WO2019185836A1

WO2019185836A1 - Torsion-damping device with a main damper and a supplementary damper

Info

Publication number: WO2019185836A1
Application number: PCT/EP2019/057929
Authority: WO
Inventors: Roel Verhoog; Michaël Hennebelle
Original assignee: Valeo Embrayages
Priority date: 2018-03-30
Filing date: 2019-03-28
Publication date: 2019-10-03
Also published as: JP2021519405A; CN112105838A; FR3079574A1; JP7213887B2; DE112019001688T5; FR3079574B1; CN112105838B

Abstract

Torsion-damping device for a vehicle transmission chain, comprising: - a first rotating torque transmission element (7); - a second rotating torque transmission element (9a, 9b); - at least one damping module (M1, M2) comprising a main damper arranged between the first rotating element and the second rotating element, each main damper comprising a group of springs which comprises a first spring (13-1) and a second spring (13-2) arranged in series by means of a phasing member (15), the first spring and the second spring being respectively arranged between the first rotating element and the phasing member and between the phasing member and the second rotating element, the first spring and the second spring enabling, when they deform, a relative rotation about an axis of rotation (X) between the first rotating element and the second rotating element.

Description

TORSION DAMPING DEVICE WITH MAIN SHOCK AND

ADDITIONAL SHOCK ABSORBER

The invention relates to the field of torque transmission in motorized devices and relates to a torsion damping device for a vehicle transmission chain.

Motor vehicles generally include such torsion damping devices that can be integrated in various elements of the transmission chain such as a dual flywheel flywheel or a clutch disc. A torque limiter may also be associated with a torsion damping device for filtering motor acyclisms and other torsional oscillations. This filtering is typically carried out by one or more torsion damping modules which are spring-damping assemblies working in torsion and allowing, during transmission of the torque, a relative rotational movement of a first rotary transmission element. a torque with respect to a second rotational torque transmission element. The relative rotation may be permitted by springs and the damping may be achieved by a friction device provided with friction washers loaded axially by spring washers, so as to dissipate by friction a part of the energy accumulated in them. springs.

When designing such a torsion damping device, special attention is given to the choice, dimensioning, and arrangement of the springs, to obtain a characteristic curve adapted to a particular application.

The invention aims to improve the torsion damping devices of the prior art by providing such a device whose characteristic curve is flexible. In particular, the invention aims to increase the angular stiffness of a damping device beyond a predetermined angular deflection threshold.

For this purpose, the invention provides a torsion damping device for a vehicle transmission chain, comprising:

a first rotating element for transmitting a torque;

a second rotary torque transmission element;

at least one damping module comprising a main damper arranged between the first rotating element and the second rotating element, each main damper comprising a group of springs comprising a first spring and a second spring arranged in series via a phasing member, the first spring and the second spring being respectively arranged between the first rotating element and the phasing member and between the phasing member and the second rotating element, the first spring and the second spring allowing, when deformed, a relative rotation about an axis of rotation between the first rotating element and the second rotating element.

Each damping module comprises an additional spring carried by the phasing member, the torsion damping device being configured so that, in a first direction of relative rotation of the first rotating element relative to the second element rotating from a position relative angular rest taken by the first rotating element and the second rotating element without stressing speed or torque:

when the angular displacement between the first rotating element and the second rotating element is less than a first angular displacement threshold between the first rotating element and the second rotating element, the additional spring is remote from the first rotating element so that no additional torque is transmissible by the additional spring between the phasing member and the first rotating element, and

when the angular displacement between the first rotating element and the second rotating element is greater than or equal to the first angular displacement threshold, the additional spring bears directly or indirectly against the first rotating element so that an additional torque can be transmitted. by the additional spring between the phasing member and the first rotating member.

Here and in the rest of the document the expression "direct and indirect" or "directly or indirectly" is used because interface elements such as seats can be used between on the one hand, the first rotating element or the second element rotating or the phasing device and secondly, the springs.

The expression "relative direction of rotation" is used to define the relative rotation of the first rotating element relative to the second rotating element.

The damping device may also include one or more of the following features:

Each additional spring is a coil spring comprising: a first bearing surface arranged to bear directly or indirectly against the phasing member, and a second bearing face adapted to bear directly or indirectly against a first actuating surface of the first rotating element when the angular displacement between the first rotating element and the second rotating element is greater than or equal to the first angular displacement threshold, in the first direction of relative rotation.

The torsion damping device is arranged such that each second spring stops compressing when the angular displacement between the first rotating element and the second rotating element is greater than or equal to a second angular displacement threshold between the first rotating element and the second element rotating in the first direction of relative rotation, from the relative angular position of rest. Thus, the deactivation of each second spring makes it possible to increase the stiffness of the damping device beyond the second predetermined threshold of angular deflection.

According to one embodiment, the torsion damping device comprises a first stop carried by the phasing member and arranged to cooperate with a second stop carried by the second rotating element when the angular displacement between the first rotating element and the second rotating element is greater than or equal to a second angular displacement threshold between the first rotating element and the second rotating element in the first relative direction of rotation, from the relative angular position of rest. Thus, bringing the first stop into contact with the second stop makes it possible to stop the compression of the second spring by transmitting a torque directly between the first stop of the phasing member and the second stop of the second rotating member so as to increase and the stiffness of the damping device.

In a variant, each second spring is configured to be compressed to its maximum, with its contiguous turns, when the angular displacement between the first rotating element and the second rotating element is greater than or equal to the second angular displacement threshold between the first rotating element and the second rotating element.

The torsion damping device has an angular position of maximum angular deflection when the angular displacement between the first rotating element and the second rotating element reaches a third threshold of angular displacement between the first rotating element and the second rotating element in the first direction. relative rotation of the first element rotating relative to the second rotating element, from the relative angular position of rest. In other words, there is no more damping of the torque when the transmitted torque is greater than the torque generating an angular displacement equal to the third threshold.

The third threshold can be obtained by means of stops and / or can correspond to a maximum compression of the springs.

Thus, in a damping phase obtained in the first direction of relative rotation and when the angular displacement between the first and second rotating elements is, relative to the relative angular position of rest, greater than zero and lower than the first threshold A1; each additional spring is not biased and the damping is obtained by: the first spring and the second spring of each group of springs then, if desired, the first spring only of each group if the first and second stops are already in support or if the second spring of each group is compressed to its maximum (contiguous turns).

Then, in a subsequent phase of damping obtained when the angular displacement between the first and second rotating elements is greater than said first threshold in the first direction of relative rotation, the second bearing surface and the first actuating surface of the first element are pressed against each other so that the additional spring is compressed in parallel with the first spring.

There are actually three possible alternatives:

- Let the first threshold and the second threshold are substantially equal, and the damping curve generally has two slopes, the first slope corresponding to the compression of the first and second series of springs and the second slope corresponding to the compression of each first spring and each additional spring in parallel. The second slope is then significantly greater than the first slope since this second slope simultaneously corresponds to the deactivation of each second spring by the first and second stops and the compression of each additional spring in parallel with each first spring.

- Either the first threshold and the second threshold are different and the damping curve then overall has three slopes, the first slope corresponding to the compressing each first spring and each second spring in series and the third slope corresponding to the compression of each first spring and each additional spring in parallel. The second slope then corresponds to: the compression of each first spring only when the second threshold is lower than the first threshold; or at the compression of each second spring, each in series with an assembly formed by a first spring and an additional spring which are arranged in parallel, when the second threshold is greater than the first threshold

A transition slope is thus obtained between the first "relatively low" stiffness slope and the "relatively strong" third stiffness slope.

According to one embodiment, the first rotating member forms the torque input member (E) of the torsion damping device and the second rotating member forms the torque output member of the torsion damping device. The element of the damping device by which torque from the motor enters the torsion damping device is referred to as the input element. The output element is the element of the damping device by which the torque exits the torsion damping device to go to the gearbox.

Alternatively, the first rotating member forms the torque output member (S) and the second rotating member forms the torque input member of the torsion damping device.

