WO2016055255A1 - Différentiel - Google Patents

Différentiel Download PDF

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Publication number
WO2016055255A1
WO2016055255A1 PCT/EP2015/071585 EP2015071585W WO2016055255A1 WO 2016055255 A1 WO2016055255 A1 WO 2016055255A1 EP 2015071585 W EP2015071585 W EP 2015071585W WO 2016055255 A1 WO2016055255 A1 WO 2016055255A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
gears
differential gear
gear according
formations
Prior art date
Application number
PCT/EP2015/071585
Other languages
German (de)
English (en)
Inventor
Rudolf Glassner
Original Assignee
Engineering Center Steyr Gmbh & Co Kg
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 Engineering Center Steyr Gmbh & Co Kg filed Critical Engineering Center Steyr Gmbh & Co Kg
Publication of WO2016055255A1 publication Critical patent/WO2016055255A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears

Definitions

  • the present invention relates to a differential, in particular a Stirnradaus istsgetriebe.
  • the differential comprises intermeshing epicyclic gears (also called planetary gears) and two central output spur gears of two output shafts, the epicyclic gears each meshing with one of the output spur gears, the epicyclic gears and the output spur gears being disposed in a housing.
  • Differential gears or differential gears are known per se and are used, for example, as axle differential in multi-lane vehicles. There is its purpose to drive two wheels so that they can turn in curves with different speeds but with the same driving force. The same purpose is served by the central differential in four-wheel drive vehicles, where power is to be distributed to two or more driven axles.
  • DE 1555887 A1 discloses a differential gear with first and second gears, which are coaxially aligned at a distance from each other and are each connected to leading in opposite directions axes.
  • a differential gear comprising intermeshing epicyclic gears and two central output spurs of two output shafts, the epicyclic gears each meshing with one of the output spur gears, the epicyclic gears and the output spur gears being arranged in a housing, the housing itself being used to support the Umlaufgan is formed and the planet gears are mounted directly on the housing.
  • the shape of the housing itself is designed so that a bearing of the epicyclic gears on the housing is possible.
  • the planetary gears are formed as externally toothed ring gears, with cavities around the respective axes of rotation of the planetary gears, and formations of the housing extend respectively into the cavities of the planetary gears, so that the planetary gears are mounted directly on the formations of the housing.
  • housings are particularly preferably cylindrical formations, in particular on each planet gear two cylindrical formations which extend axially from both sides into the cavities.
  • the housing on the outer side for each planet gear on a circular arc-shaped bulge wherein the bulge each embraces the outer contour of the planetary gear near.
  • the housing follows the minimum space requirement of the planetary gears.
  • the housing is composed of two half-shells.
  • the two half-shells along a wavy annular surface, which is formed by the circular arc-shaped bulges, joined and / or circular surfaces on which touch the two cylindrical formations - particularly preferably at both said joining surfaces.
  • the joining surfaces are normal to the axes of rotation of the planetary gears.
  • This shape of the half-shells allows a particularly rigid housing, allows a reduction of the sheet thickness and a closed shape, without the use of holes.
  • the joining surfaces of the housing are oil-tight joined, preferably welded, in particular by capacitor discharge welding, in order to achieve an oil seal of the differential gear.
  • the housing may consist of at least one, preferably of two sheet metal formed parts, in particular of two identical, deep-drawn, cup-shaped sheet metal shells.
  • oil-tight seals may be provided between the housing and the output shafts.
  • FIG. 1 is a side sectional view of a differential gear according to the invention corresponding to the section A-A of FIG. 2.
  • Fig. 2 is a sectional view of a differential gear according to the invention from the front, corresponding to the section B-B of Fig. 1.
  • Fig. 3 is a detailed view of a detail of Fig. 2nd
  • an inventive differential gear is shown in two sectional views.
  • the differential comprises eight Nander meshing epicyclic 1 and two central output spur gears 2 which are arranged axially parallel to the axes of rotation 4 of the epicyclic 1.
  • the epicyclic gears 1 each mesh with one of the output spur gears 2, namely, as shown in FIG. 2, alternately meshing one of the epicyclic gears with one output spur gear and the next epicyclic gear with the other output spur gear, so that each output spur gear meshes with four epicyclic gears altogether.
  • the planetary gears 1 and the output spur gears 2 are arranged in a housing 3, which forms the drive of the differential gear.
  • the planetary gears 1 are formed as externally toothed ring gears, with central cavities around the respective axes of rotation 4 of the planetary gears 1, and two cylindrical formations 5 of the housing 3 extend axially from both sides into the cavities of the planetary gears 1, so that the planet gears 1 directly to the cylindrical formations 5 of the housing 3 are mounted.
  • the housing 3 has on the outside for each planetary gear 1 on a circular arc-shaped bulge 6, wherein the bulge 6 each surrounds the outer contour of the planetary gear 1 near the planet wheel 1.
  • the housing 3 is composed of two half shells 7, 8, namely two identical, deep-drawn, cup-shaped sheet metal shells, which are composed in mirror symmetry.
  • the two half-shells 7, 8 are joined along a corrugated annular surface 9, which is formed by the circular arc-shaped bulges 6, and at eight circular surfaces 10, to which the two cylindrical formations 5 touch.
  • the joining surfaces 9, 10 are normal to all axes of rotation. 4
  • oil-tight seals are provided between the housing 3 and the output shafts - not shown . The only two openings of the housing 3 are those for the two output shafts.
  • Each planetary gear 1 is drivingly connected to three meshing engagements: one engagement with one output spur gear 2 and one engagement with each of the two adjacent epicyclic gears 1.
  • the number of planetary gears 1 is eight. The geometric engagement conditions caused by the three tooth engagements severely limit the choice of teeth numbers.
  • the planetary gears 1 each have 10 teeth
  • the output spur gears 2 each have 16 teeth.
  • the ratio of the number of teeth of a Popestirnrades 2 to the number of teeth of a planetary gear 1 is 1, 6.
  • the doubling of the numbers of teeth of planet wheels 1 and output spur gears 2 also fulfills the installation conditions.
  • One of the output spur gears 2 is drive-connected via four gear meshes with four epicyclic gears 1.
  • These four epicyclic wheels 1 are drivingly connected via eight tooth engagements with a further four epicyclic wheels 1 arranged in the direction of rotation by 45 degrees, which in turn are drive-connected to the other output spur gear 2 via four tooth engagements.
  • the radial positioning of the output spur gears 2 takes place via the contact surfaces to the revolving wheels 1 (FIG. 2), the axial positioning via an annular surface to the half shell 7, 8 and in the plane of symmetry of the housing 3 via an annular surface to the respective other output spur gear 2 (FIG ).
  • FIG. 3 shows a detail of FIG. 2, in which the region of engagement between a planetary gear 1 and a starting gear 1 is shown.
  • Helical 2 is easy to see.
  • the meshing gears of the planetary gears 1 and the output spur gears 2 have an optimized shape in the root of the tooth.
  • the engaging involute is reshaped in the foot area. This leads to a strengthening of the toothing in this area and to a frictional rolling contact through the cylindrical contact surfaces of the head area and foot area, each of the meshing spur gears.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

