FR2796682A1 - Clutch coupling with a driver component, a driven flywheel component and a contra rotated ramp disk mounting device for enabling engagement and disengagement - Google Patents

Abstract

A clutch has an axial driver flange (15,23) having an axial extension (17), directed towards an adjacent flywheel (31), and formed with a toothed profile (19) of which at least one tooth (20) can engage with a gap (52) in a corresponding toothed profile on a take-up ring (25) to provide an effective rotational coupling with the driven flywheel, which may form part of a fluid torque converter. The teeth (20) on the driver (23) and tooth-gaps (52) on the take-up ring (25) are formed with wedge shaped faces. The axial extension movement required for engagement of the corresponding toothed surfaces is provided by flexing of the flange (15,23) around the area of a bend (16). Two radial moveable claws (59) may be provided to replace a pair of diametrically opposed teeth on the driver flange in order to retain the fly wheel in position by engaging with depressions (63) in the take up ring (25,27) while the unit is under radial force. A mounting device (70) is provided on the the axial driver flange (15,23) to depress the teeth (20) radially inwards while the take-up ring (25) slides on to the driver, without need for application of axial force; coupling completed, the mounting device is released and radial forces then bind the two clutch components together. The mounting device (70) may take the form of e.g. : (a) A screw tightened clamp (71) with a flexible band (72) around the axial extension (17). (b) A flexible pressure-tube (78) having a connection (79) which allows the ring (25,27) to be compressed, by pressure applied from a source (80), in order to enable coupling or alternatively to disengage the radial toothed connection; such a pressure tube (78) may be provided with a protective U-shaped cover (83). (c) Other forms of mounting device, including a slidable compression ring (84) with a coned inner surface; and a circular spring collar device (87) with open ends which can be forced apart to release the compressive force. An Independent claim is included for a mounting device (70) having a pair of essentially identical annular disks (110;112) each formed with a set of uni-directional ramp surfaces (126;134) on its inner edge, and which are rotatably positioned on the axial extension (17). Each disk has a ramp corresponding to each of the tongues (116) carrying teeth (19). The two disks are arranged in co-axial contact and with their ramp surfaces opposite handed, so that contra-rotation of the disks by an actuator simultaneously urges a ramp on each disk to slide onto, or off each tongue. Engagement of the ramps with the tongues causes them to bend axially inwards, releasing the meshing force on the toothed coupling.

Description

The present invention relates to a clutch installation comprising a mass of inertia on the side of the drive, cooperating solidarily in rotation with a drive member provided on the drive means.

According to document DE-41 22 135-A1, it is known, as appears in FIG. 1, a clutch installation in the form of a hydrodynamic torque converter in which a mass of inertia, situated on the side of the drive, is formed by a radial flange; it extends radially outwardly from a bearing journal housed in an attachment of the gearbox housing being integrally connected to the pump shell of a pump rotor. The turbine rotor forms an output mass of inertia with the output shaft.

The bearing journal, radially inner, is provided with an internal toothing taken in the outer den ture of a drive shaft. This drive shaft has at its other end an external teeth by which it meshes with a corresponding internal toothing of the crankshaft of an internal combustion engine. This drive shaft thus serves as a drive member for driving the mass of inertia on the side of the drive.

Although this drive shaft thus makes a solidarity connection in rotation between the drive (motor) and the mass of inertia, the clearance in the toothing does not prevent that, the teeth do not begin to beat- under the effect of torsional oscillations.

Another difficulty of this known clutch installation is that neither the fixing of the trunnion nor the drive shaft guarantee the axial fixing of the mass of inertia on the side of the drive and thus the assembly. of the torque converter on the vile brequin. The torque converter can cause axial movements that the gearbox can not absorb and cause damage to the gearbox.

To avoid these difficulties, it is usual, as appears in Figure 1 of DE 32 22 119 C1, to screw an elastic plate in the axial direction at the free end of the crankshaft of the drive means; this plate is itself screwed in its radial zone outside the mass of inertia turned towards the drive of the clutch installation; in this case it is again a hydrodynamic torque converter. This solution is however complicated because to screw the flexible plate to the mass of inertia, it is necessary to fix tapped blocks distributed at intervals determined at the periphery and which serve to receive the screws. In addition, the screwing of the flexible plate with the corresponding mass of inertia of the clutch installation is particularly difficult because of the very small space available and access difficulties.

The object of the present invention is to develop a clutch installation which is fixed without requiring any particular clearance in the peripheral direction on a drive means with mounting means as small as possible.

To this end, the invention relates to a clutch installation of the type defined above, characterized in that the mass of inertia comprises a receiving member facing the drive member, said receiving member being provided with a toothing and the drive member comprises an axial extension whose side also facing the receiving member also has a toothing of which at least one tooth enters the interval between each time two teeth of the teeth of the receiving member, the teeth of at least one of the two teeth being prestressed ra dial relative to the other respective teeth.

As the drive member attached to the drive means, for example the crankshaft of an internal combustion engine, is made with an axial extension and at least one tooth of a toothing fits in a corresponding toothing. a drive member fixed to the mass of inertia, a link is made integral in rotation between the receiving member and the drive member and thus between the drive member and the mass of inertia . As at least one of the two sets of teeth is radially preloaded with respect to the respective other set of teeth, this connection between the drive member and the receiving member has practically no radial play. For a radial pre-tension, for example on the axial extension of the drive member, with at least one tooth, this tooth engages as deeply as possible in the toothing of the receiving member to enable a connection to be made by the force with the teeth of the receiving member.

This works particularly well if the flanks of the two toothings have wedge-shaped surfaces so that for example each tooth of the toothing of the drive member penetrates radially as a wedge between each time two teeth of the toothing of the organ reception and hangs for some depth of penetration. With such a connection, between the teeth of the drive member and the receiving member there will be no play so that even for strong torsional oscillations there will be no beat. In addition, because of the locking described above teeth of the drive member of the toothing of the receiving member, the following advantage is obtained in the transmission of the torque: because of the torque, a force peri phérique acts on the teeth. As these meshes any time without play, each tooth is supported in the peripheral direction so that the bottom of the tooth is not loaded by a bending moment. Instead, the tooth must be supported only with respect to the transverse forces so that the stresses are limited. This advantage is particularly important if the drive member can support the teeth of the toothing on teeth of the receiving member, for example in the form of a ring and thus having a shape-stable toothing in the peripheral direction.

The advantage is particularly important if the annular receiving member surrounds the drive member and has an internal toothing so that the radial prestressing in the toothing of the drive member is also supported at rotation by the centrifugal force. while the ring which surrounds the bottom of the teeth of the toothing of the receiving member radially supports the teeth of the toothing of the drive member.

The toothing of the drive member is associated with an axial fixing or locking means, for example in the form of a claw with a radial support, and this latter penetrates into a radial cavity of the receiving member. If this radial support is wedge-shaped, a clamping connection is made with the radial cavity of suitable shape provided in the receiving member.

As described above, the toothing of the drive member is radially preloaded with respect to the receiving member. To make a connection by engagement between the drive member and the receiving member, when the latter is engaged on the drive member, a mounting device acting on the drive member is tensioned. drive to deform under pretension the axial extension to make a connection by catch between the drive member and the receiving member, practically without axial effort. As soon as this connection is established, the action of the mounting device is eliminated; this can then be removed completely from the drive member or in the case where the mounting device remains on the drive member, the latter is loosened so that it no longer has effect on the teeth of the drive member.

Different embodiments of such devices are discussed below.

The means consisting in using the axial extension of the drive member as a free axial end serving as a bearing surface for the mounting device, makes it possible, under the effect of levers of this free end with respect to the other free end. connected to the radial flange of the drive member, all that is required is a relatively weak mounting force exerted by the mounting device in the radial direction; this mounting force is less than the prestressing force acting in the direction of the den on the receiving member. Such advantageous conditions for the mounting force in relation to the prestressing force make it possible to choose the latter sufficiently high so that the only friction force inside the toothing gives an axial blocking of the movement between the body of the device. drive and the receiving member. This makes it possible to omit any additional axial fastening means.

Since at the free end of the axial extension axial fixing is provided for the connection between the driving member and the receiving member, this axial attachment can penetrate the axial extension range of the teeth of the receiving member which gives a very small footprint.

The radial flange of the drive member may be provided with an elastic strap. To increase again this axial elasticity is to realize this flange with an elastic spring effect to better compensate the movements of nutation of the crankshaft. Such an elastic spring effect applied to the flange may have an even greater effect if it is provided with a damping means; this is preferably an elastomer which partially fills the free space, radial, created by the coil of the spring. With such a damping means can be damped oscillations previously triggered by the movements of nutation of the crankshaft at the spring oscillations.

The receiving member may, according to the example of the drive member, comprise an elastic axial flange and preferably the axial elasticity is applied in connection with the crankcase and the crankcase, especially if the axial elastic flange the receiving member has an elastic spring effect. In addition, if the axial extension of the receiving member is made at its free end, such as a receiving surface for the mounting device, for acceptable mounting forces, high radial prestressing can be achieved between two teeth of the drive member and the receiving member. As already mentioned, this makes it possible, on the one hand, to make a connection without flapping between the teeth and, on the other hand, to eliminate any additional axial protection.

To have the required clutch behavior in such a clutch installation, it is necessary that the teeth, which interpenetrate and put themselves reciprocally prt, are applied against each other with a relatively large radial pre-stress or that the parts used are sufficiently rigid. But this means that to engage or disengage must exert a relatively large radial force on at least one of the teeth. This is why the present invention proposes, according to another characteristic, a mounting device which is able, in such clutch systems, to generate the necessary radial forces.