One of the first rotating element and the second rotating element is formed by two guide washers which axially hold the first spring and the second spring of each group of springs; and the other of the first rotating element and the second rotating element is formed by a web arranged axially between the two guide rings. According to one embodiment, the second rotating element is formed by two guide washers which axially hold the first spring and the second spring of each group of springs, and the first rotating element is formed by a web arranged axially between the two washers. guidance. Alternatively, the first rotating element may be formed by two guide washers which axially hold the first spring and the second spring of each group of springs, and the second rotating element may be formed by a web arranged axially between the two guide rings.

Each damping module comprises at least one pair of transmission plates carried by the phasing member, each pair of transmission plates comprising a first transmission plate and a second transmission plate axially spaced relative to one another. other; each transmission plate comprising a first thrust zone cooperating directly or indirectly with a first end of the first spring and a second thrust zone cooperating directly or indirectly with a first end of the second spring, said first thrust zones of each pair of plates being axially spaced from each other and said second thrust zones of each pair of plates being axially spaced apart from each other. Thus, the transmission of the torque between the phasing member and each group of springs is directly or indirectly on the lateral zones of the faces of the first ends of the first and second springs. The zones of thrust of the plates are thus arranged axially on either side of the geometric centers of the faces of the ends of the first and second springs. It is thus possible to define the thrust polygon with the spacing between the first plate and the second plate and to improve the stability of the torque transfer by the phasing member.

The term plate is not limited here to a flat element, but an element, especially metal, thick enough thin to be deformed, especially stamped.

The first transmission plate and the second transmission plate of each pair of transmission plates are formed respectively on a first phasing washer and a second phasing washer spaced axially from each other.

The additional spring of a damping module is disposed, at least in part, circumferentially between the first spring and the second spring of this damping module.

The first spring has a first central axis and the second spring has a second central axis, the intersection of the first central axis and the second central axis being located in the space occupied by the additional spring.

There is a plane perpendicular to the axis of rotation passing through the first spring, the second spring, and the additional spring. The phasing member comprises at least one annular portion of radial extension disposed radially inside the first spring and the second spring.

Each phasing washer comprises an annular portion of radial extension disposed radially inside the first spring and the second spring.

By arranging this annular portion radially inside the first and second springs (rather than outside), there is less deformation of this annular portion. In addition, there is less inertia, which avoids a resonance frequency with a low frequency that would be detrimental,

The first spring and the second spring are arranged substantially on the same radius around the axis of rotation. In other words, they are arranged in series in the same circular trajectory.

The stiffness of the first spring is between 50% and 150% of the stiffness of the second spring.

The first spring occupies a volume of between 50% and 150% of the volume occupied by the second spring

The two phasing washers are fixed to each other axially at a distance from each other. In particular, the two phasing washers are fixed to one another by means of spacers, each spacer having a first end crimped on one of the phasing washers and a second end crimped on the other of the phasing washers .

The two phasing washers are arranged on both sides of the veil.

The second rotating element comprises two guide washers arranged axially on either side of the phasing member.

Each damping module comprises a transmission head carried by the phasing member and arranged circumferentially between the first spring and the second spring of the spring group of the damping module, each transmission head comprising a housing inside which the additional spring of the damping module is housed so as to transmit an additional torque between the phasing member and the first rotating element when the angular displacement between the first rotating element and the second rotating element is greater than or equal to the first threshold of angular deflection in the first direction of relative rotation. For each damping module, the transmission head is formed by the pair of transmission plates, the first transmission plate and the second transmission plate each comprising a recess, the recess of the first transmission plate and the recess. the second transmission plate being arranged axially vis-à-vis one with respect to the other so as to accommodate the additional spring of the corresponding damping module.

Each transmission head further comprises two axial retaining elements of the associated additional spring, the two axial retaining elements of the additional spring being arranged axially on either side of the additional spring.

Each axial retention element of the additional spring is formed by a retaining tab folded in a direction having a radial component, the retaining tab being formed in one of the first and second transmission plates of said transmission head.

Each transmission head thus comprises two axial retaining elements arranged axially on either side of the additional spring associated with the transmission head. The phasing member thus also provides axial guidance of each additional spring.

Each axial retaining tab projects with a radial component from an edge of the recess of the first or second transmission plate having said retaining tab. In particular, the retaining tab projects from the lower radial edge of the recess. In other words, the contour of the retaining tab defines a portion of the contour of the recess before the folding of the retaining tab.

Each transmission plate comprises a first radial retaining element arranged to radially maintain the first spring associated with said transmission plate with respect to the centrifugal forces and a second radial retaining element arranged to maintain radially the second spring associated with said plate. transmission against centrifugal forces.

The first radial holding member and the second radial holding member of each transmission plate are arranged in the circumferential extension of the associated additional spring, circumferentially on either side of the associated additional spring.

The first radial retaining element is a first finger extending circumferentially radially outwardly of the first spring. The second radial retaining element is a second finger extending circumferentially, radially outside the second spring.

On each plate, the first finger protrudes and extends circumferentially from an outer radial end of the first pusher zone.

On each plate, the second finger protrudes and extends circumferentially from an outer radial end of the second thrust zone.

If desired, each additional spring is mounted prestressed in its housing.

Each additional spring is arranged circumferentially between the first spring and the second spring of the associated damping module.

The volume of the first and second springs of each damping module is part of a torus and at least part of the additional spring associated is also in this torus. Thus, it is possible to provide a radially compact damping device.

The first spring and the second spring of a damping module extend respectively along a first axis and a second axis, the first axis and the second axis being substantially in a perpendicular implantation plane to the axis of rotation X, and the additional spring associated with this damping module extends along a third axis also being substantially in this implantation plane. Thus, it is possible to provide a compact damping device axially.

Each additional spring has, in a plane perpendicular to the axis X, a first inner corner facing the first spring of the module associated with said additional spring and a second inner corner facing the second spring of the module associated with said additional spring, the first corner. interior and the second inner corner being arranged, in this plane, circumferentially between the face of the first end of the first spring and the face of the first end of the second spring which cooperate with the phasing member.

Each phasing washer has an annular portion and each plate is connected to the annular portion of the phasing washer by a radial arm.

The first thrust zone of each plate is formed by a first wall of said plate and the second thrust zone of each plate is formed by a second wall of said plate. The inclination of the first wall and the inclination of the second wall of the same plate are such that, in a plane perpendicular to the axis X passing through the first wall and the second wall, the line of intersection of the first wall with said plane intersects the intersection line of the second wall with said plane between the associated additional spring and the axis of rotation X.

For example, the angular stiffness of the additional spring is at least twice the angular stiffness of the stiffest spring of the first spring and the second spring. For example, the angular stiffness of the first spring can be 1ONrn / ⁰ , plus or minus 50%, the angular stiffness of the DR2 can be 15 Nm / ° plus or minus 50%, and the angular stiffness of the additional spring can be 30 Nm / ° plus or minus 50%.

The first rotating element comprises for each group of springs a main opening adapted to accommodate the first spring and the second spring.

The first rotating element comprises for each damping module a cavity adapted to allow a circumferential movement of the additional spring relative to the first rotating element, the first actuating surface 40 forming one of the circumferential ends of this cavity.

The main opening and the cavity associated with the same damping module are formed in the same window of the first rotating element.

The first rotating element has a first bearing surface arranged to cooperate with a second end of the first spring opposite the first end of the first spring and a second bearing surface arranged to cooperate with a second end of the second spring, opposite the first end of the second spring.

The guide washers of the second rotating element are formed in a sheet and each have for each group of springs a stamped portion arranged to partially accommodate and axially guide the first spring and the second spring of the spring group.

Each guide washer has for each group of springs a third bearing surface arranged to cooperate with the second end of the first spring and a fourth bearing surface arranged to cooperate with the second end of the second spring.

The first stop is located on the outer periphery of the phasing member. The first transmission plate and / or the second transmission plate of the phasing member comprises a lug forming the first stopper bl. The lug extends axially so as to radially cover a radially outer edge of the second rotating element.

