FR3117563A1 - PRE-SHOCK ABSORBER MODULE WITH LOCKING MEANS - Google Patents

Abstract

PRE-SHOCK MODULE WITH LOCKING MEANS The invention claims a pre-damper module (M) for a torsion damper assembly (1), of axis (X) of revolution, comprising: - a first cage (10), arranged to be received inside a torque input element (7, 71, 72, 50, 4, R1), - a second cage (20), arranged to come to bear on a central web (4) of the torque input element (7, 71, 72, 50, 4, R1), the first and second cages (10 , 20) being coaxial and mounted one on top of the other at the level of support zones (150, 250), - a web (30), receiving a series of springs (R2) and being of fluted shape to be connected to a torque output element (6), the first and second cages (10, 20) being arranged axially on either side on the other side of the veil (30) so as to receive the springs (R2) and said veil (30), in which the first and second cages (10, 20) each comprise at their external periphery (14, 24): - support edges (15, 25) forming the support zones (150, 250) of the first and second cages (10, 20), and - locking means (15A, 25A, 15A', 25A') formed on the supporting edges (15, 25) of the first and second cages (10, 20), said locking means (15A, 15A') of the first cage (10) cooperating jointly with said locking means (25A, 25A') of the second cage (20), said locking means (15A, 25A) being configured in such a way as to securely connect the first cage (10) and the second cage (20) by clipping. Figure for abstract: FIGURE 2

Description

PRE-SHOCK ABSORBER MODULE WITH LOCKING MEANS

The invention relates to a pre-damper module for a torsion damper assembly, in the field of friction clutches. The invention also relates to a torsion damper assembly comprising such a pre-damper module, as well as an assembly kit for a vehicle transmission, comprising such a pre-damper module.

The torsion damper assembly is used for a clutch able to selectively connect the internal combustion engine to the gearbox, to filter vibrations due to engine acyclisms. The torsion damper assembly can be used for a hydrodynamic torque converter or for a clutch disc.

Such a torsional damper assembly is used to reduce the level of vibration generated by frequency irregularities in the rotation of the flywheel. The damping function, qualified by the progressive stiffness of the damping means and the control of the coefficient of friction, must ensure optimal operation. Such an assembly can be integrated into a clutch disc mounted on the central hub and carrying peripheral friction linings.

The torsion damper assembly is of the type comprising, on the one hand, a main damper, formed in part by a first series of so-called load springs, housed in the clutch disc and, on the other hand, a pre -damper formed in part by a second series of so-called low-load springs (of smaller size), mounted on a central web, which is fixed inside said clutch disc and which cooperates with guide washers and of friction.

It is possible to compress the second series of springs between two retaining plates and a central web. These parts of the pre-shock absorber are made of metals, and can form a cassette, mounted axially next to the central web. The central web must then be riveted to the central hub. But such a solution has drawbacks.

The cassette cannot be closed manually. The metal parts are difficult to position and assemble together, making it difficult to lock the pre-shock absorber. The use of an auxiliary tool is always necessary. The same applies to the positioning and assembly of the cassette within the damping device, for example, to rivet the central web to the central hub using another auxiliary tool. Some parts may be different depending on the type of application (diesel or gasoline, vehicle transmission torque, etc.). Retaining plate bearings may have unacceptable visual defects. The use of an auxiliary tool does not allow reliable centering of the parts.

The assembly steps, the weight and the cost of producing such a device are therefore high. In addition, the number of parts of the main shock absorber and the pre-shock absorber is substantial and cumbersome. It is necessary to reduce the size, in particular the number of parts, while preserving the functions of the main shock absorber and the pre-shock absorber.

The object of the invention is to provide a simple, efficient and economical solution to this problem. For example, the purpose of the invention is to simplify the assembly of the pre-shock absorber and its mounting within the damping.

For this purpose, the invention proposes, according to a first aspect, a pre-damper module for a torsion damper assembly, of axis X of revolution, comprising:
- a first cage, arranged to be received inside a torque input element,
- a second cage, arranged to come to bear on a central web of the torque input element, the first and second cages being coaxial and mounted one on the other at the bearing zones,
- a veil, receiving a series of springs and being of fluted shape to be connected to a torque output element, the first and second cages being arranged axially on either side of the veil so as to receive the springs and said veil ,
wherein the first and second cages each comprise at their outer periphery:
- bearing edges forming the bearing zones of the first and second cages, and
- locking means formed on the bearing flanges of the first and second cages, said locking means of the first cage cooperating jointly with said locking means of the second cage, said locking means being configured in such a way as to bind integrally the first cage and the second cage.

According to the invention, the positioning and assembly steps are simplified for such a pre-damper module, thanks to the bearing edges of the cages and their locking means, which cooperate jointly. These allow you to manually enclose the veil of the pre-shock absorber module and the springs inside the cages, in a simple, fast way, without the need for special tools, while limiting their radial and axial dimensions.

The locking means offer better visibility for the operator, being arranged on the radially peripheral support edges of each cage.

Thanks to these characteristics, better positioning of the cages is possible, one on top of the other, at their outer periphery, on their support edges. By "support edges", we mean on their surface support zones extending discontinuously around the X axis, on each cage. The bearing edges of each cage define a minimum height for the series of springs. They can be angularly spaced from each other, unlike a continuous and linear support surface. By “locking means”, here is defined means for closing the cages.

By forming bearing edges on each of their outer periphery, the remaining part of each cage no longer forms a bearing. The space between two adjacent support edges of a cage can partly receive neighboring parts of the pre-damper module or those of the torsion damper assembly, such as, for example, the end of the low module load or the end of the main shock absorber load springs.

The shape of the cages can be simplified, for example, by reducing its dimensions and/or performing other functions, such as the close reception of the veil and the series of springs. Any angular offset is avoided, the cages reliably guiding the parts they contain.

Advantageously, the locking means of the first and second cages are clipping means. In other words, said locking means can be configured in such a way as to solidly link the first cage and the second cage by clipping. By “clipping means”, we mean here retaining means, of complementary shapes and intended to be embedded or embedded in one another. The clips thus allow the maintenance of cages around or inside an axis of cooperation generally having a groove. It is a mechanical support by elasticity of the material. These means are therefore arranged axially opposite each other, cooperating jointly by mechanical retention by elasticity.

The design of such a system for locking or closing the cages then simplifies their assembly, by making it possible to hold a first cage securely on a second cage using clips. We differentiate the clip from a simple ratchet or fastener, because the clips are mounted simply by mechanical action, for example from the outside, guaranteeing mechanical retention by elasticity. The cages are firmly held together while limiting their axial spacing.

Advantageously, the pre-damper module can therefore form a unitary sub-assembly (also called “cassette”) previously mounted manually by the operator. The transport and handling of such a pre-assembled module are simplified. The design and assembly of the module are simplified and optimized. It is specified that the clipping means of a cage are made here in one piece, or in one piece for the same cage.

The locking means of the first cage can subsequently be called the “first locking means”.

The locking means of the second cage can be called the “second locking means”.

The veil of the pre-damper module can subsequently be called a “training veil”.

This first aspect of the invention may have one or other of the characteristics described below, combined with each other or taken independently of each other:

– The veil of the pre-damper module can be a torque output veil;

– At least one of the first and second cages is made of plastic;

– Preferably, the first and second cages can be made of plastic;

– In such situations, the locking means of the cages can be made of plastic material. Such a material further improving their assembly by the operator and their post-assembly mechanical retention by elasticity of the plastic.

– In other words, locking or closing the cages no longer requires the need to exert significant mechanical stress, or special tools. This plastic cage(s) has the advantage of being also resistant to wear, flexible and of having a very high elongation. Weight, costs and material losses are significantly reduced.

– By “plastic material”, we mean materials based on polymers, synthetic or artificial, capable of being molded, shaped, generally under heat and under pressure. Material removal operations (cutting, machining) are thus avoided by making each of the plastic parts, for example by molding;

– The support edges of the first and second cages can be circular, conical or polygonal, for example cage corners, of substantially triangular shape;

– The bearing edges of the first and second cages can be of identical and/or complementary shapes;

– The support edges of the first cage and the second cage can be arranged facing each other;

– The support edges of the first cage can extend in the direction of the support edges of the second cage, and vice versa;

– The support edges of a cage can be distributed angularly around the X axis, following a regular distribution;

– The locking means of a cage can be of identical shape, or alternatively, of different shapes. For example, growths or housings of the same cage can be of identical or different shapes;

– The locking means of the first cage can be of complementary shapes to the locking means of the second cage. By way of example, the first locking means can be of female shapes and the second locking means can be of male shapes, or vice versa. They are then fitted into each other to close the module, and close the cages together. Any kind of cooperation of male-female forms is possible;

– The number of locking means for each cage can be even, or alternately, odd;

– Preferably, the two cages can comprise an identical number of locking means. These locking means can be arranged axially opposite each other, to facilitate assembly thereof;

– Advantageously, the first and second cages may each comprise positioning means cooperating together and formed on the bearing edges of the cages. The centering and indexing of the cages is possible manually as soon as the cages are supported, without the need for preparatory work for the operator. These positioning means can also increase the resistance to rotation of one cage relative to the other;

– The means of positioning a cage can be of identical shape. As a variant, the means for positioning a cage can be of different shapes. For example, excrescences or housings of the same cage can be together of identical shape, or alternately, of different shapes;

– The number of positioning means for each cage can be even, or alternately, odd;

– Preferably, the two cages can comprise an identical number of positioning means. These positioning means can be arranged axially facing each other, to facilitate mounting their indexing;

– Preferably, each cage may comprise a limited number of locking means, for example strictly less than five, preferably equal to two means per cage. The advantage here is to avoid having to apply more force to clip all the cages, so that the assembly of the cages is held correctly once the module is mounted;

– Similarly, each cage may include a limited number of positioning means, for example strictly less than five, preferably equal to two means per cage.