The invention proposes in particular a mounting device for making (or opening) a catch of the meshing type between the teeth of two components, the teeth being penetrated at least radially and the toothing radially inside being prestressed radially. outwards against the toothing located radially outwardly, and the components of the toothing located radially inward being deformable elastically, radially, at least at the level of the toothing.

The mounting device comprises at least one annular element mounted or rotatably mounted on the components of the toothing located radially on the inside. This annular element comprises at least one deformation which, during the rotation of an annular element around the axis of rotation, makes it possible to modify the radial positioning of the components of the internal radial toothing at the level of this internal radial toothing.

This mounting device is preferably designed so that the deformation is associated with each tooth or each time with a group of teeth of the inner radial toothing and has deformation ramps extending in the circumferential direction directed radially towards the tooth. interior and having a variable distance from the axis of rotation in the peripheral direction. These deformation ramps make it possible to simply convert a rotation movement into a radial displacement and in particular the angle of inclination of the deformation ramps or of the deformation ramp define the conversion ratio and thus the rotational force that it must be applied.

For example, it is possible to provide in the peripheral direction a zone of minimum distance from the deformation ramp with respect to the axis of rotation and / or a zone of maximum distance from the deformation ramp with respect to the axis of rotation. continue with a zone of almost constant distance from the axis of rotation. The approximately constant distance can also charge here a short area extending substantially tangentially with respect to a radial line.

The mounting device according to the invention preferably comprises two annular elements.

These two annular elements then comprise deformation ramps offset with respect to each other and each tooth or group of teeth is associated with a pair formed by a deformation ramp of each annular element.

Such a mounting device is provided for opening a clutch engagement by rotating the two annular members about the axis of rotation in opposite directions.

It is advantageous that the two annular elements are preloaded respectively to rotate in the circumferential direction, preferably in a relative rotational position in which the clutch engagement is made between the teeth.

In order to make or open the engaged state by means of the mounting device according to the invention, at least one annular element comprises a deformation of grip for one or another which makes it possible to turn at least one annular element around the axis. of rotation.

As the mounting device according to the invention is very simple, that is to say very cheap and very light, at least one annular element is rotated on that of the components provided with the inner radial toothing. This means that at least one annular element remains permanently on this determined component even when the engaged state is achieved.

The present invention further relates to a clutch installation for producing a rotational clutch between two assemblies rotating about an axis of rotation, said clutch system comprising a first component with a first toothing associated with this assembly and the another assembly comprising a second component with a set of teeth, the two teeth interpenetrating radially with a radial prestress in the meshing. Such a clutch installation is preferably provided with a mounting device according to the invention.

As already mentioned above, the different components used for clutching in such clutch installations must satisfy two opposite conditions. On the one hand they must have sufficient radial elasticity to allow, by means of the mounting devices, to close or open the clutch state between the two teeth. On the other hand, when the engaged state is achieved, that is to say when the teeth mesh, it is necessary that the prestressing force is large enough to maintain the engaged state and that the two sets of teeth are prestressed. relative to each other in an appropriate manner in their meshing. To satisfy this condition, the invention provides, according to another characteristic, a component of teeth in particular as a drive member or receiving member for a clutch installation according to the invention, consisting of teeth having a central range. of body from which radially outwardly a set of resilient tongues and in the radially outer zone, each tongue has at least one tooth of the toothing.

For such an embodiment, the range of the teeth or groups of teeth on the respective tabs ensures firstly that thanks to the elasticity of the tabs, different mounting tools can simply open or restore the clutch plug . In addition, the various tongues provide, thanks to the various materials having the elasticity of the springs, for example spring steel, to choose a material having a sufficient prestressing force to maintain engagement with the gear teeth.

For example, it is possible for the radial projections to have a width in the circumferential direction from the body region which decreases radially outwards.

Advantageously, the ratio A / 1 can be situated between the width in the outer radial zone and the width in the inner radial zone in a range of 0.5 5 A / 1 <1.2 and preferably an equal ratio. at 0.8.

In order to achieve the radial elasticity necessary for a sufficient resistance to transmit the generated torques, it is advantageous that between two adjacent radial projections, on the central zone of the body, there is a substantially curved passage. It is also advantageous for the curved passage to have a radius of curvature greater than or equal to the thickness of the material of the gear component at the radial projections.

In order to obtain, on the one hand, the necessary radial elasticity and, on the other hand, the required radial prestressing force, it is advantageous that the ratio B / M between the width in the peripheral direction and the thickness of the the material in each case at the radial projections lies in a range defined as follows: <B / M <30, preferably a ratio of about 10.

According to a particularly advantageous embodiment of the toothed components according to the invention, which make it possible to satisfactorily satisfy the antagonistic requirements mentioned above, it is expected that starting from the central zone of the body, the radial projections are all first curved in a first bending range, preferably substantially in the axial direction and then in a second bending range essentially in a radial outward direction and then in a third bending range which substantially corresponds to the axial direction and in this substantially axial range, that is to say with an angle of the order of 0 to 5 relative to the axis of rotation, these projections comprise at least one tooth of the toothing.

Such an arrangement gives the radial elasticity by spring movement, radial, and the shape S or gooseneck, that in this elastic movement, in particular the areas bearing the teeth radially outwardly and which extend essentially axially , are offset radially and essentially not tilted so that the entire axial length of the teeth allows a regular grip or release with the complementary toothing and performs a substantially radial preload, mainly without tilting movement.

It is advantageous under these conditions that the radius of curvature in the second and / or third bending range is greater than or equal to 1.5 times the thickness of the material in the range of the radial projections.

It is further provided that the second and the third bending range form in combination a substantially continuous bending range substantially in the shape of a semicircle.

If, as described above, the radial projections are bent essentially in an S or gooseneck shape and the prestressing and the re-entrant movement essentially result from the bending-shaped deformation of the different bending ranges, it is Advantageously, the radial projections with their region extending substantially in the radial direction and each having at least one tooth are substantially not bent in the circumferential direction. Such a curvature would have in the transitional zone, with the third bending range, a curved surface in three dimensions with a corresponding rigidity, which could have a negative effect on the elastic behavior.

In this case, it is furthermore advantageous if the radial projections are substantially not bent in the circumferential direction in the region extending substantially in the axial direction and adjacent to the third bending range. This embodiment, which is visually plane in the circumferential direction, at this zone, participates in a greater spring-like elasticity.

The elastic spring-like behavior of the gear components according to the invention may further be advantageously influenced if at least one of the radial projections has at least one slot extending preferably substantially in the radial direction.

This slot may for example be made so that starting from the range of the body, it extends at least Jus at the second bending range.

According to another advantageous characteristic of the present invention, for a component of toothing, the teeth of this component may have flanks of teeth directed essentially in the peripheral direction and the flanks of teeth have with respect to a median longitudinal plane of the corresponding tooth. , an angle of the order of 10 to 50, preferably of the order of 20 to 30. Such an embodiment has the advantage that, on the one hand, the angled disposition of the tooth flanks causes the components of the radial forces produced by the induced torque to not be too great to cause accidental release of the teeth. On the other hand, such an angled disposition of the tooth flanks offers the advantage of offsetting small manufacturing loses which could lead to annoying movement play for much smaller inclined arrangements for the tooth flanks.

The present invention furthermore relates to a clutch installation having, as toothing component according to the invention, a driving member or / and a receiving member.

In order to take into account the mentioned conditions relating to the elasticity and the spring force for a gear component of a clutch installation according to the invention, it is provided according to another advantageous characteristic of the invention, that the component of the toothing comprises a set of teeth distributed in the circumferential direction, each tooth being formed on a tongue-shaped projection and having a terminal surface essentially rotated in the radial direction and a flank surface joining the end face and substantially the peripheral direction.

Under these conditions the toothing component is made of a steel sheet, preferably a spring steel sheet and the tab-shaped projections have at least one axial zone or extending substantially axially, on which is made the corresponding tooth.

By the use of steel, for example spring steel, in connection with the indicated shaping, it is possible to obtain that the spring effect generated makes it possible, on the one hand, to slide to disengage with the aid of a mounting device and on the other hand ensures a sufficient preload force for the clutch or engaged state.

To form in such a tooth component, the teeth with finishing surfaces and tooth flanks, each zone which extends substantially in the radial direction, comprises in its peripheral zones, peripheral prolongations curved in the radial direction. to achieve the flank surfaces.

If, for example, the toothing is a radially outwardly open toothing for receiving a complementary toothing radially inwardly, then the peripheral extensions are preferably curved radially inwardly. This means that in this case, the outer surface of the zone which extends substantially in the axial direction forms the finishing surface from which flanks of the teeth respectively radially inwards.

According to an alternative embodiment, lateral surface areas, turned substantially in the peripheral direction and extending in each case substantially in the axial range, form a flank surface.

In this embodiment, each substantially axially extending zone forms, with all its wall or material thickness, a tooth and the lateral surfaces correspond to the surfaces of the flanks.

According to another variant embodiment, the tooth is produced on each zone extending substantially axially, by stamping, deformation or by an analogous method.

To compensate for manufacturing tolerances, the invention provides that the flank surfaces form with respect to the median longitudinal plane of the corresponding tooth an inclination angle in a range of 10 to 50 and preferably 20 to 30.

For example, the peripheral extensions extending substantially in the axial direction may be bent in a corresponding manner to form this angle of inclination.

In the forming in which the zones which extend essentially in the axial direction form the teeth with the thickness of the material, it can be provided that the lateral surfaces turned substantially in the peripheral direction, have an angle of inclination by manufacture. or by machining the gear component.

The present invention also relates to a method of manufacturing a gear component such as the one described below.

