EP0473025B1 - Pompe à engrenages internes pour fluide hydraulique - Google Patents

Pompe à engrenages internes pour fluide hydraulique Download PDF

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Publication number
EP0473025B1
EP0473025B1 EP91113738A EP91113738A EP0473025B1 EP 0473025 B1 EP0473025 B1 EP 0473025B1 EP 91113738 A EP91113738 A EP 91113738A EP 91113738 A EP91113738 A EP 91113738A EP 0473025 B1 EP0473025 B1 EP 0473025B1
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EP
European Patent Office
Prior art keywords
eccentric
pump
radius
chamber
inlet
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
EP91113738A
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German (de)
English (en)
Other versions
EP0473025A1 (fr
Inventor
Siegfried Hertell
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.)
Barmag Luk Automobiltechnik GmbH and Co KG
Original Assignee
Barmag Luk Automobiltechnik 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.)
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Publication date
Application filed by Barmag Luk Automobiltechnik GmbH and Co KG filed Critical Barmag Luk Automobiltechnik GmbH and Co KG
Priority to AT91113738T priority Critical patent/ATE96886T1/de
Publication of EP0473025A1 publication Critical patent/EP0473025A1/fr
Application granted granted Critical
Publication of EP0473025B1 publication Critical patent/EP0473025B1/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
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • F04C15/066—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type
    • F04C15/068—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type of the elastic type, e.g. reed 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0065—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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 a gear pump according to the preamble of claim 1.
  • This pump is known from DE-OS 34 48 253 (PP-1372).
  • the inner wheel is mounted eccentrically in the recess of a rotor to the pump axis.
  • the rotor in turn is rotatably supported in the space formed by the outer wheel and is firmly connected to the pump shaft, which serves to drive the rotor.
  • the known pump has a circular-cylindrical inlet space lying in an end wall and a channel system arranged in the rotor, which meshes with the circular-cylindrical insert space and is in permanent communication.
  • the deflection of the pump shaft cannot lead to a tilting of the inner wheel and thus to a leak in the pump and a reduction in its efficiency.
  • This advantage is particularly effective when the pump shaft is also used to drive other machine parts and / or when transverse forces are introduced into the pump shaft via the drive of the pump shaft, which can lead to misalignment.
  • the solution according to claim 2 serves the further purpose of avoiding static overdeterminations, since here the inner wheel is not positively fixed by the outer wheel with regard to its current axis of rotation.
  • the solution according to claim 3 achieves good cooling and lubrication of the eccentric, which is subjected to heat and wear due to the sliding bearings inside and outside.
  • the pump is advantageously operated with suction throttling, in which the inlet is throttled and a separate outlet valve is provided in the outlet for each cell formed by the toothing.
  • a separate outlet valve is provided in the outlet for each cell formed by the toothing.
  • a solution for the position of the inlet throttling results alternatively from claims 4 or 5.
  • the solution according to claim 5 has the advantage that the outer seals of the pump are not under pressure. A vacuum is only created when it is introduced into the pump.
  • the particular advantage of the design according to this invention results when used as a hydraulic pump for the hydraulic converter or the hydraulic clutch of an automatic motor vehicle transmission.
  • the pump according to the invention in its design and centering is independent of the design and centering of the hydraulic converter or the hydraulic clutch.
  • the loads on the pump and turbine wheel of the hydraulic converter cannot affect the hydraulic pump.
  • the compressive forces acting on the inner wheel and on the eccentric, as well as the force with which the clutch flap of the drive shaft engages in the eccentric substantially compensate and are aligned parallel to one another.
  • the driver pocket of the eccentric lies behind the plane of symmetry that passes through the pump axis.
  • the radial boundary wall of the driving pocket pointing in the direction of rotation lies essentially parallel to the secant of the inner wheel, which delimits the pressure zone on the inner wheel.
  • the pump housing is formed by the pump casing 1 and the end plates 2 and 3, which are stacked on top of one another.
  • the housing jacket 1 has a circular cylindrical interior, in the cylindrical inner jacket of which a circumferential groove 4 is pierced.
  • the outer wheel 6 is fastened to the webs 5 which remain to the side.
  • the entire package consisting of housing shell 1, end plates 2 and 3 and outer wheel 6 is held together by a screw 7.
  • the screw connection 7 penetrates the outer wheel in the region of the tooth heads with holes 8.
  • the outer wheel has an internal toothing.
  • the interior of the pump is thus circumscribed by the internal toothing with tip circle 9 of the outer wheel.
