WO2006125932A1 - Multiple clutch device - Google Patents

Multiple clutch device Download PDF

Info

Publication number
WO2006125932A1
WO2006125932A1 PCT/FR2006/050377 FR2006050377W WO2006125932A1 WO 2006125932 A1 WO2006125932 A1 WO 2006125932A1 FR 2006050377 W FR2006050377 W FR 2006050377W WO 2006125932 A1 WO2006125932 A1 WO 2006125932A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive flange
clutch
cylindrical skirt
clutch device
axial
Prior art date
Application number
PCT/FR2006/050377
Other languages
French (fr)
Inventor
Mathieu Leleu
Marc Logez
Fabrice Olejniczak
Original Assignee
Renault S.A.S.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Renault S.A.S. filed Critical Renault S.A.S.
Publication of WO2006125932A1 publication Critical patent/WO2006125932A1/en

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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae

Definitions

  • the present invention relates to multiple wet friction disc clutches, particularly for power transmission in a motor vehicle.
  • the input of the engine torque in a multiple clutch is generally done by means of a so-called drive flange which ensures the mechanical connection between the engine and the engine. a secondary member of a vibration damper and the outer bell of the outer clutch of the multiple clutch.
  • additional constraints may be imposed on the drive flange, such as coaxiality, eccentricity and reduced axial clearance with respect to the clutch housing and gearbox differential. It is then necessary to ensure precise centering and effective axial positioning of the drive flange relative to a member of the drive train of the multiple clutch.
  • it is advantageous that the mechanical connection between the drive flange and the outer bell of the outer clutch of the multiple clutch is easily removable to allow maintenance operations on internal elements of the multiple clutch.
  • EP-A-I 174 633 discloses a dual clutch device in which the mechanical connection between the drive flange and the outer bell of the outer clutch is achieved by the engagement of peripheral radial teeth of the drive flange with internal splines of a cylindrical skirt of the outer bell of the outer clutch. These internal splines are also used to mount the discs or friction strips of the outer clutch.
  • Two stop rings, also mounted in grooves of the cylindrical skirt, provide axial fixation of the drive flange. One of these stop rings also acts as a stop for the external friction disk of the clutch.
  • EP-A-I 422 430 (Volkswagen and BorgWarner) also discloses a support bell for friction discs of a clutch mechanically connected to a flange training. The connection is made by peripheral teeth of the drive flange which penetrate into recesses formed in the cylindrical portion of the support bell.
  • the present invention aims to reduce or eliminate these disadvantages.
  • the invention also relates to a clutch device in which a precise centering, of low tolerance, is obtained between the drive flange and the outer bell of the clutch.
  • the invention also relates to such a clutch device in which the mechanical connection between the outer bell of the clutch and the drive flange is easily removable and reusable after disassembly.
  • the invention finally relates to such a clutch device in which the internal stresses of the outer bell of the clutch are limited and where self - centering of the outer bell relative to the drive flange is obtained from a sufficient rotation regime.
  • the wet friction disc multiple clutch device in particular for power transmission in a motor vehicle, is of the type comprising a driving flange transmitting the motor torque, possibly via a vibration damper, and an outer bell inside which are mounted a plurality of friction discs of an outer clutch.
  • the drive flange and the outer bell are interconnected by form coupling between recesses of a cylindrical skirt of the outer bell and axial teeth of the drive flange.
  • the teeth of the drive flange have folded ends axially shaped tongues capable of coming into contact with curved portions of the outer surface of the cylindrical skirt.
  • the drive flange and outer bell of the clutch are thus mounted with a sliding fit.
  • the folded ends of the teeth of the drive flange limit the deformation of the outer bell under the effect of the centrifugal force limiting the internal stresses exerted on the outer bell.
  • the curved portions have preferably been obtained by stamping the cylindrical skirt. These curved portions are rectified to a small thickness, for example from one to ten tenths of a mm, which avoids breaking the fibers of the constituent material outside the closely localized areas of the curved portions. The relaxation of the constraints of the outer bell is thus minimized and the mechanical strength of the outer bell of the clutch is maintained at its maximum.
  • An axial stop ring of the drive flange is advantageously mounted in a groove in the inner surface of the cylindrical skirt.
  • the axial stop ring of the driving flange is preferably a radially split piece. In this way, when disassembling the drive flange, for example for a clutch maintenance operation, simply remove the stop ring and then the drive flange.
  • An axial abutment ring of a support plate of the friction discs of the outer clutch is also advantageously mounted in a groove formed in the inner surface of the cylindrical skirt.
  • Figure 1 is a partial and schematic axial sectional view of an embodiment of the invention
  • Figure 2 is a partial broken perspective view showing the connection zone between the drive flange and the outer bell.
  • the clutch device is of the "double wet clutch" type.
  • Figure 1 which shows a partial axial sectional view of the clutch device 1
  • the device is normally completed by a second clutch arranged radially inside the outer clutch 2, the assembly forming a double clutch device.
  • the power from the vehicle engine passes through a vibration damping device 3 of which only the secondary member 3a has been shown in Figure 1 for the sake of simplification.
