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
  • F16H—GEARING
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
• • 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
• • 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
  • F16H—GEARING
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
  • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
• • 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
  • F16H—GEARING
  • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
  • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
  • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
  • F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members

Definitions

• Torsional damper in particular for locking clutch of a hydrokinetic coupling device.
• the present invention relates to a torsion damper, in particular for a locking clutch of a hydrokinetic coupling device, comprising two coaxial parts mounted so as to be angularly movable with respect to one another and a second group of elastic members mounted in series by means of a phasing washer, which has protrusions directed radially and each interposed between a first elastic member of the first group of elastic members and a second elastic member of the second group d 'elastic bodies.
• Such a damper is described in document FR-A-2 393 199 and is satisfactory because it makes it possible to increase the relative angular movement between the two coaxial parts.
• a problem arises because for good filtration of the vibrations likely to arise throughout the kinematic chain, in which the torsion damper is inserted, it may be desirable, on the one hand, to ensure throughout a first large angular movement between the two coaxial parts the transmission of an average torque and, on the other hand, to ensure at the end of the final angular movement between said parts the transmission of a large torque.
• the object of the present invention is to meet these requirements in a simple and economical manner.
• a torsion damper of the above-mentioned type in which one of the coaxial parts comprises a web with arms directed radially, while the second part comprises two guide washers arranged on either side of the arms of the veil and phasing washer, is characterized in that clearance interlocking means are provided between the arms of the veil and the phasing washer, in that a third group of elastic members with circumferential action intervenes between the guide washers and the phasing washer, and in that the third group of elastic members is located radially above, on the one hand, the first and second group of elastic members and, on the other hand, means of interlocking at play.
• the elastic members of the first and second group of elastic members intervene in series in a first phase until the sets of interlocking means with play are canceled.
• the elastic organs of the second and third group work in parallel.
• their stiffness is added.
• the stiffness of the elastic members of the third group of elastic members is greater than the stiffness of the elastic members of the first and third groups of elastic members.
• the elastic members all have the same stiffness.
• the invention is simple because it leads to housing facing each other in the guide washers and the phase washer for mounting additional elastic members.
• the engagement of the arms with the phasing washer is done flexibly because the phasing washer is connected elastically to the web and to the guide washers.
• the arms engage, after a relative angular movement between the wall and the phasing washers and therefore take up the play of the interlocking means with play, with a transverse shoulder forming a stop and belonging to a radial projection bearing a protuberance. So we add material to this place which makes the phasing washer robust.
• the arms have at their outer periphery lugs extending circumferentially projecting. These are the pins which are allowed to cooperate after taking up an angular play with the shoulders and which belong to the means of meshing with play.
• the lugs also retain the elastic members of the first and second group.
• the arms laterally have folds at 90 ° coming, after taking up a clearance, in engagement with the shoulders.
• the third elastic members in one embodiment are mounted in windows, or other housings, practiced opposite in ears and tabs which have in radial projection at their outer periphery respectively the phasing washer and the washers of guide and, according to one characteristic, at least one of the tongues belongs to an axially stamped zone for the formation of a shoulder at each of the ends of a stamped zone and therefore creation of a stop limiting the relative angular movement between the washers guide and phasing washer by engaging the ears with the stops.
• the guide washers, the web and the phasing washer are not mechanically weakened by oblong or other openings.
• the guide washers have tabs joined in radial projection at their outer periphery. These legs alternate with the tongues and the ears for the formation of tenons meshing without play with mortises formed for example in a driving piston or any other element of torque transmission of the driving or driven type. Thus a good torque transmission is obtained while having a minimum radial size for the torsion damper.
• the tabs of one of the guide washers have laterally folds generally at 90 ° for reception of the tabs of the other guide washer forming reinforcement tabs.
• the legs are joined.
• the pins are robust and allow good sliding of the driving element relative to the guide washers because the folds of smooth shape cooperate with the edges of the grooves and are not very aggressive. Thanks to the folds, the problems due to the presence of burrs in the prior art are eliminated, knowing that the torque transmission part and the guide washers are metal parts obtained by cutting and folding. Such folds can equip any torsion damper.
• the folds have a height greater than the thickness of the guide washer to increase the contact surface between the tabs and the grooves and further reduce the phenomena of incrustation and further promote sliding.
• the legs of the two washers can be fixed together by any means (riveting, welding, etc.), and the folds are deformed so that all the legs transmit the torque.
