Vibration damping device

Abstract

The invention relates to a vibration damper device (10) for a transmission of a motor vehicle, comprising a torque transmission flange (20), two rotationally connected guide elements (30) which are coaxial along an axis (X) and which are located on both sides of the torque transmission flange (20), helical compression springs (11) which are supported on the torque transmission flange and the guide elements, wherein a connecting disk (40) is attached to the torque transmission flange (20) by fastening regions (41) which are uniformly angularly distributed around the axis (X), the disk being arranged to be fastened to a flywheel.

Description

TECHNICAL FIELD

[0001] The present invention relates to a vibration damping device for a transmission of a motorized machine. The motorized machine can be a motor vehicle, a motorcycle or any other vehicle comprising at least one internal combustion engine. The motor vehicle can be a so-called commercial vehicle, for example a heavy vehicle, a public transport vehicle or an agricultural vehicle.

[0002] More particularly, the present invention relates to an improvement to a vibration damping device in which an axial misalignment compensation device is located between a flywheel of an internal combustion engine and a driven shaft of a gearbox. BACKGROUND

[0003] In the context of a hybrid motor vehicle, the transmission generally comprises an internal combustion engine, a gearbox, a coupling mechanism connecting the internal combustion engine to the gearbox, and an electric machine coupled to the transmission. Thus, the vehicle can sometimes run by the internal combustion engine and at other times by the electric machine, or sometimes by both the electric machine and the internal combustion engine.

[0004] It is sometimes necessary to filter the irregularities originating from the internal combustion engine upstream of the gearbox with a vibration damping device. This vibration damping device is generally mounted directly on the flywheel of the internal combustion engine and connected to the input shaft of the gearbox. This type of mounting generally creates problems of kinematic connection between the output of the device and the gearbox shaft. Due to the use of a large number of components within the transmission, the geometric positioning tolerances of the input shaft and the output shaft are large and are even amplified by the use of a rotating electric machine. Thus, there are static defects in the coaxiality between the electric machine shaft and the transmission input shaft, which are axial and angular. The specific function of the vibration damping device is to compensate for the difference in position between the output shaft connected to the internal combustion engine and the input shaft connected to the gearbox.

[0005] Likewise, when the internal combustion engine is in use, the rotation of the crankshaft transmits dynamic axial and / or nutation movements to the vibration damping device by the flywheel. The axial displacement measured on the outer periphery of the flywheel can reach peak-to-peak values of the order of a few millimetres. Another purpose of the vibration damping device is to compensate for the dynamic axial and / or nutation movements in order to avoid damaging the gearbox. SUMMARY

[0006] The present invention aims to overcome these technical problems by proposing an improved vibration damping device which is able to compensate for axial and angular tolerances and dampen the axial and / or nutation movements of the flywheel significantly better than the prior art.

[0007] Another purpose of the present invention is to provide a simple, efficient and economical solution to these problems.

[0008] It is a further object of the present invention to provide a vibration damping device that is able to reliably transmit the torque originating from the flywheel to the gearbox input shaft.

[0009] To this end, the invention proposes a vibration damping device for a transmission of a motorized machine, the vibration damping device comprising:

[0010] a torque transmission flange;

[0011] two guide elements that are coaxially rotationally connected along the rotation axis X via an intermediate hub and that are located on either side of the torque transmission flange;

[0012] helical compression springs that are directly or indirectly supported on the torque transmission flange and on the guide elements;

[0013] a connecting disc that is arranged to be fastened to the flywheel and that is fixedly connected on an inner periphery of the connecting disc to the torque transmission flange or to one of the guide elements;

[0014] and a device for compensating for axial misalignment between the flywheel and the transmission input shaft, the axial misalignment compensation device comprising at least one torque output hub that is equipped with an outer split and that is arranged radially inside an inner split of the intermediate hub, the inner split spline and the outer split spline each comprising an involute flank.

[0015] Advantageously, one of the inner split and the outer split of the axial misalignment compensation device can be enclosed inside the other, wherein a functional play is substantially uniformly distributed between the inner periphery of the split of the intermediate hub and the outer periphery of the split of the torque output hub. The functional play (measured in millimeters) can be measured when the axis of the inner split of the intermediate hub and the axis of the outer split of the torque output hub are coaxial.

