EP0422617B1 - Pompe à engrenage annulaires avec régulation d'aspiration - Google Patents

Pompe à engrenage annulaires avec régulation d'aspiration Download PDF

Info

Publication number
EP0422617B1
EP0422617B1 EP90119424A EP90119424A EP0422617B1 EP 0422617 B1 EP0422617 B1 EP 0422617B1 EP 90119424 A EP90119424 A EP 90119424A EP 90119424 A EP90119424 A EP 90119424A EP 0422617 B1 EP0422617 B1 EP 0422617B1
Authority
EP
European Patent Office
Prior art keywords
gear
pump according
ring pump
gear ring
pressure
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
EP90119424A
Other languages
German (de)
English (en)
Other versions
EP0422617A1 (fr
Inventor
Siegfried A. Dipl.-Ing. Eisenmann
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.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0422617A1 publication Critical patent/EP0422617A1/fr
Application granted granted Critical
Publication of EP0422617B1 publication Critical patent/EP0422617B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • 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
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement

Definitions

  • the invention relates to a suction-controlled gerotor pump with the features of the preamble of claim 1.
  • the pump is generally driven by the shaft carrying the pinion.
  • Such pumps are e.g. used to power hydraulic systems.
  • the invention relates to the use of such a pump according to claim 11.
  • the delivery target of the lubrication pump of a motor vehicle engine which in automatic transmissions also has to take over the function of supplying pressure to the hydraulic switching elements and filling the converter against cavitation, is only approximately proportional to the speed in both the engine and the transmission in the lower third of the operating range.
  • the oil requirement increases far less than the engine speed. It would therefore be necessary to have a drive-controlled lubrication or hydraulic pump or one with a speed-adjustable delivery rate.
  • the most common form The oil and / or lubrication pump is the gear pump because it is simple, cheap and reliable.
  • the disadvantage is that the delivery rate (per revolution) cannot be regulated, i.e. the theoretical delivery rate is proportional to the speed.
  • the practical characteristics of the delivery rate over the speed depend on a multitude of parameters such as delivery pressure, oil viscosity, flow resistance in the suction and pressure line, configuration of the toothing of the gearwheels, width of the gearwheels and design of the pump.
  • An adjustment of the delivery line to the demand line, for example of an internal combustion engine is in most cases too complex, which is why a bypass valve is used, which regulates the excess oil at a certain set delivery pressure and returns it decompressed to the suction line. This regulation is thus heavily lossy in the regulating range, so that the efficiency drops undesirably with increasing speed.
  • the flow resistances in the intake manifold are to be determined or controlled in such a way that the useful delivery rate of the gear pump is largely adapted to the consumption line.
  • the time period for the slow compression of the steam and air spaces is structurally ensured by the fact that the cells on the displacement side of the pump are initially only connected to the delivery pressure chamber via check valves, so that the delivery pressure does not become effective in the case of a cell that is not completely filled with liquid can.
  • the invention thus relates to a suction-controlled gerotor pump according to the preamble of claim 1, in which the difference in the number of teeth is 1 and the tooth shape of which ensures that the delivery cells are sealed from one another.
  • the invention solves the problem of creating a pump with a short and small diameter, which is also characterized by a favorable pressure curve in the pressure range, can also be retrofitted in existing constructions as a replacement for the lubrication pump, is reliable in operation and has a simple construction having.
  • the invention makes it possible, in most cases, to completely omit the bypass arrangement with a large passage, or to replace it with a small pressure relief valve, by adapting the conveying characteristic to the demand characteristic.
  • the housing is of extremely simple design and has only a very small axial extent. Because each feed cell can release working fluid into the leading feed cell when the feed cell shrinks when the ball valve is opened, but not in the opposite direction, the pressure in each feed cell in the reduction area can only be increased steadily until the pressure reaches the value has grown in the outlet opening. In this way, the feared implosions are avoided and the cavitation cavities are steadily reduced to zero. It is particularly advantageous here that a through the channels with the ball valves is not there is negligible flow resistance between the neighboring feed cells.