This method comprises the following steps: a) stamping, cutting or the like, applied to a component blank made of a steel sheet and preferably a spring steel sheet, b) forming the blank of component for producing an axial zone or extending substantially in the axial direction, c) before or after step b), machining the component blank to make a tooth for each axial range or extending substantially axially .

In such a method step c) comprises the following operations - bending the peripheral extensions forming the flank surfaces and an end surface to form each tooth, or - producing an inclined surface, by chamfering, ablation or the like operation, applied to the lateral surfaces of at least each substantially axially extending range to form flank and end surfaces, or - shaping, stamping or the like applied to the component blank at each zone extending substantially axially to form a tooth projecting from the substantially axially extending range.

Preferably, after forming, the tooth component is processed.

An important feature of the clutch system or gear component for such an installation according to the invention is that, to engage or disengage the clutch or meshing plug, the components of the clutch or gear component must be deformed. toothing.

According to another independent feature of the present invention, there is provided a tooth component comprising a set of teeth which follow each other in the peripheral direction, each tooth being formed on a tongue-shaped projection with a terminal surface directed sensibly into the radial direction and a flank surface joining the end surface and essentially turned in the peripheral direction.

This toothing component is characterized in that it is elastically deformable, at least at the level of tab-shaped projections, this component preferably being made of a fiber-reinforced composite material made of spring steel sheet, steel sheet or the like and the tab-shaped projections have a region which extends axially or at least approximately axially and on which the corresponding tooth is made.

Thanks to such a tooth component, it is firstly possible to deform this component elastically to em brayer and declutch. It is further possible that in operation, nutation movements between the input side and the output side of such a clutch that is to say between the drive shaft and a converter housing or a clutch or the like, occur in the range of elasticity of this toothing component. To produce such a tooth component, it is possible to use very different materials which allow such elasticity, for example spring steel or sheet metal. The use of fiber-reinforced composite material such as carbon fibers is possible, in order to obtain the necessary elasticity by certain finished material shapes or thicknesses.

The present invention will be described hereinafter with the aid of an exemplary embodiment shown schematically in the accompanying drawings in which - Figure 1 shows in a sectional view, a drive means equipped with a drive member. housed in a receiving member of a clutch installation, - Figure 2 is a detail of a tooth portion of the drive member, - Figure 3 is a top view of the body of the drive, cut along the section line III-III of Figure 1 but without the fixing screws, - Figure 4 shows a mounting device for connecting the receiving member to the drive member in the form of a clamp, FIG. 5 shows the object of FIG. 4 but with a pressure hose, FIG. 6 corresponds to the object of FIG. 5 but with a protective sheath for the pressure pipe, FIG. 7 corresponds to the object of FIG. 4 but with a clamping ring, FIG. 8 corresponds to the object of FIG. 4 but with a tightening loop, FIG. 9 shows the tightening loop of FIG. 1 in the form of a separate part, FIG. 10 corresponds to FIG. but in another embodiment, - Figure 11 corresponds to Figure 1 but with another constructive embodiment of the drive member - Figure 12 corresponds to Figure 11 but with additional damping means - Figure 13 corresponds to the object of FIG. 1 but with a different constructive embodiment of the drive member and the receiving member; FIG. 14 shows a view corresponding to that of FIG. 11 with a variant of FIG. embodiment of a mounting device; FIG. 15 is a simplified axial view of the view of FIG. 14, this view being taken according to FIG. 14 from the right for the engaged state; FIG. is a view corresponding to that of the 15, but when the engaged state is not realized, FIG. 17 is a view corresponding to that of FIG. 15, further showing additional bias elements; FIG. 18 is an axial view of the two FIGS. rings of the mounting device located one above the other, - Figure 19 is a view corresponding to that of Figure 18 showing further the prestressing element, - Figure 20 shows an enlarged detail Fig. 19 is a top view of a bias spring; Fig. 22 shows an enlarged detail of Fig. 16; Fig. 23 shows an enlarged detail of Fig. 17; FIG. 24 is a view corresponding to that of FIG. 14 of an alternative embodiment of the mounting device; FIG. 25 shows another view corresponding to that of FIG. 14 with another embodiment of a device of FIG. mounting according to the invention, - the fi FIG. 26 is an axial view of a gear element according to the invention as a drive member; FIG. 27 is a sectional view of the gear element of FIG. 26 along section line XXVII-XXVII; FIG. 26 is a variant of the tooth component shown in FIG. 26; FIG. 29 is a perspective view of another variant of the tooth component of FIG. 26; FIG. FIG. 30 shows the <B> component of the toothing of FIG. 29 in axial view; FIG. 31 is a sectional view of the denature component of FIG. 30, cut along the line XXXI-XXXI of FIG. FIG. 30; FIG. 32 is a perspective view of an alternative embodiment of a toothing component; FIG. 33 shows an axial view of the component of FIG. 32; FIG. section along the line XXXIV-XXXIV of the tooth component of FIG. 33, - FIG. 35 is a partial axial view of a Tooth component blank according to Figs. 32 to 34; Fig. 36 shows a transformation operation for making a tooth of a toothing component according to Figs 32 to 34; Fig. 37 is a sectional view of a protruding tongue bearing a tooth, in connection with a mounting device; - Fig. 38 shows the tooth of Fig. 37 engaged with an opposing toothing; - Fig. 39 is a perspective view of another embodiment of Figure 40 is an axial view of the component of Figure 39, Figure 41 is a sectional view of the component of Figure 40 along line XLI-XLI line of Figure 40. FIG. 42 shows the toothed component according to FIGS. 39-41 in its assembly with a mounting device such as that of FIGS. 14 to 25; FIG. 43 is a partial sectional view of the tooth component of FIG. 42.

FIG. 1 shows the free end of the crankshaft 15 of an internal combustion engine constituting the drive means 1. The crankshaft 3 comprises a set of threads 5 distributed around its periphery to each receive a fastening means 7 in the form of 9 of a screw with a threaded rod 11. A radial flange 13 is fixed to the crankshaft 3 by these fastening means 7. this crankshaft has in the radial zone, outside the fastening means 7, a section reduction receiving a elastic flange 15 in the axial direction. This flange 15 comprises a bending 16 continuing with an axial extension 17, the free end 22, not located on the side of the crankshaft 3, has a toothing 19 whose teeth 20 are directed substantially in the axial direction. The teeth 20 join a tooth root 21 made at the periphery, before reaching the folded portion 16. The radial flange 13 and the elastic axial flange 15, with the axial extension 17, form a drive member 23 which comes into taken with a receiving member 25 in a manner explained later; the receiving member 25 is in the form of a ring 27 and a weld bead 29 attaches it to a mass of inertia 31 having a primary flange 33.

In the present embodiment, this primary flange 33 is part of the housing 35 of a hydrodynamic torque converter constituting a clutch device but it can also be considered as a mass of inertia, drive, a steering wheel two-mass inertia such as that described in DE 44 22 732 A1. To receive the housing 35 of the hydrodynamic torque converter, the crankshaft 3 has, at its center of rotation, an axial bore 39 receiving a bearing journal 41 fixed radially inside the primary flange 33.

According to FIGS. 2 and 3, the driving member 23 comprises, in the zone of extension of its toothing 19, a gap 45 between each time two teeth 20 and a tooth 53 of a toothing 51 of the reception 25 enters this interval. Conversely, the receiving member 25 has a tooth gap 52 between each time two teeth 53 of its toothing 51 to receive a respective tooth 20 of the toothing 19 of the drive member 23. Figure 2 shows particularly clearly the tooth 20 has, on its peripheral side, flanks 47 which, relative to the radial axis of the tooth 20, an angle different from a right angle and thus constitute a corner surface 48. In the radial direction, the tooth 20 is delimited by a tooth closure surface 49. With this embodiment, the tooth 20 functions as a wedge 50 which, according to FIG. the tooth gap 52 of corresponding shape between two teeth 53 of the receiving member 25. The teeth 53 of the receiving member 25 also have an angle different from a right angle along the radial axis so that at the level of each tooth 53 we have each c removed, wedge-shaped surfaces 54 whose inclination is preferably matched to that of the corner surfaces 48 of the teeth 20. For a corresponding radial prestressing of the teeth 20 of the drive member 23 in the direction of the bottom On the receiving member 25, it is thus possible to clamp the tooth 20 in the tooth gap 52 without the tooth reaching the tooth root 55.

As already indicated, the teeth 20 of the toothing 19 of the drive member 23 have a prestress directed radially outwards. To have a simple assembly of the clutch device on the crankshaft 3, is installed on the axial extension 17, in the area between the folded portion 16 and the toothing 19, a mounting device 70 which will be described hereinafter. in more detail (Figures 4 to 10). This mounting device compresses radially inwards all the teeth 20 of the drive member 23. Thus, the receiving member 25 can engage the toothing 19 of the drive member 23 without requiring axial force. As soon as the axial end position is reached between the drive member 23 and the receiving member 25, the mounting device 70 is released, thereby freeing the teeth 20; by virtue of their axial prestressing, the teeth engage in the toothing 51 of the receiving member 25 until the tight connection, described above, is made in the zone between the corner surfaces 48, 54 of the teeth 20, 53. A clearance-free fixing is thus achieved in the peripheral direction of the clutch device and the converter housing 35 on the crankshaft 3.

So that the converter housing 35 remains in this axial position, the drive member 23 comprises two claws 59, offset in the peripheral direction, and which are also in radial prestressing. These claws 59 comprise, at their free end facing the converter housing 35, a radial attachment 61 extending in direction of the receiving member 25 and coming into a corresponding radial cavity 63 of the ring 27 of the This penetration preferably occurs when the mounting device 70 mentioned above is released and the claws 59 escape elastically outwardly in the radial direction. The radial attachment 61 is preferably wedge-shaped and penetrates into a radial cavity 63 of corresponding shape. The penetration ends as soon as the claw 59 is pinched in the radial cavity 63. As soon as this occurs, the converter housing 35 can no longer be released from the drive member 23. The claws 59 then operate as axial locking means 57.

