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EP0949419A1 - Pompe à engrenages internes - Google Patents

Pompe à engrenages internes Download PDF

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Publication number
EP0949419A1
EP0949419A1 EP99105579A EP99105579A EP0949419A1 EP 0949419 A1 EP0949419 A1 EP 0949419A1 EP 99105579 A EP99105579 A EP 99105579A EP 99105579 A EP99105579 A EP 99105579A EP 0949419 A1 EP0949419 A1 EP 0949419A1
Authority
EP
European Patent Office
Prior art keywords
ring gear
race
machine according
internal gear
ring
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
EP99105579A
Other languages
German (de)
English (en)
Other versions
EP0949419B1 (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 housed in the housing Running group consisting of a rotatable pinion and an internally toothed, meshing with the pinion Ring gear.
  • 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 Internal gear machine determined.
  • the object of the present invention is therefore a Internal gear machine of the type described above too design that constructively greater freedom for the There is a choice of delivery or operating pressure.
  • this object is achieved in that the Ring gear widened to a race on its outer circumference is.
  • the ring gear is wider on its outer circumference than in the area the gearing is between the gearing hydraulic prevailing from pinion and ring gear Compressive forces through which the ring gear in its storage is pressed, spread over a larger storage area, which reduces the specific bearing load.
  • the Widening of the ring gear on its outer circumference to one Race can be achieved in a variety of ways. From It is only important that the part forming the outer circumference the ring gear as a race together with the Internal toothing of the ring gear-bearing part as a unit circulates.
  • the part forming the race can be combined with the the part having internal teeth can be in one piece; of the separately manufactured race can also with the Part with internal toothing form-fitting and / or be non-positively connected.
  • Adequate Frictional contact arises when operating the Internal gear machine then when the internal gear supporting part of the ring gear with its peripheral surface the hydraulic forces in the teeth on the Inner circumference of the race is pressed. Because in operation only the bearing friction torque has to be overcome in order to Race together with the bearing that supports the internal toothing Allowing part to rotate is sufficient in this way achieved friction. Therefore, it is also an embodiment for the widened to a race on the outer circumference Ring gear conceivable, only for the time of pressureless start of the internal gear machine a positive connection between the race and the one that supports the internal toothing Part of the ring gear.
  • the internal gear machine shown in FIGS. 1 to 3 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 (in FIG Cross-hatching), which is in a bearing ring 4 recorded and rotatably mounted therein.
  • the pinion 2 and the ring gear 3 are, as shown in Fig. 1, relative to each other with an eccentricity e.
  • 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 the gears ahead of each other.
  • the Toothings of the pinion 2 and the ring gear 3 mesh in one way to the other on the left in FIG. 1 in the area of the dividing line A, the teeth of the pinion 2 are fully in engage the tooth gaps of the ring gear 3 and at the Tooth flanks rest 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 embodiment shown three 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 in can be effected in a known manner.
  • the tooth flanks as involute curves are exemplary embodiments formed, the tooth tips to achieve a Rolling and sliding contact rounded for the purpose of sealing are.
  • the number of teeth of the ring gear 3 differs in this embodiment from that of the pinion 2 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 of the bearing ring 4 added.
  • the axial groove is the shape of the bearing pin 16 adapted and also partially cylindrical.
  • the one in the axial groove engaging bearing pin 16 therefore forms for the bearing ring 4 one parallel to the axes of pinion 2 and ring gear 3 extending pivot axis about which the bearing ring 4 in Framework of the available radial play in the Housing bore 15 is pivotable.
  • this pivot axis lies in a quadrant of the Bearing rings 4, which is between the non-invasive Ring gear area and the center of the pressure chamber extends.
  • the openings 8 lead from the pressure chamber to the pressure outlet channel, not shown in the Housing cover 12.
  • the housing cover 12 has diametrical a suction inlet duct 9 opposite the pressure outlet duct on, which at its mouth to a suction field 10th expanded.
  • a pressure field 31 is indicated by that the respective axial disk 30 from the outside against the Effect of the inner pressure field 7 is applied so that the axial washer sealing contact in all operating states with the pinion 2 and the ring gear 3 maintained. education and mode of action of the pressure fields on axial washers well-known and therefore need at this point no further explanation.
  • Each thrust washer 30 supports itself for the purpose of it Secure 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 the housing cover 12 used pin 34 from.
  • the pins 34 each protrude into a blind hole in the outer end face of the axial disks 30 and are thereby held axially.
  • Variants are also on the housing by means of the pins 34 conceivable, the movement of the axial discs 30 together allow with pinion 2, ring gear 3 and bearing ring 4 (cf. EP 97-121 424.2 A1).
  • Fig. 4 shows the internal gear machine according to the Fig. 1 to 3 running group 20 used, the the pinion 2 and the ring gear 3.
  • the ring gear 3 has an outer part designed into a race 35, which forms the outer circumference 36 of the ring gear 3, and one the part 37 supporting the internal toothing.
  • the race 35 of the ring gear 3 exceeds Width of the part 37 bearing the internal toothing significant; the raceway width is in this Embodiment about three times the width of the internally toothed part 37.
  • the race 35b and the internally toothed part 37b separate components that joined together by pressing, shrinking or gluing are.
  • This embodiment allows a different one Choice of materials for the race and the internal gear Part that better adapt to the required storage or Combing properties allowed.
  • race form 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 radial from Outer circumference 36c forth in the internally toothed part 37c pressed-in pin 38.
  • the internally toothed part 37d with the race 35d an axially pressed-in cylindrical pin 39 is connected, which in a correspondingly partially cylindrical groove 40 of Race 35d and an unspecified, 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 radial from Outer circumference 36c forth in the internally toothed part 37c pressed-in pin 38.
  • the internally toothed part 37d with the race 35d an axially pressed-in cylindrical pin 39 is connected, which in a correspondingly partially cylindrical groove 40 of Race 35d and an unspecified, also partially cylindrical groove
  • the inner circumference of the Race 35e a shoulder 41 on which the internally toothed part 37e rests with its front edge and by a welding spot or a part or all of it circumferential weld 42 is attached.
  • the inner circumference of the race 35f two at an axial distance from each other arranged annular grooves 43, in each of which Spring ring 44 is broken. The facing each other Edges of the ring grooves 43 are spaced from one another, the maximum of the width of the internally toothed part 37f corresponds, which ensures that the spring washers 44 under frictional engagement on the front edges of the internally toothed Fit part 37f and thereby hold it.
  • the Race 35g with the internally toothed part 37g over a Coupled spring ring 45 the shape of which is shown in FIG. 7.
  • the race 35g on its inner circumference and the internally toothed part 37g on its outer circumference in each case a circumferential annular groove in which the spring ring 45th is recorded.
  • 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 by spring preload with friction in the am
  • the outer circumference of the internally toothed part 37g Ring groove are pressed (Fig. 8).
  • the embodiment of the ring gear according to FIGS. 9 and 10 corresponds to that of variant 5a, in which race and internally toothed part of the ring gear are in one piece.
  • this is Ring gear 3 'with its widened outer circumference over a Rolling bearing 60 received in a bearing ring 61, which in the same way as in the embodiment according to FIG. 1 up to 3 can be pivoted in the housing using a bearing pin can be arranged.
  • the rolling bearing 60 is here by formed a plurality of bearing needles 62, the length of which the width of the race 35 'is matched.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
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
DE19815421A DE19815421A1 (de) 1998-04-07 1998-04-07 Innenzahnradmaschine
DE19815421 1998-04-07

