WO1999036712A1 - Group gear - Google Patents

Group gear Download PDF

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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)
French (fr)
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/en

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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.

Abstract

The invention relates to a group gear for automobiles, consisting of a planetary gear (2) with a sun wheel (7), a planet carrier (8) which is connected to the driven shaft of said planetary gear (2), and a ring gear (3) which is connected to a sliding sleeve (17) by a coupling member (52). The sliding sleeve (17) is provided with internal (19) and external (11) toothing, the external toothing (11) being connected to the ring gear (3) by a coupling member (52) in such a way that it is permanently rotationally fixed.

Description

Gruppengetriebe Group transmission
Die vorliegende Erfindung bezieht sich auf ein Grup- pengetriebe für Kraftfahrzeuge nach dem Oberbegriff des Anspruchs 1.The present invention relates to a group transmission for motor vehicles according to the preamble of claim 1.
Ein derartiges Gruppengetriebe, das üblicherweise dem Grundgetriebe nachgeschaltet ist, dient dazu, Nutzkraft- fahrzeuge oder Arbeitsmaschinen im Rahmen der Gangstufen des Grundgetriebes jeweils in zwei unterschiedlichen Geschwindigkeitsbereichen zu betreiben.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.
In einer ersten ins Langsame übersetzten Schaltstufe des Gruppengetriebes wird dabei das Hohlrad des als Planetengetriebe ausgestalteten Gruppengetriebes über eine erste Schaltkupplung an das Getriebegehäuse gekuppelt, so dass die Abtriebswelle des Gruppengetriebes eine geringere Drehzahl als die Ausgangswelle des Grundgetriebes aufweist. In einer zweiten Schaltstufe erfolgt üblicherweise ein direkter Durchtrieb von der Ausgangswelle des Grundgetriebes auf die Abtriebswelle des Gruppengetriebes, wobei über die Schaltkupplung eine Verbindung zwischen dem Hohlrad und einem mit dem Planetenradträger verbundenen Kupplungsring hergestellt wird.In a first gear stage of the group transmission, which is translated into slow speed, 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. In 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.
Aus der DE 41 21 757 AI ist ein derartiges Gruppengetriebe bekannt.Such a group transmission is known from DE 41 21 757 AI.
Nachteilig dabei ist noch, dass dieses bekannte Gruppengetriebe eine Vielzahl kostenintensiver Einzelteile aufweist. Aufgabe der vorliegenden Erfindung ist es, ein Gruppengetriebe zu schaffen, welches einfacher und damit billiger in der Herstellung ist.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.
Ausgehend von einem Gruppengetriebe der eingangs näher genannten Art, erfolgt die Lösung dieser Aufgabe mit den im kennzeichnenden Teil des Anspruchs 1 angegebenen Merkmalen; vorteilhafte Ausgestaltungen sind in den Unteransprüchen beschrieben.Starting from a group transmission of the type mentioned in the introduction, this object is achieved with the features specified in the characterizing part of claim 1; advantageous embodiments are described in the subclaims.
Im folgenden wird die Erfindung anhand der Zeichnung näher erläutert; es zeigt die einzige Figur einen Teilschnitt durch ein erfindungsgemäss ausgestaltetes Gruppengetriebe.The invention is explained in more detail below with reference to the drawing; the single figure shows a partial section through a group transmission designed according to the invention.
Eine Schaltkupplung 1 dient zum Schalten eines Planetengetriebes 2, die ein Hohlrad 3, Planetenräder 4 und ein Sonnenrad 7 umfaßt. Die Planetenräder 4 sind auf Planetenbolzen 5 mittels Wälzlagern 6 in einem Planetenträger 8 gelagert. Das Sonnenrad 7 ist mit einer nicht näher dargestellten Eingangswelle verbunden und der Planetenträger 8, der mittels eines Wälzlagers 10 in einem Getriebegehäuse 9 gelagert ist, mit einer nicht näher dargestellten Ausgangswelle.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.
Die Schaltkupplung 1 besitzt eine Schiebemuffe 17 mit einer Nut 18. Ferner hat sie eine Schaltverzahnung 19 als Innenverzahnung. Im gezeichneten Zustand greift die Schaltverzahnung 19 durch einen Synchronisierring 29.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.