  • the torsion damping damping device referenced 3 as a whole can be replaced by a similar device, for example, having a double damping flywheel, or even be deleted.
  • the secondary member 3a comprises a cylindrical portion 4 which carries on its radially outer periphery splines 5 which allow the connection with corresponding splines 6 made on an annular cylindrical piece 7 which is integral with a drive flange 8 and a protective casing 9.
  • the outer clutch 2 comprises a plurality of disks or strips 10 arranged radially and side by side in an axial direction with appropriate spacings for the housing of disks or corresponding plates 11.
  • the respective friction contact between the disks 10 and the disks 11 is able to ensure the clamping of the clutch 2 and the fastening of the inner bell 12 of the clutch 2 with the outer bell 13 of said clutch.
  • the inner bell 12 has a cylindrical portion 14 provided with spaced axial grooves receiving notches provided on the bore of the discs 10. These notches can be accommodated and held in said axial grooves by allowing an axial displacement of the discs 10. the same way, the outer bell 13 has a cylindrical skirt 15 axially directed from the inside towards the damping device 3.
  • This cylindrical skirt has spaced axial grooves 15a inside which are received notches provided on the periphery of the discs 11 These notches can be accommodated and held in the grooves 15a axial by allowing axial movement of the discs 11.
  • Actuation of the clutch 2 by clamping against each other respective disks 10 and 11 is effected by a piston 17 controlled hydraulically by means not shown in the figure.
  • the piston 17 has a radial support portion 17a which exerts a compressive force on the discs 11 whose surface is generally smooth and on the discs 10 whose surface is generally coated with a liner.
  • the inner bell 12 When the clutch is tightened, the inner bell 12 is made integral with the outer bell 13 and the power of the motor passes through the clutch 2 to the output shaft schematized at 18 on which is fixed the inner bell 12 by his fixing sleeve
  • the assembly of the double clutch device comprising the outer clutch 2 and a not shown inner clutch operates in a humid environment, ie within an oil filled space. Sealing is ensured by means of a seal 19 in frictional contact with the cylindrical part 7.
  • the seal 19 is integral with a closing plate 20 which is connected to the casing 21 housing both the device of FIG. clutch 1 and a differential not shown in the figure.
  • the link allowing the transmission of power between the drive flange 8 and the outer bell 13 is done by means of a conjugation between the teeth 22 of the drive flange 8 and the curved portions 23 of the outer surface of the cylindrical skirt 15.
  • Figure 2 shows in more detail the structure of these elements.
  • the drive flange 8 has over its entire periphery, teeth 22 constituted by radial projections 24 distributed equi-angularly and leaving between them recesses 25.
  • the ends of the protrusions 24 are folded axially in the form of tongues 26 directed towards the left in the figures, that is to say from the damping device 3 to the outer bell 13.
  • the curved portions 23 which are advantageously made by stamping the material of the cylindrical skirt 15 are also arranged with regular spacings on the entire periphery of the skirt 15, with the same spacing as the tabs 26.
  • the cylindrical skirt 15 has recesses 27 in axial extension of the curved portions 23.
  • the cylindrical skirt 15 further has axial teeth 28 whose concavity is directed outwards and which are between the grooves 15a whose concavity is directed inwards. These teeth 28 are arranged between the various convex portions 23 and the recesses 27 and form axial projections which can penetrate inside the recesses 25 of the drive flange 8.
  • the inner surface of the tongues 26 comes into frictional contact with the outer surface of the curved portions 23.
  • the radial teeth 24 penetrate inside the recesses 27 while the axial teeth 28 penetrate inside the recesses 25.
  • the bulged portions 23 ensure the centering of the assembly.
  • the inner surface of the folded tabs 26 is ground to the same extent as the outer surface of the bulged portions 23 so as to ensure a precise fit between these two parts.
  • a split radial ring referenced 29 ( Figure 1) can be mounted in a groove 30 formed on the inner surface of the teeth 28 of the cylindrical skirt 15 slightly outside the curved portions 23.
  • the radial ring 29 keeps the tray a second locking ring, referenced 31 and visible in FIG. 2, provides axial locking against any potential displacement of the drive flange 8.
  • the locking ring 31 which advantageously in the form of a split ring to facilitate assembly, is housed in a groove 32 formed in the inner surface of the teeth 28 of the cylindrical skirt 15.
  • This grinding can be carried out on a small thickness of the order of a few tenths of a mm, by breaking the fibers of the outer bell only in a very localized manner.
  • the relaxation of the stresses in the outer bell is thus minimized and therefore also the possible degradation of the mechanical strength of the outer bell.
  • the mounting of the drive flange and its connection as just explained with the outer bell also has the advantage of limiting the deformation of the outer bell due to the centrifugal force.
  • the constraints on the outer bell of the clutch are therefore limited.
  • the sliding fit between the outer bell and the drive flange allows self - centering of these two parts from a sufficient rotational speed.
  • connection between the drive flange and the outer bell of the clutch is easily removable by simply removing the stop ring 31.
  • the reassembly of the parts can also be performed without difficulty after a maintenance intervention on the elements. internal clutch device.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

