EP0469135B1 - Pompe ou moteur a engrenages - Google Patents

Pompe ou moteur a engrenages Download PDF

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Publication number
EP0469135B1
EP0469135B1 EP91905137A EP91905137A EP0469135B1 EP 0469135 B1 EP0469135 B1 EP 0469135B1 EP 91905137 A EP91905137 A EP 91905137A EP 91905137 A EP91905137 A EP 91905137A EP 0469135 B1 EP0469135 B1 EP 0469135B1
Authority
EP
European Patent Office
Prior art keywords
gear pump
motor according
filler
seal
approximately
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
EP91905137A
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German (de)
English (en)
Other versions
EP0469135A1 (fr
Inventor
Jacek Zatrieb
Clemens DÖRFLINGER
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.)
Bucher GmbH Maschinenfabrik
Original Assignee
Bucher GmbH Maschinenfabrik
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 Bucher GmbH Maschinenfabrik filed Critical Bucher GmbH Maschinenfabrik
Publication of EP0469135A1 publication Critical patent/EP0469135A1/fr
Application granted granted Critical
Publication of EP0469135B1 publication Critical patent/EP0469135B1/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
    • 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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention relates to a gear pump or motor according to the preamble of claim 1.
  • the leakage currents of the medium to be conducted between the high-pressure and low-pressure space are to be kept as low as possible in the present subject.
  • the sealing between the high-pressure and low-pressure space places high demands, among other things, on the sealing element - also called a filler piece - which, on the one hand, must be able to seal the gap entering at least one side facing the toothing and to compensate for the loads of the acting forces take.
  • the sealing element on the adjacent parts should be distinguished by advantageous sliding properties.
  • an internal gear machine which has a semi-crescent shaped filler which is divided along an approximately circumferentially extending partial surface, the filler parts of which are supported with support surfaces on an axially penetrating the space between the ring gear and pinion, rotatable about its longitudinal axis Support the stored filler pin.
  • a flat support surface is provided on the filler pin and the filler has several parts, the assembly of which requires appropriate care and special attention.
  • a rotary lobe machine, pump or a motor is known from DE-B-1'280'056 (Robert Bosch). This has two internal gears, with pressure plates pressed on both sides of the same sealingly against the gear side surfaces. On the rear sides facing away from the gearwheels there is a pressure field delimited by a seal, which can be acted upon by liquid under pressure. Viewed in cross-sections through the machine, this lies eccentrically to the gear axis of rotation or shifted to one side with respect to the internally toothed outer wheel.
  • This rotary piston machine which is provided with two connections serving as pressure or low-pressure channel, is designed in such a way that the contact pressure of the pressure plates on the gear side surfaces is at least almost uniform in both directions of rotation of the gear wheels.
  • the size and position of the pressure fields can best counteract the axial forces occurring on the gear side surfaces with a simple shape. This is achieved in that the pressure field behind the pressure plate located on one side of the gearwheels, when viewed in corresponding cross-sectional planes, is arranged opposite to eccentric with respect to the gearwheel axes of rotation. It is thus shifted in relation to the outer wheel in the opposite direction to the pressure field behind the pressure plate located on the other side of the gear wheels.
  • the first-mentioned pressure field is connected to one of the connections (pressure or low-pressure channels) and the second-mentioned pressure field to the other connection of the Machine. These connections can be used alternately as inlets or outlets, which means that the machine can be used reversibly in its direction of rotation.
  • the invention is therefore based on the object of designing the filler piece of a gear pump or a geared motor of the type described at the outset in such a way that the seal between the high-pressure and low-pressure spaces is considerably improved and the assembly of the filler piece is simplified and the functional reliability is increased and less wear and tear - for example by Reduction of the support surfaces - can be determined.
  • this object is achieved in that the bearing journal (s) are arranged at least approximately at the end of the sealing body facing the low-pressure chamber and in that the separating gap extends at least approximately to the end of the filling piece facing the low-pressure chamber.
  • a preferred embodiment of the filler has a one-piece filler formed from the sealing body and bearing journal.
  • the installation of the filler in the laterally adjacent parts of the gear pump or the gear motor can be done in the simplest way.