  • the mouths of the inlet and outlet channels can have recesses in the peripheral surface of the tooth chamber that supports the ring gear, the connection between the cells and the channel mouths then being effected by radial bores in the ring gear.
  • the mouths of the inlet and outlet channels in the end walls of the gear chamber are preferably arranged as so-called inlet and outlet kidneys (claim 2). This allows very large inflow and outflow cross sections in and out of the feed cells.
  • the overflow channels can be provided, for example, in the gear bodies themselves. However, they are preferably arranged in the teeth of the wheels.
  • the check valves can e.g. be formed by cylindrical rollers arranged in corresponding widenings of the overflow channels and having an axis parallel to the pump axis, which under the influence of the flow lie in the widening against the corresponding channel mouth to be closed.
  • Spring-loaded valves can also be used.
  • the check valves are preferably designed as ball valves, the ball always striving to press the ball onto the valve seat due to the centrifugal force of the rotary movement of the gearwheel containing the valves. This training is not only simple in construction but also easier to manufacture and does not require valve springs.
  • the overflow channels can be designed, for example, as grooves in an end face of the corresponding gearwheel, a widening of the groove then accommodating the check valve.
  • part of the wall of the overflow channels is formed by the corresponding end wall of the housing. So far there are several Opportunities.
  • the gear wheel containing the check valves is formed from two halves (the parting plane of which is a normal plane to the axis of rotation of the gear wheel), each of which contains half of the valve channels and the valve seat in mirror-image form.
  • the two halves do not necessarily have to be connected to one another, since they are fixed in their rotational position by the teeth of the corresponding gear and cannot move axially from one another, since this prevents the end walls of the gear chamber.
  • the gear pump according to the invention with the number of teeth difference 1 is one in which all teeth are constantly in engagement with teeth of the counter gear. This ensures particularly good guidance of the two gear wheel halves against one another in the circumferential direction. The same also applies to centering.
  • the two halves of the wheel containing the overflow channels and check valves are connected to each other.
  • the connection can be effected, for example, by explosion welding.
  • the valve bodies must be inserted into the corresponding chambers before the weld connection.
  • the two halves of the wheel are connected to one another by sintering.
  • the two halves of the gearwheel containing the overflow channels can also be connected to one another by means of axial screws.
  • the two ring gear halves can be conventionally e.g. machined from appropriate blanks. According to a preferred embodiment of the invention, however, the two ring gear halves are produced in a powder-metallurgical sintering process. This allows you to do without any rework.
  • gears As a material for the gears come in the invention, for example, high-strength Sintered metals in question; however, depending on the intended use and the required number of pieces, steel or gray cast iron are also suitable as the material.
  • the valve body - preferably balls - can be steel balls, for example.
  • balls made of non-metallic material or metal balls which are coated with a non-metallic material are preferably used here. This counteracts caking of the balls on the valve seats. The production from non-metallic material also reduces the inertial forces.
  • the overflow channels are arranged in the teeth of the pinion and in this case have a cavity which accommodates the balls from one of the axial end faces of the pinion, the inflow and outflow channels to these cavities then being drilled.
  • valve balls A particularly good guidance of the valve balls is obtained if a support edge is provided in the non-return valve, which produces a tangential component of the centrifugal force on the ball in the direction of the valve seat. This allows the overflow channels to be guided in a particularly streamlined manner.
  • the preferred field of application of the invention is the use of the pump as an oil and / or hydraulic pump for motor vehicle engines and / or transmissions, in particular automatic transmissions.
