WO2012084366A1 - Engrenage planétaire - Google Patents

Engrenage planétaire Download PDF

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Publication number
WO2012084366A1
WO2012084366A1 PCT/EP2011/070507 EP2011070507W WO2012084366A1 WO 2012084366 A1 WO2012084366 A1 WO 2012084366A1 EP 2011070507 W EP2011070507 W EP 2011070507W WO 2012084366 A1 WO2012084366 A1 WO 2012084366A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
sun
planetary
teeth
ring gear
Prior art date
Application number
PCT/EP2011/070507
Other languages
German (de)
English (en)
Inventor
Jörg BÖRNER
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO2012084366A1 publication Critical patent/WO2012084366A1/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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/30—Toothed gearings for conveying rotary motion with gears having orbital motion in which an orbital gear has an axis crossing the main axes of the gearing and has helical teeth or is a worm

Definitions

  • the invention relates to a planetary gear according to the preamble of claim 1.
  • Planetary gear also called epicyclic gear
  • a sun gear usually include a sun gear, a plurality of planetary gears meshed with the sun gear, also called planetary, and a ring gear having internal teeth and meshing with the planets.
  • the axes of the individual gear parts such as ring gear, planet and sun gear are arranged parallel to each other.
  • Planetary gears have many advantages, u. a. a coaxial input and output and the possibility of power split. They can be operated as a planetary gear with a circulation ratio or as a stationary transmission with a stand ratio, with a gear part is held.
  • the planetary gear is designed as SSradgetriebe, d. H. the sun gear and the ring gear each make helical gear pairings with the planets, with the axes of the planets crossing with the sun and ring gear axes, i.e. H. the planets are tilted by a tilt angle. From this combination of planetary and fferradgetriebe the advantage of a higher translation of greater than 50 results.
  • the efficiency of the planetary gear according to the invention does not correspond to that of a planetary gear with parallel axes, d. H. Spur teeth, however, the loss of efficiency at lower powers is acceptable.
  • the advantage of power sharing across multiple planets can be used. The higher load of the tooth flanks due to a theoretical point contact can be compensated by a relatively high overlap in the tooth engagement, with more than three tooth pairs are always engaged.
  • the tilt angle of the planets is in a range of 15 to 40 degrees, preferably in a range of 20 to 35 degrees.
  • Tilt angle is understood to mean the angle at which the planetary axis is tilted with respect to a planetary axis arranged parallel to the axis of rotation of the sun. The tilt angle thus corresponds to the crossing angle of the planetary axes with the axis of rotation of the hollow and the sun gear.
  • the sun gear has an external toothing with a very large helix angle and a number of teeth in the Range from 2 to 6 on.
  • the helix angle is generally smaller than with a worm of a worm gear. This results in a relatively high coverage of greater than 2 in the contact between the sun and the planet. Due to the relatively large, but compared to a worm smaller helix angle results in a relatively low (screw) sliding friction and thus acceptable efficiencies. Even with a number of teeth smaller than 6 so big enough din Vietnamese dinmesser for the sun gear are possible.
  • a planetary gear is provided with three planets, which are tilted by a tilt angle of 35 °.
  • teeth numbers for the sun of 3, for the planets of 60 and for the ring gear of -159 are provided. This results in a translation of 53 with an efficiency of 77%.
  • the sun has a number of teeth of 2, the planetary teeth number of 59 and the ring gear a number of teeth of -160, which gives a translation of 80 at an efficiency of 68%. The higher ratio is thus paid for with a reduced efficiency. Nevertheless, these efficiencies are acceptable given the high achievable translations.
  • the ring gear for the two aforementioned transmission designs on a straight toothing d. H. a helix angle of 0 °. This results in a relatively large helix angle in the sun, resulting in a larger root diameter.
  • two planets are provided with a tilt angle of 20 °, with a preferred gear design providing numbers of teeth for the sun of 3, for the planet of 68, and for the ring gear of -159.
  • the ring gear is helically toothed to achieve a slightly larger helix angle for the sun gear.
