KR20010041090A - Torque damping device for friction clutch - Google Patents

Abstract

The invention relates to an apparatus comprising at least first and second shock absorbers (A, C) interposed between two rotating elements, one output element (12) forming a hub and one input element (11). Each shock absorber (A, C) comprises two guide washers, a front portion (20A, 20C) and a rear portion (21A, 21B) disposed axially on one side of the disk (22A, 22C); The disc 22C of the second shock absorber C is rotatably connected to the hub 12 and passed blockwise in the axial direction with respect to the radial flange 104 of the hub 12, the second shock absorber (C) is sandwiched between the front washer 20A and the disk 22A of the first shock absorber A centered on the hub 12 by the bearing surface 50. The present invention comprises at least one retaining element 106 in which the bearing surface 50 extends in the axial direction and the free end 108 edge is a portion 102C, 103C of the disk 22A of the second shock absorber C. It is characterized in that it extends opposite to) to block in the axial direction relative to the flange (104).

Description

Torsion Damping Device {TORQUE DAMPING DEVICE FOR FRICTION CLUTCH}

An example of such a design is described by way of example in French Patent Publication FR-A-2 735 548, which comprises a centering bearing acting between one of the guide rings of the main damper and the hub, the main damper of the pre-damper An elastic member having rigidity greater than rigidity is provided.

In such an embodiment, the radially inner circumferential surface of the damper plate of the central predamper is formed by an axial seaming operation performed from front to rear while a portion of the metal at the front axial end of the hub is disposed axially. It is fixed axially towards the rear on the hub with a stepped spline of.

This operation is carried out in a press and can limit and limit the choice of materials from which the central hub is made.

There is a need for a solution that can overcome this drawback.

Summary of the Invention

In this respect, the present invention provides a free end edge wherein the centering bearing comprises at least one retaining element, the retaining element extending axially rearward and facing the inner portion in the opposite radial direction of the damper plate of the second damper. And an axially positioned engagement with the shoulder surface.

This solution is because the axial positioning of the damper plate of the predamper derived from the conventional manufacturing method is known in the prior art of the various components for producing the torsional damping device, so that no additional components or additional assembly work is necessary. It is particularly simple, inexpensive and has an advantage. In addition, the hub can be made of a sintered material or a reinforced plastic material in the region of the spline of the hub for engaging the damper plate of the main damper. Moreover, the damper plate of the predamper and the predamper itself can be removed continuously.

According to another feature of the invention,

The retaining element is axially engaged with the facing portion of the damper plate of the second damper to eliminate axial clearance,

The retaining element is axially elastically engaged with respect to the facing portion of the damper plate of the second damper,

The retaining element has at least one elastically deformable part, in particular to reduce manufacturing tolerances,

The retaining element is connected to the body of the centering bearing via an elastically deformable connecting part, the bearing is easily manufactured by molding, and is made of a material which is moldable by conventional means,

The centering bearing has a longitudinal plate extending radially outwardly between the front guide rings of the first and second dampers, the retaining element being located radially inward of the longitudinal plate,

The retaining element extends axially rearward from the central longitudinal plane in which the longitudinal plate rests,

The retaining element is an annular cylindrical crown,

The retaining element is a retaining finger,

Each retaining finger extends axially between two consecutive stepped splines formed within the splined outer circumferential surface of the hub,

The centering bearing comprises a set of retaining fingers spaced circumferentially at regular intervals,

Each damper comprises a friction means, the friction means being operably interposed between the guide ring and the damper plate, the axial actuation of the elastic means being applied,

The second damper located directly upstream of the output element is a predamper, the first damper is a main damper located directly downstream of the input element, the device being dynamically connected between the first damper and the second damper; An intermediate third damper having the same design as the first damper and the second damper,

The holding element is produced in one piece with the centering bearing, in particular by molding from a plastic material.

The present invention relates, for example, to a torsion damping device of the same type as used in the form of friction clutches for automobiles.

Thus, the present invention is of a type having at least two damping stages and of a type comprising at least one external first damper in the radial direction and a second damper in the radial direction, in particular the first damper and the second damper , During the angular displacement between two coaxial rotating elements comprising a radially inner element, an output element in the form of a hub and a radially outer element, the input element, each damper being axially on one of the sides of the damper plate. A second damper comprising: two guide rings arranged in the first direction, i.e., a front guide ring and a rear guide ring, and a circumferentially elastic member operating between the damper plate and the two guide rings positioned on the side; Damper plate is rotated to the hub where it passes through the center, and the damper plate is rearward with respect to the radial outer circumferential shoulder surface of the hub. And a second damper, called a pre-damper, is arranged between the damper plate of the first damper, called the main damper, centered on the hub by an intervening centering bearing and the front guide ring of the first damper. A device of the type fixed in a direction.