Figures 4 to 8 show a sectional view corresponding to that of Figure 1 and for simplicity, denaturing 19 has not been shown in detail, with the exception of the cutting area of the toothing 19 itself. The reason is that Figures 4 to 8 serve only to show the mounting device 70 already mentioned, therefore only this element is shown with references in the corresponding figures.

According to FIG. 4, the mounting device 70 is formed by a collar 71 essentially axially installed between the folded portion 16 and the toothing 19 of the driving member 23 on its axial extension 17. One end of the ribbon 72 carries a screw housing 74 receiving a clamping screw 73. This screw penetrates with its thread into a thread-shaped depression formed at the straight end 75 of the ribbon 72; thus, by rotating the locking screw 73, a pulling force is exerted in the circumferential direction on the free end 75 of the ribbon 72; the collar 71 is thus pulled or released according to the direction of rotation of the clamping screw 73. When it is turned, to tighten, then, as indicated in FIG. 4, the upper half moves as it appears, although that the free end 75 of the ribbon 72 passes over the remaining portion of the ribbon 72. The resulting tightening of the collar 71 produces a rudder force exerted from the outside on the axial extension 17 which thus compresses the toothing 19 radially to inside. As soon as this compression is produced, the preparation has been completed for axially engaging the receiving member 25 on the drive member 23 without exerting axial force. At the end of this sliding engagement movement, the clamping screw 73 is rotated in the opposite direction so that the degree of overlap of the free end 75 decreases relative to the remainder of the ribbon 72 and thus allows the expansion of the clamp 71. It can then fully lift the clamp 71 of the drive member 23 or leave it in place without intervening.

FIG. 5 shows the mounting device 70 formed by a pressure pipe 72 which surrounds the axial extension 17. According to FIG. 5, this pressure pipe 78 is depressurized and thus has a flattened portion 82 at its radially inner side. This pressure pipe 78 is connected by a pressure branch 79 to a pressure source 80 only shown schematically; when pressurized by this source, the section of the pipe increases so that the pipe compresses the axial extension 17, radially inward, while decreasing the surface of its flattened portion 82. The radial extension 17 thus gets to the form necessary for editing. To suppress the effect of the mounting device 70, it is sufficient to shut off the action of the pressure source 80. In this embodiment, the pressure pipe 78 can be removed from the drive member 23 or remain on this one but in an inactive way.

Figure 6 shows a variant of the embodiment of Figure 5; in this variant only a protective sheath 83 surrounds the pressure pipe 78.

FIG. 7 shows a mounting device 70 constituted by a clamping ring 84. This clamping ring is slid over the conically shaped segment 85 of the axial extension 17. When the clamping ring 84 is slid to the right according to FIG. 7, that is to say in the direction of the flared portion of the axial extension 17, it compresses this axial extension to the size of the inner diameter of the clamping ring 84. Conversely, a displacement of the clamping ring 84 in the opposite direction allows the expansion of the axial extension 17, radially outwardly.

Figure 8 shows an embodiment of the mounting device 70 with a clamping loop 87 which appears more clearly in Figure 9. This clamping loop 87 has end tabs 88; these legs are precarious so that they tend to get closer. The tightening loop 87 then takes the diameter shown in solid lines. After placing a tool not shown on the spacing ends 88, one can pull one over the other, in the peripheral direction, until they are in the position shown in FIG. broken line. Clamping loop 87 then has a decreased diameter and thus compresses the axial extension 17 radially inwards. To eliminate the action of the clamping loop 87 it suffices to remove the tool not shown to separate it from the spacing ends 88. These ends then return elastically to their initial position and thus discharge the axial extension 17.

FIG. 10 shows another use of the elastic loop 87. For this, a tool 90 is placed radially from outside on the axial extension 17. This tool 90 comprises buffers 93 which hold the loop 87 at the level of the fixing end 91 and a pulling end 92 bearing radially against the axial extension 17. The fixing end 91 is introduced here into one of the buffers 93, namely the right pad according to the orientation of FIG. 10 to be held there while pulling end 92 is held in a pulling means 94.

This traction means 94 is generally a gripper. As soon as this pulling means 94 is moved in the direction of the arrow of FIG. 10, the loop 87, fastened to the fixing end 91, moves from the position shown in full lines to the narrowed position shown in broken lines in FIG. thus exerting a radial compressive force on the axial extension 17. To unload the loop 87 is displaced, on the contrary, the pulling means 94 in the opposite direction.

In FIG. 11, reference will be made especially to the construction of the radial flange 13 shown which shows the main difference with respect to the embodiment already described with reference to FIG. 1. Thus, the elastic axial flange 15 comprises radially outside the diameter of the portion for fixing on the crankshaft 3, an elastic loop 96 having in section substantially in the form of an inverted letter C. The outer radial branch of this elastic loop 96 is comparable to the axial extension 17 already described with reference to FIG. 1 and carries the toothing 19 at its outer periphery, in the mean axial zone. In the direction of the crankshaft 3, the toothing 19 continues with a free axial end 98 whose outer periphery has a bearing surface 99 for a mounting device 70 such as that represented for example in FIGS. 4 to 10. axial fixation 57 is provided at this free end 98; this axial attachment 57 penetrates in a known manner with a claw 59 in a radial cavity 63 of the receiving member 25. Due to the attachment of this claw 59 in the free end 98 of the axial extension 17, the latter penetrates in the region of axial extension of the den ture 51 of the receiving member 25 in the corresponding radial cavity 63 so as to make full use of the available axial space. At the same time, thanks to the leverage effect of the free end 98 with respect to the bent part 16 of the elastic axial flange 15, it suffices for a relatively weak mounting force exerted by the mounting device 70 to overcome a relatively high radial bias force, which can be created due to the constructive realization of the elastic loop 96, preferably at the drive member 23.

FIG. 12 shows, in addition to the embodiment 11, a damping means 100 in the form of an elastomer element 102 placed in the free cavity 104 of the elastic loop 96 of the radial flange 13. consider both a ring-shaped elastomeric element or a plurality of elastomeric elements distributed at pre-determined intervals in the peripheral direction.

While in the embodiments described above, the receiving member 25 still annularly surrounds the drive member 23, FIG. 13 is another embodiment in which the receiving member 25 is formed by a support 105 fixed by a weld bead 107 to the primary flange 33 of the converter housing 35. This support 105 is in the form of an elastic axial flange 106 and comprises an elastic spring loop 108 in its outer radial zone. In the embodiment according to FIG. 13, this loop has a C-shaped section and the outer radial branch of this spring loop 108 functions as an axial extension 110 for the teeth 51 of the receiving member 25 in the peripheral zone. ; on the side facing the converter housing 35, this loop has a free end 112 provided radially outside a bearing surface 114 for a mounting device 70 such as that described for example in FIGS. 4 to 10. mounting device causes the free end 112 is smaller than the dimension that should be provided for the radial prestressing force due to its lever arm which is smaller than the elastic axial element 106; this prestressing force pushes the toothing 51 radially outwards in the toothing 19 to the inner periphery of the axial extension 17 of the drive member 23. In this embodiment, due to the relatively large radial force exerted between the denatures 19, 51, it is possible to omit additional axial fixation.

Figures 14 to 23 show another embodiment of a mounting device 70 which can be used in particular with the embodiment of the drive member 23 also shown in Figures 14 to 23. It should nevertheless be noted that this device of my step 70, as well as the application to the previously described embodiments of the drive member can be used in particular for the embodiments of Figures 11 to 13.

It will first be noted that, unlike the variants described above, the drive member 23, for example made of spring steel, comprises a disk-shaped central zone 115 which continues in the peripheral direction, succession of tabs 116 in the form of res spells. Each tongue carries, in its radially outer zone, a tooth of the toothing 19; each of the teeth may have a form described in detail. In particular, each spring tongue 116 includes an axial extension 17 which carries each respective tooth extending radially outwardly. To each tooth of the toothing 19, between two teeth of the toothing 51 of the receiving member 25, is associated a gap so that in the manner described above, the teeth of the teeth 19, 51 may come into engagement with each other. . It is clear that this embodiment of the drive member 23 also allows axial locking as it has been described by way of example with reference to Figure 11.

The mounting device 70, shown in FIGS. 14 to 23, comprises two annular elements 110, 112 rotatably mounted on the bearing surface 99 at the free end 98 of the axial extension 17. In particular, it appears that the different axial extensions 17 axially block the annular elements 110, 112 between the teeth of the toothing 19 and a locking or fixing projection 120 which is produced for example by shaping, matting or a similar process, applied at the free end 98 of the axial extension 17. This means that the drive member 23 may form a pre-assembled assembly with the rings 110, 112; this assembly is made by folding radially inwards the various springs or tongues elastic 116 with the aid of a tool; then the annular elements 110, 112 are engaged and thus the spring tongues 116 are released until the rings are held on the drive member 23 in the form shown.

