FR2796681A1 - 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 integrally in rotation with a drive member acting on the drive.

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 play in the toothing does not prevent that, the teeth do start 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 Cl, 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 com carrying a toothing and the drive member, an axial extension also provided with a toothing on its side facing the receiving member and of which at least one tooth comes into the tooth gap between each two teeth of the teeth of the receiving member, - the teeth of at least one of the two teeth being pre-stressed radially 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 denier 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 furthermore an axial elasticity is applied in the connection of the converter housing with the crankshaft, 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 achieved at its free end, such as a receiving surface for the mounting device, for acceptable mounting forces, high radial prestressing can be achieved between the 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 installation comprising a first component with a first toothing mounted on one of the assemblies, and the other assembly comprising a second component with a toothing, the two teeth interpenetrating radially with a radial preload in the meshing. Such a clutch installation is preferably provided with a mounting device according to the invention.

As already mentioned above, the various components used for clutching in such clutch installations must satisfy two contrary 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, in particular as a drive member or receiving member for a clutch installation according to the invention, a toothed component formed of a central body, from which radially outwardly a set of elastic 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 a ratio equal to 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 form 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 can for example be made so that starting from the range of the body, it extends at least until the level of 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.

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, Figure 7 corresponds to the object of Figure 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. Figure 9 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, - FIG. 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; embodiment of a mounting device, - Figure 15 is a simplified axial view of the view of Figure 14, this view being taken according to Figure 14 by firing from the right, for the engaged state, - Figure 16 is a view corresponding to that of the Figure 15 but when the engaged state is not realized, - Figure 17 is a view corresponding to that of Figure 15 showing further pre-stressing elements, - Figure 18 is an axial view. of the two rings of the mounting device situated one above the other, FIG. 19 is a view corresponding to that of FIG. 18, also showing the pre-tension element, FIG. 20 shows an enlarged detail of FIG. 19, - FIG. 21 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. 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 Figs. a mounting device according to the invention 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 the line of section; XXVII-XXVII of Fig. 26; Fig. 28 is a variant of the toothing component shown in Fig. 26; Fig. 29 is a perspective view of another variant of the toothing component of Fig. 26; FIG. 30 shows the tooth component 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. 30. 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 screw 9 with a threaded rod 11. A radial flange iale 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 resilient 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 designed as 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 mass of inertia, driving a flywheel with two masses as for example that described in the DE document 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 on the one side, 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 direction of the tooth base 55 on the receiving member 25 can thus clamp the tooth 20 in the tooth gap 52 without the tooth reaches the tooth base 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. Thus a clearance-free fixing is achieved in the circumferential direction of the clutch device and the converter housing 35 on the crankshaft 3. In order for the converter housing 35 to remain in this axial position, the device drive 23 comprises two claws 59, shifted 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, the den ture 19 has not been shown in detail, with the exception of the cutting zone of the teeth 19 neatly called. 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 conical 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 internal diameter of the Conversely, a displacement of the clamping ring 84 in the opposite direction allows the extension of the axial extension 17 to 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 the outside on the axial extension 17. This or the latter 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 the pulling end 92 is held in a pulling means 94. This pulling means 94 is generally a clamp. 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 floor 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. Note firstly that contrary to the variants described above, the drive member 23, for example of spring steel, comprises a central zone 115 in the form of a disk which continues in the peripheral direction that, by a succession of tabs 116 in the form of of 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 figu res 14 23 comprises two annular elements 110, 112 rotatably supported 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 achieved for example by shaping, matting or a similar process, applied to the free end 98 of the axial extension 17. This means that the drive member 23 may form a preassembled 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, on several peripheral positions, an attack formation 138 for an actuating tool. The attacking formations 138 of the annular element 110 comprise an oblong hole 140 followed by an opening 142. Correspondingly, the etching formation 138 of the annular element 112 comprises an oblong hole 144 partially concealed followed by An opening 146. Since the two annular elements 110, 112 are identical and are arranged in opposite directions with respect to each other, the oblong hole 114 of the annular element 110 partly 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 hidden part 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 which 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 annular elements. 110, 112 even though the two end segments have been fully slid through the openings 142, 146. It should be noted that FIGS. 18, 19, 20 show a situation in which the axial extensions 17 of the respective resilient tabs 116 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, in which it appears that the teeth of the toothing 19 penetrate practically completely between each pair of teeth of the toothing 51.