[0016] Preferably, the functional play can be greater than a threshold value of 0.5 mm.

[0017] The vibration damping device according to the invention has the advantage that axial tolerances and angular tolerances are compensated for, and also the nutation movement of the flywheel due to the spline connection between the intermediate hub and the torque output hub. Due to the specific geometry of the inner split and the outer split, a kinematic freedom is obtained within the vibration damping device, which limits the mechanical stresses within the connecting disc.

[0018] Torque is also effectively transmitted by splines having involute flanks. Indeed, under the effect of the rotation of the flywheel, the inner and outer profiles of the splines having involute flanks cooperate to allow the teeth to roll and slide with respect to each other during the nutation of the torque output hub with respect to the intermediate hub. During the nutation, the teeth gradually and noiselessly engage and disengage. Due to the involute profile, the torque output hub is in contact with the intermediate hub on several teeth at the same time, which improves the mechanical fatigue strength of the splines.

[0019] Advantageously, the functional play can be equal to the value of the axial eccentricity between the axis of the flywheel and the axis of the transmission input shaft multiplied by a coefficient K, wherein K is between 1.2 and 1.8. Thus, the size of the functional play is a function of the possible axial and angular eccentricities between the axis of the flywheel and the axis of the input shaft of the transmission, of the length of overlap between the inner and outer splines, and of the manufacturing tolerances of the inner and outer splines. The coefficient K also takes into account the dynamic movements of the flywheel.

[0020] Preferably, the inner and outer splines can have a profile that allows several involute flanks to come into contact with each other at the maximum axial eccentricity of the torque output hub with respect to the intermediate hub, with a minimum spline base play in the direction of the eccentricity, such that the minimum play is strictly greater than 0. In this case, the minimum play in the direction of the maximum axial eccentricity is between the tooth tip of the outer spline and the spline base of the inner spline. This has the advantage of not wearing the end of the tooth located in the direction of the maximum eccentricity.

[0021] Advantageously, the inner and outer splines of the axial misalignment compensation device can be protected by a wear-resistant surface coating, for example a surface treatment or a heat treatment.

[0022] Preferably, the axial misalignment compensation device can comprise a resilient element for axially preloading the torque output hub on one of the guide elements along the axis X.

[0023] Advantageously, the axial misalignment compensation device can comprise a friction interface zone arranged between the side of the torque output hub and the flat face of one of the guide elements.

[0024] Preferably, the resilient element can be axially inserted between one of the guide elements and an axial retention ring inserted in an annular groove formed on the torque output hub.

[0025] Advantageously, two flat load application washers can be arranged on either side of the resilient element and between one of the guide elements and the axial retention ring. This limits the wear of the resilient element.

[0026] Preferably, the resilient element can be a conical washer or a corrugated washer.

[0027] As a variant, the elastic element can be inserted axially between one of the guide elements and the axial rim of the torque output hub.

[0028] This axial misalignment compensation device according to the application has the advantage of constantly pressing the torque output hub against one of the guide elements and thus of reducing the noise within the vibration damping device.

[0029] Advantageously, the connecting disc can be attached to the torque transmission plate or to one of the guide elements via fastening regions that are angularly distributed around the axis X and arranged to be fastened to the flywheel via anchoring regions that are angularly distributed around the axis X, each anchoring region being attached to at least two fastening regions by a separate connecting arm.

[0030] Preferably, the connecting disc can comprise cavities formed by the alternation of the connecting arms. Thus, the connecting disc is perforated so that it is flexible without affecting its mechanical strength when subjected to torque.

[0031] Advantageously, the connecting arms originating from the same anchoring region can extend in separate angular directions so that these connecting arms reach their corresponding fastening regions. The connecting arms are separate from each other and independently transmit torque to the torque transmission flange or to one of the guide elements.

[0032] Preferably, the anchoring regions of the connecting disc associated with the flywheel can be located on a mounting diameter D that is greater than the mounting diameter d of the fastening regions associated with the torque transmission flange or with one of the guide elements.

[0033] According to one variant, the connecting disc can be fastened to the torque transmission flange by means of rivet connections comprising a series of rivets located in fastening orifices of the disc and in corresponding holes of the torque transmission flange.

