49, which are shown in FIG.
  • the pins already used for centering the pressure plate and the contour ring are preferably designed to be extended so that they can engage in corresponding bores in the cold start plate 17. It has turned out to be particularly advantageous, however, to use the pins 47, 49 also for centering the pressure spring 19. Because the pins penetrate the cold start plate 17 and interact with the spring, the pins already present in vane pumps can be used for a further function. Consequently, no additional parts have to be provided for centering the spring.
  • the delivery opening 21 is closed in a pressure-tight manner with respect to the delivery opening 23, it is prevented at the start that the oil delivered by the lower pump section via the delivery opening 23 into the delivery opening 21 of the upper pump section enters and from there - because of the retracted wing - immediately returns to the suction area of the upper pump section without the pressure required to supply the lower wing areas being built up.
  • a continuous circumferential groove, labeled 50 in FIG. 1, which is arranged on the side of the rotor 7 opposite the pressure plate 11, can be divided into two parts by hydraulic resistances, for example by webs, a region of the groove 50 in each case being a lower wing region is assigned to a pump section. This ensures that hydraulic oil supplied to a lower wing area does not flow to the lower wing area of the other pump section which does not yet have a delivery function during the cold start. It is essential that the hydraulic resistance between the suction and the pressure area of a pump section is greater than between these areas and the suction and pressure area of the other pressure area of the pump.
  • the fluid connections provided in the pressure plate surface 33 and formed as grooves 35, 37, 37a, 37b, 37c can also be introduced in the surface of the cold start plate 17 facing the pressure plate 11. Furthermore, it is also possible to provide grooves in the pressure plate surface 33 as well as in the cold start plate 17 for supplying the lower wing areas. It is essential that in the cold start the pressure areas of the vane pump 1 are separated from each other and here also from the pressure chamber 13 and pure under-wing operation is guaranteed, in which the hydraulic oil delivered in the starting phase is supplied exclusively to the under-wing areas.
  • the cold start plate 17 can be made of a suitable metal or plastic.
  • the pressure force of the pressure spring 17 can be matched to the operating behavior of the vane pump 1 in individual cases. It is also possible to ensure the contact pressure acting on the cold start plate by the pressure spring pressing the pressure plate against the rotor 7.
  • the trailing lower wing area associated with the delivery opening 23 can be supplied with hydraulic oil via the feed opening 31 and / or the leading lower wing area of the other pump section via the feed opening 29. It is also conceivable that oil is applied to both lower wing areas, different delivery capacities being able to be distributed to the lower wing areas through different groove cross sections. With such a configuration, oil can also be pumped through an empty suction pipe. The pump can thus convey air in the start-up phase, the cold start or start properties of the pump then also being significantly improved by the hydraulic resistance element (sealing element) referred to as the cold start plate. In this case, air is supplied to the lower wing areas when the pump starts.
  • the hydraulic resistance element sealing element
  • FIGS. 5 and 6 Examples of pumps which have two pressure plates are described with reference to the following FIGS. 5 and 6. As in the exemplary embodiments illustrated in FIGS. 1 to 4, these are double-stroke vane pumps. The same parts, which have already been explained with reference to FIG. 1, have the same reference numbers, so that their description can be dispensed with here.
  • the vane pump 101 shown in FIG. 5 has a rotor 7, which is accommodated in a basic housing 3 and is rotatably mounted within a contour ring 9. From the sectional view in FIG. 5 it can be seen that pressure plates 11a and 11b are provided on both end faces of the rotor 7 and the contour ring 9.
  • the right-hand pressure plate 11a is constructed identically to that of the exemplary embodiment explained with reference to FIG. 1. It has two pressure channels 15 penetrating the pressure plate, which open into a pressure chamber 13 via conveyor openings explained with reference to FIGS. 2 to 4, to which a consumer can be connected in a suitable manner, for example via a connection 51.
  • the start-up or cold start plate 17 On the surface of the pressure plate 11a facing away from the rotor 17 there is a sealing element, referred to as the start-up or cold start plate 17, which closes the lower pressure channel 15 of the lower pump section of the pump 101.
  • the lower pressure channel 15 is via a suitable fluid connection 51 ', which is shown in FIGS was explained in detail, connected to the lower wing region 53 of the lower and / or upper pump section.
  • the cold start plate 17 closes off the fluid connection 51 'from the pressure chamber 13, so that while the cold start plate 17 is in sealing contact with the pressure plate 11a, a fluid emerging from the pressure channel 15 reaches the lower wing region 53 via the fluid connection 51'.
