WO2005028902A1 - Double clutch with a double control thrust bearing, in particular for a motor vehicle - Google Patents
Double clutch with a double control thrust bearing, in particular for a motor vehicle Download PDFInfo
- Publication number
- WO2005028902A1 WO2005028902A1 PCT/FR2004/050409 FR2004050409W WO2005028902A1 WO 2005028902 A1 WO2005028902 A1 WO 2005028902A1 FR 2004050409 W FR2004050409 W FR 2004050409W WO 2005028902 A1 WO2005028902 A1 WO 2005028902A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- fork
- double clutch
- guide tube
- sleeve
- axis
- Prior art date
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
- F16D13/385—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs double clutches, i.e. comprising two friction disc mounted on one driven shaft
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
- F16D13/40—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs in which the or each axially-movable member is pressed exclusively against an axially-located member
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
- F16D23/148—Guide-sleeve receiving the clutch release bearing
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0684—Mechanically actuated clutches with two clutch plates
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
- F16D2023/141—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings characterised by using a fork; Details of forks
Definitions
- the present invention relates to a double clutch, in particular for a motor vehicle, with double control stop.
- a double clutch usually makes it possible to couple the shaft of a vehicle engine alternately with two coaxial input shafts of a gearbox, known as a double clutch gearbox.
- a double clutch makes it possible to change the gear ratio while maintaining the transmission of an engine torque to the vehicle wheels.
- a double clutch usually comprises two clutches associated respectively with even and odd gear ratios.
- a first clutch is disengaged while the second clutch is engaged so that the engine torque is gradually transferred from the first to the second clutch.
- the sum of the torques transmitted by the first and second clutches is always substantially equal to the engine torque.
- a double clutch usually comprises a cover in which are housed two clutches for shifting ratios of different parities.
- Each clutch comprises a mechanism comprising a diaphragm intended to cooperate with a pressure plate integral in rotation with the cover and the motor shaft.
- Each diaphragm can be moved, by means of a corresponding control stop, between a rest position and an active position.
- the active position of the diaphragm corresponds to a coupling or uncoupling of the motor and gearbox shafts and the rest position of the diaphragm corresponds to a decoupling or coupling of these motor and gearbox shafts speeds.
- the two sleeves of the control stops slide respectively on the external surfaces of two coaxial guide tubes.
- the first sleeve, external is slidably mounted on the external surface of the second sleeve, internal.
- This internal sleeve, slidably mounted on a guide tube, itself forms another guide tube for the external sleeve.
- the object of the invention is in particular to propose a double clutch of simple structure and of reduced bulk, this ensuring an efficient operation.
- the invention relates to a double clutch of the aforementioned type, characterized in that the guide tube is common to the two stops, the first and second sleeves being slidably mounted on the external and internal surfaces of the guide tube respectively. .
- Such a double clutch makes it possible to guide the two control stops using a single guide tube, while limiting its axial size due to the partial overlapping of the control stops.
- a double clutch according to the invention may also include one or more of the following characteristics: - the first and second control stops are actuated respectively by first and second ⁇ forks each provided with at least one cooperating support zone with an additional support zone provided on the corresponding sleeve; - Each fork forms a lever of the second kind in which the support zone is placed between the operating and articulation ends of this fork; - Each fork is provided with two support zones with the corresponding sleeve substantially diametrically opposite with respect to the axis of this sleeve; - The guide tube is provided with passages through which extends the support area of the second fork; - The first sleeve, said external sleeve, is provided with passages through which extends the support zone of the second fork; - The outer sleeve and the guide tube are each provided with two passages substantially diametrically opposite with respect to their axis through which extend the two bearing zones of the second fork; - The second fork has a
- FIG. 1 a double clutch for a motor vehicle, designated by the general reference 10.
- the double clutch 10 has a cover 12 in which are housed two clutches for shifting ratios of different parities. These clutches respectively comprise first M1 and second M2 mechanisms intended to act on the first F1 and second F2 frictions.
- the mechanisms M1, M2 respectively comprise first 14A and second 14B diaphragms intended to cooperate with first 15A and second 15B pressure plates integral in rotation with the cover 12.
- the first diaphragm 14A cooperates with the first pressure plate 15A via of a movable member 16 of axial bracing partially visible in FIG. 1.
- first 24A and second 24B control stops each cooperating with the corresponding diaphragm 14A, 14B via a force transmission member 26A, 26B.
- Each diaphragm 14A, 14B is movable, by means of the corresponding control stop, 24A, 24B between a rest position and an active position.
- the double clutch 10 is of the type in which the active position of each diaphragm 14A, 14B corresponds to a coupling of the engine and gearbox shafts and the rest position of this diaphragm 14A , 14B corresponds to a decoupling of these engine and gearbox shafts.
- ball joints allow the angular movement of the fork for actuating the clutch. They also give an additional degree of freedom to allow adjustment of the parallelism between the bearing face of the fork and the sleeve 28A, 28B. In addition, these ball joints are particularly well suited to this double control because they are cumbersome, making it possible to accommodate the 2 joints in a reduced space, especially for that of the second fork 34B, which would be difficult to achieve with a pivot formed by an axis.
- the ball joint of the second fork 34B is placed on the end of an extension which is opposite to the axis of the clutch of the part in contact with the control coming from an actuator. This extension is housed in a hollow of the inner contour of the ring formed by the first fork 34A.
- each fork 34A, 34B is provided with at least one support area 36A, 36B cooperating with a complementary support area 38A, 38B formed on the sleeve 28A, 28B corresponding.
- the complementary support zone 38A of the external sleeve 28A is delimited by a radial projection 39A (see in particular FIGS. 2 and 4) of this external sleeve 28A, rigidified for example by axial ribs.
- the complementary support zone 38B of the internal sleeve 28B is delimited by an axial boss 39B at the end of this external sleeve 28B (see FIG. 4).
- each fork 34A, 34B is provided with two bearing zones 36A, 36B with the corresponding sleeve 28A, 28B, substantially diametrically opposite with respect to the axis of this sleeve. It will be noted, with reference to FIG. 1, that these forks 34A, 34B each form a lever of the second kind because each support zone 36A, 36B is placed between the maneuvering ends MA, MB and the articulation ends RA, RB of this lever.
- each support area 36B of the second fork 34B and each support area 38B of the internal sleeve 28B arranged inside the guide tube 30, the guide tube 30 and the external sleeve 28A are perforated by respective passages 40, 41 (see in particular Figure 2) through which extends the bearing area 36B of the second fork 34B.
- the guide tube 30 and the external sleeve 28A are each provided with two passages 40, 41, substantially diametrically opposite with respect to their axis through which the two bearing zones are understood. 36B of the second fork 34B.
- this second fork has an opening 42 for fitting around the guide tube 30 (see FIGS. 5 and 6), provided with two ends 42A, 42B of widths different.
- the wide end 42A allows the nesting of the second fork 34B around the guide tube 30 by displacement of this second fork 34B substantially parallel to the axis of this guide tube 30 (see Figure 5).