The invention concerns a multiple clutch device with hydraulic-actuated friction discs, in particular for power transmission in a motor vehicle, of the type comprising a drive flange (8) transmitting the engine torque, optionally via a vibration damper (3), and an outer casing (13) wherein are mounted several friction discs of an outer clutch (2), the drive flange and the outer casing being mutually connected by shape matching between recesses of a cylindrical skirt (15) of the outer casing (13) and axial teeth (24) of the drive flange. The invention is characterized in that the teeth of the drive flange have axially folded tongue-shaped ends (26) capable of being urged into contact with convex parts (23) of the outer surface of the cylindrical skirt (15).

Description

Dispositif d'embrayage multiple Multiple clutch device
La présente invention est relative aux embrayages multiples à disques de friction en milieu humide, en particulier pour transmission de puissance dans un véhicule automobile.The present invention relates to multiple wet friction disc clutches, particularly for power transmission in a motor vehicle.
Dans une boîte de vitesses à transmission de puissance classique, l' entrée du couple moteur dans un embrayage multiple, en particulier un embrayage double, se fait généralement par l' intermédiaire d'un flasque dit d' entraînement qui assure la liaison mécanique entre l' organe secondaire d'un amortisseur de vibrations et la cloche extérieure de l' embrayage extérieur de l' embrayage multiple. Dans certains cas, des contraintes supplémentaires peuvent être imposées au flasque d' entraînement, telles que, coaxialité, excentricité et débattement axial réduit par rapport au carter d' embrayage et différentiel de la boîte de vitesses. Il convient alors d' assurer un centrage précis et un positionnement axial effectif du flasque d' entraînement par rapport à un organe de la chaîne cinématique de l' embrayage multiple. De plus, il est avantageux que la liaison mécanique entre le flasque d' entraînement et la cloche extérieure de l' embrayage extérieur de l' embrayage multiple soit facilement démontable pour permettre les opérations de maintenance sur des éléments internes de l' embrayage multiple.In a conventional transmission with power transmission, the input of the engine torque in a multiple clutch, in particular a double clutch, is generally done by means of a so-called drive flange which ensures the mechanical connection between the engine and the engine. a secondary member of a vibration damper and the outer bell of the outer clutch of the multiple clutch. In some cases, additional constraints may be imposed on the drive flange, such as coaxiality, eccentricity and reduced axial clearance with respect to the clutch housing and gearbox differential. It is then necessary to ensure precise centering and effective axial positioning of the drive flange relative to a member of the drive train of the multiple clutch. In addition, it is advantageous that the mechanical connection between the drive flange and the outer bell of the outer clutch of the multiple clutch is easily removable to allow maintenance operations on internal elements of the multiple clutch.
La demande de brevet européen EP-A- I 174 633 (Mannesman Sachs) décrit un dispositif d' embrayage double dans lequel la liaison mécanique entre le flasque d' entraînement et la cloche extérieure de l' embrayage extérieur est réalisée par l'engagement de dents radiales périphériques du flasque d' entraînement avec des cannelures internes d'une jupe cylindrique de la cloche extérieure de l' embrayage extérieur. Ces cannelures internes servent également au montage des disques ou lamelles de friction de l' embrayage extérieur. Deux anneaux d' arrêt également montés dans des gorges de la jupe cylindrique, assurent la fixation axiale du flasque d'entraînement. L'un de ces anneaux d' arrêt joue en outre le rôle de butée pour le disque de friction externe de l' embrayage. La demande de brevet européen EP-A- I 422 430 (Volkswagen et BorgWarner) décrit également une cloche de support des disques de friction d'un embrayage reliée mécaniquement à un flasque d' entraînement. La liaison est réalisée par des dents périphériques du flasque d' entraînement qui pénètrent dans des évidements pratiqués dans la portion cylindrique de la cloche de support.The European patent application EP-A-I 174 633 (Mannesman Sachs) discloses a dual clutch device in which the mechanical connection between the drive flange and the outer bell of the outer clutch is achieved by the engagement of peripheral radial teeth of the drive flange with internal splines of a cylindrical skirt of the outer bell of the outer clutch. These internal splines are also used to mount the discs or friction strips of the outer clutch. Two stop rings, also mounted in grooves of the cylindrical skirt, provide axial fixation of the drive flange. One of these stop rings also acts as a stop for the external friction disk of the clutch. European Patent Application EP-A-I 422 430 (Volkswagen and BorgWarner) also discloses a support bell for friction discs of a clutch mechanically connected to a flange training. The connection is made by peripheral teeth of the drive flange which penetrate into recesses formed in the cylindrical portion of the support bell.
Dans ces deux demandes de brevet, la liaison mécanique entre la cloche extérieure de l'embrayage et le flasque d'entraînement ne permet qu'un centrage sur une faible distance axiale, correspondant à l' épaisseur des dents périphériques du flasque d' entraînement. Il en résulte une série d' inconvénients, et notamment un mouvement de rotule de ces deux pièces l'une par rapport à l' autre lors du fonctionnement de la boîte de vitesses ainsi qu'une excentricité à bas régime de rotation. Ces mouvements non désirés entraînent des défauts d' étanchéité de l' embrayage humide.In these two patent applications, the mechanical connection between the outer bell of the clutch and the drive flange only allows a centering over a small axial distance, corresponding to the thickness of the peripheral teeth of the drive flange. This results in a series of disadvantages, and in particular a swivel movement of these two parts relative to each other during the operation of the gearbox as well as an eccentricity at low rotational speed. These unwanted movements cause leakage of the wet clutch.
La présente invention a pour objet de réduire, voire de supprimer ces inconvénients. L' invention a également pour objet un dispositif d' embrayage dans lequel un centrage précis, de faible tolérance, est obtenu entre le flasque d' entraînement et la cloche extérieure de l' embrayage.The present invention aims to reduce or eliminate these disadvantages. The invention also relates to a clutch device in which a precise centering, of low tolerance, is obtained between the drive flange and the outer bell of the clutch.
L' invention a encore pour objet un tel dispositif d'embrayage dans lequel la liaison mécanique entre la cloche extérieure de l' embrayage et le flasque d' entraînement est aisément démontable et réutilisable après démontage.The invention also relates to such a clutch device in which the mechanical connection between the outer bell of the clutch and the drive flange is easily removable and reusable after disassembly.
