Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
  • F16F15/123—Wound springs
  • F16F15/1238—Wound springs with pre-damper, i.e. additional set of springs between flange of main damper and hub

Definitions

• the present invention relates to a torsion damping device of the type used for example for the constitution of a clutch f riction for a motor vehicle.
• the invention thus relates to a device said to have at least two damping stages of the type comprising at least a first damper r, radially exterior, and a second damper, radially interior, which come into action during an angular movement between two coaxial rotating elements comprising a radially inner, outlet, in particular hub-shaped element and a radially outer, inlet element, each damper comprising two front and rear guide washers arranged axially on either side of a web and comprising elastic members with a concerential action acting between the two guide washers and the web which they frame, of the type in which the web of the second damper is linked in rotation to the hub, which passes through it centrally, and is axially wedged in backward support against a radial shoulder surface of the outer periphery of the hub, and of the type in which the second he shock absorber, known as a pre-shock absorber, is located axially between the web of the first shock absorber, said main shock absorber, and the front washer of the
• the radially inner periphery of the web of the central pre-damper is wedged axially towards the rear on the stepped groove hub by an axial crimping operation, from front to back during which the metal from the part is axially pushed back. front axial end of the hub.
• the invention relates to a device of the type mentioned above, characterized in that the centering bearing comprises at least one holding element which extends axially towards the rear and whose free end edge extends opposite a radially inner portion facing the web of the second damper to axially wedge the latter in abutment against the shoulder surface.
• the centering bearing comprises at least one holding element which extends axially towards the rear and whose free end edge extends opposite a radially inner portion facing the web of the second damper to axially wedge the latter in abutment against the shoulder surface.
• the holding element is in axial abutment against the portion facing the web of the second damper to cancel the axial clearances
• the holding element is in elastic axial support against the portion facing the web of the second damper; -
• the holding element comprises at least one elastically deformable part, in particular to make up for manufacturing tolerances;
• the holding element is connected to the body of the bearing by an elastically deformable connecting part easily obtained by molding, the bearing being conventionally made of moldable material;
• the centering bearing comprises a transverse flange that extends radially outward between the front washers of the first and second dampers, and the holding element is located radially inside with respect to the flange;
• the holding element extends axially rearward from the average transverse plane in which the flange extends; -
• the holding element is an annular cylindrical crown;
• the holding element is a holding finger
• Each retaining finger extends axially between two consecutive stepped grooves formed at the grooved periphery of the hub;
• the centering bearing comprises a series of holding fingers distributed angularly in a regular manner
• Each damper comprises friction means which, acting between the guide washers and the web, are subjected to elastic means with axial action;
• the second shock absorber placed directly upstream of the output element is a pre-shock absorber while the first shock absorber is a main shock absorber placed directly downstream of the input element, and the device comprises a third intermediate shock absorber placed kinematically between the first and second shock absorbers and of the same overall design as the latter;
• the holding element is produced integrally by molding, in particular plastic, with the centering bearing.
• - F igure 1 is a view in axial section of a first embodiment of a torsion damper device comprising three torsion dampers in series and which is produced in accordance with the teachings of the invention;
• FIG. 2 is a view on a larger scale of the central part of Figure 1 on which there is shown an alternative embodiment of the retaining elements of the veil to wedge it axially towards the rear which urge it elastically towards the rear ;
• - Figure 3 is an axially exploded view of three of the components of Figure 2;
• the torsional damping device 1 0 generally comprises, between an input element 1 1 and an output element 1 2 mounted to rotate relative to each other, three dampers A, B, C, which, kinematically, enter successively in action during an angular movement between the input element 1 1 and the output element 1 2, namely, in the reverse order of their inputs in action, a main damper A, an intermediate damper B , and a pre-damper C.
• the input element 1 1 comprises a disk 1 3 which conventionally bears by riveting or gluing, annularly, on its periphery and on one and the 'other of its faces, friction linings 1 4.
• the disk 1 3 is conventionally axially elastic.
• the output element 12 is a hub which, internally, has grooves 1 5 and which, externally, comprises, at one of its ends, a portion of reduced height 1 6 and, at the other of its ends, a frustoconical bearing 1 7 with, in the meantime, grooves 1 8 extending in excess thickness.
• the axial axis of symmetry of the hub 12 constitutes the axial axis of symmetry and rotation of the torsion damping device.
