WO2007147705A1 - Agencement d'un axe de satellite dans un porte-satellites - Google Patents

Agencement d'un axe de satellite dans un porte-satellites Download PDF

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Publication number
WO2007147705A1
WO2007147705A1 PCT/EP2007/055250 EP2007055250W WO2007147705A1 WO 2007147705 A1 WO2007147705 A1 WO 2007147705A1 EP 2007055250 W EP2007055250 W EP 2007055250W WO 2007147705 A1 WO2007147705 A1 WO 2007147705A1
Authority
WO
WIPO (PCT)
Prior art keywords
planet
gear
planetary
planet carrier
transmission
Prior art date
Application number
PCT/EP2007/055250
Other languages
German (de)
English (en)
Inventor
Hermann Lanz
Michael Bodenmüller
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 WO2007147705A1 publication Critical patent/WO2007147705A1/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
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive

Definitions

  • the invention relates to the arrangement of a planetary gear in a planetary gear, in particular a planetary gear of a motor vehicle.
  • a range group transmission connected to the main transmission with its gear ratios.
  • the total ratio of the main transmission can be increased by all gear stages of the main transmission can be used together with each gear ratio of the range group transmission and in at least one gear ratio of the range group transmission, the ratio of the gear ratios of the main gear stubs or is translated.
  • An area group transmission for motor vehicles has become known, for example, from DE 41 21 709 A1.
  • the main transmission downstream planetary gear it is possible to operate the motor vehicle within its gear ratios of the main transmission in each case in two different speed ranges.
  • the ring gear of the planetary gear is coupled via a clutch to the transmission housing, so that the output shaft of the range group transmission has a lower speed than the output shaft of the main gearbox in a second switching stage is a direct drive from the output shaft of the main transmission to the output shaft of the range group transmission, wherein via a clutch the direct connection between the output shaft of the main gear and the output shaft of the range group is made.
  • the switching device is designed very expensive.
  • a planetary gear for a motor vehicle is absorbed in the axial forces from a helical toothing of the planetary gear by means of pressure combs and derived in other areas of the transmission.
  • the pressure combs are only arranged so that they can only absorb the forces occurring in the train operation of the vehicle.
  • the planet pins are fixedly connected to the planet carrier and are prevented from relative rotation to the planet carrier. This connection is usually a positive connection. A press fit of the bolt in the planet carrier can still support or replace this connection.
  • the present invention is therefore based on the object, starting from the aforementioned prior art to reduce stress damage to the planetary pin of a planetary gear.
  • the planet pins in the planet carrier are tion of an at least partial possibility of rotation of the planet pins in the planet carrier in its circumferential direction unfixed and deliberately game tainted and arranged free of rotation storage.
  • no pivot bearing for the planetary bolt is provided in the form of a special pivot bearing
  • the planetary pin is fixed in its axial direction arranged to avoid play-related axial Wan ⁇ derns the planetary bolt.
  • the planetary gear forms a main gearbox of a commercial vehicle in the torque transmission downstream range group transmission.
  • the planetary bolt allows to rotate undefined and thus change its position in the circumferential direction relative to the planet carrier undefined.
  • undefined is to be understood that the degree of rotation is not determined.
  • the on the planet pin adjusting load zone migrates in this way gradually over the entire planet pins. A start of fatigue of the component planetary pin will thus occur much later.
  • Fig. 1 is a schematic arrangement of the planetary gear
  • Fig. 2 the planetary gear with switching device.
  • a transmission 2 for a vehicle has in a transmission housing 4 a main transmission 6 and a subsequent to the main transmission 6 range group transmission in the form of a planetary gear 8.
  • the planetary transmission be 8 comprises a planet carrier 10> which is embodied with the output shaft 12 of the gearbox 2 as a common component.
  • a driven flange 14 is fixed and the output shaft 12 is mounted in the transmission housing 4 in a bearing 16.
  • the planet carrier 10 has a plurality of planet pins 18 distributed on its circumference, of which a planet pin is shown here.
  • the planet pin 20 is mounted on the planet pin 18 in a roller bearing 22 (FIG. 2).
  • Usually, three to five planet gears 20 are arranged distributed on the circumference of the planet carrier 10.
  • the planet gear 20 is surrounded on the outside by a ring gear 24, which has a toothing 26 which can engage in a toothing 28 on the gear housing 4.
  • a sleeve 50 is arranged, which serves to guide the oil between the waves.
  • the oil guide is a sleeve 54 which is provided between the main shaft 44 and the sun gear 52.
  • the planet carrier 10 has on the output shaft 12 opposite side of the planetary gear 8 an extension 36 on which the planet carrier 10 is supported by a roller bearing 38 in the transmission housing 4
  • Main transmission 6 is supported by a bearing 42 in the transmission housing 4.
  • the main shaft 44 of the main transmission 6 contributes its end a gear 46 of the reverse gear ratio.
  • the gear 46 is arranged on the main shaft 44 with slight radial play, which is typical for a manual transmission with a power split on two countershafts.
  • a pin 45 is provided at the end of the main shaft 44 of FIG. 1, a pin 45 is provided.
  • the sun gear 52 is disposed on the pin 45 of the main shaft 44, wherein according to FIG. 1, the main shaft 44 is supported in the sun gear 52.
  • two pressure ridges 56 and 58 are arranged (FIG. 2) which prevent axial movement of the planet gear 20 relative to the sun gear 52 but allow the planetary gear 20 to contact the pressure ridges to provide an axially directed one To absorb force resulting from a helical toothing of the planetary gear 8.
  • Two further pressure combs 60 and 62 are arranged radially within the ring gear 24 and also allow a contact of the planet gear 20. The two pressure combs 60 and 62 prevent axial movement of the planet gear 20 relative to the ring gear 24th
  • a sliding sleeve 66 has a first internal toothing as Schalf- toothing 68, which engages in a switching toothing 70 on the sun gear 52 and a rotationally fixed connection between the sliding sleeve 66 and the sun gear 52 produces (Fig. 2).
  • the sliding sleeve 66 has a second internal toothing 72, which engages in an external toothing 74 on the main shaft 44.
  • the sliding sleeve 66 has a switching toothing 76, which engage in a switching teeth 78 on the extension 36 of the planet carrier 10 can.
  • the switching position of the sliding sleeve 66 is shown in the upper half of the planetary gear 8, which allows a non-rotatable connection between the main shaft 44 and the sun gear 52 via the gear teeth 68 and 70.
  • the planet gear 20 is mounted on the planet pin 18 in the roller bearing 22.
  • a roller bearing 22 is also a multi-row bearing into consideration, for example, a double-row needle bearing.
  • the planet pin 18 is arranged in the planet carrier such that it can perform undefined rotational movements. By undefined is to be understood that the degree of rotation is not determined.
  • the planetary bolt is potentially axially displaceable so that it must be fixed axially. This is done on the one hand by an edge 84 on the extension 36 and on the other hand by a cup-shaped ring 86 which is clamped here between the planet pin 18 and the bearing 16 in the transmission housing 4.
  • the planetary pin 18 can also be held axially by retaining rings.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un engrenage planétaire (10) comprenant au moins un axe de satellite (18) fixé dessus, sur lequel une roue planétaire ((20) est montée bloquée en rotation. L'axe de satellite (18) est monté non fixé dans le porte-satellites (10) pour induire une possibilité de rotation au moins partielle de l'axe de satellite (18) dans le porte-satellites (10) dans son sens circonférentiel et est monté à dessein avec du jeu et sans disposition de paliers de pivotement. Dans son sens axial, l'axe de satellite (18) est monté fixe afin d'éviter de migrer dans le sens axial sous l'effet du jeu.
PCT/EP2007/055250 2006-06-24 2007-05-30 Agencement d'un axe de satellite dans un porte-satellites WO2007147705A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610029004 DE102006029004A1 (de) 2006-06-24 2006-06-24 Anordnung eines Planetenrades
DE102006029004.6 2006-06-24