As can be seen for example in FIGS. 17, 19, 22, the two annular elements 110, 112 may have cavities 150 facing each other, which are superposed in the relative rotational position shown in FIGS. 20. These cavities 150 house substantially H-shaped leaf spring elements 152 which hold the two annular elements 110, 112 axially together by respective notches or cavities 154, 156 and which further provide prestressing. 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 we arrive in the relative rotational position of the annular elements 110, 112 shown in FIGS. 16 and 22. When this relative rotation is performed, the different deformation ramps 126, 134, which are associated each time 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 drive member 23 and the receiving member 25, the tool introduced into the openings 142, 146 can be disengaged so that the action of the leaf spring elements 152 rotates. again the annular elements 110, 112 relative to each other so that in the opposite direction, the deformation ramps 126, 134 slide over the leading surface area 99 and the axial extensions 17 are again moved radially outwardly by the elasticity of the spring tongues 116 until finally one reaches the position of the toothing 19 shown in Figures 15, 17, 23, 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 release of the two annular elements 110, 112, when removing the tool, the prestressing of the axial extensions 17 directed radially towards the outside necessarily turns the annular elements 110, 112 in the position shown for example in Figure 23. This means that in such an embodiment can be completely deleted areas 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, the different drive formations 138 are preferably distributed at an angular interval of 90 which makes it possible 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 pre-tension leaf spring members may be envisaged. In principle, it should be noted that the embodiments shown of the mounting device 70 with two annular elements 110, 112 are preferential because a simple movement of two segments together by an actuating tool makes it possible to perform a rotational movement. In principle, it would also be possible to envisage a construction of the mounting device 70 from a single annular element, for example of the annular element 112, which is then rotated by means of a tool. corresponding actuation, 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 outward, they release them . Prior to the assembly of the drive member 23 with the receiving member 25, for example, the drive member 23 must be held and the annular element 110 rotated until the zones 130 are in position. 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 moved axially on the receiving member 25 and the teeth of the toothing 19 has already penetrated between the teeth of the toothing 51, by blocking the cover 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 110 is rotated again by blocking the receiving member 25 to move the axial extensions 17 radially inwards.

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 116 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 to form 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 it appears in particular in FIG. 27, starting from the zone of the body 115, the projecting portions 116 firstly have a first bending zone <B> 180 </ B> in which these projections are first bent. in an angle inclined relative to the direction of the rotational axis, substantially in an angular range of 0 to 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 third bending zones 189, 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 for 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 passage in the form of an arc or circle to avoid stress concentrations. 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 size. 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 117 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 In the range of the given values, the angle α is first determined by the fact that the component of the radial force generated by the engagement with a complementary toothing, 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 manufacturing tolerances and measurements at the teeth 19, 51 which mesh, 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. It would then be necessary to perform relatively large radial movements to compensate for small measurement inaccuracies, and to take the grip between the teeth. For flanks 48 if flat-bedded, already for a relatively low axial movement, manufacturing or measurement inaccuracies within a range of axial movement of the axial extensions 17 must be compensated for so that it does not lead to not to a significant change in the prestressing force by which the teeth 20 are pressed radially outwardly.

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 of the 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 various radii of curvature or transient ranges can also be used here advantageously.

It should be noted that the drive members 23, shown in Figures 26 to 31, can be applied to all the embodiments shown above in combination with Figures 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.

It should be noted that insofar as the preceding text and the claims refer to different directions, for example the axial direction or the radial direction or a substantially axial or substantially radial or essentially axial or essentially radial direction, this reference means that this corresponds to the main extension component of the respective parts. This does not mean that it is necessary to have an exact extension in the axial direction or in the radial direction each time but that it is simply a predetermined direction with respect to which one can have different deviations, for example in the indicated angular ranges or that these de viations may even be desirable.

Claims (1)