Die Schiebemuffe 17 ist über eine Außenverzahnung 11 über ein Koppelglied 52 mit dem Hohlrad 3 drehfest verbunden. Axial ist die Schiebemuffe 17 im Hohlrad 3 durch einen Sicherungsring 15 und eine Scheibe 53 gesichert. Das Hohlrad 3 wird über das Koppelglied 52 und die Scheibe 53 über das Planetenrad 4 axial geführt.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.
In die Aussenverzahnung 11 der Schiebemuffe 17 greift ausserdem lösbar eine Scheibe 54 ein, die mit einer Schaltgabel 64 verbunden ist. Die Scheibe 54, die in der Aussenverzahnung 11 geführt wird, ist axial über einen Ring 66 in der Nut 18 und radial über die Verzahnung 11 verdrehgesi- chert.In addition, 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.
Mit 59 ist ein separat im Getriebegehäuse 9 befestigter Synchronkonus bezeichnet und mit 60 eine Reaktionsplatte, in welcher die Kupplungsverzahnung 23 direkt eingear- beitet ist. Der Synchronkonus 59 ist über eine Mitnahmeverzahnung 13 und einen Sicherungsring 16 in dem Getriebegehäuse 9 fixiert. Somit ist in dem gezeichneten Schaltzustand das Hohlrad 3 über das Koppelglied 52, die Schiebemuffe 17 und die Reaktionsplatte 60 mit dem Getriebegehäu- se 9 verbunden.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. Thus, in the illustrated switching state, 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.
Zur Schaltkupplung 1 gehört ferner ein weiterer Kupplungskörper 20 mit einer Kuppelverzahnung 22, der über eine Mitnahmeverzahnung 12 und einen Sicherungsring 14 an dem Planetenträger 8 fixiert ist und mit einem Synchronisierring 28 zusammenarbeitet. Wird die Schiebemuffe 17 entsprechend der Figur nach rechts verschoben, wird in einen anderen Gang bzw. Getriebegruppe gewechselt, bei der das Hohlrad 3 mit dem Planetenträger 8 verbunden ist und mit diesem gemeinsam umläuft.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.
Bei der Ausführung nach der Figur ist zwischen den Synchronisierringen 28, 29 eine Ringfeder 40 vorgesehen, die in Neutralstellung der Schiebemuffe 17 in eine Rastnut der Schiebemuffe 17 eingreift. Wenn die Schiebemuffe 17 aus der Neutralstellung bewegt wird, übt die Ringfeder 40 auf die Synchronisierringe 28, 29 eine Axialkraft aus. Weitere Rastnuten können für die Schaltstellungen vorgesehen werden.In the embodiment according to the figure, 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. When the sliding sleeve 17 is moved from the neutral position, the ring spring 40 exerts an axial force on the synchronizing rings 28, 29. Additional locking grooves can be provided for the switch positions.
Die Umschaltung in Richtung schnelle Gruppe erfolgt dabei wie bei den herkömmlichen Gruppengetriebe, d. h. dass der Synchronring 28 mit der Innenverzahnung 19 der Schiebemuffe 17 ansynchronisiert wird, wobei nach dem Dreh- zahlangleich der Einkuppelvorgang in den Kupplungskörper 20 auf dem Planetenträger 8 erfolgt.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.
Der Umschaltvorgang in Richtung langsame Gruppe erfolgt durch ein Ansynchronisieren über den Synchronring 29 mit der Innenverzahnung 19 der Schiebemuffe 17 auf den separat im Gehäuse angeordneten Synchronkonus 59. Nach Dreh- zahlangleich bzw. Erreichen der Drehzahl 0 erfolgt ein Ein- kuppeln der Schiebemuffe 17 mit ihrer Aussenverzahnung 11 in die Kupplungsverzahnung 23 in der Reaktionsplatte 40. 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.
Bezugszeichenreference numeral
1 Schaltkupplung 54 Scheibe für Schaltgabel1 clutch 54 disc for shift fork
2 Planetengetriebe 59 Synchronkonus2 planetary gear 59 synchronous cone
3 Hohlrad 60 Reaktionsplatte3 ring gear 60 reaction plate
4 Planetenrad 64 Schaltgabel4 planetary gear 64 shift fork
5 Planetenbolzen 66 Ring5 planet bolts 66 ring
6 Wälzlager6 roller bearings
7 Sonnenrad7 sun gear
8 Planetenträger8 planet carriers
9 Getriebegehäuse9 gear housing
10 Wälzlager10 rolling bearings
11 Außenverzahnung11 external teeth
12 Mitnahmeverzahnung12 drive teeth
13 Mitnahmeverzahnung13 drive teeth
14 Sicherungsring14 circlip
15 Sicherungsring15 circlip
16 Sicherungsring16 circlip
17 Schiebemuffe17 sliding sleeve
18 Nut18 groove
19 Innenverzahnung19 internal toothing
20 Kupplungskörper20 coupling body
22 Kuppelverzahnung22 coupling teeth
23 Kuppelverzahnung23 coupling teeth
28 Synchronisierring28 synchronization ring
29 Synchronisierring29 synchronization ring
40 Ringfeder40 ring spring
52 Koppelglied52 coupling link
53 Scheibe 53 disc

