EP0949419B1 - Pompe à engrenages internes - Google Patents

Pompe à engrenages internes Download PDF

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Publication number
EP0949419B1
EP0949419B1 EP99105579A EP99105579A EP0949419B1 EP 0949419 B1 EP0949419 B1 EP 0949419B1 EP 99105579 A EP99105579 A EP 99105579A EP 99105579 A EP99105579 A EP 99105579A EP 0949419 B1 EP0949419 B1 EP 0949419B1
Authority
EP
European Patent Office
Prior art keywords
ring
machine according
ring gear
internal gear
rotor
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
EP99105579A
Other languages
German (de)
English (en)
Other versions
EP0949419A1 (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 EP0949419A1 publication Critical patent/EP0949419A1/fr
Application granted granted Critical
Publication of EP0949419B1 publication Critical patent/EP0949419B1/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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49229—Prime mover or fluid pump making
    • Y10T29/49236—Fluid pump or compressor making
    • Y10T29/49242—Screw or gear type, e.g., Moineau type

Definitions

  • the invention relates to an internal gear machine with a housing and with a running group accommodated in the housing with the structure according to the preamble of patent claim 1.
  • the ring gear is either in one on its outer circumference Plain bearings added, being hydrostatic or hydrodynamic storage conditions can be set, or in a rolling bearing.
  • the bearing capacity is the permissible delivery or operating pressure of the internal gear machine certainly.
  • the delivery or operating pressure is common undesirable due to the load-bearing capacity of the ring gear bearing limited so that with respect to the speed and / or the
  • the toothing width may be a compromise in terms of design must be taken to the desired funding or To be able to realize operating pressure in practice.
  • the widening of the outer peripheral surface of the ring gear in the manner described leads to a reduction in the bearing pressure.
  • a very high level of precision is required, particularly with regard to the plane parallelism of the two ring gear end faces, which is within a tolerance range of a few ⁇ m at high operating pressures and / or a small design, but these end faces are difficult to access due to the axially projecting widenings for the corresponding machining.
  • the ring gear Since the ring gear is wider on its outer circumference than in the area of the toothing, the hydraulic pressure forces prevailing between the toothing of the pinion and ring gear, by means of which the ring gear is pressed into its bearing, are distributed over a larger bearing surface, as a result of which the specific bearing load is reduced.
  • the widening of the ring gear on its outer circumference to form a raceway by assembling corresponding parts can be achieved in a variety of ways. It is only important that the part of the ring gear that forms the outer circumference rotates as a race together with the part that supports the inner toothing of the ring gear as a unit.
  • the separately produced race can be positively and / or non-positively connected to the part having the internal toothing.
  • Adequate frictional engagement occurs when the internal gear machine is in operation when the part of the ring gear carrying the internal toothing is pressed with its peripheral surface by the hydraulic forces in the toothing against the inner circumference of the race. Since only the bearing friction torque has to be overcome in operation in order to rotate the race together with the part that supports the internal toothing, the frictional engagement achieved in this way is sufficient. Therefore, an embodiment for the ring gear widened on the outer circumference to form a ring is conceivable, in which there is only a positive connection between the ring and the part of the ring gear carrying the internal toothing for the time of the still unpressurized starting of the internal gear machine.
  • the internal gear machine shown in FIGS. 1 to 3 comprises a housing generally designated 1, which consists of a Pot-shaped housing part 11 and one on the end face attached housing cover 12 is constructed.
  • a pinion shaft 14 is rotatably supported a pinion 2 is rotatably attached.
  • the pinion 2 meshes with a ring gear 3 (cross-hatched in FIG. 2 for emphasis), which is received in a bearing ring 4 and rotatably supported therein is.
