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EP0848165B1 - Pompe à engrenages internes - Google Patents

Pompe à engrenages internes Download PDF

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Publication number
EP0848165B1
EP0848165B1 EP97121424A EP97121424A EP0848165B1 EP 0848165 B1 EP0848165 B1 EP 0848165B1 EP 97121424 A EP97121424 A EP 97121424A EP 97121424 A EP97121424 A EP 97121424A EP 0848165 B1 EP0848165 B1 EP 0848165B1
Authority
EP
European Patent Office
Prior art keywords
bearing ring
internal gear
pump according
gear pump
axial
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
EP97121424A
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German (de)
English (en)
Other versions
EP0848165A2 (fr
EP0848165A3 (fr
Inventor
Otto Eckerle
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Individual
Original Assignee
Individual
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Filing date
Publication date
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Publication of EP0848165A2 publication Critical patent/EP0848165A2/fr
Publication of EP0848165A3 publication Critical patent/EP0848165A3/fr
Application granted granted Critical
Publication of EP0848165B1 publication Critical patent/EP0848165B1/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
    • F04C2/102—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
    • F04C15/0003—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention relates to a filler-less Internal gear machine with the features according to the Preamble of claim 1.
  • the object of the invention is therefore a To create internal gear machine of this type, which at perfect function is more simple.
  • the cheapest Position for the swivel axis is thus on the side of the Pressure space between the line of the resultant R the hydraulic forces and the non-invasive Ring section of the bearing ring assigned to the ring gear region, with particular preference the pivot axis of the line of Resulting R closer than that of the non-invasive Ring section associated ring gear region.
  • the pivot bearing of the bearing ring is different Realizable, for example, by the bearing ring self-provided bearing journals, which in corresponding Engage recesses in the housing. More advantageous and However, a pivot bearing of the bearing ring is easier by a bearing pin fixed in the housing, which with a Part of its peripheral surface as a bearing surface in an axial groove is on the outer circumference of the bearing ring. Because the bearing ring through the forces prevailing in the pressure chamber at the above as expediently described embodiment with the axial groove is pressed against the bearing pin is the Partially cylindrical axial groove in its dimensions on the Bearing pin matched so that it is as uniform as possible Surface pressure occurs. The bearing pin prevents at the same time a rotation of the bearing ring in the housing bore.
  • the internal gear machine described can be in one simple embodiment be designed so that pinion, Ring gear and bearing ring with their respective end faces seal directly against the housing walls.
  • axial washers are provided by pressure fields in sealing contact with the end faces of at least pinion and ring gear are held.
  • the pressure fields can be in the Housing walls and / or in the teeth end faces of the axial disks formed his.
  • a further increase in the efficiency of the Internal gear machine according to the invention in which Axial disks are provided, can then be achieved if ensured by an appropriate construction is that the thrust washers together with the bearing ring and the ring gear the desired compensation movement for the Maintaining the sealing contact between the tooth heads can execute. Because this ensures that the Control of the hydraulic pressure conditions in the pressure or. Suction chamber, which in a known manner by control or Pre-filling slots in the axial washers are made independently optimally from the movements of the ring gear and the bearing ring remains.
  • the internal gear machine shown in FIGS. 1 and 2 comprises a housing designated as a whole by 1, which consists of a cup-shaped housing part 11 and one on the latter Front end of the housing cover 12 is constructed.