  • a pin 10 is firmly inserted at one end.
  • the other end of the pin 10 projects into the interior of the pump.
  • an eccentric 11 is freely rotatable.
  • the axial width of the eccentric corresponds essentially to the axial width of the housing shell 1 and the outer wheel 6.
  • the eccentric has a circular cylindrical outer circumference, the central axis of which is indicated at 12 and which rotates with the eccentricity E about the axis 13 of the pin 10.
  • the inner wheel 14 is freely rotatably mounted on the eccentric 11.
  • the inner wheel 14 has external teeth.
  • the eccentricity E of the eccentric and the external toothing of the inner wheel are dimensioned and the toothings are designed so that the external toothing of the inner wheel meshes with the internal toothing of the outer wheel. Therefore, the top circles 9 and 15 of the toothing intersect in the circumferential intersections 21 and 22. On the inner circumference of the top circle 9 of the outer wheel, this results in between the intersections 21 and 22 on the one hand on the side of the axis 13, in which the eccentricity E points circumferential engagement area and on the other hand on the side of the axis 13, which faces away from the eccentricity, the circumferential inner sickle space 23 of the pump.
  • the teeth are designed so that the teeth of the outer and inner wheel between the intersections 21 and 22 of the tip circles 9 and 15 are in sealing engagement with their flanks. There are therefore several tooth cells between the intersections 21 and 22 in the engagement area, which are sealed by touching their flanks to one another and to the inner crescent space 23 facing away from the eccentricity.
  • the drive shaft 16 is used to drive the pump.
  • the drive shaft 16 is rotatably mounted concentrically to the central axis 13 of the pin 10 in the other end plate 2 and its end is essentially flush with the inside of the pump chamber.
  • the shaft 16 forms an end face on which a coupling tab 17 is attached eccentrically. This coupling tab 17 protrudes axially into a driving pocket 18 which is introduced into the adjacent end face of the eccentric 11 in the region of the eccentricity.
  • the pump has an essentially radial inlet channel 19 in the end plate 3.
  • the inlet channel opens into a distributor space 20 which concentrically surrounds the pin 10.
  • the distribution space is designed as a circular cylindrical recess in the end face of the end plate, which delimits the pump space. Their radius is smaller than the radius Fi of the root circle of the inner wheel.
  • a further circular cylindrical recess is made concentrically with the axis 13.
  • This recess serves as the inlet chamber 28.
  • the distributor chamber 20 and the inlet chamber 28 are connected to one another by channels which penetrate the eccentric axially. These channels are preferably designed as grooves in the inner bore of the eccentric and serve to lubricate the slide bearing of the eccentric on the journal 10 and also to cool the eccentric 11. As such Channel is the driver pocket 18, which therefore axially penetrates the eccentric 11 and rotates with its outer edge on a radius that is slightly larger than the radius of the shaft. Several such channels can also be provided. From Fig.
  • the outer radius R of the inlet chamber 28, based on the axis 13 of the pin 10, has to be kept within certain limits according to the invention, which will be discussed later.
  • the dimensioning of the outer radius R of the inlet chamber 28 is such that the root circle Fi of the inner wheel or the circular area circumscribed by this root circle covers the inlet chamber 28 with the exception of a crescent-shaped inlet surface 27.
  • the inlet surface is also partially covered by the sides of the teeth of the inner wheel.
  • the inlet surface 27 runs on the side of the interior facing away from the eccentricity.
  • the dimensioning according to the invention of the outer radius R of the inlet chamber 28 on the one hand and the root circle Fi of the inner wheel on the other hand ensures that the crescent-shaped inlet surface 27 is never covered by one of the closed tooth cells of the engagement area. This avoids a dead travel of these tooth cells in the pressure area and the hydraulic efficiency improved.
  • the outlet channel 24 is located radially in the housing shell 2 and is connected to the circumferential groove 4 of the housing shell. This circumferential groove is limited on the inside by the outer circumference of the outer wheel and forms an outer chamber.
  • the outer wheel has at least one outlet bore 25 in the region of each tooth gap.
  • Fig. 1 it is shown that two outlet bores 25.1 and 25.2 are adjacent to each other in the axial direction per tooth gap.
  • the outlet bores are each arranged in parallel radial planes.
  • Each radial plane is covered by an elastic valve ring 26.1 and 26.2, which covers all the outlet bores of a normal plane and is thereby severed in an axial plane.
  • One end is e.g. held by a rivet, the other end is free to move.
  • These valve rings 26.1, 26.2 serve as check valves for each of the outlet bores.
  • the drive shaft 16 is driven with the direction of rotation 31.
  • the clutch tab 17 engages in the driving pocket 18 of the eccentric and takes the eccentric with it.
