EP0707686B1 - Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures - Google Patents

Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures Download PDF

Info

Publication number
EP0707686B1
EP0707686B1 EP94924212A EP94924212A EP0707686B1 EP 0707686 B1 EP0707686 B1 EP 0707686B1 EP 94924212 A EP94924212 A EP 94924212A EP 94924212 A EP94924212 A EP 94924212A EP 0707686 B1 EP0707686 B1 EP 0707686B1
Authority
EP
European Patent Office
Prior art keywords
pressure
internal gear
pressure field
gears
machine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP94924212A
Other languages
German (de)
English (en)
Other versions
EP0707686A1 (fr
Inventor
Klaus BUCHMÜLLER
Reinhard Pippes
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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 Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0707686A1 publication Critical patent/EP0707686A1/fr
Application granted granted Critical
Publication of EP0707686B1 publication Critical patent/EP0707686B1/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
    • 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 is based on a hydraulic internal gear machine, which can be used as a pump or motor and which Features from the preamble of claim 1.
  • That which can be acted upon with the high pressure on the high pressure side of the machine Pressure field is in a perpendicular to the axes of the two gears running plane bounded by a seal, which the gap between the sealing plate and the housing part seals.
  • the pressure field is in the sealing plate or in the housing part.
  • a hydraulic internal gear machine that only works in one direction is operable and the features according to the preamble of claim 1, is shown in DE 18 01 825 A1.
  • an internal gear machine Has lid parts that are largely symmetrical with respect to the axes of the two gearwheels spanned the central plane, and by installing the asymmetrical middle section in one first position or in a position perpendicular to the first position to the axes of the gears in the central plane Axis rotated 180 degrees, second position to the desired one Direction of rotation is designed.
  • DE-A-2744730 already includes an internal gear machine a so-called main axial pressure field and one known as another axial pressure field. However these two pressure fields connected to each other via a groove. It is therefore only a single pressure field and not two pressure fields separated from one another in the sense of the invention, only one of which is used at a time. Also located in DE-A-2744730 the only pressure field in each case in a bearing body and not as in the internal gear machine according to the invention in a cover part.
  • the filler pin according to claim 10 is in the central plane stored in a lid.
  • the internal gear pump shown in Figures 1 and 2 has a housing 10, which consists of an annular central part 11, which radially encloses a pump chamber 12, a first Cover part 13 and a second cover part 14 is composed.
  • the two cover parts 13 and 14 limit the pump chamber 12 in axial direction.
  • the middle part 11 overlaps the two Cover parts 13 and 14 in the area of an external recess 15.
  • the cover part 13 has a through bore 16, in a plain bearing 17 is pressed. Aligned with the bore 16 a blind hole 18 of the cover part 14, in which also Plain bearing 17 is pressed.
  • a drive shaft 19 of the pump is mounted.
  • An external gear Pinion 20 is within the pump chamber 12 on the drive shaft 19 attached or made in one piece with this.
  • the Pinion is located within an internally toothed ring gear 21, the axis of which is arranged eccentrically to the axis of the pinion 20 is and on its outer circumference in the middle part 11 of the housing 10 is stored.
  • a crescent-shaped free space 23 In the area one on both sides by the two Axes of the pinion 20 and the ring gear 21 spanned center plane 22 intermesh the two gears, between them there is also a crescent-shaped free space 23.
  • This free space 23 is about half by a two-part Filler 24 filled out on the teeth of the pinion 20 and of the ring gear 21 abuts and on a flattening of a filler pin 25 supports. This crosses the free space 23 in the central plane 22 and is in two aligned blind holes the cover parts 13 and 14 on both sides of the pump chamber 12 rotatably mounted. The axial extent of the filler 24 agrees with the axial expansion of the two gear wheels 20 and 21 match.