  • the invention is also applicable to other applications e.g. suitable in hydraulic control systems.
  • the pump shown in FIG. 1 has a pump housing 1 shown in simplified form, in the cylindrical gear chamber of which the ring gear 2 is mounted with its circumference on the peripheral wall of the gear chamber.
  • the shaft 3 carrying the pinion 4 of the gerotor pump is also mounted in the pump housing. In this respect, however, other positions are also possible.
  • the pinion has one tooth less than the ring gear, so that all teeth of the pinion are constantly in engagement with a tooth of the ring gear, as a result of which all the feed cells 13 and 17 formed by the tooth gaps of the pinion and ring gear are constantly sealed against the adjacent cells.
  • the direction of rotation of the pump is clockwise, as indicated by arrow 18.
  • the suction opening 11 is provided, which is dashed in the drawing is shown.
  • the outlet opening 19 is also shown in dashed lines in the top left half. Intake and outlet opening are designed as so-called "kidneys".
  • the center points 5 and 6 of the gear wheels 2 and 4 have the center distance or the eccentricity 7, which together with the tip circle diameters of the gear wheels is responsible for the geometrically specific delivery volume of the running set. This is still proportional to the width 8 of the gears.
  • These geometric variables determine the slope of the theoretical delivery line 9 of the pump shown in dashed lines in FIG. 7. At low speed, the suction speed in the inlet channel, not shown here, is low, so that in the suction kidney 10, which extends over almost the entire circumference of the suction area and is arranged laterally in the housing, the outline of which is shown by the broken line 11, the oil can flow in without bubbles, since none significant negative pressure occurs. The course of the negative pressure is shown at 12 below in FIG. 7.
  • the suction cells in the positions 13 between the teeth 14 and 15 in engagement are filled with largely bubble-free oil.
  • the mouth of the inlet channel or the suction kidney 10 extends in the circumferential direction up to close to the point 16, which is diametrically opposite the point of deepest tooth engagement.
  • the delivery cells formed by two tooth gaps opposite each other have reached their greatest volume and are completely filled with oil at low speed. If the pump then continues to rotate and the delivery cells reach the area to the left of point 16 in FIG. 1, the cells in positions 17 become displacement cells, since the volume of the delivery cells continuously increases from here to the point of deepest tooth engagement to almost zero decreased.
  • the outlet opening 19 the outline of which is shown by the broken line 20, also becomes up to the point 16, and as far as possible, but not so far that a substantial leakage-effective short circuit can occur between the suction and pressure chamber.
  • the delivery cells in positions 17 can release the oil into the pressure channel at the start of their volume reduction without crushing losses.
  • the outlet opening and thus the delivery cell in the first position 17.1 is under full delivery pressure.
  • the outlet opening of the gear chamber or the pressure kidney is shortened very far in the circumferential direction to the point of deepest tooth engagement, as can also be seen in FIG. 1.
  • the delivery cells must also be able to empty themselves accordingly in positions 17.1 to 17.3 with bubble-free oil filling. This is made possible by the overflow channels 128 in the teeth of the ring gear 2.
  • Each overflow channel 128 is provided with a check valve 21. It can be seen that the delivery cells in positions 17.1 to 17.3, in which their volume is steadily decreasing, can empty through the series-connected overflow channels 128 with the check valves 21.1 to 21.3 arranged in them in the delivery direction towards the pressure kidney. In this case, a somewhat higher static pressure must then prevail in the delivery cells in positions 17.1 to 17.3 than in the outlet opening of the pressure kidney 19, since the overflow channels 128 with the check valves 21 are naturally lossy with respect to the flow resistance. At low speed these losses are not high because the flow velocities are low. These throttling losses should of course be kept as small as possible by means of a corresponding design of the check valves.
  • the mouths of the overflow channels and / or the tooth and tooth gap shape must of course lie or be dimensioned such that a liquid flow in the direction of pump rotation is prevented at the point of deepest tooth engagement. This is not a problem.