  • the outer wheel 6 executes a wobbling movement in the interior of the pump, whereby it rotates in the direction of rotation 32 as a result of the engagement of its toothing with the toothing of the outer wheel.
  • It forms with the toothing of the outer wheel in the engagement area between the intersection points 21, 22 of the two circles of the head a plurality of tooth cells, which continuously enlarge and reduce.
  • the cells enlarge until they open and come into contact with the inner sickle space 23 filled with oil.
  • the cells shrink on the leading side of the inner wheel. So here the oil is put under pressure. If the pressure in a cell is in the circumferential groove 4 exceeds the prevailing system pressure, there the valve rings 26.1 and 26.2 are lifted off the outlet bores 25.1, 25.2 due to the pressure difference, so that the oil can be expelled from the cell.
  • the width of the crescent-shaped inlet surface 27, which is limited on the outside by the circumferential surface of the inlet chamber 28 and on the inside by the root circle of the inner wheel, may only be one division greater than the width of the crescent-shaped interior 23, which is limited by the two root circles.
  • the width of these crescent-shaped spaces and the division is measured in each case as a central angle about the central axis 13 of the pump.
  • the pump can preferably also be used as a suction-restricted pump.
  • the inlet duct 19 has a throttle 33.
  • This throttle only a limited amount of oil can be drawn in.
  • This time-limited suction quantity is only sufficient to completely fill the pump up to a certain speed.
  • the pump delivery rate is therefore proportional to the speed only up to this speed. When the speed increases no further increase in output. Therefore, increasing the speed is not associated with increased power consumption.
  • the pump is therefore particularly suitable for consumers in motor vehicles who have an oil requirement that is not dependent on the strongly fluctuating engine speed.
  • FIG. 3 schematically shows a hydraulic converter with an integrated hydraulic pump according to this invention.
  • a hydraulic converter is e.g. B. in the book “Dubbel”, Taschenbuch des Maschinenbau, p. 904/905, 14th edition.
  • the pump wheel 34 is driven by the pump shaft 35. The output takes place via turbine wheel 36 and turbine shaft 37. Intermediate is stator wheel 38, which is rotatably mounted on stator pin 10.
  • the pump wheel 34 is connected to a hollow cylindrical drive shaft 16 which concentrically surrounds the stator pin 10.
  • the stator pin 10 is fastened in the converter housing 39.
  • the hydraulic pump is fitted into a recess in the converter housing 39. It consists of end plate 2 and 3 and the outer wheel 6 fastened in between by screw 7.
  • the eccentric 11 On the stator pin 10, the eccentric 11 is freely rotatable by means of plain bearings.
  • the inner wheel 14 is freely rotatably mounted on the eccentric 11.
  • the eccentric 11 has an axially parallel recess (driver pocket 18) into which a coupling tab 17 of the drive shaft 16 engages.
  • a seal 40 is located between the end plate 3 and the drive shaft 16.
  • the inlet chamber 28 described above is delimited by this seal 40.
  • This circular cylindrical inlet chamber 28 is designed such that it only slightly projects beyond the root circle of the inner wheel 14 in the inlet area so that the throttling required for the suction throttle control results directly on the inner wheel. This in turn means that the Inlet chamber 28 is at atmospheric pressure so that the seal 40 is not under pressure.
  • the circular cylindrical distributor space 20 On the opposite side of the eccentric 11, the circular cylindrical distributor space 20 is formed in the
  • a pressure chamber 4 is formed on the outer circumference of the outer wheel.
  • the outlet channels of the pressure cell formed by the toothing connect each cell formed between two teeth of the outer wheel to the pressure chamber 4.
  • a valve ring 26, which surrounds the outer circumference, serves as a check valve.
  • the pressure chamber 4 is delimited on the outside by the converter housing 39.
  • the pressure chamber 4 has a further outlet channel 29.
  • the plane of symmetry here denotes the axial plane of the eccentric, in which both the center of rotation of the eccentric, namely the pump axis 13, and the center of the circle 42 of the eccentric lie.
  • the Driving pocket 18 is placed so that the driving force which the clutch flap 17 exerts on the radial boundary wall of the driving pocket 18 runs essentially parallel to the resultant of the compressive forces which affect the inner wheel and the eccentric. It should be noted that this is a suction-restricted pump.
  • the most unfavorable load case for this pump lies in the lower speed range, in which all of the closed cells formed in the toothing are filled with oil and are therefore subjected to pressure in the pressure zone.
  • the front radial boundary wall of the driving pocket 18 is therefore essentially parallel to the secant which intersects the beginning and end of the pressure zone.
  • the beginning of the pressure zone lies in the plane of symmetry 41 and the end of the pressure zone lies where the tip circles of the inner wheel and the outer wheel intersect, ie where the last meshing of the inner wheel and outer wheel takes place.
  • this is preferably the case at the intersection of the tip circles.

