EP0712997B1 - Pompe à engrenages internes avec réglage de l'aspiration - Google Patents

Pompe à engrenages internes avec réglage de l'aspiration Download PDF

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Publication number
EP0712997B1
EP0712997B1 EP95115966A EP95115966A EP0712997B1 EP 0712997 B1 EP0712997 B1 EP 0712997B1 EP 95115966 A EP95115966 A EP 95115966A EP 95115966 A EP95115966 A EP 95115966A EP 0712997 B1 EP0712997 B1 EP 0712997B1
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EP
European Patent Office
Prior art keywords
working fluid
internal gear
duct
gear pump
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP95115966A
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German (de)
English (en)
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EP0712997A3 (fr
EP0712997A2 (fr
Inventor
Siegfried A. Dipl.-Ing. Eisenmann
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Individual
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Individual
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Publication date
Priority claimed from DE19944437076 external-priority patent/DE4437076C2/de
Priority claimed from DE1995123533 external-priority patent/DE19523533C2/de
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Publication of EP0712997A2 publication Critical patent/EP0712997A2/fr
Publication of EP0712997A3 publication Critical patent/EP0712997A3/fr
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Publication of EP0712997B1 publication Critical patent/EP0712997B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C14/12—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34403—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft
    • F01L1/34406—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
    • 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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes

Definitions

  • the invention relates to an internal gear pump according to the Preamble of claim 1.
  • VTC valve timing control
  • a multi-phase valve timing mechanism is from the "Motortechnische Zeitschrift” 55 (1994) 6, page 342.
  • the cam set used for a six-cylinder engine has two rocker arms. T-waves control depending on the speed simultaneously the two intake and exhaust valves per cylinder. At high speed hydraulic pistons connect the corresponding rocker arms to the T-shafts. At The T-shafts with the levers for low speed become low speed connected. In addition, with this mechanism there is a cylinder deactivation possible. To do this, the T-shafts of the rocker arms for the high speeds disengaged so that only three of the six cylinders are still working.
  • Ordinary pumps for pumping motor oil convey their working medium with one with the Pump speed constantly increasing delivery pressure or delivery volume flow.
  • the Pumps are usually mechanically driven directly from the motor via a corresponding one Toothed belt drive or another suitable gear driven, so that delivery pressure or volume flow increase with the engine speed.
  • the usable pumps must be in the lower speed range of the motor have a steep increase in their volume flow.
  • the known pumps are therefore large with a correspondingly high power consumption executed. As the engine speed increases, they therefore pump more engine oil than is required by the actuating means of the valve control, so that the excess must be returned directly from the pump outlet to a sump.
  • a pump designed as an internal gear pump is e.g. from DE 39 33 978 known.
  • the drive is usually carried out by the shaft carrying the pinion.
  • the Delivery of such pumps, e.g. the lubrication pump of a motor vehicle engine is only in the lower part of the operating range proportional to the speed. At the top The lubricant or working fluid requirement increases much lower in the speed range than the speed of the engine. This is a suction control of the pump necessary.
  • the cavitation that occurs is disadvantageous in such a suction control.
  • the through the increase in speed expected linear pressure increase can be in the pressure range such pumps are not held, rather the pressure rises from one certain speed not linear with a lower slope.
  • the full geometric delivery rate in the work area above the proportionality area cavitation occurs which leads to implosions of the gaseous components of the cell contents leads, so that unwanted noise and damage to the Cell walls are the result.
  • such pumps have higher Speed ranges relatively low efficiencies.
  • the invention has set itself the task an internal gear pump with minimal cavitation and high efficiency To make available, in particular for valve control can be used.
  • the decisive advantage of the new internal gear pump according to the invention lies in that by the controlled supply of working fluid from the outlet mouth into an inlet mouth and the simultaneous interruption of the supply a working cell from working fluid from the inlet channel into this inlet mouth, in which pressure drop and thus cavitation occur with increasing speed would be brought to the higher outlet pressure. This will Cavitation in this delivery cell avoided.
  • Another big advantage is that because no cavity, i.e. there is no negative pressure in this feed cell, but this is pressurized, this pressure has a positive torque generated on the pinion.
  • This feed cell, which is under higher pressure, is working thus like a hydraulic motor, whereby a very high efficiency can be achieved can.
  • the pump according to the invention connects by means of a device with increasing pressure in the pressure range sequentially the upstream at these adjacent inlet ports with the pressure area.
  • the above-mentioned device advantageously has one with the outlet mouth connected transfer channel, which via a valve device in at least one feed channel opens, which in turn has an inlet opening communicates.
  • the valve device can thus the regulated supply of Working fluid from the outlet mouth, i.e. the pressure area, into the Control inlet mouth and at the same time the supply of working fluid from the First throttle the inlet channel into this inlet mouth and interrupt it later.
  • a valve device preferably has a valve piston which by means of a spring supported in the housing against the pressure of the working fluid stored in the transfer channel and access by means of a heel locks or releases the working fluid into the supply channels.
  • the spring offers, at different choice of their stiffness, a way to control the Operating behavior of the valve device, while the head of the valve piston can be designed so that the pressurized working fluid counter the spring force presses against one of its surfaces while it is with its Side surfaces of the feed channels for the working fluid depending on the position of the Valve piston locks or releases.
  • the valve piston can be in the depressurized state of the transfer channel or up to one predetermined pressure in this against the force of the spring by a stop on Housing in a position where no working fluid from the Transfer channel flows into a feed channel.
  • This state corresponds to the starting position the valve device at low speed or when the Pump.
  • the opposite stop point of the valve piston can thereby be determined that the valve piston in the position where working fluid from flows into all feed channels in its movement against the Direction of the spring force is stopped because the spring is locked.