  • a pinion shaft 14 rotatably mounted on which a pinion 2 rotatably attached is.
  • the pinion 2 meshes with a ring gear 3, which in one Bearing ring 4 is added and rotatably mounted therein.
  • the Pinion 2 and the ring gear 3 are, as is apparent from Fig. 1, stored relative to each other with an eccentricity e.
  • the Eccentricity e d. H.
  • the distance between the pinion axis and the ring gear axis corresponds to the theoretical Gear geometry of pinion and ring gear and sets play-free rolling or sliding of the gears ahead of each other.
  • the teeth of the pinion 2 and Ring gear 3 mesh with each other in such a way that on the left in Fig. 1 in the region of the dividing line A Teeth of the pinion 2 fully into the tooth spaces of the ring gear 3 engage and rest on the tooth flanks while they are on the opposite, right in Fig. 1 from the tooth gaps of the ring gear 3 have emerged.
  • this non-meshing ring gear region E support several of the Tooth tips of the pinion 2 and the ring gear 3 (in the shown embodiment 3 tooth heads each) one after the other in the course of the rotation.
  • the Number of teeth and the geometry of the meshing Gears are chosen so that this type of combing can be effected.
  • the tooth flanks are formed as involute curves, whereby the tooth heads to achieve rolling and sliding contact are rounded for the purpose of sealing.
  • the number of teeth on the Ring gear 3 differs from that of pinion 2 at 1.
  • the bearing ring 4 is in a housing bore 15 of the pot-shaped housing part 11 with a radial clearance of about 0.2 mm added.
  • the wall of the housing bore 15 is partially penetrated by a bearing pin 16 which in the Bottom of the housing bore 15 is pressed firmly. With the protruding beyond the wall of the housing bore 15 is largely semi-cylindrical part of the bearing pin 16 this in an axially directed groove 17 of the bearing ring 4 added.
  • the axial groove 17 is the shape of the bearing pin 16 adapted and also partially cylindrical.
  • the bearing pin 16 engaging in the axial groove 17 forms for the bearing ring 4 one to the axes of pinion 2 and Ring gear 3 parallel pivot axis about which the Bearing ring 4 within the available Radial play in the housing bore 15 is pivotable. How 1, this pivot axis lies in one Quadrant of the bearing ring 4, which is between the non-meshing ring gear area E and the center of the Pressure chamber D extends.
  • the swivel axis is in one embodiment Angular distance of about 80 ° from the apex of the non-meshing ring gear area E. At this apex are two teeth of pinion and ring gear with their Tooth heads largely aligned with each other.
  • the mode of operation of the internal gear machine according to FIG. 1 and 2 is the following:
  • the bearing ring 4 has at a point that the Apex of the non-meshing ring gear region E is assigned a further axial groove 18 with a Rectangular cross section on its outer circumference.
  • This Axial groove 18 is in the bottom of the housing bore 15
  • Receiving hole 19 associated with a hairpin spring 20 is held.
  • the hairpin spring 20 protrudes into the axial groove 18 and loads the bearing ring 4 radially so that the teeth of the ring gear 3 in the non-meshing ring gear region E. their tooth heads are pressed against each other.
  • This Load direction largely corresponds to that Direction of movement that the bearing ring 4 as a result of Performs pivoting movement about the pivot axis 16, 17.
  • the force of the hairpin spring 20 can be kept relatively low as it only serves the necessary Sealing contact between the tooth heads in the non-invasive Ring gear area E during the startup process To ensure internal gear machine, d. H. at a time, in which no operating pressure has yet been built up in pressure chamber D. and therefore no compressive forces act.
  • the position and direction of the resultant R is largely predeterminable and corresponds essentially to that in Fig. 1 shown.
  • the pressure build-up in the pressure chamber D leaves in a known manner through pre-filling slots on the teeth of pinion 2 and / or ring gear 3, so that z. B. a largely over the tooth gaps of the pressure chamber D. same pressure exists.
