EP1725791A1 - Selecteur de vitesses et transmission - Google Patents

Selecteur de vitesses et transmission

Info

Publication number
EP1725791A1
EP1725791A1 EP05717905A EP05717905A EP1725791A1 EP 1725791 A1 EP1725791 A1 EP 1725791A1 EP 05717905 A EP05717905 A EP 05717905A EP 05717905 A EP05717905 A EP 05717905A EP 1725791 A1 EP1725791 A1 EP 1725791A1
Authority
EP
European Patent Office
Prior art keywords
fluid
shaft
transmission
actuator according
actuator
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP05717905A
Other languages
German (de)
English (en)
Inventor
John Pius Burke
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ricardo UK Ltd
Original Assignee
Ricardo UK Ltd
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 Ricardo UK Ltd filed Critical Ricardo UK Ltd
Publication of EP1725791A1 publication Critical patent/EP1725791A1/fr
Withdrawn legal-status Critical Current

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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0432—Lubricant guiding means on or inside shift rods or shift forks
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • F16H2061/307—Actuators with three or more defined positions, e.g. three position servos
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
    • 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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F16H57/0423—Lubricant guiding means mounted or supported on the casing, e.g. shields or baffles for collecting lubricant, tubes or pipes
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0458—Oil-mist or spray lubrication; Means to reduce foam formation
    • F16H57/046—Oil-mist or spray lubrication
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0493—Gearings with spur or bevel gears
    • F16H57/0494—Gearings with spur or bevel gears with variable gear ratio or for reversing rotary motion