  • the inlet mouth for those not to be connected to the transition duct The size of the conveyor cells is preferably limited to the area in which these funding cells extend. This ensures that those Conveying cells with increasing speed with pressure from the high pressure chamber should be applied, can be completely cut off from the suction chamber.
  • the outlet mouth can be approximately over the entire area of Extend conveyor cells, which in the conveying direction downstream of the conveyor cells lie, which can be connected to the transition channel. This Formation of the outlet mouth is suitable because of the connection with it standing conveyor cells under high pressure practically during the entire operation stand.
  • the end facing away from the head heel forms of the valve piston together with the housing a spring chamber, which for Damping the piston movement is filled with working fluid and over a
  • the bore is in fluid communication with the working fluid in the inlet duct.
  • the valve device advantageously acts simultaneously as a safety valve in Form of a bypass valve. If the head is at maximum pressure in the pressure range has exceeded the last supply channel to such an extent that decompression occurs a short circuit flow of the working fluid from the pressure area in the Intake channel occurs, the spring therefore only goes to block when an sufficient discharge cross-section is created.
  • the pinion of the internal gear pump has two teeth less than the toothed ring, and in the place of disengagement of the teeth is a crescent moon Filler piece fixed to the housing.
  • the teeth of the toothed ring be made sufficiently pointed so that the feed cells in the suction area over the Tooth mesh are sealed against each other.
  • the internal gear pump according to the invention can be characterized in that that the head of the valve piston from a heel base and a lengthways to this subsequent paragraph flag with the same outer diameter, the Guide and the sealing function of the valve piston in the housing bore on the Heels on the exterior of the heel base and heel tab occur.
  • An internal gear pump according to the invention can advantageously be a suction-controlled one Pump used for valve control according to this invention become.
  • FIG. 1 is a cross-sectional view of an embodiment of an inventive Internal gear pump shown.
  • the pump has a housing 201 which encloses a gear chamber 206 with a gear ring 202. With the gear ring 202 meshes a pinion 203, which has one tooth less than the toothed ring 202.
  • the pinion 203 forms with the toothed ring 202 successive against each other through the meshing sealing conveyor cells 210, 211, 212, 213, 214, 215 and 216.
  • An inlet channel 204 opens into an inlet opening designed as an inlet kidney 207, which is shown in dashed lines.
  • the inlet duct 204 is in the position shown in Figure 9 via a housing bore 217 with housing shoulders 217a, 217b, 217c and 217d with the feed channels 222a, 222b and 222c connected, which leak into the inlet ports 208a, 208b and 208c.
  • the housing On the outlet side, the housing has an outlet channel 205 which is in line with that in the gear chamber 206 arranged outlet kidney 209, which is also dashed is shown, is connected. Next is the outlet kidney 209 on their the Outlet opening 205 facing away from the side is connected to a transfer duct 220, which on the side of the housing bore opposite the inlet channel 204 217 opens into the housing shoulder 217a.
  • a valve device At the bottom of the case 201 a valve device is provided.
  • a valve piston 221 is located in this position of the valve device in the housing bore 217, a Head shoulder 224 of this valve piston 221 with its front end in the transfer channel 220 strikes against the housing and with its side surfaces the Housing bore 217 on the housing shoulder 217a against the liquid in the transfer channel 220 seals.
  • the valve piston 221 is at its rear end his rear paragraph 229 in a spring chamber 225, in which in a Spring 223 in the direction of the attachment point on the housing (in the left direction in Figure 9) against the pressure in the transfer duct 220 or against the stop of the head heel 224 on the housing 201.
  • the spring chamber 225 is on the right Tightly closed with an unspecified screw plug.
  • a Bore 226 in the valve piston 221 connects its surroundings with that Working fluid filled spring chamber 225, creating a damping effect entry.
  • the pinion 203 is rotated in the direction indicated by the arrow n. Liquid is sucked in via the inlet channel 204 and, on the one hand, fed to the delivery cells 210 and 211 via the inlet kidney 207.
  • working fluid is also supplied via the housing bore 217 in the space between the valve piston 221 and this housing bore to the feed channels 222a, 222b and 222c and via these to the inlet ports 208a, 208b and 208c, which supply the feed cells 212 and 213 with working fluid.
  • the pump delivers in the proportional range, ie the delivery volume increases linearly with an increase in the speed n.
  • the head shoulder 224 seals the housing bore 217 on the housing shoulder 217a against the liquid in the transfer channel 220, only the delivery cells 214, 215 and 216 are under pressure.
  • the spring force F0 exerts a greater or equal pressure on the valve piston 221 as the pressure P 0 against the surface of the head heel 224 labeled AK.
  • the regulation begins when the force exerted by the working fluid in the transfer channel 220 on the head heel 224 becomes greater than the spring force.