  • the axis of rotation of the sun gear is arranged displaceable radially relative to the axis of rotation or the central axis of the ring gear, wherein only two planets are provided, which are not diametrically opposed, but have a distance angle of less than 180 °.
  • the planetary gear according to the invention can also be operated as a stand-up gear. This is possible because for translations of more than 20, the stand translation deviates only slightly from the circulation ratio. For example, the drive via the sun gear, and the output via the ring gear can take place while the bridge is held with the tilted planets.
  • Fig. 2 shows a modified embodiment of an inventive
  • Fig. 3 shows another embodiment of the invention with two planetary gears
  • FIG. 4 is a side view of the planetary gear according to FIG. 3rd
  • Fig. 1 shows a schematic representation of a planetary gear 1 according to the invention, which is designed as SSradgetriebe.
  • the planetary gear set 1 comprises a centrally disposed sun gear 2, a ring gear 3 arranged coaxially with the sun gear 2, and three tilted planets 4.
  • the axes of rotation (not shown) of the sun gear 2 and the ring gear 3 are identical, ie the ring gear 3 and the sun gear 2 , also called Sun 2 for short, turn around the same axis.
  • the axes of rotation of the planetary gears 4, not shown, also briefly called planetary 4, are opposite tilted the axis of rotation of sun 2 and ring gear 3 - in the illustrated embodiment, they have a tilt angle of 35 °.
  • the sun gear 2 forms with the planet 4 fferradcrustation; also form the planet 4 with the ring gear 3 fferradcru.
  • the sun 2 has a helical gearing with a very strong helix angle
  • the planet 4 have helical gears
  • the ring gear 3 has an internal straight gearing. Due to the tilting of the planet 4 by 35 °, the largest possible helix angle is obtained on the sun 2 due to the straight toothed ring gear 3, so that there is a larger root diameter for the sun 2.
  • the planetary gear set 1 is dimensioned as follows:
  • the sun 2 has a number of teeth of 3
  • the planet 4 have numbers of teeth of 60
  • the ring gear 3 has a number of teeth of -159 (negative because of the internal teeth). This results in a stand ratio of 53 with an efficiency of 77%.
  • Fig. 2 shows a planetary gear according to the invention 5 with a sun gear 6, a coaxially arranged ring gear 7 and two tilted planets 8.
  • the sun 6 and the planetary 8 as well as the planet 8 and the ring gear 7 fferradcru, d. H. their axes of rotation intersect without cutting.
  • the tilt angle of the planet 8 is also 35 ° in this embodiment.
  • the planetary gearset 5 has the following numbers of teeth: 2 for the sun 6, 59 for the planets 8 and -160 for the ring gear 7. This results in a stand ratio of 80 at an efficiency of 68%; d. H. the higher ratio of 80 compared to the embodiment of FIG.
  • Stand translation means that one of the three gear parts, such as a not shown, the planet 8 receiving web is held firmly while the sun 6 and ring 7 rotate.
  • the stand ratios differ only slightly from the circulation ratios in these transmissions (with high ratio).
  • Fig. 3 shows another embodiment of the invention, namely a planetary gear set 9, which has a centrally disposed sun gear 10, a ring gear 1 1 and two tilted planets 12, each with the sun 10 and the ring gear 1 Forming helical gear pairs.
  • the planets 12 have penetration points P1, P2 of their axes, which are not diametrically opposed, but with the center M and the axis of rotation of the sun gear 10 and ring gear 1 1 an obtuse triangle with the vertices P1, M, P2, ie a distance angle of less than 180 °.
  • Fig. 4 shows a side view of the planetary gear set 9 with ring gear 1 1 and tilted planet 12.
  • the axis of rotation of one of the two planetary gears 12 is a and the axis of rotation of the ring gear 1 1 (or a parallel axis) is denoted by b.
  • the angle between the axes a, b is the tilt angle designated ⁇ , which is 20 ° in the illustrated embodiment.
  • the ring gear 1 1 is helically toothed in the illustrated embodiment in order to achieve a slightly larger helix angle for the sun 10.
  • the root diameter of the sun 10 is not as large as in the embodiments of FIGS. 1 and 2, but the efficiency is significantly higher.
  • the planetary gear set 9 is designed as follows:
  • the sun gear 10, the planet 12 and the ring gear 1 1 have numbers of teeth of 3, 68 and -159, which results in a state ratio of 53 at an efficiency of 88%.
  • the lower tilt angle of 20 ° in the embodiment of FIG. 3 and 4 leads to a higher efficiency. This is due to the fact that the sliding friction of the fferradcrustation decreases with decreasing crossing angle of the axes (tilt angle).