  • the pump chamber opens 12 a suction channel 26 and a pressure channel 27, the diameter of the suction channel 26 larger than the diameter of the pressure channel 27 is.
  • the ring gear 21 has in the tooth gaps radially from through holes 28 through the inside through one hydraulic fluid from the suction channel 26 into the free space 23 and can get into the pressure channel 27 from there.
  • the pump according to Figures 1 and 2 is constructed so that the Pinion 20 in operation, as seen in Figure 2, clockwise must be driven.
  • the ring gear 21 then also rotates Clockwise. Hydraulic fluid in the tooth gaps travels along the filler 24 with the tooth gaps and arrives in the meshing area of the two gears.
  • a good axial seal is essential for high pump efficiency the high pressure side of the pump, which is characterized by can delimit an area of the pump chamber 12 in which the filler 24 is located in the following the filler the two gears gradually interlock.
  • a sealing plate 35 is arranged, that of one between her and the corresponding one Cover part 13 or 14 existing pressure field 36 axially against the Gears 20 and 21 is pressed.
  • Each sealing plate 35 surrounds closely the shaft 19 and the filler pin 25 and is thereby in a plane perpendicular to the axis of the drive shaft 19 in its Location secured.
  • a pressure field 36 is defined by a recess in the Cover part 13 and 14 formed.
  • a second section 39 is also an arc of a circle, however, its center is on the axis of the ring gear 21 lies.
  • This circular arc 39 is tangential to the central plane 22 into a straight line 40 to be regarded as the third section about.
  • a section 41 connects in the area of the central plane 22 section 38 to section 40.
  • a section 42 connects the arcs 38 and 39 at their widely spaced Ends, with section 42 also partially straight is.
  • FIG 4 is in addition to the central plane 22 and a section Recess 36 with a dashed line the outer contour of a pressure field of a known internal gear pump. It can be seen that this pressure field extends over the central plane 22, while a pressure field of an internal gear pump according to the invention limited to one side of the middle plane and in Tooth engagement area maintains a distance from this.
  • the known pressure field is the circular arc 39 up to the central plane 22 continued.
  • the two cover parts 13 and 14 of the internal gear pumps shown are not only with regard to the median plane 22 on the recesses 36, but overall symmetrical. You can therefore use both for a left-handed drive as well as a clockwise driven pump used become. Overall, the two versions of a pump can the same parts. It just becomes the middle part 11 together with the two sealing plates 35 and the filler 24 around a through the two axes of the gears 20 and 21 and axis lying in the central plane 22 rotated by 180 degrees assembled with the cover parts 13 and 14.
  • the embodiment according to FIGS. 1 to 7 runs to accommodate the sealing arrangement on the edge of each recess 36 along a groove 43 which is the same over its entire circumference Has depth and breadth.
  • An elastomer seal is in the groove 43 44 inserted, which, as can be seen in Figure 5, a Z-profile Cross section with two terminal profile sections 45 and 46 and a central profile section 47.
  • the both terminal profile sections 45 and 46 are vertical on the sealing plate 35, which is on the outer wall of the groove 43 located profile section 46 axially at the bottom of the groove 43 and the inner profile section 45 axially on the Supporting sealing plate 35.
  • the terminal profile section 46 and the central profile section 47 of the elastomer seal 44 are located completely in the groove 43.
  • the Elastomeric seal 44 individual spaced and in an axial view of semicircular knobs 48 taken from the inner circumference of the central profile section 47 and the elastomer seal Support 44 on the inner wall of groove 43.
  • the pimples 48 have the same distance from the bottom of the groove 43 as the middle Profile section 47 radially within the profile section 46.