  • the pinion 203 rotates at the speed n1, which is already higher than the limit speed in the proportionality range of the pump.
  • the pressure of the working fluid in the pressure range would increase linearly to a pressure P 1 ' , so that the valve piston 221 is moved to the right.
  • the suction angle ⁇ s is reduced from ⁇ s max (see FIG. 1) to ⁇ s1 (see FIG. 2).
  • the pressure P 1 ' that could be achieved linearly cannot hold, but drops to P 1 . This means that the flow rate also drops linearly.
  • a new delivery rate and a new pressure P 1 occur , which is lower than P 1 ' , but higher than P 0 .
  • the setting of a pressure P 1 which is higher than the pressure P 0 , is also structurally dependent on the design of the valve device and the pump. If this pressure were not higher than P 0 , the valve piston 221 would be pushed back into the original position (FIG. 1) by the spring 223, and the process would start again because the speed is increased compared to the initial position.
  • the pressure P 1 must be between P 0 and P 1 '.
  • FIGS. 2 and 3 show what happens when the speed is increased further, here to the speed n 2 in FIG. 3.
  • the process described above for increasing the speed continues, so that the valve piston 221 is pushed further and further to the right by the pressure increase until, for example, as shown in FIG. 3, a state is reached where the valve piston 221 with its head shoulder 224 reaches Seals the housing bore 217 on the housing shoulder 217c, so that the feed cell designated here 212 is not supplied with suctioned working fluid via the inlet channel 204, but rather via the transition channel 220 and the channels 222a and 208a with working fluid under pressure.
  • the working fluid in the delivery cell 212 is at an increased pressure P 2 with the downstream delivery cells, so that no cavity is created in it and no negative pressure can develop even in spite of the increase in space.
  • this pressure cell 212 generates a positive torque on the pinion 203 by the application of pressure P 2 , because its space expands under high pressure and works like a hydraulic motor.
  • This internal differential control thus works with high efficiency.
  • the working fluid under pressure P 2 is not decompressed to atmospheric pressure, but instead returns its potential energy as mechanical power to the pump drive shaft with a certain loss of flow through the channels.
  • the suction angle in this position is designated ⁇ s2 .
  • the speed n 3 is now increased to such an extent that the valve piston 221 has moved so far to the right that it seals the entire housing bore 217 with its head shoulder 224 against the working fluid in the inlet channel 204 on the housing shoulder 217d.
  • the delivery chamber designated 212 and all of the downstream delivery chambers from it are now supplied with pressurized working fluid either via the outlet kidney 209 or via the transfer channel 220 and the supply and inlet channels 222a, 222b, 208a and 208b crossing them.
  • the spring 223 is pressed onto the block.
  • valve piston 221 If, as in FIG. 4, the valve piston 221 is pressed to the right up to the spring block, no further internal regulation can take place. With further speed increases the flow rate with reduced slope increases proportionally to the speed rise until in the remaining remaining suction tooth chambers in the area of the short suction kidney 207 cavitation occurs.
  • the pump described above is mainly suitable for the supply of automatic transmissions with a pressure level up to 25 bar or higher.
  • the stiffness of the spring 223 determines the steepness of the conveyor line in the regulated one Range and must be adapted to the hydraulic resistance of the consumer become.
  • FIG. 5 shows a further embodiment of the invention Internal gear pump in two further aspects of the present invention emerge.
  • a first aspect relates to the design of the pump with a Pinion 203, which has two teeth less than the toothed ring 202.
  • teeth of the pinion 203 with the ring gear 202 except Intervention here is a crescent-shaped, housing-fixed filler 227 intended.
  • the teeth 228 of the toothed ring 202 are designed to be sufficiently pointed, to ensure that the feed cells are sufficiently counter to each other in the suction area for meshing to seal.
  • FIG. 5 Another aspect of the invention, which is clear from FIG. 5, relates to the safety valve effect of the valve device.
  • This works as a bypass valve, if at maximum pressure in the pressure area the head attachment 224 the last feed channel 222c has exceeded so far that, under decompression, short circuit from the pressure area enters the inlet channel 204.
  • the spring 223 may only block go if there is a sufficient discharge cross-section at this point is reached.
  • the Head attachment 224 may be longer than the width of the cutout 230. In FIG Head attachment 224 designed accordingly. If the head base is too short, it loses Pistons his lead.
  • the head shoulder 224 of the valve piston 221 here from a sales base 224a and a sales flag adjoining it longitudinally 224b with the same outside diameter.
  • the leadership and sealing function of the Find valve piston 221 in the housing bore 217 on the housing shoulders the outer surfaces of the heel base 224a and the heel tab 224b.
  • the Heel base 224a itself is made narrow, in particular narrower than the width of the feed channels 222 can be a good one through the milled out shoulder 224b Guidance and sealing are guaranteed.