Other features and advantages of the present invention will become apparent from the following detailed description with reference to the accompanying drawings.

1 is an axial cross-sectional view of a first embodiment of a torsion damping device comprising a series of three torsional dampers manufactured in accordance with features of the present invention;

FIG. 2 shows an alternative embodiment of the damping element for holding the damper plate to be axially located rearwardly and elastically biased backwardly, an enlarged view of the central portion of FIG. 1,

3 is an axial exploded view of the three components of FIG. 2;

4 to 6 show a second embodiment of the damping element according to the invention, a view similar to FIGS.

In the following detailed description, components that are the same, similar, similar or equivalent to each other are indicated by the same reference numerals.

It will be appreciated that the drawings show a torsional damping device of the same type as described in the above-mentioned French patent publication FR-A-2 735 534.

Thus, this torsional damping device 10 is not described in detail herein all, and the essential elements of the description of French Patent Publication FR-A-2 735 548 should be considered to form an integral part of the present invention. .

The torsion damping device 10 comprises three dampers A, B and C between the input element 11 and the output element 12 mounted so that the other rotates with respect to one, which damper comprises 11) and starts to operate dynamically during the annular displacement in the reverse order of the main damper (A), the intermediate damper (B) and the pre-damper (C), that is, the order in which they begin to operate. .

Considering the configuration of the clutch friction disk for automobiles, the input element 11 is a disk which typically bears a friction liner 14 fixed by riveting or adhesive bonding annularly on its respective face and on its outer peripheral surface ( 13). This disk 13 is axially elastic in a conventional manner.

As a result, the output element 12 is a hub 16 with an inner spline 15, which hub 16 has a reduced height outer portion 16 at one end thereof. At its other end, it has a truncated conical surface 17 having an embossed spline 18 in the gap. Further, the axial axis of symmetry of the hub 12 is the axis of symmetry and rotation of the torsion damping device.

The output element 12 has a longitudinal shoulder 19 on which the corresponding end of the spline 18 is continuous on the same side as the portion 16 of the reduced height.

Each damper (A, B, C) comprises two guide rings, namely front guide rings (20A, 20B, 20C) and rear guide rings (21A, 21B, 21C), which are damper plates (22A, 22B, Circumferentially disposed on one of the sides of 22C in the axial direction and interposed circumferentially between the guide rings 20A, 21A; 20B, 21B; 20C, 21C and the damper plates 22A, 22B, 22C. Axially actuated friction means interposed between actuating elastic members 23A, 23B, 23C, and guide rings 20A, 21A; 20B, 21B; 20C, 21C and damper plates 22A, 22B, 22C ( Mounted to rotate relative to the damper plates 22A, 22B, 22C within predetermined angular displacement limits with components fixed to 25A, 25B, 25C or damper plates 22A, 22B, 22C for rotation therewith. This friction means is subjected to the action of the elastic members 26A, 26B, 26C acting in the axial direction.

In this embodiment, the front guide ring 20A and the rear guide ring 21A of the main damper A are fixed to each other, by means of spacers 27 positioned around the outer circumferential surface and by the friction liner 14. The disks 13 supporting them are held at predetermined positions away from each other by being fixed to the front guide ring 20A. In such an embodiment, the spacer 27 consists of a short post.

These spacers 27 penetrate the notches 28 formed for this purpose on the outer circumferential surface of the damper plate 22A and extend together with a circumferential gap, and are adjacent to the ends of the notches 28, thereby damping the damper plate 22A. Specifies the limit of the angular displacement of the guide rings 20A, 21A. In another embodiment, the spacer surrounds the damper plate 22A, and the displacement is determined by the spring turn coupled to the elastic member 23A.

The damper plate 22A also has a notch 29 on its inner circumferential surface, by means of which the damper plate 22A has a circumferential clearance and the spline 18 of the output element 12. Meshes with

The elastic member 23A operating in the circumferential direction of the main damper A is partially formed in the window 31 formed in the damper plate 22A in contact with the window 30 formed in the guide rings 20A and 21A. Is located. Generally, the elastic members 23A, 23B, 23C are mounted in a housing formed to face each other in the guide ring and the damper plate. These housings consist of windows. In other embodiments, these housings are press molded embossed elements, or open notches or recesses.

