WO2000040877A1 - Hydrokinetic torque transmission device with lock-up clutch - Google Patents
Hydrokinetic torque transmission device with lock-up clutch Download PDFInfo
- Publication number
- WO2000040877A1 WO2000040877A1 PCT/FR2000/000015 FR0000015W WO0040877A1 WO 2000040877 A1 WO2000040877 A1 WO 2000040877A1 FR 0000015 W FR0000015 W FR 0000015W WO 0040877 A1 WO0040877 A1 WO 0040877A1
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- Prior art keywords
- disc
- springs
- drive
- support disc
- radial wall
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Classifications
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- 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
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- 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0278—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch comprising only two co-acting friction surfaces
Definitions
- the present invention relates to a hydrokinetic torque transmission device with locking clutch. It relates in particular to a hydrokinetic torque transmission apparatus comprising a turbine wheel which can be made integral with a driven shaft and housed in an impeller wheel casing with which it can cooperate, for the hydrokinetic transmission of a torque to said shaft driven, from a driving shaft which can be made integral with said impeller, this device further comprising a clutch piston clutch device, said locking clutch, suitable for determining the locking or unlocking of 'an elastic coupling between said turbine wheel and a radial wall of said casing.
- This coupling is carried out by means of a set of helical damping springs with circumferential action held in place on either side between mutually opposite flanks and together forming a series of arcuate housings, a disc of support integral with said turbine wheel, these flanks having, at least on one side, supports for the corresponding ends of the springs and thus delimiting opposite radial ends two by two for said housings, these springs can thus be compressed each between the 'one of the two supports of its housing and one of the drive lugs with axial extension of an intermediate disc.
- These drive tabs form stop tabs for the springs.
- a hydrokinetic torque transmission device of the type defined above is, in accordance with the present invention, characterized in that this intermediate disc is mounted in the support disc and has stop lugs extending axially, beyond the springs, towards the radial wall of the casing, each passing between two consecutive springs to serve as stops and means for holding the ends of these springs, this apparatus further comprising a drive disc which is situated between said radial wall of the casing and a clutch piston movable axially and operated by hydraulic pressure, this drive disc carrying at its periphery drive tabs arranged in pairs , said legs of the intermediate disc each being meshed between the two legs of a pair of drive disc drive tabs.
- the stop lugs are thus distinct from the drive lugs.
- the drive tabs of the drive disc are no longer in contact with the ends of the springs, and they can therefore no longer be worn by friction against them.
- the stop lugs driven in rotation by the drive lugs, they are in contact with the ends of the springs, but there is no relative friction movement between them and the springs, so that there again there is no wear of the legs.
- Axial friction can therefore only occur between the drive lugs and the stop lugs, during axial displacements of the drive disc, itself driven, axially and in rotation, by the clutch piston.
- the material constituting these tabs can be given the same hardness, which greatly reduces their wear.
- the drive disc moves axially in good conditions and quickly without risk of jamming. This is favored by the floating mounting of the intermediate disc.
- FIG. 1 is a half-view in partial axial section showing the clutch device of a hydrokinetic torque transmission device according to the invention having no device for guiding the turbine hub, the connection between the piston clutch and the ends of the helical springs being effected by means of a drive disc meshed with an intermediate disc;
- FIG. 2 is a perspective view of the drive disc meshed with the intermediate disc, a single helical spring being shown;
- FIG. 3 is a perspective view of the same set of discs, but seen from the other side;
- FIG. 4 is a half view in partial axial section showing a variant provided with a device for guiding the turbine hub.
- the impeller of the paddle wheel has been generally referenced at 1
- the radial wall of the casing 2 called casing of the impeller, has been generally referenced at 2a.
- This radial wall 2a is extended axially at 2b to be connected, for example by a peripheral weld joint, to a complementary part (not shown) forming the impeller of impellers, the assembly being able to be wedged on a driving shaft, for example the crankshaft of an internal combustion engine.
- a clutch device extends radially between the turbine wheel 1 and the radial wall 2a of the casing 2 of the impeller wheel, in order to be able to secure in rotation or bridging the latter and the turbine wheel 1, and thus avoid any sliding between them, by bridging or "by-passing" the hydrokinetic coupling, when the setting in speed of the turbine wheel 1, coupled to the driven shaft, namely the shaft transmission input is complete.
- This clutch device comprises for this purpose, for example, and in the embodiment of FIG. 1, a clutch piston with a pressure plate function 5 centrally comprising a ferrule 6 through which it can slide axially and sealingly (annular seal 7) on the external periphery of a portion in the form of a thrust ring 8 of the centering shaft 4.