  • the cold start plate does not close the upper delivery opening of the upper pump section, no delivered fluid can pass from the lower pressure channel 15 to the upper pressure channel 15 via the pressure chamber 13. It is therefore possible to make the cold start plate 17 so small that it only closes the delivery opening of the lower pump section with respect to the pressure chamber.
  • a second pressure plate 11b is provided, which has a passage 55, which is assigned to the pressure region of the lower pump section, to a closed space 57. Fluid conveyed through the passage 55 into the space 57 leads to an overpressure in this space, so that the left pressure plate 11b is pressed sealingly against the rotor and contour ring.
  • FIG. 6 This also applies to the exemplary embodiment of a vane pump 201 shown in FIG. 6, which is also designed as a double-stroke pump with two pressure plates 11a and 11b, which, as can be seen from the sectional view according to FIG. 6, on the end faces of a rotor 7 or an associated contour ring 9 issue.
  • the same parts are provided with the same reference numbers here, so that reference can be made to the description according to FIG. 5 and to that according to FIG. 1.
  • the left pressure plate 11b is here provided with a pressure channel 15 ′′, which is in fluid communication with a lower wing region 53 via a fluid connection 51.
  • the fluid connection does not need to be terminated here, since the pressure channel 15 ′′, like the lower wing region 53, open into the pressure-tightly closed space 57.
  • the pressure plate 11a contains the pressure channel 15 ', which is arranged here on the right side of the rotor 7 and is closed off from the pressure chamber 13 by the sealing element, which in turn is designed here as a cold start plate. It can be assumed that Figures 5 and 6, like the other Figures 7 to 9 and 1 represent pumps that are in the start-up or cold start phase, in which the pressure delivered is not sufficient to lift the sealing element or the cold start plate 17 from the associated pressure plate.
  • the conveying pressure kidney is connected to at least one lower wing area of the pump, in order to ensure that the wings or rollers are moved outward against the contour ring, so that the conveying properties of the pump are improved during the start-up phase.
  • the cold start plate 17 ensures in the start-up or cold start phase that none from the lower pump area Hydraulic oil reaches a consumer via the pressure chamber 13.
  • the extracted oil is rather conveyed via the left pressure channel 15 ′′ to the closed space 57 and reaches the lower wing area 53 of the lower pump section via a fluid connection, which is only exemplarily designed as a groove in the pressure plate 11b.
  • the fluid connection 51 does not have to be made as a groove in the surface of the pressure plate 11b, since there is a fluid connection from the lower pressure channel 15 ′′, via the hermetically sealed space 57 to the lower wing area 53.
  • the basic principle of a single-stroke pump 301 becomes clear from the highly schematic top view of a rotor 7 and a contour ring 9 shown in FIG.
  • the rotor is provided with radially extending slots 59, in which vanes 61 are movably accommodated here, for example.
  • the rotor 7 is accommodated eccentrically in the contour ring 9, so that a practically crescent-shaped conveying space 63 is formed, which the wings 61 pass through — here counterclockwise.
  • FIG. 8 shows a first embodiment of the pump 301 addressed in FIG. 7 with two pressure plates 11a and 11b, which are arranged on the right and left of a rotor 7 and a contour ring 9 assigned to them.
  • the right pressure plate 11a is provided with the grooves 69 and 71, of which the groove 69 assigned to the suction area 65 is in hydraulic connection with the pressure area or with a pressure channel 15 assigned to the pressure area via a fluid connection 51.
  • the fluid connection 51 is designed here as a groove made in the pressure plate 11a, which is located in the surface of the pressure plate facing away from the rotor 7.
  • the fluid connection 51 between the pressure channel 15 and the groove 69 is closed by a sealing element designed as a cold start plate 17, so that fluid emerging from the pressure channel 15 cannot get into the pressure chamber 13.
  • the cold start plate 17 is pressed against the pressure plate 11a by a pressure spring 19.
  • a second pressure plate 11b Opposite the pressure plate 11a, on the other side of the rotor 7 or contour ring 9, there is a second pressure plate 11b which is provided with a circumferential groove 73 which connects the lower wing regions of both the suction region 65 and the pressure region 67 to one another.
  • the blades entering the pressure area deliver hydraulic oil to the blades extending in the suction area 65, which increases the functional reliability of the pump.
  • the pressure area 67 of the pump 301 can be connected to a closed space 57 via a passage 55. This ensures that the left pressure plate 11b is pressed against the rotor 7 and the contour ring 9 and the leakage is reduced to a minimum.
  • the left pressure plate 11b can be dispensed with and that here a sealing surface can be formed directly by the housing, which abuts the rotor and the contour ring.