- the narrow end 42B is delimited by the support zones 36B and authorizes the nesting of these support zones 36B in the passages 40 of the guide tube 30 by displacement of the second fork 34B substantially transversely to the axis of the tube guide 30 (see Figure 6).
- the sleeves 28A, 28B can be held on their respective forks 34A, 34B, for example, by means of latching these sleeves 28A, 28B on the corresponding ranges 34A, 34B. Furthermore, provision will preferably be made for means of anti-rotation of the sleeves 28A, 28B about their respective axes so that their bearing zones 38A, 38B are always in contact with the bearing zones 36A, 36B of the fork 34A , 34B corresponding.
- the latching means of the sleeves 28A, 28B on the fork 34A, 34B can in particular form these anti-rotation means.
- the shapes of the forks 34A, 34B can be adapted as a function either of the size of the various bodies of the double clutch or of the clearances to be provided for passing certain assembly tools.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The inventive double clutch (10) comprises first (24A) and second (24B) control thrust bearings provided with first (28A) and second (28B) sleeves, respectively. Said sleeves (28A, 28B) are mounted is such a way that they are slidable on a single guiding tube (30). In fact, said first (28A) and second (28B) sleeves are mounted on the external and internal surfaces of the guiding tube (30), respectively in such a way that they are slidable. In the preferred embodiment, the first (24A) and second (24B) control thrust bearings are driven by first (34A) and second (34B) forks, respectively. Each fork (34A, 34B) is provided with at lest one complementary thrust area (38A, 38B) arranged on the corresponding sleeve.
Description
Double embrayage, notamment pour véhicule automobile, à double butée de commande. Double clutch, especially for motor vehicles, with double control stop.
La présente invention concerne un double embrayage, notamment pour véhicule automobile, à double butée de commande. Un double embrayage permet habituellement de coupler alternativement l'arbre d'un moteur du véhicule avec deux arbres coaxiaux d'entrée d'une boîte de vitesses, dite boîte de vitesses à double embrayage. Ainsi, un double embrayage permet de changer de rapport de vitesses tout en maintenant la transmission d'un couple moteur aux roues du véhicule. En effet, un double embrayage comprend habituellement deux embrayages associés respectivement à des rapports de vitesses pairs et impairs. Lors d'un changement de rapport de vitesses, un premier embrayage est débrayé alors que le second embrayage est embrayé si bien que le couple moteur est transféré progressivement du premier au second embrayage. Ainsi, la somme des couples transmis par les premier et second embrayages est toujours sensiblement égale au couple moteur. Un double embrayage comporte habituellement un couvercle dans lequel sont logés deux embrayages de passage de rapports de parités différentes. Chaque embrayage comprend un mécanisme comportant un diaphragme destiné à coopérer avec un plateau de pression solidaire en rotation du couvercle et de l'arbre du moteur. Chaque diaphragme est déplaçable, au moyen d'une butée de commande correspondante, entre une position de repos et une position active. Selon le type de l'embrayage, la position active du diaphragme correspond à un couplage ou découplage des arbres de moteur et de boîte de vitesses et la position de repos du diaphragme correspond à un découplage ou couplage de ces arbres de moteur et de boîte de vitesses. Chaque plateau de pression, sollicité par le diaphragme correspondant, est destiné à enserrer un disque de friction entre ce plateau de pression et un plateau de réaction correspondant. Chaque disque de friction est lié en rotation à un arbre correspondant de boîte de vitesses et chaque plateau de réaction est solidaire en rotation du couvercle et d'un volant lié à l'arbre moteur. Ainsi, le serrage d'un disque de friction entre les plateaux de pression et de réaction correspondants permet la transmission d'un couple entre l'arbre moteur et l'arbre de boîte de vitesses associé. On connaît déjà dans l'état de la technique, notamment d'après FR-1 300 975, un double embrayage, notamment pour véhicule automobile, du type comprenant des première et seconde butées de commande comportant des premier et second manchons respectifs montés coulissant chacun sur un tube de guidage.
Selon un mode de réalisation décrit dans FR-1 300 975, les deux manchons des butées de commande coulissent respectivement sur des surfaces externes de deux tubes de guidage coaxiaux. Selon un autre mode de réalisation décrit dans FR-1 300 975, le premier manchon, externe, est monté coulissant sur la surface externe du second manchon, interne. Ce manchon interne, monté coulissant sur un tube de guidage, forme lui même un autre tube de guidage du manchon externe. L'invention a notamment pour but de proposer un double embrayage de structure simple et d'encombrement réduit, ceci en assurant un fonctionnement efficace. A cet effet, l'invention a pour objet un double embrayage du type précité, caractérisé en ce que le tube de guidage est commun aux deux butées, les premier et second manchons étant montés coulissant sur des surfaces externe et interne respectivement du tube de guidage. Un tel double embrayage permet de guider les deux butées de commande à l'aide d'un seul tube de guidage, tout en limitant son encombrement axial du fait du recouvrement partiel des butées de commande. Un double embrayage selon l'invention peut en outre comporter l'une ou plusieurs des caractéristiques suivantes : - les première et seconde butées de commande sont actionnées respectivement par des première et secondé^fourchettes munie chacune d'au moins une zone d'appui coopérant avec une zone d'appui complémentaire ménagée sur le manchon correspondant ; - chaque fourchette forme un levier du second genre dans lequel la zone d'appui est placée entre des extrémités de manœuvre et d'articulation de cette fourchette ; - chaque fourchette est munie de deux zones d'appui avec le manchon correspondant sensiblement diamétralement opposées par rapport à l'axe de ce manchon ; - le tube de guidage est muni de passages à travers lesquels s'étend la zone d'appui de la seconde fourchette ; - le premier manchon, dit manchon externe, est muni de passages à travers lesquels s'étend la zone d'appui de la seconde fourchette ; - le manchon externe et le tube de guidage sont munis chacun de deux passages sensiblement diamétralement opposés par rapport à leur axe à travers lesquels s'étendent les deux zones d'appui de la seconde fourchette ;
- la seconde fourchette comporte une ouverture d'emboîtement autour du tube de guidage munie de deux extrémités de largeurs différentes, l'extrémité large autorisant l'emboîtement de la seconde fourchette autour du tube de guidage par déplacement de cette seconde fourchette sensiblement parallèlement à l'axe de ce tube de guidage et l'extrémité étroite étant délimitée par les zones d'appui et autorisant l'emboîtement de ces zones d'appui dans les passages du tube de guidage par déplacement de la seconde fourchette sensiblement transversalement à l'axe du tube de guidage ; - la zone d'appui complémentaire du premier manchon est délimitée par une saillie radiale de ce premier manchon ; - la zone d'appui complémentaire du second manchon est délimitée par un bossage axial d'extrémité de ce second manchon ; - les première et seconde fourchettes sont articulées autour d'axes sensiblement parallèles, la première fourchette ayant une forme générale d'anneau ovalisé entourant la seconde fourchette et délimitant un espace interne de débattement de cette seconde fourchette ; - chacune des première et seconde fourchettes est liée au carter d'embrayage par le biais d'une liaison rotule ; - les première et seconde fourchettes forment des leviers du second genre ; - la liaison rotule de la seconde fourchette est placée sur une extrémité de cette seconde fourchette dans un prolongement se trouvant à l'opposé, par rapport à un axe du double embrayage, d'une partie en contact avec une commande venant d'un actionneur, ce prolongement étant logé dans un creux d'un contour intérieur d'un anneau formé par la première fourchette ; - les axes des liaisons rotules sont, suivant l'axe du double embrayage, placés à une distance inférieure à 10 mm environ l'un de l'autre ; - les axes des liaisons rotules sont, suivant l'axe du double embrayage, placés à une distance inférieure à 5 mm environ l'un de l'autre. L'invention sera mieux comprise à la lecture de la description qui va suivre, donnée uniquement à titre d'exemple et faite en se référant aux dessins annexés dans lesquels : - la figure 1 est une vue en coupe axiale d'un double embrayage selon l'invention ; - la figure 2 est une vue en coupe axiale du double embrayage selon l'invention dans le plan de coupe 2-2 de la figure 1 ;