L' invention a enfin pour objet un tel dispositif d' embrayage dans lequel les contraintes internes de la cloche extérieure de l' embrayage sont limitées et où un auto-centrage de la cloche extérieure par rapport au flasque d' entraînement est obtenu à partir d'un régime de rotation suffisant.The invention finally relates to such a clutch device in which the internal stresses of the outer bell of the clutch are limited and where self - centering of the outer bell relative to the drive flange is obtained from a sufficient rotation regime.
Dans un mode de réalisation, le dispositif d' embrayage multiple à disques de friction en milieu humide, en particulier pour transmission de puissance dans un véhicule automobile, est du type comprenant un flasque d' entraînement transmettant le couple moteur, éventuellement par l'intermédiaire d'un amortisseur de vibrations, et une cloche extérieure à l' intérieur de laquelle sont montés plusieurs disques de friction d'un embrayage extérieur. Le flasque d' entraînement et la cloche extérieure sont liés entre eux par conjugaison de forme entre des évidements d'une jupe cylindrique de la cloche extérieure et des dents axiales du flasque d' entraînement. Les dents du flasque d'entraînement présentent des extrémités repliées axialement en forme de languettes capables d' entrer en contact avec des parties bombées de la surface externe de la jupe cylindrique.In one embodiment, the wet friction disc multiple clutch device, in particular for power transmission in a motor vehicle, is of the type comprising a driving flange transmitting the motor torque, possibly via a vibration damper, and an outer bell inside which are mounted a plurality of friction discs of an outer clutch. The drive flange and the outer bell are interconnected by form coupling between recesses of a cylindrical skirt of the outer bell and axial teeth of the drive flange. The teeth of the drive flange have folded ends axially shaped tongues capable of coming into contact with curved portions of the outer surface of the cylindrical skirt.
Le flasque d' entraînement et la cloche extérieure de l' embrayage sont ainsi montés avec un ajustement glissant. De plus, les extrémités repliées des dents du flasque d' entraînement limitent la déformation de la cloche extérieure sous l'effet de la force centrifuge limitant les contraintes internes s' exerçant sur la cloche extérieure.The drive flange and outer bell of the clutch are thus mounted with a sliding fit. In addition, the folded ends of the teeth of the drive flange limit the deformation of the outer bell under the effect of the centrifugal force limiting the internal stresses exerted on the outer bell.
Les extrémités repliées axialement en forme de languettes sont avantageusement rectifiées sur leur surface interne tandis que les parties bombées sont rectifiées sur leur surface externe. Un ajustement précis est ainsi obtenu entre le flasque d' entraînement et la cloche extérieure de l' embrayage.The ends folded axially in the form of tongues are advantageously ground on their inner surface while the curved portions are rectified on their outer surface. A precise fit is thus obtained between the drive flange and the outer bell of the clutch.
Les parties bombées ont de préférence été obtenues par emboutissage de la jupe cylindrique. Ces parties bombées sont rectifiées sur une faible épaisseur, par exemple de un à dix dixièmes de mm, ce qui évite de casser les fibres de la matière constitutive en dehors des zones étroitement localisées des parties bombées. Le relâchement des contraintes de la cloche extérieure est ainsi minimisé et la tenue mécanique de la cloche extérieure de l' embrayage est donc maintenue à son maximum.The curved portions have preferably been obtained by stamping the cylindrical skirt. These curved portions are rectified to a small thickness, for example from one to ten tenths of a mm, which avoids breaking the fibers of the constituent material outside the closely localized areas of the curved portions. The relaxation of the constraints of the outer bell is thus minimized and the mechanical strength of the outer bell of the clutch is maintained at its maximum.
Un anneau d' arrêt axial du flasque d' entraînement est avantageusement monté dans une gorge pratiquée dans la surface intérieure de la jupe cylindrique.An axial stop ring of the drive flange is advantageously mounted in a groove in the inner surface of the cylindrical skirt.
L' anneau d' arrêt axial du flasque d'entraînement est de préférence une pièce fendue radialement. De cette manière, lors du démontage du flasque d' entraînement, par exemple pour une opération de maintenance de l'embrayage, il suffit de retirer l' anneau d' arrêt puis le flasque d' entraînement.The axial stop ring of the driving flange is preferably a radially split piece. In this way, when disassembling the drive flange, for example for a clutch maintenance operation, simply remove the stop ring and then the drive flange.
Un anneau de butée axiale d'un plateau d' appui des disques de friction de l' embrayage extérieur est également avantageusement monté dans une gorge pratiquée dans la surface intérieure de la jupe cylindrique.An axial abutment ring of a support plate of the friction discs of the outer clutch is also advantageously mounted in a groove formed in the inner surface of the cylindrical skirt.
L' invention sera mieux comprise à l' étude d'un mode de réalisation particulier, pris à titre d' exemple nullement limitatif, illustré par les dessins annexés sur lesquels :The invention will be better understood in the study of a particular embodiment, taken by way of non limitative example, illustrated by the appended drawings in which:
La figure 1 est une vue en coupe axiale partielle et schématique d'un mode de réalisation de l' invention ; La figure 2 est une vue partielle en perspective arrachée montrant la zone de liaison entre le flasque d' entraînement et la cloche extérieure.Figure 1 is a partial and schematic axial sectional view of an embodiment of the invention; Figure 2 is a partial broken perspective view showing the connection zone between the drive flange and the outer bell.