[0034] Preferably, the connecting disc can comprise, in a plane perpendicular to the axis X, two axes of minimum bending stiffness that are perpendicular to each other and one of the two axes passes through two fastening regions that are at opposite angles relative to the rotation axis X.

[0035] Advantageously, the connecting disc can comprise, in a plane perpendicular to the rotation axis X, two axes of symmetry that are perpendicular to each other. These two axes of symmetry can correspond to the axes of minimum bending stiffness.

[0036] Advantageously, the torque transmission plate can comprise openings for receiving helical compression springs, the fastening regions of the disc being angularly distributed between the receiving openings. Thus, the distribution of mechanical stresses within the connecting disc is substantially uniform on the periphery of the torque transmission flange.

[0037] Preferably, the guiding element can be rotationally connected to the intermediate hub by means of a rivet or a weld.

[0038] For example, the guiding element can be a guiding washer formed from a stamped metal sheet.

[0039] According to one embodiment of the application, the helical compression spring can be indirectly supported on the opening in the torque transmission flange and on the opening in the guiding washer by means of abutment means located on the two coaxial parts, the abutment means comprising, for example, spring seats placed at the ends of the helical compression spring.

[0040] According to another of the aspects of the application, the application also relates to a transmission sub-assembly for a transmission of a motorized machine, the transmission sub-assembly comprising:

[0041] a flywheel,

[0042] a vibration damping device comprising all or some of the above-mentioned characteristics, the vibration damping device being fastened to the flywheel, and

[0043] fastening screws, the fastening screws being inserted into the anchoring zone of the vibration damping device and being threadably coupled to the flywheel.

[0044] The transmission sub-assembly according to this other aspect of the application has the advantage that it can be preassembled in the factory before being delivered to the customer. BRIEF DESCRIPTION OF DRAWINGS

[0045] The application will be better understood by reading the following description, given solely by way of example, and with reference to the appended drawings in which:

[0046] Figure 1 is an axial sectional view of a transmission of a motorized machine comprising a vibration damping device according to a first embodiment of the application;

[0047] Figure 2 is Figure 1 is an exploded isometric view of a vibration damping device according to a first embodiment of the application in a motorized machine;

[0048] Figure 3 is Figure 1 is a front view of an axial misalignment compensation device according to a first embodiment of the application in a motorized machine when the two pairs of hubs are in alignment;

[0049] Figure 4 is Figure 1 is a front view of an axial misalignment compensation device according to a first embodiment of the application in a motorized machine when the two pairs of hubs are eccentric;

[0050] Figure 5 is an isometric view of a vibration damping device according to a second embodiment of the application;

[0051] Figure 6 is a front view of a connecting plate according to a second embodiment of the application. DETAILED DESCRIPTION

[0052] In the following description and claims, by way of non-limiting example and for ease of understanding, the terms "front" and "rear" will be used according to a direction of axial orientation determined with respect to a main rotation axis X of a transmission of a motorized machine of the industrial vehicle type, and the terms "inner / inside" and "outer / outer" will be used with respect to the axis X and according to a radial orientation orthogonal to said axial orientation.

[0053] Figures 1 to 4 A transmission 1 of a motorized machine of the industrial vehicle type comprising a vibration damping device 10 according to a first embodiment of the application is illustrated.

[0054] The industrial vehicle comprises in particular an internal combustion engine, a gearbox comprising a rotating electric machine (not shown), and a transmission sub-assembly 8 interposed between the internal combustion engine and the gearbox. The transmission sub-assembly 8 comprises:

[0055] a flywheel 2 having a rotation axis X,

[0056] a vibration damping device 10 fastened to the flywheel 2, fastening screws 3 inserted into the vibration damping device 10 and threadedly coupled to the flywheel.

[0057] The transmission sub-assembly 8 has the advantage that it can be pre-assembled in kit form in the factory before delivery to the customer.

[0058] The vibration damping device 10 comprises a torque transmission flange 20 having an annular shape around the rotation axis X, rotationally connected to the flywheel, guide elements 30 and a helical compression spring 11. The two guide elements 30, also called guide washers 30, are located on either side of the torque transmission flange 20, thereby clamping the helical compression spring 11 in a built-in housing. The guide washers 30 are fastened together to an intermediate hub 62 via rivets 18. This architecture of the vibration damping device 10 is called "symmetrical" when the engine torque first enters the vibration damping device through the torque transmission flange 20.