As appears in particular in the detail views of FIGS. 18, 19, 20, which show the realization of the two annular elements 110, 112, these annular elements 110, 112 have, at their inner peripheral zone 124, a deformation 122 This deformation comprises, associated with each tooth of the toothing 119, i.e. each spring tongue 116, on the ring element 110, a deformation ramp 126 which extends in the circumferential direction and which continues in the circumferential direction, each time by zones 128, 130 with a substantially constant distance with respect to the axis of rotation A. In the peripheral direction, the zone 130 is then followed by a step 132 and then again 128 correspondingly, the annular element 112, which is largely concealed in Figure 20, comprises, for each tooth of the toothing 19, that is to say each spring tongue 116, a ram deformation 134 always followed again by zones 136, 137 with substantially the same distance with respect to the axis of rotation A. The two rings can have an identical construction or can be rotated relative to one another. another to finally arrive at the arrangement shown in FIG. 20 for which each pair of deformation ramps 126, 134 extends in opposite but associated directions.

As appears in particular in Figures 18 and 19, each annular element 110, 112 comprises, in several peripheral positions, an attack formation 138 for an actuating tool. The attacking formations 138 of the annular element <B> 110 </ B> comprise an oblong hole 140 followed by an opening 142. Correspondingly, the etching formation 138 of the annular element 112 comprises a hole oblong 144 partially concealed followed by an opening 146. As the two annular elements 110, 112 are made identically and are arranged in opposite directions relative to each other, the oblong hole 114 of the annular element 110 partially covers the oblong hole 144 of the annular element 112 and further releases the opening 146 of the annular element 112. Correspondingly, the opening 142 of the annular element 110 is located on the part shown in FIG. in a hidden manner of the oblong hole 144 of the annular element 112.

The tool used may comprise for example two pins or segments, substantially parallel, which can be brought together; for example, this can be done by spring end segments connected by a helical or spiral turn. For actuation, these two segments are slid into the openings 142, 146 accessible through the oblong holes 140, 144 of the annular elements 110, 112 and in rap, reciprocally procuring the two segments, the two annular elements 110, 112 can be rotated in the direction peripheral, one compared to the other. As the segments of the actuating tool that come into the openings 142, 146 further penetrate each time into the oblong holes 144, 140 of the other annular element 112, 110, this does not interfere with the reversibility of the two elements. 110, 112 even if the two end segments have been fully slid through the openings 142, 146. It should be noted that Figures 18, 19, 20 show a situation in which the axial extensions 17 of the elastic tabs 116 The respective ones are located at the segments or zones 128, 136, i.e. they have been radially outwardly shifted. This situation is also shown in FIGS. 15, 17 where it appears that the teeth of the toothing 19 penetrate substantially completely between each pair of teeth of the toothing 51. As can be seen for example in FIGS. 17, 19 and 22, the two elements The rings 110, 112 may have recesses 150 facing each other, which are superimposed in the relative rotational position shown in FIGS. 17, 19, 20. These cavities 150 house leaf spring elements 152 essentially in H-shape, which maintain axially joined together the two annular elements 110, 112 by respective notches or cavities 154, 156 and which further provide a prestressing of the annular elements 110, 112 in the relative rotational position shown in FIGS. 17, 19, 22.

Starting, for example, from the position shown in FIG. 14, in which the two toothing 19, 51 mesh completely to loosen the clutch (the two annular elements 110, 112 also occupy in this condition the relative position shown in FIGS. , 17, 18, 19, 20, 23), at least one of the gripping formations 138 is introduced with an actuating tool with its two segments; this means that in each of the openings 142, 146 is introduced such a segment. Then, by acting against the prestressing of the leaf spring elements 152, insofar as such elements are provided, the two segments are brought together in the peripheral direction so that the segments penetrating the openings 142, 146 move each once in the oblong hole 140, 144 provided in the other annular element 110, 112 until finally one arrives in the relative rotational position of the annular elements-110, 112 shown in Figures 16 and 22. When performing this relative rotation, the different deformation ramps 126, 134, which are each associated with one of the teeth of the toothing 19, move along an associated outer edge of the driving surface 99 of the axial extension 17 so that this outer edge, and thus the entire axial extension 17, is pressed radially inwards.

The consequence is that, as appears in particular in FIG. 22, the teeth of the toothing 19 also move radially inwardly and suppress the reciprocal radial prestress between the teeth 19, 51; the wedge-shaped embodiment of the teeth allows a slight axial sliding of the teeth, that is to say of the drive member 23 and the receiving member 25 relative to each other . After this axial distance between the driving member 23 and the receiving member 25, the tool introduced into the openings 142, 146 can be disengaged so that the action of the spring-blade elements 152 rotates again. the annular members 110, 112 relative to each other so that in the opposite direction, the forming ramps 126, 134 slide over the leading surface area 99 and the axial extensions 17 are again moved radially outwards by the elasticity of the spring tongues 116 until finally the position of the toothing 19 shown in FIGS. 15, 17, 23 is reached, without however entering the toothing 51.

For example, it is also possible to create a device without a leaf spring element 152 but which nevertheless provides that, for example in the situation shown in FIG. 22, the zones 130, 137 are not aligned in the peripheral direction on the surface of the surface. reception 29 and. that furthermore, the deformation ramps 126, 134 act on the axial extensions 17 so that after releasing the two annular elements 110, 112, when the tool is removed, the prestressing of the axial extensions 17 directed radially outwards The annular elements 110, 112 necessarily turn in the position shown, for example, in FIG. 23. This means that in such an embodiment it is possible to completely remove the zones 130, 137.

It should be noted that when for example the position of the resilient tongues 116 or axial extensions 17, inwardly displaced, represented for example in FIG. 22, the annular elements 110, 112 can not fall from the drive member 23, since in this case also the locking projections 120 provide an axial clearance of the rings 110, 112.

It appears that in the assembled state, the annular elements 110, 112 can define at the same time an axial stop for the receiving member 25, that is to say the maximum position shifted from the receiving member. 25 and the drive member 23; it is then clear that, as already indicated above, it is possible to provide axial fixation at the level of the teeth. The axial clamping of the annular elements 110, 112, between the receiving member 25 and the fixing projections 120, furthermore offers the advantage of avoiding beat noises during operation thanks to the mutual support of the annular elements 110. , 112, even if the annular elements 110, 112 remain permanently against the drive member 23 in the assembled state.

Figure 24 shows a variant of the embodiment described above. This embodiment differs from those described above in that the two annular elements 110, 112 of the mounting device 70 are bent relative to one another in their outer radial zone to obtain a saucer-shaped structure. . Thus, there is additionally a force component tending to axially separate the two annular elements 110, 112; this component performs, cooperating with the axial clamping between the receiving member 25 and the locking projections 120, a better protection against beat noise.

Figures 14 and 24 show each of the embodiments in which the annular elements 110, 122 are stamped sheet metal parts. Figure 25 shows an embodiment in which the annular elements 110, 112 are for example stamped parts having substantially a pot-shaped structure. This means that these parts extend from the zone in which they cooperate with the axial extensions 17 first radially outwards to be slightly inclined in the axial direction and then radially outwards and to join, in another zone extending radially in the different drive formations 138 to receive the tool and extend further in the axial direction as shown in broken lines. The advantage of such an embodiment is that at the level of the zone in which the attack formations 138 are associated, there is greater freedom of selection. Thus, by arranging these attack formations, radially further out, we arrive at an easier accessibility thereof for the actuating tool. It would be possible to provide the etching formations 138 in the radially outer and axially extending region. This further has the advantage, because of the lever arm ratio, that the force required to deform the various resilient tongues 116, radially inward, is easier to establish.

It should be noted that, as shown, preferably the different drive formations 138 are distributed at an angular interval of 90 which allows to act on the annular elements 110, 112 from different peripheral zones. However, any other posi- tioning or any number of attack formations is possible. With respect to the leaf spring members 152 which are preferably distributed in pairs with an angular distance of 180, any other number of such leaf spring elements may be considered.

In principle it should be noted that the embodiments shown of the mounting device 70 with two annular elements 110, 11 is a preferred form because a simple movement of two segments together by an actuating tool makes it possible to carry out a movement of relative rotation and thus to actuate the axial segments 17. In principle, one could also consider a construction of the mounting device 70 from a single annu lar element for example of the annular element 112 which is then rotated by a tool corresponding actuator, only with respect to the drive member 23 so that the deformation ramps 126 move radially inwardly, the axial extensions 17 or that by rotation opposite, radially outwardly, they free. Prior to the assembly of the drive member 23 with the receiving member 25 it is necessary, for example, to hold the drive member 23 and to rotate the annular element 110 until the zones 130 are located therein. above the different attack surfaces 99 and no longer allow an accidental return of the annular element 110. After the drive member 23 has been displaced axially on the receiving member 25 and the teeth of the toothing 19 have already penetrated between the teeth of the toothing 51, by blocking the neck 31 of the torque converter, that is to say by blocking the receiving member 25, the annular element 110 can be turned in the In order to release this clutch, the annular element <B> 110 </ B> is rotated again by blocking the receiving member 25 to move the axial extensions 17 radially towards the end. inside.

It should be noted that the embodiments of the device 70 shown in FIGS. 14 to 25 can also be used for drive members of different embodiments, in particular the drive member is not necessarily made with elastic tongues. as has been described above. This means that for a drive member such as that shown in FIG. 1, such a mounting device 70 could be used.

It should also be noted that each spring tongue <B> 116 </ B> may have a plurality of teeth of the toothing 19 so that these resilient tongues 116 may radially move a group of teeth by the associated forming ramps.

FIGS. 26, 27 again show a tooth component, in this case that of the drive member 23, as in the clutch described above, which can for example be represented as indicated in FIG. 11 or FIG. 14, 24, 25.

This drive member 23 comprises a substantially ring-shaped body zone 115 provided with openings or holes 117 for attachment, for example, to a crankshaft flange or the like. The protrusions or elastic tabs 116 extend radially from the zone 115 of the body. It should be noted that such a drive member 23 is preferably stamped into a spring steel blank and bent into the shape shown.