Tel qu' il est illustré sur la figure 1 , le dispositif d' embrayage est du type « double embrayage humide ». Sur la figure 1 qui représente une vue en coupe axiale partielle du dispositif d' embrayage 1 , seul l' embrayage extérieur 2 a été représenté. On comprendra que le dispositif est normalement complété par un deuxième embrayage disposé radialement à l' intérieur de l' embrayage extérieur 2, l' ensemble formant un dispositif d' embrayage double. La puissance provenant du moteur du véhicule transite par un dispositif amortisseur de vibrations 3 dont seul l' organe secondaire 3a a été représenté sur la figure 1 aux fins de simplification. On notera que le dispositif amortisseur d' oscillation de torsion référencé 3 dans son ensemble peut être remplacé par un dispositif analogue, par exemple, comportant un double volant d' amortissement, voire même être supprimé. L' organe secondaire 3a comporte une portion cylindrique 4 qui porte sur sa périphérie radialement externe des cannelures 5 qui permettent la liaison avec des cannelures 6 correspondantes pratiquées sur une pièce cylindrique annulaire 7 qui est solidaire d'un flasque d' entraînement 8 et d'un carter de protection 9.As illustrated in FIG. 1, the clutch device is of the "double wet clutch" type. In Figure 1 which shows a partial axial sectional view of the clutch device 1, only the outer clutch 2 has been shown. It will be understood that the device is normally completed by a second clutch arranged radially inside the outer clutch 2, the assembly forming a double clutch device. The power from the vehicle engine passes through a vibration damping device 3 of which only the secondary member 3a has been shown in Figure 1 for the sake of simplification. Note that the torsion damping damping device referenced 3 as a whole can be replaced by a similar device, for example, having a double damping flywheel, or even be deleted. The secondary member 3a comprises a cylindrical portion 4 which carries on its radially outer periphery splines 5 which allow the connection with corresponding splines 6 made on an annular cylindrical piece 7 which is integral with a drive flange 8 and a protective casing 9.
L' embrayage extérieur 2 comprend une pluralité de disques ou lamelles 10 disposés radialement et côte à côte selon une direction axiale avec des écartements appropriés pour le logement de disques ou lamelles correspondantes 11. Le contact de frottement respectif entre les disques 10 et les disques 11 est capable d' assurer le serrage de l' embrayage 2 et la solidarisation de la cloche intérieure 12 de l' embrayage 2 avec la cloche extérieure 13 dudit embrayage. En effet, la cloche intérieure 12 présente une portion cylindrique 14 munie de rainures axiales espacées recevant des crans prévus sur l' alésage des disques 10. Ces crans peuvent être logés et maintenus dans lesdites rainures axiales en autorisant un déplacement axial des disques 10. De la même manière, la cloche extérieure 13 présente une jupe cylindrique 15 dirigée axialement depuis l' intérieur vers le dispositif amortisseur 3. Cette jupe cylindrique présente des rainures axiales espacées 15a à l' intérieur desquelles sont reçus des crans prévus à la périphérie des disques 11. Ces crans peuvent être logés et maintenus dans les rainures axiales 15a en autorisant un déplacement axial des disques 11. Du côté extérieur, c'est-à-dire sur la droite de la figure 1 , est également monté selon le même principe un plateau d' appui 16 qui présente des crans périphériques coopérant avec les rainures axiales 15a. L' actionnement de l' embrayage 2 par serrage les uns contre les autres des disques respectifs 10 et 11 est effectué par un piston 17 commandé hydrauliquement par des moyens non représentés sur la figure. Le piston 17 présente une portion radiale d' appui 17a qui vient exercer un effort de compression sur les disques 11 dont la surface est généralement lisse et sur les disques 10 dont la surface est généralement revêtue d'une garniture.The outer clutch 2 comprises a plurality of disks or strips 10 arranged radially and side by side in an axial direction with appropriate spacings for the housing of disks or corresponding plates 11. The respective friction contact between the disks 10 and the disks 11 is able to ensure the clamping of the clutch 2 and the fastening of the inner bell 12 of the clutch 2 with the outer bell 13 of said clutch. Indeed, the inner bell 12 has a cylindrical portion 14 provided with spaced axial grooves receiving notches provided on the bore of the discs 10. These notches can be accommodated and held in said axial grooves by allowing an axial displacement of the discs 10. the same way, the outer bell 13 has a cylindrical skirt 15 axially directed from the inside towards the damping device 3. This cylindrical skirt has spaced axial grooves 15a inside which are received notches provided on the periphery of the discs 11 These notches can be accommodated and held in the grooves 15a axial by allowing axial movement of the discs 11. On the outer side, that is to say on the right of Figure 1, is also mounted according to the same principle a support plate 16 which has peripheral notches cooperating with the axial grooves 15a. Actuation of the clutch 2 by clamping against each other respective disks 10 and 11 is effected by a piston 17 controlled hydraulically by means not shown in the figure. The piston 17 has a radial support portion 17a which exerts a compressive force on the discs 11 whose surface is generally smooth and on the discs 10 whose surface is generally coated with a liner.
Lorsque l'embrayage est serré, la cloche intérieure 12 est rendue solidaire de la cloche extérieure 13 et la puissance du moteur transite par l' embrayage 2 jusqu' à l' arbre de sortie schématisé en 18 sur lequel est fixée la cloche intérieure 12 par son manchon de fixationWhen the clutch is tightened, the inner bell 12 is made integral with the outer bell 13 and the power of the motor passes through the clutch 2 to the output shaft schematized at 18 on which is fixed the inner bell 12 by his fixing sleeve
12a.12a.
L' ensemble du dispositif d' embrayage double comprenant l' embrayage extérieur 2 et un embrayage intérieur non représenté, fonctionne en milieu humide, c' est-à-dire à l' intérieur d'un espace rempli d'huile. L' étanchéité est assurée au moyen d'un joint d' étanchéité 19 en contact de friction avec la pièce cylindrique 7. Le joint 19 est solidaire d'une tôle de fermeture 20 qui est liée au carter 21 logeant à la fois le dispositif d' embrayage 1 et un différentiel non représenté sur la figure. La liaison permettant la transmission de puissance entre le flasque d' entraînement 8 et la cloche extérieure 13 se fait par conjugaison de forme entre des dents 22 du flasque d'entraînement 8 et des parties bombées 23 de la surface externe de la jupe cylindrique 15.The assembly of the double clutch device comprising the outer clutch 2 and a not shown inner clutch operates in a humid environment, ie within an oil filled space. Sealing is ensured by means of a seal 19 in frictional contact with the cylindrical part 7. The seal 19 is integral with a closing plate 20 which is connected to the casing 21 housing both the device of FIG. clutch 1 and a differential not shown in the figure. The link allowing the transmission of power between the drive flange 8 and the outer bell 13 is done by means of a conjugation between the teeth 22 of the drive flange 8 and the curved portions 23 of the outer surface of the cylindrical skirt 15.