[0059] As illustrated in Figure 1 and Figure 2 , the coaxial parts 20 and 30 are rotationally mounted with respect to each other against a damping means, here comprising the helical compression spring 11. The helical compression spring 11 is directly supported on an opening 21 in the torque transmission flange 20 and on an opening 31 in the guide washers 30.

[0060] The end of the helical compression spring 11 is adapted to rest on the lateral edge of the opening 21 in the annular flange 20 and on the lateral edge of the opening 31 in the guide washer 30. The helical compression spring 11 is circumferentially distributed around the axis X.

[0061] When the engine torque passes through the vibration damping device 10, the angular displacement between the guide element 30 and the torque transmission flange 20 changes, causing the helical compression spring 11 to compress. The torque transmission flange 20 pivots around the intermediate hub 62.

[0062] Each guide washer 30 is formed from a stamped metal sheet of substantially constant thickness and includes an opening 31 and an outer annular portion 32 for receiving a spring 11. The outer annular portion is adapted to guide the spring 11 when the annular flange 20 undergoes angular displacement relative to the guide washer 30.

[0063] Friction devices 12 and 13 are further located between each guide washer 30 and torque transmission flange 20.

[0064] The helical compression spring 11 and friction devices 12, 13 enable the absorption and damping of vibrations and rotational irregularities originating from the internal combustion engine, as is known per se.

[0065] In one variation (not shown), the helical compression spring 11 can be indirectly supported on an opening 21 in the torque transmission flange 20 and an opening 31 in the guide washer 30 by means of mating devices located on two coaxial parts 20 and 30. More specifically, the mating device includes a spring seat placed at the end of the spring 11 and a recess formed in the guide element 30 and the torque transmission flange 20. The spring seat is adapted to interact with the recess formed in the guide element 30 and / or the torque transmission flange 20 about the pivot connection.

[0066] According to the present invention, the vibration damping device 10 includes a connecting plate 40 attached to a torque transmission flange 20 and fastened to a flywheel 2. Fastening screws 3 threaded to the flywheel 2 apply a clamping force to the connecting plate 40 to transmit the torque generated by the engine toward the gearbox.

[0067] like Figure 2 As shown, the connecting plate 40 includes an even number of anchoring regions 42 that are evenly angularly distributed around the axis X; more specifically, four anchoring regions 42 are evenly angularly distributed around the axis X at an angle of 90 degrees.

[0068] like Figure 1 and Figure 2 As shown, the connecting disc 40 is fastened to the torque transmission flange 20 by a riveting connector, which includes a series of rivets 17 located in the fastening orifice 45 of the disc and the corresponding hole 25 of the torque transmission plate.

[0069] Engine torque enters the vibration damping device 10 via the connecting disk 40 and exits via the torque output hub 15 which is centrally arranged to the vibration damping device 10. The torque output hub 61 is mounted on a driven shaft 6 of a gearbox (not shown) having a rotational axis Y and transmits engine torque via teeth 65 formed on an inner bore of the torque output hub.

[0070] At each rotation of the engine, the crankshaft transmits axial and / or bending vibrations to the vibration damping device 10 by means of the flywheel 2. The displacement measured on the outer periphery of the flywheel can then reach peak-to-peak values of the order of several millimeters.

[0071] As shown in Figure 1 , after assembly of the transmission of the motorized machine, an axial and angular offset can exist between the output shaft of the internal combustion engine having a rotational axis X and the input shaft of the gearbox having a rotational axis Y. In this case, the axial and angular offset measured between the axis X and the axis Y can reach values of the order of one millimeter and / or one degree.

[0072] The main object of the present invention is therefore to provide an improved vibration damping device which is able to compensate for axial and angular tolerances and dampen the axial displacement of the flywheel. An axial misalignment compensation device 60 is added between the flywheel of the motorized machine having the vibration damping device 10 and the transmission input shaft to allow the torque output hub 61 to more easily follow the position of the driven shaft 6 of the gearbox.

[0073] The arrangement of the axial misalignment compensation device 60 according to the first embodiment of the present invention will now be described in more detail with reference to Figures 1 to 4 .