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

Abstract

L'invention concerne un engrenage planétaire, comprenant une roue solaire (2), une couronne dentée (3) disposée de manière coaxiale à la roue solaire (2), ainsi qu'au moins deux pignons planétaires (4) qui s'engrènent avec la roue solaire (2) et la couronne dentée (3). Selon l'invention, la roue solaire (2), les au moins deux pignons planétaires (4), ainsi que la couronne dentée (3) sont réalisés sous forme de roues à dentures hélicoïdales et forment des paires de roues à dentures hélicoïdales dont les axes se croisent.
PCT/EP2011/070507 2010-12-20 2011-11-21 Engrenage planétaire WO2012084366A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010063569.3 2010-12-20
DE201010063569 DE102010063569A1 (de) 2010-12-20 2010-12-20 Planetengetriebe

Publications (1)

Publication Number Publication Date
WO2012084366A1 true WO2012084366A1 (fr) 2012-06-28

Family

ID=44993578

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/070507 WO2012084366A1 (fr) 2010-12-20 2011-11-21 Engrenage planétaire

Country Status (2)

Country Link
DE (1) DE102010063569A1 (fr)
WO (1) WO2012084366A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE720040C (de) * 1936-12-11 1942-04-22 Werke Kiel Ag Deutsche Stirnraederplanetengetriebe
GB1123269A (en) * 1965-11-09 1968-08-14 Hisashi Kaburagi Speed changing gears
DE2511973A1 (de) * 1975-03-19 1976-09-30 Konrad Prof Dr Ing Langenbeck Planetenschraubgetriebe
EP0165231A2 (fr) * 1984-05-15 1985-12-18 VOEST-ALPINE Aktiengesellschaft Transmission avec engrenage à mouvement orbital
FR2721672A1 (fr) * 1994-06-28 1995-12-29 Roger Lecal Mécanisme épicycloïdal à satellites à doubles engrèvements distincts pour mouvements intermittents.
AT6828U1 (de) * 2002-11-29 2004-04-26 Magna Steyr Powertrain Ag & Co Schaltbares planetengetriebe
DE202008015150U1 (de) * 2008-11-14 2009-01-29 Baumeister, Karlheinz Koaxiales Getriebe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB129446A (en) * 1918-07-11 1919-07-11 Brazil Straker & Company Ltd Improvements in or relating to Epicyclic or like Gears.
DD203608A1 (de) * 1981-11-02 1983-10-26 Gerhard Gramss Untersetzungsgetriebe
DE102008004498A1 (de) * 2008-01-16 2009-07-23 Schaeffler Kg Planetenradgetriebe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE720040C (de) * 1936-12-11 1942-04-22 Werke Kiel Ag Deutsche Stirnraederplanetengetriebe
GB1123269A (en) * 1965-11-09 1968-08-14 Hisashi Kaburagi Speed changing gears
DE2511973A1 (de) * 1975-03-19 1976-09-30 Konrad Prof Dr Ing Langenbeck Planetenschraubgetriebe
EP0165231A2 (fr) * 1984-05-15 1985-12-18 VOEST-ALPINE Aktiengesellschaft Transmission avec engrenage à mouvement orbital
FR2721672A1 (fr) * 1994-06-28 1995-12-29 Roger Lecal Mécanisme épicycloïdal à satellites à doubles engrèvements distincts pour mouvements intermittents.
AT6828U1 (de) * 2002-11-29 2004-04-26 Magna Steyr Powertrain Ag & Co Schaltbares planetengetriebe
DE202008015150U1 (de) * 2008-11-14 2009-01-29 Baumeister, Karlheinz Koaxiales Getriebe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
G. NIEMANN; H. WINTER, MASCHINENELEMENTE, vol. 3, 2004, pages 1 - 7

Also Published As

Publication number Publication date
DE102010063569A1 (de) 2012-06-21

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