<1> Clutch installation comprising a mass of inertia on the drive side, cooperating in a manner integral with a rotationally acting on a driving member, characterized in that the inertia mass (31) comprises a receiving member (25) facing the drive member (23), said receiving member (25) comprising a toothing (51) and the driving member (23), - an axial extension (17) also provided with a toothing (19) on its side facing the receiving member (25) and at least one tooth (20) comes to take in the tooth gap (52) each time between two teeth (53) of the toothing (51) of the receiving member (25), the teeth (20, 53) of at least one of the two teeth (19, 51) being in radial prestressing with respect to the other respective denaturing (19, 51). 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 shaped surface wedge (48) so that each of the teeth (20) comes as a wedge (50) in the gap of the corresponding teeth (52) of the toothing (51) of the receiving member (25). 3) clutch installation according to claim 2, characterized in that each of the teeth (53) of the toothing (51) of the receiving member (25) is provided on its tooth flanks (56) with a on respective wedge-shaped face (54), angularly adapted to the wedge-shaped surfaces (48) of the teeth (20) of the den ture (19) of the drive member (23), engaging on both sides. 4) Clutch installation according to claim 1, characterized in that the receiving member (25) is ring-shaped (27) and surrounds the axial extension (17) of the drive member (23). ). 5) Clutch installation according to one of claims 1 and 4, characterized in that the toothing (51) of the receiving member (25) is in the form of internal teeth in which penetrates the toothing (19) of the driving member (23) with a prestress directed radially outwards. 6) clutch installation according to claim 1, comprising a drive member which has an axial elastic flange, at least along a portion of its radial extension, characterized in that the flange (15) has at least a bent portion (16) in the peripheral area to form the axial extension (17). 7) clutch installation according to claim 1, characterized in that at least one axial locking means (57) is associated with the axial extension (17) of the drive member (23) relative to the periphery. 8) clutch installation according to claim 7, characterized in that the axial locking means (57) is in the form of claw (59) movable radially, and a radial support (61) provided at one of its ends. free, comes to take 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) is wedge-shaped and comes under radial prestress in the radial cavity (63) of the body of reception (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 by a mounting device (70) for making the connection by engagement between the driving member (23) and the receiving member (25), said retracting device at least one tooth (20) of the drive member (23) against the action of the radial bias train relative to the receiving member (25) and its effect can be suppressed after having made this connection by outlet. 12) clutch installation according to claim 11, characterized in that the mounting device (70) surrounds the axial extension (17) and this surround is at least for the duration of the realization of the grip by exerting a radial force directed inwards on at least one tooth (20). Clutch device according to Claim 12, characterized in that the mounting device (70) is formed by a clamping collar (71) which surrounds the axial extension (17) with a ribbon (72) and end of a screw housing (74) for receiving a clamping screw (73), the thread of which engages in a threaded recess (76) at the free end (75) of the ribbon (72) and which, to begin an operation of clamping, produces a relative movement of the band (72) relative to the screw case (74) by the screw connection with the screw 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 which, when applying a pressure ensures the tensioning of its section by increasing its diameter. 15) Clutch installation according to claim 14, characterized in that the pressure pipe (78) comprises a protective sheath (83). Clutch device according to Claim 12, characterized in that the mounting device (70) is formed by a locking ring (84) which is axially slidable on the conically 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) having a respective bias in the circumferential direction. Clutch device according to Claim 12, characterized in that the mounting device (70) has a clamping loop (87) held by a fastening end (91) in a tool buffer (93) ( 90) and clamped with a pulling end (92) in a pulling means (94) relatively movable with respect to the pad (93). 19) clutch installation according to claim 1 and claim 11, characterized in that the axial extension (17) has a straight axial end (98) provided with a bearing 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) carries the axial attachment (57). 21) clutch installation according to claims 7 and 20, characterized in that the axial attachment (57) acts in the axial extension zone of the teeth (19, 51) and comes into the teeth (51) provided on the receiving means (25). 22) clutch installation according to claim 6, characterized in that the flange (15) is formed radially inside the bent portion (16) with at least one elastic spring coil (96). 23) clutch installation according to claim 22, characterized in that the elastic spring coil (96) is provided at the flange (15) of a damping means (100). 24) clutch installation according to claim 23, characterized in that the damping means (100) is made with at least one elastomer element (102) which at least partially fills the free space (104) existing at level of 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) provided with the toothing (51). Clutch device according to claim 25, characterized in that the toothing (51) of the receiving member (25) is formed on the outer radial side of the axial extension (110) and is surrounded by the axial extension ( 17) of the drive member (23) with its toothing (19) in an annular form. 