EP1193395B1 - Pompe à engrenages internes - Google Patents

Pompe à engrenages internes Download PDF

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Publication number
EP1193395B1
EP1193395B1 EP01120451A EP01120451A EP1193395B1 EP 1193395 B1 EP1193395 B1 EP 1193395B1 EP 01120451 A EP01120451 A EP 01120451A EP 01120451 A EP01120451 A EP 01120451A EP 1193395 B1 EP1193395 B1 EP 1193395B1
Authority
EP
European Patent Office
Prior art keywords
housing
bearing ring
adjusting
internal
gear pump
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
EP01120451A
Other languages
German (de)
English (en)
Other versions
EP1193395A3 (fr
EP1193395A2 (fr
Inventor
Matthias Schmidl
Bernhard Rettenbacher
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1193395A2 publication Critical patent/EP1193395A2/fr
Publication of EP1193395A3 publication Critical patent/EP1193395A3/fr
Application granted granted Critical
Publication of EP1193395B1 publication Critical patent/EP1193395B1/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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance

Definitions

  • the invention is based on an internal gear pump according to the Genus of claim 1.
  • Such an internal gear pump is known from DE 38 27 573 known.
  • This internal gear pump has a housing, in to a toothed ring provided with an internal toothing a bearing ring is rotatably mounted about an axis. It is also provided with an external toothing, with the Toothed ring meshing pinion provided around an axis is rotatably mounted. The axis of rotation of the pinion is to Spindle of the toothed ring offset. The toothed ring or the Pinion is driven in rotation. Between the Pinion and the ring gear is in the radial direction with respect to the axes of rotation of the pinion and the toothed ring Consider a certain amount of play required to clamp to avoid.
  • the internal gear pump according to the invention with the features according to claim 1 has the advantage that by the Adjustment device a much finer radial play setting between the toothed ring and pinion is enabled. This allows the manufacture of the internal gear pump with larger tolerances and thus lower costs.
  • FIG. 1 shows an internal gear pump in one Cross-section along line I-I in Figure 2 and Figure 2 the Internal gear pump in a cross section along line II-II in FIG. 1
  • An illustrated in Figures 1 and 2 internal gear pump is preferably for conveying fuel from a Reservoir to a high-pressure fuel pump or a Fuel injection pump of a fuel injection system an internal combustion engine.
  • the internal combustion engine is preferably a self-igniting internal combustion engine and the is funded by the internal gear pump fuel Diesel fuel.
  • the internal gear pump has a For example, two-piece housing with a housing part 10th and one connected thereto by means of screws 12 Cover part 14 on.
  • the housing part 10 and the cover part 14 For example, metal, such as steel or aluminum exist and be designed as a casting.
  • the housing part 10 has on its side facing the cover part 14 a side Recess 16, which in cross section at least approximately is circular.
  • the lid part 14 has at its the housing part 10 side facing also a Well 20, which at least approximately congruent arranged with the recess 16 of the housing part 10 and is trained. Through the housing part 10 and the cover part 14 is with their recesses 16 and 20 in the housing a Chamber limited.
  • the cover part 14 has a pin 18 of the housing part 10 coaxial opening 22. By the Opening 22 of the cover part 14 protrudes a drive shaft 24 of outside into the housing, with its end in a bore 26 is mounted in the pin 18.
  • a pinion 30th On the pin 18 of the housing part 10 is a pinion 30th about an axis 32 rotatably mounted, with a External teeth is provided.
  • the pinion 30 is over at least one coupling element 34 rotationally with the Drive shaft 24 connected.
  • the pinion 30 is surrounding a toothed ring 36 is arranged, which with an internal toothing is provided with the external teeth of the pinion 30th combs.
  • the external teeth of the pinion 30 has a Tooth less on than the internal toothing of the toothed ring 36th
  • the toothed ring 36 has on its outer periphery a circular cross section and is above this in one Bore 38 of the toothed ring 36 surrounding bearing ring 40 to an axle 42 rotatably mounted.
  • the axis of rotation 42 of Tooth ring 36 is parallel to the axis of rotation 32 of the Zahnritzels 30, but this is by a distance a added.
  • the bore 38 is eccentric in the bearing ring 40 to whose circular outer cross section is formed.
  • the Pinion 30 and the toothed ring 36 are in the recesses 16,20 between the housing part 10 and the cover part 14 in Direction of its axis of rotation 32 and 42 with little play arranged.
  • the pinion 30, the toothed ring 36 and the Bearing ring 40 are preferably made of steel, for example Sintered steel.
  • the bearing ring 40 faces the depressions 16 and 20 the housing part 10 and the cover part 14 a something smaller cross-section on.
  • the bearing ring 40 has in his Outer jacket two axially staggered annular grooves 44th on, in each of which an elastic ring 46 is inserted.
  • the bearing ring 40 rests on the rings 46, which over the Outer shell of the bearing ring 40 protrude to the Inner lateral surfaces of the recesses 16 and 20 from.
  • the Rings 46 are between the outer shell of the bearing ring 40 and the Inner edges of the recesses 16,20 clamped.