– In such situations, it will thus be easier to adjust the production parameters and the tooling to obtain a good flatness of the contact plane between parts, if there are means formed in a limited number. The locking and positioning means can be limited, for example, by influencing their shape or the dimensioning given to these means;

– The locking means of the first cage can be of complementary shape to that of the locking means of the second cage. Similarly, the means for positioning the first cage may be of a shape complementary to that of the means for positioning the second cage;

– In particular, the locking and positioning means can be distributed alternately around the X axis, for example alternately one by one;

– Advantageously, one of the cages may include protrusions formed on its support edges, adapted to be received in housings formed on the support edges of the other cage. In other words, the first cage may comprise protuberances, or respectively housings, formed on its bearing edges and adapted to cooperate with housings, or respectively protrusions, formed in the support edges of the second plate. The advantage here is to identify each of the cages, thanks to the excrescences and housings cooperating with each other.

– A protrusion of one cage can extend axially towards a housing of the other cage;

– The growths of a cage can be distributed angularly, following a regular distribution;

– The housings of a cage can be distributed angularly, following a regular distribution;

– In a first example, protrusions are formed on the bearing edges of the first cage, so as to be received in housings formed in the bearing edges of the second cage;

– In a second example, housings are formed on the bearing edges of the first cage, so as to receive protuberances formed in the bearing edges of the second cage. The advantage of these examples is to distinguish the two cages between them, thanks to the excrescences and the housings cooperating between them;

– The first and second examples can be combined. By way of example, the first cage and the second cage can each comprise protrusions and housings formed on their bearing edges. In this situation, the growths and the housings of the same cage can be distributed alternately around the X axis;

– The protrusions can form stiffeners, in order to guarantee anti-rotation of the two cages between them;

– The growths of a cage can be portions of male shape, and can be of identical shape.

– The growths may be rounded in shape and/or with a substantially rounded edge;

– The growths can be polygonal, triangular, rectangular, or even trapezoidal. Some growths can be, in a plane orthogonal to the X axis, in the shape of a tooth, a hook or an overhang;

– The housings of a cage can be portions of female shape, and can be of identical shape.

– The housings can be rounded in shape, or even polygonal in shape, for example, of the triangular, rectangular or trapezoidal type. Preferably, the housings can be, in a plane orthogonal to the axis X, a cavity, a channel or even a through opening;

– The bearing edge of a cage may have a thickness E _R1 , E _R2 measured along a reference axis;

– A protrusion may have a thickness E _L2 extending from the bearing area of the bearing edge, which is measured along another axis parallel to the reference axis. In particular, said reference axis is in the axial direction;

– The housing may have a wall, of axial extension E _L1 , which is measured along another axis parallel to the reference axis. In particular, said reference axis is in the axial direction;

– The axial dimension E _L1 of a wall of the housing can be between 25% and 100% of the thickness E _R1 of a bearing edge of said cage. Alternatively or additionally, the axial dimension E _L1 of a wall of the housing may be between 25% and 100% of the thickness E _A1 of the central web of said cage;

– In a particular case, the housing can be through. Therefore, the axial dimension of a wall of a housing can be equal to 100% of the thicknesses E _R1 of a support flange and E _A1 of the central web, that is to say that the housing is of the through type, emerging axially on either side of the cage. In addition, the housing does not include a bottom.

– In another case, the housing can be non-through and it can include a bottom, forming a support surface intended to receive the protrusion. The housing can be delimited axially between its bottom and the support area of a support flange.

– Consequently, the axial dimension of a wall of a housing can be strictly less than 99% of the thicknesses E _R1 of a support rim and E _A1 of the central web;

– In particular, each support seat can be opened radially inwards;

– The growths of a cage can be complementary in shape to that of the housings of the other cage. The advantage here is to simplify the assembly of the cages manually, without the need for special tools;

– For example, the protrusion of a cage may include a groove cooperating with a rib formed in the housing of the other cage. Therefore, the groove can be of the shape complementary to that of the rib. The protuberances and/or the housings can be distributed angularly around the axis X, following a regular distribution;

– The thickness (or axial dimension) E _L1 , E _L2 of a groove of a protrusion can be between 25% and 100% of the thickness E _R1 , E _R2 of a support rim of said cage . Alternatively or additionally, the thickness E _L1 , E _L2 of a groove of a protuberance can be between 25% and 100% of the thickness E _A1 , E _A2 of the central web of said cage;

– Advantageously, at least two of the protuberances form the locking means of a cage, and at least two of the housings form the locking means of the other cage. Preferably, the protuberances and the housings forming the means for locking the cages are of complementary shapes;

– For example, the first cage may comprise at least two protuberances forming the first locking means, and the second cage may comprise at least two housings forming the second locking means;

– Alternatively or in addition, the first cage may comprise at least two housings forming the first locking means, and the second cage may comprise at least two protuberances forming the second locking means;

– Advantageously, at least one of the protuberances form the means for positioning a cage, and at least one of the housings forms the means for positioning the other cage. Preferably, the protuberances and the housings forming the means for positioning the cages are of mutually complementary shapes;

– For example, the first cage may comprise at least two protuberances forming the first positioning means, and the second cage may comprise at least two housings forming the second positioning means. Alternatively or in addition, the first cage may comprise at least two housings forming the first positioning means, and the second cage may comprise at least two protuberances forming the second positioning means;

– According to a first variant, the protrusions forming the locking means and the positioning means may be of identical shape to each other. Similarly, the housings forming the locking means and the positioning means may be of identical shape to each other. The manufacture of the cages is simplified here;

– According to a second variant, the protrusions forming the locking means may be of different shape from those forming the means for positioning the cages. Similarly, the housings forming the locking means may be of different shape from those forming the means for positioning the cages;

– By way of example, the positioning means of a cage can be formed by a solid protrusion;

– For example, the locking means of a cage can be formed by a hollow protrusion.

– In such a situation, the locking means can be formed inside an outgrowth of a cage. For example, it is partly formed by a groove formed in said protrusion. Such a difference in shapes makes it possible to form a mistake-proof device avoiding an erroneous assembly between the locking means and the positioning means;

– The groove can be placed on the face of a protrusion closest to the X axis.

– In other words, the groove of a protrusion can be open radially on the inside;

– The groove can be arranged on the face of a protrusion farthest from the X axis;

– In other words, the groove of a protrusion can be open radially on the outside;

- In particular, the second cage may comprise at least two protrusions inside which is formed a groove, each protrusion groove forming in part a locking means of the second cage;

- In particular, the first cage may comprise at least two housings inside which is formed a rib, each housing rib forming part of a locking means of the first cage;

– By way of example, the positioning means can be formed by a housing wall emerging axially on either side of the cage. Therefore, the housing forming the positioning means does not include any stepped shape;

– By way of example, the locking means can be formed inside a housing of a cage, in other words, by a stepped-shaped housing. Therefore, the locking means can be formed by a bottom in relief of the housing. For example, it is partly formed by a rib formed in said housing. Such a difference in shapes makes it possible to form a mistake-proof device avoiding an erroneous assembly between the locking means and the positioning means;

– The rib of a housing can be arranged as close as possible to the X axis. In other words, the rib of a housing can extend radially on the inside;

– The rib of a housing can be arranged furthest from the X axis;

– In other words, the rib of a housing can extend radially on the outside;

– The central core of the first cage may comprise a crown, of cylindrical or conical shape, extending from the internal periphery of the first cage. The crown here forms the radially internal periphery of the central core of the first cage. In particular, said crown may be arranged to bear against the torque input element, in particular against a torque output hub;

– The ring gear can be designed to be centered by a clutch disc guide washer;

– The crown can be intended to center the torque input element, in particular a torque output hub.

In such a situation the crown may be conical in shape. Consequently, the first cage of such a module can form a double function, those of direct centering of the torque hub and/or of the clutch disc, and of second hysteresis zone rubbing with the torque hub;

– Advantageously, the first cage may comprise a central web delimited axially between:
- a first bearing face, arranged to come to rest inside the torque input element, and
- A second support face, on which the veil of the pre-damper module is supported;

– Preferably, the first bearing face and second bearing face may be circumferential, for example of circular shape, over 360 degrees around the axis X. In addition, they may be axially opposite one another. other ;

– In particular, the torque input element can be formed by a clutch disc and a main damper;

– In particular, the torque input element can be a torque output hub;

– In such a situation, the pre-damper module can be:
- on one side, received inside a clutch disc, and
- on the other, press against the main shock absorber;

– The first cage of the pre-damper module can then be received inside a clutch disc;

– The second cage of the pre-shock absorber module can then be arranged to rest on a central veil of the main shock absorber. In particular, the first circumferential bearing face of the first cage is arranged to bear inside the clutch disc;

– Advantageously, the first cage may comprise a first friction zone called the main hysteresis zone F1, intended to rub on the torque input element. In particular, the first friction zone, called the main hysteresis zone, may be intended to rub against the clutch disc;

– In this way, the central core of the first cage can include said first friction zone. Said first friction zone can be arranged axially opposite the locking means of the first cage.

– Preferably, the first friction zone can be formed on the first bearing face of the central core. In particular, such a module thus forms directly from one of its cages, a hysteresis zone rubbing on the torque input element, here on the clutch disc;

– Advantageously, the first cage may include a second friction zone, called secondary hysteresis zone F2, intended to rub on the torque output element. In particular, the second friction zone, called the secondary hysteresis zone F2, can be intended to rub on the torque hub.