In this case, each elastic member 23A is composed of two coaxial helical springs extending substantially tangentially to the circumferential direction of the assembly to increase torque transmission.

The intermediate damper B and the predamper C are both axially in this embodiment on the same front side of the damper plate 22A of the main damper A between the damper plate 22A and the front guide ring 20A. In other embodiments, it may be between the damper plate 22A and the rear guide ring 20B.

Thus, the intermediate damper B and the predamper C are located axially between the guide rings 20A, 21A of the main damper A. FIG.

The intermediate damper B, which generally encloses the pre-damper C, is positioned almost inward in the radial direction of the elastic member 23A acting in the circumferential direction of the main damper A, ie past the elastic member 23A.

The rear guide ring 21B is composed of the damper plate 22A of the main damper A, more precisely the innermost part in the radial direction of the damper plate 22A.

The front guide ring 20B is a component of the synthetic material or the cover member, and is arranged in friction axial contact with the front guide ring 20A of the main damper A.

This front guide ring 20B, which is a guide ring of the intermediate damper B, which is a damper further axially from the damper plate 22A of the main damper A, has a tenon 33 rearward in the axial direction. The front guide ring 20B is rotatably mounted therethrough on the damper plate, for which purpose the tenon 33 is engaged with a notch formed at the edge of the window 31 of the damper plate 22A. .

The tenon 33 extends through the damper plate 22A from one side to the other side, and an elastically deformable hook 35 is formed past the damper plate 22A so that the tenon 33 forms a sub-assembly. Snap fit on damper plate 22A to form.

Damper plate 22B has a notch 29 on its inner circumferential surface, by means of which notch 29 damper plate 22B has a circumferential clearance with spline 18 of output element 12. While engaged, the corresponding gap is smaller than the gap of the damper plate 22A of the main damper A. FIG.

The elastic member 23B operating in the circumferential direction of the intermediate damper B faces the recessed seat portion 37 in the front guide ring 22B and the window 38 of the rear guide ring 21B. Is partially engaged with window 39 of damper plate 22B.

In this embodiment, each of these elastic members consists of two coaxial helical springs, which are aligned substantially tangential to the pitch circle of the assembly to increase torque transmission.

The limit of the angular displacement between the guide rings 20B, 21B of the intermediate damper B and the damper plate 22B is the damper plate 22A of the main damper A, which is in close proximity to the spline 18 of the output element 12. Is defined by the circumferential end of the notch 29.

In the present embodiment, one of the guide rings 20C and 21C of the predamper C is composed of the damper plate 22B of the intermediate damper B, more precisely in the radial direction of the damper plate 22B. It consists of internal parts.

In this case, it is the rear guide ring 21C closer to the damper plate 22A of the main damper A in the axial direction.

The two guide rings 20C, 21C of the predamper C are fixed to rotate with each other by axial protrusions 40 formed on one of the guide rings, and these protrusions are formed with corresponding protrusions 41 formed on the other one. Meshes with

In this embodiment, the guide ring in which the axial protrusion 40 is formed is the rear guide ring 21C closer to the damper plate 22A of the main damper A in the axial direction, and the protrusion 41 is It is formed on the outer peripheral surface of the front guide ring 20C.

Thus, the axial protrusion 40 extends away from the damper plate 22A of the main damper A. As shown in FIG.

The axial protrusion 40 is formed in the window 39 of the damper plate 22B of the intermediate damper B, and is formed of a material included in the material that is normally removed to form the window 39 in FIG.

The damper plate 22C of the predamper C is fixed to the output element 12 for rotation together and is engaged at its inner peripheral surface on a portion of the spline 18 of the output element 12 with reduced height. The damper plate 22C is axially positioned in one direction on the output element 12 by the longitudinal shoulder defined by the change in the height of the spline 18.

The elastic member 23C acting in the circumferential direction of the predamper C partially engages the window 43 in the guide rings 20C and 21C and the window 44 in a relationship facing each other in the damper plate 22C. .

In this embodiment, each of these elastic members consists of a helical spring oriented substantially tangentially to the pitch circle of the assembly.