Thus, in connection with the particular shaping described hereinafter, the spring elasticity required for the clutch and the clutch and the radial prestressing force are made on the one hand to preserve the other the engaged state.

As appears in particular in FIG. 27, starting from the zone of the body 115, the protruding parts 116 firstly have a first bending zone 180 in which these projections are first bent in an inclined manner with respect to the direction of the rotational axis, substantially in an angular range between 0 and 20. This first bending zone 180 is followed by a first zone 182 extending essentially in the axial direction. This zone 182 is followed by a second bending zone 184 directed radially outwards and joining a third bending zone 186. Because of this second bending zone 184 and the third bending zone 186, each radial projection 116 joins again the axial extension 17 which forms another zone extending substantially, that is to say substantially in the axial direction; it starts from the associated bending zone (here it is the third bending zone 86) and extends in the opposite direction to the zone 182, essentially in the axial direction so that these zones overlap practically when 'we look in the radial direction.

This contour or bending of the various radial protrusions 116, essentially in the shape of an S-shape or a cy-neck, has the advantage that, by compressing or extending radially, these movements are such that the axial protuberances 17 move only radially but do not tilt around the third bending zone 186 and the corresponding axis of rotation A. This means that when using a mounting device such as that described previously in the various embodiments, and by acting on the free end zones of the axial extensions 17, by sliding the axial extensions, radially towards the inside, the teeth 19, 51 come out of engagement substantially in a regular manner over their axial length or are out of support so that even a very small movement of these axial extensions 17 can be done radially inwards to disengage or to ensure the mutual support of the teeth, and to release the drive member 23 of the receiving member 25. The same remark applies to the establishment of the radial prestressing. In this case also the sliding of the axial extensions 17 radially outwards is essentially without tilting with respect to the axis of rotation A so that over the entire axial length of the teeth of the teeth 19, 51, is realized a regular application pressure, to avoid to a very large extent the maximum point stress at the teeth, particularly at the two axial ends of the teeth.

It should be noted that preferably the different axial extensions 17 can extend from the third bending zone 186, with respect to the axis of rotation, at a slight angle outwards, for example up to 5 . As a result, during the next request, radially inwards, to establish or disengage the clutch by the tool acting at the free ends of the axial extensions, in the case of the sliding referred to above and which is produced radially inwards, simultaneously the different axial extensions may be conducted in a position parallel to the axis or even be tilted beyond this position parallel to the axis; thus, during the subsequent contacting with the toothing of the receiving member 25 and the release of the axial extensions by the mounting device, the teeth 20 of the toothing 19 abut against the drive member 23 with their longitudinal direction practically aligned with the axis of rotation A, that is to say parallel to it.

Each axial extension 17 carries a tooth 20 of the toothing 19. In the embodiment shown, the tooth 20 is obtained by stamping the material of the spring steel at the axial extension 17. This stamping can also be done before the different bending operations with appropriate tools. In contrast to the embodiment of FIG. 25, that of FIGS. 26 and 27 shows that the second and the third bending zone 184, 186 meet and form a common bending zone, with substantially circular bending, whereas in the embodiment of Figure 25, the second and third bending zone are separated by a short substantially straight segment and have different radii of curvature. There is a relatively large freedom of design and depending on the choice of the radii of curvature of the second and the third bending zone 184, 186 or by the insertion of a segment separating the bending zones 184, 186, it is possible to adjust the resilient behavior of the radial protrusions or elastic tongues 116. It is advantageous under these conditions to have a bending or curvature range for at least the third bending range 186, the bending radius of which corresponds to a range of the order of 1.5 times the thickness of the material or more. The radius of curvature in the third bending zone 184 also makes it possible to respect this condition; in particular, as shown in FIG. 27, the second and third bending zones 184, 186 meet, so that it may be advantageous to provide a regular radius of curvature.

Figure 26 further shows that the radial projections or resilient tongues 116 are decreasing radially outwardly. This also contributes to the desired spring elasticity for the same large torque transmission capacity. It has been found that a ratio between the width of the inner zone and the width of the outer zone in an area of 0.5 to 1.2 is an advantageous ratio. Fig. 26 shows that different rates of decrease can be predicted, i.e., the different radial projections 116 may decrease more strongly in the radial zone with respect to their peripheral extension than in the radial zone. inner area. For the conditions of elasticity and prestressing it is advantageous that the ratio between the peripheral extension of the radial projections 116 and the thickness of the material or the wall of the drive member 23 was at the level of the radial projections 116 in a range of 5 to 30; for example, there is provided an average peripheral width of the various radial projections which can be related to the thickness of the material. It is furthermore advantageous that at the passage between two directly adjacent radial projections 116, at the zone 115 of the body, that is to say in the notch zones bearing the reference 188 in FIG. a wise step in the shape of an arc or a circle to avoid concentration constraints. For the radius of curvature of the arcuate passage, it is advantageous to choose a value of the order of the dimension of the thickness of the material of the drive member 25 or greater than this dimension.

Another advantageous characteristic, particularly from the point of view of the elastic behavior of the various radial projections 116, is shown in FIG. 28. This figure shows, in a dashed line, that the axial prolongations 17 of the various radial projections 116 represented as extensions with dotted lines, appear as starting from FIG. 26 with a circumferential contour adapted to a circle shape, now flattened so that the drawing of the respective axial extensions is translated in the peripheral direction by a polygonal structure. This means that in the peripheral directions, the various axial extensions <B> 117 </ B> are in principle not bent. When such a non-curved zone in the circumferential direction extends at least into the third bending zone 186, the result is that the elasticity of the spring steel in which the drive member 23 is formed is is not limited or stiffened by three-dimensional formatting as in the embodiment of FIGS. 26, 27 and in particular for the radial projection 116 which appears on the left in FIG. 27, insofar as such stiffening by a shape cinema is not sought after. The above-described features each separately, but preferably, combine in that the reciprocal requirements arrive at a sufficient radial prestressing force and give sufficient radial elasticity for cooperation with an elevation tool, in the best possible manner. possible.

According to another characteristic which participates in particular to a sufficient and guaranteed torque transmission coupling, appears in FIG. 26. This figure shows that the surfaces of the flanks of the teeth 20 of the toothing 19, practically directed in the peripheral direction, form a year gle a for their extension, radially outwardly, relative to the median longitudinal plane of the different teeth 20 bearing the reference M in Figure 26 and perpendicular to the plane of the drawing. This angle is in a range between <B> 10 '</ B> and <B> 50', </ B> preferably between 20 'and <B> 30'. </ B> The selection of the angle a in the range of the indicated values leads first of all to the component of the radial force generated by the cooperation with a complementary toothing, and which tends to radially expel the associated tooth 20, It is not sufficient for the two teeth to be able to disengage. In addition, such a value of the angle α has the consequence that the manufacturing tolerances and measurements at the teeth 19, 51 which mesh with each other do not result in an unwanted movement play; this would be the case if for example the tooth flanks 48 were parallel to the plane M or made only a small angle of inclination with respect thereto. Relatively large radial movements would then have to be made to compensate for small measurement inaccuracies, and to make the engagement between the teeth. For flanks 48 located flat, already for a relatively low axial movement, it is necessary to compensate for manufacturing inaccuracies or measurements, within a range of axial movement of the axial extensions 17 so that it does not lead to an important modification of the prestressing force by which the teeth 20 are pressed radially outwards. Figures 29 to 31 show a variant of the drive member 23, that is to say the gear of the component 23. In this case also the drive member 23 is formed mainly of a body 115 with several radial protrusions 116 curved as already described in a substantially S-shaped or gooseneck. However, it can be seen that the various radial projections have slots 190 starting practically from the body zone 115; these slits extend in the first bending range 180, with their first range 182 which essentially axially joins the second bending range 184 and, where appropriate, even up to the level of the third bending range 186. The production of such slits 190 in the various radial projections of the elastic tongues 116 makes it possible to further influence the elastic behavior. In particular, by an appropriate choice of the length of the slots or the width of the windows, one can influence the spring behavior.

Another difference of the embodiment of Figs. 29-31 is that the different teeth 20 of the denature 19 of the drive member 23 are no longer constituted by die-formed portions formed on the axial extensions 17 but directly by the This means that in the circumferential direction, the surfaces of the flanks 48 each form the thickness of the steel spring plate in which the drive member 23 is formed. resting engagement with the complementary bearing surfaces of the toothing 51 of the receiving member 25. It can be seen that the surfaces of the flanks 48 do not extend to the level of the third bending zone 186 which results in a very great axial extension of the teeth of the toothing 19 reducing the stresses applied to the material at the level of the toothing 19.

At the free ends 98 of the axial extensions 17, there are in each case blocking projections 120 made for example by shaping the material; thus, as already explained above in relation to FIGS. 14 to 25, the annular elements 110, 112 of the mounting device 70 are held on the drive member 23. It should be noted that by an appropriate embodiment surfaces of the flanks 48 on the axial extensions 17, with an angle of inclination with respect to the median longitudinal plane M of the different teeth 20, the advantages described above are obtained.

Figures 29 to 31 show that in this embodiment it is advantageous that the radial projections 116 are made outwardly with a decreasing peripheral extension. In addition, it appears that the measurement indications described above for the different radii of curvature or transient ranges can also be used here advantageously.

It should be noted that the drive members 23, shown in FIGS. 26 to 31, can be applied to all the embodiments shown above in combination with FIGS. 1 to 25 of a clutch. This concerns both the application as a drive member as described in detail above that the application as a receiving member, for example, represented in FIG. 13.

