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
  • F16H2045/0205—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
  • F16H2045/0278—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch comprising only two co-acting friction surfaces

Definitions

• the present invention relates to a hydrokinetic coupling device, in particular for a motor vehicle, of the type described and shown for example in document W3-A-99/45294.
• This document describes and represents an apparatus of the type comprising a wall, generally of transverse orientation, suitable for being linked in rotation to a driving shaft and carrying centrally attached a central ring, a turbine wheel integral in rotation with a clean hub. to be linked in rotation to a driven shaft, an axially sliding piston, sealingly mounted along a central ring interposed axially between the transverse casing wall and the turbine hub and a rear stop which limits the axial displacements of the piston relative to the central ring in the direction corresponding to its distance from the internal face of the transverse wall and which prevents your direct friction contact between the piston and the hub of the turbine wheel.
• an additional part essentially consisting of a plate in the form of a flat ring, is attached to a ring to constitute an axial support part, on the one hand for the front face of the ring and, on the other hand for the annular front end face of a guide ring for sliding the piston.
• This part therefore forms a piston abutment plate avoiding any contact, metal on metal, between the piston and the flange of the hub located opposite.
• the ring is of the metallic type to allow its connection by welding with the generally transverse wall of the casing.
• the transverse orientation wall is a part in pressed sheet metal which comprises, at its central part, a central sleeve produced integrally by stamping and which is open at its free axial end which is traversed by the central ring, the latter extending axially forwards, beyond of the cylindrical centering surface of the central ring, by a journal for the rotational connection of the central ring with the driving shaft, in particular with the crankshaft of a motor vehicle engine equipped with a hydrokinetic coupling device.
• the front axial end edge of the fixing sleeve extends substantially in line with a transverse face of the central ring which delimits axially forward the cylindrical centering surface.
• the transverse wall is fixed to the central ring by means of a welding operation carried out in the connection zone between the annular transverse face of the front end of the central sleeve of the transverse wall and the transverse face of the central ring .
• the present invention aims to provide a hydrokinetic coupling device of the type mentioned previously, which allows easy assembly of the various components of the device, reducing the number of components as well as the weight and cost of the assembly.
• the invention provides a hydrokinetic coupling device, nota ⁇ ent for a motor vehicle, of the type comprising, arranged axially from front to back:
• a transverse casing wall of generally radial orientation, suitable for being linked in rotation to a driving shaft;
• a rear stop which limits the axial displacements of the piston with respect to the central ring in the direction corresponding to its distance from the internal face of the transverse wall and which prevents direct friction contact between the piston and the wheel hub turbine, characterized in that the stop is made in one piece with the central ring.
• the central ring is axially coupled to the piston;
• the central ring is made by molding, notably in plastic material;
• the central ring is centered radially with respect to the piston;
• the central ring is centered radially with respect to the transverse casing wall;
• the central ring is centered radially with respect to the hub of the turbine;
• the stop is generally in the form of a continuous or discontinuous flat ring of radial orientation which extends radially outwards beyond the main body of generally tubular shape of the central ring;
• the central ring is centered radially and is immobilized axially relative to the transverse casing wall or relative to the hub of the turbine;
• a rear transverse face of the central ring has at least one lubrication groove
• the free end of the driven shaft extends axially inside a bore of the central ring with the interposition of a seal.
• FIG. 1 is a half-view in partial axial section of an apparatus hydrokinetic coupling according to a first example of implementation of the principles of the invention in which the central ring and the stop are overmolded around the internal periphery of the piston;
• Figure 2 is an enlarged view of the lower part of Figure 1 which illustrates an alternative embodiment of a central ring attached to the inner radial periphery of the piston by overmolding;
• Figure 3 is an enlarged view of the lower part of Figure 1 which illustrates another alternative embodiment in which the central ring with the stopper is coupled to the outer radial periphery by force fitting;
• Figure 4 is an enlarged view of the lower part of Figure 1 which illustrates another embodiment in which the central ring with the stopper is attached to the inner radial periphery of the piston by elastic interlocking;
• Figure 5 is a view similar to that of Figure 1 which illustrates an axially sliding piston,
• a hydrokinetic coupling device 50 comprises, arranged in the same sealed housing filled with oil and forming housing 52 , a torque converter and a locking clutch 54, usually den ⁇ r ⁇ ié "lock-up".