• the two guide washers can be fixed together at another location.
• the structures can be reversed, the guide washers being integral with the driving element, while the web, fixed in the above examples, can be shaped to be able to move axially.
• the folds can deform elastically and are prevented from deforming plastically because of the tabs of the other guide washer. We thus make up for the play in manufacturing tolerances, the tabs thus being engaged without play by their folds in their associated grooves forming mortises in the driving element.
• Figure 1 is a schematic view in axial section of a hydrokinetic coupling device provided with a locking clutch provided with a torsion damper according to the invention
• FIG. 2 is a view along arrow 2 of Figure 1 with local cutaway of the torsion damper;
• - Figure 3 is a view of the locking clutch of Figure 1, with the two positions of the piston;
• FIG. 4 is a partial view along arrow 4 of Figure 3;
• FIG. 5 is a view along arrow 5 of Figure 4.
• FIG. 7 shows a variant of the shape of the legs.
• a torsional damper 3 for a locking clutch 1 of a hydrokinetic coupling device In the figures is shown a torsional damper 3 for a locking clutch 1 of a hydrokinetic coupling device.
• the locking clutch 1 is intended to be mounted inside a sealed casing 100, filled with oil, of the hydrokinetic coupling device comprising, inside the casing, at least one wheel. impeller 101 and a turbine wheel 102 with blades.
• a reaction wheel 103 is also provided for forming a torque converter.
• the hydrokinetic coupling device is a starting and torque transmission member, which is interposed between a driving shaft (not visible), the crankshaft of the vehicle engine in the case of an application for a motor vehicle, and a driven shaft (not visible), the input shaft of a gearbox such as a gearbox in the case of an application for a motor vehicle as is the case in the figures.
• the casing 100 of the device constitutes the entry part of the device, while the turbine wheel 102, by means of a hub 106 which it presents, constitutes the exit part of the device.
• the casing 100 comprises two parts 104, 105 integral with one another, one of which 104 carries the blades of the impeller, and the other of which 105, known as the driving part, is shaped to be connected to the tree most often leading through a diaphragm.
• the hub 106 of the turbine wheel is internally grooved for its connection in rotation with the driven shaft.
• the casing 100 is rotated by the driving shaft and rotates the shaft driven via the turbine wheel 102 driven in rotation by the circulation of oil between the blades of the impeller wheel 101 and the turbine wheel 102.
• a locking clutch 1 is provided, in known manner, for direct coupling the casing to the turbine wheel.
• the locking clutch has a piston 2 defining with a transverse wall 107 a control chamber 108.
• This transverse wall 107 belongs to the driving part 105 of the casing intended to be fixed to the driving shaft.
• the piston 2 of annular and metallic shape, is thus located axially between the turbine wheel and the transverse wall.
• the piston 2 has a transverse orientation and is mounted movable axially relative to the transverse wall in order to clamp at least one friction lining 21 between itself and the transverse wall.
• the friction lining is integral with one of the piston 2 - transverse wall 107 elements and acts at the external periphery of the piston 2, which also delimits a main pressure chamber 109 on the side of its face facing the turbine wheel.
• the piston By varying the pressure, for example in the control chamber 108, the piston is moved in the direction of the transverse wall 107 or the piston is moved away from the transverse wall.
• This piston 2 is coupled via the torsion damper 3 to the hub of the turbine wheel.
• lock-up clutch 1 is also called the lock-up clutch.
• the torsion damper 3 comprises two coaxial parts 4,5-6 mounted movable in rotation relative to each other against elastic members with circumferential action 7,70,71 with , for the series connection of at least some of said elastic members, at least one phasing washer 8.
• One of the coaxial parts constitutes the input element 4,5 of the torsion damper 3 belonging to the locking clutch 1, while the other of the coaxial parts constitutes the output element 6 of the shock absorber 3.
• the outlet element 6 here consists of a metallic veil, which has projecting from place to place at its outer periphery transverse arms 60 directed radially outward in the direction opposite to the axis of axial symmetry XX 'which has l hydrokinetic coupling device.
• the web 6 has at its internal periphery a fixing section 61 offset axially relative to the arms and this in the direction opposite to the piston 2, that is to say in the direction of the turbine wheel.
• This section 61, of transverse orientation has holes 62 for fixing the web 6 to the hub 106 of the turbine wheel 102 here using non-visible rivets for clarity.