The lug is arranged radially above the additional spring.

A curved lip in the direction of the lug connects the lug to a radially outer edge of the recess of each plate. This lip stiffens the plate radially outside the recess.

The second stop is located on the outer periphery of the second rotating element.

The second stop is formed by a first tooth extending radially outwardly of at least one of the guide washers.

Each transmission head has a first stop.

The torsion damping device comprises a third stop carried by the first rotating element and arranged to cooperate with a fourth stop carried by the second rotating element when the angular displacement between the first rotating element and the second rotating element reaches the third threshold of angular deflection between the first rotating element and the second rotating element in the first relative direction of rotation of the first rotating element relative to the second rotating element, from the relative angular position of rest.

The third stop is located on the outer periphery of the first rotating element.

The third stop is formed by a hook formed on the outer radial periphery of the web, the hook having an end zone extending substantially axially, this end zone being able to move circumferentially, radially outwardly of an outer radial edge of one of the guide washers 9a, 9b.

The third stop is arranged circumferentially between two main openings of the first rotating element.

The fourth stop is located on the outer periphery of the second rotating element.

The fourth stop is formed by a second tooth extending radially outwardly of at least one of the guide washers.

The damping device comprises two damping modules. The torsion damping device is configured so that, in a second direction of relative rotation of the first rotating member relative to the second rotating member, opposite the first direction of relative rotation, from a relative angular position of rest taken by the first rotating element and the second rotating element without biasing speed or torque: each additional spring is remote from the first rotating element when the angular displacement between the first rotating element and the second rotating element is less than a fourth angular displacement threshold between the first rotating element. rotating element and the second rotating element, and each additional spring bears directly or indirectly against the first rotating element when the angular displacement between the first rotating element and the second rotating element is greater than or equal to the fourth angular displacement threshold, so that a Additional ouple can be transmitted by each additional spring between the phasing member and the first rotating member.

On the other hand, no additional spring transmits additional torque between the phasing member and the first rotating element when the angular displacement between the first rotating element and the second rotating element is less than the fourth angular displacement threshold.

The second bearing surface of each additional spring is arranged to bear directly or indirectly against the phasing member, and the first bearing face is adapted to bear directly or indirectly against a second actuating surface of the first rotating element when the angular displacement between the first rotating element and the second rotating element is greater than or equal to the fourth angular displacement threshold, in the second relative direction of rotation.

The second bearing surface of each additional spring is arranged to bear directly or indirectly against a second circumferential edge opposite the first circumferential edge of the recesses of the first transmission plate and the second transmission plate associated with said additional spring.

The torsion damping device is arranged so that the second spring ceases to compress when the angular displacement between the first rotating member and the second rotating element is greater than or equal to a fifth threshold of angular displacement between the first rotating element and the second rotating element in the second relative direction of rotation, from the relative angular position of rest. Thus, the deactivation of the second spring makes it possible to increase the stiffness of the damping device beyond the fifth predetermined threshold of angular deflection, in this second direction of relative rotation.

A fifth stop being carried by the phasing member and being arranged to cooperate with a sixth stop carried by the second rotating element when the angular displacement between the first rotating element and the second rotating element in the second direction of relative rotation reaches the fifth. travel threshold. Thus, bringing the fifth abutment into contact with the sixth abutment makes it possible to stop the compression of the second spring by transmitting a torque directly between the fifth abutment of the phasing member and the sixth abutment of the second rotating element so as to increase and the stiffness of the damping device.

The fifth stop is also formed on the lug forming the first stop.

The first abutment and the fifth abutment are formed on the two circumferentially opposite edges of the stub

The sixth stop is formed on the second tooth also forming the fourth stop.

The fourth abutment and the sixth abutment are formed on the two circumferentially opposite edges of the second tooth.

The torsion damping device has an angular position of maximum angular displacement when the angular displacement between the first rotating element and the second rotating element reaches a sixth threshold of angular displacement between the first rotating element and the second rotating element in the second direction. relative rotation of the first rotating element relative to the second rotating element, from the relative angular position of rest. In other words, there is no longer any damping of the torque for a torque greater than the torque generating an angular displacement equal to the sixth threshold.

The sixth threshold can be obtained by means of stops and / or can correspond to a maximum compression of the springs.

The additional spring is mounted fitted or tightened between firstly the first circumferential edges of the recesses of the first and second transmission plates and secondly their second circumferential edges. Each additional spring can be mounted prestressed in its housing.

The torsion damping device according to the preceding claim wherein the torsion damping device comprises a seventh stop carried by the first rotating element and arranged to cooperate with an eighth stop carried by the second rotating element when the angular displacement between the first rotating element and the second rotating element reaches the sixth angular displacement threshold between the first rotating element and the second rotating element in the second relative rotational direction of the first rotating element relative to the second rotating element, from the relative angular position of rest .

The seventh stop is formed on the hook also forming the third stop.

The seventh abutment and the third abutment are formed on the two circumferentially opposite slices of the hook.

The eighth stop is formed on the first tooth also forming the second stop.

The second bearing face of each additional spring is arranged to bear directly or indirectly against a second circumferential edge of the recesses of the first transmission plate and the second transmission plate associated with said additional spring.

A first support seat is interposed on the one hand between the first rotating element and the first spring of each damping module and secondly between the second rotating element and the first spring of each damping module.

A second support seat is interposed on the one hand between the first rotating element and the second spring of each damping module and secondly between the second rotating element and the second spring of each damping module.

The first bearing surface comprises a first notch arranged to house a pivot projecting from the first seat.

The second bearing surface comprises a second notch arranged to accommodate a pivot projecting from the second seat.

The third bearing surface comprises a third notch arranged to accommodate the pivot projecting from the first seat. The fourth bearing surface comprises a fourth notch arranged to accommodate the pivot projecting from the second seat.

A third support seat is interposed between the phasing member and the first spring of each damping module.

A fourth support seat is interposed between the phasing member and the second spring of each damping module.

The third seat has a front bearing face cooperating with the first end of the first spring.

The fourth seat has a front bearing face cooperating with the first end of the second spring.

According to one embodiment, the second support seat and the fourth support seat are arranged to come into contact with each other when the angular displacement between the first rotating element and the second rotating element is greater than or equal to at the second angular displacement threshold between the first rotating element and the second rotating element in the first relative direction of rotation, from the relative angular position of rest. In other words, the first stop is formed on the fourth support seat and the second stop is formed on the second support seat.

Each support seat comprises a cap arranged to retain radially the spring against which it rests, vis-à-vis the centrifugal forces.

The first stop is formed at the end of the cap of the fourth support seat and the second stop is formed at the end of the cap of the second support seat.

According to one embodiment, the two axial retaining elements of each transmission head are formed by blinkers; the first and second transmission plates associated with the corresponding transmission module each comprising a blinker.

Two notches are made on each plate, circumferentially on either side of the plate portion intended to form the eye.

If desired, at least one of the circumferential edges of the eyelet forms the first stop of the damping device. Thus, the eyecup is arranged to bear against a tooth of the second rotating element forming the second stop when the angular displacement between the first rotating element and the second rotating element is greater than or equal to second angular displacement threshold between the first rotating element and the second rotating element in the first direction of relative rotation of the first rotating element relative to the second rotating element, from the relative angular position of rest.

The other circumferential edge of the eyelet forms the fifth stop of the damping device.

The phasing member comprises means for axial guidance of the first spring and the second spring.

For example, each transmission plate comprises a first centering member arranged inside the first end of the first spring and a second centering member arranged inside the first end of the second spring.

Thus it is possible to axially guide the first spring and the second spring.

Each centering member is a tongue formed in the plate of the plate and curved in the shape of C.

The tongue forming the first centering member of the first transmission plate and the tongue forming the first centering member of the second transmission plate are arranged axially vis-à-vis to form a centering tube of the first spring.

The tongue forming the second centering member of the first transmission plate and the tongue forming the second centering member of the second transmission plate are arranged axially vis-à-vis to form a centering tube of the second spring.