The limit of the angular displacement between the guide rings 20C and 21C of the predamper C and the damper plate 22C is the damper plate 22B of the intermediate damper B engaged with the spline 18 of the output element 12. It is defined by the circumferential end of the notch 36 in the circle.

The friction means 25A acting in the axial direction of the main damper A is located at a position away from the front guide ring 20B of the intermediate damper B, and the other side of the damper plate 22A from the front guide ring 22B. And a friction ring 45 on and in contact with the rear longitudinal face of the damper plate 22A.

The associated axially acting elastic member 26A consists of a Belleville ring or a corrugated ring in another embodiment, which bears the corresponding rear guide ring 21A of the main damper A.

The friction ring 45 lies at about the same level as the front guide ring 20B and is therefore spaced away from the output element.

This friction ring 45 bears an axial tenon 46 extending radially with respect to it away from the output element 12, and the rear guide ring of the main damper A closest to the friction ring 45 ( Mounted through the tenon 46 so as to rotate on 21A, which tenants 46 engage with the opening 48, which in this embodiment consists of a hole and is provided with a rear guide ring 21A. Is formed for this purpose.

Preferably, the tenon 46 extends through the guide ring 21A from one side to the other side, and an elastically deformable hook 49 is formed beyond the guide ring 21A such that the tenon is formed of the sub-assembly. Can be snap-fitted on the guide ring 22A to form it.

The tenon 46 may also be used for the purpose of centering a dish-shaped ring composed of an elastic member 26A acting axially.

The friction means 25C acting in the axial direction of the predamper C first comprises a bearing 50, which bearing 50 has an output element 12 and a main damper () to center the guide ring 20A. Interposed radially between the front guide rings 20A of A), penetrating the concave truncated conical surface 51 to bear on the convex truncated conical surface 17 of the output element 12, and secondly the output element. At the other end of 12 a friction ring 52 is included, which bears on the shoulder 19 of the output element 12 through an intermediate ring, not shown optionally. In this embodiment, the bearing 50 is molded from a plastic material.

The friction ring 52 includes a tenon 53 extending toward the rear and is mounted on the rear guide ring 21A of the main damper A so as to rotate together by the tenon 53, and these tenon 53. Is engaged with the notch 54 formed in the guide ring 21A for this purpose.

Similarly, with tenons not shown in FIGS. 1-3, the bearing 50 is mounted on the front guide ring 20A of the main damper A to rotate together. These tenants engage the holes in the front guide ring 20A but cannot be shown in FIGS. 4 to 6.

The associated axially actuated elastic member 26C consists of a dish-shaped ring or, in another embodiment, a corrugated ring, centered by the tenon 53, and engaged with the tenon 53 by a notch.

For reasons to be described later herein, the friction means 45 are part of the friction means 25A of the main damper A, and the friction means 25C of the pre-damper C are considered in the axial direction of the assembly. A radial extension 56 suitable for holding the friction ring 52. Thus, the guide ring 21A, the ring 45 snap-fitting on the ring 21A, the ring 52 engaged on the radial extension of the ring 45, and one ring 21A It is possible to form dish-shaped rings 26A and 26B which are clogged and installed between the ring and the other rings 45 and 52. The rings 45 and 26A surround the rings 52 and 26B.

The radial extension 56 may be formed as a continuous ring or divided into radial protrusions.

The elastic member 26B acting in the axial direction of the intermediate damper B has a front guide ring 20C and a retaining ring 57 of the predamper C axially away from the damper plate 22A of the main damper A. Is effectively interposed between the retaining ring 57 and the rear guide ring 21C of the predamper C closer to the damper plate 22A of the main damper A. Are arranged.

The attachment means comprise an axial protrusion 59 on the retaining ring, which extends axially rearward toward the damper plate 22A of the main damper A and at its free end. A hook 60 is formed, and the attachment means also comprise a protruding element on the rear guide ring 21C of the predamper C which is axially closer to the damper plate 22A of the main damper A.

Each such projecting element is defined by an edge of perforation formed for this purpose in the axial projection 40 of the rear guide ring 21C of the predamper C.

In this embodiment, the axial protrusion 40 of the rear guide ring 22C is an extension of the vertical flange of the rear guide ring 21C which is closer in the axial direction than the front guide ring 20C.

The retaining ring 57 is formed integrally with the bearing, and the elastic member 26B acting in the axial direction of the intermediate damper B consists of a dish-shaped ring or a corrugated ring in another embodiment, and the bearing 50 together Centered by a tenon mounted on the front guide ring 20C of the predamper C for rotation, the axially acting elastic member penetrates the notches and engages with these tenants. In this embodiment, the ring 57 is formed integrally with the bearing 50 by molding a moldable plastic material in this case.

