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
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
  • F16F15/123—Wound springs
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
  • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
  • F16D3/10—Couplings with means for varying the angular relationship of two coaxial shafts during motion
• • 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
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material

Definitions

• the present invention relates to an elastic coupling device between two aligned or substantially aligned shafts, respectively a driving shaft and a driven shaft, said device comprising elastic damping means with circumferential action mechanically interposed between the two shafts.
• Such a device is described for example in document FR-A-2 385 940.
• the coupling device is mounted between the crankshaft of the engine of a motor vehicle and the input shaft of a transmission , says drive shaft.
• This device comprises a solid hub with internal splines fitted on the transmission shaft and an external annular web which is connected to the crankshaft by a drive plate.
• the hub is directed axially in the opposite direction to the crankshaft.
• Two guide washers arranged on either side of the web, are fixed to the hub.
• Springs mounted in housings facing each other in the guide washers and the web, resiliently couple the web to the guide washers.
• the object of the present invention is to overcome these drawbacks in a simple and economical manner.
• an elastic coupling device of the above-mentioned type is characterized in that the drive plate is integral in rotation with one of the guide washers, called the first guide washer, while the web is integral , possibly after taking up a circumferential clearance, of the hub, in that the hub is directed axially towards the first washer guide, in that the first guide washer carries its external periphery for fixing the other guide washer, called the second guide washer and in that said device is thicker at its external periphery than at its internal periphery.
• the axial size is considerably reduced.
• the web is radially less bulky and therefore more economical.
• the first washer then carries rivets axially passing through said crown and said mass in order to fix the second guide washer.
• the starter ring and the inertia mass therefore form a spacer between the guide washers.
• the guide washers are attached to their external periphery and the rivets pass through the starter ring, the contiguous parts of the guide washers and the flywheel, so that the guide washers are pinched between the flywheel and the starter ring gear.
• the rivets can be replaced by fasteners of the screw-nut type or any other means of assembly.
• the guide washers are identical at their external periphery and are faced by being joined together by a weld bead.
• One of the washers carries the flywheel mass and the other the starter ring.
• the elastic coupling device makes it possible to obtain additional functions, in particular starting, and this in a simple and economical manner.
• This device can have the desired mass for good filtration of vibrations.
• the second guide washer is shorter radially than the first guide washer.
• the central opening (or internal bore) of the second guide washer has a diameter greater than that of the first guide washer. Thanks to this, it is possible to further reduce the axial size of the elastic coupling device, the web being able to have a tortuous shape and to present internally, in line with the second guide washer, a first internal portion offset axially with respect to a second main portion located between the two guide washers.
• the first guide washer is integral with the drive plate which saves a part.
• the first guide washer can be fixed using fixing screws, the heads of which are located axially between this first guide washer and the web.
• the veil then has holes for access to the heads of the screws and for screwing them using a tool, such as a screwdriver.
• the first guide washer surrounds the drive plate and is connected thereto by elastic tongues in the axial direction.
• the drive plate is then reduced to a simple washer and that the first guide washer is linked in rotation to the drive plate while being able to move axially relative to the latter thanks to the tangential tongues.
• This damping can also be obtained by making the first guide washer flexible, for example by providing the latter with holes.
• the hub is integrally with the web, gear means with circumferential play which can be provided between the hub and the web.
• the hub is separate from the web.
• the free end of the hub can be chamfered to penetrate the interior of the drive shaft.
• the elastic coupling device forms a unitary module of low axial dimensions that can be tested and dynamically balanced in advance before being fixed to the drive shaft.
• the first guide washer has, on the one hand, at its internal periphery, first means for its direct or indirect fixing on the driving shaft and, on the other hand, radially beyond said first means, second fixing means for fixing the second guide washer.
• FIG. 2 is a sectional view along line 2-2 of Figure 3 for a second embodiment
• FIG. 3 is a view along arrow 3 of Figure 2 with local cutaway of the inertia mass and the second guide washer;
• Figures 4 and 5 are views similar to Figures 2 and 3 for a third embodiment, the left part of Figure 5 being a sectional view without the inertia mass, the starter ring being shown in dotted lines;
• FIGS 6 and 7 are views similar to Figures 2 and 3 for a fourth embodiment with, in Figure 7, two local cutouts to partially show the veil, the tabs and the windows;
• - Figures 8 and 9 are views similar to Figures 2 and 3 with in Figure 9 two local cutouts to show the web and the first guide washer.