• the converter can be replaced by a hy ⁇ rodynarnic coupler, the coupler being distinguished from the converter, which is well known in that it does not include a reactor wheel.
• the housing 52 here metallic, constitutes a driving element and it is suitable for being linked in rotation to a driving shaft, namely for example the crankshaft (not shown) of the internal combustion engine in the case of an application to a vehicle. automobile.
• the housing 52 of generally annular shape, consists of two half-shells facing each other and which are fixed in leaktight manner at their external periphery, usually by a welding operation.
• the first front half-shell 56 shown in the figures is capable of being linked in rotation to the driving shaft and it is essentially constituted by an annular wall 58 which is generally of transverse orientation, that is to say which s 'extends in a radial plane perpendicular to one axis XX of one device, and which is extended at its outer periphery by a cylindrical wall in the form of an annular skirt 60 generally of axial orientation.
• the second rear half-shell (not shown in the figures for the sake of simplicity as well as the reactor wheel of the converter) is shaped so as to define an impeller wheel and for this purpose comprises vanes on its internal face.
• blades face the blades 62 of a turbine wheel 64 fixed by riveting, or alternatively by welding, to a hub wall 68 in one piece with a hub 70 internally fluted for the rotational connection to a driven shaft 72, namely the input shaft of the gearbox in the case of an application to a motor vehicle.
• the driven shaft 72 is hollowed out internally to form a channel
• a piston 74 delimits, with a central ring 76, the annular transverse wall 58 and an annular disc 78, a chamber 82 with variable volume supplied through the driven shaft 72.
• the annular disc 78 carries fixing, for example by bonding on each of its opposite transverse faces, friction linings 80.
• the disc 78 is located at the outer periphery of the piston and has at its outer periphery, radially beyond the piston 74, lugs, with an axially oriented part, each penetrating into a notch, which has a guide washer 84 at its outer periphery.
• the disc 78 is thus linked in rotation, with axial mobility, to the guide washer 84 with the interposition of coil springs 86 with circumferential action.
• the washer 84 for guiding the springs 86 is extended radially inwards by an annular flange of transverse orientation 88 which has a series of holes 90 for circulation of the oil between the piston
• the locking clutch 54 includes a torsion damper located mainly between the turbine wheel 64 and the transverse wall 58 at the outer periphery of the first shell.
• the torsion damper comprises an inlet part, arranged radially above the piston 74 and the linings 80, constituted by the axial extension towards the rear of the disc 78, the coil springs 86 and an outlet part constituted by the flange 88 and the guide washer 84.
• the outlet part is linked in rotation to the turbine wheel 64, more precisely to the grooved hub 70 thereof, while the inlet part is linked in rotation to the disc 78 projecting radially with respect to the piston 74.
• the inlet part is therefore disengageably linked, via the disk 78 and the linings 80, to the driving shaft, the disk 78 with its friction linings 80 being suitable for being disengageably clamped between the piston 74 and the portion facing the internal face 92 of the transverse wall 58 forming a counter-piston.
• the disc 78 is therefore coupled elastically to the splined hub 70 and to the turbine wheel 64.
• the turbine wheel 64 is rotated by the impeller wheel thanks to the circulation of oil contained in the sealed casing and, after starting the vehicle, the locking clutch 54 allows, in order to '' avoid the phenomena of sliding between the turbine and impeller wheels, a direct connection (or bridging) of the driven shaft with the driving shaft and this by tightening the friction linings 80 and the disc 78 between the piston 74 and counter piston 58, 92 with direct drive of the shaft driven by the casing shell.
• the locking clutch 54 can be operated with a controlled slip.
• variable volume chain 82 is depressurized.