According to this result, the friction means 25B of the intermediate damper B has a friction ring (axially disposed between the damper plate 22A of the main damper A and the damper plate 22B of the intermediate damper B). 67).

The friction ring 67 engages the output element 12 with a gap.

To achieve this purpose, the friction ring 67 has a notch 68 on its inner circumferential surface, whereby it engages with a gap on the spline 18 of the output element 12.

The friction ring 67 has a window 69 in which the elastic member 23C acting in the circumferential direction of the predamper C is axially engaged and reduces the size of the assembly.

The corresponding device is disclosed in EP-A-0 732 525, with reference to this document in particular with respect to the width of the window 69.

The friction ring 67 has a notch on its outer circumferential surface, which notches axially with the elastic member 23B acting in the circumferential direction of the intermediate damper B, and the friction ring 67 in the circumferential direction. To be returned by the actuating elastic member 23B.

Initially, the initial sub-assembly consists of an output element 12, a predamper C, an elastic member 26B acting in the axial direction of the intermediate damper B and a retaining ring 57, the predamper C Damper plate 22C is located axially on the output element 12 for holding the assembly against it.

It is important that the retaining ring 57 seals the initial sub-assembly axially from the front side, ie from the side axially further away from the damper plate 22A of the main damper A.

Subsequently, the second sub-assembly includes the damper plate 22A of the main damper A, the damper plate 22B of the intermediate damper B, and the elastic member 23B operating in the circumferential direction of the intermediate damper B. ), The front guide ring 20B of the intermediate damper B further axially away from the damper plate 22A of the main damper A, and the damper plate 22A and the intermediate damper B of the main damper A. It consists of the friction ring 67 of the friction means 25B of the intermediate damper B between the damper plates 22B.

Finally, the third sub-assembly is on the guide ring 21A to rotate with it as part of the rear guide ring 21A of the main damper A and the friction means 25A of the main damper A. It is composed of at least a friction ring 45 to be mounted and an elastic member 26A acting in the axial direction of the main damper A between the rear guide ring 21A and the friction ring 45.

This sub-assembly furthermore comprises a pre-damper between the friction ring 52 of the friction means 25C of the pre-damper C and the corresponding rear guide ring 21A of the friction ring 52 and the main damper A. An elastic member 25C acting in the axial direction of C), wherein the retention of the friction ring 52 is provided by the axial extension 56 of the friction ring 45.

As given above, the assembly can be carried out as follows.

For example, the first operation produces a sub-assembly consisting solely of the damper plate of the output element 12 and the predamper C, and then stacks the first sub-assembly, the third assembly and the remaining components. Assemble the assembly to complete the torsion damping device 10.

However, advantageously and advantageously, the above-described initial sub-assembly and the second sub-assembly, which have in common the damper plate 22B of the intermediate damper B, are first assembled separately and then joined together.

Next, to complete the torsion damping device 10, they together form a larger sub-assembly that is subsequently assembled by stacking with the third sub-assembly and various other components.

The rigidity of the elastic member 23C operating in the circumferential direction of the predamper C is made smaller than the rigidity of the elastic member 23B operating in the circumferential direction of the intermediate damper B, and the circumferential direction of the intermediate damper B is reduced. The elastic member 23B operating in the lower portion is smaller than the rigidity of the elastic member 23A operating in the circumferential direction of the main damper A.

The rigidity of the elastic member 26C acting in the axial direction of the predamper C is made smaller than the rigidity of the elastic member 26B acting in the axial direction of the intermediate damper B, and the axial direction of the intermediate damper B is The elastic member 26B acting as a lower than the rigidity of the elastic member 26A acting in the circumferential direction of the main damper (A).

In operation, when the input element 11 and the coaxial output element 12 are rotationally driven relative to each other, only the elastic member 23C acting in the circumferential direction of the predamper C is first compressed.

At this time, only the friction means 25C of the predamper C having the smallest rigidity acts.

In this regard, the guide rings 20C, 21C of the pre-damper C are then elastic members 26B operating in the axial direction of the intermediate damper B and elastic members operating in the circumferential direction of the main damper A. FIG. Fixed to the guide rings 20A and 21A of the main damper A to rotate together by 26A, and the friction ring 52 constituting the friction means 25C is mounted on these guide rings to rotate together, The same applies to the bearing 50 through the guide ring 20C of the predamper C.

