WO1996035891A1 - Hydrokinetic coupling apparatus, particularly for a motor vehicle - Google Patents

Hydrokinetic coupling apparatus, particularly for a motor vehicle Download PDF

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Publication number
WO1996035891A1
WO1996035891A1 PCT/FR1996/000712 FR9600712W WO9635891A1 WO 1996035891 A1 WO1996035891 A1 WO 1996035891A1 FR 9600712 W FR9600712 W FR 9600712W WO 9635891 A1 WO9635891 A1 WO 9635891A1
Authority
WO
WIPO (PCT)
Prior art keywords
disc
piston
friction
grooves
wall
Prior art date
Application number
PCT/FR1996/000712
Other languages
French (fr)
Inventor
Benoît HUE
Denis Menard
Original Assignee
Valeo
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 Valeo filed Critical Valeo
Priority to DE19680460T priority Critical patent/DE19680460T1/en
Priority to KR1019970700131A priority patent/KR100494959B1/en
Priority to JP8533838A priority patent/JPH10503002A/en
Publication of WO1996035891A1 publication Critical patent/WO1996035891A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • 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
    • 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
    • F16H2045/0289—Details of friction surfaces of the lock-up clutch

Definitions

  • Hydrokinetic coupling device in particular for a motor vehicle.
  • the present invention relates to hydrokinetic coupling devices, in particular for a motor vehicle, as described for example in documents O-A-94/07058 and O-A-93/13339.
  • the device has a generally transverse orientation wall capable of being linked in rotation to a drive shaft and carrying centrally attached a guide ring.
  • a piston is mounted to move axially in leaktight fashion along the guide ring and defines, with the transverse wall and the guide ring, a variable volume chamber delimited externally by a disc and friction linings adapted to be clamped respectively between the piston. and the disc and between the disc and the transverse wall.
  • Each friction lining is integral with one of the disc-piston-transverse wall elements respectively, between which it is intended to be clamped.
  • Each groove is connected by a plurality of radial passages respectively with the internal periphery and the external periphery of the disc.
  • Radial channels also connect the two grooves together.
  • the pressure which reigns in the housing of the hydrokinetic coupling device is higher than that prevailing in the variable volume chamber and the fluid circulates towards the interior of the variable volume chamber. ie from the outer periphery to the inner periphery of the friction linings. This is not entirely satisfactory, because it reduces the torque transmitted to the disc coupled to the turbine wheel and therefore to the driven shaft. In addition, the circulation of the fluid inward is not as rapid as desired.
  • the object of the present invention is to overcome this drawback in a simple and economical manner. It is therefore an object of the present invention to cool the external periphery of the variable volume chamber while increasing the transmitted torque and the fluid flow rate.
  • a coupling device of the above-mentioned type is characterized in that said grooves are generally in the form of an arc of a circle off-center with respect to the center of the disc and generally extend in a portion of a spiral of the external periphery at the internal periphery of each friction lining being wound in a spiral according to the direction of rotation of the disc and in that the cooling grooves are distributed alternately from one friction lining to the other friction lining, one lining friction ending where a groove of the other friction pad begins.
  • the resulting flow rate in the grooves is proportional to the supply pressure and to the speed of rotation, in particular to the differential speed of rotation between the disc and the piston - transverse wall assembly.
  • variable volume chamber The fluid flow towards the interior of the variable volume chamber increases as a function of the sliding power. So the more you slide, the more you increase the fluid flow.
  • said friction linings are well cooled. No point of the fittings being far from a cooling groove or groove.
  • the number of inlets and outlets for the fluid is increased while leaving a large area for the friction linings.
  • the spiral grooves according to the invention widen in the direction of the external periphery of the friction linings.
  • FIG. 1 is a half-view in partial axial section of a hydrokinetic coupling device according to the invention
  • - Figure 2 is with local cutaway a view along arrow 2 of Figure 1;
  • FIG. 3 is a view along line 3-3 of Figure 2
  • - - Figure 4 is a view of the dorsal face of the disc fitted with friction linings according to the invention
  • FIG. 5 is a sectional view along line 5-5 of Figure 4;
  • FIG. 6 is a view of the front face of the disc fitted with friction linings according to the invention.
  • a hydrokinetic coupling device comprises, arranged in the same sealed housing filled with oil and forming crankcase, torque converter and locking clutch 1.
  • the casing forms a driving element and is suitable for being linked in rotation to a shaft leading to the crankshaft of the internal combustion engine in the case of an application to a motor vehicle.
  • This annular-shaped casing is formed by two half-shells facing each other and fixed in a sealed manner at their external periphery, usually by welding.
  • the first half-shell 2,3 is suitable for being linked in rotation to the driving shaft and comprises a generally annular wall 2 of transverse orientation extended at its external periphery by a cylindrical wall 3 generally of axial orientation.
  • the second half-shell is shaped so as to define an impeller wheel with vanes integral with the internal face of this half-shell.
  • These blades face the blades of a turbine wheel 4 fixed by riveting or welding to a hub web in one piece with a hub 5 internally fluted for its rotational connection to a driven shaft, namely the shaft d input of the gearbox in the case of an application to a motor vehicle.
  • This shaft is hollowed out internally to form a channel allowing the oil to access a guide ring 6 located axially between the hub 5 and the transverse wall 2.
  • this ring 6 is centrally provided with a centering nose 7 projecting axially and is fixed centrally by welding, of which the cord is seen at 61, to the wall 2 provided for this purpose centrally with a sleeve 60 of axial orientation facing outwards into which the centering nose 7 enters.
  • the ring 6 is also provided a flange 8 of transverse orientation. The ring 6 is thus shouldered and is in contact by its flange 8, after its fixing by welding, with the internal face of the wall 2 turned towards the hub 5.
  • a piston 9 is mounted to slide axially along the annular external periphery of the flange 8, provided with a groove for mounting an annular seal 29.
  • the piston 9 has centrally an axially oriented sleeve turned towards the wall 2 for its sliding along the flange 8.
  • the piston 9 delimits with the ring 6, the wall 2 and a disc 10, bearing fixing, for example by gluing or brazing, on each of its faces friction linings 11 , 111, a variable volume chamber 30 supplied by the ring 6 having for this purpose unreferenced bores supplied by the channel of the aforementioned driven shaft.
  • the holes affect the flange 8 and have inclined portions opening into a blind hole, which the ring 6 has centrally.
  • the disc 10 is located at the outer periphery of the piston 9 and has at its outer periphery, radially beyond the piston 9, square-shaped tabs 28 with an axial orientation part each penetrating into a notch, which has a guide washer
  • the notches are made in a transverse portion 14 of the guide washer 12.
  • This transverse portion 14 is extended by an annular portion 15 of axial orientation serving to radially maintain outside coil springs 16, retained internally by an annular holding portion 17 of a veil 18 extended inward by a flange 19 fixed by riveting to the veil of the hub 5 at the same time as the turbine wheel 4 provided for this purpose with lugs (not referenced) at its internal periphery.
  • the fixing can be carried out by welding.
  • the flange 19 has a series of holes (not referenced) for circulation of the oil between the piston 9 and the wheel 4.
  • the veil 18 has support portions 20 for the circumferential ends of the springs 16. These portions 20 are formed by means of support punctures, of sinuous shape, extending from the internal periphery to the external periphery of the portion holding 17 of the web 18. This portion 17 is in the form of a half-shell and is offset axially relative to the portions 14, 15 of the guide washer 12 also forming a half-shell.
  • the guide washer 12 is provided at its axial portion 15 with inward material deformations 21 for support of the ends of the springs 16.
  • the portion 14 also has lugs 22 for support of the ends of the springs 16.
  • the locking clutch l comprises a torsion damper 23 located mainly between the turbine wheel 4 and the wall 2 at the external periphery of the first shell, with an inlet part 12, arranged radially above the piston 9 and the linings 11,111 being constituted by the guide washer 12 in the form of a half-shell 14,15, coil springs 16 and an outlet part constituted by the web 18 also in the form of a half-shell at its periphery external.
  • the outlet part 18 is linked in rotation to the turbine wheel 4, more precisely to the hub 5 thereof, while the inlet part 12 is linked in rotation to the disc 10, projecting radially with respect to the piston 9.
  • the inlet part 12 is therefore disengageably connected via the disk 10 and the linings 11,111 to the driving shaft, said disk 10 with its linings being suitable for being disengageably clamped between the piston 9 and the wall 2 forming against -piston.
  • Disc 10 is therefore coupled elastically to the hub 5 and to the wheel 4.