- a blind space 9 which can be supplied with pressurized fluid and which communicates through passages 10 of the shaft
- the reference 12 designates lugs of the ring 8 having a cylindrical outer surface allowing the guide of the ferrule 6 of the piston 5, but letting the pressurized fluid pass between the space 9 and the chamber 11.
- the flange 13 of a hub 14, internally fluted at 14a, is secured to the turbine wheel 1, as well as to a support disc 15 which will be described below, by any suitable fastening system, for example welding spots or rivets 16.
- a wedge 17 in the form of a flat ring made of a material with a low coefficient of friction is attached to the flange 13 or to the thrust ring 8 to constitute an axial support piece between these two pieces, avoiding any metal-to-metal contact between them.
- the hub 14, by means of its grooves 14a, is intended to be secured to a driven shaft provided with a channel for supplying the chamber 11 via the space 9.
- the piston 5 is secured in rotation to the radial wall 2a of the casing 2 of the impeller, this so as to allow the relative axial displacements between these two elements.
- This coupling can be carried out by any suitable means, for example by a tenon and mortise system or by means of axially elastic tongues 18 riveted at 19 to the wall 2a and fixed moreover to bosses 20 of the piston 5 by a system any clamping 21, this so as to exert an axial traction on this disc, in the direction of the radial wall 2a.
- a device of this type is described for example in French patent n ° 94 13205 of November 4, 1994 in the name of the applicant.
- the clutch device also comprises a drive disc 22 carrying, on its two faces, friction linings referenced at 23 (see also Figures 2 and 3).
- This disc 22 comprises, as an extension of its outer edge, and angularly evenly distributed along its periphery, drive tabs 24 arranged in pairs, bent at an obtuse angle and generally directed away from the radial wall 2a.
- the support disc 15 has at its outer periphery a groove 25 opening towards the radial wall 2a of the casing 2 and terminated by a generally cylindrical flank 26 provided with radially re-entrant supports 26a constituting between them housings for a series of coil springs depreciation 27; a complementary support disc 29 is welded at 30 to the support disc 15 and comprises at its periphery an inclined flank 31, partially closing the aforementioned housings of the springs 27, which flank carries, with respect to the supports 26a, complementary supports 31a contributing to delimit said housings and serving, at the same time as the supports 26a, abutment surfaces for the ends of the springs 27 with circumferential action.
- this device comprises between the discs 15 and 29 an intermediate disc 32 (see also Figure 2) which carries, projecting radially outwards, a series of stop lugs 33 with axial extension and angularly distributed , directed towards the radial wall 2a of the casing and having on both sides of the lugs 34 in which engage the two opposite ends of each spring 27.
- Figures 2 and 3 show one mutual engagement of the drive discs 22 and intermediate 32 , each stop tab 33 of the intermediate disc engaging between two consecutive drive tabs 24 of the drive disc 22.
- the pressure of the hydraulic fluid in the chamber 11 is such that it keeps the clutch piston 5 spaced from the radial wall 2a, so that the linings 23 of the drive disc 22, spaced from the wall 2a, are not rotated, notwithstanding the (permanent) rotation of the disc 5.
- the torque of the impeller wheel is therefore transmitted to the turbine wheel 1, with sliding, only by effect hydrokinetic in the device (conversion phase).
- the springs 27 are inactive.
- the intermediate disc 32 is mounted floating between the support discs 15, 29 and that the inclination of the legs 24 of the disc 22 avoids any interference between the legs 33 and the wall 2a.
- the springs 27 are thus well compressed and the legs 33, 24 do not need to be treated to be hardened.
- the drive disc can be made of synthetic material and rub directly on the piston 5 and the wall 2a.
- the linings 23 are fixed respectively to the piston 5 and the wall 2a.