  • the pump 301 is designed as a pump with two pressure plates, it is advantageous if the passage 55 penetrates the pressure plate so that oil can get into the space 57 and the pressure plate is pressed against the rotor.
  • FIG. 9 finally shows a further exemplary embodiment of a pump 401, in which the pressure plates 11a and 11b of the pump 301 explained with reference to FIG. 8 are ultimately interchanged.
  • the same parts are therefore provided with the same reference numbers.
  • a sealing element here by a cold start plate 17. It is clear that the pressure channel 15 can be closed by any sealing element.
  • a passage 55 is provided, which opens into a hydraulically closed space 57 and which thus establishes a fluid connection to a lower wing area 53, which is assigned to the suction area 65.
  • the left pressure plate 11a can also have a fluid connection 51 in the form of a groove, as was provided for the pressure plate 11a of the pump 301 according to FIG.
  • the pressure plate 11b is in turn provided with a circumferential groove 73.
  • the fluid present in the pressure region 67 cannot reach the consumer in the start-up or cold start phase.
  • the sealing element or the cold start plate 17 ensures that the fluid is only available to the lower wing area 53 of the suction area 65, so that the pumping properties of the pump 401 are improved very quickly.
  • FIG. 10 shows a further embodiment of a double-stroke vane pump 1 in longitudinal section, the upper half representing a section through the pressure area and the lower half representing a section through the suction area.
  • the vane pump corresponds essentially to that shown in FIG. 1, so that the parts identified by the same reference numerals are not described again.
  • the essential difference from the pump shown in FIG. 1 is that in this exemplary embodiment the cold start plate as a hydraulic resistance element with infinite resistance is replaced by a hydraulic resistance element with finite resistance.
  • channels 117 which on the side facing the rotor open into lower wing areas, not shown, and on the opposite side into the pressure chamber 13 or into the pressure channels 15.
  • the grooves 35, 37 of the previous exemplary embodiments are provided with grooves 119 which are essentially corresponding to the surface of the pressure plate 11.
  • This inventive design of the hydraulic resistors leads to the cold viscous fluid initially taking the path of least resistance and in this way preferably flowing out of the pressure areas into the lower wing areas.
  • the delivery rate of the lower pump section becomes the under-wing supply of the upper pump section.
  • the delivered fluid flows via a pressure channel 15 through the delivery opening 23 and the groove 119 to the feed opening 29 and through the feed channel 117 into the lower wing area.
  • the pressure built up in this lower wing area causes the wings to be pushed out.
  • the pressure plate shown in FIGS. 2 and 3 does not differ when used in the vane pump according to FIG. 10.
  • the separate groove guide shown in Figure 2 has the advantage, however, that the function is independent of the installation position of the pump. This is because the upper pump section can also be at the bottom when installed. This is not possible with the embodiment shown in FIG. 3, since then the non-working upper pump section for the under-wing supply would be responsible, but is not designed for it.
  • grooves are provided in the pressure plate surface or on the adjacent housing wall.
  • a combination of grooves both in the pressure plate and in the housing wall is also conceivable. It is only important that the hydraulic resistance between the pressure area and the lower wing area for a viscous fluid is significantly lower than to the consumer or to the other pressure area. It must therefore be guaranteed in any case that the fluid delivered to the lower pump section can build up pressure and does not flow away without pressure.
  • FIGS. 11 to 13 show further exemplary embodiments which are distinguished from the exemplary embodiments described above by a further pressure plate 11.2. These are also double-stroke vane pumps, the same parts, which have already been explained with reference to FIG. 10, bearing the same reference numerals, so that their description can be omitted here.
  • the vane pump 1 shown in FIG. 11 also has a rotor 7, which is accommodated in a basic housing and is rotatably mounted within a contour ring 9. From the sectional view it can be seen that 9 pressure plates 11.1 and 11.2 are provided on both end faces of the rotor 7 and the contour ring.
  • the right pressure plate 11.1 is constructed identically to that of the exemplary embodiment explained with reference to FIG. 10. It has two pressure channels 15 penetrating the pressure plate, which open into a pressure chamber 13, to which a consumer can be connected in a suitable manner. With the help of the channels 15 and 117, a fluid path 141 is thus formed which serves to supply at least one lower wing area.
  • a suitable choice of hydraulic resistance for example by providing webs, deeper grooves, throttles, etc., ensures that the viscous fluid preferably takes this route and not the fluid path 143 shown in dashed lines.
  • a circumferential groove 145 is provided in the pressure plate 11.2 opposite the first pressure plate 11.1, which serves for the under-wing supply.