Claims (12)

  1. Pompe à engrenages internes, comprenant :
    a) un carter (201) avec une chambre à engrenages (206),
    b) une couronne dentée (202) dans le carter (201),
    c) un pignon (203) disposé dans la couronne dentée (202) et en prise avec cette dernière, lequel présente au moins une dent de moins que la couronne dentée (202) et forme avec cette dernière des cellules de transport (210, 211, 212, 213, 214, 215, 216) successives pour le fluide de travail, s'étanchéifiant les unes par rapport aux autres par l'engrènement, et
    d) au moins un canal d'admission (204) et au moins un canal de sortie (205) pour le fluide de travail dans le carter (201),
    e) pompe dans laquelle le fluide de travail est acheminé du canal d'admission dans la zone d'aspiration de la chambre à engrenages (206) par l'intermédiaire d'au moins un orifice d'admission (207, 208a, 208b, 208c) et évacué hors de la zone de compression de la chambre à engrenages (206) dans le canal de sortie (205), par l'intermédiaire d'au moins un orifice de sortie (209), pompe comprenant également
    f) un dispositif (220, 221, 222) qui achemine une quantité réglée de fluide de travail de l'orifice de sortie (209) à au moins un orifice d'admission (208a, 208b, 208c), en interrompant simultanément l'apport de fluide de travail du canal d'admission (204) vers cet orifice d'admission (208a, 208b, 208c),
    pompe caractérisée en ce que lorsque la pression s'élève dans la zone de compression, le dispositif (220, 221, 222) met en communication avec cette dernière les orifices d'admission (208a, 208b, 208c) qui lui sont successivement adjacents dans le sens amont.
  2. Pompe à engrenages internes suivant la revendication 1, caractérisée en ce que le dispositif (220, 221, 222) présente un canal de transfert (220) en relation avec l'orifice de sortie (209), canal qui débouche via un dispositif à soupape (221, 222, 223) dans au moins un canal d'alimentation (222a, 222b, 222c) qui est à son tour en relation avec un orifice d'admission (208a, 208b, 208c).
  3. Pompe à engrenages internes suivant la revendication 2, caractérisée en ce que le dispositif à soupape (221, 223, 224) présente un piston à soupape (221) qui est monté au moyen d'un ressort (223) en appui dans le carter (201), avec réglage à l'encontre de la pression du fluide de travail dans le canal de transfert (220), et qui coupe ou libère l'accès du fluide de travail aux canaux d'alimentation (222a, 222b, 222c) au moyen d'une tête épaulée (224).
  4. Pompe à engrenages internes suivant la revendication 3, caractérisée en ce qu'en l'absence de pression dans le canal de transfert (220) ou jusqu'à une pression prédéterminée dans celui-ci, le piston à soupape (221) est maintenu à l'encontre de la force du ressort (223), grâce à une butée prévue dans le carter (201), dans une position dans laquelle il ne s'écoule pas de fluide de travail du canal de transfert (220) à un canal d'alimentation (222).
  5. Pompe à engrenages internes suivant l'une des revendications 3 ou 4, caractérisée en ce que dans la position où du fluide de travail s'écoule du canal de transfert (220) dans tous les canaux d'alimentation (222), le piston à soupape (221) est arrêté dans son déplacement à l'encontre de la direction de la force du ressort, par le fait que le ressort (223) est bloqué.
  6. Pompe à engrenages internes suivant l'une des revendications 1 à 5, caractérisée en ce que le calibre de l'orifice d'admission (207) pour les cellules de transport (210, 211) qui ne doivent pas être mises en relation avec le canal de transfert (220) est limité à peu près à la zone dans laquelle s'étendent ces cellules de transport.
  7. Pompe à engrenages internes suivant l'une des revendications 1 à 6, caractérisée en ce que l'orifice de sortie (209) s'étend à peu près sur toute la zone des cellules de transport (214, 215, 216) situées dans le sens du transport en aval des cellules de transport (212, 213) qui peuvent être mises en communication avec le canal de transfert (220).
  8. Pompe à engrenages internes suivant l'une des revendications 1 à 7, caractérisée en ce que l'extrémité du piston à soupape (221) orientée à l'opposé de la tête épaulée (224) forme avec le carter (201) une chambre de ressort (225) qui est remplie de fluide de travail afin d'amortir le déplacement du piston et qui est en communication avec le fluide de travail se trouvant dans le canal d'admission (204) via un alésage (226).
  9. Pompe à engrenages internes suivant l'une des revendications 1 à 8, caractérisée en ce que le dispositif à soupape (221, 223, 224) sert parallèlement de soupape de sécurité adoptant la forme d'une soupape de dérivation lorsqu'à l'atteinte de la pression maximum dans la zone de compression, la tête épaulée (224) a dépassé le dernier canal d'alimentation (222c) au point que sous l'effet de la décompression qui se met en place, un écoulement de court-circuit du fluide de travail de la zone de compression au canal d'admission (204) est établi.
  10. Pompe à engrenages internes suivant l'une des revendications 1 à 9, caractérisée en ce que le pignon (203) présente deux dents de moins que la couronne dentée (202) et en ce qu'une pièce intercalaire en forme de croissant de lune, solidaire du carter, est prévue à l'endroit du désengrènement des dents.
  11. Pompe à engrenages internes suivant la revendication 10, caractérisée en ce que les dents de la couronne dentée sont suffisamment pointues pour que les cellules de transport (210, 211, 212) soient étanchéifiées les unes par rapport aux autres dans la zone d'aspiration, par l'effet de l'engrènement.
  12. Pompe à engrenages internes suivant l'une des revendications 3 à 11, caractérisée en ce que la tête épaulée (224) du piston à soupape (221) se compose d'un segment de base (224a) et d'un segment de tête (224b) de même diamètre extérieur se rattachant au premier en suivant la longueur, le guidage et la fonction d'étanchement du piston à soupape (221) dans l'alésage (217) du carter au niveau des créneaux (217a, 217b, 217c, 217d) formés dans le carter étant assurés par les faces extérieures du segment de base (224a) et du segment de tête (224b).
EP95115966A 1994-10-17 1995-10-10 Pompe à engrenages internes avec réglage de l'aspiration Expired - Lifetime EP0712997B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4437076 1994-10-17
DE19944437076 DE4437076C2 (de) 1994-10-17 1994-10-17 Ventilsteuerung mit sauggeregelter Zahnringpumpe
DE1995123533 DE19523533C2 (de) 1995-06-28 1995-06-28 Sauggeregelte Innenzahnradpumpe
DE19523533 1995-06-28