– In this way, the central core of the first cage can include said second friction zone.

– Preferably, said second friction zone can be formed by the second bearing face of the central core, or by the inner periphery of the first cage, in other words the inner periphery of the central core of the first cage ;

– Preferably, the second circumferential bearing face can be formed by a flange extending from the central core of the first cage, on which the veil of the pre-damper module rests. The flange can be annular or cylindrical in shape. In other words, said second friction zone can be formed by the annular flange or by the conical crown of the first cage;

– For example, said second friction zone can be formed on the second bearing face of the central web. In this way, such a module forms directly from one of its cages, a dual function, those of support for the veil of the pre-damper module and of second hysteresis zone rubbing with the torque output element, in particular with torque hub;

– For example, said second friction zone can be formed on the inner periphery of the central core of the first cage, for example, by the conical crown of the first cage.

Similarly, such a module can form directly from one of its cages, a dual function:
- that of centering the torque output element, for example of a torque output hub and/or of the torque output element, for example of a clutch disc, and
- that of friction, with a second hysteresis zone rubbing with the torque output element, for example of a torque output hub;

– In particular, said second friction zone can be arranged radially opposite the locking means of the first cage. Therefore, the second friction zone can be arranged as close as possible to the X axis;

– The collar can be continuous, that is to say extending over 360 degrees around the axis X. Alternatively, the collar can be discontinuous, so as to form support portions distributed angularly around the axis. x-axis;

– The flange can be arranged as close as possible to the X axis. The advantage here is to position and center the web of the pre-damper module as close as possible to the torque output element, for example the output hub of torque, in particular the spline of the web of the pre-damper module with respect to that of the torque hub;

– In other words, the collar of the first cage can be arranged radially opposite the locking means of said cage, for example, at the level of the internal periphery of the first cage;

– The second circumferential bearing face can be arranged radially opposite the locking means of the first cage. In particular, the flange can be arranged as close as possible to the X axis. The advantage here is to position and center the web of the pre-damper module as close as possible to the torque output element, for example the hub of torque, in particular to ensure the connection of the splines of the web of the pre-damper module and of the torque hub;

– Preferably, the central core of the first cage may include support seats partly receiving the series of springs, said support seats being arranged axially between the first and second circumferential support faces of the first cage. In particular, the support seats can open onto the first circumferential support face;

– The veil of the pre-damper module may include an internal spline intended to be connected to the torque output element, for example to a torque hub;

The invention also relates, according to a second aspect, to a torsion damper assembly, comprising:
- a main damper comprising a torque input element adapted to be connected to a driving shaft,
- a torque output element adapted to be connected to a driven shaft,
- a pre-damper module according to any one of the preceding claims, in which
the veil of the pre-damper module and the torque output element are mounted linked in rotation with each other,
the first cage being mounted so as to be able to rotate with respect to the torque input element, at the level of a first friction zone called the main hysteresis zone F1, and
the second cage being mounted fixed in rotation with respect to the torque input element by bearing against the torque input element.

Thus positioned, the first cage of the pre-damper module rubs and thus generates hysteresis, by pressing against the torque input element and by rotational mobility on the torque input element.

Thanks to these characteristics, the assembly of such a torsion damper assembly is simplified, while offering better visibility for the operator, in order to correctly position the pre-damper module. The assembly of such a torsion damper assembly is carried out manually, simply and quickly, without the need for any special tools for the operator. The size of said assembly is also limited, in particular by its parts close to each other.

This second aspect of the invention may have one or other of the characteristics described below, combined with each other or taken independently of each other:

– The second cage can be mounted fixed in rotation relative to the torque input element by means of guide studs inserted inside the torque input element. Preferably, the guide studs of the second cage can be of complementary shapes to the openings of the input element which receive them, so as to fit the guide studs into the input element;

– The torque input element may be a clutch disc, formed of at least one guide washer and friction linings supported by said guide washer.

– In particular, the friction linings are located on the periphery of said guide washer;

– The torque output element can be a torque output hub, capable of being connected to a driven shaft;

– In particular, the torque output hub may be of the splined type. For example, the torque output hub may include an internal spline and an external spline. In such a situation, a spline of the torque output hub is arranged to be connected to a spline of the web of the pre-damper module;

– In particular, the torque hub spline is an external spline. In this situation, the external spline of the torque output hub is arranged to be connected to the spline of the web of the pre-damper module;

– The main shock absorber may comprise at least one series of springs and a central web receiving the series of springs;

– In particular, the first cage of the pre-damper module may rub on said guide washer of the clutch disc, at the level of a first friction zone called the main hysteresis zone. Specifically, the first cage can be rotatably mounted relative to said guide washer of the clutch disc;

– In particular, the second cage can rest on the central veil of the main shock absorber. Specifically, the second cage can be mounted fixed in rotation with respect to the central veil of the main shock absorber by bearing against the central veil of the main shock absorber;

– The torque output element, in particular the torque output hub, can be received inside the pre-damper module, so that the spline of the torque output hub is connected to a spline of the web of the pre-damper module. The torque output hub is arranged radially closest to the X axis, forming the central hub;

In particular, the groove of the veil of the pre-damper module is an internal groove;

– The main shock absorber springs have larger diameters than those of the pre-shock absorber module springs;

– The pre-damper module can be inserted axially between the guide washer and the main damper;

The at least one guide washer can carry peripheral friction linings. By way of example, the clutch disc may comprise two guide washers, one of which carries peripheral friction linings;

– The main damper can be inserted axially between the two guide washers of the clutch disc;

– The pre-damper module can be arranged axially between the two guide washers of said disc;

– The guide washers can be interconnected by fixing means, such as spacers;

– Alternatively, the fixing means can be spacers, pins or even rivets;

– The main damper can be fixed integrally to the clutch disc by fixing means;

– At least one notch can be formed in the extension of the external spline of the torque output hub, inside which the web of the pre-damper module comes to rest. Preferably, each of the teeth of the external spline of the torque output hub comprises a notch.

In other words, the external spline of the torque output hub comprises a series of notches, inside which the web of the pre-damper module comes to rest. Such notches make it possible to simply assemble the torque output hub on the pre-shock absorber module, without the need for additional fixing means or special tools, such as riveting to connect them together;

– The torque output hub may comprise a shoulder, of cylindrical or conical shape, formed in the extension of the spline of the torque output hub. Such a shoulder is intended to receive the inner periphery of the first cage;

– In particular, it can receive a crown, of cylindrical or conical shape, of the first cage. Such a shoulder has the advantage of simply assembling the torque output hub on the pre-shock absorber module, without the need for additional fastening means or special tools, such as riveting to connect them together. This facilitates the assembly of said torsion damper assembly, thanks to the flange of the first cage interposed radially between the torque output hub and the flange of the clutch disc.

– The crown of the first cage, cylindrical or conical in shape, can receive at least one clutch disc guide washer. The advantage of such a crown is to center the pre-damper module on the guide washer of the clutch disc, to avoid any axial shift of the parts during assembly;

– For example, the torque output hub shoulder can be tapered. Similarly, the first cage may include a crown of conical shape, so as to center the output hub on the crown of conical shape of the first cage. Therefore, said shoulder can be centered on the conical crown of the first cage. Such a conical crown has the advantage of a dual function, those of centering the torque output hub and of the second hysteresis zone rubbing with the torque output hub.

– The shoulder can be an extension of material, produced for example by recessing the material;

The invention also relates, according to a third aspect, to an assembly kit for a torsion damper assembly, comprising:
- A clutch disc, formed of at least one flange carrying peripheral friction linings;
- a main hysteresis mechanism, called main damper, comprising
at least one series of so-called load springs, with a diameter greater than that of the springs of the pre-shock absorber module, and
a central veil receiving the series of so-called load springs;
- a pre-damper module according to any one of the preceding characteristics, adapted to be received on a flange of a clutch disc;
- A torque hub, of the splined type, received inside the pre-damper module, the splines of the torque output hub being arranged to be connected to splines in the web of the pre-damper module; And
- Fixing means intended to tie solidly together, the pre-damper module, the main hysteresis mechanism and the clutch disc.

The fixing means can be spacers, pins or even rivets;

The invention also relates, according to a fourth aspect, to an assembly kit for a vehicle transmission, comprising a torsion damper assembly comprising a pre-damper module according to any one of the preceding characteristics.

Advantageously, the assembly kit may further comprise:
- a rigid steering wheel; and or
- a release bearing; and or
- a clutch mechanism;

In particular, the rigid flywheel can be a flywheel.

In particular, the clutch mechanism may comprise at least one clutch diaphragm, and/or a multi-plate clutch assembly. The clutch mechanism may include at least one friction clutch.

In particular, the clutch(es) can be of the dry or wet type. By "wet" clutch, we mean a clutch suitable for operation in an oil bath or oil mist.