In the second step, the elastic member 23B operating in the circumferential direction of the intermediate damper B is in turn compressed, but the elastic member 23C operating in the circumferential direction of the predamper C is kept compressed.

In collaboration with them, the intermediate damper B adds the effect to the effect of the friction means 25C of the predamper C. The friction means 25B.

In this regard, the rear guide ring 21B of the intermediate damper B, which is fixed relative to the output element 12 so as to rotate together, is provided by a corresponding circumferential clearance with respect to the damper plate 22A of the main damper A. Constant lag and displaced in the circumferential direction, which is arranged axially between the rear guide ring 21B and the damper plate 22A and constitutes a friction ring 67 constituting the friction means 25B of the intermediate damper B; The same is true for.

Finally, in the third step, the elastic member 23A acting in the circumferential direction of the main damper A is in turn compressed, but the elastic member 23B and predamper (operating in the circumferential direction of the intermediate damper B) The corresponding member 23C of C) is kept compressed.

At the same time, the friction means 25A of the main damper A add its own effect to the friction means 25C of the pre-damper C, which in turn act, but the friction means 25B of the intermediate damper B It does not work.

In this regard, next, the damper plate 22A of the main damper A and the rear guide ring 21C of the predamper C, with which the friction ring constituting the friction means 25B is interposed therebetween, are together. All are fixed relative to the output element 12 to rotate.

According to the above result, during each displacement between the input element 11 and the output element, the predamper C which is dynamically arranged upstream of the output element 12 is actuated first, while the intermediate damper B is operated. Starts to operate a second time, and the main damper A, which is operated directly by the input element 11, finally starts operating a third time. All of these are disclosed in French Patent Publication No. FR-A-2 764 018, which will be described in more detail with reference to this document.

Further, according to the above, the three dampers A, B and C are arranged in series.

If necessary, the circumferentially acting elastic members 23A, 23B, 23C can be mounted while pre-compressing the respective seating portions (ie, the windows 30, 38, 43 or recess 37).

In order to avoid the discontinuity of operation, the final torque of the predamper C can be made larger than the precompression of the elastic member 23B operating in the circumferential direction of the intermediate damper B, and the final torque of the intermediate damper B. Can be greater than the precompression of the elastic member 23A operating in the circumferential direction of the main damper A. FIG.

Preferably, the hooks 35 and 49 are integrally formed with the corresponding tenants 33 and 46, and are narrower in the circumferential direction than the tenants so that they do not participate in torque transmission and are thus maintained.

As particularly shown in FIGS. 2 and 3, the longitudinal rear face 100C of the radially inner portion 102C of the damper plate 22C of the pre-damper C is connected to the longitudinal proximal face 104. Positioned axially backwards, the longitudinal proximal face 104 defines a radial shoulder extending from the splined outer circumferential surface of the hub 12, in this embodiment of the stepped spline 18. It consists of a longitudinal plane that borders two parts.

In the technique as shown in FIGS. 1 and 2 of FR-A-2 735 548, the position in the forward axial direction of the damper plate 22C that engages against the shoulder face 104 is axial. Of the material of the hub is modified to reliably fix the damper plate 22C in the axial direction with respect to the hub 12 during the seaming operation.

According to a feature of the invention, it is proposed to use the centering bearing 50 to hold the damper plate 22C positioned axially towards the rear, ie towards the right in the figure.

To this end, in the first embodiment of FIG. 1 and in the variants of FIGS. 2 and 3, the centering bearing 50 comprises a set of generally axially oriented retaining elements or fingers 106. Each retaining element 106 is a free rear axial end that faces the opposite portion of the front longitudinal face 103C of the inner portion 102C in the radial direction of the damper plate 22C of the predamper C. 108.

More precisely, the retaining elements 106 are spaced circumferentially at regular intervals, the number of retaining elements being equal to the number of splines on the outer circumferential surface of the hub 12 such that each finger-shaped retaining element 106 is connected to the hub 12. It extends axially backwards between two consecutive splines 18 in the embossed phase.

In the embodiment shown in FIG. 1, the retaining fingers 106 in each axial direction are made integrally by shaping with the annular body of the centering bearing 50, and the retaining ring 57 is in the longitudinal direction of the bearing 50. Extending axially from the central plane extending radially outward in the form of a plate of the plate, which is held firmly axially between the front guide rings 20A, 20C with elastic actuation from the dish-shaped ring 26B. .