  • the continuous circumferential groove 145 can be divided into two by hydraulic resistors, for example by webs, with an area of the groove being assigned to a pump section. This ensures that hydraulic oil supplied to a lower wing area does not flow to the lower wing area of the other pump section during cold start, which does not yet have a delivery function. It is essential that the hydraulic resistance between the suction and the pressure area of a pump section is greater than between these areas and the suction and pressure area of the other pressure area of the pump.
  • FIG. 12 shows a further exemplary embodiment of a vane pump 1, in which the pressure plate 11.1, however, only has pressure channels 15.
  • the lower wing areas are not supplied via this pressure plate.
  • the opposite pressure plate 11.2, on the other hand, has not only a pressure channel 15 but also a feed channel 117 in at least one lower wing area.
  • the pressure channel 15 opens into a hermetically sealed pressure chamber 147, into which the supply channel 17 also opens.
  • a pressure builds up in this pressure chamber 147, which on the one hand presses the pressure plate 11.2 tightly against the contour ring and rotor and on the other hand pressurizes both lower wing areas.
  • the groove 149 shown in FIG. 12 in the second pressure plate 11.2 can easily be omitted, provided that it is ensured that the hydraulic resistance of the fluid path 141 (pressure area-pressure space-lower wing area) is smaller than the fluid path 143 between the two pressure areas.
  • the exemplary embodiment of a vane pump 1 shown in FIG. 13 also works in the same way.
  • the second pressure plate 11.2 only has one pressure channel 15 which opens into the hermetically sealed pressure chamber 147. A fluid connection between the two pressure areas via the pressure space 147 is therefore also excluded here.
  • the feed channel 117 leading to a lower wing area is in turn provided in the first pressure plate 11.1.
  • the pressure plate 11.2 can also be designed in this case in accordance with the exemplary embodiments according to FIGS. 2 and 3.
  • the vane pump shown in FIG. 14a has, in addition to the parts already described in detail in connection with the preceding exemplary embodiments, a ventilation channel 165 in the pressure plate 11.2.
  • This ventilation channel passes through the pressure plate 11.2 and opens into a pressure kidney 167, which is assigned to the upper pump section.
  • the ventilation channel 165 has a small flow cross-sectional area.
  • the hydraulic resistance formed by the venting channel 165 must therefore be chosen so large for cold viscous hydraulic oil that there is essentially no fluid flow. so that almost all of the hydraulic oil delivered from the lower pump section into the pressure chamber 147 benefits the lower wing area via the channel 145.
  • FIG. 14b A further implementation is shown in FIG. 14b, in which case a ventilation channel 165 is assigned to each of the two pressure kidneys of the pressure plate 11.2. Since there are two hydraulic resistors in the form of the venting channels 165 in the fluid path from the lower pressure area via the pressure chamber 147 to the upper pressure area, the flow cross-sectional area of the individual venting channel can be designed to be somewhat larger than in the previous exemplary embodiment. It is only necessary to ensure that the sum of the two hydraulic resistors is so large that there is essentially no fluid flow in the start-up phase when the viscous hydraulic oil is cold.
  • the small cross section of the ventilation duct 165 is sufficient to allow air flowing upwards in the pressure chamber 147 to escape therefrom.
  • FIG. 14c Another implementation of ventilation is shown in Figure 14c.
  • a web 169 is preferably formed on the wall delimiting the pressure space 147.
  • This web 169 serves as a hydraulic resistance element that is introduced in the fluid path between the lower and upper pressure range. Its resistance value is chosen so large that cold viscous hydraulic oil is not flows from a pressure chamber region assigned to the lower pump section into the pressure chamber region assigned to the upper pump section, the boundary of the two pressure chamber regions being the web 169.
  • the exemplary embodiments described with reference to FIGS. 10 to 14 have in common that the hydraulic resistance of the fluid path 143 present between two pressure regions or the fluid path between the conveying pressure region and the consumer is designed to be greater than the hydraulic resistance of the fluid path 141 between pressure area and lower wing area. This ensures in any case that at the start of the vane pump, the pumping lower pump section is used essentially to supply the lower wing areas in order to increase the delivery rate of the upper pump section.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP96112844A 1995-08-14 1996-08-09 Pompe à palettes Expired - Lifetime EP0758716B1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
DE19529803 1995-08-14
DE19529803 1995-08-14
DE19531701A DE19531701C1 (de) 1995-08-14 1995-08-28 Pumpe
DE19531701 1995-08-28
DE29610896U 1996-06-21
DE29610896 1996-06-21
DE19629336 1996-07-20
DE1996129336 DE19629336C2 (de) 1996-07-20 1996-07-20 Flügelzellenpumpe