  • a delivery rate that is in principle proportional to the speed is also delivered in the pump according to the invention. If this limit speed is exceeded, so the static pressure in the feed line begins to drop and drops below a critical value, as can best be seen in FIG. 7. In the pump examined, this speed range is around 1200 rpm. From 1450 rpm the flow rate stagnates despite the increasing speed, since the static suction pressure has fallen below the evaporation pressure of the oil. From now on, cavities are created in the delivery cells in positions 13, which theoretically concentrate in the area of the root circle 22 of the pinion 4, since the bubble-free oil is forced radially outwards by centrifugal force.
  • the pump delivers only 2/3 of its maximum delivery volume, as can be seen from FIG. 7.
  • This state is shown in Fig. 1 by a dashed level line 23 as a concentric circle to the center of the ring gear.
  • This level line 23 is provided with the level symbol 24. Radially inside the level line there is essentially oil vapor and / or air, radially outside there is essentially oil.
  • the level line 23 passes through the tooth base point 25 of the delivery cell in position 17.3, which is in the process of being connected to the pressure kidney or outlet opening 19.
  • the pump is advantageously designed such that, even at the maximum operating speeds to be expected, the level line does not move radially outward much further than to the base of the pinion tooth gap of the delivery cell, which is just beginning to reach the edge of the outlet opening 19.
  • This level line can of course always be located radially further inside, as long as the suction control does not suffer.
  • the delivery cells in positions 17.1 to 17.3 are sealed against each other by tooth flanks or tooth tip engagement and the check valves in the construction shown are not only due to the centrifugal force acting on the valve ball on the one hand, but also due to the static increase from cell positions 17.1 to 17.2 to 17.3 Pressure are closed, the delivery pressure in the outlet opening 19 cannot act into the delivery cells in positions 17.1 to 17.3.
  • the cavities 26 within the leveling ring surface 23 thus have enough time to reduce until the position 17.3 is reached by reducing the cell volume until finally the Cell in position 17.3 connects to the pressure line. The feared cavitation caused by sudden imploding of the cavities is thus avoided.
  • FIG. 2 a section through the centrifugal ball check valve arrangement from FIG. 1 is shown in a greatly enlarged illustration.
  • the ring gear here consists of two halves which are soldered or welded to one another in the parting plane indicated by the parting lines 27 and 28. To the left and right of the ball 29, 30 bypass channels 30 are provided so that when the valve seat 31 is open, there is sufficient passage cross section.
  • the overflow channels 33, 34 are generated in the teeth of the pinion by drilling.
  • the sprocket made here, for example, of steel is undivided.
  • a cavity 35 is incorporated into the teeth from one end face of the pinion, which has a supporting edge 32 which, like the construction to be described later, according to FIGS. 4 and 5, serves to guide the ball 36 during the closing movement .
  • the cavern is not sintered, which is the cheapest, it can also be milled using an NC-controlled milling machine, for example.
  • the overflow channels 33 and 34 can be simply drilled here.
  • the balls 36 are also automatically pressed centered on the valve seat by the centrifugal force and the hydrostatic force. They are prevented from falling out by the housing wall 37.
  • the channels with the ball valves should always be guided in such a way that the centrifugal force already tries to press the valve balls onto their seats.
  • the valve channels should be curved in such a way that the ball movement, as is the case in FIG. 1, has an essential radial component. If you do not have such a possibility, you can use a support edge 32, around which the ball can tilt, so that the ball is first pressed against the support edge 32 by the centrifugal force and continues under the influence of the centrifugal force around this edge 32 into its Valve seat closing position can pivot.
  • the overflow channels and the check valves are arranged in the ring gear, but are somewhat more streamlined than in the embodiment according to FIGS. 1 and 2.
  • a support edge 32 is provided, which is caused by the centrifugal force Tangential closing force component generated so that the valve seat has a tangential line of action C - C.
  • the pump can be manufactured, for example, according to FIGS. 3 and 4.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (12)