Each retaining finger 106 in this embodiment is in solid form. In order to achieve manufacturing tolerances and parts of good work, there needs to be some possibility of small axial displacement between the centering bearing 50 and the damper plate 22C of the predamper C. This possibility can be achieved by providing some axial working clearance between the free end 108 of the retaining finger 106 and the front longitudinal face 103C. Because of this operating gap, the operation of the axially acting elastic ring 26C is not impaired.

In other embodiments, the retaining fingers 106 in the axial direction may be arranged to have elastically deformable in the axial direction, in particular to reduce clearances and manufacturing tolerances. In this regard, it is possible, for example, to form each free rear end 108 of the finger 106 in a way to provide axially elastic deformation. Such deformability can be ensured, for example, by manufacturing each free rear end 108 from an elastomeric material using techniques known as co-molding.

Other possibilities shown in FIGS. 2 and 3 each free end 108 in the axial body of the retaining finger through a reduced thickness cutout that acts as a compression spring and constitutes an elastically deformable tongue 112. It is configured by connecting.

Accordingly, the inner portion 102 in the radial direction of the damper plate 22C of the predamper C is formed by integrally forming with the longitudinal shoulder face 104 oriented forward and the body of the centering bearing 50. It is firmly held in the axial direction between the front axial ends of the retaining finger 106.

The shiming operation of the damper plate 22C is omitted, and the hub 12 can then advantageously be made of a sintered material.

It is also possible to remove the damper plate 22C from the hub 12 by removing the centering bearing 50. In all cases, the stiffness of the ability for elastic deformation of the finger 106 or the end 108 of the tongue 112 is less than the stiffness of the elastic means 26C so as not to interfere with the operation of the elastic means 26C. .

Now, a second embodiment of the present invention will be described in detail.

The second embodiment relates to a torsional damping device having two stages (A, C) of the same type directly as in French Patent 94.02960, which is published by reference to Publication No. 2,718,208.

4 to 6 show a central block constituting the predamper C having its guide rings 20C and 21C, and a damper plate 22C which is rotationally driven by the spline 18 of the hub 12. As shown, the interior 102C in the radial direction of the damper plate 22C is positioned axially towards the rear with respect to the longitudinal shoulder face 104.

The driving projection 59 oriented rearward in the axial direction is a portion of the front guide ring 20C, and extends axially beyond the rear guide ring 21C through the slot in the damper plate 22A of the main damper A. do.

In order to position the damper plate 22C of the damper C in the rearward axial direction, an annular cylindrical retaining crown 106 is provided, which is integrally formed with the body of the centering bearing 50. And an annular axial end edge which cooperates with the facing portion of the rear longitudinal surface 103C of the inner portion 102C in the radial direction of the damper plate 22C.

Thus, a single continuous axial retaining element 106 is provided for the damper plate 22C, and in this embodiment a small axial gap between its distal edge 108 and the damper plate 22C is provided. It is a solid material having.

As in the case of the multiple retaining fingers described above, the fabrication of the edge 108 of the elastically deformable material and the biasing in the axial engagement from the rearward to the front face 103C of the damper plates 22C and 102C. It is possible to interpose elements constituting an axial compression spring between the annular cylindrical rear end portion and the body of the centering bearing 50.

Also shown in FIG. 4 is a tenon (without reference numeral) of the conical bearing 50 which engages the hole in the guide ring 20A.

In another embodiment, the bearing 50 may be made hollow to receive the elastic member of the predamper (C).

Next, the bearing 50 acts as a guide ring for the resilient member of the predamper, and in other embodiments FIG. 1 and FIG. 1 of FR-A-2 728 642, which can be found in more detail by reference. It has a curved shape as shown at 12.

In the figure, the retaining element 106 according to the invention lies radially inward of the ring 57 and does not interfere with the operation of the elastic ring 26C. More precisely, when the retaining elements 106, 108 are axially elastically engaged with the facing portions 102C, 103C of the damper plate 22C, this elasticity is axially acting elastic means 26C. Must be smaller than the elasticity, i.e., the rigidity is smaller than the elastic means 26C. 4 to 6, the retaining element 106 according to the invention first extends radially inward of the resilient member 23C of the predamper C and secondly the spline of the hub 12 having a reduced height. Extend radially outward of the portion of (18). In other embodiments, the retention element can of course pass into a recess between two splines, as in FIGS. 1-3.