- the presence of a reactor wheel is not essential, the torque transmission device then comprising a coupler.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
APPAREIL DE TRANSMISSION DE COUPLE HYDROCINETIQUE A EMBRAYAGE DE VERROUILLAGE HYDROKINETIC TORQUE TRANSMISSION APPARATUS WITH LOCKING CLUTCH
La présente invention concerne un appareil de transmission de couple hydrocinetique à embrayage de verrouillage. Elle concerne notamment un appareil de transmission de couple hydrocinetique comportant une roue de turbine pouvant être rendue solidaire d'un arbre mené et logée dans un carter de roue d'impulseur avec laquelle elle peut coopérer, pour la transmission hydrocinétique d'un couple audit arbre mené, à partir d'un arbre menant pouvant être rendu solidaire de ladite roue d'impulseur, cet appareil comportant en outre un dispositif d'embrayage à piston d'embrayage, dit embrayage de verrouillage, propre à déterminer le verrouillage ou le déverrouillage d'un accouplement élastique entre ladite roue de turbine et une paroi radiale dudit carter. Cet accouplement est réalisé par l'intermédiaire d'un jeu de ressorts hélicoïdaux d'amortissement à action circonférentielle maintenus en place de part et d'autre entre des flancs mutuellement en regard et formant ensemble une série de logements arqués, d'un disque de support solidaire de ladite roue de turbine, ces flancs possédant, au moins d'un côté, des appuis pour les extrémités correspondantes des ressorts et délimitant ainsi des extrémités radiales opposées deux à deux pour lesdits logements, ces ressorts pouvant ainsi être comprimés chacun entre l'un des deux appuis de son logement et l'une des pattes d'entraînement à extension axiale d'un disque intermédiaire. Ces pattes d'entraînement forment des pattes d'arrêt pour les ressorts .The present invention relates to a hydrokinetic torque transmission device with locking clutch. It relates in particular to a hydrokinetic torque transmission apparatus comprising a turbine wheel which can be made integral with a driven shaft and housed in an impeller wheel casing with which it can cooperate, for the hydrokinetic transmission of a torque to said shaft driven, from a driving shaft which can be made integral with said impeller, this device further comprising a clutch piston clutch device, said locking clutch, suitable for determining the locking or unlocking of 'an elastic coupling between said turbine wheel and a radial wall of said casing. This coupling is carried out by means of a set of helical damping springs with circumferential action held in place on either side between mutually opposite flanks and together forming a series of arcuate housings, a disc of support integral with said turbine wheel, these flanks having, at least on one side, supports for the corresponding ends of the springs and thus delimiting opposite radial ends two by two for said housings, these springs can thus be compressed each between the 'one of the two supports of its housing and one of the drive lugs with axial extension of an intermediate disc. These drive tabs form stop tabs for the springs.
On connaît déjà un appareil de ce type par le brevet des Etats-Unis n°5 383 540. Selon ce brevet, les pattes à extension axiale sont dirigées à l'opposé de la paroi radiale du carter, et le disque intermédiaire porte à la périphérie de ses deux faces des garnitures de friction et est propre à être pressé, et à être entraîné par friction, entre ledit piston d'embrayage et ladite paroi radiale du carter de la roue menante d'impulseur. Ce disque intermédiaire, manœuvré par pression hydraulique, est donc mobile axialement, dans les deux sens, à la manière d'un piston. Il en résulte évidemment des frottements répétitifs entre ses pattes d'entraînement à extension axiale formant également des pattes d'arrêt et les ressorts, qui sont réalisés en acier dur, d'où une usure rapide des pattes du disque intermédiaire. En outre, il y a des risques de coincement, et le déplacement axial du disque, qui de toute façon est freiné, n'est pas aussi rapide que souhaitable. Enfin, les pattes doivent avoir une extension axiale importante, ce gui les fragilise encore et augmente la consommation de matière.An apparatus of this type is already known from United States Patent No. 5,383,540. According to this patent, the axially extending lugs are directed opposite the radial wall of the casing, and the intermediate disc carries friction linings at the periphery of its two faces and is suitable for being pressed, and to be driven by friction, between said piston clutch and said radial wall of the casing of the driving impeller. This intermediate disc, operated by hydraulic pressure, is therefore axially movable, in both directions, like a piston. This obviously results in repetitive friction between its drive lugs with axial extension also forming stop lugs and the springs, which are made of hard steel, hence rapid wear of the lugs of the intermediate disc. In addition, there is a risk of jamming, and the axial movement of the disc, which in any case is braked, is not as rapid as desirable. Finally, the legs must have a significant axial extension, this mistletoe weakens them further and increases the consumption of material.