  • the Pinion 30 is about the drive shaft 24 about the axis 32nd driven in rotation.
  • the Suction side 48 is from the pressure side 49 through the on each other sliding teeth of the pinion 30 and of the toothed ring 36 separately. It is therefore necessary that between the teeth of the pinion 30 and the Tooth ring 36 the lowest possible radial clearance b is present and the axis of rotation 32 of the pinion 30 and the axis of rotation 42 of the toothed ring 36 in the radial direction the axes of rotation 32,42 are aligned exactly to each other.
  • the bearing ring 40 is a Adjusting device 50 assigned by means of the bearing ring 40 and thus the mounted in this toothed ring 36 in one radial direction with respect to the axes of rotation 32,42 to a Adjustment movable and in a set position is blockable.
  • the direction in which the bearing ring 40 is movable by means of the adjusting device is in Figure 2 illustrated by the double arrow 52.
  • the adjustment 52 is both to the axis of rotation 42 of the toothed ring 36 and the Rotary axis 32 of the pinion 30 radially.
  • the Adjustment device 50 is on the axis of rotation 42 of the Tooth ring 36 opposite side of the axis of rotation 32 of the Zahnritzels 30 arranged.
  • the adjusting device 50 has a with the bearing ring 40th firmly connected adjusting 54 on.
  • the adjusting element For example, with one of these protruding Bolt 56 in a bore 58 in the outer casing of the bearing ring 40 screwed between the two annular grooves 44 or pressed.
  • the adjusting element 54 has a with the Bolt 56 preferably integral slide-shaped Section 60 on.
  • In the housing part 10 and the cover part 14th is in each case a laxative of their depression 16 and 20 respectively Groove 62 formed, wherein the depth of the grooves 62 in the direction the axes of rotation 32,42 is less than the depth of Depressions 16,20.
  • the grooves 62 have starting from the Edge of the recesses 16,20 first a portion 62a with a small width and then with an area 62b larger width.
  • the slider portion 60 of the adjustment 54 is slidable between the grooves 62 in their areas 62b guided.
  • the width of the slider portion 60 is little smaller than the width of the portions 62b of the grooves 62, so that the slider portion 60 is guided with little play.
  • In the adjustment 52 is the length of the areas 62 b of Grooves 62 greater than the length of the slide portion 60, so that this in the adjustment direction 52 in the areas 62b can be moved.
  • the areas 62b of the grooves 62 and the slide portion 60 of the adjusting 54 can in Cross section as shown in Figure 2, for example, approximately be formed rectangular, the corners rounded are.
  • the bolt 56 of the adjusting element 54 passes through the Areas 62 a of the grooves 62 therethrough.
  • the adjusting element 54 has in its slide portion 60th a recess 64, for example in the form of an opening or a hole.
  • the recess 64 extends in Direction of the axes of rotation 32,42.
  • a fixing element 66 which may be used as an in a threaded bore 68 in the housing part 10 screwed Adjusting screw is formed.
  • the adjusting screw 66 protrudes on the outside of the housing part 10 and is there accessible, so that at this by means of a tool attacked and this can be twisted.
  • the Adjusting screw 66 may at her from the housing part 10th projecting end, for example, a cross or Phillips in which a corresponding blade of a Screwdrivers can be introduced.
  • the adjusting screw 66 due to Threaded connection with the housing part 10 in the direction of her Longitudinal axis 67 moves.
  • the adjusting screw 66 can self-locking thread to ensure that not inadvertently, for example as a result of occurring during operation of the internal gear pump Shaking, can twist what an adjustment of the radial play would result.
  • the Adjusting screw 66 also by means of a on the Housing part 10 projecting end portion screwed Locknut to be secured against rotation.
  • the recess 64 has a radial direction to the Rotary axes 32,42 side facing surface 70, at the the screw 66 with her in the recess 64th engaging end portion is applied.
  • the side surface 70 of Recess 64 is to the longitudinal axis 67 of the screw 66th arranged inclined so that the side surface 70 for Lid 14 towards the longitudinal axis 67 approaches.
  • the Recess 64 of the adjustment 54 for example as an at least approximately conical bore be formed, whereby the inclined arrangement of Side surface 70 is reached. It can also be provided that only the side surface 70 of the recess 64 through appropriate processing by means of a grinding or Milling tool is arranged inclined.
  • the side surface 70 the recess 64 may also be formed as an inclined plane be.
  • Adjusting screw 66 By rotation of the Adjusting screw 66 can thus from outside the housing and after complete assembly of internal gear pump the radial clearance between the toothed ring 36 and the pinion 30th be set to the required value.
  • a restoring force the bearing ring 40 is replaced by the elastically deformed rings 46 generated so that when unscrewing the screw 66, the side surface 70 of the recess 64 of the adjusting 54 remains in contact with the adjusting screw 66, since the Adjustment element 54 via the bearing ring 40 to the rotation axis 42nd of the toothed ring 36 is pressed.
  • unscrewing the adjusting screw 66 thus becomes the bearing ring 40 in FIG. 2 moves to the right and increases the radial clearance b.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)