• the phasing washer 8 is also metallic and has from place to place radially projecting radially inwards, that is to say towards the axis XX ', protuberances 80, the number of which is equal to that arms 60 of veil 6 and depends on the applications.
• the arms 60 and the protrusions 80 are directed radially in the opposite direction.
• the arms 60 alternate circumferentially with the protuberances 80, here of triangular shape, for support of some of the elastic members 70, 71 consisting here of coil springs.
• Each arm 60 therefore comprises two lugs 63 belonging here to play-engaging means 9 and are adapted to cooperate with shoulders 83 described below.
• the lugs 63 form buttresses.
• the entry part comprises two metal guide washers 4, 5.
• the arms 60 of the web 6 penetrate between the two guide washers 4, 5 arranged on either side of the arms 60 and of the phasing washer 8 surrounding the web 6.
• the guide washers 4, 5 have at their outer periphery circumferential tongues 40, 50 which are circumferentially longer than they are radially high.
• the tongues 40, 50 alternate circumferentially with tabs 41, 51 that each washer 4, 5 has in radial projection at its outer periphery.
• the legs 41, 51 and the tongues 40, 50 of one of the guide washers 4, 5 are facing each other. opposite the tabs 51, 41 and the tabs 50, 40 on the other side of the guide washers 5, 4.
• tabs 41, 51 and tabs 40, 50 depends on the applications.
• three tabs 40, 50 are provided by guide washer 4, 5 and between two consecutive tabs 40.50 there are three tabs 41, 51 of the guide washers, the distribution of the tabs 41, 51 and tabs 40.50 being regular .
• legs 41, 51 and the tongues 40.50 are of transverse orientation.
• the legs 41, 51 are higher radially than wide circumferentially.
• the legs 41, 51 are narrower circumferentially than the tongues 40.50.
• the phasing washer 8 has ears 81 of transverse orientation at its outer periphery. These ears 81 are each implanted between two tongues 40.50 facing each of the guide washers 4.5. Three ears 81 are therefore provided. These ears 81 are longer circumferentially than high radially, while being shorter circumferentially than the tongues 40.50 which, for the position of rest of the torsional damper, protrude from both sides. other of the ears 81.
• the ears 81 are located radially above the triangular protrusions 80.
• the radial axis of symmetry of the protuberances 80 coincides with the radial axis of symmetry of the ears 81.
• the phasing washer 8 thus has ears 81 and protuberances 80 directed radially in opposite directions, the protuberances 80 being shorter. circumferentially that the ears 81, the point of the protuberances 80, in the form of a wedge, being directed towards the axis XX ′.
• the ears 81 are connected to the protrusions 80 by a ring 82 inclined towards the turbine wheel.
• the ears 81 are thus offset axially relative to the protrusions 80, and this in the direction opposite to the piston 2.
• the external periphery (the ears 81) of the phasing washer 8 is axially offset relative to the internal periphery (the protrusions 80) of said washer 8.
• the outer periphery of the veil 6 (the arms 60) is axially offset with respect to the internal periphery (the section 61) of said veil 6.
• a sleeve 64 connects the section 61 to the arms 60. These arms 60 are offset axially in the direction of the piston.
• the fixing section 61 is axially offset with respect to the external periphery of the guide washers 4,5.
• the section 61 is more axially distant from the arms 60 than is the external periphery of the guide washers 4,5, axially offset with respect to the internal periphery of said washers.
• Each guide washer has an inclined section 42 connecting its internal periphery to its external periphery constituted by the tabs 41, 51 and the tongues 40.50.
• piston 2 and the transverse wall 107 are stamped centrally axially in the direction opposite to the turbine wheel 102 in order to be able to accommodate the central part of the torsion damper 3, that is to say the arms 60 and the inner periphery of the guide washers 4.5.
• the internal periphery of said washers 4,5 is here provided with three internal windows 53 of curved shape distributed regularly circumferentially.
• the guide washer 4, the closest to the turbine wheel 102, has at its internal periphery an edge 55 of axial orientation surrounding the sleeve 64 of the web 6.
• Each tongue 40.50 has an external window 54.
• Each lug 81 has external windows 84 facing windows 54 facing one guide washer to the other.
• the inclined sections and rings allow the torsional damper to conform to the shape of the turbine wheel and to best occupy the available space.