The invention will be better understood, and other aims, details, characteristics and advantages thereof will appear more clearly during the following description of a particular embodiment of the invention, given solely by way of illustration and not limiting, with reference to the appended figures:
– is an exploded perspective view of a torsion damper assembly comprising a pre-damper module, according to a first embodiment of the invention;
– is a view in axial section of the torsion damper assembly, with in particular the means for locking the cages, according to the first embodiment illustrated in ;
– is another view in axial section of the torsion damper assembly, with in particular the means for positioning the cages, according to the first embodiment illustrated in ;
– is another view in axial section of the torsion damper assembly, according to the first mode illustrated in ;
– is another view in axial section of the torsion damper assembly, according to the first mode illustrated in ;
– is an exploded perspective view of the pre-damper module, according to the first mode illustrated in ;
– is a perspective view of the cages of the pre-shock absorber module, according to the first mode illustrated in ;
– is a "front" view of the pre-assembled pre-shock absorber module, according to the first mode illustrated in ;
– is a "rear" view of the pre-assembled pre-shock absorber module, according to the first mode illustrated in ;
– is a detailed view of a locking means, according to the first mode illustrated in ;
– is a detailed view of another locking means, according to the first mode illustrated in ;
– is an exploded perspective view of the pre-damper module and the torque output element, according to the first mode illustrated in ;
– is another view in axial section of the torsion damper assembly, with in particular the means for locking the cages, according to a second embodiment of the invention;
– is another view in axial section of the torsion damper assembly, with in particular the means for positioning the cages, according to the second embodiment illustrated in ;
– is a view in axial section of the torsion damper assembly, with in particular the means for locking the cages, according to a third embodiment of the invention;

"Vehicle" means motor vehicles, which include not only passenger vehicles, but also industrial vehicles, including in particular heavy goods vehicles, public transport vehicles or agricultural vehicles, but also any transport vehicle allowing move a living being and/or an object from one point to another.

Unless otherwise specified, “axially” means “parallel to the X axis of rotation of the pre-damper module or torsion damper assembly”; "radially" means "along a transverse axis intersecting the axis of rotation of the pre-damper module or of the torsion damper assembly"; “angularly” or “circumferentially” means “around the X axis of rotation of the pre-damper module or the torsion damper assembly”.

In the remainder of the description and the claims, the terms "inner/internal" or "outer/external" with respect to the X axis and in a radial orientation will be used, without limitation and in order to facilitate understanding thereof. , orthogonal to said axial orientation; and the terms "rear" AR and "front" AV to define the relative position of one element with respect to another in the axial direction, an element intended to be placed close to the heat engine being designated rear and an element intended to be placed close to the gearbox being designated by front.

By way of example, “internal spline” means a series of teeth extending in the direction of the X axis; Conversely, “external spline” means a series of teeth extending in the opposite direction to the X axis;

The thicknesses E _A1 , E _R1 , E _L1 , E _P1 , E _A2 , E _R2 , E _L2 , E _P2 are here measured along the axis X of rotation.

There is shown in FIGURES 1 to 12 a first embodiment of a torsion damper assembly 1 of a transmission chain for a vehicle, comprising in particular a pre-damper module M. There illustrates the assembly of the various components of a torsion damper assembly 1.

Referring to FIGURES 1 to 5, it is noted that the torsion damper assembly 1 comprises a clutch disc 7 consisting of two facing guide washers 71, 72 (also called flanges), called drive flange 71 and bearing flange 72, respectively arranged at the rear rear and at the front front of the torsion damper assembly 1. These flanges 71, 72 are secured to one another by enclosing in their space between , a hub 6 (also called the central hub), a pre-damper module M, as well as a main hysteresis mechanism 50, called the main damper.

The main hysteresis mechanism and the pre-damper module M are interposed axially between the two flanges 71, 72. In particular, the pre-damper module M is arranged inside the clutch disc 7. Other mechanical components may possibly be interposed between the two flanges 71, 72.

By “inside” of the clutch disc 7 is meant here the front face of the drive flange 71 on which the pre-damper module M bears. More precisely, the place of the flange 71 coming to rest on a first friction zone called the main hysteresis zone F1, here the radially inner end of the flange 71.

In a variant not shown, drive flange 71 may comprise a peripheral fixing part, called abutment projection, opposite flange 72 along axis X. The abutment projection may be formed by at least one step of bending the flange 71, to simplify its assembly on the flange 72 without interfering with the other mechanical components.

Furthermore, the clutch disc 7 carries, on the side of the bearing flange 72, peripheral friction linings G which, in the engaged position, come into pressure contact with the engine flywheel of the vehicle (not shown).

The torque input element of the torsion damper assembly 1 consists of a clutch disc 7, defined by at least one flange 72, and carrying, at its outer periphery, for fixing on each of its faces, friction linings G, possibly divided into pads, as shown in the . The friction linings G may for example be intended to be clamped between the pressure and reaction plates (not shown) of the clutch, so that the input element is fixed in rotation on a driving shaft, the crankshaft of the vehicle's internal combustion engine.

The torque input element of the torsion damper assembly 1 further consists of a main damper 50 linked in rotation to the clutch disc 7. In particular, the main damper 50 further comprises:
- A first series of coil springs R1, forming the main damping means;
- A central veil 4 of support, fixed inside the disc 1, and in which the springs R1 are worn. The washers 71, 72 are arranged on either side of the central web 4 being of transverse orientation just like the central web 4.

The torsion damper assembly 1 can also be associated with other mechanical elements (not shown) that are usually found in a friction clutch. Furthermore, the two washers 71, 72 are coaxial and mounted to move relative to each other against:
- first elastic members with circumferential action of the main damper 50, called springs R1 of high stiffness;
- First axially acting friction means, called main hysteresis means;
- cages 10, 20 of the pre-damper module M;

Therefore, the springs R1 are mounted in the windows 710, 720 facing each other and rest on the side edges of said windows 710, 720 via cups 81 with a dorsal face in the shape of a dihedral to match the forms side edges. These cups 81 can each have a centering stud penetrating inside a spring R1 to hold the springs R1 radially. The flanges 71, 72 surround the hub 6. The central web 4 surrounds the hub 6. In the examples shown, the washers 71, 72 are connected to each other for fixing by fixing means, here by spacers 70. The spacers 70 , on the one hand, cross with circumferential clearance the central web 4 by means of indentations 46 provided at the outer periphery of the latter, and, on the other hand, secure the input element to the flanges 71, 72 .

In a variant not shown, the spacers 70 can secure the central veil to the flanges.

Referring in particular to FIGURES 6 to 12, the pre-damper module M further comprises:
- second elastic members with circumferential action, here a series of low-load springs R2;
- A first so-called drive cage 10, defined by a first central core 100, on which the drive flange 71 rests. The central core 100 partly receives the springs R2;
- A second so-called cover cage 20, defined by a second central core 200, on which the drive flange 71 rests. The central core 200 partly receives the springs R2;
- a veil 30 called training, fixed inside the cages 10, 20 and carrying the springs R2 through windows 36 crossing, formed in the veil 30 and distributed angularly regularly around the axis X.

The drive web 30 extends radially between an inner periphery and an outer periphery 34, here continuous around the axis X. Its outer periphery 34 is circular and free. Its internal periphery forms an internal groove 33.
Thus, the cages 10, 20 delimit between them a space inside which are received the springs R2 and the veil 30 of training. These two cages 10, 20 thus enclose between them the springs R2 and the drive web 30, in order to form a unitary sub-assembly, called cassette, constituting the pre-damper module M.

Furthermore, the first cage 10 comprises distinct bearing zones, called first bearing zones 150, intended to receive the second cage 20. Similarly, the second cage 20 comprises distinct bearing zones, called second zones support 250, intended to receive the first cage 10.

Preferably, the space between the separate support zones 150, 250 of a cage 10, 20 partly receives neighboring parts of the pre-damper module M or of the rest of the torsion damper assembly 1, such as, for example, the end of the springs R1 of said module M or else the end of the springs R2 of the main shock absorber 50.

By central core 100, 200 is meant the essential base or the main base constituting the cage. The two cores 100, 200 are coaxial and they are arranged axially on either side of the drive web 30, being of transverse orientation just like the drive web 30.

Furthermore, the central core 100 further comprises first bearing seats 19, formed on the side of the second bearing surface 12. These bearing seats 19 partly receive the springs R2, being arranged opposite the R2 springs. The bearing seats are delimited axially between the first and second bearing surfaces 11, 12.

By way of example, the support seats 19 open onto the first support surface 11, through partial openings 16'. The openings 16' are through and formed in the central core 100, having for example a closed outline, of the arcuate type, guaranteeing better visibility of the second springs R2 and a reduced weight of the cage 10.

Furthermore, the central core 200 further comprises second bearing seats 29, formed on the side of the first bearing surface 11. These bearing seats 29 partly receive the springs R2, being arranged facing the first support seats 19. The support seats 29 are delimited axially between the first and second support faces 21, 22.

By way of example, the support seats 29 lead to the second support face 21, through partial openings 26'. The openings 26' are through and formed in the central web 200, having for example a closed outline, of the arcuate type, guaranteeing better visibility of the second springs R2 and a reduced weight of the cage 20.

Furthermore, the first springs R1 intervene in a stepped manner by being stiffer than the second members R2, i.e. the second springs R2 are of lower stiffness and/or of smaller dimensions than those of the first springs R1, in order in particular to filter the vibrations in the range of vehicle engine idling speed. The first springs R1 of strong stiffness are intended to filter the vibrations in the running mode of the vehicle.

Furthermore, the second springs R2, here six in number, can be divided into pairs of springs. The pairs of springs R2 are mounted, on the one hand, without play for some in bearing seats 19 and with play for the other pairs in said bearing seats 19 of the first cage 10, and on the other hand, without play for some in the support seats 29 and with play for the other pairs in said support seats 29 of the second cage 20. Also, the pairs of springs R1 are mounted without play in the windows 36 of the veil 30 d 'coaching. The windows 36 and the support seats 19, 29 are through and arranged axially facing each other, angularly distributed regularly around the axis X. Each series of springs R1, R2 is thus angularly distributed around the axis X, according to an even distribution.