[0074] The axial misalignment compensation device 60 acting between the flywheel and the transmission input shaft particularly comprises a torque output hub 61 equipped with an outer splined 63 and radially arranged inside an inner splined 64 of an intermediate hub 62, the inner and outer splined 64, 63 both comprising involute flanks. The involute flank geometry ensures a greater mechanical fatigue strength and limits the wear between the inner and outer splined. The inner and outer splined 64, 63 are rectilinear.

[0075] To ensure the axial misalignment compensation capacity between the flywheel and the transmission input shaft, one of the inner and outer splined 64, 63 of the axial misalignment compensation device is enclosed inside the other, with the functional play J substantially uniformly distributed between the inner periphery of the splined of the intermediate hub and the outer periphery of the splined of the torque output hub (see Figure 3 ). The functional play is greater than the threshold of 0.5 mm. The tolerance of the uniform distribution of the functional play is of the order of + / - 0.1 mm. The functional play applies to the outer and inner diameter of the splined.

[0076] More precisely, the functional play J is equal to the value of the maximum axial eccentricity E between the axis of the flywheel and the axis of the transmission input shaft multiplied by a coefficient K, where K is between 1.2 and 1.8. This sizing of the functional play is thus a function of the possible axial and angular eccentricity E between the axis of the flywheel and the axis of the input shaft of the transmission device, for example the gearbox, of the overlap length between the inner and outer splines, which is approximately between 15 and 40 mm, and of the manufacturing tolerances of the inner and outer splines.

[0077] On the basis of the design complying with the standard NF E22-141, the inner and outer splines 64, 63 are determined in particular by the following influencing parameters: the number of teeth, the modulus corresponding to the pitch p divided by π, the nominal diameter D1, the pitch diameter d, the outer diameter d2 and the pressure angle a. These parameters are also visible in Figure 3 With respect to the standard dimensions, the inner or outer splines 64, 63 according to the application are locally thinned. In particular, the inner and outer splines 64, 63 have a profile which allows several involute flanks to come into contact with each other at the maximum axial eccentricity E of the torque output hub 61 with respect to the intermediate hub 62, with a minimum spline base play Jminin the direction of the eccentricity, such that the minimum play Jminis strictly greater than 0. As Figure 4 illustrated, the minimum play Jminin the direction of the maximum axial eccentricity E is between the tooth tip of the outer spline 63 and the spline base of the inner spline 64.

[0078] According to the application, the inner and outer splines 64, 63 of the axial misalignment compensation device can be protected by a wear-resistant surface coating, for example a surface treatment of the nickel plating type, or a thermal treatment of the high-frequency surface hardening type.

[0079] In order to damp the dynamic movements coming from the flywheel 2, the axial misalignment compensation device 60 comprises an elastic element 67 for axially preloading the torque output hub 61 along the axis X in one of the guide elements 30.

[0080] As Figure 1 and Figure 2 illustrated, the elastic element 67 is axially inserted between one of the guide elements 30 and an axial retaining ring 68 inserted in an annular groove 61a formed on the torque output hub 61. Preferably, the elastic element 67 is a conical washer. As a variant, the elastic element 67 can be a bellows washer.

[0081] To limit the wear on the elastic element, two flat load-applying washers 69 can be arranged on either side of the elastic element 67 and between one of the guide elements 30 and the axial retaining ring 68. The axial misalignment compensation device 60 comprises a friction interface zone 70 arranged between the side 61b of the torque output hub 61 and the flat face 30b of one of the guide elements. Thus, the torque output hub 61 is constantly pressed against one of the guide elements 30 and thus reduces the noise within the vibration damping device.

[0082] As a variant, the elastic element 67 can be axially inserted between one of the guide elements 30 and the axial rim of the torque output hub 61.

[0083] Reference is made to Figure 5 and Figure 6 A vibration damping device 10 according to a second embodiment of the application will now be described, in which the connecting disc 40 is attached to the torque transmission plate via fastening zones that are angularly distributed around the axis X and arranged to be fastened to the flywheel via anchoring zones that are angularly distributed around the axis X, each anchoring zone being attached to at least two fastening zones by a separate connecting arm.

[0084] As Figure 5 illustrated, the connecting disc 40 comprises an even number of anchoring zones 42 that are angularly distributed uniformly around the axis X; more particularly, four anchoring zones 42 are angularly distributed uniformly around the axis X at an angle of 90 degrees. The four anchoring zones 42 are identified by way of illustration by dashed lines that substantially correspond to the bearing areas on the flywheel 2.