Le but de la présente invention est de remédier à tous ces inconvénients, et à cet effet, un appareil de transmission de couple hydrocinétique du type défini ci- dessus est, conformément à la présente invention, caractérisé en ce que ce disque intermédiaire est monté dans le disque de support et possède des pattes d'arrêt s ' étendant axialement, au-delà des ressorts, vers la paroi radiale du carter en passant chacune entre deux ressorts consécutifs pour servir de butées et de moyens de maintien des extrémités de ces ressorts, cet appareil comportant en outre un disque d'entraînement qui est situé entre ladite paroi radiale du carter et un piston d'embrayage mobile axialement et manœuvré par pression hydraulique, ce disque d'entraînement portant à sa périphérie des pattes d'entraînement disposées par paires, lesdites pattes d'arrêt du disque intermédiaire étant engrenées chacune entre les deux pattes d'une paire de pattes d'entraînement du disque d'entraînement. Les pattes d'arrêt sont ainsi distinctes des pattes d'entraînement. De la sorte, les pattes d'entraînement du disque d'entraînement ne sont plus en contact avec les extrémités des ressorts, et elles ne peuvent donc plus être usées par frottement contre ceux-ci. Quant aux pattes d'arrêt, entraînées en rotation par les pattes d'entraînement, elles sont en contact avec les extrémités des ressorts, mais il n'y a aucun mouvement relatif de frottement entre elles et les ressorts, de sorte que là encore il n'y a pas d'usure des pattes. Les frottements axiaux ne peuvent donc se produire qu'entre les pattes d'entraînement et les pattes d'arrêt, lors des déplacements axiaux du disque d'entraînement, lui-même entraîné, axialement et en rotation, par le piston d'embrayage. On peut cependant conférer à la matière constituant ces pattes la même dureté, ce qui diminue fortement leur usure. Le disque d'entraînement se déplace axialement dans de bonnes conditions et rapidement sans risques de coincements. Cela est favorisé par le montage flottant du disque intermédiaire .The object of the present invention is to remedy all these drawbacks, and for this purpose, a hydrokinetic torque transmission device of the type defined above is, in accordance with the present invention, characterized in that this intermediate disc is mounted in the support disc and has stop lugs extending axially, beyond the springs, towards the radial wall of the casing, each passing between two consecutive springs to serve as stops and means for holding the ends of these springs, this apparatus further comprising a drive disc which is situated between said radial wall of the casing and a clutch piston movable axially and operated by hydraulic pressure, this drive disc carrying at its periphery drive tabs arranged in pairs , said legs of the intermediate disc each being meshed between the two legs of a pair of drive disc drive tabs. The stop lugs are thus distinct from the drive lugs. In this way, the drive tabs of the drive disc are no longer in contact with the ends of the springs, and they can therefore no longer be worn by friction against them. As for the stop lugs, driven in rotation by the drive lugs, they are in contact with the ends of the springs, but there is no relative friction movement between them and the springs, so that there again there is no wear of the legs. Axial friction can therefore only occur between the drive lugs and the stop lugs, during axial displacements of the drive disc, itself driven, axially and in rotation, by the clutch piston. However, the material constituting these tabs can be given the same hardness, which greatly reduces their wear. The drive disc moves axially in good conditions and quickly without risk of jamming. This is favored by the floating mounting of the intermediate disc.
L'invention sera mieux comprise, et d'autres particularités apparaîtront, à la lecture des modes de réalisation ci-dessous décrits à titre d'exemples nullement limitatifs, avec référence au dessin ci-annexé dans lequel :The invention will be better understood, and other particularities will appear on reading the embodiments described below by way of non-limiting examples, with reference to the attached drawing in which:
- la figure 1 est une demi-vue en coupe axiale partielle montrant le dispositif d'embrayage d'un appareil de transmission de couple hydrocinétique conforme à l'invention ne comportant pas de dispositif de guidage du moyeu de turbine, la liaison entre le piston d'embrayage et les extrémités des ressorts hélicoïdaux s 'effectuant grâce à un disque d'entraînement engrené avec un disque intermédiaire ;- Figure 1 is a half-view in partial axial section showing the clutch device of a hydrokinetic torque transmission device according to the invention having no device for guiding the turbine hub, the connection between the piston clutch and the ends of the helical springs being effected by means of a drive disc meshed with an intermediate disc;
- la figure 2 est une vue en perspective du disque d'entraînement engrené avec le disque intermédiaire, un seul ressort hélicoïdal étant représenté ;- Figure 2 is a perspective view of the drive disc meshed with the intermediate disc, a single helical spring being shown;
- la figure 3 est une vue en perspective du même ensemble de disques, mais vu de l'autre côté ; et- Figure 3 is a perspective view of the same set of discs, but seen from the other side; and
- la figure 4 est une demi-vue en coupe axiale partielle montrant une variante pourvue d'un dispositif de guidage du moyeu de turbine .- Figure 4 is a half view in partial axial section showing a variant provided with a device for guiding the turbine hub.