- la figure 3 est une vue en perspective d'un ensemble du double embrayage représenté sur les figures 1 et 2, comprenant les butées de commande agencées sur le tube de guidage, les butées de commandes coopérant chacune avec une fourchette ; - la figure 4 est une vue en perspective avec une coupe partielle de l'ensemble représenté sur la figure 3 ; - les figures 5 et 6 sont des vues en perspective d'une fourchette du double embrayage représenté sur les figures 1 et 2 agencée sur le tube de guidage. On a représenté sur les figures 1 et 2 un double embrayage pour véhicule automobile, désigné par la référence générale 10. Le double embrayage 10 comporte un couvercle 12 dans lequel sont logés deux embrayages de passage de rapports de parités différentes. Ces embrayages comprennent respectivement des premier M1 et second M2 mécanismes destinés à agir sur des première F1 et seconde F2 frictions. Les mécanismes M1, M2 comprennent respectivement des premier 14A et second 14B diaphragmes destinés à coopérer avec des premier 15A et second 15B plateaux de pression solidaires en rotation du couvercle 12. Le premier diaphragme 14A coopère avec le premier plateau de pression 15A par l'intermédiaire d'un organe mobile 16 d'entretoisement axial partiellement visible sur la figure 1. Le second diaphragme 14B coopère avec le premier plateau de pression 15B par l'intermédiaire d'une saillie annulaire 17 (continue ou discontinue angulairement) solidaire de ce premier plateau de pression 15B. Les frictions F1, F2 comprennent respectivement des premier 18A et second 18B disques de friction. Chaque plateau de pression 15A, 15B, sollicité par le diaphragme correspondant est destiné à enserrer un disque de friction 18A, 18B entre ce plateau de pression et un plateau de réaction correspondant 20A, 20B, solidaire en rotation d'un volant moteur et du couvercle 12. Les deux disques de friction 18A, 18B sont liés en rotation respectivement à deux arbres 22A, 22B de boîte de vitesses correspondant à des rapports de vitesses de parités différentes. La commande des premier et second embrayages se fait respectivement au moyen de première 24A et seconde 24B butées de commande coopérant chacune avec le diaphragme 14A, 14B correspondant par l'intermédiaire d'un organe de transmission d'effort 26A, 26B.
Chaque diaphragme 14A, 14B est déplaçable, au moyen de la butée de commande correspondante, 24A, 24B entre une position de repos et une position active. Dans le mode de réalisation illustré sur les figures, le double embrayage 10 est du type dans lequel la position active de chaque diaphragme 14A, 14B correspond à un couplage des arbres de moteur et de boîte de vitesses et la position de repos de ce diaphragme 14A, 14B correspond à un découplage de ces arbres de moteur et de boîte de vitesses. Ces première 24A et seconde 24B butées de commande comportent des premier 28A et second 28B manchons respectifs, dits manchons externe 28A et interne 28B, montés coulissant chacun sur un tube de guidage 30, commun aux deux butées 24A, 24B. Ce tube de guidage 30 est fixé sur un carter fixe 31 du double embrayage 10 au moyen d'une collerette 30A. En général, ces manchons 28A, 28B sont en matière plastique. Le manchon externe 28A est monté coulissant sur la surface externe 30E du tube de guidage 30, alors que le manchon interne 28B est monté coulissant sur la surface interne 30I du tube de guidage 30. Chaque butée 24A, 24B comporte en outre une extrémité distale portant un roulement 32A, 32B destiné à coopérer avec l'organe de transmission d'effort 26A, 26B. Par ailleurs, les première 24A et seconde 24B butées de commande sont actionnées respectivement par des première 34A et seconde 34B fourchettes. Ces fourchettes 34A, 34B sont articulées sur le carter 31 autour d'axes sensiblement parallèles. Ces axes d'articulation sont sensiblement orthogonaux aux axes des manchons 28A, 28B. La première fourchette 34A a une forme générale d'anneau ovalisé entourant la seconde fourchette 34B et délimitant un espace interne de débattement de cette seconde fourchette 34B, comme cela est visible sur la figure 3. Les fourchettes 34A, 34B sont ainsi agencées de manière à occuper un espace axial réduit. Dans l'exemple présenté sur les figures, les fourchettes sont articulées chacune autour d'une liaison rotule fixée sur le carter fixe 31. Ces liaisons rotules permettent le débattement angulaire de la fourchette pour l'actionnement de l'embrayage. Elles donnent aussi un degré de liberté supplémentaire pour permettre un ajustage du parallélisme entre la face d'appui de la fourchette et le manchon 28A, 28B. De plus, ces liaisons rotules sont particulièrement bien adaptées à cette double commande car elles sont peut encombrantes, permettant de loger les 2 articulations dans un espace réduit, surtout pour celle de la seconde fourchette 34B, ce qui serait difficile à réaliser avec un pivot formé par un axe. La rotule de la seconde fourchette 34B est placée sur l'extrémité d'un prolongement qui se trouve à l'opposé par rapport à l'axe de l'embrayage de la partie en
contact avec la commande venant d'un actionneur. Ce prolongement est logé dans un creux du contour intérieur de l'anneau formé par la première fourchette 34A. De cette manière, les 2 rotules sont suivant une direction radiale au plus près l'une de l'autre. Les fourchettes qui sont placées dans un plan sensiblement perpendiculaire à l'axe se trouvent, suivant cet axe, proches l'une de l'autre. Les points d'articulation des liaisons rotules sont suivant cet axe distants de moins de 10 mm, en variante, distants de moins de 5 mm. Les fourchettes disposent d'une certaine épaisseur suivant ce même axe qui leur donne de la rigidité. Elles sont réalisées par exemple en tôle emboutie, en acier forgé ou moulé. Cette distance réduite entre les liaisons rotules permet aux deux fourchettes d'avoir des encombrements suivant l'axe, en comprenant le volume libre pour leur débattement, sensiblement identiques ce qui optimise au mieux les volumes occupés. En se référant en particulier à la figure 2, on voit que chaque fourchette 34A, 34B est munie d'au moins une zone d'appui 36A, 36B coopérant avec une zone d'appui complémentaire 38A, 38B ménagée sur le manchon 28A, 28B correspondant. La zone d'appui complémentaire 38A du manchon externe 28A est délimitée par une saillie radiale 39A (voir notamment figures 2 et 4) de ce manchon externe 28A, rigidifiée par exemple par des nervures axiales. La zone d'appui complémentaire 38B du manchon interne 28B est délimitée par un bossage axial 39B d'extrémité de ce manchon externe 28B (voir figure 4). Dans le mode de réalisation illustré sur les figures, chaque fourchette 34A, 34B est munie de deux zones d'appui 36A, 36B avec le manchon 28A, 28B correspondant, sensiblement diamétralement opposées par rapport à l'axe de ce manchon. On notera, en se référant à la figure 1, que ces fourchettes 34A, 34B forment chacune un levier du second genre car chaque zone d'appui 36A, 36B est placée entre des extrémités de manœuvre MA, MB et d'articulation RA, RB de ce levier. Afin de pouvoir assurer le contact entre chaque zone d'appui 36B de la seconde fourchette 34B et chaque zone d'appui 38B du manchon interne 28B, agencé à l'intérieur du tube de guidage 30, le tube de guidage 30 et le manchon externe 28A sont ajourés par des passages respectifs 40, 41 (voir notamment figure 2) à travers lesquels s'étend la zone d'appui 36B de la seconde fourchette 34B. Dans le mode de réalisation représenté sur les figures, le tube de guidage 30 et le manchon externe 28A sont munis chacun de deux passages 40, 41, sensiblement diamétralement opposés par rapport à leur axe à travers lesquels s'entendent les deux zones d'appui 36B de la seconde fourchette 34B.