  • the pinion 2 and the ring gear 3 are, as in FIG. 1 emerges relative to each other with an eccentricity e stored.
  • the eccentricity e that is the distance between the pinion axis and the ring gear axis, corresponds to this Embodiment of the theoretical gear geometry of Pinion and ring gear and sets play-free rolling or sliding of the gears ahead.
  • the gears of the Pinion 2 and the ring gear 3 mesh with one another in a manner that on the left in Fig. 1 in the region of the dividing line A the teeth of the pinion 2 fully into the tooth gaps of the ring gear 3 engage and rest on the tooth flanks while on the opposite, in Fig. 1 right side entirely from the Tooth gaps of the ring gear 3 have emerged.
  • this non-intrusive ring gear area support several of the Tooth tips of the pinion 2 and the ring gear 3 (in the shown Embodiment three tooth heads each) in succession Course of the rotation on each other.
  • the number of teeth and the The geometry of the meshing gears are like this chosen that this type of combing causes in a known manner can be.
  • the Tooth flanks formed as involute curves, with the tooth heads to achieve a rolling and sliding contact for the purpose of Sealing are rounded.
  • the number of teeth of the ring gear 3 differs from that in this embodiment the pinion 2 by 1.
  • the bearing ring 4 is in a housing bore 15 of the cup-shaped Housing part 11 with a radial clearance of about 0.2 mm added.
  • the wall of the housing bore 15 is partially from a bearing pin 16 which penetrates into the bottom of the Housing bore 15 is firmly pressed. With that over the wall the housing bore 15 protruding largely semi-cylindrical part of the bearing pin 16, this is in one axially directed groove of the bearing ring 4 is added.
  • the Axial groove is adapted to the shape of the bearing pin 16 and also partially cylindrical.
  • the bearing pin 16 engaging in the axial groove therefore forms one for the bearing ring 4 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 from Fig. 1 shows, this pivot axis lies in a quadrant of the bearing ring 4, which is between the non-invasive Ring gear area and the center of the pressure chamber extends. Out of it there is a known mode of operation of this Embodiment shown inner wheel machine in that a torque due to the pressure forces prevailing in the pressure chamber is generated around the bearing pin 16 through which the bearing ring 4 about the pivot axis formed by the bearing pin 16 is pivoted. This will make it non-invasive Ring gear area with the tooth heads of pinion 2 and ring gear 3 a force proportional to the size of the compressive forces moved against each other and kept in sealing contact (cf. DE 196 51 683 A1).
  • FIGS. 1 to 3 is the Pinion shaft 14 both in the cup-shaped housing 11 and stored in the housing cover 12 via bushings.
  • the bearing ring 4 exceeds its width the width of pinion 2 and ring gear 3 is considerable and lies with its end faces slidably on the walls of the housing 11 or the cover 12.
  • Each of the two axial disks 30 has the toothing on it facing surface a pressure field 7, in the area in the thrust washer 30 on the side of the housing cover 12 is arranged, three openings 8 are provided.
  • the Breakthroughs 8 do not lead from the pressure chamber to the shown pressure outlet channel in the housing cover 12.
  • the Housing cover 12 faces diametrically opposite the pressure outlet channel a suction inlet channel 9, which is at its Junction expanded to a suction field 10.
  • a suction inlet channel 9 which is at its Junction expanded to a suction field 10.
  • In the wall of the Housing 11 and the housing cover 12 are each a pressure field 31 indicated by the respective axial disk 30 from the outside forth against the action of the inner pressure field 7 so is that the thrust washer in all operating conditions Maintains tight contact with the pinion 2 and the ring gear 3. Training and mode of operation of the pressure fields on axial washers are well known and therefore need to be found here no further explanation.
  • Each thrust washer 30 is supported for the purpose of securing its position on the one hand over the circumference of a bearing bore 33 on the Pinion shaft 14 and on the other hand on one in the housing 11 or from the housing cover 12 used pin 34.