Publications (3)

Publication Number Publication Date
EP0758716A2 true EP0758716A2 (fr) 1997-02-19
EP0758716A3 EP0758716A3 (fr) 1998-04-01
EP0758716B1 EP0758716B1 (fr) 2003-12-10

Family

ID=27438170

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96112844A Expired - Lifetime EP0758716B1 (fr) 1995-08-14 1996-08-09 Pompe à palettes

Country Status (3)

Country Link
US (1) US5807090A (fr)
EP (1) EP0758716B1 (fr)
JP (1) JP4164133B2 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001094788A1 (fr) * 2000-06-05 2001-12-13 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pompe
DE102014212022A1 (de) 2013-07-08 2015-01-08 Magna Powertrain Bad Homburg GmbH Pumpe
WO2015010700A1 (fr) * 2013-07-26 2015-01-29 Schaeffler Technologies Gmbh & Co. Kg Système fluidique
US9765777B2 (en) 2012-06-12 2017-09-19 Magna Powertrain Bad Homburg GmbH Pump
CN109812298A (zh) * 2019-02-19 2019-05-28 东南大学 一种气缸随转的滑片式膨胀机
DE102017222825A1 (de) 2017-12-15 2019-06-19 Robert Bosch Gmbh Verfahren zur Ansteuerung einer Flüssigkeitspumpen-/Antriebskombination in einem Fahrzeug

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6030195A (en) * 1997-07-30 2000-02-29 Delaware Capital Formation Inc. Rotary pump with hydraulic vane actuation
DE19857560A1 (de) * 1997-12-23 1999-06-24 Luk Fahrzeug Hydraulik Pumpe ohne eigene Lagerung
DE19900926B4 (de) * 1998-01-28 2015-01-22 Magna Powertrain Bad Homburg GmbH Pumpe
DE10030838A1 (de) * 1999-07-05 2001-01-11 Luk Lamellen & Kupplungsbau Verfahren zur Versorgung eines eine Getriebesteuerung aufweisenden Automatik-Getriebes und Automatik-Getriebe
US6450146B1 (en) 2000-12-12 2002-09-17 International Engine Intellectual Property Company, L.L.C. High pressure pump with a close-mounted valve for a hydraulic fuel system
US6688851B2 (en) 2001-12-28 2004-02-10 Visteon Global Technologies, Inc. Oil pump for controlling planetary system torque
JP2007113640A (ja) * 2005-10-19 2007-05-10 Toyota Motor Corp 駆動装置
US7955063B2 (en) * 2008-05-19 2011-06-07 Stackpole Limited Vane pump
CA2679776A1 (fr) * 2008-10-08 2010-04-08 Magna Powertrain Inc. Pompe a ailettes, a commande directe de debit
EP2337928B1 (fr) * 2008-10-22 2013-02-13 ixetic Bad Homburg GmbH Pompe, notamment pompe à palettes
WO2010051640A1 (fr) 2008-11-07 2010-05-14 Stt Technologies Inc., A Joint Venture Of Magna Powertrain Inc. And Shw Gmbh Pompe à huile électrique intégrée entièrement immergée
US8696326B2 (en) * 2009-05-14 2014-04-15 Magna Powertrain Inc. Integrated electrical auxiliary oil pump
JP5214644B2 (ja) * 2010-02-09 2013-06-19 ジヤトコ株式会社 自動変速機用オイルポンプの空気抜き構造
US9127674B2 (en) * 2010-06-22 2015-09-08 Gm Global Technology Operations, Llc High efficiency fixed displacement vane pump including a compression spring
US20130089456A1 (en) * 2011-10-07 2013-04-11 Steering Solutions Ip Holding Corporation Cartridge Style Binary Vane Pump
DE102015215982B4 (de) 2015-08-21 2017-03-16 Magna Powertrain Bad Homburg GmbH Pumpe sowie System zur Versorgung eines Verbrauchers
DE102019132729A1 (de) * 2019-12-02 2021-07-01 Schwäbische Hüttenwerke Automotive GmbH Sickendichtung