Afin de faciliter le montage de la seconde fourchette 34B sur le tube de guidage 30, cette seconde fourchette comporte une ouverture 42 d'emboîtement autour du tube de guidage 30 (voir figures 5 et 6), munie de deux extrémités 42A, 42B de largeurs différentes. L'extrémité large 42A autorise l'emboîtement de la seconde fourchette 34B autour du tube de guidage 30 par déplacement de cette seconde fourchette 34B sensiblement parallèlement à l'axe de ce tube de guidage 30 (voir figure 5). L'extrémité étroite 42B est délimitée par les zones d'appui 36B et autorise l'emboîtement de ces zones d'appui 36B dans les passages 40 du tube de guidage 30 par déplacement de la seconde fourchette 34B sensiblement transversalement à l'axe du tube de guidage 30 (voir figure 6). Pour assurer le pré-montage de l'ensemble représenté sur les figures 3 et 4, les manchons 28A, 28B peuvent être maintenus sur leurs fourchettes 34A, 34B respectives, par exemple, par des moyens d'encliquetage de ces manchons 28A, 28B sur les fourchettes 34A, 34B correspondantes. Par ailleurs, on prévoira de préférence des moyens d'anti-rotation des manchons 28A, 28B autour de leurs axes respectifs afin que leurs zones d'appui 38A, 38B soient toujours en contact avec les zones d'appui 36A, 36B des fourchette 34A, 34B correspondantes. Les moyens d'encliquetage des manchons 28A, 28B sur la fourchette 34A, 34B peuvent notamment former ces moyens d'anti-rotation. On notera que les formes des fourchettes 34A, 34B peuvent être adaptées en fonction soit de l'encombrement des différents organes du double embrayage soit des dégagements à prévoir pour passer certains outils de montage.
The present invention relates to a double clutch, in particular for a motor vehicle, with double control stop. A double clutch usually makes it possible to couple the shaft of a vehicle engine alternately with two coaxial input shafts of a gearbox, known as a double clutch gearbox. Thus, a double clutch makes it possible to change the gear ratio while maintaining the transmission of an engine torque to the vehicle wheels. Indeed, a double clutch usually comprises two clutches associated respectively with even and odd gear ratios. During a gear change, a first clutch is disengaged while the second clutch is engaged so that the engine torque is gradually transferred from the first to the second clutch. Thus, the sum of the torques transmitted by the first and second clutches is always substantially equal to the engine torque. A double clutch usually comprises a cover in which are housed two clutches for shifting ratios of different parities. Each clutch comprises a mechanism comprising a diaphragm intended to cooperate with a pressure plate integral in rotation with the cover and the motor shaft. Each diaphragm can be moved, by means of a corresponding control stop, between a rest position and an active position. Depending on the type of clutch, the active position of the diaphragm corresponds to a coupling or uncoupling of the motor and gearbox shafts and the rest position of the diaphragm corresponds to a decoupling or coupling of these motor and gearbox shafts speeds. Each pressure plate, biased by the corresponding diaphragm, is intended to enclose a friction disc between this pressure plate and a corresponding reaction plate. Each friction disc is linked in rotation to a corresponding gearbox shaft and each reaction plate is integral in rotation with the cover and a flywheel linked to the motor shaft. Thus, the tightening of a friction disc between the corresponding pressure and reaction plates allows the transmission of a torque between the motor shaft and the associated gearbox shaft. Already known in the prior art, in particular from FR-1 300 975, a double clutch, in particular for a motor vehicle, of the type comprising first and second control stops comprising first and second respective sleeves mounted to slide each on a guide tube. According to an embodiment described in FR-1 300 975, the two sleeves of the control stops slide respectively on the external surfaces of two coaxial guide tubes. According to another embodiment described in FR-1 300 975, the first sleeve, external, is slidably mounted on the external surface of the second sleeve, internal. This internal sleeve, slidably mounted on a guide tube, itself forms another guide tube for the external sleeve. The object of the invention is in particular to propose a double clutch of simple structure and of reduced bulk, this ensuring an efficient operation. To this end, the invention relates to a double clutch of the aforementioned type, characterized in that the guide tube is common to the two stops, the first and second sleeves being slidably mounted on the external and internal surfaces of the guide tube respectively. . Such a double clutch makes it possible to guide the two control stops using a single guide tube, while limiting its axial size due to the partial overlapping of the control stops. A double clutch according to the invention may also include one or more of the following characteristics: - the first and second control stops are actuated respectively by first and second ^ forks each provided with at least one cooperating support zone with an additional support zone provided on the corresponding sleeve; - Each fork forms a lever of the second kind in which the support zone is placed between the operating and articulation ends of this fork; - Each fork is provided with two support zones with the corresponding sleeve substantially diametrically opposite with respect to the axis of this sleeve; - The guide tube is provided with passages through which extends the support area of the second fork; - The first sleeve, said external sleeve, is provided with passages through which extends the support zone of the second fork; - The outer sleeve and the guide tube are each provided with two passages substantially diametrically opposite with respect to their axis through which extend the two bearing zones of the second fork; - The second fork has a nesting opening around the guide tube provided with two ends of different widths, the wide end allowing the nesting of the second fork around the guide tube by displacement of this second fork substantially parallel to the axis of this guide tube and the narrow end being delimited by the support zones and authorizing the nesting of these support zones in the passages of the guide tube by displacement of the second fork substantially transversely to the axis guide tube; - The complementary support zone of the first sleeve is delimited by a radial projection of this first sleeve; - The complementary support zone of the second sleeve is delimited by an axial boss at the end of this second sleeve; - The first and second forks are articulated around substantially parallel axes, the first fork having the general shape of an ovalized ring surrounding the second fork and delimiting an internal clearance space of this second fork; - Each of the first and second forks is linked to the clutch housing by means of a ball joint; - The first and second forks form levers of the second kind; - the ball joint connection of the second fork is placed on one end of this second fork in an extension located opposite, with respect to an axis of the double clutch, of a part in contact with a control coming from an actuator , this extension being housed in a hollow of an inner contour of a ring formed by the first fork; the axes of the ball joint connections are, along the axis of the double clutch, placed at a distance of less than approximately 10 mm from one another; the axes of the ball joint connections are, along the axis of the double clutch, placed at a distance of less than approximately 5 mm from one another. The invention will be better understood on reading the description which follows, given solely by way of example and made with reference to the accompanying drawings in which: - Figure 1 is an axial sectional view of a double clutch according to the invention; - Figure 2 is an axial sectional view of the double clutch according to the invention in the section plane 2-2 of Figure 1; - Figure 3 is a perspective view of an assembly of the double clutch shown in Figures 1 and 2, comprising the control stops arranged on the guide tube, the control stops each cooperating