Furthermore, the central core 100 of the first cage 10 extends radially between an inner periphery 13 and an outer periphery 14. In the examples illustrated, the central core 100 extends axially between:
- A first support face 11, of the continuous type around the X axis, on which the flange 71 drive is supported;
- A second support face 12, of the continuous type around the axis X, on which the drive web 30 is supported;
The first and second bearing surfaces 11, 12 define between them the thickness E _A1 of the central core 100 of the cage 10.

Similarly, the central core 200 of the second cage 20 extends radially between an inner periphery 23 and an outer periphery 24. In the examples illustrated, the central core 200 also extends axially between:
- A first bearing face 21, of the continuous type around the X axis, free and intended to stop the drive web 30;
- A second support face 22, of the continuous type around the axis X, on which the support flange 72 is supported;
The first and second bearing surfaces 21, 22 define between them the thickness E _A2 of the central core 200 of the cage 20.

In the examples illustrated, the central core 100 has a radial dimension greater than that of the central core 200.

Furthermore, the thicknesses E _A1 and E _A2 of the central cores 100 of said cages 10, 20 are here equal to each other.

Furthermore, the first elastic springs R1, here four in number, can be divided into pairs of springs. The pairs of these springs R1 are mounted without play for certain pairs in windows 46 of the central veil 4 and with play for the other pairs in said windows 46. Also, the pairs of springs R1 are mounted without play in windows 710, 720 respectively flanges 71, 72. The windows 46, 710, 720 are through and arranged axially opposite each other, and they are for example distributed angularly regularly around the axis X. These springs R1 also cooperate by one end with the central veil 4 and by another end with the flanges 71, 72.

Furthermore, the second cage 20 is remarkable in that it further comprises guide studs 27, which extend from the central web 200, along the axis X, in the direction of the central web 4. The studs 27 are arranged on the side of the second bearing face 22 of the central core 200, here towards the rear AV of said module M. The guide studs 27 are made in one piece with the central core 200. The studs 27 cooperate in openings 47 of the central web 4. The openings 47 and the studs 27 are arranged facing each other, preferably one by one, i.e. an opening 47 for a stud 27.

Preferably, the guide studs 27 of the second cage are of complementary shapes to the openings 47 of the central web 4, so as to form a connection by fitting of the guide studs 27 in the central web 4 .

Furthermore, the torsion damper assembly 1 further comprises a torque output element, consisting of a hub 6, comprising a flange and internally provided with an internal spline 63, for its connection in rotation to a driven shaft, to namely the input shaft of the gearbox in the case of an application for a motor vehicle. The engine torque is transmitted from the input element, here the clutch disc 7, to the torque output element, here the hub 6.

In particular, the engine torque is transmitted from the clutch disc 7 to the main hysteresis mechanism 50, then to the pre-damper module M as far as the hub 6. To do this, the web 30 and the torque output hub 6 are mounted movable relative to each other against second elastic members with circumferential action, hereinafter referred to as springs R2 of low stiffness, with intervention:
- Clearance meshing means, and;
- second axially acting friction means, called secondary hysteresis means;

By "play meshing means" is meant here a cooperation of the splines of the hub 6 and the web 30. The play meshing means here limit the relative angular displacement between the central web 3 and the hub 6. Therefore , the hub 6 comprises a spline 60, complementary for its connection in rotation with the drive web 30 of the pre-damper module M. The hub 6 thus comprises teeth of trapezoidal shape meshing with circumferential clearance with those of the drive web 30 and vice versa, as illustrated in the . The internal spline 33 of the drive web 30 is therefore integrally connected in rotation to the external spline 60 of the hub 6.

Furthermore, a series of so-called guide and/or application washers 51, 52, 53, 54, 54' partly constitute the main damper 50, and they are mounted between the two flanges 71 and 72, at the inside the clutch disc 7 and resting against the central veil 4, on the side opposite to the friction linings G. Referring to FIGURES 1 to 5, the central web 4 is mounted so as to cooperate, on the one hand, with the series of coaxial washers 51, 52, 53, on the other hand, with a second cage of the module M pre -shock absorber.

By "first axially acting friction means" is meant here means forming the main hysteresis F1 of the torsion damper assembly 1, which are also linked to the pre-damper module. In other words, such a main hysteresis, illustrated schematically in FIGURES 4 and 14 by an arrow F1, is axially routed between the flanges 71, 72, the components of the main damper 50 and those of the module M pre -shock absorber

In the examples illustrated, the first friction means F1 intervene between the two coaxial parts of said torsion damper assembly 1, comprising respectively, on the one hand, the flanges 71, 72 and, on the other hand:
- A series of washers 51, 52, as well as the central web 4, from the main damper 50; And
- the cages, as well as the second springs R2, from the pre-damper module M;

Specifically, the first friction means formed by the main damper 50 further comprise:
- A first axially acting washer, called the first elastic member 51, interposed between the flange 72 and the central web 4;
- A second washer, said support member 52 of the first elastic member 51, resting on the central web 4 at a circumferential bearing surface 42, so as to at least partially surround the first elastic member 51;

By way of example, the elastic member 51 consists of a corrugated washer resting on the flange 72 for action on the flange 72 and stressing the latter into contact with the central web 4, here via the intermediary of the member support 52.

By way of example, the support member 52 is made of metallic material and it comprises, on its outer periphery, guide lugs or pins 525, here four in number, penetrating in a complementary manner into the orifices 725 formed in the flange 72 for connection in rotation of said flange 72 with the central web 4. These orifices 725 are regularly distributed angularly around the axis X.

Specifically, the first friction means formed by the pre-damper module M further comprise:
- the first cage 10, resting on the flange 71 at its first bearing face 11;
- the second cage 20, resting on the central web 4 at its second bearing face 22;
- the second springs R2, partly housed in the support seats 19, 29 of the cages (see previous paragraphs);

In such a situation, the first bearing surface 11 partly forms the first friction means F1 of the pre-damper module M. In other words, the first cage 10 is remarkable in that it also comprises a friction zone, called the main hysteresis zone F1, defined by its first bearing face 11, so that the module M rubs on the flange 71 of the clutch disc 7. Consequently, this friction zone is formed externally on the central web 100 and it partly forms the first friction means F1 of the pre-damper module M.

By way of example, the first bearing surface 11 consists of a bearing surface, for example of the circular and linear type, resting on the flange 72 for action on the flange 72 and stressing the latter in contact with the central web 4, here in particular via said springs R2. Similarly, the second bearing face 22 can partly form the first friction means F1 of said module M. By way of example, the first bearing face 11 consists of a bearing surface, for example of the type circular and linear, resting on the central veil for action on the flange 72 and biasing the latter into contact with the central veil 4, here in particular via said springs R2.

By "second axially acting friction means" is meant here means forming the secondary hysteresis F2 of the torsion damper assembly 1 (called in English "predamper hysteresis"), which are further linked to the pre-damper module . In other words, such a secondary hysteresis action, illustrated schematically in FIGURES 4 and 14 by an arrow F2, travels axially between the flanges 71, 72, the components of the main damper 50 and those of the module M pre-shock

In the first mode, the second friction means F2 intervene between the two coaxial parts of said torsion damper assembly 1, comprising respectively, on the one hand, the guide washers 71, 72 and, on the other hand:
- A series of washers forming part of the main damper 50, as well as the hub 6;
- The drive web 30, as well as the first cage 10 of said module M on which said web 30 rests.

Specifically, the second friction means formed by the main damper 50 further comprise:
- A third axially acting washer, called elastic member 53, interposed between the flange 72 and the hub 6;
- A fourth washer, said support member 54 of the elastic member 53, resting on the hub 6 at a bearing surface 62 circumferential; and eventually,
- A fifth support washer 55, interposed between the fourth washer 54 and the spline 60 of the hub 6;

By way of example, the elastic member 53 consists of a Belleville washer resting on the flange 72 for action on the flange 72 and stressing the latter into contact with the hub 6, here by means of the holder 52.

By way of example, the elastic member 51 partly forming the first friction means F1 surrounds the elastic member 53 partly forming the second friction means F2.

By way of example, the support member 54 comprises an annular base 540, on which the elastic member 53 bears, and an annular skirt 541 extending from the annular base 540. The skirt 541 is inserted radially between the puddle 72 and a hub 6. The puddle 72 and the hub 6 are arranged radially bearing on either side of the annular skirt 541. In particular, the support member 53 externally comprises a splined profile, at the level of its skirt 541, here six teeth in number. The support member 54 also comprises internally a splined profile, so as to bind the washers 53, 54 integrally in rotation and avoid any angular offset between them. Also, the support member 54 is inserted between the puddle 72 and a hub 6, at the level of the bearing surface 62. These two washers 53, 54 are therefore arranged axially bearing on either side of the base 540 annular.

Furthermore, the elastic member 51 develops an axial load which takes into account the stiffness of the springs R1. This elastic member 51 has a higher calibration than that of the elastic washer 53.

Specifically, the second friction means formed by the pre-damper module M comprise the first cage 10. In this way, the second friction means of the pre-damper module M are formed,
- either, in the first and third modes, by the second bearing surface 12 of the first cage 10.
- either, in the second mode, by a third bearing surface 130 of the first cage 10.

Furthermore, the internal spline 33 of the drive web 30 extends axially between two opposite side faces, called first bearing face 31 and second bearing face 32, of the continuous type around the axis X. , the first bearing face 31 of the veil 30 thus cooperates with the second bearing face 12 of the cage 10.