La figure 2 montre plus en détail la structure de ces éléments. Comme on peut le voir sur cette figure, le flasque d' entraînement 8 présente sur toute sa périphérie, des dents 22 constituées par des excroissances radiales 24 réparties équi-angulairement et laissant entre elles des évidements 25. Les extrémités des excroissances 24 sont repliées axialement en forme de languettes 26 dirigées vers la gauche sur les figures, c'est-à-dire depuis le dispositif amortisseur 3 vers la cloche extérieure 13. Les parties bombées 23 qui sont avantageusement réalisées par emboutissage de la matière de la jupe cylindrique 15 sont également disposées avec des écartements réguliers sur toute la périphérie de la jupe 15, avec le même écartement que les languettes 26. La jupe cylindrique 15 présente des évidements 27 en prolongation axiale des parties bombées 23. La jupe cylindrique 15 présente en outre des dents axiales 28 dont la concavité est dirigée vers l' extérieur et qui se trouvent entre les rainures 15a dont la concavité est dirigée vers l' intérieur. Ces dents 28 sont disposées entre les différentes parties bombées 23 et les évidements 27 et forment des saillies axiales qui peuvent pénétrer à l' intérieur des évidements 25 du flasque d' entraînement 8.Figure 2 shows in more detail the structure of these elements. As can be seen in this figure, the drive flange 8 has over its entire periphery, teeth 22 constituted by radial projections 24 distributed equi-angularly and leaving between them recesses 25. The ends of the protrusions 24 are folded axially in the form of tongues 26 directed towards the left in the figures, that is to say from the damping device 3 to the outer bell 13. The curved portions 23 which are advantageously made by stamping the material of the cylindrical skirt 15 are also arranged with regular spacings on the entire periphery of the skirt 15, with the same spacing as the tabs 26. The cylindrical skirt 15 has recesses 27 in axial extension of the curved portions 23. The cylindrical skirt 15 further has axial teeth 28 whose concavity is directed outwards and which are between the grooves 15a whose concavity is directed inwards. These teeth 28 are arranged between the various convex portions 23 and the recesses 27 and form axial projections which can penetrate inside the recesses 25 of the drive flange 8.
Lorsque le flasque d' entraînement 8 est monté sur la cloche extérieure 13 comme illustré sur la figure 1 , la surface interne des languettes 26 vient en contact de friction avec la surface extérieure des parties bombées 23. De plus, les dents radiales 24 viennent pénétrer à l'intérieur des évidements 27 tandis que les dents axiales 28 viennent pénétrer à l'intérieur des évidements 25.When the drive flange 8 is mounted on the outer bell 13 as illustrated in FIG. 1, the inner surface of the tongues 26 comes into frictional contact with the outer surface of the curved portions 23. In addition, the radial teeth 24 penetrate inside the recesses 27 while the axial teeth 28 penetrate inside the recesses 25.
De cette manière, on comprend que le flasque d' entraînement 8 est parfaitement solidarisé en rotation avec la cloche extérieure 13 par la coopération des différentes dents 24, 28 avec les évidements correspondants 25, 27 pratiqués sur ces deux pièces.In this way, it is understood that the drive flange 8 is perfectly secured in rotation with the outer bell 13 by the cooperation of the different teeth 24, 28 with the corresponding recesses 25, 27 made on these two parts.
Les parties bombées 23 assurent le centrage de l'ensemble. La surface interne des languettes repliées 26 est rectifiée au même titre que la surface externe des parties bombées 23 de façon à assurer un ajustement précis entre ces deux pièces.The bulged portions 23 ensure the centering of the assembly. The inner surface of the folded tabs 26 is ground to the same extent as the outer surface of the bulged portions 23 so as to ensure a precise fit between these two parts.
Un anneau radial fendu référencé 29 ( figure 1 ) peut être monté dans une gorge 30 pratiquée sur la surface intérieure des dents 28 de la jupe cylindrique 15 légèrement à l'extérieur des parties bombées 23. L' anneau radial 29 permet de maintenir le plateau d' appui 16 de l' embrayage 2. Un autre anneau d' arrêt, référencé 31 et visible sur la figure 2, assure le blocage axial contre tout déplacement potentiel du flasque d' entraînement 8. L' anneau d' arrêt 31 qui se présente avantageusement sous la forme d'un anneau fendu pour faciliter le montage, vient se loger dans une gorge 32 pratiquée dans la surface interne des dents 28 de la jupe cylindrique 15. Grâce à cette disposition, le flasque d' entraînement 8 et la cloche extérieure 13 sont montés avec un ajustement glissant de grande précision compte tenu de la rectification de surface effectuée comme indiqué précédemment. Cette rectification peut s' effectuer sur une faible épaisseur de l' ordre de quelques dixièmes de mm, en ne cassant les fibres de la cloche extérieure que de manière très localisée. Le relâchement des contraintes dans la cloche extérieure est ainsi minimisé et donc également la dégradation éventuelle de la tenue mécanique de la cloche extérieure. Le montage du flasque d'entraînement et sa liaison comme il vient d' être expliqué avec la cloche extérieure, a également pour avantage de limiter la déformation de la cloche extérieure en raison de la force centrifuge. Les contraintes sur la cloche extérieure de l' embrayage se trouvent donc limitées. De plus, l' ajustement glissant entre la cloche extérieure et le flasque d' entraînement permet un autocentrage de ces deux pièces à partir d'un régime de rotation suffisant.A split radial ring referenced 29 (Figure 1) can be mounted in a groove 30 formed on the inner surface of the teeth 28 of the cylindrical skirt 15 slightly outside the curved portions 23. The radial ring 29 keeps the tray a second locking ring, referenced 31 and visible in FIG. 2, provides axial locking against any potential displacement of the drive flange 8. The locking ring 31 which advantageously in the form of a split ring to facilitate assembly, is housed in a groove 32 formed in the inner surface of the teeth 28 of the cylindrical skirt 15. With this arrangement, the drive flange 8 and the outer bell 13 are mounted with a sliding adjustment of high accuracy given the surface grinding performed as indicated above. This grinding can be carried out on a small thickness of the order of a few tenths of a mm, by breaking the fibers of the outer bell only in a very localized manner. The relaxation of the stresses in the outer bell is thus minimized and therefore also the possible degradation of the mechanical strength of the outer bell. The mounting of the drive flange and its connection as just explained with the outer bell, also has the advantage of limiting the deformation of the outer bell due to the centrifugal force. The constraints on the outer bell of the clutch are therefore limited. In addition, the sliding fit between the outer bell and the drive flange allows self - centering of these two parts from a sufficient rotational speed.
La liaison entre le flasque d' entraînement et la cloche extérieure de l' embrayage est aisément démontable par simple retrait de l' anneau d' arrêt 31. Le remontage des pièces peut également être effectué sans difficulté après une éventuelle intervention de maintenance sur les éléments internes du dispositif d'embrayage. The connection between the drive flange and the outer bell of the clutch is easily removable by simply removing the stop ring 31. The reassembly of the parts can also be performed without difficulty after a maintenance intervention on the elements. internal clutch device.