with a fork; - Figure 4 is a perspective view with a partial section of the assembly shown in Figure 3; - Figures 5 and 6 are perspective views of a fork of the double clutch shown in Figures 1 and 2 arranged on the guide tube. There is shown in Figures 1 and 2 a double clutch for a motor vehicle, designated by the general reference 10. The double clutch 10 has a cover 12 in which are housed two clutches for shifting ratios of different parities. These clutches respectively comprise first M1 and second M2 mechanisms intended to act on the first F1 and second F2 frictions. The mechanisms M1, M2 respectively comprise first 14A and second 14B diaphragms intended to cooperate with first 15A and second 15B pressure plates integral in rotation with the cover 12. The first diaphragm 14A cooperates with the first pressure plate 15A via of a movable member 16 of axial bracing partially visible in FIG. 1. The second diaphragm 14B cooperates with the first pressure plate 15B by means of an annular projection 17 (continuous or angularly discontinuous) integral with this first plate pressure 15B. Frictions F1, F2 respectively comprise first 18A and second 18B friction discs. Each pressure plate 15A, 15B, biased by the corresponding diaphragm is intended to enclose a friction disc 18A, 18B between this pressure plate and a corresponding reaction plate 20A, 20B, integral in rotation with a flywheel and the cover 12. The two friction discs 18A, 18B are linked in rotation respectively to two gearbox shafts 22A, 22B corresponding to gear ratios of different parities. The control of the first and second clutches is done respectively by means of first 24A and second 24B control stops each cooperating with the corresponding diaphragm 14A, 14B via a force transmission member 26A, 26B. Each diaphragm 14A, 14B is movable, by means of the corresponding control stop, 24A, 24B between a rest position and an active position. In the embodiment illustrated in the figures, the double clutch 10 is of the type in which the active position of each diaphragm 14A, 14B corresponds to a coupling of the engine and gearbox shafts and the rest position of this diaphragm 14A , 14B corresponds to a decoupling of these engine and gearbox shafts. These first 24A and second 24B control stops comprise first 28A and second 28B respective sleeves, called external sleeves 28A and internal 28B, each slidably mounted on a guide tube 30, common to the two stops 24A, 24B. This guide tube 30 is fixed to a fixed casing 31 of the double clutch 10 by means of a flange 30A. In general, these sleeves 28A, 28B are made of plastic. The outer sleeve 28A is slidably mounted on the outer surface 30E of the guide tube 30, while the inner sleeve 28B is slidably mounted on the inner surface 30I of the guide tube 30. Each stop 24A, 24B further has a distal end bearing a bearing 32A, 32B intended to cooperate with the force transmission member 26A, 26B. Furthermore, the first 24A and second 24B control stops are actuated respectively by first 34A and second 34B forks. These forks 34A, 34B are articulated on the casing 31 around substantially parallel axes. These articulation axes are substantially orthogonal to the axes of the sleeves 28A, 28B. The first fork 34A has the general shape of an ovalized ring surrounding the second fork 34B and delimiting an internal clearance space of this second fork 34B, as can be seen in FIG. 3. The forks 34A, 34B are thus arranged so as to occupy a reduced axial space. In the example presented in the figures, the forks are each articulated around a ball joint fixed to the fixed casing 31. These ball joints allow the angular movement of the fork for actuating the clutch. They also give an additional degree of freedom to allow adjustment of the parallelism between the bearing face of the fork and the sleeve 28A, 28B. In addition, these ball joints are particularly well suited to this double control because they are cumbersome, making it possible to accommodate the 2 joints in a reduced space, especially for that of the second fork 34B, which would be difficult to achieve with a pivot formed by an axis. The ball joint of the second fork 34B is placed on the end of an extension which is opposite to the axis of the clutch of the part in contact with the control coming from an actuator. This extension is housed in a hollow of the inner contour of the ring formed by the first fork 34A. In this way, the 2 ball joints are in a radial direction as close as possible to each other. The forks which are placed in a plane substantially perpendicular to the axis are, along this axis, close to one another. The articulation points of the ball joint connections are along this axis spaced less than 10 mm, as a variant, spaced less than 5 mm. The forks have a certain thickness along this same axis which gives them rigidity. They are made for example from stamped sheet metal, forged or cast steel. This reduced distance between the ball joint connections allows the two forks to have dimensions along the axis, including the free volume for their travel, substantially identical which optimizes the occupied volumes. Referring in particular to FIG. 2, it can be seen that each fork 34A, 34B is provided with at least one support area 36A, 36B cooperating with a complementary support area 38A, 38B formed on the sleeve 28A, 28B corresponding. The complementary support zone 38A of the external sleeve 28A is delimited by a radial projection 39A (see in particular FIGS. 2 and 4) of this external sleeve 28A, rigidified for example by axial ribs. The complementary support zone 38B of the internal sleeve 28B is delimited by an axial boss 39B at the end of this external sleeve 28B (see FIG. 4). In the embodiment illustrated in the figures, each fork 34A, 34B is provided with two bearing zones 36A, 36B with the corresponding sleeve 28A, 28B, substantially diametrically opposite with respect to the axis of this sleeve. It will be noted, with reference to FIG. 1, that these forks 34A, 34B each form a lever of the second kind because each support zone 36A, 36B is placed between the maneuvering ends MA, MB and the articulation ends RA, RB of this lever. In order to be able to ensure contact between each support area 36B of the second fork 34B and each support area 38B of the internal sleeve 28B, arranged inside the guide tube 30, the guide tube 30 and the external sleeve 28A are perforated by respective passages 40, 41 (see in particular Figure 2) through which extends the bearing area 36B of the second fork 34B. In the embodiment shown in the figures, the guide tube 30 and the external sleeve 28A are each provided with two passages 40, 41, substantially diametrically opposite with respect to their axis through which the two bearing zones are understood. 36B of the second fork 34B. In order to facilitate the mounting of the second fork 34B on the guide tube 30, this second fork has an opening 42 for fitting around the guide tube 30 (see FIGS. 5 and 6), provided with two ends 42A, 42B of widths different. The wide end 42A allows the nesting of the second fork 34B around the guide tube 30 by displacement of this second fork 34B substantially parallel to the axis of this guide tube 30 (see Figure 5). The narrow end 42B is delimited by the support zones 36B and authorizes the nesting of these support zones 36B in the passages 40 of the guide tube 30 by displacement of the second fork 34B substantially transversely to the axis of the tube guide 30 (see Figure 6). To ensure the pre-assembly of the assembly shown in Figures 3 and 4, the sleeves 28A, 28B can be held on their respective forks 34A, 34B, for example, by means of latching these sleeves 28A, 28B on the corresponding ranges 34A, 34B. Furthermore, provision will preferably be made for means of anti-rotation of the sleeves 28A, 28B about their respective axes so that their bearing zones 38A, 38B are always in contact with the bearing zones 36A, 36B of the fork 34A , 34B corresponding. The latching means of the sleeves 28A, 28B on the fork 34A, 34B can in particular form these anti-rotation means. It will be noted that the shapes of the forks 34A, 34B can be adapted as a function either of the size of the various bodies of the double clutch or of the clearances to be provided for passing certain assembly tools.