  • Pins 34 each protrude into a blind hole in the outer end face of the axial disks 30 and are thereby held axially.
  • a movement of the Axial disks 30 together with pinion 2, ring gear 3 and bearing ring 4 allow (cf. EP 97-121 424.2 A1).
  • FIG. 4 shows the internal gear machine according to FIG. 1 to 3 used run group 20, which from the pinion 2 and the ring gear 3.
  • the ring gear 3 has an outer, to a race 35 designed part that the outer circumference 36 of the ring gear 3 forms, as well as the internal teeth load-bearing part 37.
  • the Race 35 of the ring gear 3 the width of the internal toothing load-bearing part 37 considerably; the raceway width is in this embodiment about three times the width of the internally toothed part 37.
  • 5b to 5f show variants of the corresponding one Connection type of these two parts.
  • the race 35b and the internally toothed part 37b separate components joined together by pressing, shrinking or glue are connected.
  • This embodiment allows one different choice of materials for the race and internally toothed part that better adapt to the required storage or combing properties allowed.
  • the race and internally toothed part of the ring gear each also separate Components.
  • the variant according to FIG. 5c shows one Positive connection between the race 35c and the internally toothed part 37c by means of a radially from the outer periphery 36c forth in the internally toothed part 37c pressed pin 38.
  • the internally toothed part 37d with the race 35d by an axially pressed cylindrical pin 39 connected in a corresponding partially cylindrical groove 40 of the race 35d and one not specified, also partially cylindrical groove of the internally toothed part 37d sits.
  • FIG. 5c shows one Positive connection between the race 35c and the internally toothed part 37c by means of a radially from the outer periphery 36c forth in the internally toothed part 37c pressed pin 38.
  • the inner circumference of the race 35e has a shoulder 41, on which the internally toothed part 37e with its front edge is present and by a welding spot or a partial or all-round weld 42 is attached.
  • the Embodiment according to variant 5f has the inner circumference of the Race 35f two at an axial distance from each other arranged ring grooves 43, in each of which a spring ring 44 is blown up.
  • the facing edges of the Annular grooves 43 have a distance from each other that is at most Width of the internally toothed part corresponds to 37f, whereby it is ensured that the spring washers 44 with frictional engagement abut the front edges of the internally toothed part 37f and hold it by this.
  • the race 35g with the internally toothed part 37g via a spring ring 45 coupled the shape of which is apparent from Fig. 7.
  • the Race 35g on its inner circumference and the internally toothed part 37g each have a circumferential annular groove on its outer circumference, in which the spring ring 45 is received.
  • the sections 50 can also adapt to the curvature of the Outer circumference of the internally toothed part 37g in the area of Adjusted groove base or even inwards, that is to say Groove bottom, curved opposite to the bulges 4B his.
  • the spring ring 45 is in the installed state with its Bulges 48 with friction in the groove on the inner circumference of the Race 35g while its connecting portions 50 through Spring preload with frictional engagement in the outer circumference of the internally toothed part 37g located ring groove are pressed (Fig. 8).
  • the ring gear 3 'with its widened outer circumference is received via a roller bearing 60 in a bearing ring 61 which, in the same way as in the embodiment according to FIGS. 1 to 3, can be pivoted in the housing via a bearing pin can be arranged.
  • the rolling bearing 60 is formed here by a plurality of bearing needles 62, the length of which is matched to the width of the race 35 '.
  • the race to which the ring gear is widened in the area of the outer circumference, not symmetrical with respect to the center plane of the toothing but can only be above the level of one end of the Protruding ring gear.
  • the internal gear machine in which the ring gear on its Outer circumference via sealing elements with a circumferential race is coupled (EP 789 814 A1), this race as part of the To view ring gear, which to reduce the bearing load widened compared to the internally toothed part of the ring gear can be.

