EP0993570A1 - Boite de vitesses compacte - Google Patents
Boite de vitesses compacteInfo
- Publication number
- EP0993570A1 EP0993570A1 EP99916966A EP99916966A EP0993570A1 EP 0993570 A1 EP0993570 A1 EP 0993570A1 EP 99916966 A EP99916966 A EP 99916966A EP 99916966 A EP99916966 A EP 99916966A EP 0993570 A1 EP0993570 A1 EP 0993570A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- gearbox
- gear
- fork
- shafts
- 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- Withdrawn
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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/32—Gear shift yokes, e.g. 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
- F16H63/20—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate
-
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H2063/3086—Shift head arrangements, e.g. forms or arrangements of shift heads for preselection or shifting
-
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/3069—Interrelationship between two or more final output mechanisms
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19377—Slidable keys or clutches
- Y10T74/19414—Single clutch shaft
- Y10T74/1947—Selective
- Y10T74/19474—Multiple key
- Y10T74/19479—Spur gears
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/20—Control lever and linkage systems
- Y10T74/20012—Multiple controlled elements
- Y10T74/20018—Transmission control
- Y10T74/20177—Particular element [e.g., shift fork, template, etc.]
- Y10T74/20183—Shift fork structure
Definitions
- the invention relates to a gearbox for a motor vehicle.
- the invention relates more particularly to a motor vehicle gearbox, of the type comprising at least two parallel primary and secondary longitudinal shafts, of the type comprising at least two gears in each of which a non-idler pig, mounted for rotation on a first shaft, meshes with a fixed pinion carried by a second shaft, and of the type comprising means of interconnection of each idler pinion on its shaft by means of axially movable coaxial rings, under the action of control means comprising control forks which are slidably mounted parallel to the shafts, each of which is provided with a transverse leg at the end of which a contact key is arranged, the keys being aligned transversely in an arc to be received in a fork of an actuator which can be ordered in transverse movement along the arc to select a suitable range ciée to a gear ratio, and parallel to the shafts to engage the gear associated with the selected range by moving longitudinally a clutch ring of the idler gear corresponding to this ratio.
- gearboxes comprising control means for the interconnection of idler pinions on the shafts which carry them, so as to cause their meshing with associated fixed pinions belonging to at least one other shaft and thus selectively engage gear ratios. determined reduction associated with said idler gears.
- Automobile gearboxes conventionally use clutch devices with synchronizers of the type of those mentioned above, said synchronizers being capable of being moved axially by forks, carried by axes, and capable of being actuated longitudinally. the driver of the vehicle using a gear shift lever arranged inside the vehicle cabin.
- the gearshift lever actuates a linkage which acts directly on the forks, and in the case of a so-called “robotized” or automated control gearbox, the gear shift lever indirectly controls the movement of the forks, in particular by means of jacks or other types of actuators.
- Document FR-A-2,609.1 38 describes such a device.
- This document describes more particularly an automated gearbox architecture in which the clutching of the idler sprockets on their shaft and the displacement of the synchronizers parallel to this shaft is achieved by forks displaced by actuators, in this case jacks. Each fork is moved by an associated actuator.
- This arrangement is particularly cumbersome because it requires a large number of forks, fork axes and actuators.
- an actuator comprises an arm at the end of which a key is capable of being displaced in rotation and in translation in order to respectively select a fork and engage a gear associated with the fork considered by moving it parallel to the shaft of the box.
- the device described has a definite advantage over the previous one in that the number of actuators is considerably reduced. However, it remains very bulky due to the multiplicity of fork axes and their arrangement in which they are distributed transversely.
- the invention proposes to improve the compactness of the gearbox by reducing its transverse dimensions.
- the invention provides a gearbox of the type mentioned above, characterized in that all of the control forks are slidably mounted on a common axis of forks, parallel to the shafts. According to other characteristics of the invention:
- a dog clutch at most is arranged near a idler gear, to selectively occupy a neutral position or a dog clutch position of the only pinion considered corresponding to the engagement of a gear ratio, and in that the others interconnection rings are arranged between two idlers, to occupy a neutral position or two opposite positions of interconnection of each of the idlers considered, located axially on either side of the neutral position and each corresponding to the engagement of a gear ratio;
- the actuator comprises a rod, longitudinal and parallel to the shafts, which comprises a transverse arm with the end of which the fork is arranged, which can occupy several predefined angular positions of selection, which each correspond to the selection of a fork, and at least two predefined longitudinal positions of passage, which comprise at least one extreme longitudinal position d 'engagement of a gear ratio and a neutral position;
- the axis of the forks is coaxial with the rod of the actuator; - the idler gears and the associated clutching rings are arranged axially on the first shaft of the gearbox;
- the gearbox is a robotically controlled gearbox and the actuator is a roto-linear actuator driven by stepping motors, controlled in response to movements of a shift lever of the vehicle on which acts the driver ;
- the gearbox is manually controlled and the actuator is connected by a linkage to the gear shift lever of the vehicle on which the driver acts.