  • the Resulting R drawn perpendicular to that in Fig. 1 line shown which is the vertex of the non-meshing ring gear region E with the pinion tooth fully engages in a tooth gap of the ring gear.
  • Embodiment according to FIGS. 1, 2 show FIGS. 3 to 18 embodiments of the invention Internal gear machine on the front of the gearing have sealing axial discs.
  • the housing bore corresponds to that of the Embodiment according to FIGS. 1, 2 and needs therefore no separate explanation.
  • the bearing ring 104 has on its inner circumference one pressed in and consequently one with the bearing ring Unit-forming race 105 made of a bearing metal, e.g. B. Bronze, in which the ring gear 103 is mounted.
  • a bearing metal e.g. B. Bronze
  • the bearing ring 104, 105 exceeds the Width of pinion 102 and ring gear 103 significantly and is with its end faces slidable on the walls of the Housing 111 or cover 112.
  • the Teeth of pinion and ring gear on both sides of the front Sides each an axial washer 130, the shape of which Fig.
  • Each of the two axial washers has a pressure field 107 on its surface facing the toothing on.
  • the axial disk 130 arranged on the side of the housing cover 112 is, three openings 108, which from the pressure chamber to the Pressure outlet channel, not shown, in the housing cover 112 to lead.
  • the housing cover 112 faces diametrically opposite Pressure outlet channel on a suction inlet channel 109, which is expanded at its mouth to a suction field 110.
  • each a pressure field 131 indicated by which the respective Axial disk 130 from the outside against the action of inner pressure field 107 is applied so that the Axial disc with all operating conditions sealing contact with Retains pinion 102 and ring gear 103. Training and Effect of the pressure fields on axial washers well-known and therefore need at this point no further explanation.
  • the Axial disks 130 prefill slots 132 through which the Pressure distribution in the pressure chamber of the gearing is controlled.
  • Each thrust washer 130 supports itself for the purpose of it Secure position on the one hand over the circumference of a bearing bore 133 on the associated bearing bush 113 and on the other on one in the housing 111 or the housing cover 112 inserted pin 134 from.
  • the pins 134 each protrude into a blind hole in the outer face of the Axial disks 130 and are thereby held axially.
  • FIGS. 6 and 7 differs from that according to FIGS. 3 to 5 only in that the axial washers 230 align with the inner circumference of their Bearing bore 233 not on the respectively assigned Support bushing 213, but directly on the Pinion shaft 214.
  • the bearing bushes 213 thus end in front of the Axial washers 230.
  • each thrust washer 330 provided two pins 334, 335 which in each case in the end regions of the axial disks 330 Blind hole on the one hand and in a corresponding hole of the housing on the other hand.
  • the bearing bushes 313 extend in this embodiment among the Axial disks 330 close to the toothing.
  • the axial disks are relative to the housing fixed. It follows that in operation the internal gear machine with the operational movement of pinion, ring gear and bearing ring relative to the housing due to the permitted pivoting movement of the bearing ring the pressure space in the toothing relative to that in the Axial disks provided control slots and pressure fields also changed its location. Because this inevitably Deviations from the optimal position set occur, the efficiency can be reduced. Around to prevent this; are in accordance with the embodiments 10 to 18, the thrust washers in a manner arranged that they together with pinion, ring gear and Bearing ring are movable together. Are in all Cases the thrust washers as part of the game, e.g. B. of Bearing play, sufficiently free with respect to the pinion shaft, that they can follow the pivoting movement of the bearing ring, in order not to achieve the desired sealing contact of the tooth heads hinder.
  • the Bearing ring 404 on the right (in FIG. 11) on both End faces a radial groove 440 on the groove bottom with the End faces, the toothing lies in one plane.
  • the Axial disks 430 have one on their outer edge Extension 441, which projects into the groove 440 with play and is performed in it.
  • the thrust washers 430 support themselves with a certain amount Bearing play on the circumference of the pinion shaft 413.