Definitions

  • This invention relates to improvements in gear selectors for gear transmissions, especially twin clutch transmissions.
  • a twin clutch transmission generally comprises a manual multi-speed gear set in which the drive to individual gear pairs is alternately through one of two clutches.
  • the 'odd' ratios e.g. first and third
  • the even ratios e.g. second and fourth
  • Additional ratios can be added if necessary.
  • This arrangement permits pre-selection of one adjacent ratio so that a 'hot' gear shift is obtained by disengaging one clutch as the other is engaged.
  • This kind of transmission is conceptually relatively simple, and permits the use of conventional gears and other components of a manual transmission to produce a semi or fully automatic transmission.
  • a known six speed twin clutch transmission has co-axial input shafts driving 'odd' and 'even' input gear clusters.
  • Twin layshafts carry constant mesh output gears, and conventional synchromesh hubs for engaging the required output gears to the respective layshaft.
  • Such an arrangement provides a short but relatively wide transmission, well suited to front wheel drive vehicles in which space between the driving wheels is restricted by steering and suspension arrangements.
  • a shift actuator for a gear transmission having an actuating axis and comprising a housing defining a plurality of adjacent fluid chambers about said axis and a plurality of fluid members one in each fluid chamber and reciprocally movable longitudinally of said axis from a respective mid position to two respective end positions, the actuator further comprising a plurality of telescopic shafts reciprocal along said axis, one each connected to a respective fluid member, and the distal end of each shaft being adapted for connection to a gear selector.
  • two shafts are provided, the inner shaft protruding from the outer shaft, and each shaft having a selector fork protruding at one side for engagement with the ring of a synchromesh coupling.
  • two concentric shafts can engage four loose gear with the shaft on which the gears rotate.
  • the fluid chambers are adapted to hydraulic fluid under pressure, and the fluid members are pistons reciprocal in respective bores of the chambers.
  • the fluid members may comprise diaphragms.
  • the fluid members may be returned to the centre position by resilient means, but in the preferred embodiment incorporate hydraulic centring whereby the centre position is assured by application of pressure to both sides.
  • the inner telescopic member defines a fluid pathway, the outer telescopic member having apertures in the wall thereof, one said apertures being aligned with said pathway in the end position of one respective actuator and the centre position of the other respective actuator.
  • Such an arrangement may be used to direct a jet of fluid under pressure from within the telescopic members to the exterior thereof.
  • the telescopic members may further include anti-rotation means to prevent relative rotation with respect to each other, and relative rotation with respect to said housing.
  • the actuator further includes a tubular member fixed relative to said housing and engaging the distal end of the innermost shaft.
  • the tubular member engages the innermost shaft internally.
  • the housing may be mounted at one end, and the tubular member at the other end, so that the actuator extends along the full length of the layshaft.
  • the inner ram is tubular; this arrangement reduces inertia and manufacturing cost, and provides the fluid pathway via apertures in the wall thereof.
  • the inner ram could be solid, and define passageways for providing fluid to apertures of a tubular outer ram.
  • the apertures permit fluid to be sprayed on gear pairs which are driving, and allows both lubrications and cooling.
  • the invention comprises a twin clutch gear transmission having a shift actuator according to the first aspect, the distal end of each ram being connected to a double acting gear selector hub of the transmission.
  • the transmission has twin layshafts, and two of said actuators are provided, one each in association with each layshaft.
  • the transmission has an input shaft axis and two parallel layshaft axes, the actuators being located within a boundary defined by radii of the input shaft axis and passing through each layshaft axis.
  • the actuators are provided side by side about a radius substantially bisecting said radii.
  • the transmission may further include one or more fluid passageways aligned with one or more external apertures of the outer telescopic ram and adapted to direct fluid to gears of the transmission.
  • Such passageways may comprise pipes mounted in the transmission casing and directed to spray fluid at the leading edge of a gear pair, so as to cool and lubricate the gear teeth immediately prior engagement thereof.
  • Said pipes may be grouped as a spray bar assembly in any suitable and convenient manner.
  • the invention comprises a fluid component assembly for a twin clutch gear transmission, the assembly comprising a substantially tubular housing having one end adapted for attachment to an engine and the other end adapted for attachment to a gear set, and the tubular housing having a wall transverse to the axis thereof, the wall being adapted on one side to support a twin clutch pack for rotation, and on the other side to support a fluid valve block, whereby in use the valve block lies between the clutch pack and gear set.
  • Such an arrangement is compact, and provides for a fluid component sub-assembly for connection to a gear set sub-assembly, to the intent that each sub-assembly may be manufactured and/or tested in a separate facility.
  • the transverse wall is a partition wall, and is substantially to the centre of said tubular housing.
  • said wall defines with said valve block a plurality of fluid passageways for directing fluid under pressure within said transmission.
  • the transverse wall includes necessary aperture for output shafts of the clutch pack.
  • said transverse wall has on the engine side a collar projecting from said aperture and co-axial therewith, the collar being adapted to support the clutch pack casing for rotation, and including fluid passageways therein for supplying fluid under pressure to said clutch pack.
  • transverse wall is further adapted for mounting of an oil pump thereon on the gear set side.
  • Said wall may further be adapted for mounting of one or more actuators thereon.
  • the transverse wall provides fluid connection between the valve block, pump, actuator(s) and clutch pack in use.
  • the fluid component casing includes a pump assembled thereto, and further includes an aperture for a pump drive shaft whereby the pump is on one side of the wall, and the drive is provided on the other side.
  • the casing may further include the valve block, clutch pack and or shift actuator(s) as a sub-assembly.
  • Such a sub-assembly can be conveniently tested as a unit for fluid integrity and performance before connection to the gear set.
  • the invention comprises a m dular twin clutch transmission comprising a gear module having a housing and including gears, input shafts and layshaft assembled thereto, and a hydraulic module comprising a housing and having twin clutch pack, pump and valve block assembled thereto whereby the modules are adapted for assembly and testing at locations remote from each other.
  • the modular transmission may further include a final drive module comprising a housing having final drive gears assembled thereto.
  • the invention comprises a transmission assembly having a transmission axis, and sequentially along said axis a clutch and a gear transmission, wherein said assembly has a final drive including opposite co-axial output shafts extending transversely of said axis, the final drive including on one side of said axis a crown wheel and pinion, and on the other side of said axis a differential gear.
  • the transmission assembly is a twin clutch, twin layshaft transmission, and in the preferred embodiment the axis of said output shafts is between said clutch and gear transmission.
  • Fig. 1 is a developed plan view of a schematic twin clutch transmission according to one aspect of the invention
  • Fig. 2 is a schematic end view of the transmission of Fig. 1 showing the true relationship of input shafts and layshafts;
  • Fig. 3 is a schematic longitudinal section through an actuator according to the invention.
  • Fig. 4 is a schematic axial section through a hydraulic module of the invention.
  • Figs. 5-8 show several similar transmission having a common gear module.
  • Fig. 1 illustrates schematically a seven speed twin clutch transmission according to the invention.