- FIG. 1 is a perspective view of the control means of a gearbox according to the invention in which one of the forks is illustrated in its position of selection and engagement of a report;
- - Figure 2 is a top view of the control means according to fig ure 1 in which all the forks are illustrated in neutral position;
- FIG. 3 is a view along the axis of the forks of the control means according to FIG. 2.
- the figures show all of the control means 10 of a gearbox (not shown), according to an embodiment of the invention.
- forks 12 are capable of sliding longitudinally in a longitudinal direction to cooperate with rings (not shown) for clutching idler sprockets (not shown) of the gearbox.
- the longitudinal displacement along L of the clutching rings by the forks 12 causes, for each of the idler sprockets, the clutching of the idler sprocket on the shaft which carries it and the engagement of a gear ratio.
- the idler gears allowing the engagement of the different ratios of the gearbox are seven in number and controlled by the interconnection of four rings arranged, like the idler gears, on a shaft common of the gearbox.
- the forks 12 extend transversely downward from an axis 14 for guiding the forks 12, of longitudinal geometric axis A1, which allows their longitudinal displacement along L by means of sleeves 16 guide forks 12, slidably mounted on the fork axis 14.
- the fork axis 14 is cylindrical and has a longitudinal keying groove 18, intended to cooperate with a key shape 20, carried by a bore 22 of each sleeves 16 of the forks 12.
- each fork 12 has a transverse leg 22, substantially diametrically opposite the fork 12 relative to the fork axis 14, integrally formed with the sleeve 16, and comprising at its free end a control key 24, which has two bearing surfaces 26 and 28 which are parallel and of transverse orientation.
- the sleeves 16 of the forks 12 are arranged longitudinally on the axis 14 at regular intervals, so that each fork 12 occupies a position longitudinal intermediate between two consecutive idler gears of the gearbox, so that none of the idler gear clutching rings cause the interconnection of any idler gear of the gearbox.
- control keys 24 of the forks 12 are all situated in the same transverse plane and, as can be seen more precisely in FIG. 3, they are arranged in an arc of a circle C in this vertical transverse plane.
- This arrangement is made possible by a particular shape of each of the transverse arms 22 which are bent to extend transversely and longitudinally so that the keys 24 are copianary in the transverse plane.
- the gearbox comprises an actuator 30, arranged above the axis 14 of the forks 12, and including a longitudinal rod 32 and axis A2, parallel to the shaft which carries the clutching rings of the gearbox, comprises a transverse arm 34 at the end of which is arranged a control fork 36.
- the axis A2 of the rod 32 of the actuator 30 and the axis A1 of the fork axis 14 can be combined to advantageously reduce the total size of the control means.
- the actuator 30 is a rotolinear cylinder which controls displacements of the rod 32 in translation along the longitudinal direction L in both directions and in rotation in both directions around its axis longitudinal.
- the actuator may simply consist of a rod secured to a linkage of the vehicle gearbox, of a cable control, or of another mechanical transmission method, actuated by the driver by the through a gear shift lever.
- the axis A2 of the long itudinal rod 32 of the actuator 30 passes through the center C of the arc of a circle C of the keys 24 of the transverse arms 22 of the forks 12, so that the fork 36, located at the end of the arm 34 of adequate length, can move in a circular translational movement in the transverse plane of the keys 24 of the forks 12.
- the engagement of a gearbox report comprises two main phases: - a first selection phase in which, starting from a neutral neutral position of the gearbox described with reference to Figures 2 and 3, a rotational movement of the rod 32 of the actuator causes the rotational movement of the fork 36 in the transverse plane corresponding to the neutral position of the gearbox for q u 'It stops next to a button 24 of a fork 12 of the gearbox.
- the angular position of the longitudinal rod 32 of the actuator is defined by an appropriate control of a stepping motor causing a determined angle rotation of the rod 32 of the actuator 30 around its axis A2.