  • the locking clutch 1 allows, to avoid the phenomena of sliding between the turbine and impeller wheels, a direct connection of the driven shaft with the driving shaft and this by tightening the friction linings 11,111 and the disc 10 between the piston 9 and the counter-piston 2 with direct drive of the tree driven by the shell 1.
  • the piston 9 is linked in rotation to the wall 2 of the first shell by tangential elastic tongues 40 distributed regularly circumferentially, here four sets of tongues (FIG. 3).
  • tongues 40 allow axial movement of the piston.
  • the tongues are coupled to the transverse wall 2 by means of an annular piece 44, here metallic, secured to the wall 2 here by rivets 45 which have come here in one piece from it, for example by extrusion .
  • the annular part 44 has from place to place tabs 48 offset axially with respect to its main part for fixing to the wall 2.
  • the tongues 40 formed here from a stack of two tongues, are secured to the one of their ends by rivets 43 to the legs 48.
  • the rivets may consist of screws or bolts.
  • fixing means 41, 42 are used, which, while being capable of passing generally through the tongues 40 and the piston 9, have two parts, know, a first part 41, which, in advance, is subject to the tongues 40, on the side thereof opposite the piston 9, and a second part 42, which, in order to come into engagement with the first part 41, does not require intervention as on the side of the piston 9.
  • the tongues 40 extend in the volume which extends radially between the friction linings 11, 111 and the axis of the assembly, that is to say in the chamber 30.
  • tongues 40 extend axially between the wall 2 and the piston 9 in a region where the wall 2 projects axially in the direction opposite to the turbine wheel so that axially, at the flange 8 of the ring 6, a small space requirement axial exists between the piston 9 and the wall 2.
  • the fixing in two parts 41,42 is of the crimped bolt rod type.
  • the first part 41 comprises a rod with a support head.
  • the rod plays through the bore of the piston 9 and has a first smooth section and a first notched section.
  • This part 41 is fixed by force fitting or alternatively by knurling or gluing to the tongues 40.
  • the support head of the rods 41 is mounted in the chamber 30.
  • the second part 42 consists of a crimping ring, which comprises, side of the piston, a larger diameter base to prevent its creep in the bore of the piston.
  • the ring 42 is therefore mounted outside the chamber 30.
  • the ring 42 is crushed so that it comes into engagement with the notched section of the rod 41.
  • rivets of the "POP" type can be used.
  • the first part may consist of a nut or a screw fixed for example by gluing to the tongues 40 and the second part may consist of a screw or a nut.
  • stop means 50 are installed in the chamber 30 in particular in order to limit the bending of the tongues 40 and to spare them.
  • These abutment means 50 are formed by means of the part 44 used for driving and fixing the tongues 40 to the wall 2. More precisely, the tangential tongues 40 are here extended circumferentially au- beyond the fixing in two parts 41, 42 of the tongues 40 to the piston 9.
  • each of the extensions 47 is adapted to cooperate with a stop 46 facing the wall 2 ( Figures 2 and 3).
  • This stop 46 belongs to the means 50 and extends locally parallel to the wall 2. It is formed by stamping in favor of the tabs 48 offset axially relative to the main part of the annular part 44.
  • a lug 48 therefore has one end for fixing a rivet 43 and a stop 46.
  • the piece 44 is formed overall in section of the brackets (or claws) with a part of axial orientation surrounding the free end of the tongues 40 (the extension 47), extended by a part d transverse orientation 46 forming the abutment means 50 suitable for cooperating with the face of the tongues 40 facing the piston 9, that is to say with the dorsal face of the tongues 40.
  • the stops 46 therefore limit the displacement of the piston 9 in the direction opposite to the transverse wall 2.
  • the stop means 50 may consist of an added ring, for example by riveting or snap-fastening, on the guide ring 6 while being in contact with the dorsal face of the latter.
  • This ring then projects relative to the external periphery of the flange 8 and is adapted to cooperate with the internal periphery of the piston 9 to limit the displacement of the latter in the direction opposite to the wall 2.
  • stop means 50 it is possible to reduce the spacing which exists between the piston 9 and the lining 11 when the locking clutch is disengaged or released. This makes it possible to reduce the response times and is favorable to the creation of a controlled slip described below.
  • the piston 9 delimits two chambers, namely the chamber 30 with variable volume and a main chamber situated on the side of the dorsal face of the piston 9 turned away from the wall 2.
  • variable volume chamber 30 By varying the pressure in the variable volume chamber 30, it is possible to achieve controlled sliding of the friction linings 11,111 relative to the piston 9 and to the wall 2 respectively forming a counter-piston.
  • This controlled sliding allows in particular to slide or slip the friction linings 11,111 and therefore the disc 10 for certain engine speeds in order to better filter vibrations.
  • a relative movement therefore occurs between the disc 10 fitted with the linings 11,111 and the piston 9 - transverse wall 2 assembly.
  • the oil therefore heats up beyond the variable-volume chamber 30 close to the latter.
  • piston 9 and the wall 2 have transverse portions at the external periphery of the chamber 30 in order to provide plane friction faces (of transverse orientation) to the friction linings 11,111.
  • the pressure prevailing in the main part of the housing of the hydrokinetic coupling device is greater than that prevailing in the variable volume chamber 30.
  • the invention proposes to create in the friction linings 11,111 grooves 80,180 generally extending in a portion of a spiral from the external periphery to the internal periphery of each friction lining 11,111 by being wound in a spiral according to the direction of rotation ( Figure 4) of the disc opposite to that of the motor F to achieve a scoop effect.
  • four grooves or grooves 80,180 are provided by friction lining 11,111.
  • These grooves are regularly distributed circumferentially as best seen in Figures 4 and 6. They are generally, according to a characteristic of the invention, in the form of an arc of a circle offset from the center of the disc 10 and are wound in practice in a spiral according to a portion of a spiral.
  • these grooves can have a greater or lesser length. Note the fact that the grooves extend in a spiral portion, increases the number of inlets and outlets for the fluid passing through the grooves while leaving a large area for the linings.
  • the grooves preferably widen in the direction of the external periphery of the friction linings 11,111. They preferably have a width greater than their depth. They are wider at their internal and external peripheries to facilitate the circulation of the fluid (here oil) and to collect and evacuate the maximum of fluid.
  • the linings are not chipped.
  • the fixing of the friction linings on the disc 10 is advantageous because, thanks to the tabs 28, the grooves can be easily oriented relative to the direction of rotation of the disc identified by the arrow F in FIGS. 4 and 6.
  • connection in rotation of the piston 9 with the first half-shell 2,3 can be achieved by means of the piston 9 having at its internal periphery grooves suitable for meshing with complementary grooves, which has the ring 6 at its periphery. internal, that is to say at the external periphery of its flange.
  • the rotational connection can also be produced as described in document WO-A-93/13339, that is to say a connection involving a splined hub carried by the piston and a fluted disc internally worn which is secured by the wall 2.
  • the grooved disc offers a friction face to the lining 111 so that said linings are suitable for being clamped directly or indirectly, for example with the interposition of a disc, a plate, coating etc., between the piston 9 and the transverse wall 2.
  • the friction linings 11,111 instead of being secured by bonding or brazing the disc 10, can be secured respectively to the piston 9 or to the wall 2 and this for example by bonding or brazing so that each friction lining is secured to one of the piston and transverse wall elements respectively, between which it is intended to be clamped.
  • the grooves 180,80 can therefore affect the faces of the friction linings 111,11 facing the disc 10.
  • connection 13 can be inverted, the disc 10 then having mortises in which pins of the guide washer 12 engage.
  • the disc 10 can be coupled by a link of the tenon-mortise type to a crown attached to the turbine wheel 4. In this case the disc 10 is rigidly coupled to the turbine wheel 4.
  • cooling grooves 80,180 depends on the applications, in particular on the external diameter of the friction linings 11,111.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Braking Arrangements (AREA)

Abstract

A hydrokinetic coupling device has a generally transversally extending wall (2) on which is centrally mounted a guide ring (6), wherein a piston (9) is axially displaceable along the guide ring (6) and defines therewith and with the transversal wall (2) a variable volume chamber (30) outwardly defined by a disc (10) and by friction seals (11, 111) arranged to be clamped between the piston (9) and the disc (10) and between the disc (10) and the transversal wall (2) respectively, each friction seal (11, 111) having at least one so-called cooling groove (80, 180) and the one or more grooves (80, 180) extending from the outer periphery to the inner periphery of each fiction seal (11, 111) in a spiral following the direction of rotation of the disc (10) and being alternately distributed from one friction seal to the other. The invention is useful for motor vehicles.