• This device is intended to couple two shafts 100, 200 substantially aligned, namely a driving shaft 100 and a driving shaft 200 ( Figure 1).
• the driving shaft 100 is here the crankshaft of the vehicle combustion engine
• the driven shaft 200 is the input shaft of a transmission here with variable pulleys not shown.
• This device comprises a drive plate 1 fixed at its internal periphery at the end of the crankshaft, here by means of screws. fixing 4, the heads 5 of which each have an imprint (not referenced) for a screwing tool.
• the crankshaft 100 has a cylindrical centering seat 7, of axial orientation, for intimate contact with the internal periphery of the plate 1. It will be noted that the crankshaft is hollowed out centrally and has at its free end a chamfer 8.
• the elastic and rotary coupling device also includes two guide washers 1.9 ( Figures 1 to 3, 8 and 9) 1.3 ( Figures 4 and 5) - 2.9 ( Figures 6 and 7) arranged on one side and on the other side of a web 10, the guide washer 1-2 being called the first guide washer and the guide washer 3-9, called the second guide washer.
• Elastic circumferential action means 11 ( Figures 1 to 3, 6, 7, 8 and 9) -110 ( Figures 4 and 5) are housed in housings 12,13 ( Figures 1 to 3, 6, 7, 8 and 9 ) - 120,130 ( Figures 4 and 5) made opposite each other in the web 10 and the guide washers 1.9 - 1.3 - 2.9. These elastic means 11, 110 therefore intervene between the web 10 and the guide washers 1.9 - 1.3 - 2.9 by being mechanically interposed between said guide washers and the web.
• the elastic means can consist of a stack of Belleville springs, as described in document FR-A-2 385 940 to which reference may be made for more details.
• the elastic means 11, 110 consist of coil springs.
• the springs 11 are coil springs of short length.
• these are curved springs 110 of great circumferential length, which can be pre-bent.
• the elastic means may comprise blocks of elastomer.
• the elastic means 11, 110 are all housed here without play in the housings 13, 130 of the guide washers.
• the elastic means 11 are housed, for some of them, without play in the housings 12 of the web 10 and, for others, with play circumferential in the housings 12, for a stepwise intervention of said elastic means and better filtration of vibrations.
• these friction means comprise, as described in the aforementioned document FR-A-2 494 795, a first application washer 15 integral in rotation with the second guide washer 9 and inducing friction against the web 10 (on the face thereof facing the second guide washer 3,9).
• An axial action elastic washer 16, here a Belleville washer, as a variant a wavy washer, is inserted under prestress between the second guide washer 3,9 and the first application washer 15.
• This application washer 15 has projections , here in the form of cylindrical pins (not referenced), engaged in holes (not referenced) of the second guide washer for connection in rotation, with axial mobility, from the first application washer 15 to the second guide washer 3 , 9.
• the first application washer is here made of plastic and rubs directly against the web 10. It is loaded for example with glass fibers. Opposite the first application washer 15, on the other side of the web 10, is installed a second friction washer 25 here identical in shape to the first application washer 15. The washer 25 is inserted between the first guide washer 1-2 and the web 10. This washer 25 rubs against the web 10 (on the face of the latter facing the first guide washer), and is linked in rotation to the first guide washer by cylindrical pins it has, said pins being engaged in holes in the first guide washer.
• the elastic washer 16 is supported on the second guide washer to urge the first application washer 15, in the direction of the web 10, and tighten by reaction the second friction washer 25 between the first guide washer 1, linked in the manner described below to the second guide washer, to induce friction in contact with the web 10.