  • the arrangement of the bearing journals on the end of the sealing body facing the low-pressure chamber permits optimal use of the sealing surfaces on the tooth tips, in that the outer sides of the sealing body extend over the entire length of the filler in the intermediate space.
  • the filler can be provided with a separating gap which extends in the circumferential direction from the high-pressure region and forms an inner and an outer leg.
  • sealing body and bearing journal together form a filler piece makes it possible, among other things, for the separating gap to be designed at least approximately over the entire length of the filler piece. This means that the inner and outer legs are connected to each other at the end of the filling piece facing the low-pressure chamber.
  • the separating gap has a cavity at the end facing the low-pressure chamber, in order to thereby largely avoid the notch effect occurring in the sealing body as a result of the separating gap and to increase the elasticity of the inner and outer legs.
  • the cavity can have partition walls which are evenly spaced approximately in the circumferential direction, in order to be able to provide the cavity as a core during the manufacture of the filler blank by casting.
  • the cavity could be tapered towards the low-pressure chamber, and thereby have an advantageous effect on the strength, wear and elasticity of the filler.
  • the separating gap is arranged at least approximately in the center of the sealing body at least in the region of the bearing journal. This also applies if the separation gap ends before the journal.
  • a copper alloy such as brass or bronze, which has good sliding and dry running properties, is recommended as the material.
  • another material equipped with these properties and a favorable elasticity behavior can also be used.
  • Bi-metals or coated materials can also be used.
  • the constructive measure that the cavity in the sealing body extends beyond the circumference of the bearing journal facing the high-pressure region can simplify the manufacture of the separation gap in front of the cavity, for example by wire EDM.
  • the proposed design and type of manufacture of the separation gap can save manufacturing costs.
  • the sealing body could have a cavity which extends over a large proportion of the filler piece and is connected, for example, to the high-pressure region via one or more bores or lateral grooves.
  • This cavity would be advantageous in terms of a favorable adaptability of the inner and outer legs to the outer shape of the sealing body, i.e. the walls of the cavity run approximately parallel to the outer sides of the inner and outer legs.
  • the cavity could be designed as the core of a model.
  • the filler formed from the sealing body and bearing journal could be separated into two separate parts by the separating gap, it being possible for the low-pressure and high-pressure space to be separated by a shaft arranged across the width of the separating gap.
  • the inner and outer legs are preferably provided with bearing shells.
  • the shaft itself can be anchored or supported rotatably or rotatably in these bearing shells.
  • the latter embodiment allows pivoting movements of the inner and outer legs in the pivot bearing formed by the shaft and bearing shells, that also separates the high pressure area from the low pressure room.
  • the arrangement of the swivel bearing along the length of the separation gap is to be determined in coordination between the volumetric efficiency of the gear pump or motor and the wear caused by friction between the teeth and the sealing body.
  • the seal between the high-pressure area and the low-pressure space takes place by means of a shaft and bearing shells on the inner 15 and outer legs 16.
  • the shaft could be offset along the length of the separating gap from the axis of the bearing journal and thus serve to seal the separating gap.
  • the bearing journal (s) can be arranged away from the end of the sealing body facing the low-pressure chamber.
  • the sealing body in the region of the bearing journal (s) is designed with a recessed section on at least one of the sides facing the tooth tips, so that the pivoting movements of the inner and outer legs result in favorable sealing conditions.
  • bearing pins have a larger diameter than the height of the sealing body, that at least one outer side of the sealing body merges approximately flush with the circumference of the bearing pin.
  • the bearing journal (s) are arranged on the sealing body in the line of action of the resultants resulting from the hydraulic forces acting on the sealing body; also with a shortened separation gap that ends in front of the bearing journal (s).
  • the shape at the end of the sealing body facing the low-pressure space is advantageously adapted to the peripheral shape of the bearing journal.
  • An improvement in the efficiency of the filler piece can be achieved if at least one of the inner and outer legs is designed to bear against the toothing of the ring gear and / or pinion.
  • the filler can be fixed rigidly or movably for its effectiveness.
  • FIG. 1 shows an internal gear pump 1 with an internally toothed ring gear 2 and a pinion 3 meshing therewith, between which a filler 8 formed from a sealing body 7 and at least one bearing pin 6 is arranged or supported in an intermediate space 4.
