EP1364126A1 - Pompe a engrenages interieurs sans pieces intercalaires - Google Patents

Pompe a engrenages interieurs sans pieces intercalaires

Info

Publication number
EP1364126A1
EP1364126A1 EP02714072A EP02714072A EP1364126A1 EP 1364126 A1 EP1364126 A1 EP 1364126A1 EP 02714072 A EP02714072 A EP 02714072A EP 02714072 A EP02714072 A EP 02714072A EP 1364126 A1 EP1364126 A1 EP 1364126A1
Authority
EP
European Patent Office
Prior art keywords
bearing ring
ring
housing
pinion
internal gear
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.)
Withdrawn
Application number
EP02714072A
Other languages
German (de)
English (en)
Inventor
Reinhard Pippes
Stefan Bellemann
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.)
Eckerle Industrie Elektronik GmbH
Original Assignee
Eckerle Industrie Elektronik GmbH
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 Eckerle Industrie Elektronik GmbH filed Critical Eckerle Industrie Elektronik GmbH
Publication of EP1364126A1 publication Critical patent/EP1364126A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes

Definitions

  • the invention relates to an internal gear pump with the features according to the preamble of patent claim 1.
  • Suction chamber and pressure chamber between the toothing of the pinion and ring gear are each delimited by housing inserts sealingly abutting the end faces of the pinion and ring gear, one of which is screwed or screwed onto an external thread of the pinion shaft and the other into an internal thread of the housing.
  • this design of the housing, the housing inserts and the bearing ring with circumferentially eccentric surfaces is complex because compliance with the high precision required in production, in particular at higher operating pressures, is very complex.
  • the object of the invention is therefore to reduce the manufacturing costs of the housing and the bearing ring without running the risk that the tooth tip wear through the sealing abutment of the tooth tips against each other in the non-engaging area of the toothing is excessive.
  • Trochoid toothings do not make sealing contact with each other during the entire revolution, but first diverge after full engagement and only in the non-engagement area of the toothing do the tooth heads of some teeth come into contact with the necessary sealing contact. There is therefore a risk of excessive wear of the tooth heads and thus a reduced service life of the machine if the tooth heads are pressed excessively against one another by the swiveling torque acting on the bearing ring in proportion to the pressure. This is prevented according to the invention in that the pressing force of the tooth tips against one another can be kept within limits by limiting the pivoting path of the bearing ring to a predetermined value.
  • a bore running approximately parallel to its axial direction can be provided in the bearing ring, through which a pin fixed in the housing protrudes with a play determining the swivel path.
  • This pin can be designed as a spiral spring, which presses the bearing ring in the pivoting direction in the depressurized state of the internal gear pump, but prevents or hinders the bearing ring from further pivoting after being relieved by the predominant hydraulic pressure forces.
  • a stop pin can be placed in the crescent-shaped radial gap between the bearing ring and the housing recess from the bottom thereof protrude at which the bearing ring strikes after a certain swivel path.
  • the stop pin can be fixed to the housing, for example at the bottom of the housing recess or on the bearing ring.
  • the swivel path can be determined most precisely from the outset if this pin is arranged offset by approximately 90 ° with respect to the swivel axis of the bearing ring.
  • the pivoting path of the bearing ring can be limited by a step which projects axially into the crescent-shaped radial gap between the bearing ring and the housing wall and which can be produced by means of a milling tool in the course of precision machining of the recess base. Since this base is worked out for the sealing contact of the end faces of the pinion and ring gear or corresponding axial plates thereon centrally to the ring gear axis, the step mentioned is given a contour corresponding to the crescent-shaped radial gap.
  • Figure 1 is an end view of the unit pinion / ring gear / bearing ring as a section along the line C - C in Figure 2.
  • FIG. 4 shows a representation of a second embodiment analogous to FIG. 1;
  • FIG. 6 shows a representation of a third embodiment analogous to FIG. 1,
  • FIG. 7 shows a partial section along the line E.-E in Fig.6.
  • the internal gear pump shown in Figures 1 and 2 includes a whole
  • housing 1 designated housing, which is constructed from a cup-shaped housing part 11 and a cup-shaped housing cover 12 fastened to the end face thereof.
  • the housing 1 contains suction and pressure channels, not shown, which conduct the conveying liquid to and from the internal gear pump in the usual way.
  • a pinion shaft 14 with an axis of rotation 15 is rotatably supported via slide bearings, not shown, and has a coupling part 16 on the right-hand end in FIG. 2 for engagement in the drive shaft of a drive motor, not shown.
  • a pinion 2 which meshes with a ring gear 3, is formed in one piece on the pinion shaft 14.
  • the ring gear 3 is widened on its outer circumference to form a race 4 and rotatably supported in a bearing ring 5 which is received in a housing recess 13.
  • a bearing bush 6 made of a bearing metal is pressed into the bearing ring 5.
  • sealing axial plates 8 which axially limit the tightly sealed suction and pressure chamber within the toothing of pinion 2 and ring gear 3 and connect them to the suction channel or the pressure channel by an opening (not shown).
  • the pinion 2 and the ring gear 3 are mounted relative to one another with an eccentricity e.
  • This distance between the pinion axis 15 and the ring gear axis 18 corresponds to the theoretical tooth geometry of the pinion and ring gear and presupposes that the toothings roll and slide together without play.