Furthermore, the first cage 10 is remarkable in that it further comprises an annular flange 17 which extends from the central core 100, along the axis X, in the direction of the drive web 30, this is that is to say here towards the front AV of said module M. Preferably, the collar 17 is continuous around the axis X and it forms the second bearing face 12, so as to receive the veil 30. The collar 17 is here arranged as close as possible to the axis X, i.e. as close as possible to the hub 6, and to its spline 60. In a variant not shown, the flange 17 can be crenellated, forming teeth, crenellations or even discontinuous bearing portions, which cooperate with the drive web 30 .

In the first mode, the second friction means F2 of the pre-damper module M are formed in particular by the second bearing surface 12. As a result, the collar 17 partly forms the second friction means F2.

Furthermore, the first cage 10 is remarkable in that it further comprises a crown 18, which extends from the central core 100 along the axis X, in the opposite direction from the hub 6, here towards the rear AR said module M. The collar 18 is continuous around the axis X. Preferably, the collar 18 extends from the inner periphery 13, that is to say at the end of the part of the central core 100, and it receives the radially inner end of flange 71. Collar 18 is arranged as close as possible to axis X, so as to center flange 71 as close as possible to hub 6. This further reduces the radial space between parts. Hub 6 and flange 71 are arranged radially on either side of flange 18.

Furthermore, the hub 6 further comprises a series of indentations 69, called recesses, inside which the inner periphery of the drive web 30 comes to rest. In particular, the groove 33 of the training veil 30 is received in part by the indentations 69, here six in number. In the examples illustrated, the notches 69 are formed at the end of the spline 60 of the hub 6, here on the rear rear end of the teeth of the hub 6. In FIGURES 3 and 12, each tooth of the spline 60 comprises a notch 69. In the first embodiment, the hub 6 is thus centered on the drive web 30, without the need for additional fasteners (rivets) or special tools.

Furthermore, the hub 6 comprises a shoulder 68, formed in the extension of the spline 60 of the hub 6 and extending continuously around the axis X. The shoulder 68 receives inside the crown 18 of the first cage 10. Such a shoulder has the advantage of simply assembling the hub 6 on the pre-shock absorber module, without the need for additional fixing means, or special tools, such as riveting to connect them together.

Preferably, the shoulder 68 of the hub 6 is of complementary shape to that of the crown 18 of the cage 10. In the first mode, the crown 18 and the hub 6, in particular the shoulder 68, are of cylindrical shapes, d X axis.

Furthermore, the first and second cages 10, 20 are made of plastic material.

The invention may also aim to improve the pre-damper module M and, more particularly, the positioning and locking of such a module, in particular by modifying the structure of the cages 10, 20.

By “locking” the cages of the module, we mean closing or fixing the cages together, so as to contain the parts placed inside said cages.

We will describe the structure of the cages 10, 20 ensuring their positioning during the assembly of the module M.

Advantageously, the first cage 10 comprises first bearing flanges 15, distinct from each other, which are here located on the outer periphery 14 of the central core 100. These support flanges 15, here four in number, extend along the X axis, in the direction of the second cage 20, here towards the front AV of said module M. The first support flanges 15 extend from the central core 100 along a thickness E1R. Each support rim 15 comprises a distal portion of the central core 100, which serves as a support zone 150 for the cage.

The support flange 15 thus has a thickness E _R1 of a support flange 15 defined axially between the support zone 150 and the second support face 12 of the central web 100

Furthermore, the second cage 20 further comprises second bearing flanges 25, distinct from each other, which are here located on the outer periphery 24 of the central core 200. These support flanges 25, here four in number, extend along the X axis, in the direction of the first cage 20, here towards the rear rear of said module M. The second support flanges 25 extend from the central core 200 along a thickness ER2. Each support rim 25 comprises a distal portion of the central core 200, which serves as a support zone 250 for the cage.

The support flange 25 thus has a thickness E _R2 of a support flange 25 defined axially between the support zone 250 and the second support face 22 of the central web 200 .

Thanks to the support edges 15, 25, the support zones 150, 250 are offset radially and axially with respect to the drive web 30, and in particular as far as possible from the central web 100, 200 and the seats of support 19, 29 of springs R2.

Preferably, the first support zones 150 receive the second support flanges 250. The second support zones 150 receive the first support flanges 250. In the examples illustrated, the first and second support zones 150, 250 are arranged facing each other. Therefore, the first and second support flanges 15, 25 of the cages are arranged axially facing each other.

By way of example, the thicknesses E _R1, E _R2 of the support flanges 15, 25 are here equal.

Furthermore, the support flanges 15, 25 are regularly distributed angularly around the axis X. Preferably, the support flanges 15, 25 are of complementary shapes, here of identical radial and angular dimensions. In a variant not shown, the bearing edges 15, 25 can be distributed alternately around the axis X.

In the examples illustrated, the first bearing faces 11, 21 and the second bearing faces 12, 22 of the cages are circular in shape, over 360 degrees. The remaining portions of each cage 10, 20 form bearing flanges 15, 25.

Furthermore, the bearing edges 15 are defined relative to the second bearing face 12 and to the bearing seats 19, i.e. on the remaining portions of the central core 100. Similarly, the bearing edges 25 are here defined relative to the first bearing face 21 and to the bearing seats 29, i.e. on the remaining portions of the central web 200.

Therefore, the bearing edges 15, 25 are defined on the remaining portions with respect to the bearing faces 12, 21, i.e. the corners of the cages. In the examples illustrated, the bearing edges 15, 25 are defined respectively in the corners of the central core 100, 200, here in the four corners of the corresponding cage 10, 20.

Furthermore, each cage 10, 20, and in particular each central core 100, 200, has a polygonal shape in section, such as a quadrilateral, for example of cubic shape, or an octagon, for example cubic with beveled corners. By "bevelled" corners or ends, we mean here a shape with an edge made obliquely.

By way of example, a bevelled end (of the "wedge" type) is located on the outside of each support flange 15, 25. Therefore, the support flanges 15, 25 of a cage 10, 20 each include a beveled edge or a beveled end.

In other words, each support rim 15, 25 includes a tangential rounding (stop type), which can partly define the contour of the support zone 100, 200. In FIGURES 1, 5 to 10, the bevelled ends of the bearing flanges 15, 25 extend radially opposite the axis X and can be rounded (chamfer-like shapes).

Furthermore, the support flanges 15, 25 are therefore of substantially triangular or conical shape, with a radially internal edge, of the arcuate type for each support flange 15, 25. Such support flanges 15, 25 have the advantage of substantially reducing the size of the parts within the module M without the latter interfering with each other.

Advantageously, the second cage 20 comprises protrusions 250A and 250B which are formed on the support flanges 25. Preferably, a protrusion 250A, 250B is an axial projection, which comprises several support faces 251, 252, 253 intended to be received in a housing 150A, 150B. In FIGURES 6 to 7, the protrusions 250A, 250B are formed from the beveled corners or ends of said cage 20. The protrusions 250A, 250B extend axially, from the support zones 250, along a thickness E _L2 . Preferably, the thickness E _L2 of the protrusion 250A, 250B is delimited axially between its free end and the bearing surface 250 of said bearing rim.

By "free end" is meant here the distal end of the protrusion 250A, 250B, i.e. the portion furthest from the bearing rim 25, from which the head of the protrusion can be defined. By way of example, the shape of the protrusions 250A, 250B is polygonal in shape.

In the examples illustrated, the protrusions 250A, 250B, here four in number, are rectangular. They are formed in one piece with the central core 200. Some protrusions 250A are here in the form of a hook or cantilever. In addition, each protuberance 250A, 250B is centered in the middle of the support rim 25, that is one by one.

As a variant not shown, a support rim 25 can comprise at least two protrusions 250A and/or 250B.

Advantageously, the first cage 10 comprises housings 150A and 150B, formed in the thickness E _1R of the bearing flanges 15. Preferably, the housings 150A, 150B and the protrusions 250A, 250B cooperate together. The housings 150A, 150B are formed from the bevelled corners or ends of said cage 10. The housings 150A, 150B extend, from the support zones 150, in the direction opposite to the second cage 20. Each housing 150A, 150B is centered in the middle of the support rim 5, one by one.

By “housing”, we mean a recess such that it is distinguished from a simple notch or notch, and makes it possible to correctly position and assemble the support edges of the cages. Preferably, a housing 150A, 150B is a recess, of the open type, made in the support rim 15, 25 to house therein a protrusion of another cage. A housing can comprise several bearing faces 151, 152, 153 intended to receive a protuberance 250A, 250B.

In the examples illustrated, the housings 150A, 150B of a cage 10 are open towards the support rim 25 of the other cage 20, to receive there a protrusion 250A, 250B. In particular, the housings 150A, 150B and the protuberances 250A, 250B are of mutually complementary shapes. In a variant not shown, the protuberances and the housings can be respectively of concave and convex shapes.

By way of example, each housing 150A, 150B extends angularly between two opposite side faces 152, on which a protuberance 250A, 250B bears. The housing 150A, 150B further comprises a support wall 153 of axial extension E _L1 . The support wall 153 is delimited angularly between the side faces 152 of the housing support. The side faces 152 angularly define the wall 153 of a housing 150A, 150B.

In the examples illustrated, the housing 150A, 150B is of the through type, ie it opens out axially on either side of the corresponding cage 10, 20. The axial extension (or axial dimension) E _L1 of the wall 153 of a housing is here the sum of the thickness E _R1 of the bearing rim 15 and the thickness E _A1 of the central core 100 of the crate 10.

As a variant not shown, the housing 150A, 150B can be non-through and include a bottom located inside the central core 100. The housing may extend axially to 100% of the thickness E _R1 of the bearing flange 15 and to 50% of the thickness E _A1 of the central core 100 . In another variant not shown, a support rim 15 may comprise at least two housings 150A and/or 150B.