Claims
1. Double embrayage (10), notamment pour véhicule automobile, du type comprenant des première (24A) et seconde (24B) butées de commande comportant des premier (28A) et second (28B) manchons respectifs montés coulissant chacun sur un tube de guidage (30), caractérisé en ce que le tube de guidage (30) est commun aux deux butées, les premier (24A) et second (24B) manchons étant montés coulissant sur des surfaces externe et interne respectivement du tube de guidage (30). 1. Double clutch (10), in particular for a motor vehicle, of the type comprising first (24A) and second (24B) control stops comprising first (28A) and second (28B) respective sleeves each sliding mounted on a guide tube (30), characterized in that the guide tube (30) is common to the two stops, the first (24A) and second (24B) sleeves being slidably mounted on the external and internal surfaces of the guide tube (30) respectively.
2. Double embrayage (10) selon la revendication 1, caractérisé en ce que les première (24A) et seconde (24B) butées de commande sont actionnées respectivement par des première (34A) et seconde (34B) fourchettes munie chacune d'au moins une zone d'appui (36A, 36B) coopérant avec une zone d'appui (38A, 38B) complémentaire ménagée sur le manchon (28A, 28B) correspondant. 2. Double clutch (10) according to claim 1, characterized in that the first (24A) and second (24B) control stops are actuated respectively by first (34A) and second (34B) forks each provided with at least a support area (36A, 36B) cooperating with a complementary support area (38A, 38B) provided on the corresponding sleeve (28A, 28B).
3. Double embrayage (10) selon la revendication 2, caractérisé en ce que chaque fourchette (34A, 34B) forme un levier du second genre dans lequel la zone d'appui (36A, 36B) est placée entre des extrémités de manœuvre et d'articulation de cette fourchette. 3. Double clutch (10) according to claim 2, characterized in that each fork (34A, 34B) forms a lever of the second kind in which the bearing zone (36A, 36B) is placed between the operating ends and d articulation of this fork.
4. Double embrayage (10) selon la revendication 2 ou 3, caractérisé en ce que chaque fourchette (34A, 34B) est munie de deux zones (36A, 36B) d'appui avec le manchon (28A, 28B) correspondant sensiblement diamétralement opposées par rapport à l'axe de ce manchon (28A, 28B). 4. Double clutch (10) according to claim 2 or 3, characterized in that each fork (34A, 34B) is provided with two zones (36A, 36B) bearing with the sleeve (28A, 28B) corresponding substantially diametrically opposite relative to the axis of this sleeve (28A, 28B).
5. Double embrayage (10) selon l'une quelconque des revendications 2 à 4, caractérisé en ce que le tube de guidage (30) est muni de passages (40) à travers lesquels s'étend la zone d'appui (36B) de la seconde fourchette (34B). 5. Double clutch (10) according to any one of claims 2 to 4, characterized in that the guide tube (30) is provided with passages (40) through which extends the support zone (36B) from the second fork (34B).
6. Double embrayage (10) selon l'une quelconque des revendications 2 à 5, caractérisé en ce que le premier manchon (28A), dit manchon externe (28A), est muni de passages (41) à travers lesquels s'étend la zone d'appui (36B) de la seconde fourchette (34B). 6. Double clutch (10) according to any one of claims 2 to 5, characterized in that the first sleeve (28A), said external sleeve (28A), is provided with passages (41) through which extends the support area (36B) of the second fork (34B).
7. Double embrayage (10) selon la revendication 2 prise en combinaison avec les revendications 5 et 6, caractérisé en ce que le manchon externe (28A) et le tube de guidage (30) sont munis chacun de deux passages (40) sensiblement diamétralement opposés par rapport à leur axe à travers lesquels s'étendent les deux zones d'appui (36B) de la seconde fourchette (34B). 7. Double clutch (10) according to claim 2 taken in combination with claims 5 and 6, characterized in that the outer sleeve (28A) and the guide tube (30) are each provided with two passages (40) substantially diametrically opposite with respect to their axis through which extend the two support zones (36B) of the second fork (34B).
8. Double embrayage (10) selon la revendication 7, caractérisé en ce que la seconde fourchette (34B) comporte une ouverture (42) d'emboîtement autour du tube de guidage (30) munie de deux extrémités (42A, 42B) de largeurs différentes, l'extrémité large (42A) autorisant l'emboîtement de la seconde fourchette (34B) autour du tube de guidage (30) par déplacement de cette seconde fourchette (34B) sensiblement parallèlement à l'axe de ce tube de guidage (30) et l'extrémité étroite (42B) étant délimitée par les zones d'appui (38B) et autorisant l'emboîtement de ces zones d'appui (38B) dans les passages (40) du tube de guidage (30) par déplacement de la seconde fourchette (34B) sensiblement transversalement à l'axe du tube de guidage (30). 8. Double clutch (10) according to claim 7, characterized in that the second fork (34B) has an opening (42) for fitting around the guide tube (30) provided with two ends (42A, 42B) of widths different, the end wide (42A) allowing the nesting of the second fork (34B) around the guide tube (30) by displacement of this second fork (34B) substantially parallel to the axis of this guide tube (30) and the end narrow (42B) being delimited by the support zones (38B) and authorizing the nesting of these support zones (38B) in the passages (40) of the guide tube (30) by displacement of the second fork (34B ) substantially transversely to the axis of the guide tube (30).