  • An input shaft 11 drives the casing of a conventional twin multi plate wet clutch 12 from which extends concentric output shafts 13,14.
  • the centre shaft 13 is fast with input gears of the Odd' ratios 1,3,5,7, whilst the hollow shaft 14 is fast with the 'even' ratios 2,4,6, and a reverse ratio comprising idler 15 and output gear 16. Reverse ratio will not be further described, but is conventional.
  • Twin layshafts 17,18 receive the loose output gears of the individual ratios as illustrated, which are grouped in pairs so that four synchromesh dog clutches 19 are shiftable to the left and to the right to engage each of the seven forward and one reverse ratio, as required.
  • Each layshaft drives an output shaft 20 via gear train 21.
  • Partition walls 22-25 of the transmission support the various shafts and act as a casing for the transmission.
  • valve block 26 and oil pump 27 are provided between the twin clutch 12 and the gears, as illustrated, and will be further described below.
  • Fig. 1 illustrates the transmission as a developed plan.
  • Fig. 2 is a schematic cross-section showing the approximate location of respective shafts of a typical transmission, and some representative gears.
  • the input shafts 13,14 and layshafts 17,18 are arranged at the apices of triangle. Conventionally the input shafts are at the top.
  • Reverse gear idler 15 and output gear are shown by a solid line, whereas second ratio gears '2' and the first ratio layshaft gear T are shown in dotted outline.
  • a mechanism for shifting the synchromesh hubs 19 can be mounted in the space around the layshaft, but for packaging purposes the region on either side of the second rather input gear (represented by actuator 30A) , or between and below the layshafts (represented by actuator 30B) is advantageous.
  • a shift actuator 30 is illustrated in Fig. 3, and comprises concentric shafts 31,32 as illustrated, each being reciprocated in use by a respective double acting piston 33,34 at one end.
  • the inner shaft 31 is hollow, and supported at the end remote from the pistons by a stub shaft 35 projecting from a wall 36 of the gearbox casing.
  • each of the shafts 31,32 is a respective shift fork 37,38 which couples conventionally with a respective synchromesh hub on one of the transmission layshafts 17,18.
  • the forks 37,38 may be shifted to the left and to the right by introducing hydraulic fluid under pressure to the appropriate side of the respective piston 33,34, and shifted back to the centre position by, for example releasing fluid on the pressurized side and allowing the fork to return under a resilient load.
  • the piston may centralize under hydraulic pressure applied to both sides.
  • Typical locations for a shift actuator are illustrated in Fig. 2 and marked by reference numerals 30A and 3 OB. It will be appreciated that one such actuator is required for each layshaft 17,18, and that both actuators could be housed in the transmission adjacently between and below the layshafts.
  • the inner shaft 31 is hollow and slides within and relative to the outer shaft 32.
  • the stub shaft 35 slides within the inner shaft 31.
  • Apertures 39 are provided in the respective shafts, and are aligned in pairs when a fork is shifted to the left or to the right. Thus when both forks 37,38 are in the neutral condition, as illustrated, no layshaft gears are engaged with a layshaft, and no apertures are aligned.
  • the apertures may be aligned to spray lubricant on the gear ratio which is engaged and is transmitting drive through the transmission.
  • This spray can both cool the gears and reduce friction, so providing transmission efficiency. It will be appreciated that the arrangement is particularly effective since fluid is sprayed only on the gears of the ratio(s) which are engaged at any time.
  • Fluid under pressure can be introduced into the inner shaft 31 in any suitable manner, but is typically via the ends.
  • the preferred embodiment arranges the dual pistons immediately adjacent the input end of the transmission, and thus next to the valve block 26 and pump 27. This arrangement minimizes hydraulic path length, and avoids long passages by which fluid under pressure is supplied to the piston chambers, and to the inner shaft 31 for lubrication.
  • lubrication oil should be sprayed on the gears from the leading side so as to the immediately drawn into the tooth contact region.
  • the shift actuator may however be located on the trailing side of the gears.
  • a suitable static duct or multiple duct spray bar can be provided, and mounted on an internal wall of the transmission, to take fluid from the outlet aperture of the actuator 30 to the required location.
  • a duct comprises a simple pipe 41 having an inlet end 42 in sliding contact with the outer surface of the respective shaft 31,32, and the outlet end 43 pointing at the leading side of the respective gear set.
  • Such a pipe is illustrated by way of example in Fig. 2 showing a path from actuator 30B.
  • Plainly actuator 30A could for example spray oil directly into the leading side of second speed gears '2'.
  • FIG. 4 illustrates modularity of one aspect of the invention.
  • a front housing 50 connects on engine 51 to that part 52 of a twin clutch transmission which houses the gears.
  • a partition wall 22 Within the housing is a partition wall 22, on the engine side of which is located the twin clutch assembly, and on the gearbox side of which is located the valve block and oil pump.
  • a collar 53 On the engine side of the partition wall is mounted a collar 53 which surrounds the input shafts of the gearbox (not illustrated).
  • gear set and gear casing can be manufactured separately from the remainder of the transmission. This means that a production facility for manual transmissions can without difficulty produce the gear set assembly and ship it to an assembly location. No change to this facility needs to be made in order to accommodate production and assembly of hydraulic components.
  • the associated advantage is that the hydraulic components, particularly the valve block can be produced and tested and assembled in a conventional facility adapted to the appropriate standards.
  • partition wall 22 not only provides a convenient mounting surface for the valve block and pump, but can also provide the necessary fluid pathways to the wet clutch pack, and to the piston end of the shift actuators 30. It will be understood that the shift actuators can, if required form part of this 'hydraulic' sub-assembly and be mounted directly with respect to the partition wall.
  • the collar 53 On the engine side the collar 53 both supports the clutch housing for rotation thereon, and provides internal fluid pathways for clutch actuation and lubrication.
  • the valve block 26 typically comprises an electro-hydraulic unit having a plurality of hydraulic passageways and valves, and an electronic control module thereon.
  • the control module is mounted to the exterior of the valve block, on the gear transmission side, and communicates with the vehicle electrical system via a multi-terminal connector on the top surface of the front housing 50. This arrangement ensures that hydraulic and electrical testing of the sub-assembly can be completed prior to shipping to a final assembly facility.
  • Figs. 5-8 illustrate modularity of a transmission according to the invention.
  • a conventional rear drive transmission is illustrated (as shown in Fig. 1) in which a gear set 60 has on the front side a hydraulic assembly 61 comprising clutch pack 62, valve block 63, pump 64 and other hydraulic components. On the rear side is a transfer gear set 65 and a single propeller shaft 66 as output. A partition wall 67 is provided in the hydraulic assembly on which the major hydraulic components are mounted.
  • a front drive assembly has opposite drive shafts 71, a gear set 60 as in Fig. 5, and an end plate 72.
  • Two partition walls 73,74 respectively mount the clutch pack and valve block/pump.
  • a crown wheel 75 is provided at one side, and a differential gear 76 at the other side.
  • the layshafts are coupled at the clutch end to a pinion for driving connection to the crown wheel.
  • Drive is transmitted to the differential carrier across the transmission, and above or below the input shafts.
  • Output from the differential gear is conventional.
  • This arrangement is particularly space-efficient since the crown wheel and differential gear are provided on either side of the input shafts rather than comprising a combined assembly on one side.
  • the transmission protrudes minimally on both sides, and is substantially symmetrical.
  • Fig. 7 is similar to Fig. 5 but has an integrated rear axle 77 with opposite drive shafts 78.
  • Fig. 8 is similar to Fig. 7 but has a bolt-on transaxle 79, also with opposite drive shafts 78.