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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)

Claims (8)

  1. Pompe à engrenages internes pour liquide hydraulique, dans laquelle la roue extérieure pourvue d'une denture intérieure est fixe et définit une chambre interne fermée, dans laquelle la roue intérieure plus petite pourvue d'une denture extérieure engrène avec la roue extérieure et est montée libre en rotation sur un excentrique et dans laquelle l'excentrique (11) est entraîné en rotation autour de l'axe de pompe (13) concentrique avec la roue extérieure (6) par l'arbre d'entraînement (16) qui est également concentrique à celui-ci, caractérisée par le fait que l'excentrique (11) est monté libre en rotation sur un tourillon (10) concentrique à l'axe de pompe (13), monté fixe et en porte-à-faux sur le carter et est rendu solidaire en rotation de l'arbre d'entraînement (16) par un moyen d'accouplement (17), (18).
  2. Pompe selon la revendication 1, caractérisée par le fait que la différence de nombre de dents de la roue extérieure par et de la roue intérieure (14) est d'au moins 2.
  3. Pompe selon la revendication 1 ou 2, caractérisée par le fait que l'aspiration comporte une chambre d'aspiration (28) cylindrique circulaire, concentrique avec la roue extérieure, qui est aménagée dans la paroi frontale et dont le rayon extérieur est inférieur à la somme de l'excentricité et du rayon du cercle de pied de la roue intérieure (14) et supérieur à la différence entre le rayon du cercle de pied de la roue intérieure et l'excentricité, par le fait que la roue intérieure (14) couvre partiellement la chambre d'aspiration (28) en laissant libre une surface d'aspiration (27) en forme de croissant qui tourne et s'étend sur un angle au centre mesuré à partir de l'axe de pompe (13) qui est inférieur à la somme de l'angle de pas et de l'angle au centre, mesuré à partir de l'axe de pompe (13), de l'espace intérieur (23) tournant en forme de croissant qui est défini par les cercles de tête du côté opposé à l'excentricité.
  4. Pompe selon l'une au moins des revendications précédentes, caractérisée par le fait que le conduit d'aspiration (19) comporte un étranglement (33).
  5. Pompe selon l'une des revendications 1 à 4, caractérisé par le fait que la chambre de répartition (28) a une forme d'anneau circulaire, est concentrique à l'axe de pompe, a un rayon qui est légèrement supérieur à la différence entre le rayon de cercle de pied de la roue intérieure et l'excentricité et communique exclusivement par étranglement avec les cellules formées par la denture.
  6. Pompe selon l'une des revendications précédentes, caractérisé par le fait que l'excentrique est monté tournant sur le tourillon (10) de l'aubage directeur d'un convertisseur hydraulique et est solidaire en rotation de l'arbre d'entraînement de la pompe du convertisseur hydraulique.
  7. pompe selon la revendication 3, caractérisé par le fait que l'excentrique (11) est contigu d'une part à la chambre d'aspiration (28) et d'autre part à une chambre de répartition (20) cylindrique circulaire, qui communique avec le conduit d'aspiration (19) et a un rayon extérieur qui est inférieur au rayon du cercle de pied de la roue intérieure, par le fait que la chambre de répartition et la chambre d'aspiration communiquent par des conduits (19, 29, 30) parallèles qui traversent l'excentrique et, de préférence, sont aménagés sous forme de rainure axiales dans le palier lisse de montage de l'excentrique sur le tourillon et/ou dans le palier lisse de montage de la roue intérieure sur l'excentrique, le logement d'entraînement (18) servant à l'accouplement avec l'arbre d'entraînement pouvant aussi être utilisé à cet effet.
  8. Pompe selon l'une des revendications précédentes, caractérisée par le fait que l'arbre d'entraînement (16) est lié à l'excentrique (11) par une languette (17) d'accouplement axiale qui pénètre dans un logement d'entraînement (18) de l'excentrique et par le fait que, par rapport au sens de rotation de l'arbre d'entraînement, le logement d'entraînement (18) est situé derrière le plan de symétrie de l'excentrique , c'est-à-dire le plan axial dans lequel se trouvent l'axe de pompe (13) et le centre du cercle de l'excentrique, de manière telle que la force d'appui de la languette d'accoupiement dans le logement d'entraînement et la résultante des forces de pression se compensent sensiblement mutuellement.
EP91113738A 1990-08-20 1991-08-16 Pompe à engrenages internes pour fluide hydraulique Expired - Lifetime EP0473025B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT91113738T ATE96886T1 (de) 1990-08-20 1991-08-16 Innenzahnradpumpe fuer hydraulikfluessigkeit.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4026261 1990-08-20
DE4026261 1990-08-20