- a second engagement phase in which the rod 32 of the actuator 30 is moved longitudinally forwards or backwards as illustrated in FIG. 1, the fork 36 then then taking support respectively on one of the surfaces d 'support 28 or 26 of the fork 12 previously selected so as to longitudinally move this fork 12 forwards or backwards.
- the fork 12 selected causes the axial displacement of a dog clutch ring and the engagement of one of the ratios associated with this ring.
- the longitudinal rod 32 of the actuator When changing from one gear ratio to another, the longitudinal rod 32 of the actuator is brought back longitudinally to the intermediate position in which it is in the transverse plane corresponding to the neutral position of the gearbox, then is moved axially to its other engagement position of the other ratio associated with this ring, or is rotated to another key 24 of another fork 12 of the gearbox, then is again moved longitudinally to initiate another gearbox report.
- the arrangement of the forks 12 on a single and common axis 14 considerably simplifies the arrangement of the forks 12 in the casing of the gearbox, and allows the production of a gearbox substantially more compact than the gearboxes. conventional, while reducing the risk of failure of the gear engagement controls due to the reduction in the number of mechanical parts involved.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear-Shifting Mechanisms (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9805675A FR2778444B1 (fr) | 1998-05-05 | 1998-05-05 | Boite de vitesses compacte |
FR9805675 | 1998-05-05 | ||
PCT/FR1999/001034 WO1999057463A1 (fr) | 1998-05-05 | 1999-04-30 | Boite de vitesses compacte |
Publications (1)
Publication Number | Publication Date |
---|---|
EP0993570A1 true EP0993570A1 (fr) | 2000-04-19 |
Family
ID=9526046
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99916966A Withdrawn EP0993570A1 (fr) | 1998-05-05 | 1999-04-30 | Boite de vitesses compacte |
Country Status (5)
Country | Link |
---|---|
US (1) | US6389919B1 (fr) |
EP (1) | EP0993570A1 (fr) |
KR (1) | KR20010021703A (fr) |
FR (1) | FR2778444B1 (fr) |
WO (1) | WO1999057463A1 (fr) |
Families Citing this family (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19951683A1 (de) * | 1999-10-27 | 2001-05-03 | Zahnradfabrik Friedrichshafen | Einstangen-Schalteinrichtung für Kraftfahrzeug-Handschaltgetriebe |
DE10191680B4 (de) * | 2000-04-28 | 2020-03-19 | Schaeffler Technologies AG & Co. KG | Betätigungseinrichtung für ein Getriebe |
FR2830597B1 (fr) * | 2001-10-04 | 2004-08-27 | Peugeot Citroen Automobiles Sa | Dispositif de commande de boite de vitesses a selection par rotation d'un arbre de commande |
DE10148980A1 (de) * | 2001-10-04 | 2003-04-10 | Ina Schaeffler Kg | Schaltarm |
DE10150054A1 (de) * | 2001-10-10 | 2003-04-17 | Bayerische Motoren Werke Ag | Schaltgetriebe |
FR2850441B1 (fr) * | 2003-01-24 | 2005-03-11 | Renault Sa | Dispositif de commande interne de boite de vitesses mecanique |
SE0400621L (sv) | 2004-03-12 | 2005-09-13 | Kongsberg Automotive Asa | System för att utföra växling |
FR2868144B1 (fr) * | 2004-03-23 | 2007-06-01 | Peugeot Citroen Automobiles Sa | Systeme de commande interne de boite de vitesses |
EP1596103B1 (fr) * | 2004-04-06 | 2008-02-20 | Getrag Ford Transmissions GmbH | Actionneur pour boîte de vitesse automatisée |
SE529176C2 (sv) * | 2004-06-30 | 2007-05-22 | Kongsberg Automotive Asa | System för skifte av gir |
CN100455852C (zh) * | 2005-06-20 | 2009-01-28 | 上海依赛工业有限公司 | 汽车换挡机构的拨叉装置 |
US7845249B2 (en) * | 2006-09-08 | 2010-12-07 | Schaeffler Technologies Gmbh & Co. Kg | Single motor transmission shifting mechanism for a motor vehicle transmission |