One of the first rotating element and the second rotating element is rotatably coupled to a friction disc and the other one of the first rotating element and the second rotating element is coupled in rotation with a hub adapted to drive a rotation thereof. gearbox input shaft.

The first rotating element is rotatably coupled to a friction disc and the second rotating element is rotatably coupled to a hub adapted to rotate a gearbox input shaft.

The damping device also comprises a friction device F intended to dissipate the energy of the springs and to avoid oscillation phenomena. Preferably, the friction device is arranged to rub only in the direction of retro transmission. The invention also relates to a transmission system comprising a torque limiter comprising a friction disc and a damping device according to one of the preceding claims, the friction disk being mounted integral in rotation with one of the first rotating element and the second rotating element of the damping device.

The additional spring is disposed radially inside the friction disc.

According to another solution: the third support seat is pivotally mounted on the phasing member. the fourth support seat is pivotally mounted on the phasing member.

The third seat and the fourth seat are mounted pivoting about the same pivoting axis. Thus the inclination of the third seat and the fourth seat can change depending on the torque transmitted by the damping device and depending on the centrifugal forces. The pivoting of the seats thus makes it possible to limit the friction at the level of the first and second springs.

The third support seat and / or the fourth support seat 180 are pivotally mounted around the connecting spacer of the two phasing washers, the spacer 116 forming the pivoting axis of the seats;

The third seat and the fourth seat each comprise a pierced connecting lug axially overlapping so that their drilling also overlaps, the pivoting shaft being introduced both into the piercing of the connecting lug of the third seat and into the piercing. the connecting leg of the fourth seat.

The third seat has a back support face cooperating with the additional spring. This bearing face is formed in a notch of the third seat.

The third seat is interspersed circumferentially between the first spring and the additional spring.

The fourth seat has a back support face cooperating with the additional spring. This bearing face is formed in a notch of the fourth seat.

The fourth seat is interspersed circumferentially between the second spring and the additional spring. The additional spring is clamped between the third seat, via its first bearing face, and the fourth seat, via its second bearing face. Thus, the supports of the springs on the seats are approaching angularly when the additional spring is compressed. An additional stiffness increase can thus be obtained.

The third seat comprises a first pin, arranged in a notch of the first transmission plate, the ends of the notch being able to limit the displacement of the first pin thus limiting the pivoting of the third seat.

The third seat comprises a second pin, arranged in a notch of the second transmission plate, the ends of the notch being able to limit the movement of the second pin thus limiting the pivoting of the third seat.

The fourth seat comprises a first pin, arranged in a notch of the first transmission plate, the ends of the notch being able to limit the displacement of the first pin thus limiting the pivoting of the fourth seat.

The third seat comprises a second pin, arranged in a notch of the second transmission plate, the ends of the notch being able to limit the movement of the second pin thus limiting the pivoting of the fourth seat.

Preferred embodiments of the invention will now be described with reference to the accompanying drawings in which:

FIGS. 1 and 2 are schematic diagrams illustrating the operating principle of the invention,

FIG. 3 is an exploded view of a first embodiment;

FIG. 4 is a perspective view of the first embodiment;

FIG. 5 is a perspective view of the first embodiment in which a guide ring of the second rotating element is not shown;

- Figures 6 and 7 are sectional views of the first embodiment;

FIG. 8 is a graph showing three damping characteristic curves corresponding to three variant embodiments of the first embodiment;

Figures 9 and 10 are detail perspective views of a second embodiment at two distinct stages of angular deflection; - Figures 11 and 12 are perspective views illustrating a phasing member of another solution.

- Figure 13 is a perspective view of a phasing member according to a third embodiment.

FIG. 14 is a perspective view of the damping device according to the third embodiment.

Figures 1 and 2 illustrate two schematic diagrams in which a torsion damping device for a vehicle transmission chain is shown, comprising:

a first rotating element 7 for transmitting a torque;

a second rotating element 9 for transmitting the torque;

- A damping module comprising a main damper A arranged between the first rotating element 7 and the second rotating element 9, each main damper A comprising a group of springs comprising a first spring 13-1 and a second spring 13- 2 arranged in series through a phasing member 15, the first spring 13-1 and the second spring 13-2 being respectively arranged between the first rotating member 7 and the phasing member 15 and between the phasing member 15 and the second rotating element 9, the first spring 13-1 and the second spring 13-2 allowing, when they deform, a relative rotation about an axis of rotation X between the first rotating element 7 and the second element 9 turning.

The damping module comprises an additional spring 25 carried by the phasing member 15, the torsion damping device being configured so that, in a first direction of relative rotation of the first rotating element 7 relative to the second rotating element 9 from a relative angular position of rest taken by the first rotating element 7 and the second rotating element 9 without stressing speed or torque:

when the angular displacement between the first rotating element 7 and the second rotating element 9 is smaller than a first threshold A1 of angular displacement between the first rotating element 7 and the second rotating element 9, the additional spring 25 is remote from the first rotating element 7 so that no additional torque is transmissible by the additional spring 25 between the phasing member 15 and the first rotating element, and when the angular displacement between the first rotating element 7 and the second rotating element 9 is greater than or equal to the first angular displacement threshold A1, the additional spring bears directly or indirectly against the first rotary element 7 so that a torque additional can be transmitted by the additional spring 25 between the phasing member 15 and the first rotating element 7.

The torsion damping device is arranged such that each second spring 13-2 stops compressing when the angular displacement between the first rotating element 7 and the second rotating element 9 is greater than or equal to a second threshold A2 of angular displacement. between the first rotating element 7 and the second rotating element 9 in the first direction of relative rotation of the first rotating element 7 relative to the second rotating element 9, from the relative angular position of rest.

To do this, the torsion damping device as schematized comprises a first abutment bl carried by the phasing member 15 and arranged to cooperate with a second abutment b2 carried by the second rotating element 9 when the angular movement between the first rotating element 7 and the second rotating element 9 is greater than or equal to a second threshold A2 of angular displacement between the first rotating element 7 and the second rotating element 9 in the first relative direction of rotation, from the relative angular position of rest.

The torsion damping device also has an angular position of maximum angular displacement when the angular displacement between the first rotating element 7 and the second rotating element 9 reaches a third threshold A3 of angular displacement between the first rotating element 7 and the second element. rotating 9 in the first direction of relative rotation, from the relative angular position of rest. In other words, there is no more damping of the torque when the transmitted torque is greater than the torque generating an angular displacement equal to the third threshold A3.

To do this, the torsion damping device as schematized comprises a third abutment b3 carried by the first rotating element 7 and arranged to cooperate with a fourth abutment b4 carried by the second rotating element 9 when the angular deflection between the first element 7 and the second rotating element 9 reaches the third threshold A3 of angular displacement between the first rotating element 7 and the second rotating elements 9 in the first direction of relative rotation, from the relative angular position of rest.

In FIG. 1, the torque input element of the damping device is the first rotating element 7 and the torque output element of the damping device is the second rotating element 9.

In FIG. 2, the torque input element of the damping device is the second rotating element 9 and the torque output element of the damping device is the first rotating element 7.

As can be seen in FIGS. 1 and 2, the first angular deflection threshold Al is reached when the angular displacement between the first rotary element 7 and the phasing member 15 has reached a threshold AG and the second angular displacement threshold A2 is reached when the angular displacement between the phasing member 15 and the second rotating element has reached a threshold A2 '.

In the description and the claims, the terms "external" and "internal" as well as the "axial" and "radial" orientations are used to designate, according to the definitions given in the description, elements of the damping device. The X axis of rotation determines the "axial" orientation. The "radial" orientation is directed orthogonal to the X axis. The "circumferential" orientation is directed orthogonal to the X axis of rotation and orthogonal to the radial direction. The terms "external" and "internal" are used to define the relative position of one component relative to another, with reference to the axis X of rotation, a component close to said axis is thus described as internal as opposed to an external component located radially at the periphery. Moreover, the angles and angular sectors expressed are defined in relation to the axis of rotation X.

Figures 3 to 7 show a first embodiment of a torsion damping device as shown schematically in Figure 1.

