EP1364127A1 - Pompe a engrenages interieurs sans pieces intercalaires - Google Patents

Pompe a engrenages interieurs sans pieces intercalaires

Info

Publication number
EP1364127A1
EP1364127A1 EP02714073A EP02714073A EP1364127A1 EP 1364127 A1 EP1364127 A1 EP 1364127A1 EP 02714073 A EP02714073 A EP 02714073A EP 02714073 A EP02714073 A EP 02714073A EP 1364127 A1 EP1364127 A1 EP 1364127A1
Authority
EP
European Patent Office
Prior art keywords
bearing ring
ring
housing
bore
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.)
Granted
Application number
EP02714073A
Other languages
German (de)
English (en)
Other versions
EP1364127B1 (fr
Inventor
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.)
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 EP1364127A1 publication Critical patent/EP1364127A1/fr
Application granted granted Critical
Publication of EP1364127B1 publication Critical patent/EP1364127B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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

Definitions

  • the invention relates to a solid internal gear pump with the features according to the preamble of patent claim 1.
  • the spring acting on the bearing ring can be a hairpin leaf spring which is received in an axial groove with a rectangular cross-section on the outer circumference of the bearing ring and lies flat against the groove base, or a helical compression spring which extends in a manner starting from the outer circumference of the bearing ring Radial bore is arranged and is supported on the housing wall via a ball foot (EP-A 848 165).
  • Freedom of movement can be impaired by the spring force and the flat contact of the leaf spring or the helical compression spring.
  • the impairment particularly in the case of non-lubricating fluids, can lead to the fact that when the internal gear pump is depressurized, e.g. when starting, the bearing ring and with it the ring gear are kept tilted relative to the pinion, there being no perfect sealing contact between the tooth heads. With frequent start / stop operation, this leads to operating problems because the pressure build-up is then only delayed.
  • the object of the invention is therefore to propose an internal gear pump of the type described, in which a perfect sealing contact, in particular between the tooth heads, is also ensured due to the spring loading of the bearing ring.
  • the freedom of movement of the bearing ring can be further improved if the bore in the bearing ring contains an abutment against which the bar spring rests and otherwise has no contact with the bore wall.
  • the contact projection can be provided anywhere in the longitudinal course of the bore, but is expediently arranged in the longitudinal center thereof; its axial extension is small relative to the bore length and advantageously rounded in the sense of a reduction in the contact area with the bar spring, so that theoretically there is point contact.
  • the rod spring is expediently supported at both ends in housing bores provided on both sides of the bearing ring, the position of which is relative to the pinion axis and to the bore of the bearing ring is determined so that in the assembled and depressurized state of the internal gear pump, the bar spring is bent out to the desired extent under pretension.
  • Figure 1 is an end view of the pinion / ring gear unit as a section along the line C - C in Figure 2.
  • the internal gear pump shown in FIGS. 1 and 2 comprises a housing, designated as a whole by 1, which is constructed from a cup-shaped housing part 11 and a likewise cup-shaped housing cover 12 fastened to its end face.
  • 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 mounted via slide bearings, not shown, and has a coupling part 16 on the right-hand end in FIG. 2 for engaging the drive shaft of a 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 accommodated in the housing 1 with axial and radial play.
  • the axial and radial play which is indicated in FIG. 1 by thick lines and is exaggerated in FIG. 3, is, for example, 0.2 to 0.5 mm.
  • a bearing bush 6 made of a bearing metal is pressed into the bearing ring 5.
  • sealing axial plates 8 On the end faces of the housing part 11 and the cover 12 on the one hand and on the end faces of the pinion 2 and ring gear 3, on the other hand, are 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 and the pressure channel by a breakthrough, 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, i.e. there is one
  • Involute toothing in front the tooth heads being rounded in order to achieve a bump-free run-up on one another in the non-engagement area 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 one receiving the bearing ring 5 is
  • Housing part 11 rotated concentrically to the pinion axis 15.
  • the bearing surface of the bearing ring 5 is concentric with the ring gear axis 18, which means that the outer peripheral surface of the bearing ring 5 is in turn eccentric to the bearing surface.
  • the wall of the bore or recess of the housing part 11 receiving the running unit is partially penetrated by a bearing pin 20 which is pressed into the bottom of this recess. With the largely semi-cylindrical partial circumferential surface of the bearing pin 20 protruding beyond the wall, it protrudes into an axial groove 22 of the bearing ring 5, which corresponds to the circular cylindrical cross section of the bearing pin 20 is adapted.
  • 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 of the housing part 11 within the scope of the radial play available.
  • this swivel axis is offset by approximately 80 ° in the direction of rotation indicated by the arrow with respect to the apex of the non-engaging region in which two tooth heads lie exactly opposite one another.
  • the bearing ring 5 has a through bore 24 which is parallel to the axes of rotation 15 and 18 and through which a rod spring 25 extends, offset by approximately the same amount in the opposite direction of rotation.
  • the bore 24 is offset from both ends to form a shoulder, so that an annular projection 26 is thereby created in the longitudinal center of the bore.
  • 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 bar spring extends contact-free through the bore 24 and the latter relative to considerably further housing recesses 28.
  • the support ends of the bar spring 25 are each accommodated with play in the housing bores 32.
  • the bar spring 25 has a constant circular cross section over its entire length.
  • Spring force depends on the pump size and is generally 2 - 5% of the pressure forces occurring in the pressure chamber
  • 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. Since the contact of the rod spring 25 with the bearing ring 5 is limited to the short section of the contact projection 26 in the bore 24, the bearing ring 5 and with it the ring gear 3 can follow lateral tilting and sliding movements which are due to the hydraulic and mechanical forces due to tolerances Operation occur.
  • the friction hysteresis between the bar spring 25 and the contact projection 26 is so low that when the operating pressure is lifted, e.g. after switching off, the teeth of pinion 2 and ring gear 3, and in particular their tooth heads, lie tightly against one another and consequently a perfect restart with immediate pressure build-up is ensured.
  • the invention is not limited to the design of the internal gear pump according to the exemplary embodiment.
  • trochoidal or cycloid toothing can also be used be used.
  • the bar spring can have cross sections other than circular and need not be of constant cross section.
  • the bearing ring bore penetrated by the bar spring does not necessarily have to be exactly axially parallel to the pinion axis or cylindrical, but as a whole can have a curved or conical surface of revolution as the inner surface, which results in a minimal contact area with the bar spring.
  • the bar spring itself could also have a preferably central thickening which leads to a locally limited contact with the otherwise smooth bore.
  • the two support bores 32 do not necessarily have to be aligned with one another, but can deviate slightly from the coaxial orientation, provided the required prestress of the bar spring is ensured and there is contact with at least one edge of the bore.