Claims

REVENDICATIONS
1. Dispositif d'embrayage multiple à disques de friction en milieu humide, en particulier pour transmission de puissance dans un véhicule automobile, du type comprenant un flasque d' entraînement (8) transmettant le couple moteur, éventuellement par l'intermédiaire d'un amortisseur de vibrations (3), et une cloche extérieure ( 13) à l' intérieur de laquelle sont montés plusieurs disques de friction d'un embrayage extérieur (2), le flasque d' entraînement et la cloche extérieure étant liés entre eux par conjugaison de forme entre des évidements (27) d'une jupe cylindrique ( 15) de la cloche extérieure ( 13) et des dents axiales (24) du flasque d'entraînement, caractérisé par le fait que les dents du flasque d' entraînement présentent des extrémités repliées axialement en forme de languettes (26) capables d' entrer en contact avec des parties bombées (23) de la surface externe de la jupe cylindrique ( 15).1. Multiple clutch device with wet friction discs, in particular for power transmission in a motor vehicle, of the type comprising a driving flange (8) transmitting the motor torque, possibly via a vibration absorber (3), and an outer bell (13) inside which are mounted a plurality of friction discs of an outer clutch (2), the drive flange and the outer bell being interconnected by conjugation. form between recesses (27) of a cylindrical skirt (15) of the outer bell (13) and axial teeth (24) of the drive flange, characterized in that the teeth of the drive flange have axially tongue - shaped folded ends (26) capable of coming into contact with curved portions (23) of the outer surface of the cylindrical skirt (15).
2. Dispositif d' embrayage multiple selon la revendication 1 caractérisé par le fait que les parties bombées ont été obtenues par emboutissage de la jupe cylindrique.2. Multiple clutch device according to claim 1 characterized in that the curved portions were obtained by stamping the cylindrical skirt.
3. Dispositif d' embrayage multiple selon les revendications 1 ou 2 caractérisé par le fait qu'un anneau d' arrêt axial (31 ) du flasque d' entraînement est monté dans une gorge pratiquée dans la surface intérieure de la jupe cylindrique (15).3. Multiple clutch device according to claim 1 or 2, characterized in that an axial stop ring (31) of the drive flange is mounted in a groove in the inner surface of the cylindrical skirt (15). .
4. Dispositif d' embrayage multiple selon la revendication 3 caractérisé par le fait que l' anneau d' arrêt axial (31 ) du flasque d' entraînement est une pièce fendue radialement.4. Multiple clutch device according to claim 3 characterized in that the axial stop ring (31) of the drive flange is a radially split piece.
5. Dispositif d' embrayage multiple selon l'une des revendications précédentes, caractérisé par le fait qu'un anneau de butée axiale (29) d'un plateau d' appui ( 16) des disques de friction de l' embrayage extérieur est monté dans une gorge pratiquée dans la surface intérieure de la jupe cylindrique ( 15).5. Multiple clutch device according to one of the preceding claims, characterized in that an axial abutment ring (29) of a support plate (16) of the friction discs of the outer clutch is mounted. in a groove in the inner surface of the cylindrical skirt (15).
6. Dispositif d' embrayage multiple selon l'une des revendications précédentes, caractérisé par le fait que les surfaces de contact respectives des languettes et des parties bombées sont rectifiées pour un ajustement glissant axial précis. 6. Multiple clutch device according to one of the preceding claims, characterized in that the respective contact surfaces of the tongues and the curved portions are ground for precise axial sliding adjustment.
PCT/FR2006/050377 2005-05-23 2006-04-24 Multiple clutch device WO2006125932A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0505149A FR2885975B1 (en) 2005-05-23 2005-05-23 MULTIPLE CLUTCH DEVICE
FR0505149 2005-05-23