This torsion damping device is coupled to a friction disk 2 of a torque limiter intended, in normal operation, to transmit a torque by turning about an axis X and to limit this torque to a certain value. The friction disc 2 comprises a support disk on either side of which two friction linings 3 are fixed by means of a first set of rivets 4. The friction disc 2 is fixed by a second set of rivets 6 to a first rotary torque transmission member which is constituted by a disk referred to as "sail" 7.

In the transmission system, as shown in FIGS. 6 and 7, the friction disk 2 coupled to the damping device is part of a torque limiter, the lining 3 of the friction disk being pressed by means of a pressure disc 86 resiliently loaded by means of a spring such as a Belleville washer 87, against a support disc 88 mounted integral with a flywheel.

A hub 5 is fixed by a third set of rivets 8 to the second rotating torque transmission member which is constituted by a pair of discs called "guide rings" 9a, 9b. A first guide ring 9a is fixed against one side of the hub 5 while a second guide ring 9b is fixed against an opposite side of the hub 5. The two guide washers 9a and 9b axially hold the first spring and the second spring each group of springs, and the web 7 is arranged axially between the two guide rings 9a and 9b.

The hub 5 has internal splines adapted to cooperate with external splines of a transmission shaft.

Two torsion damping modules M1 and M2 interposed between the web 7 and the guide washers 9a, 9b so that the web 7 on the one hand, and the guide washers 9, 10 on the other hand, can rotate. relative to each other by compressing the two damping modules M1 and M2.

In operation, the flywheel rotates the friction disk 2 and thus the web 7 which is secured thereto. The web 7 compresses the damping modules which transmit the torque to the guide washers 9a, 9b and thus to the hub 5 which is integral therewith. By transmitting the torque between the web 7 and the guide washers 9a, 9b, the damping modules filter the passage of the acyclisms and other undesirable twisting movements.

In each damping module, the additional spring 25 is a helical spring comprising:

a first bearing face 25a arranged to bear directly or indirectly against the phasing member 25, and a second bearing surface 25b able to bear directly or indirectly against a first actuating surface 40 of the web 7 when the angular displacement between the web 7 and the guide washers 9a, 9b is greater than or equal to the first threshold Al of angular displacement, in the first direction of relative rotation.

Each damping module comprises a pair of transmission plates 17a and 17b carried by the phasing member 15, each pair of transmission plates comprising a first transmission plate 17a and a second transmission plate 17b axially spaced apart by report to the other.

Each transmission plate comprises a first thrust zone P1 cooperating directly or indirectly with a first end 13-11 of the first spring 13-1 and a second thrust zone P2 cooperating directly or indirectly with a first end 13-21 of the second spring 13 -2, said first thrust zones of each pair of plates being axially spaced from each other and said second thrust zones of each pair of plates being axially spaced from each other. Thus, the transmission of the torque between the phasing member and each group of springs is directly or indirectly on the lateral areas of the faces of the first ends of the first and second springs 13-1 and 13-2. The thrust areas of the plates are thus arranged axially on either side of the geometric centers of the faces of the first ends of the first and second springs 13-1 and 13-2. It is thus possible to vary and in particular enlarge the spring thrust polygon as a function of the spacing between the first plate and the second plate and thereby improve the stability of the torque transfer by the phasing member.

The first transmission plate 17a and the second transmission plate 17b of each pair of transmission plates are respectively formed on a first phasing washer 15a and a second phasing washer 15b axially spaced from each other. The two phasing washers l5a and l5b are fixed to each other by means of spacers 16, each spacer 16 having a first end crimped onto one of the phasing washers and a second end crimped on the other phasing washers.

The two phasing washers 15a and 15b are arranged on either side of the web 7 and the two guide washers 9a and 9b are arranged axially on either side of the two phasing washers 15a and 15b.

Each damping module Ml, M2 comprises a transmission head 17 interposed, directly or indirectly, between the first spring 13-1 and the second spring 13. 2 of the spring group of the damping module. Each transmission head 17 comprises a housing L inside which is housed the additional spring 25 of the damping module.

Each pair of transmission plates 17a, 17b form a transmission head 17 of the phasing member 15, the first transmission plate 17a and the second transmission plate 17b of each pair of transmission plates each comprising a recess 47a, 47b, the recess 47a of the first transmission plate 17a and the recess 47b of the second transmission plate 17b are arranged axially facing each other so as to house the additional spring. 25 damping modulus Ml, M2 corresponding.

The first bearing surface 25a of each additional spring 25 is arranged to bear directly or indirectly against a first circumferential edge 47al of the recess 47 of the first transmission plate 17a and a first circumferential edge 47b 1 of the recess 47b. second transmission plate 17b.

Each transmission head 17 further comprises two axial retention elements 18a, 18b, arranged axially on either side of the additional spring 25 associated with the transmission head, for axially retaining the additional spring 25.

Each axial retention element 18a, 18b of the additional spring is formed by a retaining tab 18a, 18b folded in a direction having a radial component, the retaining tab 18a, 18b being formed in one of the first 17a and second 17b plate. transmission of said transmission head. The phasing member 15 thus also provides axial guidance of each additional spring 25.

Each axial retaining lug 18a, 18b projects with a radial component from a lower radial edge of the recess 47a, 47b of the first 17a or second 17b transmission plate having said retaining tab 18a, 18b. In other words, the contour of the retaining lug 18a, 18b defines a portion of the contour of the recess 47a, 47b prior to folding of the retaining tab 18a, 18b.

Each transmission plate 17a, 17b comprises a first radial holding member 19a, 19b arranged to radially maintain the first spring 13-1 associated with the centrifugal forces and a second radial holding member 20a, 20b arranged to hold radially the second spring 13-2 associated vis-à-vis the centrifugal forces.

In particular, the first radial retaining element 19a, 19b and the second radial retaining element 20a, 20b of each transmission plate are arranged in the extension circumferential of the additional spring 25 associated, circumferentially on either side of the additional spring associated 25.

Each first radial retaining element 19a, 19b is formed by a first finger extending circumferentially, radially outside the first spring 13-1. Each second radial retaining element 20a, 20b is formed by a second finger extending circumferentially, radially outside the second spring 13-2.

On each plate 17a, 17b, the first finger 19a, 19b protrudes and extends circumferentially from an outer radial end of the first thrust zone P1. On each plate, the second finger 20a, 20b protrudes and extends circumferentially in a direction opposite the first finger from an outer radial end of the second thrust zone P2.

According to one embodiment, each additional spring 25 is arranged circumferentially between the first spring and the second spring of the associated damping module. The volume of the first and second springs 13-1 and 13-2 of each damping module Ml, M2 is part of a torus and at least a part of the additional spring 25 associated is also in this torus. Thus, it is possible to provide a radially compact damping device.

The first spring 13-1 and the second spring 13-2 of the damping module M 1 extend respectively along a first axis and a second axis, the first axis and the second axis being substantially in a plan of implantation perpendicular to the axis of rotation X, and the additional spring 25 of the damping module M1 extends along a third axis also being substantially in this implantation plane. Thus, it is possible to provide a compact damping device axially. The axes of the springs of the second damping module M2 are substantially part of the same layout plan.

Each additional spring 25 has, in a plane perpendicular to the axis X, a first inner corner 253 facing the first spring of the module associated with said additional spring and a second inner corner 252 facing the second spring of the damping module associated with said additional spring, the first inner corner and the second inner corner being arranged, in this plane, circumferentially between the first end 13-11 of the first spring 13-1 and the first end 13-21 of the second spring 13-2 which cooperate with the phasing member 15. As seen in FIGS. 3 and 5, each phasing washer 15a, 15b has an annular portion and each plate 17a, 17b is connected to the annular portion of the phasing washer 15a, 15b by a radial arm.