SE530675C2 (sv) * | 2006-12-13 | 2008-08-12 | Scania Cv Ab | Manöveranordning för differentialspärr |
US7861613B2 (en) * | 2007-04-17 | 2011-01-04 | Eaton Corporation | Selector mechanism for dual-clutch transmissions |
CN101457831B (zh) * | 2007-12-13 | 2012-09-05 | 比亚迪股份有限公司 | 变速器的自动换档机构和自动换挡系统 |
DE102008031815B4 (de) * | 2008-06-25 | 2019-05-16 | GETRAG B.V. & Co. KG | Schaltanordnung für ein Kraftfahrzeuggetriebe |
EP2189681B1 (fr) * | 2008-11-25 | 2011-06-08 | Magneti Marelli S.p.A. | Boîte de vitesse à double embrayage |
DE102009014312A1 (de) * | 2009-03-25 | 2010-09-30 | Valeo Systèmes d'Essuyage | Elektromotorischer Hilfsantrieb, insbesondere Wischerantrieb |
US8627739B2 (en) * | 2009-09-15 | 2014-01-14 | GM Global Technology Operations LLC | Dual fork single shift rail assembly |
EP2556277B1 (fr) * | 2010-04-06 | 2014-01-15 | Kongsberg Automotive AB | Ensemble fourchette de changement de vitesse |
US20150308567A1 (en) * | 2014-04-28 | 2015-10-29 | Deere & Company | Gear shifter arrangement |
KR101637693B1 (ko) * | 2014-10-15 | 2016-07-08 | 현대자동차주식회사 | 수동변속기용 변속 장치 |
US10738887B2 (en) * | 2018-02-06 | 2020-08-11 | Arvinmeritor Technology, Llc | Shift fork and method of manufacture |
CN110594369A (zh) * | 2019-09-24 | 2019-12-20 | 浙江宇田新能源科技有限公司 | 一种电动车辆的二档减速器 |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE839903C (de) * | 1949-04-08 | 1952-05-26 | Kloeckner Humboldt Deutz Ag | Wechselgetriebe und Gruppengetriebe von Kraftfahrzeugen |
GB935501A (en) * | 1960-09-16 | 1963-08-28 | Vauxhall Motors Ltd | Improvements relating to change-speed gear mechanisms |
GB983563A (en) * | 1963-04-11 | 1965-02-17 | Vauxhall Motors Ltd | Improvements relating to change-speed gear mechanisms |
GB1186791A (en) * | 1968-01-18 | 1970-04-02 | Vauxhall Motors Ltd | Change-Speed Gear Mechanisms |
US3929029A (en) * | 1974-02-25 | 1975-12-30 | Borg Warner | Transmission shift control linkage |
US4320824A (en) * | 1980-01-04 | 1982-03-23 | Nissan Motor Company, Limited | Clutch housing for a transmission |
DE3001935C2 (de) * | 1980-01-21 | 1982-09-16 | Ford-Werke Ag, 5000 Koeln | Schaltvorrichtung für ein Wechselgetriebe |
JPS57137750A (en) * | 1981-02-20 | 1982-08-25 | Nissan Motor Co Ltd | Operator for change gear |
USRE34260E (en) * | 1989-06-19 | 1993-05-25 | Eaton Corporation | Dual pressure pressurized fluid actuated shifting mechanism |
US5251503A (en) * | 1991-09-12 | 1993-10-12 | General Motors Corporation | Electro-mechanical power controller for a gear shift mechanism |
GB9221205D0 (en) * | 1992-10-08 | 1992-11-25 | Massey Ferguson Sa | Transmission units |
DE19610104C2 (de) * | 1996-03-15 | 1999-07-01 | Daimler Chrysler Ag | Schaltvorrichtung für ein Zahnräderwechselgetriebe sowie Verfahren zum Steuern dafür |
US5743143A (en) * | 1996-08-09 | 1998-04-28 | Eaton Corporation | Transmission shifting mechanism and position sensor |
-
1998
- 1998-05-05 FR FR9805675A patent/FR2778444B1/fr not_active Expired - Fee Related
-
1999
- 1999-04-30 WO PCT/FR1999/001034 patent/WO1999057463A1/fr not_active Application Discontinuation
- 1999-04-30 US US09/462,070 patent/US6389919B1/en not_active Expired - Fee Related
- 1999-04-30 KR KR1020007000262A patent/KR20010021703A/ko not_active Application Discontinuation
- 1999-04-30 EP EP99916966A patent/EP0993570A1/fr not_active Withdrawn
Non-Patent Citations (1)
Title |
---|
See references of WO9957463A1 * |
Also Published As
Publication number | Publication date |
---|---|
FR2778444B1 (fr) | 2000-06-23 |
WO1999057463A1 (fr) | 1999-11-11 |
FR2778444A1 (fr) | 1999-11-12 |
US6389919B1 (en) | 2002-05-21 |
KR20010021703A (ko) | 2001-03-15 |
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