WO1999036712A1 - Groupe planetaire - Google Patents

Groupe planetaire Download PDF

Info

Publication number
WO1999036712A1
WO1999036712A1 PCT/EP1998/008417 EP9808417W WO9936712A1 WO 1999036712 A1 WO1999036712 A1 WO 1999036712A1 EP 9808417 W EP9808417 W EP 9808417W WO 9936712 A1 WO9936712 A1 WO 9936712A1
Authority
WO
WIPO (PCT)
Prior art keywords
sliding sleeve
gear
toothing
group transmission
ring
Prior art date
Application number
PCT/EP1998/008417
Other languages
German (de)
English (en)
Inventor
Josef Bader
Gerhard Buri
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 WO1999036712A1 publication Critical patent/WO1999036712A1/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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/78—Special adaptation of synchronisation mechanisms to these gearings
    • 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
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed

Definitions

  • the present invention relates to a group transmission for motor vehicles according to the preamble of claim 1.
  • Such a group transmission which is usually connected downstream of the basic transmission, is used to operate commercial vehicles or working machines in the course of the gear stages of the basic transmission in each case in two different speed ranges.
  • the ring gear of the group transmission designed as a planetary gear is coupled to the transmission housing via a first clutch, so that the output shaft of the group transmission has a lower speed than the output shaft of the basic transmission.
  • a second shift stage there is usually a direct drive through from the output shaft of the basic transmission to the output shaft of the group transmission, a connection between the ring gear and a coupling ring connected to the planet gear carrier being established via the clutch.
  • Another disadvantage is that this known group transmission has a large number of cost-intensive individual parts.
  • the object of the present invention is to provide a group transmission which is simpler and therefore cheaper to manufacture.
  • a clutch 1 is used to switch a planetary gear 2, which includes a ring gear 3, planet gears 4 and a sun gear 7.
  • the planet gears 4 are mounted on planet pins 5 by means of roller bearings 6 in a planet carrier 8.
  • the sun gear 7 is connected to an input shaft, not shown, and the planet carrier 8, which is mounted in a gear housing 9 by means of a roller bearing 10, with an output shaft, not shown.
  • the clutch 1 has a sliding sleeve 17 with a groove 18. Furthermore, it has a switching toothing 19 as an internal toothing. In the drawn state, the gear teeth 19 engage through a synchronizing ring 29.
  • the sliding sleeve 17 is non-rotatably connected to the ring gear 3 via an external toothing 11 via a coupling member 52.
  • the sliding sleeve 17 is axially in the ring gear 3 by a Circlip 15 and a washer 53 secured.
  • the ring gear 3 is guided axially via the coupling member 52 and the disk 53 via the planet gear 4.
  • a disk 54 which is connected to a shift fork 64, removably engages in the external toothing 11 of the sliding sleeve 17.
  • the disk 54 which is guided in the external toothing 11, is secured against rotation axially via a ring 66 in the groove 18 and radially via the toothing 11.
  • 59 denotes a synchronous cone which is fastened separately in the gear housing 9, and 60 denotes a reaction plate in which the coupling toothing 23 is directly incorporated.
  • the synchronous cone 59 is fixed in the gear housing 9 by means of driving teeth 13 and a locking ring 16.
  • the ring gear 3 is connected to the transmission housing 9 via the coupling member 52, the sliding sleeve 17 and the reaction plate 60.
  • the clutch 1 also includes a further clutch body 20 with a coupling toothing 22, which is fixed to the planet carrier 8 via a driving toothing 12 and a locking ring 14 and cooperates with a synchronizing ring 28. If the sliding sleeve 17 is shifted to the right in accordance with the figure, a change is made to another gear or gear group in which the ring gear 3 is connected to the planet carrier 8 and rotates together with the latter.
  • an annular spring 40 is provided between the synchronizing rings 28, 29, which engages in a locking groove of the sliding sleeve 17 in the neutral position of the sliding sleeve 17.
  • the ring spring 40 exerts an axial force on the synchronizing rings 28, 29. Additional locking grooves can be provided for the switch positions.
  • the switch in the direction of the fast group takes place as in the conventional group transmission, i. H. that the synchronizer ring 28 is synchronized with the internal toothing 19 of the sliding sleeve 17, the coupling process into the coupling body 20 on the planet carrier 8 taking place at the same speed after the speed.
  • the switching process in the direction of the slow group takes place by synchronizing via the synchronizer ring 29 with the internal toothing 19 of the sliding sleeve 17 to the synchronizing cone 59 arranged separately in the housing External toothing 11 in the coupling toothing 23 in the reaction plate 40.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne un groupe planétaire pour véhicules à moteur comprenant un engrenage planétaire (2) qui présente une roue planétaire (7), un porte-satellites (8) raccordé à l'arbre de sortie de l'engrenage planétaire (2), et une couronne (3) raccordée à un manchon coulissant (17) par l'intermédiaire d'un élément d'accouplement (52). Le manchon coulissant (17) comporte une denture intérieure (19) et une denture extérieure (11), cette dernière (11) étant raccordée de façon constamment solidaire en rotation avec la couronne (3) par l'intermédiaire de l'élément d'accouplement (52).
PCT/EP1998/008417 1998-01-16 1998-12-22 Groupe planetaire WO1999036712A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1998101477 DE19801477B4 (de) 1998-01-16 1998-01-16 Gruppengetriebe
DE19801477.5 1998-01-16

Publications (1)

Publication Number Publication Date
WO1999036712A1 true WO1999036712A1 (fr) 1999-07-22

Family

ID=7854815

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/008417 WO1999036712A1 (fr) 1998-01-16 1998-12-22 Groupe planetaire

Country Status (2)

Country Link
DE (1) DE19801477B4 (fr)
WO (1) WO1999036712A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10025849A1 (de) * 2000-05-25 2001-11-29 Zahnradfabrik Friedrichshafen Gruppengetriebe
DE102005021698A1 (de) * 2005-05-11 2006-11-16 Zf Friedrichshafen Ag Nachschalt-Gruppe eines Mehrgruppengetriebes in Planetenbauweise

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2528141A1 (fr) * 1982-06-07 1983-12-09 Volvo Ab Boite de vitesses secondaire pour vehicules motorises et transmission de vehicule incorporant cette boite
DE4121709A1 (de) * 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen Bereichsgetriebe fuer kraftfahrzeuge
DE4121757A1 (de) 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen Bereichsgetriebe fuer kraftfahrzeuge

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1201744A (fr) * 1957-08-28 1960-01-05 Eaton Axles Ltd Perfectionnements aux dispositifs de synchronisation pour embrayage à dents
CS152065B1 (fr) * 1969-12-04 1973-12-19
DE3330303A1 (de) * 1983-08-23 1985-03-14 Volkswagenwerk Ag, 3180 Wolfsburg Getriebeanordnung fuer fahrzeuge, insbesondere kraftfahrzeuge
SE450944B (sv) * 1983-12-06 1987-08-17 Volvo Ab Rangevexellada for motorfordon
DE3844166C1 (fr) * 1988-12-23 1990-01-25 Mannesmann Ag, 4000 Duesseldorf, De

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2528141A1 (fr) * 1982-06-07 1983-12-09 Volvo Ab Boite de vitesses secondaire pour vehicules motorises et transmission de vehicule incorporant cette boite
DE4121709A1 (de) * 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen Bereichsgetriebe fuer kraftfahrzeuge
DE4121757A1 (de) 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen Bereichsgetriebe fuer kraftfahrzeuge

Also Published As

Publication number Publication date
DE19801477B4 (de) 2006-11-30
DE19801477A1 (de) 1999-07-22

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