  • the filler 8 and the toothings 9, 10 of the ring gear 2 and the pinion 3 delimit the low-pressure space 11 into which the pumped medium flows on the one hand, and on the other hand there is a high-pressure region 13 between these toothings 9, 10 at the end of the sealing body 7 at the rear in the flow direction .
  • a dash-dotted line 12 is to illustrate the possibility of arranging the bearing journal (s) 6 on the length of the sealing body 7 in the intermediate space 4.
  • the offset bearing journal 6 can also be seen outside a possible central axis of the sealing body 7.
  • the filler piece 8 which, like in FIG. 1, is formed in one piece, with the difference that in the sealing body 7, from the rear end of which is located in the high-pressure region 13, one to the Axes of the ring gear 2 and the pinion 3, the separation gap 14, which has approximately parallel separating surfaces, extends into and ends in the bearing journal 6, in the present case the bearing journal 6 being arranged on the end of the sealing body 7 facing the low-pressure chamber 11.
  • the separation gap 14 divides the sealing body 7 into an inner leg 15 and an outer leg 16, which are firmly connected at the end facing the low-pressure chamber 11.
  • the separating gap 14 is formed by the two aligned bearing journals 6 in an enlarging manner by means of a continuously increasing or drop-like cavity 23 which is intended to considerably reduce the notch effect.
  • a sealing device 18 each consisting of a half-shell 19 assigned to each leg 15, 16, which together hold a sealing roller 20, which seals the opening of the continuing separating gap 14 from the high-pressure chamber 13 by the pressure from the high-pressure region 13.
  • This sealing device 18 is arranged in coordination with an expansion caused by the pressure in the separating gap 14 on the legs 15, 16 at a corresponding location in the separating gap 14, which extends approximately through the axis of the cylindrical bearing journal 6 and at least approximately in the center of the crescent-shaped shape of the sealing body 7 is distributed.
  • the width of the sealing body 7 is matched to those widths of the ring gear 2 and pinion 3 so that the sealing body 7 remains movable.
  • the sealing body 7 has a recessed section 21 on the outer leg 16 or on its outer side facing the toothing 9 of the ring gear 2.
  • the separation gap 14, as well as the cavity 23 provided at its end, are arranged approximately centrally in the circumferential direction in the sealing body 7 and extend over the entire length of the bearing journal 6.
  • FIG. 4 An alternative embodiment is shown in FIG. 4, according to which the separating gap 14 is formed at the end with a cavity 23 which continues approximately in alignment and has spaced apart partitions 22.
  • This cavity 23 improves the elasticity and adaptability of the legs 15, 16 on the tooth heads of the toothings 9, 10 of the ring gear 2 and pinion 3 and can be left out by a core when casting the filler blank.
  • the partition walls 22, which run approximately parallel according to FIG. 4 and are connected at the end by a regular circular curvature, could also be arranged to form a different geometric shape. Since the separation gap 14 can be produced by wire EDM, but paragraphs are a hindrance to such processing, the cavity 23 expands over the journals 6 in the sealing body 7.
  • This embodiment could also have a sealing device 18, as can be seen in FIG. 2, and the recessed section 21 could also be provided on the opposite side of the sealing body 7 or on both sides.
  • the filler 8 or sealing body 7 in FIG. 5 has a crescent-shaped cavity 23 which is connected to the high-pressure region 13 by a bore 24.
  • This embodiment is particularly suitable when using an elastic material.
  • the dividing walls 22 are preferably arranged parallel to the outer sides of the sealing body 7 or in alignment with the curvature of the separating gap 14 and connected at both ends by curvatures.
  • FIG. 6 shows a filling piece 8 in which the separating gap 14 ends in an expanded form, as for example in FIG. 2, but in front of the bearing journal 6 in the sealing body 7.
  • FIG. 7 shows a two-part filling piece 8, the separating gap 14 from the high-pressure region 13 to the low-pressure chamber 11, approximately evenly distributed over the crescent-shaped cross-sectional shape, forming two separate parts made of inner leg 15 and bearing part 25 on the one hand and outer leg 16 and bearing part 26 on the other .
  • a shaft 29 in bearing shells 27, 28 which, when the filler piece 8 is mounted, keeps the pressurized space of the separating gap tight with respect to the low-pressure space 11.
  • a sealing device 18 - as shown in FIG. 2 - could be installed in front of the axis of the bearing journal 6 in the separating gap 14 or in addition to the shaft 29, a sealing device 18 in the separating gap 14.
  • the design of the filler pieces 8 according to FIGS. 1 to 7 allow the special arrangement between the sealing body 7 and the journal 6, such that the line of action of the resulting hydraulic force acting on the sealing body 7 intersects the axis of the journal 6.