Claims (8)

  1. Pompe à engrenage intérieur comportant un boítier (10, 14) ayant :
    une couronne dentée (36) à denture intérieure montée à rotation autour d'un axe (42) dans le boítier (10, 14) par l'intermédiaire d'une bague formant palier (40) ; et
    une roue dentée (30) munie d'une denture extérieure, tournant autour d'un axe (32) dans le boítier (10, 14) ;
    la roue dentée (30) ou la couronne dentée (36) étant entraínées en rotation et l'axe de rotation (42) de la couronne dentée (36) est décalé par rapport à l'axe de rotation (32) de la roue dentée (30),
    caractérisée en ce que
    un dispositif de réglage (50) est associé à la bague de palier (40) permettant de déplacer la bague de palier (40) dans une direction radiale (52) par rapport à l'axe de rotation (42) de la couronne dentée (36) dans le boítier (10, 14) pour effectuer un réglage et bloquer en position réglée.
  2. Pompe à engrenage intérieur selon la revendication 1,
    caractérisée en ce que
    le dispositif de réglage (50) comporte un élément de réglage (54) relié à la bague formant palier (40), guidé en coulissement dans la direction radiale (52) dans le boítier (10, 14), et un élément de blocage (66), relié au boítier (10) et accessible à partir du côté extérieur de ce boítier (10), agit sur cet élément de réglage et peut coulisser avec cet élément de réglage (54) dans la direction radiale (52) et être bloqué en position réglée.
  3. Pompe à engrenage intérieur selon la revendication 2,
    caractérisée en ce que
    l'élément de réglage (54) comporte une cavité (64) dans laquelle pénètre l'élément de blocage (66), transversalement à la direction radiale (52) ;
    l'élément de blocage (66) s'appliquant contre une surface latérale (70) de la cavité (64), tourné radialement vers l'axe de rotation (42) de la couronne dentée (36) ou s'écartant de celle-ci ;
    l'élément de blocage (66) est relié au boítier (10) de manière mobile dans la direction de son axe longitudinal (67) ; et
    la face latérale (70) de la cavité (64) est inclinée par rapport à l'axe longitudinal (67) de l'élément de blocage (66) pour que lors du mouvement de l'élément de blocage (66) dans la direction de son axe longitudinal (67), la surface latérale inclinée (70) de la cavité (64) entraíne un déplacement de l'élément de réglage (54) dans la direction radiale (52).
  4. Pompe à engrenage intérieur selon la revendication 3,
    caractérisée en ce que
    la cavité (64) de l'élément de réglage (54) est au moins sensiblement de forme conique.
  5. Pompe à engrenage intérieur selon la revendication 3 ou 4,
    caractérisée en ce que
    l'élément de blocage (66) est réalisé sous la forme d'une vis de réglage vissée dans un taraudage (68) du boítier (10), et le mouvement de rotation de cette vis se traduit par un mouvement de déplacement en direction de son axe longitudinal (67).
  6. Pompe à engrenage intérieur selon l'une des revendications précédentes,
    caractérisée en ce que
    la bague formant palier (40) est montée par l'intermédiaire d'au moins une bague élastique (46) serrée entre son enveloppe extérieure et le boítier ( 10, 14), cette bague élastique générant une force de rappel agissant sur la bague de palier (40), et s'opposant à la force de réglage exercée par le dispositif de réglage (50) sur la bague de palier (40).
  7. Pompe à engrenage intérieur selon la revendication 6,
    caractérisée en ce qu'
    au moins une bague (46) sert d'élément d'étanchéité pour le boítier (10, 14).
  8. Pompe à engrenage intérieur selon l'une des revendications précédentes,
    caractérisée en ce que
    la direction (52) dans laquelle la bague de palier (40) est déplacée par le dispositif de réglage (50) est radiale à la fois par rapport à l'axe de rotation (42) de la bague dentée (36) et par rapport à l'axe de rotation (32) de la roue dentée (30).
EP01120451A 2000-09-27 2001-08-28 Pompe à engrenages internes Expired - Lifetime EP1193395B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10047738 2000-09-27
DE10047738A DE10047738A1 (de) 2000-09-27 2000-09-27 Innenzahnradpumpe