• This chamber 82 is therefore delimited externally by the disc 78 and the linings 80, the piston 74 and the wall 58 each having at their outer periphery a transverse plane friction face for the linings 80.
• the piston 74 is linked in rotation to the transverse wall 58 of the first half-shell by elastic tongues 94 of tangential orientation distributed regularly circumferentially, these tongues 94 allowing an axial movement of the piston 74.
• the tongues can be coupled to the transverse wall 58 by means of a metallic annular piece 96, integral with the transverse wall 58.
• fixing means for the coupling of the tongues 94 to the piston 74, fixing means of known design are used.
• the tongues 94 extend in the volume delimited radially by the friction linings 80 and the axis X-X of the assembly, that is to say in the variable-volume chamber 82.
• the central ring 76 is an independent component of the transverse wall 58 of the casing and it is interposed axially between the internal face 92 of the transverse wall 58 and a front transverse face 98 of the hub 70, the hub 70 extending radially outward by the flange 68.
• the free end section 100 of the shaft conduit 72 extends axially inside an internal radial bore 102 of the ring 76 with the interposition of a sealing gasket 104.
• the gasket dynamic seal 104 is here a segment, alternatively a seal.
• the central ring 76 is a plastic molded part which is attached to the inner radial periphery 103 of the piston 74.
• the ring 76 is in the form of an annular part produced by molding, here preferably made of plastic, which is axially delimited by a front transverse face 106 adjacent to the internal face 92 of the wall 58 of the casing and by a rear transverse face 108 adjacent to the front transverse face 98 of the flange 68 of the hub 70.
• the annular central ring 76 is also delimited radially inwardly by its bore 102 and outwardly by an outer cylindrical face 110.
• the central ring 76 is preferably produced by overmolding around the inner radial periphery 103 of the piston 74 so as to make it integral with the piston 74 and also to ensure a perfectly sealed connection between these two elements.
• the ring 76 is axially coupled to the piston 74 due to its shape and its overmolding around the inner radial periphery 103 with front 112 and rear 114 flanges which extend radially towards
• the rear cheek 114 here constitutes a stop 178 in the form of a flat ring which delimits axially towards the rear, that is to say towards the web 68, the axial sliding in leaktight manner of the ring-piston assembly 76, 74 by compared to the led tree 72.
• the stop 178 is therefore produced in accordance with the invention, in one piece with the ring 76, thus avoiding any direct contact, in particular a metal-to-metal friction, between the piston 74 and the web 68 located opposite.
• stop 178 can be envisaged, so by way of example the stop can be a ring discontinuous, ie a succession of sectors, which also makes it possible to reduce the material necessary for its production.
• stop 178 As will be understood, the production of the stop 178 by molding or overmolding, in particular of plastic material, offers great ease of implementation and great adaptability with the surrounding parts such as the piston or the crew. turbine wheel-hub and this whatever the radial or axial dimensions.
• the inner radial periphery 103 of the latter may include means such as teeth or slots 116 distributed angularly, notably regularly, around the axis X-X.
• the slots can be replaced by axial holes formed in the radially inner part 103 of the piston 74 and which are traversed by the molding material.
• the coupling means belong to the central ring 76.
• the transverse face 106 of the ring 76 has a series of passages 118 which put into communication a central chamber 120, produced in favor a central stamping 122 which extends axially towards the front of the transverse wall 68 of the casing, and the control chamber 82 delimited between the piston 64 and the wall 58.
• Each passage 118 is for example constituted by a groove opening radially at its two opposite ends, the front transverse face 106 of the ring 76 comprises a series of grooves 118 distributed angularly in a regular manner around the axis X-X.
• seal 104 which, in this first embodiment, is a segment mounted in a groove 124 machined in the outer radial periphery 126 of the section of free front end 100 of the driven shaft 72.
• the ring 76 with the piston 74 to which it is coupled, is thus free to slide in leaktight manner with respect to the driven shaft 72 in order to allow the bridging or dismounting operation of the clutch to be carried out.
• a series of grooves 128 is formed in the rear transverse face 108 of the central ring 76.
