EP1930595A2 - Agrégat de transport - Google Patents

Agrégat de transport Download PDF

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Publication number
EP1930595A2
EP1930595A2 EP07117869A EP07117869A EP1930595A2 EP 1930595 A2 EP1930595 A2 EP 1930595A2 EP 07117869 A EP07117869 A EP 07117869A EP 07117869 A EP07117869 A EP 07117869A EP 1930595 A2 EP1930595 A2 EP 1930595A2
Authority
EP
European Patent Office
Prior art keywords
gear
internal gear
external gear
pair
internal
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
EP07117869A
Other languages
German (de)
English (en)
Other versions
EP1930595A3 (fr
EP1930595B1 (fr
Inventor
Heinz Siegel
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 EP1930595A2 publication Critical patent/EP1930595A2/fr
Publication of EP1930595A3 publication Critical patent/EP1930595A3/fr
Application granted granted Critical
Publication of EP1930595B1 publication Critical patent/EP1930595B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04C2/084—Toothed wheels

Definitions

  • oil pumps which are used for example in the context of ESP control systems that are used for vehicle dynamics control, come as oil pumps an internally toothed precharge, which is designed according to the gerotor principle used.
  • the pair of gears used in this internally toothed precharge pump includes a pinion and a ring gear enclosing it. Both the pinion and the ring gear represent sintered components which are subjected to a curing process after sintering. Due to the manufacturing process sintering, however, a different degree of scattering radial clearance arises between the tooth heads or tooth flanks due to the prevailing sinter tolerances. This has an influence on the efficiency and the achievable delivery rate of this pre-charging pump used on ESP systems, for example, which is designed as an internal gear pump. If the sintering tolerances fluctuate very much, the delivery rate of the internally toothed precharge pump inevitably fluctuates very strongly, which represents a rather unsatisfactory overall situation.
  • the pinion and the surrounding ring gear of a delivery unit such as a precharge pump for ESP systems or an oil pump for internal combustion engines are sintered or alternatively manufactured by way of metal powder injection molding. Both the pinion and the ring gear are then subjected to a hardening process.
  • the toothing between the sintered and hardened pinion and this surrounding also sintered and hardened ring gear is tapered. This means that the lying on the end faces of the tooth tips or the tooth flanks are on different pitch circles with respect to the pinion and the ring gear.
  • the gear pairs i. the combination of ring gear and pinion, if necessary, the pinion can be processed simultaneously on suitable grinding machines at the same time, as the parts produced by means of the sintering process or by means of metal injection molding technology usually represent tool-falling parts.
  • FIG. 1 is a plan view of a pair of gears, an internal gear and an external gear comprising, refer to.
  • a gear pair 10 as shown in FIG. 1 which can be used for example within an oil pump, comprises an internal gear 12 and an external gear 14.
  • the internal gear 12 has a driving teeth 18 which meshes with a counter-toothing 20 of the shaft 16.
  • the shaft 16 and the internal gear 12 are in an eccentricity e, see.
  • Reference numeral 22 is mounted with respect to an axis 44 of the external gear 14.
  • FIG. 1 is a plan view of a first plan side 24 of the interconnected gear pair 10, ie, the internal gear 12 and the external gear 14 is shown.
  • the internal gear 12 is free of play in the ring gear representing external gear 14 joined.
  • the internal gear 12 has a number of teeth 28, each having tooth heads 30.
  • a radial play which is established between the tooth heads 30 and corresponding tooth heads on the inner circumference of the external gearwheel 14 is indicated by reference numeral 32.
  • a first plan side 24 of the gear pair 10 is formed by the first planar side 34 of the internal gear 12 and the first planar side 36 of the external gear 14.
  • FIG. 2 Shown according to FIG. 2 is a cut through the in FIG. 1 in the assembled state shown gear pair 10 along the cutting path II - II.
  • FIG. 2 shows that the internal gear 12 is inserted into the external gear 14 of the gear pair 10. From the sectional view according to FIG. 2 that the in FIG. 1 represented sectional course II - II, it can further be seen that the first plane side 24 of the gear pair 10, the first planar side 34 of the internal gear 12 and the first planar side 36 of the external gear 14 includes. Thus, the first plan side 24 of the gear pair disintegrates into two plan sides of two separate components. From the illustration according to FIG. 2 also shows that the first planar side 34 of the internal gear 12 projects beyond a projection c over the first planar side 36 of the external gear 14.
  • the second plan side 26 of the joined gear pair 10 represented by a second plan side 38, the internal gear 12 and by a second plan side 40, which by the external gear 14 of the gear pair 10 for an oil pump in in FIG. 1 formed, joined state formed.
  • the internal gear 12 is arranged with an undersize d with respect to its second plane side 38.
  • the second plan side 38 of the internal gear 12 is about the undersize d under the second plan side 40 of the external gear 14 of the gear pair 10 in the assembled state.
  • FIG. 2 shown, joined state with the above-described supernatant c or the undersize d represents the state in which an assembled gear pair 10, the internal gear 12 and the external gear 14 comprising frontally ground flat. Before the surface grinding process of the plan sides 24, 26 of the gear pair 10, the components internal gear 12 and external gear 14 are hardened.
  • a flat grinding of the first plane side 24 of the gear pair 10 in the non-backlash state of the internal gear 12 and external gear 14 is carried out.
  • the first plan page 24 is removed by the grinding amount a, so that in in FIG. 2 State shown a ground flat, common first plan side 24 on the gear pair 10, that is, both the internal gear 12 and the external gear 14 is obtained.
  • a flat grinding the second plan page 26 is generated, ie the undersize d as shown in FIG FIG.
  • the common axial dimension corresponds to the axial dimension H 1 , which is formed by the removal of material on the joined gear pair 10 by the grinding a or the grinding b, can after the separation of the components 12, 14 after the surface grinding a further grinding of the internal gear 12 done.
  • an axial play of the order of a few microns, preferably within the range between 3 .mu.m and 6 .mu.m can be achieved on the internal gear 12, so that the possibly this further grinding operation to be subjected to internal gear 12 has a also called Ritzel Adjustnexcellent axial dimension H 2 , which of the after the grinding process of the plan sides 24, 26 obtained common axial dimension H 1 of the two components joined together inner gear 12 and outer gear 14 deviates by the few microns mentioned.
  • first pitch circle diameter 48 lying on the first plan side 24 of the joined gear pair 10 exceeds the second pitch circle diameter 50 which is formed on the rear side, ie the second plane side 26 of the joined gear pair 10.
  • the diameter difference between the Pitch diameters 48, 50 results depending on the selected cone angle of the conical toothing 46 according to the sectional view in FIG. 2 ,
  • the back grinding of the inside arranged internal gear 12 by the said measure preferably lying in the range between 3 .mu.m and 6 .mu.m, also omitted.
  • the dimension H 2 corresponds to the common axial dimension H 1 of the joined components internal gear 12 and external gear 14.
  • the substantially reduced radial clearance 32 on the mutually contacting tooth heads 30 of the internal gear 12 and the external gear 14 is required because between the tooth tips 30 line contact occurs and therefore no gap coverage occurs.
  • a gap overlap adjusts itself to the axially sealing surfaces of the gearwheel pair 10, ie its end faces 12 and 14 and the inner sides of the pump housing which are respectively opposite thereto. The longer the gap overlap between the face sides 24, 26, equivalent to the first face side 34 of the internal gear 12, the first face 36 of the external gear 14, which represent the first face side 24 and the second face 38 of the internal gear 12, which together with the second face side 40 of the external gear 14 represent the second plan side 26 of the gear pair 10 and the opposite surfaces of the pump housing, a greater sealing effect can be achieved.
  • the solution proposed by the invention provides a gear pair 10 available, which, for example, for an oil pump or for a feed pump for a Hydraulic fluid for a manual transmission, to use application examples, can be used.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • General Details Of Gearings (AREA)
EP07117869.3A 2006-12-01 2007-10-04 Agrégat de transport Expired - Fee Related EP1930595B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200610056845 DE102006056845A1 (de) 2006-12-01 2006-12-01 Förderaggregat