• the alternative housings may consist of stampings 130 produced in the guide washers 1,3 and in notches 120 open radially outwards produced in the web 10. These notches 120 are delimited by radial lugs 121 with circumferential fingers 122 engaging in a recess of a support cup 123 serving to support the curved springs 110. Shoes 124 are hooked by clipping on each one a turn of the spring 110 and are interposed between the outer periphery of the springs 110 and the inner periphery of the stampings 130 of generally semicircular shape, in order to reduce friction as described in document US-A-2,002,115. It will be noted that the cups 123 are extended at their outer periphery to form a pad retaining the end turns of the springs 110, two in number here and extending generally over 180 °.
• the guide washers 1,3 are identical at their outer periphery.
• the washers are facing by their free edge and are welded together as described in document FR-A-2 411 999.
• stampings 130 it is thus formed, thanks to the stampings 130, a torus at the outer periphery of the guide washers 1.3 of the same thickness. This toroid envelops the springs 110 for the most part. More precisely the stampings 130 are extended at their internal periphery by transverse parts belonging to the main parts of the guide washers. Sealing washers 40 are pinched between the web 10 and respectively the first 15 and the second 25 friction washers. The washers 40 are inclined beyond the washers 15.25 to bear on the internal faces, facing the web 10, respectively of the washers 1 and 3. It is thus defined a sealed cavity delimited by the stampings 130 and closed to the inside by the sealing washers.
• This cavity is filled with a pasty or viscous agent such as grease in order to lubricate the springs 110, which thus work in good conditions and are not likely to become embedded in the stampings 130 thanks to the pads 124, which can be replaced. by pieces in the shape of a chute.
• a pasty or viscous agent such as grease
• the guide washers 1,3 are flattened to form flat parallel parts 126 and supports at the ends of the springs 110 mounted without play in the stampings 130, interrupted by the flat parts 126, and in the notches 120. This takes advantage of the friction means 14, the web 10 penetrating by its legs 121 into the aforementioned cavity.
• the washers 15.25 are notched to form a centering shoulder for the sealing washer 40 concerned.
• the friction means 14 can have another shape, however it will be noted that here the friction means are economical because they use, on the one hand, a reduced number of washers 15,16,25 and, on the other hand , to friction washers 25 and to application 15 identical to their thickness. It also follows that the two guide washers 1.9 - 1.3 - 2-9 have identical holes for the pins of the washers 15.25.
• the elastic coupling device comprises a drive plate 1 for connection in rotation of said device to the driving shaft (here the crankshaft 100) and a hub 17 for connection in rotation of said device to the driven shaft (here the input tree 200). Between the plate 1 and the hub 17 intervene two coaxial parts mounted movable angularly with respect to each other against elastic means 11,110 with circumferential action and friction means 14 with axial action.
• One of the parts includes the guide washers 1.9 - 2.9 - 1.3 and the other part of the web 10.
• Figure 1 we see in XX the axis of rotation of the device which coincides with the 'axis of the shafts 100,200 substantially aligned, taking into account manufacturing and assembly tolerances.
• the invention proposes that the first guide washer 1,2 be secured in rotation to the drive plate and that the web 10 is secured, possibly after taking up a circumferential clearance, from the hub 17 directed axially towards the first guide washer 1 forming a drive plate.
• the first guide washer 1 forms a single piece with the drive plate 1.
• the first guide washer 1 carries here, with fixing, the second guide washer 3.9, which is a simple form part, as well as the web 1 0 and the first guide washer 1.
• the guide washers 1,9, the web 10 and the hub 17 are metal parts, the web 10 and the guide washers 1,9 being obtained in a simple manner by stamping. It is the same in the other figures.
• the hub 17 may be in one piece with the web 10, the internal periphery of which is then shaped as a previously grooved sleeve. Here the web 10 is added by crimping at the end of the hub 17.
• the hub 17 is less hard than the web 10 and has an end stepped in diameter on the side opposite to the first guide washer 1.
• the web 10 is grooved at its internal periphery and is forcibly engaged on the reduced diameter portion of the hub 17 until it abuts against
• the material is made to flow from the end of the hub 17 to form a second shoulder and axially wedge the web 10 in the other direction.
• This veil 10 is fixed in rotation on the hub 17 thanks to the grooves that it cuts therein and to its grooves engaged in said grooves.
• the web 1 0 is welded at the end of the hub 17.
• the other end of the hub 17 is connected to the zone for fixing the web 10 by a portion of frustoconical shape.