  • the tooth flanks of the toothings are each designed as involute curves, ie there is involute toothing, the tooth heads being rounded in the non-engagement area to achieve a bump-free run-up and for the purpose of sealing.
  • the number of teeth of the ring gear 3 differs from that of the pinion 2 by 1.
  • the toothing meshes with one another in such a way that in FIG.
  • the housing recess 13 receiving the bearing ring 5 and the outer surface 17 of the housing part 11 with the radii R1 and R2 are machined concentrically with the pinion axis 15.
  • the bearing surface 19 and the outer peripheral surface 20 of the bearing ring 5, however, are both concentric to the ring gear axis 18, which means that the outer peripheral surface 20 of the bearing ring 5 with its radius R3 is in turn eccentric to the housing recess 13 and with this a crescent-shaped radial gap
  • the wall of the recess 13 is partially penetrated by a bearing pin 22 which is pressed into the bottom of this recess. With the largely semi-cylindrical partial peripheral surface of the bearing pin protruding beyond the wall
  • this bearing pin forms a pivot axis parallel to the axes of the pinion 2 and the ring gear 3, about which the bearing ring 5 can be pivoted in the recess 13.
  • this pivot axis is offset by approximately 80 ° in the direction of rotation indicated by the arrow in relation to the apex of the non-engaging region in which two tooth heads lie exactly opposite one another.
  • the bearing ring 5 has an offset parallel to the axes of rotation 15 and 18 parallel to the direction of rotation by approximately the same amount
  • the bore 24 is offset from each shoulder to a shoulder, so that thereby a in the longitudinal center of the bore Ring projection 26 is created.
  • the bore 24 opens at both ends in the region of a recess 28 in the housing or cover wall, which has a conically tapering bottom 30, which in turn merges into a housing bore 32 for supporting the bar spring 25.
  • the two housing bores 32 are aligned with one another and are offset radially with respect to the pinion axis 15 with respect to the bore 24. This results in the bending prestress of the bar spring 25 shown in FIG.
  • the pumped medium is conveyed through the suction channel into the suction chamber (to the left in FIG. 1 from the line AA) between the teeth of the pinion 2 and the ring gear 3.
  • the pumped medium is pressed out of the pressure chamber (to the right of line A - A in Fig. 1) with increased pressure through the pressure channel.
  • the toothing of the pinion and ring gear is an involute toothing in the exemplary embodiment, its teeth are in mutual sealing contact only in the area of full engagement with their flanks and in the non-engagement area with their tooth heads. In the remaining part of the suction chamber and pressure chamber, the teeth move away from each other to such an extent that essentially the same pressure prevails over the suction chamber and the pressure chamber, and approach each other again in the entry-free area to produce the sealing contact between the tooth heads.
  • the prestressed bar spring 25 produces in the depressurized state, i.e. outside of the operation of the internal gear pump and in its start-up phase, approximately in the same direction as the pressure forces, a pivoting moment on the bearing ring 5 and thereby ensures that the toothing is correctly mutually connected and arranged, as well as for the required sealing contact, regardless of the occurrence of the hydraulic pressure forces in the non-invasive area.
  • the bias of the bar spring 25 is selected so that in the operating state of the internal gear pump, the hydraulic pressure forces alone ensure the sealing contact and the bar spring 25 is relieved and rests on the opposite side while consuming the play in the annular contact projection 26. In this position, the bar spring has a limiting effect on a further pivoting of the bearing ring 5 and thus relieves the tooth heads of a further contact pressure.
  • FIGS. 4 and 5 differs from the previous one in that, instead of the bar spring 25, two stop pins 35 are pressed into the bottom of the housing recess 13 and protrude axially into the sickle-shaped annular gap 21, one of which is about 70 ° and the other another is offset by approximately 170 ° in the direction of rotation indicated by the arrow with respect to the pivot axis 22.
  • the thickness of the stop pins 35 and their position are coordinated with respect to the local width of the annular gap 21 so that when the bearing ring 5 abuts the housing wall on one side, a predetermined one Distance to the circumferential surface 20 results, which defines the limited pivot path of the bearing ring 5.
  • the stop pins 35 can also be attached to or in the bearing ring 5 instead of being attached in the housing, e.g. welded or glued to the outer peripheral surface of the bearing ring 5, preferably received in an axially directed receiving groove in the peripheral surface of the bearing ring 5.
  • a desired tolerance compensation can be set by appropriately selecting the diameter of the stop pin 35.
  • the embodiment according to FIGS. 6 and 7 has, as a swivel path limitation for the bearing ring 5, an axially protruding step 45 in the annular gap 21, which extends with the radius R4 concentrically to the ring gear axis and whose contour is aligned with the crescent-shaped annular gap.
  • the annular gap 46 present between the step 45 and the outer surface 20 of the bearing ring 5 determines the total pivoting path of the bearing ring 5 on one side of the housing wall diametrically opposite the step 45.
  • the bearing ring 5 is acted upon solely by hydraulic pressure forces and the pivoting moment generated therefrom about the pivot axis 22 in order to maintain the sealing contact of the tooth heads in the entry-free area. It comes into contact with the stop pins 35 or the step 45 in the course of the pivoting movement, which then take over part of the pivoting moment and thereby the
  • a bar spring of the type described above can additionally be provided, which either also contributes to limiting the pivoting path of the bearing ring or only ensures the sealing contact of the tooth heads in the unpressurized state of the pump in the pretensioned state.