Description

Appareil d'accouplement hydrocinétique, notamment pour véhicule automobile. Hydrokinetic coupling device, in particular for a motor vehicle.
La présente invention concerne les appareils d'accouplement hydrocinétique, notamment pour véhicule automobile, tel que décrit par exemple dans les documents O-A-94/07058 et O-A-93/13339.The present invention relates to hydrokinetic coupling devices, in particular for a motor vehicle, as described for example in documents O-A-94/07058 and O-A-93/13339.
Dans ce document l'appareil comporte une paroi globalement d'orientation transversale propre à être liée en rotation à un arbre menant et portant à fixation centralement une bague de guidage.In this document the device has a generally transverse orientation wall capable of being linked in rotation to a drive shaft and carrying centrally attached a guide ring.
Un piston est monté mobile axialement de manière étanche le long de la bague de guidage et définit avec la paroi transversale et la bague de guidage une chambre à volume variable délimitée extérieurement par un disque et des garnitures de frottement adaptées à être serrées respectivement entre le piston et le disque et entre le disque et la paroi transversale.A piston is mounted to move axially in leaktight fashion along the guide ring and defines, with the transverse wall and the guide ring, a variable volume chamber delimited externally by a disc and friction linings adapted to be clamped respectively between the piston. and the disc and between the disc and the transverse wall.
Chaque garniture de frottement est solidaire de l'un des éléments disque respectivement piston - paroi transversale entre lesquels elle est destinée à être serrée.Each friction lining is integral with one of the disc-piston-transverse wall elements respectively, between which it is intended to be clamped.
Comme décrit dans le document WO-A-93/13339 en contrôlant la pression dans la chambre à volume variable, on peut contrôler la pression différentielle s 'exerçant sur le piston sachant que deux chambres s'étendent de part et d'autre dudit piston.As described in document WO-A-93/13339, by controlling the pressure in the variable-volume chamber, it is possible to control the differential pressure exerted on the piston, knowing that two chambers extend on either side of said piston .
Cela permet de réaliser un glissement contrôlé par l'intermédiaire des garnitures de frottement entre le disque et l'ensemble piston - paroi transversale formant contre-piston. On peut faire glisser ou patiner le disque pour certains régimes du moteur du véhicule afin de mieux filtrer les vibrations. Ainsi un mouvement relatif se produit entre le disque et l'ensemble piston - paroi transversale.This allows a controlled sliding to be achieved by means of the friction linings between the disc and the piston-transverse wall assembly forming a counter-piston. You can slide or skate the disc for certain engine speeds of the vehicle to better filter vibrations. Thus a relative movement occurs between the disc and the piston - transverse wall assembly.
Ce glissement conduit à un échauffement au niveau du disque c'est-à-dire à la périphérie externe de la chambre à volume variable. L'huile de l'appareil d'accouplement hydrocinétique s'échauffe donc à ce niveau à l'extérieur de la chambre à volume variable. Afin de réduire cet échauffement, on a prévu dans le document WO-A-93/13339 de doter chaque garniture de frottement de deux rainures annulaires.This sliding leads to overheating at the level of the disc, that is to say at the outer periphery of the variable volume chamber. The oil of the hydrokinetic coupling device therefore heats up at this level outside the variable volume chamber. In order to reduce this overheating, provision has been made in document WO-A-93/13339 to provide each friction lining with two annular grooves.
Chaque rainure est reliée par une pluralité de passages radiaux respectivement avec la périphérie interne et la périphérie externe du disque.Each groove is connected by a plurality of radial passages respectively with the internal periphery and the external periphery of the disc.
Des canaux radiaux relient également les deux rainures entre elles.Radial channels also connect the two grooves together.
Ainsi en période de glissement contrôlé, la pression qui règne dans le boîtier de l'appareil d'accouplement hydrocinétique est supérieure à celle régnant dans la chambre à volume variable et le fluide circule vers l'intérieur de la chambre à volume variable c'est-à-dire de la périphérie externe à la périphérie interne des garnitures de frottement. Ceci n'est pas entièrement satisfaisant, car cela diminue le couple transmis au disque accouplé à la roue de turbine et donc à l'arbre mené. En outre la circulation du fluide vers l'intérieur n'est pas aussi rapide que souhaité.Thus, during a period of controlled sliding, the pressure which reigns in the housing of the hydrokinetic coupling device is higher than that prevailing in the variable volume chamber and the fluid circulates towards the interior of the variable volume chamber. ie from the outer periphery to the inner periphery of the friction linings. This is not entirely satisfactory, because it reduces the torque transmitted to the disc coupled to the turbine wheel and therefore to the driven shaft. In addition, the circulation of the fluid inward is not as rapid as desired.
La présente invention a pour objet de pallier, de manière simple et économique cet inconvénient. C'est donc un but de la présente invention de refroidir la périphérie externe de la chambre à volume variable tout en augmentant le couple transmis et le débit de fluide.The object of the present invention is to overcome this drawback in a simple and economical manner. It is therefore an object of the present invention to cool the external periphery of the variable volume chamber while increasing the transmitted torque and the fluid flow rate.
Suivant l'invention un appareil d'accouplement du type sus-indiqué est caractérisé en ce que lesdites rainures sont globalement en forme d'arc de cercle décentré par rapport au centre du disque et s'étendent globalement en portion de spirale de la périphérie externe à la périphérie interne de chaque garniture de frottement en étant enroulées en spirale selon le sens de rotation du disque et en ce que les rainures de refroidissement sont réparties de manière alternée d'une garniture de frottement à l'autre garniture de frottement, une garniture de frottement se terminant là où commence une rainure de l'autre garniture de frottement. Grâce à l'invention on obtient une circulation rapide de fluide du type centripète avec un effet de pompage et un couple transmis au disque plus important puisque l'huile à plus de mal à ressortir de manière centrifuge lorsque l'embrayage de verrouillage est serré. En outre avec une surface de rainure moindre, on peut obtenir une bonne circulation de fluide.According to the invention a coupling device of the above-mentioned type is characterized in that said grooves are generally in the form of an arc of a circle off-center with respect to the center of the disc and generally extend in a portion of a spiral of the external periphery at the internal periphery of each friction lining being wound in a spiral according to the direction of rotation of the disc and in that the cooling grooves are distributed alternately from one friction lining to the other friction lining, one lining friction ending where a groove of the other friction pad begins. Thanks to the invention, a rapid circulation of fluid of the centripetal type is obtained with a pumping effect and a greater torque transmitted to the disc since the oil has more difficulty in coming out centrifugally when the clutch of lock is tight. In addition, with a smaller groove area, good fluid circulation can be obtained.
Ainsi les garnitures de frottement sont bien refroidies et les rainures créent un effet d'entraînement du fluide par cisaillement visqueux.Thus the friction linings are well cooled and the grooves create a fluid entrainment effect by viscous shearing.
Ainsi grâce aux rainures, on vient puiser de l'huile chaude à la périphérie externe du piston, au-delà des garnitures, pour la transférer et la refroidir à l'intérieur de la chambre à volume variable plus froide. On notera que le débit résultant dans les rainures est proportionnel à la pression d'alimentation et à la vitesse de rotation, notamment à la vitesse de rotation différentielle entre le disque et l'ensemble piston - paroi transversale.Thus, thanks to the grooves, hot oil is drawn from the external periphery of the piston, beyond the linings, to transfer it and cool it inside the cooler variable-volume chamber. It will be noted that the resulting flow rate in the grooves is proportional to the supply pressure and to the speed of rotation, in particular to the differential speed of rotation between the disc and the piston - transverse wall assembly.
Le débit de fluide vers l'intérieur de la chambre à volume variable augmente en fonction de la puissance de glissement. Ainsi plus on glisse, plus on augmente le débit de fluide.The fluid flow towards the interior of the variable volume chamber increases as a function of the sliding power. So the more you slide, the more you increase the fluid flow.
D'une manière générale lesdites garnitures de frottement sont bien refroidies. Aucun point des garnitures n'étant loin d'une rainure ou gorge de refroidissement. En outre grâce à l'alternance des rainures d'une garniture de frottement à l'autre, on augmente le nombre des entrées et des sorties pour le fluide tout en laissant une surface importante pour les garnitures de frottement. De préférence les rainures en spirale selon l'invention s'évasent en direction de la périphérie externe des garnitures de frottement.In general, said friction linings are well cooled. No point of the fittings being far from a cooling groove or groove. In addition, thanks to the alternation of the grooves from one friction lining to another, the number of inlets and outlets for the fluid is increased while leaving a large area for the friction linings. Preferably the spiral grooves according to the invention widen in the direction of the external periphery of the friction linings.