The first thrust zone of each plate is formed by a first wall Pl of said plate and the second thrust zone of each plate is formed by a second wall P2 of said plate. These walls correspond to edge portions of the first 17a and second 17b transmission plates. The inclination of the first wall P1 and the inclination of the second wall P2 of the same plate are such that, in a plane perpendicular to the axis X passing through the first wall P1 and the second wall P2, the straight line d intersection of the first wall P1 with said plane intersects the intersection line of the second wall P2 with said plane between the associated additional spring 25 and the axis of rotation X.

The sail 7 comprises for each group of springs a main opening 71 adapted to accommodate both the first spring 13-1 and the second spring 13-2. In addition, the web 7 comprises for each damping module M1, M2 a cavity 72 able to allow a circumferential displacement of the additional spring 25 with respect to the web 7. The first actuating surface 40 forms one of the circumferential ends of this cavity 72. The main opening 71 and the cavity 72 associated with the same damping module Ml, M2 are here formed in the same window of the web 7.

The web 7 has a first bearing surface 74 arranged to cooperate with a second end 13-12 of the first spring 13-1 opposite the first end 13-11 of the first spring 13-1 and a second bearing surface 73 arranged to cooperate with a second end 13-22 of the second spring 13-2, opposite the first end 13-21 of the second spring 13-2.

The guide washers 9a, 9b are formed in a sheet and each have for each group of springs a stamped portion 9a, 9lb arranged to partially accommodate and axially guide the first spring 13-1 and the second spring 13-2 of the group of spring.

Each guide washer 9a, 9b has for each group of springs a third bearing surface 94 arranged to cooperate with the second end 13-12 of the first spring 13-1 and a fourth bearing surface 93 arranged to cooperate with the second end 13-22 of the second spring 13-2.

Each guide washer 9a, 9b comprises, for each group of springs: a first lumen, passing a portion of the second end 13-12 of the first spring 13-1, arranged between the stamped portion and the third bearing surface 94

a second light, passing a portion of the second end 13-22 of the second spring 13-2, arranged between the stamped portion and the fourth bearing surface 93

As seen in Figure 5, the first spring 13-1 and the second spring 13-2 are arranged substantially on the same radius about the axis of rotation. In other words, they are arranged in series in the same circular trajectory.

The additional spring 25 of a damping module is disposed, at least in part, circumferentially between the first spring 13-1 and the second spring 13-2 of the damping module. The first spring 13-1 has a first central axis and the second spring 13-2 has a second central axis, the intersection of the first central axis and the second central axis being located in the space occupied by the additional spring 25.

In addition, there is a plane perpendicular to the axis of rotation passing through the first spring 13-1, the second spring 13-2, and the additional spring 25.

We also see that the phasing member comprises two annular portions of radial extension arranged radially inside the first spring 13-1 and the second spring 13-2. Each phasing washer comprises an annular portion of radial extension disposed radially inside the first spring 13-1 and the second spring 13-2.

In this first embodiment, the first angular displacement threshold A1 is approximately 40 degrees and is substantially equal to the second angular deflection threshold A2. The angular stiffness of the additional spring 25 of each damping module is greater than the angular stiffness of the first spring 13-1 and greater than the angular stiffness of the second spring 13-2. Here, the stiffness of each first spring 13-1 is about. 10 Nm / °, the stiffness of each second spring 13-2 is about. 15 Nm / ° and the stiffness of each additional spring is about 30 Nm / °.

Examples of damping curves are shown in FIG. 8. These graphs illustrate alternative embodiments before the deflection reaches the third threshold of angular deflection. In these variants, there is no stop between the first rotating element and the second rotating element. Graph 1 illustrates a variant in which the first threshold A1 is equal to the second threshold A2. Graphs 2 and 3 illustrate the damping of two other variants.

Graph 2: the second threshold A2 is greater than the first threshold Al

Graph 3: the second threshold A2 is lower than the first threshold Al

On the graphs 2 and 3, we see that it is possible, by adjusting the angular threshold of the stops, to obtain a transition damping slope.

In the first embodiment shown in FIGS. 3 to 7, the first stopper bl is made on the outer periphery of the phasing member 15, on each transmission head. The first transmission plate 17a and the second transmission plate 17b of the phasing member 15 each comprise a lug 41 forming the first stopper b1. The lugs 41 extend axially so as to each radially cover a radially outer edge of a guide ring 9a, 9b. Each lug 41 is formed radially above the additional spring 25.

On each transmission plate 17a, 17b, a lip 159 curved towards the lug 41 connects the lug 41 to a radially outer edge of the recess 47a, 47b of the transmission plate 17a, 17b. This lip 159 stiffens the plate radially outside the recess.

The second stop b2 is formed on the outer periphery of the two guide washers 9a, 9b. The second stop b2 is formed by first teeth 42 extending radially outwardly of the guide rings 9a, 9b.

The torsion damping device also comprises a third stop b3 carried by the web 7 and arranged to cooperate with a fourth stop b4 carried by the second guide ring 9b when the angular displacement between the web 7 and the second guide ring 9b reaches the third threshold A3 of angular displacement in the first direction of relative rotation, from the relative angular position of rest. The third abutment b3 is formed on the outer periphery of the veil 7. The third stop b3 is formed by two hooks 43 each having an end zone extending substantially axially, this end zone being able to move circumferentially, radially. outside an outer radial edge of the second guide ring 9b. The third abutment b3 is made circumferentially between two main openings 71 of the veil 7.

The fourth stop b4 is formed on the outer periphery of the second guide ring 9b. The fourth stop b4 is formed by two second teeth 44 extending radially outwardly of the second guide ring 9b.

The operating principle described above works as well in a so-called direct transmission direction, that is to say for a torque path from the motor to the vehicle gearbox, or the torque input element. to the torque output member of the damping device, or in a so-called retro transmission direction, that is to say for a torque path from the gearbox to the vehicle engine, or torque output member to the torque input member of the damping device.

Thus, the torsion damping device is configured so that, in a second relative direction of rotation of the web 7 relative to the guide washers 9a, 9b, opposite the first direction of relative rotation, from a relative angular position of rest taken by the web 7 and the second rotating element 9 without biasing speed or torque, when the angular displacement between the web 7 and the guide washers 9a, 9b is less than a fourth threshold A4 of angular displacement between the web 7 and the guide washers 9a, 9b, each additional spring 25 is remote from the web 7. Thus, no additional spring 25 transmits torque between the phasing member 15 and the web 7 when the angular displacement between the web 7 and the washers 9a, 9b is less than the fourth angular deflection threshold A4.

When the angular displacement between the web 7 and the guide washers 9a, 9b is greater than or equal to the fourth angular displacement threshold A4, each additional spring 25 bears directly or indirectly against the web 7 so that an additional torque can be transmitted by each additional spring 25 between the phasing member 15 and the web 7.

The torsion damping device is arranged so that the second spring 13-2 ceases to compress when the angular displacement between the web 7 and the second rotating element 9 is greater than or equal to a fifth threshold A5 of angular displacement between the web 7 and the guide washers 9a, 9b in the second direction of relative rotation, from the relative angular position of rest. Thus, the deactivation of the second spring 13-2 makes it possible to increase the stiffness of the damping device beyond the fifth predetermined threshold of angular deflection A5, in this second direction of relative rotation. A fifth stop b5 carried by the phasing member 15 is arranged to cooperate with a sixth abutment b6 carried by the guide washers 9a, 9b when the angular displacement in the second direction of relative rotation reaches the fifth clearance threshold A5.

The fifth abutment b5 is also formed on the lugs 41 forming the first abutment bl. The first stop b1 and the fifth stop b5 are formed on the two circumferentially opposite edges of the lugs 41.

The sixth abutment b6 is formed on the second teeth 44 also forming the fourth abutment b4. The fourth stop b4 and the sixth abutment b6 are formed on the two circumferentially opposite edges of the second teeth 44.

Thus, bringing the fifth abutment b5 and the sixth abutment b6 into contact makes it possible to stop the compression of the second spring 13-2 by transmitting a torque directly between the fifth abutment b5 of the phasing member 15 and the sixth abutment b6. guide washers 9a, 9b so as to increase the stiffness of the damping device.