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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)

Abstract

L'élément intercalaire (8) d'une pompe (1) ou d'un moteur à engrenages, monté dans l'espace intermédiaire (4) formé par une roue à denture intérieure (2) et un pignon (3), présente un élément d'étanchéité (7) en forme de faucille auquel sont reliés des tourillons (6) à écartement latéral, et est formé d'une seule pièce et/ou est séparé en deux parties par une fente de séparation (14) s'étendant de la partie haute pression (13) à la chambre basse pression (11).

Claims (21)

  1. Pompe ou moteur à engrenages comprenant une pièce intercalaire (8) qui est disposée dans un intervalle formé par un pignon (3) et d'une roue à denture intérieure (2), qui est appliquée, au moins partiellement, contre les sommets des dents du pignon et/ou de la roue à denture intérieure et qui est composée d'un corps d'étanchéité (7) approximativement en forme de croissant qui présente, au moins d'un côté, un tourillon saillant (6), sachant que le corps d'étanchéité (7) et le tourillon (6) sont réalisés d'un seul tenant au moins en tant que partie de la pièce intercalaire (8) et que la pièce intercalaire (8) présente au moins une fente de séparation (14) s'étendant approximativement dans la direction du pourtour à partir de la zone de haute pression (13) et formant chaque fois une aile intérieure (15) et une aile extérieure (16) pouvant être appliquées, au moins partiellement, contre les sommets des dents (9, 10) de la roue à denture intérieure (2) et du pignon (3), caractérisé(e) en ce que le(les) tourillon(s) (6) est (sont) disposé(s) au moins approximativement à l'extrémité du corps d'étanchéité (7) qui est tournée vers l'espace de basse pression (11), et en ce que la fente de séparation (14) s'étend au moins approximativement jusqu'à l'extrémité de la pièce intercalaire (8) qui est tournée vers l'espace de basse pression (11).
  2. Pompe ou moteur à engrenages selon la revendication 1, caractérisé(e) en ce que la fente de séparation (14) s'étend au moins jusque dans la zone de la pièce intercalaire (8) dans laquelle sont placés les tourillons (6).
  3. Pompe ou moteur à engrenages selon la revendication 1 ou 2, caractérisé(e) en ce que l'aile intérieure (15) et l'aile extérieure (16) sont reliées entre elles à l'extrémité de la pièce intercalaire (8) qui est tournée vers l'espace de basse pression (11).
  4. Pompe ou moteur à engrenages selon l'une des revendications 1 à 3, caractérisé(e) en ce que la fente de séparation (14) présente un espace vide (23), de préférence, à l'extrémité tournée vers l'espace de basse pression (11).
  5. Pompe ou moteur à engrenages selon la revendication 4, caractérisé(e) en ce que l'espace vide (23) est réalisé en s'élargissant progressivement vers l'espace de basse pression (11).
  6. Pompe ou moteur à engrenages selon la revendication 4, caractérisé(e) en ce que l'espace vide (23) présente des parois de séparation (22) s'étendant en direction du pourtour avec un écartement constant.
  7. Pompe ou moteur à engrenages selon la revendication 4, caractérisé(e) en ce que l'espace vide (23) est réalisé en se rétrécissant vers l'espace de basse pression (11).
  8. Pompe ou moteur à engrenages selon l'une des revendications 1 à 7, caractérisé(e) en ce que la fente de séparation (14) est placée au moins approximativement au centre du corps d'étanchéité (7), tout au moins dans la zone du (des) tourillon(s) (6).
  9. Pompe ou moteur à engrenages selon l'une des revendications 1 à 8, caractérisé(e) en ce que la largeur de la fente de séparation (14) s'étend sur toute la largeur de la pièce intercalaire (8).