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

Claims (16)

  1. Pompe à engrenages internes du type comprenant un carter (11, 12) et un train d'entraínement logé dans le carter et se composant d'un pignon (2) monté pivotant et d'une roue creuse (3) à denture interne engrenant avec le pignon, et dans lequel la roue creuse est élargie en une bague d'entraínement sur sa périphérie externe, caractérisée en ce que la bague d'entraínement (35 b - 35 g) et la portion portant la denture interne (37 b-37 g) de la roue creuse sont des éléments constructifs séparés insérés l'un dans l'autre.
  2. Pompe à engrenages internes, selon la revendication 1, caractérisée en ce que la bague d'entraínement et l'élément portant la denture interne sont insérés l'un dans l'autre avec un palier à glissement.
  3. Pompe à engrenages internes, selon la revendication 1, caractérisée en ce que la bague d'entraínement (35) est réunie solidairement en rotation avec la portion à denture interne (37) de la roue creuse.
  4. Pompe à engrenages internes, selon la revendication 3, caractérisée en ce que la bague d'entraínement est réunie à la portion à denture interne de la roue creuse par verrouillage de formes.
  5. Pompe à engrenages internes, selon la revendication 4, caractérisée en ce que la bague d'entraínement (35 c, 35 d) est réunie à la portion à denture interne (37 c, 37 d) de la roue creuse par l'intermédiaire d'au moins une cheville (38, 39).
  6. Pompe à engrenages internes, selon la revendication 3, caractérisée en ce que la bague d'entraínement est réunie avec la portion à denture interne de la roue creuse par verrouillage à force.
  7. Pompe à engrenages internes, selon la revendication 6, caractérisée en ce que la bague d'entraínement (35 g) est réunie avec la portion à denture interne (37 g) de la roue creuse par au moins une bague élastique (45), qui repose élastiquement sur la périphérie interne de la bague d'entraínement.
  8. Pompe à engrenages internes, selon la revendication 7, caractérisée en ce que la bague élastique (45) est reçue dans une rainure de la périphérie externe de la portion à denture interne et/ou de la périphérie interne de la bague d'entraínement.
  9. Pompe à engrenages internes, selon la revendication 6, caractérisée en ce que la portion à denture interne (37 f) est maintenue entre deux bagues élastiques (44) reposant chacune sur chacune de ses faces frontales et qui sont reçues dans une rainure (44) de la périphérie interne de la bague d'entraínement (35 f).
  10. Pompe à engrenages internes, selon l'une des revendications 1 à 9, caractérisée en ce que le train d'entraínement (20) est sans pièce pleine et la roue creuse est montée mobile en rotation dans une bague d'appui disposée solidaire en rotation du carter.
  11. Pompe à engrenages internes, selon l'une des revendications 1 à 9, caractérisée en ce que la roue creuse est montée mobile en rotation dans un alésage du carter.
  12. Pompe à engrenages internes, selon l'une des revendications 1 à 9, caractérisée en ce qu'un espace de compression créé entre les dentures du train d'entraínement (20) est séparé d'un espace d'aspiration par une pièce pleine.
  13. Pompe à engrenages internes, selon l'une quelconque des revendications 1 à 12, caractérisée en ce que la roue creuse est reçue sur sa périphérie externe dans un palier à glissement.
  14. Pompe à engrenages internes, selon l'une des revendications 1 à 12, caractérisée en ce que la roue creuse est reçue sur sa périphérie externe dans un palier à rouleaux.
  15. Pompe à engrenages internes, selon l'une des revendications 1 à 14, caractérisée en ce que la bague d'entraínement dépasse axialement sur au moins une des faces frontales de la roue creuse.
  16. Pompe à engrenages internes, selon l'une des revendications 1 à 15, caractérisée en ce que, sur au moins une face frontale de la roue creuse, les dentures du pignon et de la roue creuse reposent hermétiquement dans une zone de l'espace de compression recouvrant un disque axial 30, et en ce que la face frontale de la bague d'entraínement faisant face au disque axial et la face externe axiale du disque axial sont situées dans un même plan.
EP99105579A 1998-04-07 1999-03-18 Pompe à engrenages internes Expired - Lifetime EP0949419B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19815421 1998-04-07
DE19815421A DE19815421A1 (de) 1998-04-07 1998-04-07 Innenzahnradmaschine