The torsion damping device has an angular position of maximum angular displacement when the angular displacement between the web 7 and the guide washers 9a, 9b reaches a sixth threshold A6 of angular displacement between the web 7 and the guide washers 9a, 9b in the second direction of rotation, from the relative angular position of rest. In other words, there is no more damping of the torque for a torque greater than the torque generating an angular displacement equal to the sixth threshold A6.

The sixth threshold A6 can be obtained by means of stops and / or can correspond to a maximum compression of the springs.

The torsion damping device comprises a seventh stop b7 carried by the web 7 and arranged to cooperate with an eighth stop b8 carried by the second guide ring 9b when the angular displacement between the web 7 and the second rotating element 9 reaches the sixth threshold A6 of angular displacement between the web 7 and the guide washers 9a, 9b in the second direction of rotation, from the relative angular position of rest.

The seventh abutment b7 is formed on the hooks 43 also forming the third abutment b3. The seventh abutment b7 and the third abutment b3 are formed on the two circumferentially opposite slices of the hooks 43. The eighth stop b8 is formed on the first teeth 42 also forming the second stop b2.

The second bearing surface 25b of each additional spring 25 is arranged to bear directly or indirectly against a first circumferential edge 47 a2, 47b2 of the recesses 47a and 47b of the first transmission plate 17a and the associated second transmission plate 17b. to said additional spring 25.

The first bearing surface 25a is adapted to bear directly or indirectly against a second actuating surface 48 of the web 7 when the angular displacement between the web 7 and the guide washers 9a and 9b is greater than or equal to the fourth threshold. A4 angular deflection, in the second direction of relative rotation.

The first bearing surface 25a of each additional spring 25 is also arranged to bear directly or indirectly against a second circumferential edge 47a1, 47b1 opposed to the first circumferential edge 47a2, 47b2 of the recesses 47a, 47b of the first transmission plate 17a and of the second transmission plate 17b associated with said additional spring 25.

If desired, the additional spring 25 is mounted fitted or tightened between firstly the first circumferential edges 47a2, 47b2 of the recesses of the first and second transmission plates 17a and 17b and secondly their second circumferential edges 47a1. , 47b2. Each additional spring 25 can also be mounted prestressed in its housing L.

The damping device 1 also comprises a friction device F intended to dissipate the energy of the springs and to avoid oscillation phenomena. Here, the friction device F is arranged to rub only in the direction of retro transmission. Reference may be made to French patent application number 1758778 with regard to the characteristics of this friction device. Another conventional friction device is also possible.

In each damping module Ml, M2, a first support seat 77 is interposed on the one hand, between the web 7 and the first spring 13-1 and on the other hand, between the guide washers 9a, 9b and the first spring 13-1 of each damping module. Similarly, a second support seat 78 is interposed on the one hand, between the web 7 and the second spring 13-2 and on the other hand, between the guide washers 9a, 9b and the second spring 13-2. The first bearing surface 74 of the web 7 comprises a first notch 76 arranged to accommodate a pivot projecting from the first seat 77. Similarly, the second bearing surface 73 of the web 7 comprises a second notch 75 arranged to house a pivot protruding from the second seat 78. The third bearing surface 94 has a third notch 96 arranged to accommodate the pivot projecting from the first seat 77. The fourth bearing surface 93 also has a fourth notch 95 arranged to house the pivot protruding from the second seat 78.

In the second embodiment shown in Figures 9 and 10, a third support seat 79 is interposed between the phasing member 15 and the first spring 13-1 and a fourth support seat 80 is interposed between the phasing member 15 and the second spring 13-2 of each damping module.

The second support seat 78 and the fourth support seat 80 are arranged to come into contact with one another when the angular displacement between the web 7 and the guide washers 9a and 9b is greater than or equal to the second A2 threshold of angular displacement between the web 7 and the guide washers 9a, 9b in the first direction of relative rotation. In other words, the first abutment bl is formed on the fourth abutment seat 80 and the second abutment b2 is formed on the second abutment seat 78.

Each support seat 78, 80 comprises a cap arranged to retain radially the spring against which it rests, vis-à-vis the centrifugal forces. The first abutment bl is formed at one end of the cap of the fourth abutment seat 80 and the second abutment b2 is formed at one end of the cap of the second abutment seat 78.

A third embodiment is shown in Figures 13 and 14

The two axial retaining elements of each transmission head 17 are formed by blinkers 11a and 118b. The first 17a and second 17b transmission plates associated with a group of springs each include a cup 118a, 118b. To promote the realization of blinkers, two notches are made on each plate, circumferentially on either side of the plate portion intended to form the eye.

One of the circumferential edges of each eyelet 118a, 118b forms the first stopper bl of the damping device and the other circumferential edge of the eyelet forms the fifth stopper b5 of the damping device. Thus, each eyelet 118a, 118b is arranged to bear against a first tooth 142 forming the second stop b2 of the guide ring 9b when the angular displacement between the web 7 and the guide washers is greater than or equal to the second threshold A2 angular deflection in the first direction of relative rotation.

In retro, each eyelet 118a, 118b is arranged to bear against a second tooth 144 forming the sixth stop b6 of the guide ring 9b when the angular displacement between the web 7 and the guide washers is greater than or equal to the fifth threshold A5 angular displacement in the second direction of relative rotation.

The guide washers 9a and 9b comprise for each damping module, a notch E4 extending between their first tooth 142 and their second tooth 144 to allow the movement of the blinkers 118a and 118b.

Each transmission plate 17a, 17b also comprises a first centering member 65a, 65b arranged inside the first end 13-11 of the first spring 13-1 and a second centering member 66a, 66b arranged inside the the first end 13-21 of the second spring 13-2.

Each centering member 65a, 65b, 66a, 66b is a tongue formed in the plate of the plate and curved in the shape of C.

The tabs forming the first centering member 65a of the first transmission plate 17a and the tabs forming the first centering member 65b of the second transmission plate 17b are each arranged axially in facing relation to form a centering tube 67 from the first spring. Similarly, the tongue forming the second centering member 66a of the first transmission plate 17a and the tongue forming the second centering member 66b of the second transmission plate 17b are arranged axially vis-à-vis to form a transmission tube. centering 68 of the second spring 13-2.

Another solution is shown in FIGS. 11 and 12. Here, the third support seat 179 and the fourth support seat 180 are pivotally mounted on the phasing member 115 around the same pivoting shaft 116.

Thus, the inclination of the third seat 179 and the fourth seat 180 may change as a function of the torque transmitted by the damping device and as a function of the centrifugal forces. The third support seat 179 and the fourth support seat 180 are mounted pivoting about the spacer 116 connecting the two phasing washers l5a and l5b, G spacer 116 forming the pivoting axis of the seats.

The third seat 179 and the fourth seat 180 each comprise a piercing lug 192 axially overlapping so that their drilling also overlaps, the pivoting shaft 116 being introduced both into the piercing of the connecting lug 192 of the third seat 179 and in the drilling of the connecting lug 192 of the fourth seat 180.

The third seat 179 and the fourth seat 180 each comprise a dorsal support surface cooperating with the additional spring 25. These bearing faces are formed in notches 193 and 195 of the third seat 179 and the fourth seat 180. The third seat 179 is interspersed circumferentially between the first spring 13-1 and the additional spring 25 and the fourth seat 180 is interposed circumferentially between the second spring 13-2 and the additional spring 25.

In other words, the additional spring 25 is clamped between the third seat 179, via its first bearing face 25a, and the fourth seat 180, via its second bearing face 25b. An additional increase in stiffness can thus be obtained by pivoting the seats. Here we have the first spring, the second spring and the additional spring arranged in series with a delayed compression of the additional spring.

The third seat 179 comprises a first pin 81, arranged in a notch 197 of the first transmission plate 117a, the ends of the notch being 197 able to limit the movement of the first pin 81 thus limiting the pivoting of the third seat 179. The third seat also comprises a second pin 82, arranged in a notch of the second transmission plate 11b, the ends of the notch being able to limit the movement of the second pin 82, thus limiting the pivoting of the third seat.