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 effect (108). Clutch assembly according to claims 11 and 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 11, characterized in that the mounting device (70) is feasible in the form of a clutch or clutch between the teeth (19, 51) of two components (23, 25), the toothing (19, 51) is engaged at least radially and the toothing (19) radially inward is biased radially outwardly against the toothing (51) radially outwardly and the component (23) , which has the toothing (19) radially on the inside, is deformable radially, elastically, at least at its toothing (19), the mounting device (70) comprises at least one annular element (110, 112) mounted with rotation or being rotatably mounted on the component (23) having a toothing (19) located radially inward, at least one annular element (110, 112) has a deformation (122) which, by rotation at least one annular element (110, 112) at rotation of an axis of rotation (A) makes it possible to modify the radial positioning of the component (23) which has a set of teeth (19) located radially inwards, at the level of this toothing (19) located radially at the inside. 32) clutch installation according to claim 31, characterized in that the deformation (122) comprises, associated with each tooth or cha group of teeth of the toothing (19) located radially inward, a deformation ramp ( 126, 134) extending in the peripheral direction, and directed radially inwards, this ramp being at a variable distance from the axis of rotation (A), in the peripheral direction. Clutch device according to claim 32, characterized by an area (128, 130, 136, 137) having a substantially constant distance from the axis of rotation (A) in the circumferential direction, in an area of minimum distance of the deformation ramp (126, 134) from the rotational axis (A) and / or in a zone of maximum distance from the deformation ramp (126, 134) relative to the axis of rotation (A). 34) Clutch installation according to one of claims 31-33, characterized in that it comprises two annular elements (110, 112). 35) clutch installation according to claim 34 or one of claims 32 or 33, characterized in that the two annular elements (110, 112) have deformation forming ramps (126, 134) each opposing, and each tooth or each group of teeth of the radially inwardly-arranged toothing (19) is associated with a pair each formed of a deformation ramp (126, 134) of each annular element (110, 112). . 36) Clutch installation according to claim 34 or 35, characterized in that to make a clutch or disengagement between the teeth (19, 51), the two annular elements (110, 112) are rotated about the axis rotation (A) in opposited directions. 37) Clutch installation according to one of claims 34 to 36, characterized in that the two annular elements (110, 112) are preloaded relative to each other to rotate in the peripheral direction, preferably in a relative rotational position corresponding to the establishment of a meshing between the teeth (19, 51). 38) Clutch installation according to one of claims 31 to 37, characterized by at least one annular element (110, 112) having at least one tool-forming formation (138) for a tool allowing at least one element annular (110, 112) to rotate about the axis of rotation (A). 39) clutch installation according to one of claims 31 to 38, characterized in that at least one annular element (110, 112) is rotatably mounted on at least one component (23) toothing (19) radially to inside. 40) clutch installation according to claim 1, characterized by - a central body area (115) with a set of projections (116) in the form of resilient tongues turned radially outwards and in a radially outer area of each protrusion (116), at least one tooth (20) of a toothing (19) is provided. 41) clutch installation according to claim 40, characterized in that starting from the body region (115), the radial projections (116) have, radially outwardly, a width which decreases in the peripheral direction. 42) A clutch assembly according to claim 1, characterized in that the ratio A / 1 between the width in the outer radial zone and the width in the inner radial zone is in the range of 0.5 to <A / 1 S 1,2 and is preferably of the order of 0.8. 43) Clutch installation according to one of claims 40 to 42, characterized by a transition (188) substantially arcuate between two adjacent radial projections (116) at the central region (115) of the body. 44) A clutch assembly according to claim 43, characterized in that the arcuate transient area has a radius of curvature greater than or equal to the thickness of the material of the toothing component (23) at the radial projections (116). 45) Clutch installation according to one of claims 40 to 44, characterized by a ratio B / M between the width in the peripheral direction and the thickness of the material each time in the range of the radial projections (116). is in a range of 5 5 B / M <_ 30, and this ratio is preferably of the order of 10. 46) Clutch installation according to one of claims 40 to 45, characterized in that starting from the central region (115), the radial projections (116) are first bent in a first bending range (180), preferably substantially in the axial direction, and then in a second bending range (184) essentially in a radially outward direction, then in a third bending range (186), again substantially in the axial direction and in that range (17) which extends at least approximately in the axial direction, the extensions comprise at least less than one tooth (20 ) of the toothing (19). 47) Clutch installation according to claim 46, characterized by a radius of curvature of the second and / or third bending range (184, 186) greater than or equal to 1.5 times the thickness of the material of the component toothing (23) at the level of the radial projections (116). 48) Clutch installation according to one of claims 46 or 47, characterized in that the second and the third bending range (184, 186) form a substantially continuous bending range, substantially in the shape of a semicircle. . Clutch device according to one of claims 46 to 48, characterized in that the radial projections (116) extend essentially in the axial direction and are not bent in at least one zone (17) with tooth in the peripheral direction. Clutch device according to claim 49, characterized in that the radial projections (116) are substantially not bent in the circumferential direction at the third bending zone (186), extending essentially in the direction axial with a zone (17) carrying at least one tooth (20). 51) A clutch assembly according to at least one of claims 40 to 50, characterized in that at least one of the radial projections has at least one slot (190) extending preferably substantially in the radial direction . Clutch device according to one of claims 51 and 46, characterized in that the slot (190) extends from the body (150) to at least the second bending range. (184). 53) clutch installation according to claim 1, comprising a toothing component (23) according to one of claims 40 to 52 as a drive member (23) and / or as a receiving member (25).