  • Die Nubs 48 are therefore not directly connected to the profile section 46, so that radially within this an uninterrupted circumferential pressure surface 49 present on the elastomer seal 44 is. From the high pressure side of the pump through holes in a sealing plate 35 flowing into a recess 36 Hydraulic fluid can thus pass between the knobs 48 get to the back of the elastomer seal 44 and this in Apply pressure to the area of the pressure surface 49 so that the Elastomer seal 44 depending on the level of pressure on the high pressure side the pump rotating with a different force is pressed against the sealing plate 35. On the other hand the elastomer seal is supported radially inside and outside in the Groove 43 so that it maintains its position safely.
  • a support ring 51 made of plastic which has a rectangular cross section and which is in a region radially outside the first terminal Profile section 45 and axially between the middle Profile section 47 of the elastomer seal 44 and the sealing plate 35 is arranged.
  • the support ring 51 is a so-called open support ring with two ends 52, which is in the straight region of section 42 of the outer contour a recess 36 relatively far in one to the sealing plate 35 parallel plane overlap.
  • Overlapping the parallel plane means that when you advance traverses both ends 52 in such a plane.
  • the support ring is of course on the outer contour adapted a recess 36 so that the two overlap Ends 52 also in the area of a straight section of the Support ring 51 are. Tolerances in the outer circumference of a pressure field and tolerances of the support ring itself can this because balance its open design so that it is radial can create gaps on the wall of a cover part 13 or 14.
  • the embodiment according to FIGS. 8 to 10 basically has the same construction as the embodiment according to FIGS. 1 to 7. Therefore, in the section according to FIG. 8, the section according to FIG 1 corresponds to a small part of the pump. From Figure 9 it can be seen that also in this embodiment in the cover parts 13 and 14, of which in Figure 9 Cover part 14 is shown, two recesses 36 are present are symmetrical to each other with respect to the central plane 22 lie. However, the two recesses 36 in the area of Gear engagement of the two gears 20 and 21 a greater distance from the central plane 22 as the two recesses 36 of the Execution according to FIGS. 1 to 7. As a result, the web 37 wider.
  • each cover part now has 13 or 14 in Area of the web 37 and at a distance from the recesses 36 a circular recess 60 that is symmetrical on both sides the central plane 22.
  • This recess is over one in the sealing plate adjacent to the respective cover part 35 located axial bore 61 which opens into the recess 60 and from a recess 62 on the gearwheels Side surface of the sealing plate 35 goes out with the high pressure side connected to the pump, regardless of the High pressure side connected, whether the pump turns left or right is driven.
  • the cover part 14 Assigned sealing plate 35 which is now the cover part, not shown 13 is adjacent, while the sealing plate shown in Figure 9 35 is assigned to the cover part 13.
  • the two sealing plates are symmetrical to each other with respect to the central plane 22 trained, provided you put them side by side towards the same facing away from the gears or facing the gears Side viewed.
  • a sealing plate 35 covers in essentially only the high pressure side of a pump, while the Low pressure side is kept free, so that there is no friction can take place between the gears and a sealing plate, which would lower the efficiency of the pump.
  • Effective in one concrete left-handed or right-handed execution of a Pump are the pressure field 60 and that in an axial View of the gears from hidden by the sealing plate 35 Pressure field 36. Only these two pressure fields are also with one Elastomer seal 63 to the axial gap between the sealing plate 35 and the respective cover part sealed.
  • the elastomer seal is a simple rectangular seal, the axial dimension of which is smaller than that Depth of a recess 36 or 60 and thus on their Back of the pressure prevailing in the pressure field and can be pressed against the sealing plate 35.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (10)