  1. Pompe à engrenages annulaires à régulation d'aspiration comportant
    - un carter,
    - une roue à denture intérieure (2) disposée à rotation dans une chambre à engrenages du carter (1),
    - un pignon (4) présentant une dent de moins que la roue à denture intérieure (2), disposé dans celle-ci, engrenant avec la roue à denture intérieure (2), et dont les dents forment conjointement avec les dents de la roue à denture intérieure (2) des cavités de transport pour le liquide de travail s'agrandissant (13) et se réduisant à nouveau (17) en succession et étanches entre elles,
    - des canaux d'admission et de sortie disposés dans le carter (1) pour l'admission et l'évacuation du fluide de travail, qui débouchent dans la chambre à engrenages des deux côtés du point d'engrènement le plus bas (10, 19),
    - un point d'étranglement fixe ou variable prévu dans le canal d'admission,
    - et des soupapes de retenue (21) dans la zone de compression de la pompe,
    caractérisée en ce que
       l'extrémité s'éloignant du point d'engrènement le plus bas de l'embouchure (19) du canal de sortie se trouve près du point d'engrènement le plus bas, de sorte qu'entre elle et le point de la périphérie (16), auquel commencent à se rétrécir les cavités de transport (13, 17), se trouvent en permanence plusieurs cavités de transport (17),
       en ce que les cavités de transport (13, 17) sont reliées avec les cavités de transport adjacentes par les canaux de débordement (128) prévus dans au moins l'une des roues dentées (2, 4),
       et en ce que les soupapes de retenue (21) sont disposées dans les canaux de débordement (128), de sorte qu'elles s'opposent à un écoulement du fluide de travail à l'encontre de la direction de transport.
  2. Pompe à engrenages annulaires selon la revendication 1, caractérisée en ce que les embouchures (10, 19) des canaux d'admission et de sortie se trouvent dans les parois frontales ou dans une paroi frontale de la chambre à engrenages.
  3. Pompe à engrenages annulaires selon la revendication 1 ou 2, caractérisée en ce que les canaux de débordement (128) sont disposés dans les dents des roues (2, 4).
  4. Pompe à engrenages annulaires selon l'une des revendications 1 à 3, caractérisée en ce que les soupapes de retenue (21) sont réalisées sous la forme de soupapes à bille, la force centrifuge du mouvement de rotation de la roue dentée contenant les soupapes ayant tendance à pousser la bille sur le siège de soupape.
  5. Pompe à engrenages annulaires selon l'une des revendications 1 à 4, caractérisée en ce que la roue dentée (2) contenant les soupapes de retenue se compose de deux moitiés, qui contiennent sous forme à symétrie de miroir chacune la moitié des canaux de débordement (128) et du siège de soupape.
  6. Pompe à engrenages annulaires selon la revendication 5, caractérisée en ce que les deux moitiés de roue dentée sont fabriquées par frittage selon la métallurgie des poudres.
  7. Pompe à engrenages annulaires selon la revendication 5, caractérisée en ce que les deux moitiés de la roue sont réunies l'une à l'autre par soudage par explosion.
  8. Pompe à engrenages annulaires selon la revendication 5, caractérisée en ce que les deux moitiés de la roue sont réunies par frittage.
  9. Pompe à engrenages annulaires selon l'une des revendications 4 à 8, caractérisée en ce que les billes (26) sont en matériau non métallique ou sont recouvertes d'un matériau non métallique.
  10. Pompe à engrenages annulaires selon l'une des revendications 1 à 3, caractérisée en ce que les canaux de débordement (33, 34) sont disposés dans le pignon, avec des renfoncements (35) recevant les billes de soupapes usinés depuis une surface frontale axiale du pignon, qui présentent des canaux d'amenée et d'évacuation forés (33, 34).
  11. Pompe à engrenages annulaires selon l'une des revendications 4 à 10, caractérisée en ce que dans la soupape de retenue est prévu un bord d'appui (32) qui crée sur la bille une composante de la force centrifuge s'exerçant tangentiellement en direction du siège de soupape.
  12. Utilisation de la pompe à engrenages annulaires selon l'une des revendications 1 à 11 en tant que pompe à huile et/ou hydraulique pour des moteurs et/ou des transmissions de camions.
EP90119424A 1989-10-11 1990-10-10 Pompe à engrenage annulaires avec régulation d'aspiration Expired - Lifetime EP0422617B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3933978A DE3933978A1 (de) 1989-10-11 1989-10-11 Sauggeregelte zahnringpumpe
DE3933978 1989-10-11