FIGS. 32 to 38 show another embodiment of a toothing component according to the invention, which is also embodied here as a drive member 23. This tooth component or this drive member 23 comprises a central body area 115 from which extend radially outwardly a set of projections 116 in the form of tongues. As appears in particular in Figure 34; the radial or tongue-like protrusions 116 extend from the body region 115 first in a first bend range 180, and then in a second bend range 184 which extends substantially axially with respect to the first region 182; then, there is a third range 186 joining the axial extension 17. Each axial extension 17 forms with its outer surface, that is to say its surface 49 rotated radially outwards, the end surface of each respective tooth 20 of the toothing 19. Peripheral extensions 200, 202 extend in both circumferential directions from each axial extension 17; these peripheral extensions form, as shown in FIGS. 32 to 34, flank surfaces 48 since they are bent radially inwards; these surfaces 48 join the end surfaces 49 of each tooth 20. At the free end 98 of each axial extension 17, there are locking projections 120 which, as previously described, cooperate with the annular elements 110, 112 of the mounting device. 70 to lock the latter on the drive member 23 (see FIGS. 37 and 38) The bending is such that for the extension of the flank surfaces 48 radially outwards, the extension lines form with a median longitudinal plane M (it is perpendicular to the plane of the drawing in Figure 33 and passes through a radial line), an acute angle has of the order of 10 to 50 and preferably of the order 20 to 30. This has the advantages discussed above regarding the compensation of manufacturing tolerances.

The realization of the flank surfaces 48 by peripheral extensions 200, 202, curved, leads to the gearing of the teeth 19, 51, incorporating a peripheral elasticity resulting from the elastic connection of the peripheral extensions 200, 202 to each axial extension 17. This elasticity also makes it possible to compensate for manufacturing tolerances. The folded extensions 200, 202 furthermore have the advantage that the different teeth 20 come very rigid in the axial direction thanks to the plastic deformation produced by the bending of these peripheral extensions 200, 202. Moreover, the bending provides the advantage that the axial extension 17 does not have areas of the teeth protruding radially outwardly, so that for the same embodiment, that is to say the length of the radial projections 116 the radius of the toothing can be reduced.

It should be noted that such an embodiment of the teeth 20 is also possible if the range of the body 115 extends radially outward in the third bending range 186, i.e. if only substantially axial extensions 17 are bent with respect to the body portion 15. According to FIG. 37, the axial extensions 17 are preferably made in such a way that, in the unfilled state, they extend radially outwardly, away from each other. slightly in the third zone 186. Thus, in the view of FIG. 37, the two annular elements 110, 112 can be fitted from the right until they abut against the locking protrusions 120 of the teeth 20; during this engagement, the teeth are slightly displaced, radially inward, that is to say prestressed. By the spacing action of the teeth 20, the annular elements 110, 112 are then held against the gear components 23 by this frictionally gripped connection. Hereinafter, this component is engaged with the annular elements 110, 112 axially in the toothing 51 of the receiving member 25; if necessary, this is done before the annular elements 110, 112 by turning as described above with reference to FIGS. 14 to 25. It should be noted that, as has been described with reference to FIG. Different axial extensions 17 may be made so as not to be adapted to a peripheral line or a circular line but to extend essentially tangentially with respect to the peripheral direction relative to a radial line, so that in this case also, to the benefits of the elasticity mentioned above. It should be noted that after the execution of the processing or forming operations, the spring steel part can be treated. This also relates to the embodiment which will be described hereinafter and which is shown in FIGS. 39 to 43.

In this embodiment which corresponds essentially to the embodiment of Figs. 29 to 31, the axial extensions 17 in themselves form the teeth 20. This means that lateral surface areas in the peripheral direction form the surfaces. flanks 48, so that each tooth has an extension in the radial direction which corresponds to the thickness of the material of the projections 116 in the outer radial zone, especially in the region of the axial extensions 17. It can be seen that at the level of axial extensions, the various projecting portions 116 are widened in the peripheral direction relative to the third bending zone 186 directly adjacent, which gives a larger tooth width. This allows adaptation to different types of teeth. In the continuous transition between the third bending range 186 and the axial extension 17, the advantage described above with reference to FIGS. 29-31, namely that the axial length of each tooth may be greater because the third bending zone 186 may also partially participate with its lateral surface area at the surface of the flanks.

In this embodiment, the surfaces of the flanks 48 have, with respect to the median longitudinal plane of each tooth 20, an inclination of an angle α of the order of 10 to 50%. This inclination can be achieved for example by machining after stamping the blank components, using a release tool or the like tool. For the rest, the embodiment of FIGS. 39 to 43 for the other parts of the embodiment and the operation correspond to the embodiments described above. In particular, as shown in FIGS. 42 and 43, this embodiment can also be used in connection with the mounting device 70 which uses the two annular elements 110, 112.

It should be noted that in the embodiments described above, for which a gear component may constitute either a drive member or a receiving member, and according to which by transformation of a steel blank to spring or other sheet blank, one can achieve such a component, the realization of the different teeth according to the type of embodiment of the teeth can be done before and after the transformation of a blank ma ma material or cut. For example when making the teeth by stamping or bending peripheral extensions, it is advantageous to perform this operation before the various axial extensions or radial projections have been bent into their shape. If the individual teeth are made by the axial extensions themselves, ie if the flank surfaces are at the thickness of the material or the wall, it is advantageous to bend first. the different axial extensions, then to make the surfaces of the flanks obliquely with a release tool or similar means. In carrying out this machining operation, for example, the various axial extensions 17, which deviate radially outwards with respect to the axis of rotation or slightly with respect to the third bending zone, may be and then terminated in a position parallel to the axis, which ultimately corresponds to the position taken by the axial extensions 17, and thus the teeth 19 carried by them when the clutch state is established. This means that the ramps made by clearing have exactly the shape they must have. For example, it is possible to simulate or similarly form the different teeth components after the axial extensions, fixing them in a tool and aligning the teeth parallel to the axis with the help of a tool. ; several tooth components can then be positioned successively in the axial direction with axial, aligned extensions, so that for a displacement operation in the axial direction, a clearance tool makes it possible to simultaneously treat several flank surfaces on different components. teeth.

It is furthermore advantageous to carry out a surface treatment on all the embodiments represented, after having carried out the various shaping operations so that, in particular in the different adjacent tooth surface areas of the different toothing, it is possible to avoid the appearance of wear phenomena.

The use of a body capable of being molded, made of stampable spring steel, to form the tooth components makes it possible in a simple manner to perform the multiple aspects set out above with regard to obtaining a certain stability or Spring elasticity, in that during the stamping operation, for example, the different radial projections are made with a decreasingly sloping profile, the slots are made, the transient rays between the different radial projections are suitably adjusted. and in that, following the shaping preparation, the different bending ranges or, if appropriate, the essentially non-curved areas which are between the bending ranges and, if appropriate, during the shaping preparation are provided. it is ensured that the different axial extensions are not bent in the peripheral direction. It should be noted that, among various hypotheses, it may be desirable that, in order to obtain sufficient rigidity, the different axial prolongations 17 be bent in the peripheral direction, that is to say, when looking in the peripheral direction, these have a circular shape or an approximate outline, ana logue.

Insofar as in the preceding description and in the claims, different directions are evoked, that is to say for example the axial direction or the radial direction or a direction substantially axial or substantially radial or essentially axial or essentially radial, these directions correspond to a main component of extension of the respective parts. But this does not mean that there is an exact alignment in the axial direction or in the radial direction; on the contrary, it is simply a directional indication allowing certain deviations for example in the angular ranges. Such deviations may even be desirable.

Claims (1)