Publications (3)

Publication Number Publication Date
EP0712997A2 EP0712997A2 (fr) 1996-05-22
EP0712997A3 EP0712997A3 (fr) 1996-08-28
EP0712997B1 true EP0712997B1 (fr) 2000-04-12

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Application Number Title Priority Date Filing Date
EP95115966A Expired - Lifetime EP0712997B1 (fr) 1994-10-17 1995-10-10 Pompe à engrenages internes avec réglage de l'aspiration

Country Status (9)

Country Link
US (2) US5738501A (fr)
EP (1) EP0712997B1 (fr)
JP (2) JP2825782B2 (fr)
KR (1) KR960014598A (fr)
CN (1) CN1131731A (fr)
BR (1) BR9504427A (fr)
CA (1) CA2159672C (fr)
DE (1) DE59508170D1 (fr)
ES (1) ES2146694T3 (fr)

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DE102008056629A1 (de) 2008-11-10 2009-07-23 Audi Ag Innenzahnradpumpe mit variablem Fördervolumen

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0785361B1 (fr) * 1996-01-19 2003-04-23 Aisin Seiki Kabushiki Kaisha Appareil de pompe à huile
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BR9504427A (pt) 1997-05-20
JP2825782B2 (ja) 1998-11-18
EP0712997A3 (fr) 1996-08-28
CA2159672A1 (fr) 1996-04-18
US5842449A (en) 1998-12-01
US5738501A (en) 1998-04-14
DE59508170D1 (de) 2000-05-18
JP3292458B2 (ja) 2002-06-17
EP0712997A2 (fr) 1996-05-22
CN1131731A (zh) 1996-09-25
JPH08210116A (ja) 1996-08-20
JPH10317932A (ja) 1998-12-02
ES2146694T3 (es) 2000-08-16
CA2159672C (fr) 2009-09-15
KR960014598A (ko) 1996-05-22

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