Landscapes

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

Abstract

L'invention concerne un sélecteur de vitesses comprenant des arbres télescopiques creux (31, 32) dont les extrémités peuvent être reliées à des moyeux de sélecteur d'une transmission par engrenages. Les arbres (31, 32) peuvent être creux et comportent des ouvertures (39) qui s'alignent de sorte à permettre l'application d'un lubrifiant depuis l'intérieur sur une paire sélectionnée d'engrenages. L'invention concerne également de nouvelles configurations de transmission.
EP05717905A 2004-03-05 2005-03-04 Selecteur de vitesses et transmission Withdrawn EP1725791A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB0405094.4A GB0405094D0 (en) 2004-03-05 2004-03-05 Twin clutch transmission
PCT/GB2005/000835 WO2005085683A1 (fr) 2004-03-05 2005-03-04 Selecteur de vitesses et transmission

Publications (1)

Publication Number Publication Date
EP1725791A1 true EP1725791A1 (fr) 2006-11-29

Family

ID=32088850

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05717905A Withdrawn EP1725791A1 (fr) 2004-03-05 2005-03-04 Selecteur de vitesses et transmission

Country Status (3)

Country Link
EP (1) EP1725791A1 (fr)
GB (1) GB0405094D0 (fr)
WO (1) WO2005085683A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110088511A (zh) * 2016-12-23 2019-08-02 沃尔沃卡车集团 用于车辆的变速器的换档装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE542899C2 (en) * 2018-09-18 2020-08-18 Scania Cv Ab Retarder Arrangement and Related Devices

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55106823A (en) * 1979-02-07 1980-08-16 Nissan Motor Co Ltd Transmission for automobile
DE3527390A1 (de) * 1985-07-31 1987-02-05 Klaue Hermann Stirnradwechselgetriebe mit einer antriebs- und einer die achsantriebswelle bildenden abtriebswelle, insbesondere fuer personenkraftwagen
US4719812A (en) * 1985-08-29 1988-01-19 Kubota, Ltd. Transmission casing including a hydraulic clutch
GB9218202D0 (en) * 1992-08-27 1992-10-14 Lotus Car Transmission unit and engagement means for a shaft and gear

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005085683A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110088511A (zh) * 2016-12-23 2019-08-02 沃尔沃卡车集团 用于车辆的变速器的换档装置
CN110088511B (zh) * 2016-12-23 2020-10-27 沃尔沃卡车集团 用于车辆的变速器的换档装置

Also Published As

Publication number Publication date
WO2005085683A1 (fr) 2005-09-15
GB0405094D0 (en) 2004-04-07

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