Landscapes

  • 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'invention concerne une pompe à engrenages intérieurs qui ne comporte pas de pièces intercalaires, qui présente un corps (1) et un coussinet (5), qui est logé dans une cavité (13) dudit corps de façon à pouvoir se déplacer transversalement par rapport à son axe mais de façon à ne pas pouvoir tourner. La pompe à engrenages intérieurs comporte également une roue à denture intérieure (3) qui est montée, de façon à pouvoir tourner, à l'intérieur du coussinet ainsi qu'un pignon (2) qui est monté dans le corps de pompe de façon à pouvoir tourner et est en prise avec la roue à denture intérieure. La surface périphérique intérieure de la cavité (13) du corps s'étend coaxialement par rapport au pignon (2), et le coussinet, qui est disposé de façon excentrique par rapport à l'axe de pignon (15), peut pivoter par rapport à cette cavité de corps, autour d'un axe de pivotement (20, 22, 23) qui est parallèle à son axe, de telle sorte que le contact serré entre les têtes des dents du pignon (2) et de la roue à denture intérieure (3) est maintenu. La surface périphérique intérieure du coussinet (5) qui forme la surface de support de la roue à denture intérieure (3) s'étend coaxialement par rapport à sa surface périphérique extérieure (20), et le trajet de pivotement du coussinet est délimité à une amplitude prédéterminée par une goupille (25) qui le traverse où qui est disposée dans l'interstice (21) en forme de croissant, ou bien par un gradin faisant saillie, situé dans cet interstice.
EP02714072A 2001-03-01 2002-02-28 Pompe a engrenages interieurs sans pieces intercalaires Withdrawn EP1364126A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10109769A DE10109769A1 (de) 2001-03-01 2001-03-01 Füllstücklose Innenzahnradpumpe
DE10109769 2001-03-01
PCT/DE2002/000709 WO2002070898A1 (fr) 2001-03-01 2002-02-28 Pompe a engrenages interieurs sans pieces intercalaires

Publications (1)

Publication Number Publication Date
EP1364126A1 true EP1364126A1 (fr) 2003-11-26

Family

ID=7675874

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02714072A Withdrawn EP1364126A1 (fr) 2001-03-01 2002-02-28 Pompe a engrenages interieurs sans pieces intercalaires

Country Status (6)

Country Link
US (1) US20030161748A1 (fr)
EP (1) EP1364126A1 (fr)
JP (1) JP2004518866A (fr)
KR (1) KR20030011826A (fr)
DE (1) DE10109769A1 (fr)
WO (1) WO2002070898A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10244556A1 (de) * 2002-06-13 2003-12-24 Continental Teves Ag & Co Ohg Motor-Pumpen-Aggregat, insbesondere für schlupfgeregelte Bremssysteme
JP5141993B2 (ja) * 2008-08-01 2013-02-13 アイシン精機株式会社 オイルポンプ
DE102018222179A1 (de) * 2018-12-18 2020-06-18 Eckerle Technologies GmbH Zahnradfluidmaschine

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3118387A (en) * 1964-01-21 Reveksible gear pump
US2792788A (en) * 1957-05-21 eames
US3034446A (en) 1957-09-06 1962-05-15 Robert W Brundage Hydraulic pump or motor
GB1233376A (fr) * 1967-11-17 1971-05-26
DE2313085C2 (de) * 1973-03-16 1984-05-24 Otto 7502 Malsch Eckerle Axial und radial kompensierte Hochdruck-Zahnradpumpe
DE4328733C1 (de) * 1993-08-26 1994-09-08 Voith Gmbh J M Innenzahnradpumpe
DE19651683A1 (de) 1996-12-12 1998-06-18 Otto Eckerle Füllstücklose Innenzahnradpumpe
DE19815421A1 (de) * 1998-04-07 1999-10-14 Eckerle Ind Elektronik Gmbh Innenzahnradmaschine
DE10047738A1 (de) * 2000-09-27 2002-04-11 Bosch Gmbh Robert Innenzahnradpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO02070898A1 *

Also Published As

Publication number Publication date
US20030161748A1 (en) 2003-08-28
WO2002070898A1 (fr) 2002-09-12
KR20030011826A (ko) 2003-02-11
DE10109769A1 (de) 2002-09-05
JP2004518866A (ja) 2004-06-24

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