• the outlet element 12 On the side of the reduced height portion 1 6, the outlet element 12 has a transverse shoulder 1 9 with which the corresponding end edge of the grooves 1 8 is in continuity.
• Each of the shock absorbers A, B, C has two front and rear guide washers, respectively 20A-21 A, 20B-21 B, 20C-21 C which, arranged axially on either side of a web, respectively 22A, 22B, 22C, are mounted rotatable relative to the latter within the limits of a determined angular movement, of the elastic members with circumferential action, respectively 23A , 23B, 23C, which are circumferentially interposed between the guide washers 20A-21 A, 20B-21 B, 20C-21 C and the web 22A, 22B, 22C, and friction means with axial action, respectively 25A, 25B , 25C which, intervening between the guide washers 20A-21 A, 20B-21 B, 20C-21 C and the web 22A, 22B, 22C or parts integral in rotation thereof, are subjected to elastic means to axial action, respectively 26A, 26B, 26C.
• the front guide washers 20A and rear 21 A of the main damper A are secured to one another, and are kept at a determined distance from each other, by spacers 27, which intervene from place to place, at their periphery, and with the aid of which the disc 1 3 carrying the friction linings 14 is secured to the front guide washer 20A.
• the spacers 27 here consist of balusters.
• spacers 27 pass through, with a circumferential clearance, notches 28 provided for this purpose at the external periphery of the web 22A and, by cooperation in abutment with the ends of the notches 28, they define the limits of the angular movement of the guide washers 20A, 21 A relative to the web 22A.
• the spacers surround the web 22A and the travel is determined by coming into contiguous turns of the members 23A.
• the web 22A also includes notches 29 by which it meshes, with a circumferential clearance, with the grooves 1 8 of the outlet element 1 2.
• the elastic circumferential members 23A of the main damper A are installed partly in windows 30 of the guide washers 20A, 21 A and, partly in windows 31, facing each other, of the web 22A.
• the elastic members 23A, 23B, 23C are mounted in housings made opposite one another in the guide washers and the webs. These accommodations consist of windows. As a variant, these are open stamps or open cut-outs or recesses.
• the members 23A here each consist of two coaxial helical springs elongated substantially tangentially to a circumference of the assembly for increasing the torque transmission.
• the intermediate damper B and the pre-damper C are both axially arranged on the same front side of the web 22A of the main damper A, between this web 22A and here the front guide washer 20A, in variant between the web 22A and the rear guide washer 20B.
• the intermediate damper B which generally surrounds the pre-damper C, is located radially for the most part below, that is to say below, the elastic members with circumferential action 23A of the main damper A.
• Its rear guide washer 21 B is formed by the web 22A of the main damper A and, more precisely, by the radially innermost portion of this web 22A.
• Its front guide washer 20B is a plastic part, or confinement piece, arranged axially in frictional contact with the front guide washer 20A of the main damper A.
• This front guide washer 20B which is the washer of guiding the intermediate shock absorber B furthest axially from the web 22A from the main shock absorber A, has axially rearwardly studs 33 by which it is locked in rotation on this sail 22A, these studs 33 being engaged with notches 34 provided for this purpose at the edge of the windows 31 of this veil 22A.
• the tenons 33 pass right through the web 22A and, shaped as elastically deformable hooks 35 beyond this web 22A, they are capable of snap-fastening thereon to form a sub-assembly.
• the veil 22B has notches 36 through which it engages, with a circumferential clearance, with the grooves 1 8 of the outlet element 1 2, but the corresponding clearance is less than that of the veil 22A of the main damper A.
• the elastic circumferential members 23B of the intermediate damper B are engaged, in part, in recesses in the form of recesses 37 in the front guide washer 20B and in windows 38 in the rear guide washer 21 B, and, in part, in windows 39, facing each other, of the veil 22B. They are here each made up of two coaxial helical springs elongated substantially tangentially to a circumference of the assembly for increasing the torque transmission.
• the limits of the angular movement between the guide washers 20B, 21 B of the intermediate damper B and the web 22B thereof are defined by the abutment of the circumferential ends of the notches 29 of the web 22A of the main damper A with the grooves 1 8 of the outlet element 1 2.
• One of the guide washers 20C, 21 C of the pre-damper C is here formed by the web 22B of the intermediate damper B and, more precisely, by the radially innermost portion of this web 22B.