<U> CLAIMS </ U> 1) Clutch installation comprising a mass of inertia on the drive side, co-operating in rotation with a drive member provided on the driving means, characterized in that the mass of inertia (31) comprises a receiving member (25) facing the drive member (23), said receiving member being provided with a toothing (51) and the driving member ( 23) has an axial extension (17) whose side facing the receiving member (25) has a toothing (19) of which at least one tooth (20) enters the gap (52) between each two teeth ( 53) of the toothing (51) of the receiving member (25), the teeth (20, 53) of at least one of the two sets of teeth (19, 51) being in radial prestress relative to the other den ture (19, 51) respectively. 2) Clutch installation according to claim 1, characterized in that the toothing (19) of the drive member (23) is formed on the flanks (47) of each tooth (20) with a wedge surface ( 48) so that each tooth (20) penetrates as a wedge (50) into the corresponding tooth gap (52) of the den ture (51) of the receiving member (25). 3) clutch installation according to claim 2, characterized in that the flanks (56) of each tooth (53) of the toothing (51) of the receiving member (25) each have a corner surface (54) angularly adapted to the corner surfaces (48) of the teeth (20) of the toothing (19) of the drive member (23) acting on both sides. 4) clutch installation according to claim 1, characterized in that the receiving member (25) ring-shaped (27) surrounds the axial extension (17) of the drive member (23). 5) Clutch installation according to claims 1 and 4, characterized in that the toothing (51) of the receiving member (25) is an internal toothing receiving the toothing (19) of the drive member (23). ) with prestressing directed radially outwards. 6) clutch installation according to claim 1 comprising a drive member having at least along a portion of its radial extension, an axial elastic flange, characterized in that the flange (15) has a bent portion ( 16) at least in the peripheral zone to form the axial extension (17). 7) Clutch installation according to claim 1, characterized in that the axial extension (17) of the drive member (23) is associated with at least one axial attachment (57) attached to the periphery. 8) clutch installation according to claim 7, characterized in that the axial attachment (57) is in the form of claw (59) movable radially which penetrates with a radial support (61) provided at its free end, in a radial cavity (63) provided on the receiving member (25). 9) Clutch installation according to claim 8, characterized in that the radial support (61) of the claw (59) wedge-shaped, penetrates with radial prestress in the radial cavity (63) of the receiving member ( 25). 10) clutch installation according to claim 9, characterized in that the radial cavity (63) is adapted by the shape of the radial support (61) of the claw (59). 11) Clutch installation according to claim 1, characterized in that to achieve the connection by meshing between the drive member (23) and the receiving member (25), there is provided a mounting device (70). ) which separates at least one tooth (20) of the drive member (23) against the action of the radial prestressing with respect to the receiving member (25) and the effect of which can be suppressed again a times commitment by catch, realized. 12) clutch installation according to claim 11, characterized in that the mounting device (70) surrounds the axial extension (17) and this wrapping is at least for the duration of the realization of the connection by taking into exertion a radial force directed inwards on at least one tooth (20). 13) clutch installation according to claim 12, characterized in that the mounting device (70) is formed by a clamping collar (71) which surrounds with a ribbon (72) the axial extension (17) and one end carries a screw housing (74) for receiving a clamping screw (73) whose thread penetrates into a threaded depression (76) at the free end (75) of the strip (72) and which generates a relative movement of the ribbon (72) relative to the screw housing (74) for inducing clamping by the threaded connection with the threaded depression (76) ,. Clutch device according to claim 12, characterized in that the mounting device (70) is formed by a pressure pipe (78) connected to a pressure source (80) by a pressure branch (79). ) and ensuring the tightening by the application of the pressure by extension of the diameter of its section. 15) Clutch installation according to claim 14, characterized by a protective sheath (83) associated with the pressure pipe (78). Clutch device according to claim 12, characterized in that the mounting device (70) is formed by a locking ring (84) axially slidable on a conical shaped segment (85) of the axial extension (17). ). Clutch device according to claim 12, characterized in that the mounting device (70) comprises a clamping loop (87) with spacing ends (88) by a respective pre-tension in the circumferential direction. Clutch device according to claim 12, characterized in that the mounting device (70) comprises a clamping loop (87) held with a fastening end (91) in a tool buffer (93) ( 90) and gripped by a pulling end (92) in a pulling means (94) movable relative to the pad (93). 19) Clutch installation according to claims 1 and 11, characterized in that the axial extension (17) has a straight axial end (98) provided with a driving surface (99) for the mounting device ( 70). 20) Clutch installation according to claims 7 and 19, characterized in that the free end (98) of the axial extension (17) solidly supports the axial attachment (57). Clutch device according to Claim 20, characterized in that the axial fastening (57) acts in the axial extension range of the toothing (19, 51) and penetrates into the toothing (51) provided in the actuator member. reception (25). 22) clutch installation according to claim 6, characterized in that the flange (15) is formed radially inside the coil (16) with at least one spring coil (96), elasti that. 23) clutch installation according to claim 22, characterized in that the elastic spring turn (96) of the flange (15) is provided with a damping means (100). 24) clutch installation according to claim 23, characterized in that the damping means (100) is made with at least one elastomeric element (102) which at least partially fills the free cavity (104) existing at the spring coil (96). 25) Clutch installation according to claim 1, characterized in that the receiving member (25) comprises a support (105) for an axial extension (110) receiving the toothing (51). Clutch device according to Claim 25, characterized in that the toothing (51) of the receiving member (25) on the outer radial side of the axial extension (110) is surrounded by an annular shape by the toothing (19) of the axial extension (17) of the drive member (23). 27) Clutch installation according to claim 25, characterized in that the support (105) of the receiving member (25) is formed by an elastic axial flange (106). 28) clutch installation according to claim 27, characterized in that the flange (106) of the receiving member (25) has an elastic spring behavior (108). Clutch assembly according to claims 11, 25, characterized in that the axial extension (110) has a bearing surface (114) for the mounting device (70). 30) clutch installation according to claim 29, characterized in that the bearing surface (114) is formed at the free end (112) of the axial extension (110). 31) clutch installation according to claim 1, characterized by at least one annular element (110, 112) having a deformation (122) which, when rotating at least one annular element (110, 112) around an axis of rotation (A), ensures the radial positioning of the component (23) with the internal toothing (19), and can be modified at its internal teeth (19). 32) Apparatus according to claim 31, characterized in that the deformation (122) is associated with each tooth or each group of teeth of the toothing (19) inner, with a ramp (126, 134) peripheral directed radially inwards having in the peripheral direction a variable distance from the axis of rotation (A). 33) Installation according to claim 32, characterized in that in the peripheral direction, a zone of minimum distance of the deformation ramps (126, 134) with respect to the axis of rotation (A) and / or a zone of maximum distance deformation ramps (126, 134) relative to the axis of rotation (A), is followed by a zone (128, 130, 136, 137) at a substantially constant distance from the axis of rotation (A). 34) Apparatus according to claim 31, characterized in that the mounting device (70) comprises two annular elements (110, 112). 35) Installation according to claim 34, characterized in that the two annular elements (110, 112) comprise deformation ramps (126, 134) directed each time oppo sively, and each tooth or group of teeth of the toothing (19) is associated with a pair formed of a deformation ramp (126, 134) of each annular element (110, 112). 36) Installation according to claim 34, characterized in that the two annular elements (110, 112) are preloaded in rotation in the circumferential direction, relative to each other and preferably correspond to a relative rotational position producing the clutch between the teeth (19, 51). 37) Mounting device according to claim 31, characterized in that the annular element (110, 112) comprises at least one socket (138) for a tool which can be rotated by the annular element (110, 112) around of the axis of rotation (A). 38) Installation according to claim 31, characterized in that the annular element (110, 112) is rotatably held on the respective component (23) having an internal toothing (19). 39) Installation according to claim 1, characterized in that the drive member (23) or the receiving member (25) have a central zone (115) extended by a set of elastic tongues (116), directed radially outwardly, and the radially outer zone of each tongue (116) has at least one tooth (20) of the toothing (19). 40) Apparatus according to claim 39, characterized in that the radial projections (116) have from the body (115), a width taken in the peripheral direction which decreases radially outwardly. 41) Apparatus according to claim 40, characterized in that the ratio A / I between the width of the outer radial zone and the width of the inner radial zone is in a range between 0.5 <A / I 5 1, 2 and this ratio is preferably equal to about 0.8. 42) Installation according to claim 39, characterized in that two neighboring radial projections (116) in the central region of the body (115) are connected by a transition (118) of curved shape. 43. Installation according to claim 42, characterized in that the curved transition has a radius of curvature greater than or equal to the thickness of the material of the toothing component (23) at the projections (116). 44) Installation according to claim 39, characterized by a ratio B / M between the width in the peripheral direction and the thickness of the material which is located, each time in the field of radial projections (116), in a range of B / M <30, and this ratio is preferably of the order of 10. 45) Installation according to claim 39, characterized in that starting from the central range of the body (11), the radial projections ( 116) are bent - in a first bending range (180), preferably substantially in the axial direction, - in a second bending range (184) substantially in the radial direction, outwards, - and then in a third range bending (186) again substantially in the axial direction and in that region (17) which extends substantially in the axial direction. 46) Apparatus according to claim 45, characterized in that the radius of curvature in the second and / or third bending ranges (184, 186) is greater than or equal to 1.5 times the thickness of the material of the tooth component (23) at the radial projections (116). 47) Apparatus according to claim 45, characterized in that the second and third bending ranges (184, 186) form a substantially continuous bending range, substantially in the shape of a semicircle. 48) Installation according to claim 45, characterized in that the radial projections (116) extending substantially in the axial direction and having a tooth, are not bent in the peripheral direction (17). 49) Installation according to claim 48, characterized in that the radial projections (116) are substantially not bent in the peripheral direction at the third bending zone (186) adjacent to the zone (17) carrying at least one tooth (20) and extending at least substantially in the axial direction. 50) Apparatus according to claim 39, characterized in that at least one of the radial projections comprises at least one slot (190) extending substantially in the radial direction. 51) Installation according to claim 50, characterized in that the slot (190) extends at least to the second bending zone (184) from the range (150) of the body. 52) Installation according to claim 1, characterized in that the teeth (20) of the toothing (19) have flanks (48) rotated in the circumferential direction and inclined relative to a longitudinal median plane (M) of the tooth corresponding to an angle of the order of 10 to 50, and preferably of the order of 20 to 30. 53) Installation according to claim 1, characterized in that the member (23) is made of a steel sheet, preferably a spring steel sheet and has tab-shaped projections (17, 116) having at least one region (17) axial or substantially axial provided with a tooth (20). 54) Installation according to claim 52, characterized in that each zone (17), substantially radial, comprises peripheral extensions (200, 202) curved in the radial direction to achieve the flank surfaces (48). 55) Installation according to claim 52, characterized in that the toothing (19) is open radially outwardly to receive a toothing (51) complementary open radially inwardly and the peripheral extensions (200, 202) are bent radially. towards the inside. 56) Apparatus according to claim 53, characterized in that the flank surface (48) is formed by lateral surface areas substantially in the circumferential direction and extending in each case substantially in the axial range (17). . 57) Installation according to claim 53, characterized in that the tooth (20) is formed on each zone (17) extending substantially axially, by stamping or deformation. 58) Apparatus according to claim 53, characterized in that the flank surfaces have an angle of inclination (a) with respect to the median longitudinal plane (M) of the corresponding tooth (20) in a range of 10 to 50 and preferably 20 to 30. 59) Installation according to claims 55 and 58, characterized in that the peripheral extensions (200, 202) of the substantially axial range, are bent to form the angle of inclination (a). 60) Apparatus according to claim 58, characterized in that the essentially peripheral side surfaces (48) have an angle of inclination (a) by manufacture or machining of the toothing (23).