  • the respective pressure field 407 are the External pressure fields 431 assigned to axial disks 430 exclusively on the respective outer surface of the Axial disks 430 formed. With the operational Pivotal movements of the bearing ring 404 around the bearing pin 416 therefore remains the location of the pressure fields 407, 431 and the Control slots 432 largely relative to the pressure chamber unchanged.
  • the raceway pressed into the bearing ring 404 405 is limited to the width of the ring gear.
  • the embodiment according to FIGS. 13 to 15 differs from the embodiment described above 10 to 12 by the shape of the axial discs 530 and their type of position assurance.
  • the thrust washers 530 are in in this case with a circular border and between the pinion, Ring gear on the one hand and the associated housing wall on the other hand, fully absorbed in the space created by the Larger width of the bearing ring compared to the ring gear and pinion 504 is created. Again, the width of the in the Bearing ring 504 pressed race 505 to the width of the Ring gear limited.
  • the outer circumference of the axial washers 530 lies on the exposed inner circumference of the bearing ring 504 close and has a small extension 541 with which the axial disc 530 in the on each end face of the Bearing rings 504 engages provided radial groove 540. Since the Thrust washers 530 over their outer circumference in the bearing ring 504 are held, encompasses the circumference of their bearing bore 533 with the pinion shaft 513 in this embodiment clear game.
  • thrust washers 530 in this embodiment are pinions and completely cover the ring gear on the face is in the range of Suction space of the teeth a part-circular breakthrough 536 provided that the inflow of the medium from the Suction channel 509 allowed for toothing.
  • the axial washers 630 are circular, but have such a shape large outer diameter that they are beyond the ring gear overlap the bearing ring 604 on its end faces. For this is the width of the bearing ring 604 along with that in it Pressed race 605 to the width of the ring gear and Pinion limited.
  • the bearing ring 604 has an axially continuous Hole in which a pin 642 is received. This protrudes on both ends of the end faces of the bearing ring 604 out and into elongated holes 643 of the axial washers 630.
  • The are supported with the inner circumference of their bearing bore 633 Axial washers 630 in this case with a tight bearing clearance pinion shaft 613. Through this and through the pin 642 they are uniform in motion with the bearing ring 604 coupled. As described in the above Embodiments according to FIGS. 10 to 15 therefore remain the relative position of the control slots 632 and the pressure fields 607 or 631 received for the teeth.
  • the Axial washers 630 made a breakthrough in the area of the suction chamber 636 to ensure access to the pumped medium.
  • the invention is not based on the training of Internal gear machine according to those described above Embodiments limited. So it is basically possible instead of the one selected for pinion and ring gear Involute toothing with rounded tooth heads one Trochoid or cycloid toothing to choose.
  • Farther can also be a mirror image of the on the bearing ring Dividing line A one of the axial groove for the swivel axis appropriate axial groove may be provided in the event that the internal gear machine for both directions of rotation of the Pinion 2 should be designed. In this case the would Bearing pin determining the pivot axis is offset accordingly be arranged in the housing.
  • the grooves must be in the end faces of the bearing ring (Fig.
  • Axial disks are shown and described basically only one axial disk can be provided, where necessary control slots and Pressure fields are provided directly in the housing wall, rest on the front of the pinion and ring gear.
  • a pen Swivel axis of the bearing ring also through a ball be realized in a dome-shaped recess the housing bore is received. This is the Bearing ring not only around a parallel to the pinion axis Swivel axis, but swiveling on all sides to Adaptation movements to shape deviations of the individual To be able to execute components.