[0085] In this example, each anchoring zone 42 of the connecting disc 40 comprises several anchoring orifices 44 that are angularly offset from one another around the axis X. Each anchoring zone comprises three anchoring orifices 44 that are angularly offset by an angle of 15 degrees relative to the axis X.

[0086] According to a further possible example, the anchoring orifices in the same anchoring zone can be angularly offset from one another around the axis X by an angle of between 10 and 45 degrees.

[0087] As Figure 6 illustrated, the connecting disc 40 comprises an even number of fastening zones 41 that are angularly distributed uniformly around the axis X; more particularly, six fastening zones 41 are angularly distributed uniformly around the axis X at an angle of 60 degrees.

[0088] The six fastening zones 41 are borne on the torque transmission flange 20 and each of the fastening zones 41 of the connecting disc 40 comprises two fastening orifices 45.

[0089] In this example, the number of anchoring zones 42 is less than the number of fastening zones 41.

[0090] The torque transmission flange 20 comprises openings 21 for receiving the helical compression springs 11, the fastening zones 41 of the disc being angularly distributed between each receiving opening 21. The distribution of the mechanical stresses in the disc is therefore substantially uniform on the periphery of the torque transmission plate.

[0091] In order for the connecting disc 40 to be flexible axially, each anchoring zone 42 is connected to at least two fastening zones by a separate connecting arm 43. The connecting arms 43 are separate from one another and independently transmit the torque to the torque transmission flange 20.

[0092] The connecting arms 43 originating from different anchoring orifices 44 can intersect and interleave. The connecting disc 40 particularly comprises cavities 46 formed by the interleaving of the connecting arms, which makes the vibration damping device flexible. The anchoring zones 42 of the connecting disc 40 associated with the flywheel 2 are located on a mounting diameter D that is greater than the mounting diameter d of the fastening zones 41 associated with the torque transmission plate 20.

[0093] In this example, one of the anchoring zones 42 of the connecting disc 40 associated with the flywheel 2 is offset by an angle A of 15 degrees relative to an axis X3 passing through two fastening zones 41 that are at opposite angles relative to the rotation axis X. This 15-degree offset of the axis X3 has the effect of increasing the number of connecting arms 43 and increasing the torque transmission capacity of the connecting disc 40. This effect also occurs when the angle A is between 5 and 25 degrees.

[0094] The connecting disc 40 also comprises, in a plane P’ perpendicular to the axis X, two axes X1, X2 of minimum bending stiffness, the axes X1, X2 of minimum bending stiffness being perpendicular to one another and one of the two axes X1 passing through two fastening zones 41 that are at opposite angles relative to the rotation axis X. The axis X1 is not coincident with the axis X3. The axes X1, X2 of minimum bending stiffness correspond to preferred axes around which the disc 40 can more easily bend and deform. The stiffness can be measured by applying a load in newtons in a direction perpendicular to the plane P’ on the periphery of the disc, for example in the anchoring zones 42. The stiffness is measured only on the connecting disc 40, i.e. when the connecting disc is not assembled on the vibration damping device.

[0095] Advantageously, the connecting disc 40 comprises, in a plane perpendicular to the rotation axis X, two axes of symmetry X1, X2 that are perpendicular to one another. The two axes of symmetry X1, X2 that are perpendicular to one another correspond to axes of minimum bending stiffness.

[0096] The connecting disks 40 have a uniform geometry, regularly distributed around the axis X. The distribution of the mechanical stresses within the connecting disks 40 is substantially uniform over the periphery of the torque transmission flange 20.

[0097] Each connecting arm 43 comprises, in a plane P parallel to the axis X, a material section having a thickness E and a width L, such that the ratio L / E is greater than 10.

[0098] The connecting disks 40 are preferably made of a steel sheet, the thickness of which can be variable. According to a variant, the connecting arms 43 can comprise a variable thickness E over all or part of the extent of the connecting arms and / or a variable width L over all or part of the extent of the connecting arms.

[0099] The application is not limited to use in an industrial vehicle transmission as described above. The vibration damping device 10 can also be incorporated into the transmission of a "conventional" motorized machine that does not comprise a rotating electric machine.