Publications (3)

Publication Number Publication Date
EP1930595A2 true EP1930595A2 (fr) 2008-06-11
EP1930595A3 EP1930595A3 (fr) 2015-03-18
EP1930595B1 EP1930595B1 (fr) 2016-12-14

Family

ID=39198189

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07117869.3A Expired - Fee Related EP1930595B1 (fr) 2006-12-01 2007-10-04 Agrégat de transport

Country Status (2)

Country Link
EP (1) EP1930595B1 (fr)
DE (1) DE102006056845A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012193769A (ja) * 2011-03-15 2012-10-11 Asmo Co Ltd 内接型遊星歯車減速機及び歯車ポンプ
WO2011128218A3 (fr) * 2010-04-16 2013-03-07 Robert Bosch Gmbh Pompe à engrenage
WO2013013883A3 (fr) * 2011-07-28 2013-08-22 Zf Friedrichshafen Ag Pompe à engrenage
JP2013199849A (ja) * 2012-03-23 2013-10-03 Hitachi Automotive Systems Ltd 内接歯車ポンプ

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008054755A1 (de) 2008-12-16 2010-06-17 Robert Bosch Gmbh Förderaggregat
DE102008054767A1 (de) 2008-12-16 2010-06-17 Robert Bosch Gmbh Förderaggregat

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3364162D1 (en) * 1982-04-07 1986-07-24 Sumitomo Heavy Industries Planetary rotation machine
DE9405502U1 (de) * 1994-03-26 1994-07-28 WITEG Wissenschaftlich- Technische Gesellschaft mbH Werkstoffe und Baugruppen, 01640 Coswig Präzisionsflüssigkeitspumpe aus Formteilen mit großer Toleranzbreite
JP2000027769A (ja) * 1998-07-08 2000-01-25 Unisia Jecs Corp 内接型歯車ポンプまたはモータおよびその製造方法

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011128218A3 (fr) * 2010-04-16 2013-03-07 Robert Bosch Gmbh Pompe à engrenage
JP2012193769A (ja) * 2011-03-15 2012-10-11 Asmo Co Ltd 内接型遊星歯車減速機及び歯車ポンプ
WO2013013883A3 (fr) * 2011-07-28 2013-08-22 Zf Friedrichshafen Ag Pompe à engrenage
CN103717900A (zh) * 2011-07-28 2014-04-09 Zf腓德烈斯哈芬股份公司 变速器泵
JP2013199849A (ja) * 2012-03-23 2013-10-03 Hitachi Automotive Systems Ltd 内接歯車ポンプ

Also Published As

Publication number Publication date
EP1930595A3 (fr) 2015-03-18
EP1930595B1 (fr) 2016-12-14
DE102006056845A1 (de) 2008-06-05

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