Publications (2)

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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10013760A1 (de) * 2000-03-20 2001-10-04 Continental Teves Ag & Co Ohg Innenzahnradmaschine mit einem Wälzlager gelagerten Hohlrad
WO2010006575A2 (fr) * 2008-07-16 2010-01-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Machine du type volumétrique
WO2012066483A2 (fr) * 2010-11-15 2012-05-24 Hnp Mikrosysteme Gmbh Ensemble de pompes entraîné magnétiquement doté d'une micropompe à lavage forcé et procédé de fonctionnement

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
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

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1990750A (en) * 1931-03-02 1935-02-12 Gulf Res & Dev Corp Variable volume pump and hydraulic transmission
US2053919A (en) * 1932-07-30 1936-09-08 Gulf Research Development Co Rotary pump
US2650544A (en) * 1949-05-17 1953-09-01 John B Parsons Rotary pump assembly
US3327636A (en) * 1965-04-30 1967-06-27 Ashtabula Bow Socket Company Fluid pump or motor structure
US3722329A (en) * 1970-05-07 1973-03-27 Huck Mfg Co Fastener installation tool
EP0789814A1 (fr) 1995-09-01 1997-08-20 Otto Eckerle Pompe a engrenages a denture interieure sans piece intercalaire
DE19651683A1 (de) 1996-12-12 1998-06-18 Otto Eckerle Füllstücklose Innenzahnradpumpe