  10. Pompe ou moteur à engrenages selon l'une des revendications 4 à 9, caractérisé(e) en ce que l'espace vide (23) dans la pièce intercalaire (8) s'étend au-delà du pourtour du (des) tourillon(s) (6) qui est tourné vers la zone de haute pression (13).
  11. Pompe ou moteur à engrenages selon la revendication 1, caractérisé(e) en ce qu'au moins le corps d'étanchéité (7) présente un espace vide (23) pouvant, de préférence, être sollicité par un fluide sous pression.
  12. Pompe ou moteur à engrenages selon la revendication 11, caractérisé(e) en ce que les parois de l'espace vide (23) sont disposées approximativement parallèlement aux côtés extérieurs du corps d'étanchéité (7) qui sont appliqués contre les dents (9, 10) de la roue à denture intérieure (2) et du pignon (3).
  13. Pompe ou moteur à engrenages selon la revendication 1, caractérisé(e) en ce que la pièce intercalaire (8) est réalisée en deux parties par une fente de séparation (14) s'étendant de l'extrémité tournée vers la zone de haute pression (13) à l'extrémité du corps d'étanchéité (7) qui est tournée vers l'espace de basse pression (11), et en ce qu'entre l'aile intérieure (15) et l'aile extérieure (16) est placé un arbre (29) traversant parallèlement la fente de séparation (14).
  14. Pompe ou moteur à engrenages selon la revendication 13, caractérisé(e) en ce que l'arbre (29) est logé dans des coquilles de coussinet (28) de l'aile intérieure (15) et de l'aile extérieure (16), de préférence de façon étanche.
  15. Pompe ou moteur à engrenages selon la revendication 13 ou 14, caractérisé(e) en ce que l'arbre (29) est disposé de façon concentrique par rapport à l'axe du (des) tourillon(s) (6).
  16. Pompe ou moteur à engrenages selon l'une des revendications 1 à 15, caractérisé(e) en ce que le corps d'étanchéité (7) présente, dans la zone du (des) tourillon(s) (6), sur au moins un côté extérieur, une partie en retrait (21).
  17. Pompe ou moteur à engrenages selon l'une des revendications 1 à 16, caractérisé(e) en ce qu'au moins l'un des côtés du corps d'étanchéité (7) qui sont appliqués contre les dents (9, 10) de la roue à denture intérieure (2) et/ou du pignon (3) part approximativement en affleurement vers le (les) tourillon(s) (6).
  18. Pompe ou moteur à engrenages selon l'une des revendications 1 à 17, caractérisé(e) en ce que le (les) tourillon(s) (6) sont placés sur l'élément d'étanchéité (7) sur la ligne d'influence des résultantes issues des forces hydrauliques qui agissent sur le corps d'étanchéité (7).
  19. Pompe ou moteur à engrenages selon l'une des revendications 1 à 18, caractérisé(e) en ce que l'extrémité du corps d'étanchéité (7) qui est tournée vers l'espace de basse pression (11) présente au moins approximativement la forme du (des) tourillon(s) (6).
  20. Pompe ou moteur à engrenages selon l'une des revendications 1 à 19, caractérisé(e) en ce qu'au moins l'une des ailes intérieure (15) et extérieure (16) est réalisée en étant appliquée avec une précontrainte contre les dents (9, 10) de la roue à denture intérieure (2) et du pignon (3).
  21. Pompe ou moteur à engrenages selon l'une des revendications 1 à 20, caractérisé(e) en ce que la pièce intercalaire (8) est montée de façon fixe ou mobile dans le carter de la pompe ou du moteur à engrenages.
EP91905137A 1990-02-19 1991-02-19 Pompe ou moteur a engrenages Expired - Lifetime EP0469135B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH522/90 1990-02-19
CH522/90A CH682836A5 (de) 1990-02-19 1990-02-19 Innenzahnrad-Maschine.
PCT/EP1991/000312 WO1991012430A1 (fr) 1990-02-19 1991-02-19 Pompe ou moteur a engrenages