Dans le mode de réalisation de la figure 1, la roue de turbine à aubes a été référencée globalement en 1 , et la paroi radiale du carter 2, dit carter de la roue d'impulseur, a été référencée globalement en 2a. Cette paroi radiale 2a se prolonge axialement en 2b pour être raccordée, par exemple par un joint périphérique de soudure, à une partie complémentaire (non représentée) formant la roue d'impulseur à aubes, l'ensemble pouvant être calé sur un arbre menant, par exemple le vilebrequin d'un moteur à combustion interne. En 3 on a représenté sur la paroi radiale 2a l'un des goujons permettant de fixer le carter 2 de roue d'impulseur, par l'intermédiaire d'un flasque non représenté, sur le volant du moteur, la référence 4 désignant un arbre centreur soudé en 4a sur cette même paroi radiale 2a. La roue du réacteur, intervenant dans la phase dite "de conversion", lors de la mise en vitesse de la roue de turbine, n'a pas été non plus représentée sur le dessin, n'intervenant pas dans la compréhension de l'invention, et son principe de fonctionnement étant connu, sachant que l'ensemble roue d'impulseur - roue de turbine - roue de réacteur constitue un convertisseur de couple. De façon également connue, un dispositif d'embrayage s'étend radialement entre la roue de turbine 1 et la paroi radiale 2a du carter 2 de la roue d'impulseur, pour pouvoir assurer une solidarisation en rotation ou pontage de cette dernière et de la roue de turbine 1, et éviter ainsi tout glissement entre elles, en pontant ou "by-passant" l'accouplement hydrocinétique, lorsque la mise en vitesse de la roue de turbine 1, accouplée à l'arbre mené, à savoir l'arbre d'entrée de la transmission, est terminée.In the embodiment of FIG. 1, the impeller of the paddle wheel has been generally referenced at 1, and the radial wall of the casing 2, called casing of the impeller, has been generally referenced at 2a. This radial wall 2a is extended axially at 2b to be connected, for example by a peripheral weld joint, to a complementary part (not shown) forming the impeller of impellers, the assembly being able to be wedged on a driving shaft, for example the crankshaft of an internal combustion engine. 3 shows on the radial wall 2a one of the studs making it possible to fix the casing 2 of the impeller wheel, by means of a flange not shown, on the engine flywheel, the reference 4 designating a shaft centralizer welded in 4a on this same radial wall 2a. The reactor wheel, involved in the so-called "conversion" phase, when the turbine wheel is speeding up, has also not been shown in the drawing, not being involved in understanding the invention , and its operating principle being known, knowing that the impeller wheel - turbine wheel - reactor wheel assembly constitutes a torque converter. In a manner also known, a clutch device extends radially between the turbine wheel 1 and the radial wall 2a of the casing 2 of the impeller wheel, in order to be able to secure in rotation or bridging the latter and the turbine wheel 1, and thus avoid any sliding between them, by bridging or "by-passing" the hydrokinetic coupling, when the setting in speed of the turbine wheel 1, coupled to the driven shaft, namely the shaft transmission input is complete.
Ce dispositif d'embrayage comporte à cet effet, par exemple, et dans le mode de réalisation de la figure 1, un piston d'embrayage à fonction de plateau de pression 5 comportant centralement une virole 6 par 1 ' intermédiaire de laquelle il peut coulisser axialement et de façon étanche (joint annulaire 7) sur la périphérie externe d'une partie en forme de bague de poussée 8 de l'arbre centreur 4. A l'intérieur de l'arbre 4 est ménagé un espace borgne 9 qui peut être alimenté en fluide sous pression et qui communique par des passages 10 de l'arbreThis clutch device comprises for this purpose, for example, and in the embodiment of FIG. 1, a clutch piston with a pressure plate function 5 centrally comprising a ferrule 6 through which it can slide axially and sealingly (annular seal 7) on the external periphery of a portion in the form of a thrust ring 8 of the centering shaft 4. Inside the shaft 4 is provided a blind space 9 which can be supplied with pressurized fluid and which communicates through passages 10 of the shaft
4 avec une chambre 11 de commande ménagée entre le piston4 with a control chamber 11 formed between the piston
5 et la paroi radiale 2a. La référence 12 désigne des ergots de la bague 8 possédant une surface extérieure cylindrique permettant le guidage de la virole 6 du piston 5, mais laissant passer le fluide sous pression entre l'espace 9 et la chambre 11. Le flasque 13 d'un moyeu 14, cannelé intérieurement en 14a, est solidarisé de la roue de turbine 1, ainsi que d'un disque de support 15 qui sera décrit plus bas, par tout système de solidarisation approprié, par exemple des points de soudure ou des rivets 16. Une cale 17 en forme d'anneau plat en un matériau à faible coefficient de frottement est rapportée sur le flasque 13 ou sur la bague de poussée 8 pour constituer une pièce d'appui axial entre ces deux pièces en évitant entre elles tout contact métal sur métal. Le moyeu 14, par l'intermédiaire de ses cannelures 14a, est destiné à être solidarisé d'un arbre mené doté d'un canal pour alimenter la chambre 11 via l'espace 9.5 and the radial wall 2a. The reference 12 designates lugs of the ring 8 having a cylindrical outer surface allowing the guide of the ferrule 6 of the piston 5, but letting the pressurized fluid pass between the space 9 and the chamber 11. The flange 13 of a hub 14, internally fluted at 14a, is secured to the turbine wheel 1, as well as to a support disc 15 which will be described below, by any suitable fastening system, for example welding spots or rivets 16. A wedge 17 in the form of a flat ring made of a material with a low coefficient of friction is attached to the flange 13 or to the thrust ring 8 to constitute an axial support piece between these two pieces, avoiding any metal-to-metal contact between them. The hub 14, by means of its grooves 14a, is intended to be secured to a driven shaft provided with a channel for supplying the chamber 11 via the space 9.