9. Double embrayage (10) selon l'une quelconque des revendications 2 à 8, caractérisé en ce que la zone d'appui complémentaire (38A) du premier manchon (28A) est délimitée par une saillie radiale (39A) de ce premier manchon (28A). 9. Double clutch (10) according to any one of claims 2 to 8, characterized in that the complementary bearing zone (38A) of the first sleeve (28A) is delimited by a radial projection (39A) of this first sleeve (28A).
10. Double embrayage (10) selon l'une quelconque des revendications 2 à 9, caractérisé en ce que la zone d'appui complémentaire (38B) du second manchon (28B) est délimitée par un bossage axial (39B) d'extrémité de ce second manchon (28B). 10. Double clutch (10) according to any one of claims 2 to 9, characterized in that the complementary bearing zone (38B) of the second sleeve (28B) is delimited by an axial boss (39B) at the end of this second sleeve (28B).
11. Double embrayage (10) selon l'une quelconque des revendications 2 à 10, caractérisé en ce que les première (34A) et seconde (24B) fourchettes sont articulées autour d'axes sensiblement parallèles, la première fourchette (34A) ayant une forme générale d'anneau ovalisé entourant la seconde fourchette (34B) et délimitant un espace interne de débattement de cette seconde fourchette (34B). 11. Double clutch (10) according to any one of claims 2 to 10, characterized in that the first (34A) and second (24B) forks are articulated around substantially parallel axes, the first fork (34A) having a general shape of an ovalized ring surrounding the second fork (34B) and delimiting an internal clearance of this second fork (34B).
12. Double embrayage (10) selon la revendication 11, caractérisé en ce que chacune des première (34A) et seconde (34B) fourchettes est liée au carter d'embrayage par le biais d'une liaison rotule. 12. Double clutch (10) according to claim 11, characterized in that each of the first (34A) and second (34B) forks is linked to the clutch housing by means of a ball joint.
13. Double embrayage (10) selon la revendication 11, caractérisé en ce que les première (34A) et seconde (34B) fourchettes forment des leviers du second genre. 13. Double clutch (10) according to claim 11, characterized in that the first (34A) and second (34B) forks form levers of the second kind.
14. Double embrayage (10) selon la revendication 11 ou 12, caractérisé en ce que la liaison rotule de la seconde fourchette (34B) est placée sur une extrémité de cette seconde fourchette dans un prolongement se trouvant à l'opposé, par rapport à un axe du double embrayage, d'une partie en contact avec une commande venant d'un actionneur, ce prolongement étant logé dans un creux d'un contour intérieur d'un anneau formé par la première fourchette (34A). 14. Double clutch (10) according to claim 11 or 12, characterized in that the ball joint of the second fork (34B) is placed on one end of this second fork in an extension being opposite, relative to an axis of the double clutch, of a part in contact with a control coming from an actuator, this extension being housed in a hollow of an interior contour of a ring formed by the first fork (34A).
15. Double embrayage (10) selon la revendication 12, caractérisé en ce que les axes des liaisons rotules sont, suivant l'axe du double embrayage, placés à une distance inférieure à 10 mm environ l'un de l'autre. 15. Double clutch (10) according to claim 12, characterized in that the axes of the ball joints are, along the axis of the double clutch, placed at a distance of less than 10 mm from one another.
16. Double embrayage (10) selon la revendication 12, caractérisé en ce que les axes des liaisons rotules sont ,suivant l'axe du double embrayage, placés à une distance inférieure à 5 mm environ l'un de l'autre. 16. Double clutch (10) according to claim 12, characterized in that the axes of the ball joints are, along the axis of the double clutch, placed at a distance of less than about 5 mm from one another.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0350548 | 2003-09-16 | ||
FR0350548A FR2859773B1 (en) | 2003-09-16 | 2003-09-16 | DOUBLE CLUTCH, IN PARTICULAR FOR MOTOR VEHICLE, WITH DOUBLE STOPPING OF CONTROL |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005028902A1 true WO2005028902A1 (en) | 2005-03-31 |
Family
ID=34203546
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2004/050409 WO2005028902A1 (en) | 2003-09-16 | 2004-09-01 | Double clutch with a double control thrust bearing, in particular for a motor vehicle |
Country Status (2)
Country | Link |
---|---|
FR (1) | FR2859773B1 (en) |
WO (1) | WO2005028902A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010086540A1 (en) | 2009-01-30 | 2010-08-05 | Valeo Embrayages | Dual clutch mechanism including a dual fork control device |
US20120222512A1 (en) * | 2009-11-03 | 2012-09-06 | Gm Global Technology Operations, Inc. | Double clutch actuation arrangement |
DE102012222892A1 (en) | 2012-01-18 | 2013-07-18 | Schaeffler Technologies AG & Co. KG | Actuating device for a double clutch |
WO2013143394A1 (en) * | 2012-03-31 | 2013-10-03 | Shenzhen Byd Auto R&D Company Limited | Operation mechanism, double-action clutch assembly and vehicle |
DE102014213097A1 (en) * | 2014-07-07 | 2016-01-07 | Schaeffler Technologies AG & Co. KG | Gimbal unit with a rotation axis for a friction clutch |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
MX2010003905A (en) | 2007-10-11 | 2010-06-01 | Luk Lamellen & Kupplungsbau | Clutch actuation system. |
JP5149975B2 (en) | 2011-02-28 | 2013-02-20 | 株式会社エクセディ | Clutch device |
IN2015DN00794A (en) * | 2012-08-03 | 2015-07-03 | Schaeffler Technologies Gmbh |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1300975A (en) | 1961-07-01 | 1962-08-10 | Ferodo Sa | Clutch refinements |
US3212611A (en) * | 1962-09-14 | 1965-10-19 | Porsche Kg | Double clutch construction |
DE2931816A1 (en) * | 1979-08-06 | 1981-02-26 | Luk Lamellen & Kupplungsbau | Declutching mechanism for vehicle clutch - has operating arm swung by drive member above clutch about spherical joint below clutch |
US5299677A (en) * | 1991-10-15 | 1994-04-05 | Claude Caillaud | Guide-tube with integral sealing for motor vehicle gearbox clutch release bearing |
DE10238403A1 (en) * | 2001-10-09 | 2003-04-17 | Zf Sachs Ag | Multiple clutch unit comprises at least two coupling zones, with at least in one of these zones materials with different coefficients of thermal expansion being used for clutch elements dependent on their position |
EP1384911A2 (en) * | 2002-07-25 | 2004-01-28 | ZF Sachs AG | Double clutch assembly |