Publications (2)

Publication Number Publication Date
EP0469135A1 EP0469135A1 (fr) 1992-02-05
EP0469135B1 true EP0469135B1 (fr) 1995-04-12

Family

ID=4188932

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91905137A Expired - Lifetime EP0469135B1 (fr) 1990-02-19 1991-02-19 Pompe ou moteur a engrenages

Country Status (5)

Country Link
US (1) US5188523A (fr)
EP (1) EP0469135B1 (fr)
CH (1) CH682836A5 (fr)
DE (1) DE59105149D1 (fr)
WO (1) WO1991012430A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6659728B2 (en) * 2001-11-09 2003-12-09 Viking Pump, Inc. Liquid dispensing pump system
DE102005044576A1 (de) * 2005-09-17 2007-03-22 Voith Turbo Gmbh & Co. Kg Innenzahnradmaschine
DE102012208851A1 (de) * 2012-05-25 2013-11-28 Robert Bosch Gmbh Innenzahnradpumpe
BE1027453B1 (fr) * 2019-07-22 2021-02-22 Safran Aero Boosters Sa Pompe a engrenage

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1905146A1 (de) * 1969-02-03 1970-10-29 Westinghouse Bremsen U Appbau Verschleissausgleichende Hochdruck-Zahnradpumpe

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE551485C (de) * 1932-06-01 Ludwig Geb Zahnradspinnpumpe mit zwei ineinanderliegenden Zahnraedern
DE1280056B (de) * 1963-07-11 1968-10-10 Bosch Gmbh Robert Drehkolbenmaschine mit zwei Zahnraedern im Inneneingriff
DE2313085C2 (de) * 1973-03-16 1984-05-24 Otto 7502 Malsch Eckerle Axial und radial kompensierte Hochdruck-Zahnradpumpe
SU603770A1 (ru) * 1975-08-27 1978-04-25 Кировоградский Ордена "Знак Почета" Завод Тракторных Гидроагрегатов Шестеренный насос внутреннего зацеплени
DE2641278A1 (de) * 1976-09-14 1978-03-16 Voith Getriebe Kg Innenzahnradpumpe
DE2942417A1 (de) * 1979-10-19 1981-05-14 Otto Eckerle GmbH & Co KG, 7502 Malsch Innenzahnradmaschine
DE3544857C2 (de) * 1985-12-18 1994-09-29 Eckerle Rexroth Gmbh Co Kg Innenzahnradmaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1905146A1 (de) * 1969-02-03 1970-10-29 Westinghouse Bremsen U Appbau Verschleissausgleichende Hochdruck-Zahnradpumpe

Also Published As

Publication number Publication date
CH682836A5 (de) 1993-11-30
US5188523A (en) 1993-02-23
DE59105149D1 (de) 1995-05-18
EP0469135A1 (fr) 1992-02-05
WO1991012430A1 (fr) 1991-08-22

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