Ainsi on obtient un meilleur effet d'entraînement du fluide par cisaillement visqueux. La description qui va suivre illustre l'invention en regard des dessins annexés dans lesquels : la figure 1 est une demi-vue en coupe axiale partielle d'un appareil d'accouplement hydrocinétique selon l'invention ; - la figure 2 est avec arrachement local une vue selon la flèche 2 de la figure 1 ;Thus, a better entrainment effect of the fluid is obtained by viscous shearing. The description which follows illustrates the invention with reference to the appended drawings in which: FIG. 1 is a half-view in partial axial section of a hydrokinetic coupling device according to the invention; - Figure 2 is with local cutaway a view along arrow 2 of Figure 1;
- la figure 3 est une vue selon la ligne 3-3 de la figure 2 ,- - la figure 4 est une vue de la face dorsale du disque équipé des garnitures de frottement selon 1'invention ;- Figure 3 is a view along line 3-3 of Figure 2, - - Figure 4 is a view of the dorsal face of the disc fitted with friction linings according to the invention;
- la figure 5 est une vue en coupe selon la ligne 5-5 de la figure 4 ;- Figure 5 is a sectional view along line 5-5 of Figure 4;
- la figure 6 est une vue de la face frontale du disque équipé des garnitures de frottement selon l'invention.- Figure 6 is a view of the front face of the disc fitted with friction linings according to the invention.
Ainsi qu'on le sait, comme décrit par exemple dans le document O-A-94/07058, auquel on pourra se reporter pour plus de précision, un appareil d'accouplement hydrocinétique comporte, agencé dans un même boîtier étanche rempli d'huile et formant carter, un convertisseur de couple et un embrayage de verrouillage 1.As is known, as described for example in document OA-94/07058, to which reference may be made for more precision, a hydrokinetic coupling device comprises, arranged in the same sealed housing filled with oil and forming crankcase, torque converter and locking clutch 1.
Le carter forme un élément menant et est propre à être lié en rotation à un arbre menant à savoir le vilebrequin du moteur à combustion interne dans le cas d'une application à un véhicule automobile.The casing forms a driving element and is suitable for being linked in rotation to a shaft leading to the crankshaft of the internal combustion engine in the case of an application to a motor vehicle.
Ce carter, de forme annulaire, est formé de deux demi- coquilles se faisant face et fixées de manière étanche à leur périphérie externe usuellement par soudage.This annular-shaped casing is formed by two half-shells facing each other and fixed in a sealed manner at their external periphery, usually by welding.
La première demi-coquille 2,3 est propre à être liée en rotation à l'arbre menant et comporte une paroi 2 annulaire globalement d'orientation transversale prolongée à sa périphérie externe par une paroi 3 cylindrique globalement d'orientation axiale.The first half-shell 2,3 is suitable for being linked in rotation to the driving shaft and comprises a generally annular wall 2 of transverse orientation extended at its external periphery by a cylindrical wall 3 generally of axial orientation.
La deuxième demi-coquille, non représentée par simplicité ainsi que la roue de réaction du convertisseur, est conformée de façon à définir une roue d'impulseur à aubes solidaires de la face interne de cette demi-coquille. Ces aubes font face aux aubes d'une roue de turbine 4 fixée par rivetage ou soudage à un voile de moyeu d'un seul tenant avec un moyeu 5 cannelé intérieurement pour sa liaison en rotation à un arbre mené, à savoir l'arbre d'entrée de la boîte de vitesses dans le cas d'une application à un véhicule automobile. Cet arbre est creusé intérieurement pour formation d'un canal permettant à l'huile d'accéder à une bague de guidage 6 implantée axialement entre le moyeu 5 et la paroi transversale 2.The second half-shell, not shown for simplicity as well as the reaction wheel of the converter, is shaped so as to define an impeller wheel with vanes integral with the internal face of this half-shell. These blades face the blades of a turbine wheel 4 fixed by riveting or welding to a hub web in one piece with a hub 5 internally fluted for its rotational connection to a driven shaft, namely the shaft d input of the gearbox in the case of an application to a motor vehicle. This shaft is hollowed out internally to form a channel allowing the oil to access a guide ring 6 located axially between the hub 5 and the transverse wall 2.
Plus précisément, cette bague 6 est centralement dotée d'un nez de centrage 7 saillant axialement et est fixée centralement par soudage, dont on voit en 61 le cordon, à la paroi 2 dotée à cet effet centralement d'un manchon 60 d'orientation axiale tourné vers l'extérieur dans lequel pénètre le nez de centrage 7. La bague 6 est dotée également d'une collerette 8 d'orientation transversale. La bague 6 est ainsi épaulée et est en contact par sa collerette 8, après sa fixation par soudage, avec la face interne de la paroi 2 tournée vers le moyeu 5.More specifically, this ring 6 is centrally provided with a centering nose 7 projecting axially and is fixed centrally by welding, of which the cord is seen at 61, to the wall 2 provided for this purpose centrally with a sleeve 60 of axial orientation facing outwards into which the centering nose 7 enters. The ring 6 is also provided a flange 8 of transverse orientation. The ring 6 is thus shouldered and is in contact by its flange 8, after its fixing by welding, with the internal face of the wall 2 turned towards the hub 5.
Un piston 9 est monté coulissant axialement le long de la périphérie externe annulaire de la collerette 8, pourvue d'une rainure pour montage d'un joint annulaire d'étanchéité 29. Le piston 9 présente centralement un manchon d'orientation axiale tourné vers la paroi 2 pour son coulissement le long de la collerette 8. Le piston 9 délimite avec la bague 6, la paroi 2 et un disque 10, portant à fixation, par exemple par collage ou brasage, sur chacune de ses faces des garnitures de frottement 11, 111, une chambre 30 à volume variable alimentée par la bague 6 présentant à cet effet des perçages non référencés alimentés par le canal de l'arbre mené précité. Ici les perçages affectent la collerette 8 et comportent des portions inclinées débouchant dans un trou borgne, que présente centralement la bague 6. Le disque 10 est implanté à la périphérie externe du piston 9 et présente à sa périphérie externe, radialement au-delà du piston 9, des pattes en forme d'équerre 28 avec une partie d'orientation axiale pénétrant chacune dans une encoche, que présente une rondelle de guidageA piston 9 is mounted to slide axially along the annular external periphery of the flange 8, provided with a groove for mounting an annular seal 29. The piston 9 has centrally an axially oriented sleeve turned towards the wall 2 for its sliding along the flange 8. The piston 9 delimits with the ring 6, the wall 2 and a disc 10, bearing fixing, for example by gluing or brazing, on each of its faces friction linings 11 , 111, a variable volume chamber 30 supplied by the ring 6 having for this purpose unreferenced bores supplied by the channel of the aforementioned driven shaft. Here the holes affect the flange 8 and have inclined portions opening into a blind hole, which the ring 6 has centrally. The disc 10 is located at the outer periphery of the piston 9 and has at its outer periphery, radially beyond the piston 9, square-shaped tabs 28 with an axial orientation part each penetrating into a notch, which has a guide washer
12 à sa périphérie interne, et une partie d'orientation radiale de raccordement à la partie principale du disque 10. Ce disque 10 est ainsi lié en rotation, avec mobilité axiale, à la rondelle de guidage 12 par une liaison du type tenons-mortaises12 at its internal periphery, and a radial orientation part for connection to the main part of the disc 10. This disc 10 is thus linked in rotation, with axial mobility, to the guide washer 12 by a connection of the tenon-mortise type
13 à pattes et encoches.13 with legs and notches.
Les encoches sont réalisées dans une portion transversale 14 de la rondelle de guidage 12. Cette portion transversale 14 est prolongée par une portion annulaire 15 d'orientation axiale servant à maintenir radialement extérieurement des ressorts à boudin 16, retenus intérieurement par une portion annulaire de maintien 17 d'un voile 18 prolongé vers l'intérieur par un flasque 19 fixé par rivetage au voile du moyeu 5 en même temps que la roue de turbine 4 dotée à cet effet de pattes (non référencées) à sa périphérie interne.The notches are made in a transverse portion 14 of the guide washer 12. This transverse portion 14 is extended by an annular portion 15 of axial orientation serving to radially maintain outside coil springs 16, retained internally by an annular holding portion 17 of a veil 18 extended inward by a flange 19 fixed by riveting to the veil of the hub 5 at the same time as the turbine wheel 4 provided for this purpose with lugs (not referenced) at its internal periphery.
En variante la fixation peut être réalisée par soudage. Le flasque 19 présente une série de trous (non référencés) pour circulation de l'huile entre le piston 9 et la roue 4.As a variant, the fixing can be carried out by welding. The flange 19 has a series of holes (not referenced) for circulation of the oil between the piston 9 and the wheel 4.