• the two guide washers 20C, 21 C of the pre-damper C are secured in rotation with one another by axial lugs 40 which one of them has and which are engaged with notches 41 provided in correspondence on the other.
• the guide washer having these axial tabs 40 is the rear guide washer 21 C axially closest to the web 22A of the main damper A, and the notches 41 are provided at the outer periphery of the front guide washer 20C .
• the axial tabs 40 therefore extend in the direction opposite to the web 22A of the main damper A.
• These axial tabs 40 are formed in favor of the windows 39 of the web 22B of the intermediate damper B, the material which constitutes being taken from that normally eliminated for the formation of these windows 39, FIG. 4.
• the web 22C of the pre-damper C is integral in rotation with the outlet element 1 2 while being engaged, at its internal periphery, over a portion of reduced height of the grooves 1 8 of this outlet element 12 so that the web 22C is axially wedged in one direction on the output element 1 2 by the transverse shoulder formed by the change in height of the grooves 1 8.
• the elastic circumferential members 23C of the pre-damper C are engaged, in part, in windows 43 of the guide washers 20C, 21 C and, in part, in windows 44, facing the web 22C.
• the friction means 25A with axial action of the main damper A comprise, in addition to the front guide washer 20B of the intermediate damper B, a friction washer 45 which, from the 'other side of the veil 22A relative to the front guide washer 20B, is in contact with the rear transverse face of this veil 22A.
• the associated axial action elastic means 26A are constituted by a Belleville washer, as a variant by a wavy washer, which bears on the corresponding rear guide washer 21 A of the main damper A.
• the friction washer 45 extends substantially level with the front guide washer 20B and therefore at a distance from the outlet element 1 2.
• This friction washer 45 carries, axially, tenons 46 which, with respect to it, are offset radially in the direction opposite to the outlet element 12 and by which it is locked in rotation on the rear guide washer 21 A of the main damper A the most close, these tenons 46 being engaged with recesses 48, here holes, provided for this purpose in this rear guide washer 21 A.
• the tenons 46 pass right through the guide washer 21 A and, shaped as elastically deformable hooks 49 beyond this guide washer 21 A, they are capable of snap-fastening thereon to form a subset.
• the pins 46 are also used to center the Belleville washer constituting the elastic means with axial action 26A.
• the friction means 25C with axial action of the pre-damper C comprise on the one hand a bearing 50, which intervenes radially between the output element 12 and the front guide washer 20A of the main damper A for centering this washer guide 20A, and which, by a concave frustoconical bearing 51, bears on the frustoconical convex bearing surface 1 7 of the output element 1 2, and, on the other hand, at the other end of this output element 1 2, a friction washer
• the bearing 50 is here made of moldable plastic.
• This friction washer 52 has axially, towards the rear, pins 53 by which it is locked in rotation on the rear guide washer 21 A of the main damper A, these pins
• the associated axial action elastic means 26C are formed by a Belleville washer, as a variant a wavy washer which is centered by the pins 53 and which, by notches, is engaged with these.
• the friction washer 45 belonging to the friction means 25A of the main damper A comprises, in the direction of the axis of the assembly, a radial extension 56 suitable for retaining the washer friction 52 belonging to the friction means 25C of the pre-damper C. It is thus possible to form a sub-assembly comprising the guide washer 21 A, the washer 45 snapped onto the washer 21 A, the washer 52 resting on the radial extension of the washer 45 and the Belleville washers 26A, 26B trapped between the washer 21 A and respectively the washer 45 and the washer 52.
• the washers 45, 26A surround the washers 52, 26B.
• This radial extension 56 can be circularly continuous or be split into radial lugs.
• the axial action elastic means 26B of the intermediate shock absorber B intervene between the front guide washer 20C of the pre-shock absorber C furthest axially from the web 22A of the main shock absorber A and a retaining washer 57, with coupling means likely to intervene axially between this retaining washer 57 and the rear guide washer 21 C of the pre-damper C axially closest to the web 22A of the main damper A.
• the coupling means comprise, on the retaining washer 57, axial tabs 59 which extend axially towards the rear in direction of the web 22A of the main damper A and which, at their free end, are shaped as hooks 60 and have notches on the rear guide washer 21 C of the pre-damper C axially closest to the web 22A of the main damper A.
• These notches are each formed by the edge of an opening provided for this purpose in the axial tabs 40 of the guide washer 21 C of the pre-damper C.