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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)
  • Gears, Cams (AREA)

Claims (19)

  1. Machine à engrenages intemes sans pièce de remplissage, du type comprenant un carter (1), une bague d'appui (4) reçue non mobile en rotation dans un alésage (15) du carter et qui peut basculer autour d'un axe de basculement parallèle à son axe, une roue creuse à denture intérieure (3) et un pignon (2) monté rotatif dans le carter, engrenant avec la roue creuse et dont les dents, par engrènement complet avec les vides situés entre les dents de la roue creuse, d'une part, et par contact étanche avec les têtes de dents de la roue creuse, dans une zone (E) de la roue creuse sans engrènement avec les vides entre les dents, située à peu près diamétralement opposée à la zone d'engrènement, d'autre part, définissent un espace d'aspiration (S) et un espace de compression (D) de la denture, caractérisée en ce que, en vue du maintien d'une pression pratiquement égale dans la totalité de l'espace de compression (D), un contact étanche entre les dents du pignon et les dents de la roue creuse est restreint à la zone comprise entre la zone d'engrènement complet et le domaine sans engrènement (E) de la roue creuse, et au moins une fente de commande (132, 432, 632) est prévue dans l'espace de compression situé dans une paroi du carter (11, 12) situé du côté frontal faisant face aux dents du pignon et/ou de la roue creuse, ou à un disque axial (130, 230, 330, 430, 530, 630) du carter (11, 12), et en ce que l'axe de basculement (16, 17 ; 416) de la bague d'appui est situé par rapport à la résultante (R) de la pression hydraulique régnant dans l'espace de compression (B) de manière telle qu'est provoqué un basculement de la bague d'appui dans le sens d'un rapprochement réciproque des têtes de dents du pignon et de la roue creuse dans la zone sans engrènement de la roue creuse (E).
  2. Machine à engrenages intemes selon la revendication 1, caractérisée en ce que l'axe de basculement (16, 17) de la bague d'appui est situé du côté de l'espace de compression (D) entre la ligne de la résultante (R) des forces de compression et la section de l'anneau située dans la zone sans engrènement (E) de la roue creuse.
  3. Machine à engrenages internes selon la revendication 2, caractérisée en ce que l'axe de basculement est situé plus près de la ligne de la résultante (R) que la section située dans la zone sans engrènement (E) de la roue creuse.
  4. Machine à engrenages internes selon l'une des revendications 1 à 3, caractérisée en ce que l'axe de basculement est situé sur le périmètre externe de la bague d'appui.
  5. Machine à engrenages internes selon la revendication 1, caractérisée en ce que l'axe de basculement est constitué par une cheville d'appui (16) solidaire du carter et qui est partiellement reprise sur sa périphérie dans une rainure axiale (17) de la surface périphérique externe de la bague d'appui.
  6. Machine à engrenages internes selon l'une quelconque des revendications 1 à 5, caractérisée en ce que la section de la bague située dans la zone sans engrènement (E) de la roue creuse est soumise à un ressort exerçant une action radiale par rapport à l'axe du pignon.
  7. Machine à engrenages internes selon la revendication 6, caractérisée en ce que la section de la bague située dans la zone sans engrènement (E) de la roue creuse présente sur sa périphérie externe un évidement (18) dans lequel s'accroche le ressort (20) s'appuyant dans le carter (1).
  8. Machine à engrenages internes selon l'une des revendications 1 à 7, caractérisée en ce que l'espace de compression (2) est rendu étanche par un disque axial (130 à 630) situé sur la face frontale de la denture du pignon et de la roue creuse.
  9. Machine à engrenages internes selon la revendication 8, caractérisée en ce que chaque disque axial (130, 230) s'appuie au moins par une saillie (cheville 134) sur le carter et par un alésage d'appui (133, 233) sur l'axe du pignon (113, 114 ; 214).
  10. Machine à engrenages internes selon la revendication 8, caractérisée en ce que chaque disque axial (330) s'appuie par deux saillies (chevilles 334, 335) sur le carter.
  11. Machine à engrenages internes selon la revendication 8, caractérisée en ce que les disques axiaux (430, 530, 630) en même temps que la bague d'appui (404, 504, 604) ainsi que la roue creuse sont montés basculables par rapport au carter.
  12. Machine à engrenages internes selon la revendication 11, caractérisée en ce que la bague d'appui est réunie par verrouillage de formes avec les disques axiaux.
  13. Machine à engrenages internes selon la revendication 12, caractérisée en ce que la bague d'appui (404, 504) présente au moins un évidement (440, 540) dans lequel s'accroche une saillie (441, 541) de chaque disque axial (430, 530).
  14. Machine à engrenages internes selon la revendication 13, caractérisée en ce que chaque saillie des disques axiaux est disposée dans un évidement particulier de la bague d'appui.
  15. Machine à engrenages internes selon l'une des revendications 13 ou 14, caractérisée en ce que la saillie est guidée dans l'évidement de la bague d'appui avec un certain jeu et en ce que le disque axial appuie sur l'axe du pignon par l'intermédiaire d'un alésage d'appui (433, 533).
  16. Machine à engrenages internes selon l'une des revendications 11 ou 12, caractérisée en ce que chaque disque axial (530) est circulaire et reçu sur sa périphérie externe dans la bague d'appui (504).
  17. Machine à engrenages internes selon la revendication 11, caractérisée en ce que chaque disque axial (630) est de forme circulaire et s'appuie sur la surface frontale correspondante de la bague d'appui (604) ainsi que par un alésage d'appui (633) sur l'arbre du pignon.
  18. Machine à engrenages internes selon la revendication 17, caractérisée en ce que le disque axial est réuni par verrouillage de formes à la bague d'appui.
  19. Machine à engrenages internes selon la revendication 18, caractérisée en ce que la liaison par verrouillage de formes comporte une cheville d'accrochage (642) située dans un alésage de la bague d'appui et dans un trou longitudinal (643) du disque axial.
EP97121424A 1996-12-12 1997-12-05 Pompe à engrenages internes Expired - Lifetime EP0848165B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19651683 1996-12-12
DE19651683A DE19651683A1 (de) 1996-12-12 1996-12-12 Füllstücklose Innenzahnradpumpe