Le voile 18 présente des portions d'appui 20 pour les extrémités circonférentielles des ressorts 16. Ces portions 20 sont formées à la faveur de crevés d'appui, de forme sinueuse, s'étendant de la périphérie interne à la périphérie externe de la portion de maintien 17 du voile 18. Cette portion 17 est en forme de demi-coquille et est décalée axialement par rapport aux portions 14,15 de la rondelle de guidage 12 formant également une demi-coquille. La rondelle de guidage 12 est dotée au niveau de sa portion axiale 15 de déformations de matière vers l'intérieur 21 pour appui des extrémités des ressorts 16. La portion 14 présente également des pattes 22 pour appui des extrémités des ressorts 16. Pour plus de précision on se reportera au document O-A-94/1047058 notamment aux figures 24 à 28 de celui-ci. On notera, à l'exception du joint 29 et des garnituresThe veil 18 has support portions 20 for the circumferential ends of the springs 16. These portions 20 are formed by means of support punctures, of sinuous shape, extending from the internal periphery to the external periphery of the portion holding 17 of the web 18. This portion 17 is in the form of a half-shell and is offset axially relative to the portions 14, 15 of the guide washer 12 also forming a half-shell. The guide washer 12 is provided at its axial portion 15 with inward material deformations 21 for support of the ends of the springs 16. The portion 14 also has lugs 22 for support of the ends of the springs 16. For more precision, reference is made to document OA-94/1047058, in particular to FIGS. 24 to 28 thereof. Note, with the exception of the gasket 29 and the linings
11,111, que les pièces de l'appareil d'accouplement hydrocinétique sont métalliques.11,111, that the parts of the hydrokinetic coupling device are metallic.
Ainsi l'embrayage de verrouillage l comporte un amortisseur de torsion 23 implanté en majeure partie entre la roue de turbine 4 et la paroi 2 à la périphérie externe de la première coquille, avec une partie d'entrée 12, disposée radialement au-dessus du piston 9 et des garnitures 11,111 en étant constituée par la rondelle de guidage 12 en forme de demi- coquille 14,15, des ressorts à boudin 16 et une partie de sortie constituée par le voile 18 également en forme de demi-coquille à sa périphérie externe.Thus the locking clutch l comprises a torsion damper 23 located mainly between the turbine wheel 4 and the wall 2 at the external periphery of the first shell, with an inlet part 12, arranged radially above the piston 9 and the linings 11,111 being constituted by the guide washer 12 in the form of a half-shell 14,15, coil springs 16 and an outlet part constituted by the web 18 also in the form of a half-shell at its periphery external.
La partie de sortie 18 est liée en rotation à la roue de turbine 4, plus précisément au moyeu 5 de celle-ci, tandis que la partie d'entrée 12 est liée en rotation au disque 10, saillant radialement par rapport au piston 9. La partie d'entrée 12 est donc liée de manière débrayable via le disque 10 et les garnitures 11,111 à l'arbre menant, ledit disque 10 avec ses garnitures étant propre à être serré de manière débrayable entre le piston 9 et la paroi 2 formant contre-piston. Le disque 10 est donc accouplé de manière élastique au moyeu 5 et à la roue 4.The outlet part 18 is linked in rotation to the turbine wheel 4, more precisely to the hub 5 thereof, while the inlet part 12 is linked in rotation to the disc 10, projecting radially with respect to the piston 9. The inlet part 12 is therefore disengageably connected via the disk 10 and the linings 11,111 to the driving shaft, said disk 10 with its linings being suitable for being disengageably clamped between the piston 9 and the wall 2 forming against -piston. Disc 10 is therefore coupled elastically to the hub 5 and to the wheel 4.
Plus précisément la roue de turbine 4 est entraînée en rotation par la roue d'impulseur grâce à la circulation de fluide contenu dans le boîtier au carter étanche et après démarrage du véhicule l'embrayage de verrouillage 1 permet, pour éviter les phénomènes de glissement entre les roues de turbine et d'impulseur, une solidarisation directe de l'arbre mené avec l'arbre menant et ce par serrage des garnitures de frottement 11,111 et du disque 10 entre le piston 9 et le contre-piston 2 avec entraînement direct de l'arbre mené par la coquille 1.More precisely, the turbine wheel 4 is rotated by the impeller wheel by virtue of the circulation of fluid contained in the sealed casing and after starting the vehicle, the locking clutch 1 allows, to avoid the phenomena of sliding between the turbine and impeller wheels, a direct connection of the driven shaft with the driving shaft and this by tightening the friction linings 11,111 and the disc 10 between the piston 9 and the counter-piston 2 with direct drive of the tree driven by the shell 1.
Pour desserrer l'embrayage 1 (figure 1), on envoie de la pression dans la chambre 30 par l'intermédiaire du canal de l'arbre mené, du trou borgne de la bague 6 et des perçages de celle-ci. Cette chambre 30 est rendue étanche par le joint 29 porté par la collerette 8.To loosen the clutch 1 (Figure 1), pressure is sent to the chamber 30 via the channel of the driven shaft, the blind hole of the ring 6 and the holes thereof. This chamber 30 is sealed by the seal 29 carried by the flange 8.
En position embrayage engagé (garnitures 11,111 serrées) ladite chambre 30 est dépressurisée. Cette chambre 30 est donc délimitée extérieurement par le disque 10 et les garnitures 11,111.In the engaged clutch position (linings 11,111 tight) said chamber 30 is depressurized. This chamber 30 is therefore delimited externally by the disc 10 and the linings 11,111.
On notera que le piston 9 est lié en rotation à la paroi 2 de la première coquille par des languettes élastiques tangentielles 40 réparties régulièrement circon- férentiellement, ici quatre jeux de languettes (figure 3) . Ces languettes 40 autorisent un mouvement axial du piston. Ici les languettes sont attelées à la paroi transversale 2 par l'intermédiaire d'une pièce annulaire 44, ici métallique, solidaire de la paroi 2 ici par des rivets 45 venus ici d'un seul tenant de celle-ci, par exemple par extrusion. A sa périphérie interne la pièce annulaire 44 présente de place en place des pattes 48 décalées axialement par rapport à sa partie principale de fixation à la paroi 2. Les languettes 40, formées ici d'un empilage de deux languettes, sont solidarisées à l'une de leur extrémité par des rivets 43 aux pattes 48. En variante les rivets peuvent consister en des vis ou des boulons.It will be noted that the piston 9 is linked in rotation to the wall 2 of the first shell by tangential elastic tongues 40 distributed regularly circumferentially, here four sets of tongues (FIG. 3). These tongues 40 allow axial movement of the piston. Here, the tongues are coupled to the transverse wall 2 by means of an annular piece 44, here metallic, secured to the wall 2 here by rivets 45 which have come here in one piece from it, for example by extrusion . At its internal periphery the annular part 44 has from place to place tabs 48 offset axially with respect to its main part for fixing to the wall 2. The tongues 40, formed here from a stack of two tongues, are secured to the one of their ends by rivets 43 to the legs 48. As a variant, the rivets may consist of screws or bolts.
Pour l'attelage de l'autre extrémité des languettes 40 au piston 9, on met en oeuvre des moyens de fixation 41,42, qui, tout en étant aptes à traverser globalement les languettes 40 et le piston 9, comportent deux parties, à savoir, une première partie 41, qui, par avance, est assujettie aux languettes 40, du côté de celles-ci opposées au piston 9, et d'une deuxième partie 42, qui, pour venir en prise avec la première partie 41, ne nécessite d'intervenir que du côté du piston 9. Les languettes 40 s'étendent dans le volume qui s'étend radialement entre les garnitures de frottement 11,111 et l'axe de l'ensemble c'est-à- dire dans la chambre 30. Ces languettes 40 s'étendent axialement entre la paroi 2 et le piston 9 dans une région où la paroi 2 est saillante axialement en direction opposée à la roue de turbine en sorte qu'axialement, au niveau de la collerette 8 de la bague 6, un faible encombrement axial existe entre le piston 9 et la paroi 2.For coupling the other end of the tongues 40 to the piston 9, fixing means 41, 42 are used, which, while being capable of passing generally through the tongues 40 and the piston 9, have two parts, know, a first part 41, which, in advance, is subject to the tongues 40, on the side thereof opposite the piston 9, and a second part 42, which, in order to come into engagement with the first part 41, does not require intervention as on the side of the piston 9. The tongues 40 extend in the volume which extends radially between the friction linings 11, 111 and the axis of the assembly, that is to say in the chamber 30. These tongues 40 extend axially between the wall 2 and the piston 9 in a region where the wall 2 projects axially in the direction opposite to the turbine wheel so that axially, at the flange 8 of the ring 6, a small space requirement axial exists between the piston 9 and the wall 2.
Ici la fixation en deux parties 41,42 est du type tige de boulon sertie. La première partie 41 comporte une tige avec une tête d'appui. La tige traverse à jeu le perçage du piston 9 et comporte un premier tronçon lisse et un premier tronçon cranté. Cette partie 41 est assujettie par emmanchement à force ou en variante par moletage ou collage aux languettes 40. La tête d'appui des tiges 41 est montée dans la chambre 30. La deuxième partie 42 consiste en une bague de sertissage, qui comporte, du côté du piston, une embase de plus grand diamètre pour éviter son fluage dans le perçage du piston. La bague 42 est donc montée à l'extérieur de la chambre 30.Here the fixing in two parts 41,42 is of the crimped bolt rod type. The first part 41 comprises a rod with a support head. The rod plays through the bore of the piston 9 and has a first smooth section and a first notched section. This part 41 is fixed by force fitting or alternatively by knurling or gluing to the tongues 40. The support head of the rods 41 is mounted in the chamber 30. The second part 42 consists of a crimping ring, which comprises, side of the piston, a larger diameter base to prevent its creep in the bore of the piston. The ring 42 is therefore mounted outside the chamber 30.