Publications (1)

Publication Number Publication Date
WO2006125932A1 true WO2006125932A1 (en) 2006-11-30

Family

ID=35509302

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/FR2006/050377 WO2006125932A1 (en) 2005-05-23 2006-04-24 Multiple clutch device

Country Status (2)

Country Link
FR (1) FR2885975B1 (en)
WO (1) WO2006125932A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106442157A (en) * 2016-12-07 2017-02-22 贵州黎阳航空动力有限公司 Subarea detection casing hydraulic strength testing device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016013539A1 (en) * 2016-11-12 2018-05-17 Borgwarner Inc. Rotary drive arrangement and multi-plate clutch device with such a rotary driving arrangement

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4944376A (en) * 1987-05-02 1990-07-31 Aisin-Warner Kabushiki Kaisha Brake band drum for planetary gear-type transmissions
US5267807A (en) * 1990-11-09 1993-12-07 Ford Motor Company Driveable connection between drum components for automatic transmission friction disc clutch
US5305943A (en) * 1992-02-20 1994-04-26 Koppy Corporation Splined assembly
EP1422430A1 (en) * 2002-11-19 2004-05-26 Volkswagen Aktiengesellschaft Motor vehicle transmission with multi-disc clutch

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4944376A (en) * 1987-05-02 1990-07-31 Aisin-Warner Kabushiki Kaisha Brake band drum for planetary gear-type transmissions
US5267807A (en) * 1990-11-09 1993-12-07 Ford Motor Company Driveable connection between drum components for automatic transmission friction disc clutch
US5305943A (en) * 1992-02-20 1994-04-26 Koppy Corporation Splined assembly
EP1422430A1 (en) * 2002-11-19 2004-05-26 Volkswagen Aktiengesellschaft Motor vehicle transmission with multi-disc clutch

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106442157A (en) * 2016-12-07 2017-02-22 贵州黎阳航空动力有限公司 Subarea detection casing hydraulic strength testing device

Also Published As

Publication number Publication date
FR2885975B1 (en) 2007-08-10
FR2885975A1 (en) 2006-11-24

Similar Documents

Publication Publication Date Title
EP2990678B1 (en) Clutch device for a motor vehicle
FR2706550A1 (en) Torque transmission device
FR2787843A1 (en) TORQUE TRANSMISSION DEVICE
FR2670856A1 (en) OSCILLATION DAMPING DEVICE.
FR2886996A1 (en) Motor vehicle multiple clutch mechanism has one friction disc with hub in two coaxial sections for quicker assembly
FR2688564A1 (en) Double damping flywheel, particularly for motor vehicles
FR2706962A1 (en)
FR2817934A1 (en) MULTIPLE DISC CLUTCH FOR A MOTOR VEHICLE
WO1995028576A1 (en) Reaction plate for friction clutch, in particular for motor vehicles
EP0859920B1 (en) Motor vehicle double damping flywheel, comprising improved means for friction damping of vibrations
FR2687749A1 (en) Torsion damper device, particularly double damping flywheel and clutch friction disc for motor vehicles
WO1996014521A1 (en) Torsional damper, particularly a driven plate assembly for a motor vehicle clutch
FR2748539A1 (en) HYDROKINETIC COUPLING APPARATUS WITH TAB DRIVE PART, PARTICULARLY FOR MOTOR VEHICLE
FR3081952A1 (en) ASSEMBLED DISC HOLDER AND WET CLUTCH MECHANISM INCLUDING THIS ASSEMBLED DISC HOLDER
WO2006125932A1 (en) Multiple clutch device
EP1595084B1 (en) Device comprising a centred clutch/clutch release module
FR2644538A1 (en) TORSIONAL DAMPER, ESPECIALLY DOUBLE DAMPER FLYWHEEL FOR MOTOR VEHICLE
WO2018104139A1 (en) Torsion damping device
WO2016184986A1 (en) Torsional damper for motor vehicle torque transmission device
FR2765937A1 (en) COMPACT DYNAMIC SHOCK ABSORBER ASSEMBLY AND STEERING WHEEL ASSEMBLY COMPRISING SUCH A DYNAMIC SHOCK ABSORBER ASSEMBLY
FR2728642A1 (en) Torsion damper, esp. for vehicle friction clutch
FR2663387A1 (en) Double damping flywheel, particularly for a motor vehicle
EP0833075B1 (en) Torsional damper with finger-like projections for transmission element, in particular vehicle friction clutch
EP3101309B1 (en) Clutch disc
WO2014207374A1 (en) Clutch device, in particular for a motor vehicle

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application
NENP Non-entry into the national phase

Ref country code: DE

WWW Wipo information: withdrawn in national office

Country of ref document: DE

NENP Non-entry into the national phase

Ref country code: RU

WWW Wipo information: withdrawn in national office

Country of ref document: RU

122 Ep: pct application non-entry in european phase

Ref document number: 06743834

Country of ref document: EP

Kind code of ref document: A1