Publications (3)

Publication Number Publication Date
EP0848165A2 EP0848165A2 (fr) 1998-06-17
EP0848165A3 EP0848165A3 (fr) 1999-08-18
EP0848165B1 true EP0848165B1 (fr) 2001-09-26

Family

ID=7814476

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97121424A Expired - Lifetime EP0848165B1 (fr) 1996-12-12 1997-12-05 Pompe à engrenages internes

Country Status (6)

Country Link
US (1) US6074189A (fr)
EP (1) EP0848165B1 (fr)
JP (1) JP3323432B2 (fr)
KR (1) KR100325593B1 (fr)
AT (1) ATE206183T1 (fr)
DE (3) DE19651683A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018222173A1 (de) 2018-12-18 2020-06-18 Eckerle Technologies GmbH Füllstücklose Innenzahnradfluidmaschine
DE102020111435A1 (de) 2020-04-27 2021-10-28 Eckerle Technologies GmbH Füllstücklose Innenzahnradfluidmaschine

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DE19804133A1 (de) * 1998-02-03 1999-08-12 Voith Turbo Kg Sichellose Innenzahnradpumpe
DE19815421A1 (de) 1998-04-07 1999-10-14 Eckerle Ind Elektronik Gmbh Innenzahnradmaschine
US6152717A (en) * 1998-06-11 2000-11-28 Unisia Jecs Corporation Internal gear pumps
DE10004518A1 (de) * 2000-02-02 2001-08-09 Continental Teves Ag & Co Ohg Bremsanlage
DE10013760A1 (de) * 2000-03-20 2001-10-04 Continental Teves Ag & Co Ohg Innenzahnradmaschine mit einem Wälzlager gelagerten Hohlrad
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DE10035900A1 (de) * 2000-07-21 2002-01-31 Bosch Gmbh Robert Innenzahnradpumpe
DE10052779A1 (de) 2000-10-25 2002-05-08 Eckerle Ind Elektronik Gmbh Füllstücklose Innenzahnradpumpe
DE10109769A1 (de) 2001-03-01 2002-09-05 Eckerle Ind Elektronik Gmbh Füllstücklose Innenzahnradpumpe
DE10109770A1 (de) 2001-03-01 2002-09-05 Eckerle Ind Elektronik Gmbh Füllstücklose Innenzahnradpumpe
DE10114148C1 (de) * 2001-03-22 2002-06-06 Dieter Brox Selbstzentrierende Zahnradpumpe
DE10150653A1 (de) 2001-10-13 2003-04-30 Bosch Gmbh Robert Innenzahnradpumpe
US7278841B2 (en) * 2001-12-13 2007-10-09 Performance Pumps, Llc Gerotor pump
US20050063851A1 (en) * 2001-12-13 2005-03-24 Phillips Edward H Gerotor pumps and methods of manufacture therefor
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DE59704716D1 (de) 2001-10-31
DE29703656U1 (de) 1997-05-15
KR100325593B1 (ko) 2002-07-08
JP3323432B2 (ja) 2002-09-09
DE19651683A1 (de) 1998-06-18
JPH10281079A (ja) 1998-10-20
EP0848165A2 (fr) 1998-06-17
US6074189A (en) 2000-06-13
ATE206183T1 (de) 2001-10-15
EP0848165A3 (fr) 1999-08-18
KR19980064065A (ko) 1998-10-07

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