De façon également connue, le piston 5 est solidarisé en rotation de la paroi radiale 2a du carter 2 de la roue d'impulseur, ceci de façon à autoriser les déplacements axiaux relatifs entre ces deux éléments. Cet accouplement peut être réalisé par tout moyen approprié, par exemple par un système à tenon et mortaise ou par l'intermédiaire de languettes axialement élastiques 18 rivetées en 19 sur la paroi 2a et fixées par ailleurs sur des bossages 20 du piston 5 par un système de serrage quelconque 21, ceci de sorte à exercer une traction axiale sur ce disque, en direction de la paroi radiale 2a. Un dispositif de ce type est décrit par exemple dans le brevet français n° 94 13205 du 4 novembre 1994 au nom de la demanderesse. Le dispositif d'embrayage comporte par ailleurs un disque d'entraînement 22 porteur, sur ses deux faces, de garnitures de frottement référencées en 23 (voir également figures 2 et 3) . Ce disque 22 comporte en prolongement de son bord extérieur, et angulairement équiréparties selon sa périphérie, des pattes d'entraînement 24 disposées par paires, pliées sous un angle obtus et globalement dirigées à l'opposé de la paroi radiale 2a.In a manner also known, the piston 5 is secured in rotation to the radial wall 2a of the casing 2 of the impeller, this so as to allow the relative axial displacements between these two elements. This coupling can be carried out by any suitable means, for example by a tenon and mortise system or by means of axially elastic tongues 18 riveted at 19 to the wall 2a and fixed moreover to bosses 20 of the piston 5 by a system any clamping 21, this so as to exert an axial traction on this disc, in the direction of the radial wall 2a. A device of this type is described for example in French patent n ° 94 13205 of November 4, 1994 in the name of the applicant. The clutch device also comprises a drive disc 22 carrying, on its two faces, friction linings referenced at 23 (see also Figures 2 and 3). This disc 22 comprises, as an extension of its outer edge, and angularly evenly distributed along its periphery, drive tabs 24 arranged in pairs, bent at an obtuse angle and generally directed away from the radial wall 2a.
Quant au disque de support 15 cité plus haut, il comporte à sa périphérie externe une gorge 25 s ' ouvrant en direction de la paroi radiale 2a du carter 2 et terminée par un flanc globalement cylindrique 26 pourvu d'appuis radialement rentrants 26a constituant entre eux des logements pour une série de ressorts hélicoïdaux d'amortissement 27 ; un disque de support complémentaire 29 est soudé en 30 au disque de support 15 et comporte à sa périphérie un flanc incliné 31, refermant partiellement les logements précités des ressorts 27, lequel flanc porte, vis-à-vis des appuis 26a, des appuis complémentaires 31a contribuant à délimiter lesdits logements et servant, en même temps que les appuis 26a, de surfaces de butée pour les extrémités des ressorts 27 à action circonférentielle. Conformément à l'invention, cet appareil comporte entre les disques 15 et 29 un disque intermédiaire 32 (voir aussi figure 2) qui porte, en saillie radiale vers l'extérieur, une série de pattes d'arrêt 33 à extension axiale et angulairement équiréparties, dirigées vers la paroi radiale 2a du carter et présentant des deux côtés des ergots 34 dans lesquels s'engagent les deux extrémités opposées de chaque ressort 27. Les figures 2 et 3 montrent 1 ' engrènement mutuel des disques d'entraînement 22 et intermédiaire 32, chaque patte d'arrêt 33 du disque intermédiaire s 'engageant entre deux pattes 24 d'entraînement consécutives du disque d'entraînement 22.As for the support disc 15 mentioned above, it has at its outer periphery a groove 25 opening towards the radial wall 2a of the casing 2 and terminated by a generally cylindrical flank 26 provided with radially re-entrant supports 26a constituting between them housings for a series of coil springs depreciation 27; a complementary support disc 29 is welded at 30 to the support disc 15 and comprises at its periphery an inclined flank 31, partially closing the aforementioned housings of the springs 27, which flank carries, with respect to the supports 26a, complementary supports 31a contributing to delimit said housings and serving, at the same time as the supports 26a, abutment surfaces for the ends of the springs 27 with circumferential action. According to the invention, this device comprises between the discs 15 and 29 an intermediate disc 32 (see also Figure 2) which carries, projecting radially outwards, a series of stop lugs 33 with axial extension and angularly distributed , directed towards the radial wall 2a of the casing and having on both sides of the lugs 34 in which engage the two opposite ends of each spring 27. Figures 2 and 3 show one mutual engagement of the drive discs 22 and intermediate 32 , each stop tab 33 of the intermediate disc engaging between two consecutive drive tabs 24 of the drive disc 22.