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DE2835816A1 (de) * 1978-08-16 1980-02-21 Zahnradfabrik Friedrichshafen Drehkolbenpumpe
EP0481347A1 (fr) * 1990-10-11 1992-04-22 Toyoda Koki Kabushiki Kaisha Pompe à palettes
DE19529806A1 (de) * 1995-08-14 1997-02-20 Luk Fahrzeug Hydraulik Flügelzellenpumpe

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US3781145A (en) * 1972-05-10 1973-12-25 Abex Corp Vane pump with pressure ramp tracking assist
DE2423474C3 (de) * 1974-05-14 1981-11-05 Daimler-Benz Ag, 7000 Stuttgart Flügelzelleneinrichtung, insbesondere -pumpe für Flüssigkeiten
DE2512433C2 (de) * 1975-03-21 1982-03-04 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Doppelhubige Drehkolbenpumpe, insbesondere für Hilfskraftlenkungen
US4386891A (en) * 1981-04-23 1983-06-07 General Motors Corporation Rotary hydraulic vane pump with undervane passages for priming
EP0083491A1 (fr) * 1981-12-24 1983-07-13 Concentric Pumps Limited Pompe à gerotor
JPH02252988A (ja) * 1988-12-02 1990-10-11 Jidosha Kiki Co Ltd オイルポンプ
DE4209840A1 (de) * 1992-03-26 1993-09-30 Zahnradfabrik Friedrichshafen Flügelzellenpumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2835816A1 (de) * 1978-08-16 1980-02-21 Zahnradfabrik Friedrichshafen Drehkolbenpumpe
EP0481347A1 (fr) * 1990-10-11 1992-04-22 Toyoda Koki Kabushiki Kaisha Pompe à palettes
DE19529806A1 (de) * 1995-08-14 1997-02-20 Luk Fahrzeug Hydraulik Flügelzellenpumpe

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001094788A1 (fr) * 2000-06-05 2001-12-13 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pompe
US9765777B2 (en) 2012-06-12 2017-09-19 Magna Powertrain Bad Homburg GmbH Pump
DE102014212022A1 (de) 2013-07-08 2015-01-08 Magna Powertrain Bad Homburg GmbH Pumpe
DE102014212022B4 (de) * 2013-07-08 2016-06-09 Magna Powertrain Bad Homburg GmbH Pumpe
US9366252B2 (en) 2013-07-08 2016-06-14 Magna Powertrain Bad Homburg GmbH Pump having a cold starting device
WO2015010700A1 (fr) * 2013-07-26 2015-01-29 Schaeffler Technologies Gmbh & Co. Kg Système fluidique
DE102017222825A1 (de) 2017-12-15 2019-06-19 Robert Bosch Gmbh Verfahren zur Ansteuerung einer Flüssigkeitspumpen-/Antriebskombination in einem Fahrzeug
WO2019115366A1 (fr) 2017-12-15 2019-06-20 Robert Bosch Gmbh Procédé de commande d'un ensemble pompe pour liquides-entraînement dans un véhicule
CN109812298A (zh) * 2019-02-19 2019-05-28 东南大学 一种气缸随转的滑片式膨胀机

Also Published As

Publication number Publication date
EP0758716A3 (fr) 1998-04-01
JPH09119383A (ja) 1997-05-06
JP4164133B2 (ja) 2008-10-08
EP0758716B1 (fr) 2003-12-10
US5807090A (en) 1998-09-15

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