• the hub 17 is thicker at its axial end adjacent to the web 10, than at its other axial end adjacent to the crankshaft.
• the heads of the fixing screws 4 extend radially above the hub 17.
• the hub 17 thus penetrates slightly inside the crankshaft 100, more specifically inside the aforementioned central recess 6 of said crankshaft 100 serving as a receptacle at the free end of the input shaft 200 for the benefit of a reduction of axial dimensions.
• the hub 17 extends partially radially below the heads 5 of the fixing screws 4 and penetrates inside the chamfer 8 of the crankshaft 100, the frustoconical portion 18 of the hub 17 being parallel to said chamfer 8.
• said hub is thinner so that it penetrates more into the recess 6. In this FIG. 1, the web 10 is thus integral while rotating only axially with the hub 17.
• the web 10 may be axially integral with the hub 17 optionally after taking up an axial clearance and be integral in rotation with the hub 17 after taking up a circumferential clearance.
• the web 10 has a female toothing at its internal periphery, while the hub has at its external periphery a male teeth.
• Each set of teeth has an alternation of teeth and notches, advantageously of trapezoidal shape.
• the tooth of the male teeth penetrates with circumferential play in the notches of the female teeth and vice versa for formation of gear means with circumferential play.
• Notches are formed opposite in the male and female teeth for housing elastic members of low stiffness for filtering vibrations in the idle range of the vehicle engine.
• the elastic members most often consist of coil springs with the interposition of support plates, with a dihedral-shaped dorsal face, between the circumferential ends of the springs and notches as visible in FIG. 3 of the document FR-A-2 496 210 cited above, the content of which is considered to be incorporated into the present invention.
• the male toothing is formed thanks to an extra thickness so that it is possible to delimit the male toothing laterally by two washers added for example by welding, riveting or crimping on the hub. These washers thus plug the axial ends of the notches of the male toothing and therefore constitute axial stops for the teeth of the female toothing of the web 10 so that the web 10 is connected axially to the hub 17.
• a module can be formed in the manner described below.
• the first guide washer 1 has holes 36 at its internal periphery for passage of the threaded part of the screws 4. After mounting on the crankshaft 100 the first guide washer 1 is interposed tightly between the crankshaft and the heads 5 of the screws fixing 4 distributed circularly in a regular manner.
• the first guide washer 1, forming a carrier element is fixed using studs or bolts, rivets or the like to the crankshaft.
• the first guide washer 1,2 has, at its internal periphery, first fixing means for fixing it to the driving shaft (here the holes 36 for the passage of the screws 4), either directly or indirectly (FIGS. 6 and 7).
• the first guide washer 1,2 carries the second guide washer 3,9 for fixing. More precisely, the first guide washer carries fixing at its outer periphery the other guide washer.
• the two guide washers 1.9 can be connected and fixed together using posts passing through the notches of the web 10 as described in document FR-A-2 494
• the notches can affect the lower edge of the windows.
• the fixing is carried out using assembly rivets 20 connecting the guide washers 1.9 to each other.
• rivets 20 therefore pass through axially aligned openings of the guide washers as well as openings made in axial coincidence in a starter ring 21, attached to the first guide washer 1, and in a flywheel mass 22, attached to the second guide washer 9.
• the starter ring 21 and the flywheel mass 22 therefore form a spacer between the two guide washers 1 , 9, while projecting radially outwards relative to said washers 1.9.
• the first guide washer 1 has at its external periphery a portion 23 of transverse orientation offset axially towards the outside with respect to the main part of the first guide washer 1, and therefore in the opposite direction by relative to the second guide washer 9.
• the starter ring 21 is attached to the portion 23, the height of which depends on the ring 21.
• the mass of inertia 22 has, at its internal periphery, projections in the form of legs directed radially inwards to cooperate with notches produced at the external periphery of the web 10.
• the projections penetrate into circumferential play in the notches.
• the relative angular movement between the guide washers 1,9 and the web 10 is limited by engaging the projections with the lateral edges concerned of the notches.
• this limitation is achieved by coming into contiguous turns of the springs 11.