Of course, the input element of the torsion damping device consists directly of an extension or disc 13 of the guide ring 20A fixed on the engine flywheel as shown in FIG. 1 of US Patent Publication No. US-A-4,351,168.

Claims (14)

A type comprising at least one radially external first damper A and a radially internal second damper, wherein the first damper A and the second damper C are in particular in the form of hubs. It operates during the angular displacement between two coaxial rotating elements 11, 12 comprising an inner element 12 radially as an output element and an outer element 11 radially as an input element, said dampers A, C) is located at the side with two guide rings, ie front guide rings 20A, 20C and rear guide rings 21A, 21B, disposed axially on one of the sides of the damper plates 22A, 22C. A type including circumferentially elastic members 23A and 23C operating between the damper plates 22A and 22C and the two guide rings 20A, 21A; 20C and 21C, and the second damper ( The damper plate 22C of C) is rotatably connected to the hub 12 through which it passes through the center, and the dam The hub is of a type in which the plate is axially positioned to engage rearward with respect to the radially outer circumferential shoulder surface 104 of the hub 12 and a centering bearing 50 with the second damper C interposed therebetween. A torsional damping device 10 of the type axially fixed between the damper plate 22A of the first damper A and the front guide ring 20A of the first damper A centered on 12. (a torsion damping device), The centering bearing 50 comprises at least one retaining element 106, the retaining element 106 extending in the axial rearward direction, the opposite radius of the damper plate 22A of the second damper C. Characterized in that it is axially positioned in engagement with the shoulder surface 104 with a free distal edge 108 facing the inner portions 102C, 103C in the direction thereof. Torsion damping device. The method of claim 1, Characterized in that the retaining elements (106, 108) are axially engaged with respect to the facing portions (102C, 103C) of the damper plate (22C) of the second damper (C). Torsion damping device. The method of claim 2, Characterized in that the retaining elements (106, 108) are elastically engaged in the axial direction with respect to the facing portion of the damper plate (22C) of the second damper (C). Torsion damping device. The method of claim 3, wherein Characterized in that the retaining elements (106, 108) have at least one elastically deformable portion (108, 112). Torsion damping device. The method of claim 3, wherein Characterized in that the retaining elements (106, 108) are connected to the body of the centering bearing (50) via an elastically deformable connecting portion (112). Torsion damping device. The method according to any one of claims 1 to 5, The centering bearing 50 has a longitudinal plate 57 extending radially outwardly between the front guide rings 20A, 20C of the first and second dampers A, C, the holding Element 106, 108 is characterized in that it is located radially inward of the longitudinal plate 57. Torsion damping device. The method of claim 6, The retaining elements 106, 108 are characterized in that they extend axially rearward from the central longitudinal plane in which the longitudinal plates 57 rest. Torsion damping device. The method according to any one of claims 1 to 7, Characterized in that the retaining elements (106, 108) are annular cylindrical crowns Torsion damping device. The method according to any one of claims 1 to 7, Characterized in that the retaining elements (106, 108) are retaining fingers. Torsion damping device. The method of claim 9, Each retaining finger 106, 108 extends axially between two consecutive stepped splines 18 formed in the splined outer circumferential surface of the hub 12. Torsion damping device. The method of claim 10, The centering bearing 50 is characterized in that it comprises a set of holding fingers (106, 108) spaced circumferentially at regular intervals Torsion damping device. The method according to any one of claims 1 to 11, Each of the dampers A, C includes friction means 25A, 25C, and the friction means 25A, 25C comprise the guide rings 20A, 20C; 21A, 21C and the damper plates 22A, 22C. It is interposed operatively, and the axial actuation of the elastic means 26A, 26C is applied, It is characterized by the above-mentioned. Torsion damping device. The method according to any one of claims 1 to 12, The second damper (C) located directly upstream of the output element (12) is a pre-damper, the first damper (A) is a main damper located directly downstream of the input element (11), and the device (10) has a design 20B, 21B, 22B which is dynamically connected between the first damper A and the second damper C and is identical to the first damper A and the second damper C. It characterized in that it comprises an intermediate third damper Torsion damping device. The method according to any one of claims 1 to 13, Characterized in that the retaining elements (106, 108) are produced in one piece with the centering bearing (50), in particular by molding from a plastic material. Torsion damping device.