Le fonctionnement de l'appareil qui vient d'être décrit est le même que celui des appareils classiques et n'est donc rappelé ici que pour mémoire : en phase de démarrage, la pression du fluide hydraulique dans la chambre 11 est telle qu'elle maintient le piston d'embrayage 5 écarté de la paroi radiale 2a, de sorte que les garnitures 23 du disque d'entraînement 22, écartées de la paroi 2a, ne sont pas entraînées en rotation, nonobstant la rotation (permanente) du disque 5. Le couple de la roue d'impulseur est donc transmis à la roue de turbine 1, avec glissement, uniquement par effet hydrocinétique dans l'appareil (phase de conversion). Les ressorts 27 sont inactifs.The operation of the device which has just been described is the same as that of conventional devices and is therefore recalled here only for the record: in the start-up phase, the pressure of the hydraulic fluid in the chamber 11 is such that it keeps the clutch piston 5 spaced from the radial wall 2a, so that the linings 23 of the drive disc 22, spaced from the wall 2a, are not rotated, notwithstanding the (permanent) rotation of the disc 5. The torque of the impeller wheel is therefore transmitted to the turbine wheel 1, with sliding, only by effect hydrokinetic in the device (conversion phase). The springs 27 are inactive.
Lorsque la roue de turbine 1 n'accélère plus, on relâche la pression du fluide hydraulique dans la chambre 11, et les languettes de ressort 18 font coulisser le piston d'embrayage 5 vers la paroi radiale 2a, ce qui presse les garnitures 23 du disque d'entraînement 22 entre le piston 5 et la face intérieure de cette paroi 2a, ces deux pièces étant entraînées en rotation permanente par la roue d'impulseur. Avec l'amortissement de couple dû aux ressorts 27, la roue de turbine 1 se trouve ainsi entraînée rapidement à la même vitesse que la roue d'impulseur, avec disparition de tout glissement. Les ressorts 27 évitent tout à-coup du couple, puisqu'ils peuvent être comprimés chacun entre une paroi radiale d'extrémité 26a-31a des logements du disque de support 15- 29 et la patte correspondante 33 du disque intermédiaire, lequel est alors entraîné en rotation par le disque d'entraînement 22. On voit qu'il ne peut y avoir ici des frottements qu'entre les pattes 24 et 33, sans aucun frottement entre les pattes 33 et les ressorts d'amortissement 27.When the turbine wheel 1 no longer accelerates, the pressure of the hydraulic fluid is released in the chamber 11, and the spring tabs 18 cause the clutch piston 5 to slide towards the radial wall 2a, which presses the linings 23 of the drive disc 22 between the piston 5 and the inner face of this wall 2a, these two parts being driven in permanent rotation by the impeller. With the damping of torque due to the springs 27, the turbine wheel 1 is thus quickly driven at the same speed as the impeller, with disappearance of any slip. The springs 27 suddenly avoid torque, since they can each be compressed between a radial end wall 26a-31a of the housings of the support disc 15-29 and the corresponding tab 33 of the intermediate disc, which is then driven in rotation by the drive disc 22. It can be seen that there can be friction here only between the legs 24 and 33, without any friction between the legs 33 and the damping springs 27.