Publications (2)

Publication Number Publication Date
EP0949419A1 EP0949419A1 (fr) 1999-10-13
EP0949419B1 true EP0949419B1 (fr) 2001-10-31

Family

ID=7863787

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99105579A Expired - Lifetime EP0949419B1 (fr) 1998-04-07 1999-03-18 Pompe à engrenages internes

Country Status (5)

Country Link
US (1) US6186757B1 (fr)
EP (1) EP0949419B1 (fr)
JP (1) JPH11324939A (fr)
KR (1) KR100373064B1 (fr)
DE (2) DE19815421A1 (fr)

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US6149415A (en) * 1999-02-11 2000-11-21 Viking Pump, Inc. Internal gear pump having a feed groove aligned with the roots of the idler teeth
DE10013760A1 (de) * 2000-03-20 2001-10-04 Continental Teves Ag & Co Ohg Innenzahnradmaschine mit einem Wälzlager gelagerten Hohlrad
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
US7220111B2 (en) * 2004-08-02 2007-05-22 Production Research, Llc Hydraulic pump
US20070177952A1 (en) * 2006-01-31 2007-08-02 The Boeing Company Hole locating device and mechanism
JP2007270678A (ja) * 2006-03-30 2007-10-18 Jtekt Corp 電動ギヤポンプ
JP2008057444A (ja) * 2006-08-31 2008-03-13 Jtekt Corp 電動ポンプユニット
DE112009001565A5 (de) * 2008-07-16 2011-03-31 Schaeffler Technologies Gmbh & Co. Kg Verdrängermaschine
DE102011001041B9 (de) * 2010-11-15 2014-06-26 Hnp Mikrosysteme Gmbh Magnetisch angetriebene Pumpenanordnung mit einer Mikropumpe mit Zwangsspuelung und Arbeitsverfahren
DE102011100105A1 (de) 2011-04-30 2012-10-31 Robert Bosch Gmbh Füllstücklose hydrostatischeInnenzahnradmaschine
DE102012207259A1 (de) * 2012-05-02 2013-11-07 Robert Bosch Gmbh Innenzahnradpumpe
JP7404047B2 (ja) * 2019-12-05 2023-12-25 東京コスモス電機株式会社 回転角度検出装置
CN113447176B (zh) * 2021-06-17 2022-04-01 人本股份有限公司 双半外圈轴承摩擦力矩检测装置

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US2053919A (en) * 1932-07-30 1936-09-08 Gulf Research Development Co Rotary pump
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US2650544A (en) * 1949-05-17 1953-09-01 John B Parsons Rotary pump assembly
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US3907470A (en) * 1971-08-19 1975-09-23 Hohenzollern Huettenverwalt Gear machine
DE2300484A1 (de) * 1973-01-05 1974-07-18 Otto Eckerle Hochdruck-zahnradpumpe
DE2606898A1 (de) * 1976-02-20 1977-09-01 Bosch Gmbh Robert Zahnradmaschine (pumpe oder motor)
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US5890885A (en) 1995-09-01 1999-04-06 Eckerle; Otto Filling member-less internal-gear pump having a sealed running ring
DE19651683A1 (de) * 1996-12-12 1998-06-18 Otto Eckerle Füllstücklose Innenzahnradpumpe

Also Published As

Publication number Publication date
DE59900366D1 (de) 2001-12-06
KR19990082985A (ko) 1999-11-25
EP0949419A1 (fr) 1999-10-13
DE19815421A1 (de) 1999-10-14
JPH11324939A (ja) 1999-11-26
KR100373064B1 (ko) 2003-02-25
US6186757B1 (en) 2001-02-13

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