Différentiel qui comporte des roues planétaires (1) qui s'engrènent les unes avec les autres, et deux pignons de sortie centraux (2) de deux arbres de sortie. Les roues planétaires (1) s'engrènent chacune avec l'un des pignons de sortie (2). Les roues planétaires (1) et les pignons de sortie (2) sont agencés dans un carter (3), le carter (3) étant conçu pour servir de support aux roues planétaires (1) et les roues planétaires (1) étant directement montées sur le carter (3).
PCT/EP2015/071585 2014-10-10 2015-09-21 Différentiel WO2016055255A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014220601.4 2014-10-10
DE102014220601.4A DE102014220601B4 (de) 2014-10-10 2014-10-10 Ausgleichsgetriebe

Publications (1)

Publication Number Publication Date
WO2016055255A1 true WO2016055255A1 (fr) 2016-04-14

Family

ID=54207484

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/071585 WO2016055255A1 (fr) 2014-10-10 2015-09-21 Différentiel

Country Status (2)

Country Link
DE (1) DE102014220601B4 (fr)
WO (1) WO2016055255A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11448300B1 (en) * 2021-06-15 2022-09-20 Schaeffler Technologies AG & Co. KG Sealed planetary differential

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3406593A (en) * 1966-09-15 1968-10-22 Illinois Tool Works Limited slip differential mechanism
US3738192A (en) * 1971-06-29 1973-06-12 Illinois Tool Works Limited slip differential mechanisms
WO2014019744A1 (fr) * 2012-07-31 2014-02-06 Schaeffler Technologies AG & Co. KG Différentiel à pignons droits

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3292456A (en) 1964-04-30 1966-12-20 Illinois Tool Works Spin limiting differential
DE102012214767A1 (de) 2012-08-20 2014-02-20 Schaeffler Technologies AG & Co. KG Differentialgetriebe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3406593A (en) * 1966-09-15 1968-10-22 Illinois Tool Works Limited slip differential mechanism
US3738192A (en) * 1971-06-29 1973-06-12 Illinois Tool Works Limited slip differential mechanisms
WO2014019744A1 (fr) * 2012-07-31 2014-02-06 Schaeffler Technologies AG & Co. KG Différentiel à pignons droits

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11448300B1 (en) * 2021-06-15 2022-09-20 Schaeffler Technologies AG & Co. KG Sealed planetary differential

Also Published As

Publication number Publication date
DE102014220601A1 (de) 2016-04-14
DE102014220601B4 (de) 2018-08-30

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