• the grooves 128 are for example distributed angularly in a regular manner and, like the grooves 118, they are advantageously produced by molding during the production of the ring 76.
• the production by plastic molding of the ring 76 allows a reduction in weight, facilitates the assembly operations insofar as it is coupled to the piston 74 and makes it possible to guarantee a perfect seal of the control chamber 82 thanks to the presence of a single seal 104, the transverse wall 58 being moreover of simpler design than in the prior art insofar as its central part 122 does not have an opening, the sealing of the assembly being here further improved, and where no particular machining is necessary.
• the gasket 104 which intervenes between the central ring 76 and the driven shaft 72 is a gasket which is mounted in a groove 124, which is here produced integrally by molding with the ring 76 while being formed in the internal bore 102 of the latter.
• the gasket 104 is a seal which is molded in the groove 124 or which is produced with the ring 76 according to a co-molding or co-extrusion technique.
• the groove 124 formed in the internal bore 102 of the central ring 76 receives a heel of a gasket 104 which is here an asymmetrical lip seal.
• the lining 104 then comprises a rear sealing lip of great axial length, and therefore flexible, which cooperates with the part opposite the outer periphery 126 of the free end section before the driven shaft 72, and it also has an axially shorter front lip, a third lip or intermediate rib being provided between the two rear and front lips.
• the gasket 104 has two symmetrical rear and front lips of great axial length, the heel being here, previously bent, fitted into the groove 124 or molded in the latter, if necessary during an operation of co molding of the lining 104 with the ring 76.
• the sealing lining 104 comprises a single rear lip which cooperates in leaktight manner with the radially outer periphery 126 of the free end section before the driven shaft 72 under the action of a ring-shaped clamping spring.
• the gasket 104 has, in cross section, a U-shaped section whose vertical lateral branch constitutes the mounting heel of the gasket 104 on the central ring 76 and whose rear vertical lateral branch extends in an additional internal radial groove formed in the internal bore 102 of the ring 76.
• the central part or central branch of the U-shaped lining cooperates in a sealed manner with the radially outer periphery 126 of the free end section before the driven shaft 72, holes or axial passages being formed in the annular branch to allow good operation of the seal.
• the seal 104 which, with its U-shaped profile, here surrounds a radially inner rib formed in the wall of the inner bore 102 of the central ring 76 for a better sealing resistance of the seal 104, one or more bores being formed at an angle in the central ring 76 in order to bring the interior of the seal 104 into a U-shaped connection with the lubrication grooves 128
• the central ring 76 is added by force fitting between the radially inner part 103 of the piston 74 and the driven shaft 72.
• the central ring 76 here has substantially the shape of an "L" comprising a vertical branch and a horizontal branch respectively.
• the vertical branch axially interposed between the rear lateral face of the piston 74 opposite the casing 58 and opposite the web 68, forms the stop 178 in the form of a flat ring which axially limits the rearward slide of the piston.
• the stop 178 has grooves 128 for lubrication.
• the stop 178 may consist of a continuous crown in a discontinuous variant, that is to say a succession of sectors.
• the stop 178 is made of synthetic material, loaded or not, said material being chosen according to the desired coefficient of friction.
• the horizontal branch is forcibly fitted into the radially inner part 103 of the piston 74 according to a method which makes it possible to ensure the seal between the radially outer periphery of the horizontal branch and the piston 74.
• the dynamic seal between the ring 76, here the radially inner periphery of the horizontal branch, and the driven shaft 72 is obtained by the interposition of a gasket 104, which can be indifferently associated with one or the other of these two elements.
• the ring 76 with its two branches of the "L" is made of plastic, for example by molding, and it may include a reinforcing ferrule 300, here metallic, which constitutes the radially outer periphery of the horizontal branch to allow 1 ' force fitting.
• the metallic ferrule 300 thus constitutes a reinforcement insert for the ring.
• the stop 178 is made in one piece with the central ring 76.
• the choice of material can optimize the friction coefficient of the vertical branch forming stop 178.