The fourth seat also comprises a first pin 81, arranged in a notch 198 of the first transmission plate 117a, the ends of the notch being able to limit the displacement of the first pin 81 thus limiting the pivoting of the fourth seat 180. fourth seat 180 also comprises a second pin 82, arranged in a notch of the second transmission plate 117b, the ends of the notch being able to limit the displacement of the second pin thus limiting the pivoting of the fourth seat 180.

Claims

A torsion damping device for a vehicle transmission chain, comprising:

- a first rotating element (7) for transmitting a torque;

a second rotating element (9) for transmitting the torque;

at least one damping module (Ml, M2) comprising a main damper (A) arranged between the first rotating element (7) and the second rotating element (9), each main damper comprising a group of springs comprising a first spring (13-1) and a second spring (13-2) arranged in series via a phasing member (15), the first spring (13-1) and the second spring (13-2) being arranged respectively between the first rotating element (7) and the phasing member (15) and between the phasing member (15) and the second rotating element (9), the first spring (13-1) and the second spring ( 13-2) allowing, when deformed, a relative rotation about an axis of rotation (X) between the first rotating element (7) and the second (9) rotating element; characterized in that each damping module (Ml, M2) comprises an additional spring (25) carried by the phasing member (15), the torsion damping device being configured so that, in a first sense of relative rotation of the first rotating element (7) relative to the second rotating element (9) from a relative angular rest position taken by the first rotating element (7) and the second rotating element (9) without speed or torque biasing:

when the angular displacement between the first rotating element (7) and the second rotating element (9) is smaller than a first threshold (Al) of angular displacement between the first rotating element (7) and the second rotating element (9), the additional spring (25) is remote from the first rotating element (7) so that no additional torque is transmissible by the additional spring (25) between the phasing member (15) and the first rotating element (7) , and

when the angular displacement between the first rotating element (7) and the second rotating element (9) is greater than or equal to the first threshold (A1) of angular displacement, the additional spring (25) bears directly or indirectly against the first rotating element (7) so that an additional torque can be transmitted by the additional spring (25) between the phasing member (15) and the first rotating element (7).

The torsion damping device according to claim 1 wherein each additional spring (25) is a helical spring comprising:

a first bearing face (25a) arranged to bear directly or indirectly against the phasing member (25), and

a second bearing face (25b) able to bear directly or indirectly against a first actuating surface (40) of the first rotating element (7) when the angular displacement between the first rotating element (7) and the second rotating elements (9) is greater than or equal to the first threshold (A1) of angular displacement in the first direction of relative rotation.

A torsion damping device according to one of the preceding claims wherein the torsion damping device is arranged such that each second spring (13-2) ceases to compress when the angular displacement between the first rotating member (7) and the second rotating element (9) is greater than or equal to a second threshold (A2) of angular displacement between the first rotating element (7) and the second rotating element (9) in the first direction of relative rotation, since the relative angular position of rest.

4. torsion damping device according to the preceding claim wherein the torsion damping device comprises a first stop (bl) carried by the phasing member (15) and arranged to cooperate with a second stop (b2) scope by the second rotating element (9) when the angular displacement between the first rotating element (7) and the second rotating element (9) is greater than or equal to a second threshold (A2) of angular displacement between the first rotating element (7) and the second rotating element (9) in the first direction of relative rotation, from the relative angular position of rest.

5. damping device according to one of the preceding claims wherein one of the first rotating element (7) and the second rotating element (9) is formed by two guide washers (9a, 9b) which axially maintain the first spring (13-1) and the second spring (13-2) of each group of springs; and the other of the first rotating element (7) and the second rotating element (9) is formed by a web (7) arranged axially between the two guide washers (9a, 9b).

6. damping device according to one of the preceding claims wherein the additional spring (25) of a damping module (Ml, M2) is disposed, at least in part, circumferentially between the first spring (13-1 ) and the second spring (13-2) of this damping module.

7. A damping device according to one of the preceding claims wherein the phasing member comprises an annular portion of radial extension disposed radially inside the first spring (13-1) and the second spring (13-2). ).

8. damping device according to one of the preceding claims wherein each damping module (Ml, M2) comprises at least one pair of transmission plates (17a, 17b) carried by the phasing member, each pair of transmission plates comprising a first transmission plate (17a) and a second transmission plate (17b) axially spaced apart from each other; the first (17a) and second (17b) transmission plates each comprising a first thrust zone (P1) cooperating directly or indirectly with a first end (13-11) of the first spring (13-1) and a second thrust zone (P2) cooperating directly or indirectly with a first end (13-21) of the second spring (13-2), said first thrust zones of each pair of plates being axially spaced from each other and said second zones of pushing each pair of plates axially spaced from each other.

9. damping device according to the preceding claim wherein the first transmission plate (17a) and the second transmission plate (17b) of each pair of transmission plates are formed respectively on a first phasing washer (15a) and a second phasing washer (15b) spaced axially from each other.

10. damping device according to one of the preceding claims wherein each damping module (Ml, M2) comprises a transmission head (17) carried by the phasing member (15) and arranged circumferentially between the first spring (13-1) and the second spring (13-2) of the spring unit of the damping module, each transmission head (17) having a housing (L) inside which is housed the additional spring (25) of the damping module so as to transmit an additional torque between the phasing member (15) and the first rotating element (7) when the angular displacement between the first rotating element (7) and the second rotating element (9) is greater than or equal to the first threshold (A1) of angular displacement in the first direction of relative rotation.

11. damping device according to claim 10 combined with one of claims 8 to 9 wherein, for each damping module (Ml, M2), the transmission head (17) is formed by the pair of plates of transmission (17a, 17b), the first transmission plate (17a) and the second transmission plate (17b) each comprising a recess (47a, 47b), the recess (47a) of the first transmission plate (17a) and the recess (47b) of the second transmission plate (17b) being arranged axially facing one another so as to accommodate the additional spring (25) of the corresponding damping module.

12. damping device according to one of claims 10 to 11 wherein each transmission head (17) further comprises two axial retaining elements (l8a, l8b) of the associated additional spring (25), the two retaining elements axial (18a, 18b) of the additional spring (25) being arranged axially on either side of the additional spring (25).

13. damping device according to one of the preceding claims wherein the torsion damping device is configured so that in a second direction of relative rotation of the first rotating member (7) relative to the second rotating member (9). ), opposite to the first direction of relative rotation, from a relative angular position of rest taken by the first rotating element (7) and the second rotating element (9) without stressing speed or torque:

each additional spring (25) is remote from the first rotating element (7) when the angular displacement between the first rotating element (7) and the second rotating element (9) is less than a fourth threshold (A4) of angular displacement between the first rotating element (7) and the second rotating element (9), and each additional spring bears directly or indirectly against the first rotating element (7) when the angular displacement between the first rotating element (7) and the second rotating element (9) is greater than or equal to the fourth angular displacement threshold (A4), so that an additional torque can be transmitted by each additional spring (25) between the phasing member (15) and the first rotating element (7). ).

A torsion damping device according to claims 4, 8 and 13 in which the torsion damping device is arranged so that the second spring (13-2) ceases to compress when the angular displacement between the first element rotating (7) and the second rotating element (9) is greater than or equal to a fifth threshold (A5) of angular displacement between the first rotating element (7) and the second rotating element (9) in the second relative direction of rotation, from the relative angular position resting, a fifth stop (b5) being carried by the phasing member (15) and being arranged to cooperate with a sixth stop (b6) carried by the second rotating element (9) when the angular displacement between the first rotating element (7) and the second rotating element (9) in the second relative rotational direction reaches the fifth deflection threshold (A5), the first transmission plate (17a) and / or the second transmission plate (17b) of the phasing member (15) comprising a lug (41) forming the first stop (bl), and the fifth stop (b5) being also formed on this lug (41).

15. A transmission system comprising a torque limiter comprising a friction disk and a damping device according to one of the preceding claims, the friction disk being mounted integral in rotation with one of the first rotating element (7). and the second rotating element (9, 10) of the damping device.