Ainsi qu'on l'aura compris on écrase la bague 42 pour que celle-ci vienne en prise avec le tronçon cranté de la tige 41. En variante on peut utiliser des rivets du type "POP".As will be understood, the ring 42 is crushed so that it comes into engagement with the notched section of the rod 41. As a variant, rivets of the "POP" type can be used.
En variante la première partie peut consister en un écrou ou une vis fixée par exemple par collage aux languettes 40 et la deuxième partie en une vis ou un écrou. Toutes les dispositions décrites dans le documentAs a variant, the first part may consist of a nut or a screw fixed for example by gluing to the tongues 40 and the second part may consist of a screw or a nut. All the provisions described in the document
FR94 13205 déposé le 4 novembre 1994 sont envisageables.FR94 13205 filed on November 4, 1994 are possible.
Dans le mode de réalisation des figures 1 à 3 des moyens de butée 50 sont implantés dans la chambre 30 pour notamment limiter le cambrage des languettes 40 et ménager celles-ci. Ces moyens de butée 50 sont formés à la faveur de la pièce 44 servant à l'entraînement et à la fixation des languettes 40 à la paroi 2. Plus précisément les languettes tangentielles 40 sont ici prolongées circonférentiellement au- delà de la fixation en deux parties 41,42 des languettes 40 au piston 9.In the embodiment of FIGS. 1 to 3, stop means 50 are installed in the chamber 30 in particular in order to limit the bending of the tongues 40 and to spare them. These abutment means 50 are formed by means of the part 44 used for driving and fixing the tongues 40 to the wall 2. More precisely, the tangential tongues 40 are here extended circumferentially au- beyond the fixing in two parts 41, 42 of the tongues 40 to the piston 9.
L'extrémité libre de chacun des prolongements 47 est propre à coopérer avec une butée 46 tournée vers la paroi 2 (figures 2 et 3) . Cette butée 46 appartient au moyen 50 et s'étend localement parallèlement à la paroi 2. Elle est formée par emboutissage à la faveur des pattes 48 décalées axialement par rapport à la partie principale de la pièce annulaire 44.The free end of each of the extensions 47 is adapted to cooperate with a stop 46 facing the wall 2 (Figures 2 and 3). This stop 46 belongs to the means 50 and extends locally parallel to the wall 2. It is formed by stamping in favor of the tabs 48 offset axially relative to the main part of the annular part 44.
Une patte 48 présente donc une extrémité pour la fixation d'un rivet 43 et une butée 46.A lug 48 therefore has one end for fixing a rivet 43 and a stop 46.
Ainsi à partir de la partie principale de la pièce 44, il est formé globalement en section des équerres (ou griffes) avec une partie d'orientation axiale entourant l'extrémité libre des languettes 40 (le prolongement 47) , prolongées par une partie d'orientation transversale 46 formant les moyens de butée 50 propres à coopérer avec la face des languettes 40 tournée vers le piston 9 c'est-à-dire avec la face dorsale des languettes 40.Thus from the main part of the piece 44, it is formed overall in section of the brackets (or claws) with a part of axial orientation surrounding the free end of the tongues 40 (the extension 47), extended by a part d transverse orientation 46 forming the abutment means 50 suitable for cooperating with the face of the tongues 40 facing the piston 9, that is to say with the dorsal face of the tongues 40.
Les butées 46 limitent donc le déplacement du piston 9 en direction opposée à la paroi transversale 2.The stops 46 therefore limit the displacement of the piston 9 in the direction opposite to the transverse wall 2.
Ainsi on évite tout contact du piston 9 avec le moyeu 5 ou le flasque 19 et on limite le déplacement relatif entre la bague 6 et le piston 9, qui reste en toute circonstance en prise avec le joint 29. La chambre 30 est donc toujours étanche et ce malgré le gonflement du boîtier qui se produit ainsi qu'on le sait lors de la rotation de l'appareil d'accouplement hydrocinétique.This avoids any contact of the piston 9 with the hub 5 or the flange 19 and limits the relative displacement between the ring 6 and the piston 9, which remains in all circumstances in engagement with the seal 29. The chamber 30 is therefore always sealed and this despite the swelling of the housing which occurs as is known during the rotation of the hydrokinetic coupling device.
Bien entendu, en variante, les moyens de butée 50 peuvent consister en un anneau rapporté, par exemple par rivetage ou encliquetage, sur la bague de guidage 6 en étant en contact avec la face dorsale de celle-ci. Cet anneau fait alors saillie par rapport à la périphérie externe de la collerette 8 et est adapté à coopérer avec la périphérie interne du piston 9 pour limiter le déplacement de celui-ci en direction opposée à la paroi 2.Of course, as a variant, the stop means 50 may consist of an added ring, for example by riveting or snap-fastening, on the guide ring 6 while being in contact with the dorsal face of the latter. This ring then projects relative to the external periphery of the flange 8 and is adapted to cooperate with the internal periphery of the piston 9 to limit the displacement of the latter in the direction opposite to the wall 2.
Grâce aux moyens de butée 50 on peut réduire l'écartement qui existe entre le piston 9 et la garniture 11 lorsque l'embrayage de verrouillage est désengagé ou déponté. Ceci permet de réduire les temps de réponse et est favorable à la création d'un glissement contrôlé décrit ci- après.Thanks to the stop means 50, it is possible to reduce the spacing which exists between the piston 9 and the lining 11 when the locking clutch is disengaged or released. This makes it possible to reduce the response times and is favorable to the creation of a controlled slip described below.
Ainsi qu'on l'aura compris le piston 9 délimite deux chambres à savoir la chambre 30 à volume variable et une chambre principale située du côté de la face dorsale du piston 9 tourné à l'opposé de la paroi 2.As will be understood, the piston 9 delimits two chambers, namely the chamber 30 with variable volume and a main chamber situated on the side of the dorsal face of the piston 9 turned away from the wall 2.
Ainsi en faisant varier la pression dans la chambre à volume variable 30, on peut réaliser un glissement contrôlé des garnitures de frottement 11,111 par rapport respectivement au piston 9 et à la paroi 2 formant contre-piston.Thus by varying the pressure in the variable volume chamber 30, it is possible to achieve controlled sliding of the friction linings 11,111 relative to the piston 9 and to the wall 2 respectively forming a counter-piston.
Ce glissement contrôlé permet notamment de faire glisser ou patiner les garnitures de frottement 11,111 et donc le disque 10 pour certains régimes du moteur afin de mieux filtrer les vibrations.This controlled sliding allows in particular to slide or slip the friction linings 11,111 and therefore the disc 10 for certain engine speeds in order to better filter vibrations.
Un mouvement relatif se produit donc alors entre le disque 10 équipé des garnitures 11,111 et l'ensemble piston 9 - paroi transversale 2.A relative movement therefore occurs between the disc 10 fitted with the linings 11,111 and the piston 9 - transverse wall 2 assembly.
Ce glissement conduit donc à un échauffement desdites garnitures de frottement ainsi que du piston 9, du disque 10 et de la paroi 2 et ce à la périphérie externe de la chambre 30.This sliding therefore leads to heating of said friction linings as well as of the piston 9, of the disc 10 and of the wall 2 and this at the outer periphery of the chamber 30.
L'huile s'échauffe donc au-delà de la chambre 30 à volume variable à proximité de celle-ci.The oil therefore heats up beyond the variable-volume chamber 30 close to the latter.
On notera que le piston 9 et la paroi 2 comportent des portions transversales à la périphérie externe de la chambre 30 pour offrir des faces de friction planes (d'orientation transversale) aux garnitures de frottement 11,111.It will be noted that the piston 9 and the wall 2 have transverse portions at the external periphery of the chamber 30 in order to provide plane friction faces (of transverse orientation) to the friction linings 11,111.
Ainsi lors du glissement contrôlé la pression qui règne dans la partie principale du boîtier de l'appareil d'accouplement hydrocinétique est supérieure à celle régnant dans la chambre à volume variable 30.Thus, during controlled sliding, the pressure prevailing in the main part of the housing of the hydrokinetic coupling device is greater than that prevailing in the variable volume chamber 30.
Pour diminuer l'échauffement, l'invention propose de créer dans les garnitures de frottement 11,111 des rainures 80,180 s'étendant globalement en portion de spirale de la périphérie externe à la périphérie interne de chaque garniture de frottement 11,111 en étant enroulées en spirale selon le sens de rotation (figure 4) du disque inverse de celui F du moteur pour réaliser un effet d'écope. Ici quatre rainures ou gorges 80,180 sont prévues par garniture de frottement 11,111. Ces rainures sont réparties régulièrement circonférentiellement telle que mieux visible dans les figures 4 et 6. Elles sont globalement, suivant une caractéristique de l'invention, en forme d'arc-de-cercle décentré par rapport au centre du disque 10 et s'enroulent en spirale en pratique selon une portion de spirale.To reduce overheating, the invention proposes to create in the friction linings 11,111 grooves 80,180 generally extending in a portion of a spiral from the external periphery to the internal periphery of each friction lining 11,111 by being wound in a spiral according to the direction of rotation (Figure 4) of the disc opposite to that of the motor F to achieve a scoop effect. Here four grooves or grooves 80,180 are provided by friction lining 11,111. These grooves are regularly distributed circumferentially as best seen in Figures 4 and 6. They are generally, according to a characteristic of the invention, in the form of an arc of a circle offset from the center of the disc 10 and are wound in practice in a spiral according to a portion of a spiral.