• the ferrule 300 has an inner radial orientation edge which is inserted into the horizontal branch of the ring 76 to ensure the axial connection between these two parts.
• the central ring 76 is a molded plastic part which is attached and coupled to the radially inner portion 103 of the piston 74, but it is here fixed by elastic interlocking.
• the radially inner part of the central ring 76 is of a design generally similar to that illustrated in FIG. 1, while its upper part, that is to say radially outer, 158 is shaped to conform to the shape of the radially inner part 103 of the piston 64 and allow its attachment and coupling.
• a radially outer and rear cheek 114 extends along the rear lateral face opposite the part 103, while an intermediate annular skirt 160 extends axially opposite the radially inner edge of the part 103.
• the rear cheek 114 forms, as in FIGS. 1 and 2, a stop 178 which limits axially towards the rear, that is to say towards the web 68, the sliding of the piston 74 coupled to the ring 76, by compared to the led tree 72.
• a hollowed out annular part 162 gives elasticity, radially inwards to the annular cheek 160 so as to allow its elastic deformation for fixing by interlocking or snap-fastening of the radially inner part 103 of the piston 74 behind a retaining heel 164 formed at the front axial free end edge of the skirt 160.
• the cheek 114 extends between additional stamped ribs 166 of the radially inner part 103 of the piston 74.
• an O-ring seal 170 is interposed between the radially inner edge of the part 103 of the piston 74 and the part opposite the skirt 160 of the ring. central 76, the seal 170 being here received in a complementary radial groove 172 produced by molding with the ring 76, in the radially outer periphery of its fixing skirt 160.
• the central ring 76 is advantageously produced by plastic molding.
• central ring 76 is a central guide ring for sliding the piston 74 and which is produced in the form of a component which is mounted axially free between the casing wall 58 and the hub 68, 70 of the turbine wheel.
• the radially lower part 103 of the piston 74 is slidably mounted axially relative to the central ring 76 for guiding the piston.
• the radially inner cylindrical edge 174 of the part 103 extends opposite, with a slight radial clearance, from a radially outer cylindrical bearing 176 of the central guide ring 76 which is delimited axially towards the rear by a stop 178 which is here produced integrally by molding with the ring 76 in the form of a radially outer veil against which can axially bear the portion opposite the rear transverse face of the radially inner portion 103 of the piston 74.
• the tightness of the chamber 82 is ensured by a seal 170 which is received in a groove 172 formed here in the central guide ring 76, the groove 172 being for example produced by molding with the ring 176.
• the ring 76 is therefore free axially with respect to the casing wall 58 and by relative to the radially inner section of the flange 68 of the hub 70 of the turbine wheel 64.
• FIG. 6 differs from that of FIG. 5 in that means are provided for radial centering of the central ring 76 relative to the casing wall 58.
• central ring 76 is extended radially inside and axially forwards by an annular centering heel.
• the external shape 182 of which is complementary to the internal shape of the elbow 184 which connects the central part 122 to the transverse wall 58 of the casing.
• the general design of the central ring 76 is generally identical to that illustrated notably in FIG. 5, that is to say that the radially inner part 103 of the piston 74 is axially free relative to the central guide ring 76 , with interposition of a seal 170.
• the central guide ring 76 is fixed to the cover or housing, and more particularly to the transverse wall 58 of the latter.
• the wall 58 comprises a series of hooking pins 200 with a chamfered head 202 which extend axially towards the rear from the internal face 92 of the wall 58 and each of which is received, by elastic interlocking, in a complementary hole 204 formed opposite and which opens axially towards the front in the front transverse face 106 of the central guide ring 76.
• the latter comprise, in the vicinity of their free end, elastically deformable hooking lips which are formed in the form of heels 206 received, without play axial, in the additional groove 208 delimited axially towards the rear by the head 202.
• FIG. 9 is generally identical to that of FIG. 8 with the exception of the axial dimension of the heels 206 which is less than that of the groove 208 so as to allow axial movement of the central ring 76 relative to the transverse wall 58.