FR2851626A1 (en) * | 2003-02-20 | 2004-08-27 | Valeo Embrayages | Torque transmission device for motor vehicles robotized gear box, has tightening discs radial at clutchs exterior to link two flywheels and to allow their rotation when actuator is in and starts from rest position, respectively |
-
2003
- 2003-09-16 FR FR0350548A patent/FR2859773B1/en not_active Expired - Lifetime
-
2004
- 2004-09-01 WO PCT/FR2004/050409 patent/WO2005028902A1/en active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1300975A (en) | 1961-07-01 | 1962-08-10 | Ferodo Sa | Clutch refinements |
US3212611A (en) * | 1962-09-14 | 1965-10-19 | Porsche Kg | Double clutch construction |
DE2931816A1 (en) * | 1979-08-06 | 1981-02-26 | Luk Lamellen & Kupplungsbau | Declutching mechanism for vehicle clutch - has operating arm swung by drive member above clutch about spherical joint below clutch |
US5299677A (en) * | 1991-10-15 | 1994-04-05 | Claude Caillaud | Guide-tube with integral sealing for motor vehicle gearbox clutch release bearing |
DE10238403A1 (en) * | 2001-10-09 | 2003-04-17 | Zf Sachs Ag | Multiple clutch unit comprises at least two coupling zones, with at least in one of these zones materials with different coefficients of thermal expansion being used for clutch elements dependent on their position |
EP1384911A2 (en) * | 2002-07-25 | 2004-01-28 | ZF Sachs AG | Double clutch assembly |
FR2851626A1 (en) * | 2003-02-20 | 2004-08-27 | Valeo Embrayages | Torque transmission device for motor vehicles robotized gear box, has tightening discs radial at clutchs exterior to link two flywheels and to allow their rotation when actuator is in and starts from rest position, respectively |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010086540A1 (en) | 2009-01-30 | 2010-08-05 | Valeo Embrayages | Dual clutch mechanism including a dual fork control device |
US20120222512A1 (en) * | 2009-11-03 | 2012-09-06 | Gm Global Technology Operations, Inc. | Double clutch actuation arrangement |
DE102012222892A1 (en) | 2012-01-18 | 2013-07-18 | Schaeffler Technologies AG & Co. KG | Actuating device for a double clutch |
WO2013107435A1 (en) | 2012-01-18 | 2013-07-25 | Schaeffler Technologies AG & Co. KG | Activation device for a double clutch |
CN104094006A (en) * | 2012-01-18 | 2014-10-08 | 舍弗勒技术有限两合公司 | Activation device for a double clutch |
CN104094006B (en) * | 2012-01-18 | 2017-03-22 | 舍弗勒技术股份两合公司 | Operating device for a double clutch |
WO2013143394A1 (en) * | 2012-03-31 | 2013-10-03 | Shenzhen Byd Auto R&D Company Limited | Operation mechanism, double-action clutch assembly and vehicle |
US9631683B2 (en) | 2012-03-31 | 2017-04-25 | Shenzhen Byd Auto R&D Company Limited | Operation mechanism, dual-clutch assembly and vehicle |
DE102014213097A1 (en) * | 2014-07-07 | 2016-01-07 | Schaeffler Technologies AG & Co. KG | Gimbal unit with a rotation axis for a friction clutch |
DE102014213097B4 (en) * | 2014-07-07 | 2016-04-07 | Schaeffler Technologies AG & Co. KG | Gimbal unit with a rotation axis for a friction clutch |
Also Published As
Publication number | Publication date |
---|---|
FR2859773A1 (en) | 2005-03-18 |
FR2859773B1 (en) | 2006-11-24 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1681481B1 (en) | Transmission element with bearing for centering and absorbing vibrations | |
WO2005028902A1 (en) | Double clutch with a double control thrust bearing, in particular for a motor vehicle | |
EP1676042B1 (en) | Clutch, in particular for a motor vehicle and method for assembling said clutch | |
EP1688634B1 (en) | Mounting device for a bearing on a transmission element | |
EP1673546B1 (en) | Double clutch, in particular for a motor vehicle | |
WO2016055637A1 (en) | Clutch device | |
WO2018096114A1 (en) | Radial assembly of a clutch mechanism on a transmission | |
EP2384403B1 (en) | Dual clutch with a double fork actuator | |
EP1778999B1 (en) | Clutch, in particular for a motor vehicle provided with an improved member for connecting to a drive member | |
WO2015180778A1 (en) | Clutch device, in particular for a motor vehicle | |
FR3092373A1 (en) | DOUBLE WET CLUTCH AND ELASTIC RETURN DEVICE FOR SUCH A DOUBLE WET CLUTCH | |
FR2995376A1 (en) | TORQUE TRANSMISSION ASSEMBLY HAVING A DOUBLE DRY CLUTCH AND A SHOCK ABSORBER WHEEL | |
FR3090773A1 (en) | Transmission device for motor vehicle | |
EP2348224B1 (en) | Coupling comprising a diaphragm spring with an extension especially for actuating an accessory device of the coupling | |
EP2449278B1 (en) | Transmission system comprising a module with a built-in dual clutch mechanism, and device for controlling same | |
FR3038949A1 (en) | DOUBLE CLUTCH, IN PARTICULAR FOR MOTOR VEHICLE | |
WO1999031410A1 (en) | Motor vehicle gearbox | |
EP1666751B1 (en) | Clutch, in particular for automotive vehicle, comprising a mechanism having an improved clutch housing | |
EP3857090A1 (en) | Compact double wet clutch mechanism | |
FR2839759A1 (en) | Elastic coupling between motor vehicle internal combustion engine crankshaft and electric machine rotor, has elastomeric insert blocks in one housing section | |
FR3073588A1 (en) | DEVICE AND SYSTEM FOR TORQUE TRANSMISSION | |
EP2184502A1 (en) | Absorption of torque oscillations for a coupling device of a gearbox shaft with an idler gear installed on this shaft | |
FR3058488A1 (en) | COMPACT DOUBLE CLUTCH MECHANISM AND TRANSMISSION SYSTEM COMPRISING SUCH A DOUBLE CLUTCH MECHANISM | |
FR2826416A1 (en) | Friction clutch release bearing comprises two bushes and bearings, operating bush engaging interface part with force in bearing axial direction, bearing resiliently mounted with radial and axial play | |
FR2898651A1 (en) | Wet-type multi-disc clutch for gearbox of motor vehicle, has set of friction discs intercalated between another set of friction discs and rotationally coupled to input bell, where odd number of friction linings is provided on friction discs |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AE AG AL AM AT AU AZ BA BB BG BW BY BZ CA CH CN CO CR CU CZ DK DM DZ EC EE EG ES FI GB GD GE GM HR HU ID IL IN IS JP KE KG KP KZ LC LK LR LS LT LU LV MA MD MK MN MW MX MZ NA NI NO NZ PG PH PL PT RO RU SC SD SE SG SK SY TJ TM TN TR TT TZ UA UG US UZ VN YU ZA ZM |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): BW GH GM KE LS MW MZ NA SD SZ TZ UG ZM ZW AM AZ BY KG MD RU TJ TM AT BE BG CH CY DE DK EE ES FI FR GB GR HU IE IT MC NL PL PT RO SE SI SK TR BF CF CG CI CM GA GN GQ GW ML MR SN TD TG |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
122 | Ep: pct application non-entry in european phase |