• the external windows 84, 54 allow the mounting of elastic members 7, while the internal windows 53 allow the mounting of other elastic members 70, 71 according to a characteristic of the invention.
• all the elastic members 7,70,71 are coil springs and, according to another characteristic, the lugs 41, 51 allow a connection in rotation of the guide washers 4,5 to the piston 2 with axial mobility.
• the elastic members 7, 70, 71 comprise two stages of elastic members implanted on circumferences of different diameter, namely third elastic members 7 implanted on a circumference of diameter greater than that of the second and first elastic members 71, 70 mounted. serial.
• the third, second and third elastic members 7,70,71 are three in number and the third elastic members 7 are coil springs at the end of travel. They have here a stiffness greater than that of the other elastic members 70, 71 which are of the concentric type and each consist of two concentric coil springs.
• the third elastic members 7 are also located radially above the clearance engagement means 9, that is to say radially above the lugs 63 and the shoulders 83.
• the second elastic members 71 belong to a second group of three elastic members 71, while the first elastic members 70 belong to a first group of three elastic members.
• the third elastic members 7 belong to a third group of three elastic members 7.
• the second and the first group of elastic members 71, 70 are arranged along the same circumference, and here have the same stiffness.
• the elastic members of the first group of elastic members may have a lower stiffness than those of the second group, which have a lower stiffness than that of the elastic members of the third group.
• shock absorber 3 may or may not work symmetrically.
• Each protuberance 80 of the phasing washer 8 is interposed between a second elastic member 71 of the second group and a first elastic member of the first group 70 for mounting the members 70,71 in series.
• the protrusions 80 have a triangular shape, and that the windows 53 have an arcuate (curved) shape for mounting two consecutive members 70, 71 in the same window 53 of large circumferential extent.
• the pins 63 of the arms 60 make it possible to retain radially outwards the external springs of the elastic members 70 and 71 located on either side of the same arm 60.
• the lugs 63 have, according to another characteristic, another function because they are adapted to engage each with a shoulder 83 belonging to the internal periphery of the phasing washer.
• the arms 60 are therefore each mounted in a circular notch 86, which has the phasing washer 8 at its internal periphery between two consecutive shoulders 83.
• the phasing washer 8 therefore has additional material at its internal periphery at the level of the protrusions 80. It is thus formed at the internal periphery of the phasing washer three radial projections 85 each delimited laterally by a shoulder 83 and each comprising a central protuberance 80, which makes it possible to stiffen the phasing washer 8 in its zone where the elastic members of the three groups bear.
• a notch 86 thus exists at the internal periphery of the washer 8 between two consecutive projections 85.
• each elastic member 70, 71 consists of two concentric coil springs (an external spring surrounding an internal spring). This transmits more torque.
• each member 70, 71 consists of a single coil spring or of a number greater than two.
• the outer periphery of an arm 60 is in intimate contact with the inner periphery of the phasing washer 8 at its notch 86.
• the phasing washer 8 is therefore centered by the web 6 and the same applies to the guide washers 4,5, which are centered by the flange 55 relative to the sleeve 64, which thus has a double function.
• the veil 6 therefore serves as a centering device for the guide washers 4.5 and the veil 6.
• the springs 7 of the third group of elastic members are mounted here floating in the windows 84,54 as described in the document FR 97 07479 filed on 17 June 1997.
• the length of the windows 84, 54 is greater than the length of the spring 7 at rest. Thus, for a dead stroke determined by the interlocking means with clearance 9, necessary for delayed intervention of the spring 7, the length of the windows is reduced. For more details, see the aforementioned document.
• Each internal radial projection 85 is longer circumferentially than an ear 81 and therefore a tab 41, 51. Thanks to all these arrangements, the ears 81 can have a reduced circumferential size and the phasing washer is robust thanks to its internal radial projections 85 located at the level of the ears 81.
• the guide washers 4,5, the phasing washer 8 and the web 6 are made of sheet metal and are obtained by cutting and / or folding with the press.
• the external 54 and internal 53 windows of the guide washers 4,5 can thus be delimited by curved edges 56 so as to conform to the cylindrical external profile of the coil spring which it receives.
• the windows 54, 53 thus have a robust continuous contour making it possible to retain the springs, in particular the springs 7.
• the shoulders 83 of transverse orientation and the lugs 63 constitute the means of engagement with play 9 above.
• shoulders 83 can be replaced by first stops of another shape.
• the elastic members 70, 71 work in series and with a relatively low stiffness.