Bien entendu ces rainures peuvent avoir une plus ou moins grande longueur. On notera le fait, que les rainures s'étendent en portion de spirale, permet d'augmenter le nombre d'entrées et de sorties pour le fluide transitant dans les gorges tout en laissant une surface importante pour les garnitures.Of course, these grooves can have a greater or lesser length. Note the fact that the grooves extend in a spiral portion, increases the number of inlets and outlets for the fluid passing through the grooves while leaving a large area for the linings.
D'une manière générale on a intérêt à augmenter le nombre de gorges pour un transfert rapide d'huile dans la chambre 30. Bien entendu tout cela dépend des applications.In general, it is advantageous to increase the number of grooves for a rapid transfer of oil into the chamber 30. Of course, this all depends on the applications.
Les rainures s'évasent de préférence en direction de la périphérie externe des garnitures de frottement 11,111. Elles ont de préférence une largeur supérieure à leur profondeur. Elles sont plus larges à leur périphérie interne et externe pour faciliter la circulation du fluide (ici de l'huile) et recueillir et évacuer le maximum de fluide. En outre on évite un écaillage des garnitures.The grooves preferably widen in the direction of the external periphery of the friction linings 11,111. They preferably have a width greater than their depth. They are wider at their internal and external peripheries to facilitate the circulation of the fluid (here oil) and to collect and evacuate the maximum of fluid. In addition, the linings are not chipped.
On notera la disposition alternée d'une garniture de frottement à l'autre, c'est-à-dire qu'une rainure 80 de la garniture de frottement 11 se termine à la périphérie interne de ladite garniture là ou commence une rainure 180 de la garniture de frottement 111.Note the alternating arrangement of one friction lining to the other, that is to say that a groove 80 of the friction lining 11 ends at the internal periphery of said lining where a groove 180 of the friction lining 111.
Ainsi les garnitures de frottement sont bien refroidies car aucun point des garnitures de frottement n'est loin d'une gorge de refroidissement 80,180.Thus the friction linings are well cooled because no point of the friction linings is far from a cooling groove 80,180.
Grâce à l'invention lors du glissement contrôlé on obtient une circulation de fluide du type centripète avec effet de pompage, le fluide circulant de la périphérie externe du disque 10 à la périphérie interne dudit disque, du fait que la pression régnant sur la face dorsale du piston 9 est en général plus grande que la pression régnant dans la chambre à volume variable. Ainsi l'huile chaude, présente au-delà des garnitures 11,111, est transférée dans la chambre 30 via les rainures 80,180 puisant l'huile chaude. L'huile est donc refroidie dans la chambre 30. On notera que le débit du fluide à travers les rainures est proportionnel à la vitesse et que l'on obtient grâce aux rainures un effet d'entraînement du fluide par cisaillement visqueux, les rainures puisant de l'huile à la périphérie externe de la chambre 30. Le débit est proportionnel à la pression différentielle et à la vitesse, notamment à la vitesse différentielle entre le disque 10 et l'ensemble piston 9 - paroi transversale 2. Ce débit augmente en fonction de la puissance de glissement.Thanks to the invention during controlled sliding, a circulation of fluid of the centripetal type with pumping effect is obtained, the fluid circulating from the external periphery of the disc 10 to the internal periphery of said disc, because the pressure prevailing on the dorsal face piston 9 is generally greater than the pressure in the variable volume chamber. Thus the hot oil, present beyond the linings 11,111, is transferred into the chamber 30 via the grooves 80,180 drawing the hot oil. The oil is therefore cooled in chamber 30. It will be noted that the flow rate of the fluid through the grooves is proportional to the speed and that the effect of the grooves is obtained by a fluid entrainment effect by viscous shearing, the grooves drawing of oil at the outer periphery of the chamber 30. The flow is proportional to the differential pressure and to the speed, in particular to the differential speed between the disc 10 and the piston 9 - transverse wall 2 assembly. This flow increases in function of sliding power.
On obtient une bonne transmission de couple de la paroi 2 au disque 10 malgré la présence des rainures de refroidissement 80,180. En résumé tout dépend de la vitesse relative entre le moteur (et donc la paroi 2) et le disque 10.Good torque transmission is obtained from the wall 2 to the disc 10 despite the presence of the cooling grooves 80,180. In summary everything depends on the relative speed between the motor (and therefore the wall 2) and the disc 10.
On notera que la fixation des garnitures de frottement sur le disque 10 est avantageuse car grâce aux pattes 28 on peut orienter aisément les rainures par rapport au sens de rotation du disque repéré par la flèche F aux figures 4 et 6.It will be noted that the fixing of the friction linings on the disc 10 is advantageous because, thanks to the tabs 28, the grooves can be easily oriented relative to the direction of rotation of the disc identified by the arrow F in FIGS. 4 and 6.
Bien entendu la présente invention n'est pas limitée à l'exemple de réalisation décrit. En particulier la liaison en rotation du piston 9 avec la première demi-coquille 2,3 peut être réalisée à la faveur du piston 9 présentant à sa périphérie interne des cannelures propres à engrener avec des cannelures complémentaires, que présente la bague 6 à sa périphérie interne c'est-à-dire à la périphérie externe de sa collerette.Of course, the present invention is not limited to the embodiment described. In particular, the connection in rotation of the piston 9 with the first half-shell 2,3 can be achieved by means of the piston 9 having at its internal periphery grooves suitable for meshing with complementary grooves, which has the ring 6 at its periphery. internal, that is to say at the external periphery of its flange.
En variante on peut utiliser le type de liaison en rotation à bossages décrit dans le document O-A-94/07058 précité.As a variant, it is possible to use the type of rotation link with bosses described in the document O-A-94/07058 mentioned above.
Bien entendu la liaison en rotation peut être réalisée également comme décrit dans le document WO-A-93/13339 c'est-à- dire une liaison faisant intervenir un moyeu cannelé porté par le piston et un disque cannelé intérieurement porté à solidarisation par la paroi 2. Dans ce cas le disque cannelé offre une face de friction à la garniture 111 en sorte que lesdites garnitures sont propres à être serrées directement ou indirectement, par exemple avec interposition d'un disque, d'une plaque, d'un revêtement etc., entre le piston 9 et la paroi transversale 2.Of course, the rotational connection can also be produced as described in document WO-A-93/13339, that is to say a connection involving a splined hub carried by the piston and a fluted disc internally worn which is secured by the wall 2. In this case the grooved disc offers a friction face to the lining 111 so that said linings are suitable for being clamped directly or indirectly, for example with the interposition of a disc, a plate, coating etc., between the piston 9 and the transverse wall 2.
En variante les garnitures de frottement 11,111, au lieu d'être solidaires par collage ou brasage du disque 10, peuvent être solidarisées respectivement au piston 9 ou à la paroi 2 et ce par exemple par collage ou brasage en sorte que chaque garniture de frottement est solidaire de l'un des éléments respectivement piston - paroi transversale entre lesquels elle est destinée à être serrée. Les rainures 180,80 peuvent donc affecter les faces des garnitures de frottement 111,11 tournées vers le disque 10.As a variant, the friction linings 11,111, instead of being secured by bonding or brazing the disc 10, can be secured respectively to the piston 9 or to the wall 2 and this for example by bonding or brazing so that each friction lining is secured to one of the piston and transverse wall elements respectively, between which it is intended to be clamped. The grooves 180,80 can therefore affect the faces of the friction linings 111,11 facing the disc 10.
Bien entendu on peut inverser la structure de la liaison 13 le disque 10 présentant alors des mortaises dans lesquelles s'engagent des tenons de la rondelle de guidage 12. En variante le disque 10 peut être accouplé par une liaison de type tenons-mortaises à une couronne rapportée sur la roue de turbine 4. Dans ce cas le disque 10 est accouplé de manière rigide à la roue de turbine 4.Of course, the structure of the connection 13 can be inverted, the disc 10 then having mortises in which pins of the guide washer 12 engage. Alternatively, the disc 10 can be coupled by a link of the tenon-mortise type to a crown attached to the turbine wheel 4. In this case the disc 10 is rigidly coupled to the turbine wheel 4.
Bien entendu le nombre des rainures de refroidissement 80,180 dépend des applications, notamment du diamètre externe des garnitures de frottement 11,111. Of course, the number of cooling grooves 80,180 depends on the applications, in particular on the external diameter of the friction linings 11,111.