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 ne comportant pas de pièces intercalaires, qui présente un corps (11), un coussinet (5), qui est logé dans un alésage du corps de façon à pouvoir se déplacer transversalement par rapport à l'axe de celui-ci mais de façon à ne pas pouvoir tourner, une roue à denture intérieure (3) montée rotative dans le coussinet et un pignon (2), lequel est monté de façon à pouvoir tourner dans ledit corps et est en prise avec la roue à denture intérieure, les dents de ce pignon définissant une chambre d'aspiration et une chambre de refoulement dans les dentures, d'une part, par engagement complet dans les entredents de la roue à denture intérieure et, d'autre part, par un contact serré avec les têtes des dents de la roue à denture intérieure dans une zone de la roue à denture intérieure sans prise presque diamétralement opposée à la zone d'engagement dans les entredents. Un ressort (25) qui exerce une force sur le coussinet (5) permet à celui-ci de pivoter par rapport à alésage, autour d'un axe de pivotement (20, 22) parallèle à son axe, de telle sorte que le contact serré est maintenu entre les têtes des dents du pignon (2) et de la roue à denture intérieure (3). Le ressort (25) agissant sur le coussinet (5) est une barre de torsion qui traverse un alésage (24, 26) s'étendant à l'intérieur du coussinet approximativement dans le sens axial de celui-ci et qui, au moins à une extrémité, est soutenu dans un alésage de corps (32).
EP02714073A 2001-03-01 2002-02-28 Pompe a engrenages interieurs sans pieces intercalaires Expired - Lifetime EP1364127B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE2001109770 DE10109770A1 (de) 2001-03-01 2001-03-01 Füllstücklose Innenzahnradpumpe
DE10109770 2001-03-01
PCT/DE2002/000710 WO2002070899A1 (fr) 2001-03-01 2002-02-28 Pompe a engrenages interieurs sans pieces intercalaires

Publications (2)

Publication Number Publication Date
EP1364127A1 true EP1364127A1 (fr) 2003-11-26
EP1364127B1 EP1364127B1 (fr) 2007-08-15

Family

ID=7675875

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02714073A Expired - Lifetime EP1364127B1 (fr) 2001-03-01 2002-02-28 Pompe a engrenages interieurs sans pieces intercalaires

Country Status (3)

Country Link
EP (1) EP1364127B1 (fr)
DE (2) DE10109770A1 (fr)
WO (1) WO2002070899A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012211228A1 (de) 2012-06-29 2014-01-02 Robert Bosch Gmbh Innenzahnradpumpe
DE102012215023A1 (de) 2012-06-29 2014-01-02 Robert Bosch Gmbh Innenzahnradpumpe
DE102012214243A1 (de) 2012-08-10 2014-02-13 Robert Bosch Gmbh Innenzahnradpumpe
DE102018222179A1 (de) * 2018-12-18 2020-06-18 Eckerle Technologies GmbH Zahnradfluidmaschine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19651683A1 (de) 1996-12-12 1998-06-18 Otto Eckerle Füllstücklose Innenzahnradpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO02070899A1 *

Also Published As

Publication number Publication date
EP1364127B1 (fr) 2007-08-15
DE50210701D1 (de) 2007-09-27
DE10109770A1 (de) 2002-09-05
WO2002070899A1 (fr) 2002-09-12

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