Claims

1. A vibration damping device (10) for a transmission device of a motorized machine, the vibration damping device comprising: Torque transmission flange (20); Two guide elements (30) are rotatably connected coaxially along the axis of rotation (X) via an intermediate hub (62) and located on both sides of the torque transmission flange (20); A helical compression spring (11) is directly or indirectly supported on the torque transmission flange and the guide element; A connecting disc (40) is arranged to be fastened to the flywheel and fixedly connected on its inner periphery to either the torque transmission flange (20) or one of the guide elements (30); And an axial misalignment compensation device (60) for compensating for axial misalignment between the flywheel and the drive input shaft, the axial misalignment compensation device including at least one torque output hub (61), the at least one torque output hub being equipped with an outer slot (63) and radially arranged inside the inner slot (64) of the intermediate hub (62), both the inner slot spline and the outer slot spline (63, 64) including involute sides.

2. The vibration damping device (10) according to claim 1, characterized in that, One of the inner slots and outer slots (63, 64) of the axial misalignment compensation device (60) is surrounded inside the other, wherein the functional clearance (J) is substantially uniformly distributed between the inner periphery of the inner slot (64) of the intermediate hub and the outer periphery of the outer slot (63) of the torque output hub.

3. The vibration damping device (10) according to claim 1 or 2, characterized in that, The inner slot and the outer slot (63, 64) have contours that allow a plurality of involute sides to contact each other at the maximum axial eccentricity (E) of the torque output hub (61) relative to the intermediate hub (62), wherein there is a minimum spline base clearance (Jmini) in the eccentricity direction, such that the minimum spline base clearance (Jmini) is strictly greater than 0.

4. The vibration damping device (10) according to claim 1 or 2, characterized in that, The axial misalignment compensation device (60) includes an elastic element (67) for axially preloading the torque output hub (61) along the rotation axis (X) onto one of the guide elements (30).

5. The vibration damping device (10) according to claim 4, characterized in that, The axial misalignment compensation device (60) includes a friction interface region (70) disposed between the side surface (61b) of the torque output hub (61) and the flat surface (30a) of one of the guide elements.

6. The vibration damping device (10) according to claim 4, characterized in that, The elastic element (67) is inserted axially between one of the guide elements (30) and the axial retaining ring (68), which is inserted into an annular groove (61a) formed on the torque output hub.

7. The vibration damping device (10) according to claim 6, characterized in that, Two flat load-applying washers (69) are arranged on both sides of the elastic element (67) and are located between one of the guide elements and the axial retaining ring (68).

8. The vibration damping device (10) according to claim 1 or 2, characterized in that, The connecting disc (40) is attached to the torque transmission flange or one of the guide elements via fastening areas (41), the fastening areas being angled around the axis of rotation (X) and arranged to be fastened to the flywheel via anchoring areas (42) angled around the axis of rotation (X), each anchoring area (42) being attached to at least two fastening areas (41) via a separate connecting arm (43).

9. The vibration damping device (10) according to claim 8, characterized in that, The connecting arm (43) originating from the same anchoring area (42) extends in a separate angular direction, such that the connecting arm reaches the corresponding fastening area (41) of the connecting arm.

10. The vibration damping device (10) according to claim 8, characterized in that, The connecting disc (40) includes cavities (46) formed by the interlacing of the connecting arms (43).

11. The vibration damping device (10) according to claim 8, characterized in that, The connecting disc (40) includes two axes (X1, X2) with minimum bending stiffness in a plane (P') perpendicular to the axis of rotation (X), the axes (X1, X2) with minimum bending stiffness being perpendicular to each other, and one of the two axes (X1, X2) passing through two fastening regions (41), the two fastening regions being angularly opposite each other with respect to the axis of rotation (X).

12. The vibration damping device (10) according to claim 11, characterized in that, The connecting disk (40) includes two symmetrical axes (X1, X2) that are perpendicular to each other and correspond to the axis with minimum bending stiffness in a plane perpendicular to the axis of rotation (X).

13. A transmission subassembly (8) for a transmission device (1) for a motorized machine, the transmission subassembly comprising: Flywheel (2), The vibration damping device (10) according to any one of claims 1 to 12, wherein the vibration damping device is fastened to the flywheel (2), and A fastening screw (3) is inserted into the anchoring area (42) of the vibration damping device and threaded to the flywheel.

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