Claims

P a t e n t a n s p r ü c h e Patent claims
1. Gruppengetriebe für Kraftfahrzeuge in Form eines Planetengetriebes (2), mit einem Sonnenrad (7), einem mit der Abtriebswelle des Gruppengetriebes verbundenen Planetenträger (8) und mit einem Hohlrad (3), das über ein Koppelglied (52) mit einer Schiebemuffe (17) verbunden ist, dadurch g e k e n n z e i c h n e t , dass die Schiebe- muffe (17) sowohl mit einer Innenverzahnung (19) als auch mit einer Aussenverzahnung (11) versehen ist und dass die Aussenverzahnung (11) über das Koppelglied (52) ständig drehfest mit dem Hohlrad (3) verbunden ist.1. Group transmission for motor vehicles in the form of a planetary gear (2), with a sun gear (7), a planet carrier (8) connected to the output shaft of the group transmission and with a ring gear (3) which is connected via a coupling member (52) with a sliding sleeve ( 17), characterized in that the sliding sleeve (17) is provided with an internal toothing (19) as well as with an external toothing (11) and that the external toothing (11) via the coupling member (52) is permanently non-rotatable with the Ring gear (3) is connected.
2. Gruppengetriebe nach Anspruch 1, dadurch g e k e n n z e i c h n e t , dass eine Scheibe (54), die mit einer Schaltgabel (64) verbunden ist, lösbar in die Aussenverzahnung (11) der Schiebemuffe (17) eingreift und die Schiebemuffe (17) über die Scheibe (54) axial verschiebbar ist.2. Group transmission according to claim 1, characterized in that a disc (54), which is connected to a shift fork (64), detachably engages in the external toothing (11) of the sliding sleeve (17) and the sliding sleeve (17) over the disc ( 54) is axially displaceable.
3. Gruppengetriebe nach Anspruch 1 oder 2, dadurch g e k e n n z e i c h n e t , dass die Aussenverzahnung (11) der Schiebemuffe (17) in eine Reaktionsplat- te (60) mit einer darin eingearbeiteten Kupplungsverzahnung (23) eingreift.3. Group transmission according to claim 1 or 2, characterized in that the external toothing (11) of the sliding sleeve (17) engages in a reaction plate (60) with a coupling toothing (23) incorporated therein.
4. Gruppengetriebe nach einem der vorhergehenden Ansprüche, dadurch g e k e n n z e i c h n e t , dass ein Synchronkonus (59) separat im Getriebegehäuse (9) angeordnet ist zum Ansynchronisieren im Bereich der langsamen Gruppe mittels eines Synchronringes (29) über die Innenverzahnung (19) der Schiebemuffe (17) . 4. Group transmission according to one of the preceding claims, characterized in that a synchronizing cone (59) is arranged separately in the transmission housing (9) for synchronizing in the area of the slow group by means of a synchronizing ring (29) via the internal toothing (19) of the sliding sleeve (17) .
PCT/EP1998/008417 1998-01-16 1998-12-22 Group gear WO1999036712A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1998101477 DE19801477B4 (en) 1998-01-16 1998-01-16 group transmission
DE19801477.5 1998-01-16

Publications (1)

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

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ID=7854815

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/008417 WO1999036712A1 (en) 1998-01-16 1998-12-22 Group gear

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WO (1) WO1999036712A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10025849A1 (en) * 2000-05-25 2001-11-29 Zahnradfabrik Friedrichshafen Group gear as planetary gear has sun wheel forming driven shaft, planetary wheel support, ring gear and support, and gearing base
DE102005021698A1 (en) 2005-05-11 2006-11-16 Zf Friedrichshafen Ag Downstream group of a multi-group planetary gearbox

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2528141A1 (en) * 1982-06-07 1983-12-09 Volvo Ab SECONDARY GEARBOX FOR MOTOR VEHICLES AND VEHICLE TRANSMISSION INCORPORATING THIS GEARBOX
DE4121757A1 (en) 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen RANGE GEARBOXES FOR MOTOR VEHICLES
DE4121709A1 (en) * 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen Planetary drive for vehicle - uses combination of two couplings to reduce gear tooth load

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1201744A (en) * 1957-08-28 1960-01-05 Eaton Axles Ltd Improvements to timing devices for toothed clutch
CS152065B1 (en) * 1969-12-04 1973-12-19
DE3330303A1 (en) * 1983-08-23 1985-03-14 Volkswagenwerk Ag, 3180 Wolfsburg Gear arrangement for vehicles, especially motor vehicles
SE450944B (en) * 1983-12-06 1987-08-17 Volvo Ab RANGEVEXELLADA FOR MOTOR VEHICLES
DE3844166C1 (en) * 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 (en) * 1982-06-07 1983-12-09 Volvo Ab SECONDARY GEARBOX FOR MOTOR VEHICLES AND VEHICLE TRANSMISSION INCORPORATING THIS GEARBOX
DE4121757A1 (en) 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen RANGE GEARBOXES FOR MOTOR VEHICLES
DE4121709A1 (en) * 1990-07-03 1992-01-09 Zahnradfabrik Friedrichshafen Planetary drive for vehicle - uses combination of two couplings to reduce gear tooth load

Also Published As

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

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