• the starter ring 21 in FIG. 1 is offset axially with respect to the web 10, so that the mass of inertia 22 can mesh with clearance with the web 10.
• the mass of inertia 22 s extends partially radially above the second guide washer 9.
• This mass 22 projects axially outwards with respect to this second washer 9 and this by a value corresponding to the thickness of the head of the rivet 20.
• the elastic coupling device is therefore thicker at its external periphery than at its internal periphery and comprises second fixing means 20, 21, 22 distinct from the first fixing means for forming a unitary module, which can be handled and transported.
• This device has masses (the crown 21 and the mass 22), radially beyond the elastic means 11, 110 for increasing its inertia.
• inertia 22 is less hard than the starter ring 21 so that there is no need to harden the web 10.
• the rings 41, 42 of the guide washers are therefore pinched between the parts 21, 22 each having a countersink (not referenced) for housing the heads and feet of the rivets 20 respectively.
• the rings 41, 42 are offset axially with respect to the main part of the associated guide washers 1,2 - 9 and extend to the external periphery of said washers.
• the ring 41 of the guide washer 1,2 has tabs 43 projecting radially inward.
• the legs are obtained by cutting and folding from the first guide washer 1,2 with the appearance of a slot 44.
• the legs 43 extend in the plane of the web 10 and are intended to cooperate with the edges of notches , here in the form of notches 143, which has the web 10 at its outer periphery to limit the relative angular movement between the web 10 and the guide washers 1,2 - 9.
• first guide washer 1,2 is thicker than the second guide washer 9 because this guide washer carries the second guide washer 9 at its outer periphery.
• the guide washers 1,3 have the same thickness for manufacturing reasons because they are identical at their external periphery, the first guide washer 1 carrying the second guide washer thanks to a cord of continuous welding (not referenced).
• the second fastening means between the two guide washers can therefore consist of welding or use fasteners 20 in the form of rivets or alternatively of bolts (screw-nut system) or any other means.
• the starter ring 21 extends radially above the first guide washer 1 as fixed to the latter by a weld bead not referenced.
• the coupling device comprises radially four stages, namely, going from the external periphery to the internal periphery of the elastic coupling device, namely, a first stage comprising the rivets 20 or the welds or any other means of fixing, the crown 21 (intended to be driven by the starter of the vehicle), and the mass of inertia 22, a second stage comprising the elastic means with circumferential action 11,110, a third stage comprising the friction means 15,25,16 and a fourth stage comprising the first means for fixing the first guide washer 1. Thanks to this arrangement, the available space is best occupied while having a maximum of functions and being axially compact.
• At least one of the washers 25, 15 may be replaced by a friction washer glued to a metal washer comprising drive tabs penetrating into holes in the guide washer concerned.
• the web 10 has at its internal periphery a portion 24 of transverse orientation offset axially with respect to the main part of the web 10 located between the two guide washers 1.9.
• the portion 24 extends radially below the friction means 14.
• This internal portion 24 is offset axially in the direction of the second guide washer 3.9, that is to say axially in the opposite direction relative to the external portion 23 of the first guide washer 1.
• This axial offset is made possible thanks to the configuration of the second guide washer 3,9 which is shorter than the first guide washer 1.
• the second guide washer 3, 9 surrounds the internal portion 24 in all cases. This internal position enters the internal central bore of the second guide washer 3, 9.
• the internal bore of the second guide washer 3.9 (FIGS. 1 to 5 and 8.9) has a diameter greater than that of the internal bore of the first guide washer 1.2 which, thus radially, extends inwardly projecting from the second guide washer 3.9.
• the portion 24 of the web can penetrate the internal bore of the second guide washer while being offset axially in the direction of said bore.
• the axial size is not increased and the heads 5 of the fixing screws can be arranged axially between the first guide washer 1 and the internal portion 24 of the web 10.
• This portion 24 is perforated at 26 for access to the heads of screw.
• the hole 26 may be of diameter greater than that of the head 5 of the screws 4 or be less than the diameter of the head 5 of the screws 4 as shown in the figure.
• the first guide washer 1 facilitates the assembly of the module-forming coupling device. Indeed, the mounting of the device is carried out by laying the first guide washer 1 flat, then by axial stacking of the other components on the first guide washer 1, the second guide washer closing the assembly.