Publications (3)

Publication Number Publication Date
EP1193395A2 EP1193395A2 (fr) 2002-04-03
EP1193395A3 EP1193395A3 (fr) 2003-05-07
EP1193395B1 true EP1193395B1 (fr) 2004-11-03

Family

ID=7657741

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01120451A Expired - Lifetime EP1193395B1 (fr) 2000-09-27 2001-08-28 Pompe à engrenages internes

Country Status (4)

Country Link
US (1) US6568930B2 (fr)
EP (1) EP1193395B1 (fr)
JP (1) JP4843168B2 (fr)
DE (2) DE10047738A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10109769A1 (de) * 2001-03-01 2002-09-05 Eckerle Ind Elektronik Gmbh Füllstücklose Innenzahnradpumpe
DE10240287A1 (de) * 2002-08-31 2004-03-11 Continental Teves Ag & Co. Ohg Pumpen-Aggregat
WO2005080755A1 (fr) * 2004-01-30 2005-09-01 Performance Pumps, Llc. Pompes de type gerotor perfectionnees
DE102004020357A1 (de) * 2004-04-26 2005-11-17 Sauer-Danfoss Aps Verfahren und Hydromaschine zum Steuern einer Verdrängung
WO2005119066A2 (fr) * 2004-06-04 2005-12-15 Entek Manufacturing Inc. Engrenage convenant pour l'utilisation dans une pompe a engrenages
DE102004036106A1 (de) 2004-07-24 2006-03-16 Ina-Schaeffler Kg Periodisch beaufschlagbarer Stößel für einen Ventil- oder Pumpentrieb
KR100662806B1 (ko) 2005-09-30 2006-12-28 현담산업 주식회사 자동차용 전동기식 연료펌프
WO2007093592A1 (fr) * 2006-02-15 2007-08-23 Continental Automotive Gmbh Pompe rotative et procédé de fabrication d'un BOITIER de pompe rotative
WO2007120503A2 (fr) * 2006-03-31 2007-10-25 Metaldyne Company, Llc Pompe à déplacement variable dotée d'un rotor denté
JP4966638B2 (ja) * 2006-12-18 2012-07-04 日立オートモティブシステムズ株式会社 オイルポンプ及びオイルポンプの組立方法
DE102008003843A1 (de) * 2008-01-10 2009-07-16 Robert Bosch Gmbh Förderaggregat
DE102015002352A1 (de) * 2014-12-17 2016-06-23 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Elektrische Ölpumpe, insbesondere für ein Kraftfahrzeug
DE102015213387A1 (de) * 2015-07-16 2017-01-19 Robert Bosch Gmbh Rotationskolbenpumpe
JP6430557B2 (ja) * 2017-03-02 2018-11-28 日本電産トーソク株式会社 電動オイルポンプ
DE102019002949B4 (de) * 2019-04-24 2021-02-25 Bastian Voigt Innenzahnradpumpe

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2792788A (en) * 1957-05-21 eames
US1505707A (en) * 1923-10-24 1924-08-19 Hill Compressor & Pump Company Rotary pump
US2822124A (en) * 1956-02-07 1958-02-04 Allied Prod Corp Gear type fluid pump with adjustable gear sets
JPS4329251Y1 (fr) * 1965-06-30 1968-12-02
GB1233376A (fr) * 1967-11-17 1971-05-26
DE2705256A1 (de) * 1977-02-09 1978-08-10 Bosch Gmbh Robert Zahnradmaschine (pumpe oder motor)
DE2808731A1 (de) 1978-03-01 1979-09-06 Bosch Gmbh Robert Verfahren zum betrieb einer kraftstoffeinspritzanlage und kraftstoffeinspritzanlage
JPS63223381A (ja) * 1987-03-11 1988-09-16 Mitsubishi Metal Corp 内接型ギヤポンプ
JPH0633776B2 (ja) * 1987-11-09 1994-05-02 株式会社ユニシアジェックス 歯車式ポンプ
DE19517296C2 (de) * 1995-05-11 2000-08-03 Otto Eckerle Füllstücklose Innenzahnradpumpe

Also Published As

Publication number Publication date
JP2002155872A (ja) 2002-05-31
DE50104369D1 (de) 2004-12-09
US20020110468A1 (en) 2002-08-15
JP4843168B2 (ja) 2011-12-21
EP1193395A3 (fr) 2003-05-07
US6568930B2 (en) 2003-05-27
DE10047738A1 (de) 2002-04-11
EP1193395A2 (fr) 2002-04-03

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