Claims

REVENDICATIONS
1- Appareil d'accouplement hydrocinétique, notamment pour véhicule automobile, comportant une paroi globalement d'orientation transversale (2) propre à être liée en rotation à un arbre menant et portant à fixation centralement une bague de guidage (6) , un piston (9) monté mobile axialement à étanchéité le long de la bague de guidage (6) et définissant avec ladite bague (6) et ladite paroi transversale (2) une chambre à volume variable (30) délimitée extérieurement par un disque (10) et des garnitures de frottement (11,111) adaptées à être serrées respectivement entre le piston (9) et le disque (10) et entre le disque (10) et la paroi transversale (2) , chaque garniture de frottement (11,111) étant solidaire de l'un des éléments disque (10) respectivement piston (9) - paroi transversale (2) entre lesquels elle est destinée à être serrée, dans lequel chaque garniture de frottement (11,111) est dotée d'au moins une rainure (80,180) , dite rainure de refroidissement, caractérisé en ce que lesdites rainures (80,180) sont globalement en forme d'arc de cercle décentré par rapport au centre du disque (10) et s'étendent globalement en portion de spirale de la périphérie externe à la périphérie interne de chaque garniture de frottement (11,111) en étant enroulées en spirale selon le sens de rotation du disque (10) et en ce que les rainures de refroidissement (80,180) sont réparties de manière alternée d'une garniture de frottement (11,111) à l'autre garniture de frottement (11,111) , une garniture de frottement se terminant là où commence une rainure (18à) de l'autre garniture de frottement (11,111) . 2- Appareil selon la revendication 1, caractérisé en ce que les rainures (80,180) sont plus larges à leur périphérie interne et externe.1- Hydrokinetic coupling device, in particular for a motor vehicle, comprising a wall of generally transverse orientation (2) suitable for being linked in rotation to a driving shaft and carrying centrally attached a guide ring (6), a piston ( 9) mounted axially movable with sealing along the guide ring (6) and defining with said ring (6) and said transverse wall (2) a variable volume chamber (30) delimited externally by a disc (10) and friction linings (11,111) adapted to be clamped respectively between the piston (9) and the disc (10) and between the disc (10) and the transverse wall (2), each friction lining (11,111) being integral with the one of the disc elements (10) respectively piston (9) - transverse wall (2) between which it is intended to be clamped, in which each friction lining (11,111) is provided with at least one groove (80,180), called groove chilled ment, characterized in that said grooves (80,180) are generally in the form of an arc of a circle off-center with respect to the center of the disc (10) and extend generally in a portion of a spiral from the external periphery to the internal periphery of each lining friction (11,111) being wound in a spiral in the direction of rotation of the disc (10) and in that the cooling grooves (80,180) are distributed alternately from one friction lining (11,111) to the other lining friction pad (11,111), a friction pad ending where a groove (18a) begins on the other friction pad (11,111). 2- Apparatus according to claim 1, characterized in that the grooves (80,180) are wider at their inner and outer periphery.
3- Appareil selon la revendication 1, caractérisé en ce que les rainures (80,180) s'évasent en allant de la périphérie interne à la périphérie externe de la garniture de frottement.3- Apparatus according to claim 1, characterized in that the grooves (80,180) flare going from the inner periphery to the outer periphery of the friction lining.
4- Appareil selon la revendication 1, caractérisé en ce que les garnitures de frottement (11,111) sont solidaires du disque (10) doté à sa périphérie externe de pattes (28) pour sa liaison en rotation de manière élastique ou rigide avec la roue de turbine (4), que présente l'appareil d'accouplement hydrocinétique.4- Apparatus according to claim 1, characterized in that the friction linings (11,111) are integral with the disc (10) provided at its outer periphery with lugs (28) for its rotationally elastic or rigid connection with the wheel turbine (4), presented by the hydrokinetic coupling device.
5- Appareil selon la revendication 4, caractérisé en ce que les pattes (28) sont en forme d'equerre avec une partie d'orientation axiale pénétrant dans une encoche d'une rondelle de guidage (12), que comporte l'appareil d'accouplement hydro¬ cinétique, et une partie d'orientation radiale de raccordement à la partie principale du disque (10) , ladite rondelle de guidage (12) étant reliée élastiquement à la roue de turbine (4) . 5- Apparatus according to claim 4, characterized in that the legs (28) are in the form of a square with a portion of axial orientation penetrating into a notch of a guide washer (12), which comprises the apparatus d 'hydro¬ kinetic coupling, and a radial orientation part for connection to the main part of the disc (10), said guide washer (12) being elastically connected to the turbine wheel (4).
PCT/FR1996/000712 1995-05-11 1996-05-10 Hydrokinetic coupling apparatus, particularly for a motor vehicle WO1996035891A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE19680460T DE19680460T1 (en) 1995-05-11 1996-05-10 Hydrodynamic transmission, in particular for motor vehicles
KR1019970700131A KR100494959B1 (en) 1995-05-11 1996-05-10 Hydrokinetic coupling apparatus, particularly for a motor vehicle
JP8533838A JPH10503002A (en) 1995-05-11 1996-05-10 Hydrodynamic coupling device for automobiles

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9505822A FR2734038B1 (en) 1995-05-11 1995-05-11 HYDROKINETIC COUPLING APPARATUS, PARTICULARLY FOR A MOTOR VEHICLE
FR95/05822 1995-05-11

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Country Status (5)

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JP (1) JPH10503002A (en)
KR (1) KR100494959B1 (en)
DE (1) DE19680460T1 (en)
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WO (1) WO1996035891A1 (en)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
FR2783298A1 (en) * 1998-09-10 2000-03-17 Valeo HYDROKINETIC COUPLING APPARATUS WITH COOLING GROOVE

Families Citing this family (4)

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Publication number Priority date Publication date Assignee Title
FR2765296B1 (en) * 1997-06-30 1999-12-03 Valeo HYDROKINETIC COUPLING APPARATUS WITH LOCKING CLUTCH FOR MOTOR VEHICLE
FR2820482B1 (en) * 2001-02-15 2003-04-11 Valeo HYDROKINETIC COUPLING APPARATUS
FR2856453B1 (en) 2003-06-17 2006-05-19 Valeo Embrayages HYDROKINETIC COUPLING APPARATUS, ESPECIALLY FOR A MOTOR VEHICLE, AND FRICTION FITTING FOR SUCH AN APPARATUS
DE102015016938A1 (en) * 2015-12-24 2017-06-29 Daimler Ag A power train assembly

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EP0533426A2 (en) * 1991-09-20 1993-03-24 Toyota Jidosha Kabushiki Kaisha Fluid coupling power transmission with lockup clutch
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EP0533426A2 (en) * 1991-09-20 1993-03-24 Toyota Jidosha Kabushiki Kaisha Fluid coupling power transmission with lockup clutch
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Also Published As

Publication number Publication date
FR2734038B1 (en) 1998-08-07
DE19680460T1 (en) 1997-05-28
KR100494959B1 (en) 2005-11-01
FR2734038A1 (en) 1996-11-15
JPH10503002A (en) 1998-03-17
KR970704986A (en) 1997-09-06

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