Preferably, the housings 150A, 150B can be through. In other words, each housing 150A, 150B emerges axially on either side of the bearing flange 15 and the central web 100.

In such a situation, the housings 150A, 150B are formed in the thickness E _A1, E _A1 ' of the central core 100. Each housing 150A, 150B opens axially, on the one hand, on a support surface 150, here towards the front AV, and, on the other hand, on the first support surface 11 of the cage 11. On the FIGURES 5 to 9, the depth E _L1 of a housing 150A, 150B is delimited axially between the bearing zone 150 and the first bearing face 11 of the cage 10. The depth of a housing 150A, 150B is thus defined by the sum of the thicknesses E _A1 and E _R1 .

We will now describe in more detail the positioning of the cages 10, 20 during the assembly of the module M.

Advantageously, the first and second cages 10, 20, in particular their bearing edges 15, 25, are positioned fixedly together, thanks to:
- First positioning means 15B, 15B', formed on the outer periphery 14 of the cage 10; And
- second positioning means 25B, 25B', formed on the outer periphery 24 of the cage 20;

The location of the positioning means 15A, 15A', 25A, 25A' allows simple and visual positioning of the cages. The first and second positioning means 15A, 15A', 25A, 25A' cooperate jointly with each other, being arranged axially opposite each other.

Preferably, the first positioning means 15B, 15B' and the second positioning means 25B, 25A' are interlocking means, having complementary shapes and arranged axially opposite each other. Such interlocking means ensure quick and simplified positioning of the cages by the operator.

Furthermore, first positioning means 15B, 15B' are formed on the support flanges 15. In particular, they are at the end of the support flanges 15, in other words, formed on the portions of the support flanges 15 furthest from the axis X. Preferably, the positioning means 15B, 15B' are made on the radially outer end of the support flanges 15, called bevelled ends.

In particular, these first positioning means 15B, 15B' are formed in one piece with the central core 100, preferably made of plastic. By way of example, the positioning means 15B, 15B', here two in number, are of identical shapes. These positioning means 15B, 15B', are of female shapes.

In the first mode, some housings 150B partly form the first positioning means 15B, here one housing 150B per first means 15B.

Furthermore, the second positioning means 25B, 25B' are formed on the support flanges 25. These second positioning means 25B, 25B' are formed at the end of the support flanges 25, i.e. on the portions of the flanges of support 25 furthest from the axis X. Preferably, the positioning means 25B, 25B' are made on the radially outer end of the support flanges 15, called beveled ends.

In particular, these positioning means 25B, 25B' are formed in one piece with the central core 200, preferably made of plastic. By way of example, the positioning means 25B, 25B', here two in number, are of identical shapes. These positioning means 25B, 25B', are of male shapes.

In the first mode, some projections 250B partly form the second positioning means 25B, here one projection 250B per second means 25B.

We will now describe the locking or fixing of the cages 10, 20 during assembly of the pre-damper module M.

Advantageously, the first and second cages 10, 20, in particular their bearing edges 15, 25, are fixedly mounted together, thanks to:
- First locking means 15A, 15A', formed on the outer periphery 14 of the cage 10; And
- second locking means 25A, 25A', formed on the outer periphery 24 of the cage 20;
The location of the locking means 15A, 15A', 25A, 25A' makes it possible to close the cages from outside the module M, in a visually simple manner. The first and second locking means 15A, 15A', 25A, 25A' jointly cooperate with each other, being arranged axially opposite each other.

Furthermore, the first locking means 15A, 15A' are first clipping means.

Furthermore, the second locking means 25A, 25A' are second clipping means, having shapes complementary to the first locking means 15A, 15A'. By "clipping means", we mean here clips or shapes allowing mechanical retention by elasticity of the material, hence a preference for plastic. Such clipping means, in particular made of plastic material, allow better flexibility and resistance to wear, as well as simplified assembly of the cages, quickly and without great effort for the operator.

By “clipping means”, one can define for example a slender profile and a large bearing or retaining surface. This means, for example, combinations of shapes called clips in the form of staples, tabs, male-female parts or metal hooks. Any form of "clipping" is possible, if it maintains the cages around or inside a cooperation axis.

Furthermore, first locking means 15A, 15A' are formed on the outer periphery 13 of the cage 10, in particular formed on the support flanges 15. These locking means 15A, 15A' are formed at the end of the flanges of support 15, i.e. on the portions of the support flanges 15 furthest from the axis X.

The locking means 15A, 15A' are made on the radially outer end of the support flanges 15, called bevelled ends. In particular, these first locking means 15A, 15A' are formed in one piece with the central core 100, preferably made of plastic. By way of example, the locking means 15A, 15A' here two in number, are of identical shapes. These locking means 15A, 15A' called clipping, are of female shapes.

In the first mode, some housings 150A partly form the locking means 15A, here one housing 150A per first means 15A.

Furthermore, second locking means 25A, 25A' are formed on the outer periphery 23 of the second cage 20, in particular formed on the bearing flanges 25. These second locking means 25A, 25A' are formed at the end of the flanges support 25, i.e. the portions of the support flanges 25 farthest from the axis X.

The locking means 25A, 25A' are made on the radially outer end of the support flanges 15, called bevelled ends. In particular, these locking means 25A, 25A' are formed in one piece with the central core 200, preferably made of plastic. By way of example, the so-called clipping locking means 25A, 25A', here two in number, are of identical shapes. These locking means 25A, 25A', are of male shapes.

In the first mode, some projections 250A partly form the second locking means 25A, here one projection 250A per second means 25A.

It is noted that the locking means 15A, 25A, 15A', 25A', called clipping means, and the positioning means 15A, 25A, 15A', 25A', called interlocking means, are visually distinguished from each other, in particular by the different shape of their lodgings and by the different shape of their excrescences.

Preferably, the first locking means 15A, 15A' and the second locking means 25A, 25A' are remarkable in that they each comprise a particular profile, called reliefs, adapted to cooperate jointly. The profiles in relief of the housings 150A and the protrusions 250A forming the locking means 25A cooperate with each other.

Additionally, the first and second locking means 15A, 25A, 15A′, 25A′ can perform a dual function, due to their complementary shapes, in particular that of centering the cages together.

In the examples illustrated, certain housings of a cage called "housings 150A, 250A'" constituting the locking means 15A, 25A' of said cage, are remarkable in that they comprise a profile in relief, of positive or crowded shape. . In other words, the locking means 25A, 15A' of a cage is formed by a stepped housing 150A, 250A'. The interior of said certain housings 150A, 250A' partly form the locking means 15A, 25A' of said cage. In other words, the locking means 25A, 15A' of a cage is formed from a bearing edge along an axis which is orthogonal to the axis X. Consequently, a distal portion of the housing 150A, 250A' extends over a greater depth (radial distance) than a proximal portion of this housing 150A, 250A'.

In particular on the , the housings 150A forming the locking means 15A of the first cage 10, each comprise a rib 151, of thickness EP1, extending from the bottom 153 of the housing 150A, here in the direction opposite to the axis X. For example, the thickness EP1 of the rib 151 is equal to 10% that EL1 of the wall of the housing, or even 20% the thickness ER1 of the bearing rim 15.

The distal part of the housing 150A, 250A' defines the bottom 153 of the housing. The proximal portion of the housing 150A, 250A' defines a rib 151 of the housing. The end of the protrusion is then supported on the distal part of the housing 150A, 250A'. Thanks to these ribs 151, the operator visually distinguishes the housings 150A forming the locking means and the housings 150B forming the positioning means, within the same cage.

Conversely, the other housings of a cage, called "housings 150B, 250B'" constituting the positioning means 15B, 25B' of said cage, are remarkable in that they comprise a smooth profile. These housings 150B, 250B' are then of hollow and strictly smooth shapes, i.e. without any ribs or projections.

Furthermore, certain protrusions of a cage called “protrusions 250A, 150A′” constituting the locking means 25A, 15A′ of said cage, are remarkable in that they comprise a profile in relief, of negative or hollow shape. The inside of said protrusions 250A, 150A' partly form the locking means 25A, 15A' of said cage.

In particular on the , the protrusions 250A forming the locking means 15A of the first cage 10, each comprise a groove 251, of thickness EP2, extending in the thickness EP1 of the protrusion 250A, here open radially on the inside. By way of example, the axial dimension EP2 of the groove 251 is equal to 60% the thickness EL2 of the protrusion 250A, or even 80% the thickness ER2 of the bearing rim 25.

By way of example, each protrusion 250A, 250B extends angularly between two opposite side faces 252, coming to rest on the faces 152 of a housing 150A, 150B. The housing 150A, 150B further comprises a free end 153 for support. The groove 251 is delimited axially between the free support end 153 and the rest of the protuberance. The side faces 252 angularly define the groove 251

Thanks to grooves 251, the operator visually distinguishes the protrusions 250A forming the locking means and the housings 150 forming the positioning means, within the same cage.

Conversely, the other protrusions of a cage, called “protrusions 250B, 150B′” constituting the positioning means 25B, 15B′ of said cage, are remarkable in that they comprise a smooth profile. These protrusions 250B, 150B' are then of solid and strictly smooth shapes, i.e. without any groove or recess.

It has been described on the , a second embodiment of the invention substantially similar to the first embodiment, except that:
- the first locking means 15A' and the first positioning means 15B' are of male shapes;
- the second locking means 25A' and the second positioning means 25B' are of female shapes;

According to this second mode, the shapes of the locking means and of the positioning means are then reversed (inversion of male-female shapes) between the first and second cages 10, 20, with respect to the first embodiment.