Publications (2)

Publication Number Publication Date
EP0422617A1 EP0422617A1 (fr) 1991-04-17
EP0422617B1 true EP0422617B1 (fr) 1994-03-09

Family

ID=6391284

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90119424A Expired - Lifetime EP0422617B1 (fr) 1989-10-11 1990-10-10 Pompe à engrenage annulaires avec régulation d'aspiration

Country Status (5)

Country Link
US (2) US5096397A (fr)
EP (1) EP0422617B1 (fr)
JP (1) JP2638282B2 (fr)
KR (1) KR0153522B1 (fr)
DE (2) DE3933978A1 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4129854A1 (de) * 1991-09-07 1993-03-11 Teves Gmbh Alfred Zahnradpumpe mit einer nichtlinear von der drehzahl abhaengenden foerdermenge
JPH05164059A (ja) * 1991-12-13 1993-06-29 Aisin Seiki Co Ltd トロコイド型オイルポンプ
DE4209143C1 (fr) * 1992-03-20 1993-04-15 Siegfried A. Dipl.-Ing. 7960 Aulendorf De Eisenmann
DE4216823A1 (de) * 1992-05-21 1993-11-25 Schwaebische Huettenwerke Gmbh Verfahren zur Herstellung eines Zahnrades einer Innenzahnradpumpe
EP0619430B1 (fr) * 1993-03-05 1997-07-23 Siegfried A. Dipl.-Ing. Eisenmann Pompe à engrenage internes pour gamme de vitesses rotatives élévées
CA2159672C (fr) * 1994-10-17 2009-09-15 Siegfried A. Eisenmann Soupape et dispositif de commande a couronne commandee pr aspiration et pompe a engrenages interieurs
DE19523533C2 (de) * 1995-06-28 1998-06-18 Eisenmann Siegfried A Sauggeregelte Innenzahnradpumpe
DE19538633A1 (de) * 1995-10-17 1997-04-24 Schwaebische Huettenwerke Gmbh Pumpenaggregat
DE19622688A1 (de) * 1996-06-05 1997-12-11 Bayerische Motoren Werke Ag Brennkraftmaschine mit mittels schmierölversorgten gesonderten Hydraulikkreisen
US6023990A (en) * 1997-01-17 2000-02-15 Carr; John Bimetallic gear rim
EP1396639A1 (fr) * 2002-09-03 2004-03-10 Techspace Aero S.A. Pompe volumétrique rotative à gerotor
JP2004245151A (ja) * 2003-02-14 2004-09-02 Hitachi Unisia Automotive Ltd オイルポンプ
CN104549793B (zh) * 2015-01-13 2016-03-23 中国石油大学(华东) 一种新型旋流器口径可调式溢流嘴装置
DE102015004984A1 (de) * 2015-04-18 2016-10-20 Man Truck & Bus Ag Innenzahnradpumpe und Fahrzeug mit einer Innenzahnradpumpe
US20190301453A1 (en) * 2018-03-29 2019-10-03 Schaeffler Technologies AG & Co. KG Integrated motor and pump including inlet and outlet fluid control sections
EP4338722A3 (fr) * 2019-01-07 2024-05-29 LuxCan Innovation S.A. Dispositif et procédé de fabrication de comprimés d'une composition de principe actif pulvérulente, liquide, pâteuse, encapsulée ou granulaire
DE102022203867A1 (de) * 2022-04-20 2023-10-26 Hanon Systems Efp Deutschland Gmbh Gerotorpumpe

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7116089U (de) * 1972-10-26 Steyr-Daimler-Puch Ag Zahnradpumpe, insbesondere für Kraftfahrzeuggetriebe
FR405613A (fr) * 1908-11-18 1910-01-08 Hugo Lentz Dispositif d'équilibrage des ailettes de pompes rotatives
US2468373A (en) * 1945-10-03 1949-04-26 Vadim S Makaroff Rotary compressor and fluid seal therefor
US3515496A (en) * 1968-05-06 1970-06-02 Reliance Electric Co Variable capacity positive displacement pump
US4233003A (en) * 1978-10-10 1980-11-11 Jeng Wang Shing Rotary pump
DE3005657C2 (de) * 1980-02-15 1987-01-02 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Zahnradpumpe
JPS57142798A (en) * 1981-02-26 1982-09-03 Nippon Piston Ring Co Ltd Powder molding method and molded article
JPS58215299A (ja) * 1982-06-09 1983-12-14 Nippon Piston Ring Co Ltd 複合バルブシ−トの製造方法
EP0225338B1 (fr) * 1985-05-09 1989-10-25 B a r m a g AG Pompe a capacite variable
DE3627414A1 (de) * 1986-08-13 1988-02-18 Barmag Barmer Maschf Verbrennungsmotor
US4850814A (en) * 1987-01-09 1989-07-25 Barmag Ag Hydraulic gear pump
DE3819623A1 (de) * 1988-01-14 1989-07-27 Vdo Schindling Fluegelzellenpumpe