  1. Une machine hydraulique à pignons internes (pompe ou moteur), qui ne peut être actionnée que dans un sens de rotation, qui comprend un corps (10), possédant un raccord de haute pression et un raccord de basse pression et comportant d'une part un élément (11) médian, lequel contient le raccord de haute pression, lequel referme une chambre (12) à l'aide d'une roue (21) creuse et d'un pignon (20) s'enclenchant dans cette dernière dans une direction perpendiculaire aux axes des deux roues (20, 21) dentées, et lequel est conçu de façon asymétrique par rapport à un plan (22) médian passant par les axes des deux roues (20, 21) dentées, et comportant d'autre part deux éléments (13, 14) couvercle disposés de part et d'autre de l'élément (11) médian, qui présente une plaque (35) d'étanchéité, disposée entre les deux roues (20, 21) dentées et un élément (13, 14) couvercle dans la direction axiale, et qui dans la zone de haute pression présente un champ (36) de pression, lequel est disposé dans un des éléments (13, 14) couvercle, lequel est ouvert dans le sens de la plaque (35) d'étanchéité et lequel peut être soumis à une haute pression, caractérisée en ce que l'élément (11) médian contient également le raccord de basse pression, que dans l'un des éléments (13, 14) couvercle est disposé un deuxième champ (36) de pression, raccordé au côté basse pression, que le premier champ (36) de pression est disposé exclusivement d'un côté et le deuxième champ (36) de pression exclusivement de l'autre côté d'un plan (22) médian passant par les axes de rotation des deux roues (20, 21) dentées, de façon à ce que des entretoises (37) de l'élément (13, 14) couvercle restent présentes entre les deux champs (36) de pression, et que les deux éléments (13, 14) couvercle soient conçus de façon entièrement symétrique, indépendamment du sens de rotation, par rapport au plan (22) médian,.
  2. Une machine hydraulique à pignons internes conforme à la revendication n° 1, caractérisée en ce que chacun des éléments (13, 14) couvercle présente deux champs (36) de pression et qu'une plaque (35) d'étanchéité asymétrique par rapport au plan (22) médian est disposée entre les deux roues (20, 21) dentées et chacun des éléments (13, 14) couvercle, dans la direction axiale.
  3. Une machine hydraulique à pignons internes conforme à la revendication n° 1, caractérisée en ce que un champ (36) de pression présente partiellement comme ligne de délimitation un arc (39) de cercle, dont le centre se trouve sur l'axe de la roue (21) creuse, et qu'en tant que ligne de délimitation, dans le sens du plan (22) médian et dans la zone d'engrenage entre les deux roues (20, 21) dentées, cet arc (39) de cercle est prolongé par une section (40) de contour, dont la distance par rapport au centre est supérieure au rayon de l'arc (39) de cercle.
  4. Une machine hydraulique à pignons internes conforme à la revendication n° 3, caractérisée en ce que la section (40) de contour est une droite et prolonge l'arc (39) de cercle dans sa tangente.
  5. Une machine hydraulique à pignons internes conforme à une revendication précédente, caractérisée en ce que dans l'élément (13, 14) couvercle, dans la zone d'engrenage entre les deux roues (20, 21) dentées, entre le premier champ (36) de pression et le deuxième champ (36) de pression, se trouve un troisième champ (60) de pression s'étendant de part et d'autre du plan (22) médian, et que ce troisième champ (60) de pression peut être soumis à une haute pression avec l'un ou l' autre des deux champs (36) de pression, selon le cas.
  6. Une machine hydraulique à pignons internes conforme à la revendication n° 5, caractérisée en ce que le troisième champ (60) de pression est conçu de façon symétrique par rapport au plan (22) médian.
  7. Une machine hydraulique à pignons internes conforme à la revendication n° 5 ou n° 6, caractérisée en ce que le troisième champ (60) de pression est conçu de forme circulaire.
  8. Une machine hydraulique à pignons internes conforme à une des revendications n° 5 à n° 7, caractérisée en ce que la plaque (35) d'étanchéité présente une ouverture débouchant dans le troisième champ (60) de pression, en particulier un alésage (61), et, dans sa surface latérale orientée vers les roues (20, 21) dentées, présente un évidement (62), qui s'étend du plan (22) médian jusqu'au côté haute pression et qui sert de départ à l'ouverture (61).
  9. Une machine hydraulique à pignons internes conforme à une revendication précédente, caractérisée en ce que un champ (36, 60) de pression se trouve à l'intérieur d'un évidement dans l'élément (13, 14) couvercle.
  10. Une machine hydraulique à pignons internes conforme à une revendication précédente, caractérisée en ce que un élément (24) de remplissage, qui se trouve entre une roue (21) creuse à denture intérieure et un pignon (20) à denture extérieure, est étayé par un goujon (25) d'élément de remplissage, lequel est guidé dans le plan (22) médian dans un élément (13, 14) couvercle.
EP94924212A 1993-07-03 1994-06-29 Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures Expired - Lifetime EP0707686B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4322240 1993-07-03
DE4322240A DE4322240C2 (de) 1993-07-03 1993-07-03 Hydraulische Innenzahnradmaschine (Pumpe oder Motor)
PCT/EP1994/002114 WO1995002125A1 (fr) 1993-07-03 1994-06-29 Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures

Publications (2)

Publication Number Publication Date
EP0707686A1 EP0707686A1 (fr) 1996-04-24
EP0707686B1 true EP0707686B1 (fr) 2000-10-18

Family

ID=6491930

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94924212A Expired - Lifetime EP0707686B1 (fr) 1993-07-03 1994-06-29 Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures

Country Status (5)

Country Link
US (1) US5674060A (fr)
EP (1) EP0707686B1 (fr)
JP (1) JP3841823B2 (fr)
DE (2) DE4345273C2 (fr)
WO (1) WO1995002125A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6042352A (en) * 1998-08-12 2000-03-28 Argo-Tech Corporation Bearing with pulsed bleed configuration
US6273527B1 (en) * 1998-10-06 2001-08-14 Denso Corporation Rotary pump with better fluid sealing structure and brake apparatus having same
DE19847144B4 (de) * 1998-10-13 2006-03-02 Bosch Rexroth Aktiengesellschaft Hydraulische Innenzahnradmaschine
DE19858483A1 (de) 1998-12-18 2000-08-31 Mannesmann Rexroth Ag Hydraulische Verdrängermaschine, insbesondere Verdrängerpumpe
DE19917593C2 (de) * 1999-04-19 2002-05-02 Hydraulik Ring Gmbh Hydraulische Verdrängermaschine
ES2218021T3 (es) 1999-04-30 2004-11-16 Hydraulik-Ring Gmbh Alimentacion con medio a presion para una transmision cvt.
DE10059059A1 (de) * 2000-11-28 2002-05-29 Continental Teves Ag & Co Ohg Innenzahnradpumpe
FR2844312B1 (fr) * 2002-09-05 2006-04-28 Centre Nat Rech Scient Machine tournante a capsulisme
DE102005004657A1 (de) * 2005-02-02 2006-08-03 Eckerle Industrie-Elektronik Gmbh Innenzahnradmaschine
DE102011075415A1 (de) 2011-05-06 2012-11-08 Robert Bosch Gmbh Zahnpumpe
US9163628B2 (en) 2013-03-11 2015-10-20 Imo Industries, Inc. Self adjusting gear pump
US10514032B2 (en) * 2015-02-05 2019-12-24 Circor Pumps North America, Llc Tolerance independent crescent internal gear pump
GB2559136B (en) * 2017-01-25 2020-04-15 Edwards Ltd Vacuum pump with biased stator seals and method of manufacture thereof
TR201910917A2 (tr) * 2019-07-22 2019-08-21 Muhammed Veysel Hi̇dromotor
DE202022002997U1 (de) 2021-08-05 2024-04-18 Hydraulik Nord Technologies GmbH Innenzahnradmaschine

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT46017B (de) 1909-10-13 1911-01-25 Siemens Schuckertwerke Wien Kühleinrichtung für Dynamomaschinen.
DE1553015B2 (de) * 1963-04-11 1977-04-21 Eckerle, Otto, 7502 Maisch Verschleissausgleichende, innenachsige zahnradpumpe
DE1528954A1 (de) * 1964-08-08 1970-07-02 Bosch Gmbh Robert Verdraengermaschine
US3303793A (en) * 1965-08-17 1967-02-14 Morita Nobuo Rotary gear pump
DE1653837A1 (de) * 1968-03-14 1975-03-20 Otto Eckerle Hochdruckpumpe, insbesondere hochdruck-zahnradpumpe
DE1728085C2 (de) * 1968-08-22 1986-12-04 Eckerle, Otto, 7502 Malsch Zahnradpumpe
DE1801825A1 (de) * 1968-10-08 1970-06-04 Eckerle Otto Hochdruckinnenzahnradpumpe
DE2223916A1 (de) * 1972-05-17 1973-11-29 Friedrich Reichert Gmbh Maschf Innenverzahnte zahnradpumpe fuer hohe druecke
DE2554960C2 (de) * 1975-12-06 1984-08-23 J.M. Voith Gmbh, 7920 Heidenheim Innenzahnradpumpe
DE7730698U1 (de) * 1977-10-05 1978-04-13 Otto Eckerle Gmbh & Co, Kg, 7502 Malsch Hochdruck-zahnradmaschine
GB2051241B (en) * 1979-06-16 1983-03-16 Dowty Hydraulic Units Ltd Rotary positive-displacement fluid-pressure machines
FR2574517B1 (fr) * 1984-12-10 1988-09-02 Hydroperfect Int Joint d'etancheite et son application a la realisation de la compensation hydrostatique de pompes et moteurs hydrauliques
FR2585083B1 (fr) * 1985-07-16 1989-09-01 Hydroperfect Internal Hpi Dispositif a action hydraulique pure pour la compensation hydrostatique de pompes et moteurs hydrauliques du type a engrenage
DE8707256U1 (de) * 1987-05-20 1988-09-22 Robert Bosch Gmbh, 7000 Stuttgart Zahnradmaschine (Pumpe oder Motor)
DE8707735U1 (de) * 1987-05-30 1988-09-29 Robert Bosch Gmbh, 7000 Stuttgart Reversierbare Zahnradmaschine (Pumpe oder Motor)
JPH01147178A (ja) * 1987-11-30 1989-06-08 Shimadzu Corp 内接歯車ポンプ又はモータ
DE9011541U1 (de) * 1990-08-08 1991-12-05 Robert Bosch Gmbh, 7000 Stuttgart Zahnradmaschine (Pumpe oder Motor)
IT224734Z2 (it) * 1991-05-07 1996-06-27 Macchina ad ingranaggi fungente da pompa o motore.
DE9108238U1 (de) * 1991-07-04 1992-10-29 Robert Bosch Gmbh, 7000 Stuttgart Hydraulischer Zahnradmotor