Dans le mode de réalisation de la figure 4, on a représenté une variante selon laquelle le moyeu de turbine 14 peut être guidé par l'arbre centreur 4, par l'intermédiaire d'une bague de guidage radial 35. En 36 on a représenté une butée axiale entre la paroi radiale 2 et le moyeu de la turbine, cette butée étant pourvue de rainures pour le passage de l'huile entre l'espace borgne 9 et la chambre 11. Les autres références ont la même signification que sur la figure 1.In the embodiment of Figure 4, there is shown a variant in which the turbine hub 14 can be guided by the centering shaft 4, by means of a radial guide ring 35. At 36 there is shown an axial stop between the radial wall 2 and the hub of the turbine, this stop being provided with grooves for the passage of oil between the blind space 9 and the chamber 11. The other references have the same meaning as in the figure 1.
On appréciera que le disque intermédiaire 32 est monté flottant entre les disques de support 15, 29 et que l'inclinaison des pattes 24 du disque 22 évite toute interférence entre les pattes 33 et la paroi 2a. Les ressorts 27 sont ainsi bien comprimés et les pattes 33, 24 n'ont pas besoin d'être traitées pour être durcies. Grâce à l'invention, le disque d'entraînement peut être en matière synthétique et frotter directement sur le piston 5 et la paroi 2a. En variante, les garnitures 23 sont fixées respectivement sur le piston 5 et la paroi 2a. Bien entendu, la présence d'une roue de réacteur n'est pas indispensable, l'appareil de transmission de couple comprenant alors un coupleur. It will be appreciated that the intermediate disc 32 is mounted floating between the support discs 15, 29 and that the inclination of the legs 24 of the disc 22 avoids any interference between the legs 33 and the wall 2a. The springs 27 are thus well compressed and the legs 33, 24 do not need to be treated to be hardened. Thanks to the invention, the drive disc can be made of synthetic material and rub directly on the piston 5 and the wall 2a. As a variant, the linings 23 are fixed respectively to the piston 5 and the wall 2a. Of course, the presence of a reactor wheel is not essential, the torque transmission device then comprising a coupler.
Claims
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR9900025A FR2788093B1 (en) | 1999-01-05 | 1999-01-05 | HYDROKINETIC TORQUE TRANSMISSION APPARATUS WITH LOCKING CLUTCH |
| FR99/00025 | 1999-01-05 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2000040877A1 true WO2000040877A1 (en) | 2000-07-13 |
Family
ID=9540625
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/FR2000/000015 Ceased WO2000040877A1 (en) | 1999-01-05 | 2000-01-05 | Hydrokinetic torque transmission device with lock-up clutch |
Country Status (2)
| Country | Link |
|---|---|
| FR (1) | FR2788093B1 (en) |
| WO (1) | WO2000040877A1 (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5383540A (en) | 1993-10-04 | 1995-01-24 | Ford Motor Company | Torque converter bypass clutch piston-pump drive for an automatic transmission |
| WO1996014526A1 (en) | 1994-11-04 | 1996-05-17 | Valeo | Lock-up clutch for a hydrokinetic coupling device, in particular for motor vehicles, and method for mounting same |
| WO1997047901A1 (en) * | 1996-06-10 | 1997-12-18 | Valeo | Hydrokinetic coupling device in particular for motor vehicle |
| FR2765296A1 (en) * | 1997-06-30 | 1998-12-31 | Valeo | HYDROKINETIC COUPLING APPARATUS WITH LOCKING CLUTCH FOR MOTOR VEHICLE |
-
1999
- 1999-01-05 FR FR9900025A patent/FR2788093B1/en not_active Expired - Lifetime
-
2000
- 2000-01-05 WO PCT/FR2000/000015 patent/WO2000040877A1/en not_active Ceased
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5383540A (en) | 1993-10-04 | 1995-01-24 | Ford Motor Company | Torque converter bypass clutch piston-pump drive for an automatic transmission |
| WO1996014526A1 (en) | 1994-11-04 | 1996-05-17 | Valeo | Lock-up clutch for a hydrokinetic coupling device, in particular for motor vehicles, and method for mounting same |
| US5826690A (en) * | 1994-11-04 | 1998-10-27 | Valeo | Process for the assembly of a locking clutch for a hydrokinetic coupling device, especially for a motor vehicle, a corresponding locking clutch and a hydrokinetic coupling device comprising such a locking clutch |
| WO1997047901A1 (en) * | 1996-06-10 | 1997-12-18 | Valeo | Hydrokinetic coupling device in particular for motor vehicle |
| FR2765296A1 (en) * | 1997-06-30 | 1998-12-31 | Valeo | HYDROKINETIC COUPLING APPARATUS WITH LOCKING CLUTCH FOR MOTOR VEHICLE |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2788093A1 (en) | 2000-07-07 |
| FR2788093B1 (en) | 2001-03-23 |
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