Publications (1)

Publication Number Publication Date
WO2007147705A1 true WO2007147705A1 (fr) 2007-12-27

Family

ID=38370410

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/055250 WO2007147705A1 (fr) 2006-06-24 2007-05-30 Agencement d'un axe de satellite dans un porte-satellites

Country Status (2)

Country Link
DE (1) DE102006029004A1 (fr)
WO (1) WO2007147705A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015214735A1 (de) * 2015-08-03 2017-02-09 Zf Friedrichshafen Ag Wärmerückgewinnungseinrichtung für einen Kraftfahrzeugantriebsstrang
DE102017119962A1 (de) 2017-08-31 2019-02-28 Schaeffler Technologies AG & Co. KG Planetengetriebe mit einem Stützlager zur Lagerung mindestens eines Planetenbolzens

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4756212A (en) * 1987-01-12 1988-07-12 General Motors Corporation Planet gear carrier assembly
DE4121709A1 (de) * 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen Bereichsgetriebe fuer kraftfahrzeuge
DE4439976A1 (de) * 1994-11-09 1996-05-15 Zahnradfabrik Friedrichshafen Schrägverzahntes Planetengetriebe
WO2004104445A1 (fr) * 2003-05-23 2004-12-02 Zf Friedrichshafen Ag Engrenage planetaire

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4756212A (en) * 1987-01-12 1988-07-12 General Motors Corporation Planet gear carrier assembly
DE4121709A1 (de) * 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen Bereichsgetriebe fuer kraftfahrzeuge
DE4439976A1 (de) * 1994-11-09 1996-05-15 Zahnradfabrik Friedrichshafen Schrägverzahntes Planetengetriebe
WO2004104445A1 (fr) * 2003-05-23 2004-12-02 Zf Friedrichshafen Ag Engrenage planetaire

Also Published As

Publication number Publication date
DE102006029004A1 (de) 2008-01-03

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