Publications (2)

Publication Number Publication Date
EP0473025A1 EP0473025A1 (fr) 1992-03-04
EP0473025B1 true EP0473025B1 (fr) 1993-11-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP91113738A Expired - Lifetime EP0473025B1 (fr) 1990-08-20 1991-08-16 Pompe à engrenages internes pour fluide hydraulique

Country Status (4)

Country Link
EP (1) EP0473025B1 (fr)
JP (1) JP3011797B2 (fr)
AT (1) ATE96886T1 (fr)
DE (1) DE59100553D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016217267A1 (de) 2016-09-09 2018-03-15 Mahle International Gmbh Anordnung für eine Kälteanlage mit einem Spiralverdichter

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1271052B (it) * 1993-11-18 1997-05-26 Pompa ad ingranaggi interni con sporgenze volumetriche
AU2003287862A1 (en) * 2002-11-14 2004-06-03 Luk Automobiltechnik Gmbh And Co. Kg Pump
JP2008251687A (ja) 2007-03-29 2008-10-16 Toshiba Corp プリント回路板、およびこれを備えた電子機器

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2350469A1 (fr) * 1976-05-03 1977-12-02 Bosch Gmbh Robert Groupe de refoulement de carburant constitue d'une pompe et d'un moteur electrique

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1099560A (fr) * 1954-02-15 1955-09-07 Perfectionnements aux machines à engrenages conjugués et leurs applications
DE3005657A1 (de) * 1980-02-15 1981-08-20 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Zahnradpumpe
DE3444859A1 (de) * 1983-12-14 1985-06-27 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Rotationszellenpumpe fuer hydrauliksysteme
DE3504783A1 (de) * 1984-02-15 1985-10-24 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Zahnradpumpe mit innenverzahnung
GB2219631B (en) * 1988-06-09 1992-08-05 Concentric Pumps Ltd Improvements relating to gerotor pumps

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2350469A1 (fr) * 1976-05-03 1977-12-02 Bosch Gmbh Robert Groupe de refoulement de carburant constitue d'une pompe et d'un moteur electrique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016217267A1 (de) 2016-09-09 2018-03-15 Mahle International Gmbh Anordnung für eine Kälteanlage mit einem Spiralverdichter

Also Published As

Publication number Publication date
JPH04255585A (ja) 1992-09-10
ATE96886T1 (de) 1993-11-15
JP3011797B2 (ja) 2000-02-21
DE59100553D1 (de) 1993-12-09
EP0473025A1 (fr) 1992-03-04

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