Also Published As

Publication number Publication date
KR910008286A (ko) 1991-05-31
KR0153522B1 (ko) 1999-01-15
US5122335A (en) 1992-06-16
DE3933978A1 (de) 1991-05-02
US5096397A (en) 1992-03-17
JP2638282B2 (ja) 1997-08-06
DE3933978C2 (fr) 1991-08-22
DE59004887D1 (de) 1994-04-14
JPH03175182A (ja) 1991-07-30
EP0422617A1 (fr) 1991-04-17

Similar Documents

Publication Publication Date Title
EP0422617B1 (fr) Pompe à engrenage annulaires avec régulation d'aspiration
DE3333647C2 (de) Schmiermittelpumpe für die Druckerzeugung bei einem druckumlaufgeschmierten Verbrennungsmotor
DE1703251C3 (de) Schraubenverdichter mit zwei Schraubenrotoren und ölzufuhr zum Arbeitsraum und zu Wellenlagern
DE3005657A1 (de) Zahnradpumpe
EP0619430B1 (fr) Pompe à engrenage internes pour gamme de vitesses rotatives élévées
DE1528951B2 (fr)
DE2637263A1 (de) Rotorverdraengermaschine mit einer schnecke
EP1141551B1 (fr) Ensemble de pompes comportant deux pompes hydrauliques
DE1528949A1 (de) Pumpe mit in der Saugleitung eingebauter,verstellbarer Drossel
EP1749145A1 (fr) Commande du courant de fuite d'intervalle d'une machine a engrenages
DE2826071A1 (de) Fluessigkeitspumpe der spiral-bauart
WO2009092719A2 (fr) Pompe à engrenage intérieur, à volume variable
EP0839283B1 (fr) Pompe a vide a palettes rendue etanche a l'huile, avec alimentation en huile
DE102016207093B4 (de) Zahnradfluidmaschine
EP0561304B1 (fr) Pompe à engrenages avec contrôle de l'aspiration
DE4011671C2 (de) Regelbare Flügelzellenpumpe
EP0225338B1 (fr) Pompe a capacite variable
WO2005024237A1 (fr) Machine a piston rotatif
EP0846861B1 (fr) Pompe annulaire à engrenages continuellement variable
WO2005093259A1 (fr) Pompe volumetrique a debit volumetrique variable
WO2011128218A2 (fr) Pompe à engrenage
DE19507975A1 (de) Flügelzellenverdichter
DE4338677C2 (de) Pumpe zum Fördern von Fluid, insbesondere als Kraftstoff-Förderaggregat für Kraftfahrzeuge
DE4330586A1 (de) Innenzahnradpumpe für großen Drehzahlbereich
DE3931186C2 (de) Zahnradmotor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE FR GB IT LI SE

17P Request for examination filed

Effective date: 19910607

17Q First examination report despatched

Effective date: 19920904

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR GB IT LI SE

ITF It: translation for a ep patent filed
REF Corresponds to:

Ref document number: 59004887

Country of ref document: DE

Date of ref document: 19940414

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19940325

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

EAL Se: european patent in force in sweden

Ref document number: 90119424.1

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20000915

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20000921

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20001002

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20001005

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20001012

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011010

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011011

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011031

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011031

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20011010

EUG Se: european patent has lapsed

Ref document number: 90119424.1

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020628

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020702

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051010