• the axial tabs 40 of the guide washer 22C extend a square return of this guide washer 21 C against which the guide washer 20C is axially in abutment.
• the retaining washer 57 is in one piece with the bearing 50 and the resilient axially acting means 26B of the intermediate damper B are constituted by a Belleville washer, alternatively a wavy washer, which is centered by the pins ensuring the setting in rotation of the bearing 50 on the guide washer 20C of the pre-damper C and which, by notches, is engaged with these let's hold on.
• the washer 57 is here molded with the bearing 50, here in moldable plastic.
• the friction means 25B of the intermediate damper B are constituted by a friction washer 67 disposed axially between the web 22A of the main damper A and the web 22B of the intermediate damper B.
• This friction washer 67 meshes with play with the outlet element 1 2.
• the friction washer 67 has windows 69 in which the elastic members with circumferential action 23C of the pre-damper C are engaged axially, which allows a reduction in the axial size of the assembly.
• the friction washer 67 has, at its outer periphery, notches, in which the circumferential action elastic members 23B of the intermediate damper B are engaged axially, which allows this friction washer 67 to be returned by these elastic members with circumferential action 23B.
• the retaining washer 57 which axially closes this first sub-assembly.
• I t also includes the friction washer 52 belonging to the friction means 25C of the pre-damper C and, between this friction washer 52 and the corresponding rear guide washer 21 A of the main damper A, the elastic means with axial action 26C of the pre-damper C, the retention of the friction washer 52 being ensured by the radial extension 56 of the friction washer 45.
• it can, during assembly, be carried out as follows.
• first sub-assembly detailed above and the second sub-assembly having in common the web 22B of the intermediate damper are first assembled in isolation and then are assembled.
• the stiffness of the elastic members with circumferential action 23C of the prelock absorber r C is lower than that of the elastic members with circumferential action 23B of the intermediate damper B, and this itself is lower than that of the elastic members with circumferential action 23A of the main shock absorber A.
• 26C of the pre-damper C is weaker than that of the elastic means with axial action 26B of the intermediate damper B, and the latter is itself weaker than that of the elastic means with axial action 26A of the main damper A.
• the guide washers 20C, 21 C of this pre-shock absorber C are then integral in rotation with the guide washers 20A, 21 A of the shock absorber A on which the friction washer 52 is fixed in rotation constituting these friction means 25C and, by means of the guide washer 20C of the pre-shock absorber C, the same applies to the bearing 50.
• the elastic members with circumferential action 23B of the intermediate damper B are compressed in their turn, while the elastic members with circumferential action 23C of the pre-damper C remain compressed.
• the friction means 25B of the intermediate damper B add their effects to those of the friction means 25C of the pre-damper C.
• the friction means 25A of the main shock absorber A in turn come into action, adding their effects to the friction means 25C of the pre-shock absorber C, while the friction means 25B of the intermediate shock absorber B have no effect .
• I t also follows from the above that the three shock absorbers A, B, C are connected in series.
• their circumferential action elastic members 23A, 23B, 23C can be pre-loaded in their respective housings (windows 30, 38, 43 or recesses 37).
• the final torque of the pre-shock absorber C can then be greater than the prestressing elastic members with circumferential action 23B of the intermediate damper B, and the final torque of this intermediate damper B can then itself be greater than the prestressing of the elastic members with circumferential action 23A of the main damper A.
• the hooks 35, 49 have come from molding with the corresponding pins 33, 46, being preferably narrower circumferentially than these so as not to participate in the transmission of the torque and thus be spared.
• the rear transverse face 1 00C of the radially inner part 1 02C of the web 22C of the pre-damper C is axially wedged rearward against a transverse face of stop 104 forming a radial shoulder which s 'extends from the grooved periphery of the hub 1 2 and which is here constituted by the transverse face delimiting the two sections of the stepped grooves 1 8.
• centering bearing 50 it is proposed to use the centering bearing 50 to keep the web 22C wedged axially rearward, that is to say to the right when considering the figures.
• the centering bearing 50 comprises a series of holding elements 1 06 of generally axial orientation and each of which has a rear axial free end 108 which extends opposite the portion facing the front transverse face 1 03C of the radially inner part 1 02 C of the web 22C of the preamplifier C.
• the holding elements 1 06 are distributed angularly in a regular manner and are at most equal in number to that of the grooves of the periphery of the hub 1 2 so that each element in the form of a retaining finger 1 06 extends axially towards the rear between two consecutive grooves in relief 1 8 of the hub 1 2.