In this second mode, the first locking means 15A' of the first cage 10 have male shapes, preferably identical to one another. Consequently, certain projections 150A' partly form the first locking means 15A', here one projection 250A' per first means 15A'.

On the , the second locking means 25A' of the second cage 10 are of male shapes, preferably identical to one another. Consequently, certain housings 250A' partly form the second locking means 25A', here one protrusion 250A' per second means 25A'.

In this second mode, the first positioning means 15B' of the first cage 10 have male shapes, preferably identical to one another. Consequently, certain protrusions 150B' partly form the first positioning means 15B', here one protrusion 250B' per first means 15B'.

On the , the second positioning means 25B' of the second cage 10 are of male shapes, preferably identical to each other. Consequently, certain housings 250B' partly form the second locking means 25B', here a protrusion 250B' per second means 25B'.

Logically, the protrusions 150A' forming the first locking means 15A' each comprise a groove 151', here open radially outwards. The housings 250A' forming the second locking means 25A', each comprise a rib 251', extending from the bottom of the housing, extending here in the direction of the axis X.

There has been described in FIGURES 14 to 15, a third embodiment of the invention substantially similar to the first embodiment, except that:
- The hub 6, in particular the shoulder 68, is conical in shape and has an X axis;
- the internal periphery 13 of the first cage 10, in particular the crown 18, is of conical shape and of axis X;
- The internal periphery 13 of the first cage 10, in particular the crown 18, partly form the second friction means F2 of the pre-damper module M;

In this third mode, the first cage 10 is remarkable in that it additionally comprises a third support face 130, which delimits the internal periphery 13 between the first and second support faces 11, 12 of the cage 10. in other words, a third bearing surface 130 is formed on the inner periphery 13 of the central core 100. This third bearing face 130 supports the shoulder 68 of the hub 6.

Therefore, the second friction means F2 intervene between the two coaxial parts of said torsion damper assembly 1, comprising respectively, on the one hand, the guide washers 71, 72 and, on the other hand:
- A series of washers forming part of the main damper 50, as well as the hub 6;
- The first cage 10 of said module M on which said hub 6 bears;

In FIGURES 14 to 15, the second friction means F2 of the pre-damper module M are formed in part by the third bearing surface 130. In other words, the first cage 10 is remarkable in that it comprises furthermore a friction zone, called secondary hysteresis zone F2, defined by its third bearing face 130. Therefore, this friction zone is formed externally on the central core 100, at the end of the cage 10, more precisely on its inner periphery 3.

Furthermore, this third bearing face 130 is defined by ring 18. Therefore, ring 18 partly forms the second friction means F2 of the pre-damper module M. In particular, the third support face 130 is conical in shape. In FIGURES 14 to 15, crown 18 is of complementary shape to that of shoulder 68 of hub 6, here of complementary conical shapes, so as to cooperate with each other. The third support face 130 performs a dual function. Additionally, the hub 6 is also centered on the first cage, in particular at the level of the third bearing surface 130, without the need for additional fasteners (rivets) or special tools.

All the characteristics previously described in the first mode apply mutatis mutandis in the second mode and in the third mode.

Although the invention has been described in connection with several particular embodiments, it is obvious that it is in no way limited thereto and that it includes all the technical equivalents of the means described as well as their combinations if these fall within the scope of the invention.

The use of the verb "to comprise", "to understand" or "to include" and of its conjugated forms does not exclude the presence of other elements or other steps than those set out in a claim. In the claims, any reference sign in parentheses cannot be interpreted as a claim limitation.

Claims (16)

Pre-damper module (M) for torsion damper assembly (1), axis (X) of revolution, comprising:
- a first cage (10), arranged to be received inside a torque input element (7, 71, 72, 50, 4, R1),
- a second cage (20), arranged to bear against a central web (4) of the torque input element (7, 71, 72, 50, 4, R1), the first and second cages (10 , 20) being coaxial and mounted one on the other at support zones (150, 250),
- a veil (30), receiving a series of springs (R2) and being of splined shape to be connected to a torque output element (6), the first and second cages (10, 20) being arranged axially on either side on the other side of the veil (30) so as to receive the springs (R2) and said veil (30),
wherein the first and second cages (10, 20) each comprise at their outer periphery (14, 24):
- bearing edges (15, 25) forming the bearing zones (150, 250) of the first and second cages (10, 20), and
- locking means (15A, 25A, 15A', 25A') formed on the bearing edges (15, 25) of the first and second cages (10, 20), said locking means (15A, 15A') of the first cage (10) cooperating jointly with the said locking means (25A, 25A') of the second cage (20), the said locking means (15A, 25A) being configured in such a way as to solidly link the first cage (10) and the second cage (20) by clipping. Pre-damper module (M) according to Claim 1, in which the first and second cages (10, 20) are made of plastic material. Pre-damper module (M) according to claim 1 or 2, in which the first cage (10) comprises a central web (100) delimited axially between:
- a first bearing face (11), arranged to come to rest inside the torque input element, and
- a second support face (12), on which the web (30) of the pre-damper module (M) is supported,
in which the first cage (10) comprises a first friction zone, called main hysteresis zone (F1), intended to rub on the torque input element, said first friction zone being formed on the first face of support (11), and/or
in which the first cage (10) comprises a second friction zone, called the secondary hysteresis zone (F2), intended to rub on the torque output element (6), the said second friction zone being formed on the second bearing face (12) of the core (100) central or on the inner periphery (13) of the first cage (10). Pre-damper module (M) according to claim 3, in which the second circumferential bearing face (220) is formed by an annular flange (17) extending from the central web (100) of the first cage (10 ), on which the web (30) of the pre-damper module (M) rests. Pre-damper module (M) according to any one of the preceding claims, in which one of the cages (20, 10) comprises protuberances (250A, 250B, 150A', 150B'), formed on its bearing edges (25, 15') and adapted to be received in housings (150A, 150B, 250A', 250B') formed on the bearing edges of the other cage plate (10, 20). Pre-damper module (M) according to the preceding claim, in which:
- at least two of the protrusions (250A, 150A') form the locking means (25A, 15A') of a cage (20, 10), and
- at least two of the housings (150A, 250A') forming the locking means (15A, 25A') of the other cage (10, 20),
and in which the protrusions (250A, 150A') and the housings (150A, 250A') forming the means for locking the cages (10, 20) are of complementary shapes. Pre-damper module (M) according to claim 5 or 6, in which:
- at least one of the protrusions (250B, 150B') form positioning means (25B, 15B') of a cage (20, 10), and
- at least one of the housings (150B, 250B') forming the positioning means (15B, 25B') of the other cage (10, 20),
and in which the protrusions (250B, 150B') and the housings (150B, 250B') forming the means for positioning the cages (10, 20) are of complementary shapes. Pre-damper module (M) according to any one of the preceding claims, in which
- the first cage (10) comprises at least two housings (150A) inside which are each formed a rib (151), each rib (151) of the housing (150A) partly forming a locking means (15A) of the first cage (10).
- the second cage (20) comprises at least two protrusions (250A) inside which are each formed a groove (251), each groove (251) of protrusion (250A) partly forming a locking means (25A) of the second cage (20). Torsion damper assembly (1) comprising:
- a main damper (50) comprising a torque input element (7, 71, 72, R1) capable of being connected to a driving shaft,
- a torque output element (6) adapted to be connected to a driven shaft,
- a pre-damper module (M) according to any one of the preceding claims, in which
the web (30) of the pre-damper module (M) and the torque output element (6) are mounted linked in rotation with each other, the first cage (10) being mounted so as to be able to rotate with respect to to the torque input element (7, 71, R1), at the level of a first friction zone called the main hysteresis zone (F1), and
the second cage (20) being mounted fixed in rotation relative to the torque input element (7, 72) by bearing against the torque input element (7, 72). Torsion damper assembly (1) according to claim 9, of axis (X) of rotation, in which
- the torque input element (7, 71, 72, R1) is a clutch disc (7), formed by at least one guide washer (71, 72) and friction linings (G) peripherals supported by said guide washer (71, 72);
- the torque output element (6) is a torque output hub, of the splined type, suitable for being connected to a driven shaft,
wherein a spline (60) of the torque output hub is arranged to be connected to a spline (33) of the web (30) of the pre-damper module (M). Torsion damper assembly (1) according to Claim 10, in which the spline (60) of the torque output hub comprises a series of notches (69) intended to bear against the web (30) of the module (M) pre-damper. Torsion damper assembly (1) according to any one of Claims 10 to 11, in which the first cage (10) comprises a crown (18) of cylindrical or conical shape, extending from the internal periphery (13) of the first cage (10), said crown (18) being centered on the guide washer (71) of the clutch disc (7). Torsion damper assembly (1) according to any one of claims 10 to 12, in which the torque output hub comprises a shoulder (68) of cylindrical or conical shape, formed in the extension of the spline (60) of the hub torque output and intended to receive the inner periphery (13) of the first cage (10). A torsion damper assembly (1) as claimed in claim 13 taken in combination with claim 12, wherein the torque output hub shoulder (68) is tapered and wherein the first cage (10) comprises a crown ( 18) of conical shape, so as to be centered on the crown (18) of conical shape of the first cage (10). Assembly kit for a vehicle transmission, comprising a torsion damper assembly (1) comprising a pre-damper module (M) according to one of Claims 1 to 8. Assembly kit according to the preceding claim, further comprising:
- a rigid steering wheel; and or
- a release bearing; and or
- a clutch mechanism;