Family Cites Families (16)

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US3118387A (en) * 1964-01-21 Reveksible gear pump
GB453044A (en) * 1935-07-31 1936-09-03 Chan Ting Yu Improvements in and relating to electric battery lamps
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)
US4117025A (en) * 1977-07-20 1978-09-26 Phillips Petroleum Company Process for purifying diolefin
JPS5844875B2 (ja) * 1978-06-30 1983-10-05 トキコ株式会社 歯車ポンプ
JPS597036B2 (ja) * 1978-08-31 1984-02-16 株式会社不二越 内接ギヤポンプモ−タ
DE3723557A1 (de) * 1987-07-16 1989-01-26 Eckerle Otto Gmbh & Co Innenzahnradmaschine
DE3900263A1 (de) * 1989-01-07 1990-07-12 Bosch Gmbh Robert Aggregat zum foerdern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges
DE4024628A1 (de) * 1990-08-03 1992-02-06 Bosch Gmbh Robert Aggregat zum foerdern von kraftstoff aus einem vorratstank zu brennkraftmaschine eines kraftfahrzeugs
JPH04105986A (ja) * 1990-08-28 1992-04-07 Canon Inc 光記録媒体及びこれを用いる記録及び消去方法
JP3168184B2 (ja) * 1991-05-13 2001-05-21 ジヤトコ・トランステクノロジー株式会社 自動変速機
DE4336966A1 (de) * 1993-10-29 1995-05-04 Otto Eckerle Innenzahnradmaschine
DE4401783A1 (de) * 1994-01-21 1995-07-27 Cerasiv Gmbh Förderaggregat mit einer keramischen Innenzahnradpumpe
DE4421255C1 (de) * 1994-06-17 1995-06-29 Otto Eckerle Füllstücklose Innenzahnradpumpe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1990750A (en) * 1931-03-02 1935-02-12 Gulf Res & Dev Corp Variable volume pump and hydraulic transmission
US2053919A (en) * 1932-07-30 1936-09-08 Gulf Research Development Co Rotary pump
US2650544A (en) * 1949-05-17 1953-09-01 John B Parsons Rotary pump assembly
US3327636A (en) * 1965-04-30 1967-06-27 Ashtabula Bow Socket Company Fluid pump or motor structure
US3722329A (en) * 1970-05-07 1973-03-27 Huck Mfg Co Fastener installation tool
EP0789814A1 (fr) 1995-09-01 1997-08-20 Otto Eckerle Pompe a engrenages a denture interieure sans piece intercalaire
DE19651683A1 (de) 1996-12-12 1998-06-18 Otto Eckerle Füllstücklose Innenzahnradpumpe

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10013760A1 (de) * 2000-03-20 2001-10-04 Continental Teves Ag & Co Ohg Innenzahnradmaschine mit einem Wälzlager gelagerten Hohlrad
WO2010006575A2 (fr) * 2008-07-16 2010-01-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Machine du type volumétrique
WO2010006575A3 (fr) * 2008-07-16 2010-08-05 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Machine du type volumétrique
WO2012066483A2 (fr) * 2010-11-15 2012-05-24 Hnp Mikrosysteme Gmbh Ensemble de pompes entraîné magnétiquement doté d'une micropompe à lavage forcé et procédé de fonctionnement
WO2012066483A3 (fr) * 2010-11-15 2013-06-27 Hnp Mikrosysteme Gmbh Ensemble de pompes entraîné magnétiquement doté d'une micropompe à lavage forcé et procédé de fonctionnement
CN103348141A (zh) * 2010-11-15 2013-10-09 Hnp微系统有限责任公司 具有带有强制冲洗的微型泵的磁驱动泵装置以及工作方法
US10012220B2 (en) 2010-11-15 2018-07-03 Hnp Mikrosysteme Gmbh Magnetically driven pump arrangement having a micropump with forced flushing, and operating method

Also Published As

Publication number Publication date
JPH11324939A (ja) 1999-11-26
US6186757B1 (en) 2001-02-13
DE19815421A1 (de) 1999-10-14
KR100373064B1 (ko) 2003-02-25
EP0949419B1 (fr) 2001-10-31
KR19990082985A (ko) 1999-11-25
DE59900366D1 (de) 2001-12-06

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