• the pins 200 with their heads 202 are produced integrally with the wall 58.
• the variant embodiment shown in FIG. 10 differs from that shown in FIG. 8 by the nature of the holes 204 which are replaced by a single axial groove formed in the front transverse face 106 of the central ring 76 and which is delimited radially towards 1 inside in the vicinity of the front transverse face 106 by an elastically deformable heel 200 in the form of a continuous ring behind which the heads 202 of the pins 200 come to fit elastically.
• the central ring 76 for guiding the piston 74, 103 is fixed to the turbine wheel, and more particularly to the flange 68 of its hub 70.
• the central ring 76 has for this purpose a series of elastically deformable pins 210, angularly distributed in a regular manner around the axis XX and which extend axially rearward from the rear transverse face 108 of the central ring 76, each pin being fitted elastically into a complementary hole 212 formed opposite in the flange 68.
• the central ring 76 is fixed by gluing, respectively to the transverse wall 58 of the cover or to the flange 68 of the splined hub 70 so as to fix the ring 76 radially and axially with respect to the corresponding element.
• beads of glue 214 can be deposited in corresponding grooves formed in the front transverse face 106 respectively rear 108 of the central ring 76.
• the central ring 76 is centered radially with respect to the transverse wall 58 of the casing which for this purpose comprises a series of pins 200, without heads, similar to the pins 200 of FIG. 8 of which each is received in an additional hole 204 in the central part 76.
• the pins 200 thus ensure a radial centering of the ring 76 relative to the casing, but the ring 76 can move axially relative to the latter by sliding the pins 200 in the holes 204, the ring 76 being here also free axially by relative to the hub 68, 70 of the turbine wheel.
• the central ring 76 for guiding the piston 74 can be centered radially with respect to the turbine wheel with a possibility of axial displacement relative to the latter.
• the central ring 76 comprises a series of pins, without heads, similar to the pins 210 of FIG. 11 each of which is received in sliding in a complementary hole formed opposite 212 in the flange 68 of the grooved hub 70 .
• the central ring 76 is again fixed radially and axially relative to the transverse wall 58 according to a crimping technique.
• the body of the ring 76 has an annular groove 204, or else a counterbore of axial orientation which gives access to the interior to form heads 202 belonging to pins 200 which extend axially towards the rear from the wall 58 passing through holes 201 formed for this purpose in the front transverse face 106 of the central ring 76.
• the fixing of the central ring 76, here on the turbine hub 68, 70 can also be carried out by means of rivets 250 which pass through holes 252 provided for this purpose in the body of the central ring 76, the riveting operation being carried out for example from the outside to form the rivet heads 252.
• the rivets 250 can be replaced by screws 254 which are here screwed into the flange 68 of the hub 70.
• the seals 104 and the seal 70 may each be of different design and their arrangement also, the seal 104 being able to be indifferently associated with the shaft 72 or with the body of the central ring 76.
• the various embodiments of the invention with the stop 178 in one piece with the ring illustrate, on the one hand, the great freedom of design of the stop, in particular when it is produced by molding or overmolding with the main body of the ring and, on the other hand, the different possibilities offered for the arrangement of the ring, and in particular its radial centering and its axial coupling, as well as the different assembly methods which result therefrom.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
• Sealing Devices (AREA)
• Control Of Fluid Gearings (AREA)
• Sowing (AREA)
• Braking Arrangements (AREA)
• Press Drives And Press Lines (AREA)

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• 1999
  • 1999-11-17 FR FR9914467A patent/FR2801084B1/fr not_active Expired - Lifetime
• 2000
  • 2000-11-17 FR FR0014993A patent/FR2801085B1/fr not_active Expired - Lifetime
  • 2000-11-17 WO PCT/FR2000/003211 patent/WO2001036844A1/fr active Application Filing
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  • 2000-11-17 KR KR1020027006300A patent/KR100767331B1/ko active IP Right Grant
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  • 2000-11-17 WO PCT/FR2000/003212 patent/WO2001036845A1/fr active Application Filing
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