• each axial retaining finger 1 06 is produced integrally by molding with the annular body of the centering bearing 50 and it extends axially from the mean plane in which extends radially outwardly the retaining washer 57 in the form of a transverse flange of the bearing 50 which is pinched axially between the front guide washers 20A and 20 C with elastic action of the Belleville washer 26B.
• Each retaining finger 106 is here solid or solid.
• each rear free end section 108 of the fingers 106 with an elastic deformation capacity in the axial direction.
• Such a capacity can be ensured by producing each free end section 108 in an elastomeric material, for example according to the so-called co-molding technique.
• each free end section 1 08 to the axial body of the retaining finger by a recessed and thinned portion forming a tongue 1 12 which is elastically deformable by acting as a compression spring.
• the radially inner part 1 02C of the web 22C of the pre-damper C is pinched axially between the transverse shoulder face 1 04 facing forward and the front axial ends holding fingers 106 produced integrally by molding with the body of the centering bearing 50.
• the crimping operation of the web 22C is eliminated and the hub 1 2 can then advantageously be made of sintered material. It is also possible to dismantle the web 22C from the hub 1 2 by dismantling the centering bearing 50. In all cases, the stiffness of the elastic deformation capacity of the end 1 08 of the fingers 1 06 or of the tongues 1 12 is lower than the stiffness of the elastic means 26C so as not to hinder the action of the latter.
• This embodiment relates to a two-stage torsional damping device A and C of the type that is the subject of French patent application No. 94.02960. published under n ° 2 71 8 208 to the content of which we can refer.
• the rearwardly oriented drive projections 59 belong to the front guide washer 20C and they extend axially beyond the rear guide washer 21 C through indentations in the web 22A of the shock absorber main A. For axial backward setting of the pre-damper web 22C
• annular cylindrical crown 1 06 holding which is made integrally with the body of the centering bearing 50 and whose annular edge of axial end cooperates with the portion opposite the rear transverse face 1 03C of the radially internal part 1 02C of the web 22C.
• edge 1 08 of material elastically deformable or else to interpose an element forming an axial compression spring between the body of the centering bearing 50 and the annular cylindrical section of rear end which is urged to bear axially towards the rear against the front face 1 03C of the web 22C, 1 02C.
• a stud (not referenced) of the conical bearing 50 engaged in a hole in the guide washer 20A.
• the bearing 50 can be hollowed out to receive the elastic members of the pre-damper C.
• the bearing 50 therefore acts as a guide washer for the elastic members of the pre-damper which, as a variant, are of curved shape as visible in FIGS. 1 and 1 2 of document FR-A-2 728 642 to which reference will be made for more details.
• the holding element 1 06 according to the invention extends in the figures radially below the washer 57 and does not interfere with the action of the elastic washer 26C. More precisely when the retaining element 106, 108 is in elastic axial abutment against the opposite portion 1 02C, 1 03C of the web 22C, this elasticity must be less than that of the elastic means with axial action 26C. say of stiffness lower than that of the means 26C.
• the holding element 1 06 according to the invention extends on the one hand, radially below the elastic members 23C of the pre-damper C and, on the other hand, radially above the portion of reduced height of the grooves 1 8 of the hub 12.
• the holding element can penetrate into the recesses between two grooves as in FIGS. 1 to 3.
• the input element of the torsion damping device can be constituted directly by the disk 1 3 or an extension of the guide washer 20A fixed on a flywheel visible in FIG. 1 of document US-A-4,351, 1 68. In this case, no pressure plate is provided.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Acoustics & Sound (AREA)
• Aviation & Aerospace Engineering (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)

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Citations (7)

• 1998
  • 1998-12-21 FR FR9816099A patent/FR2787539B1/fr not_active Expired - Lifetime
• 1999
  • 1999-12-07 KR KR1020007009129A patent/KR20010041090A/ko not_active Application Discontinuation
  • 1999-12-07 HU HU0100667A patent/HU222138B1/hu active IP Right Grant
  • 1999-12-07 WO PCT/FR1999/003046 patent/WO2000037824A1/fr not_active Application Discontinuation
  • 1999-12-07 DE DE19982946T patent/DE19982946B3/de not_active Expired - Lifetime

Patent Citations (7)

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