Also Published As

Publication number Publication date
JPH09503261A (ja) 1997-03-31
EP0707686A1 (fr) 1996-04-24
US5674060A (en) 1997-10-07
DE4322240A1 (de) 1995-01-19
WO1995002125A1 (fr) 1995-01-19
JP3841823B2 (ja) 2006-11-08
DE4345273C2 (de) 1997-02-06
DE4322240C2 (de) 1997-01-09

Similar Documents

Publication Publication Date Title
DE19613833B4 (de) Innenzahnradmaschine, insbesondere Innenzahnradpumpe
EP0707686B1 (fr) Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures
EP1701038B1 (fr) Pompe à engrenages internes
DE102005041579B4 (de) Innenzahnradpumpe mit Füllstück
DE1553276C3 (de) Dichtungsanordnung in einer Zahnradpumpe
DE102016207093B4 (de) Zahnradfluidmaschine
DE1703077C3 (de) Hydraulische Zahnradpumpe oder hydraulischer Zahnradmotor mit AuBeneingriffszahnrädern
DE2000477A1 (de) Hydraulische Pumpe oder Motor
EP2711552B1 (fr) Machine à roue dentée pourvue d'un raccord basse pression déviant de la forme circulaire
DE4322239C2 (de) Innenzahnradmaschine (Pumpe oder Motor)
DE4338875C2 (de) Reversierbare Innenzahnradmaschine (Pumpe oder Motor)
DE1264958B (de) Zahnradpumpe oder -motor
DE4421255C1 (de) Füllstücklose Innenzahnradpumpe
DE19609992B4 (de) Zahnradmaschine
DE102005033679B4 (de) Ölpumpe
DE102018104976A1 (de) Außenzahnradmaschine
DE4322584C2 (de) Innenzahnradmaschine (Pumpe oder Motor)
DE60211966T2 (de) Spiralverdichter
DE102004046934A1 (de) Hydraulische Maschine
DE3346519C2 (fr)
CH663446A5 (de) Aussenachsige rotationskolbenmaschine.
EP3276127A1 (fr) Machine hydraulique à roue dentée
WO2008125106A1 (fr) Moteur à pistons rotatifs
DE9321656U1 (de) Reversierbare Innenzahnradmaschine (Pumpe oder Motor)
DE2852477C2 (de) Rotationskolbenmaschine

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

17P Request for examination filed

Effective date: 19951123

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): FR GB IT SE

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MANNESMANN REXROTH AG

17Q First examination report despatched

Effective date: 19980814

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): FR GB IT SE

ITF It: translation for a ep patent filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20010112

Year of fee payment: 8

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20010118

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

Effective date: 20010111

ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20010621

Year of fee payment: 8

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

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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: 20020629

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

Effective date: 20020629

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: 20030228

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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

Ref country code: IT

Payment date: 20100624

Year of fee payment: 17

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

Effective date: 20110629