• the present invention is not limited to the embodiment described.
• the first guide washer 2 is separate from the drive plate 1 fixed with the screws 4 on the crankshaft of the vehicle engine (not shown) as in Figure 1, the web 10 therefore having holes 26 as in the other figures.
• the drive plate 1 is simplified and is surrounded by the guide washer 2, linked in rotation to the drive washer by axially elastic tongues 50 and allowing an axial displacement of the first guide washer 2 relative to the plate drive. It is thus possible to filter the axial vibrations generated by the axial oscillations of the crankshaft.
• each tongue 50 is fixed by means of two holes for the passage of the screws 4, for this a hollow rivet
• Each rivet bears against one of the faces of the plate 1 and is folded down, at the level of the other face of the plate 1, in contact with the tongue 5 to fix the latter.
• the tongues 50 are therefore in contact with the face of the drive plate facing the web 10.
• the plate 1 has tabs 160 at its outer periphery to limit the axial movement of the tongues 50 before mounting the coupling device on the crankshaft.
• the legs 160 are obtained by cutting and folding and protrude axially in the direction opposite to the web 10. These legs 160 are intended to cooperate with the internal periphery of the guide washer 2, more precisely with the face of the latter facing the opposite veil 10.
• the legs 160 belong to a bayonet-type assembly 161 existing between the internal periphery of the first guide washer 2 and the external periphery of the plate 1. Passages exist in the washer 2 and after introduction of the legs 160 in the passages a rotation is carried out, the legs 160 being opposite the legs 170 of the plate 1.
• the washer 2 before fixing to the crankshaft, is wedged axially between lugs 160, 170 of the plate 1.
• the lugs 170 limit the movement of the tongues.
• vibrations can be filtered by making the first guide washer 1 flexible as shown in FIGS. 8 and 9.
• the first guide washer then has holes 180 of trapezoidal shape below the windows 13.
• the other references being identical to those of Figures 2 and 3.
• the first guide washer 1 can carry the starter ring 21 and for this purpose comprise, at its external periphery, a ring directed axially towards the second guide washer 9.
• the ring 21 is then fitted on the ring which can also carry a ignition target.
• the ignition target can be produced on the mass of inertia 22 whose external diameter is equal to that of the crown 21.
• the crown 21 and the mass 22 can be combined.
• the presence of the mass 22 may, in certain cases, not be necessary.
• the first guide washer 1 can carry the crown 21 in the aforementioned manner and the rivets 10 are replaced by balusters of the type of those described in document FR-A-2 494 795.
• the second fixing means may comprise a crown which extends continuously from the periphery of one of the guide washers to the other as described in document FR-A-2 411 999.
• This ring extends for example radially above the web 10 from the first guide washer 1, the second washer being fixed at the end of the ring, for example by crimping, or welding as described in this document FR- A-2 411 999.
• the starter ring can be fitted on the fixing ring.
• the rivets 20 can be replaced by bolts.
• the transmission casing can come very close to the coupling device according to the invention, more precisely very close to line D in the figure.
• the first fixing means comprise the tongues.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• Acoustics & Sound (AREA)
• Aviation & Aerospace Engineering (AREA)
• Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
• Mechanical Operated Clutches (AREA)
• Bolts, Nuts, And Washers (AREA)
• Gears, Cams (AREA)

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• 1997
  • 1997-06-25 FR FR9708251A patent/FR2762058B1/fr not_active Expired - Lifetime
• 1998
  • 1998-04-10 US US09/194,928 patent/US6186898B1/en not_active Expired - Lifetime
  • 1998-04-10 BR BR9804819A patent/BR9804819A/pt not_active IP Right Cessation
  • 1998-04-10 WO PCT/FR1998/000733 patent/WO1998045616A1/fr not_active Application Discontinuation
  • 1998-04-10 JP JP54247198A patent/JP4612124B2/ja not_active Expired - Lifetime
  • 1998-04-10 EP EP98920610A patent/EP0910756A1/de not_active Withdrawn
  • 1998-04-10 DE DE19880665T patent/DE19880665B4/de not_active Expired - Lifetime

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