• the springs 7, 71 work in parallel and have a higher stiffness.
• the characteristic curve A - transmitted torque C (on the ordinate) as a function of the relative angular movement D - (on the abscissa) between the guide washers 4, 5 and the web 6 makes it possible to dampen vibrations well .
• the vehicle engine drives the vehicle wheels
• the second stops 10 are located radially above the first stops 83 and the backlash engagement means 9.
• first 83 and second stops 10 are formed without additional parts and without weakening the mechanical resistance of the parts 4,5,6,8.
• the tongues 50 of the guide washer 5, the closest to the piston 2 are stamped axially in the opposite direction from the other guide washer, that is to say in the direction of the piston 6. More precisely, it is stamped the tongues 50, as well as the annular zones 58 located on either side of each tongue 50 and extending to the vicinity of a tab 51. There is thus formed a shoulder 10, forming the abovementioned stop 10, at level of connection of a zone 58 to a tab 51.
• the height, measured axially, of this shoulder 10 is a function of the thickness of the phasing washer 8.
• the axial height of the shoulder 10 is at least equal to the thickness of the phasing washer.
• the axial height of the shoulder 10 is slightly greater than the thickness of the phasing washer 8, so that a very small axial clearance exists between the phasing washer 8 and the guide washers 4, 5.
• a relative angular movement occurs between the phasing washer 8 and the guide washers 4, 5 until the lateral edges 87 of the ears 81 come into engagement with the stops 10 of the zones 58 framing the tongues 50.
• the guide washer 5 thus has a wavy shape and has tongues 50 and zones 58 constituting stamped zones offset axially relative to the legs and this in the direction of the piston 2, which is stamped below its zone cooperating with the friction lining 21 to adapt to the shape of the torsion damper.
• the legs 51, 41 are adjacent, being joined and linked to each other by fixing means 11, here spot welding performed centrally in the legs 51, 41.
• the legs 41 are reinforcement legs for the legs 51.
• the fixing is carried out by gluing, riveting, bolting or any other mechanical means.
• the washers 4,5 can be secured to one another in another place.
• the legs 51 are provided with folds 59 at 90 ° laterally. These folds are axially oriented.
• the legs 51 thus have a U-shaped section and form studs engaged in a complementary manner in grooves 22 formed in an annular skirt of axial orientation 23, which has the piston 2 at its outer periphery.
• the skirt 23 is directed axially towards the guide washer 4 and towards the turbine wheel.
• the skirt 23 thus has the shape of an annular comb, its axial length depending on the applications.
• the folds 59 are axially longer than the thickness of the guide washer 5. This thus limits the phenomena of incrustation of the legs 51 in the edges of the grooves 22. The contact zone between the legs 51 and the edge of the grooves 22 is thus increased which reduces the risk of jamming and promotes the sliding of the piston 2, in a reliable and durable manner. This is all the more so as the folds 59 are elastic.
• the tabs 41 of the other guide washer engage in the U-shaped tabs 51.
• the thickness of the tabs 41 is preferably less than the axial length of the folds 59 and a circumferential clearance exists between the edges lateral of the legs 41 and the folds 59.
• the folds 59 yield elastically and are therefore elastically deformable.
• the folds 59 have a height greater than the thickness of the reinforcement tabs 41.
• the reinforcement tabs 41 prevent the folds 59 from deforming plastically, the clearance between the tabs 41 and the folds 59 being determined accordingly. Thus all the legs 51 will participate in the transmission of the torque.
• the elasticity of the folds 59 makes it possible to make up for manufacturing tolerances, to reduce noise and to reduce stresses.
• the deformation of the folds 59 is favored by the fact that the lugs 41, 51 are integral with one another thanks to the fixing means 11.
• the legs 41, 51 and the tongues 40.50 have the same external circumference.
• the legs 51 are higher than the legs 41 to be able to produce the folds 59 so that the washers 4,5 are not symmetrical. It will be appreciated that the torsional damper 3 is very compact radially and this thanks to the circumferential alternation of the legs 41, 51 and the tongues 40.50 for housing the third springs 7.
• the legs 41 reinforce the legs 51 so that we obtain tenons of great resistance.
• the legs 41 are therefore received in the legs 50.
• the folds 59 can be crushed at 150 (FIG. 5) to fix the legs 41.
• the embodiment of the legs 41, 51 is applicable to a torsion damper 3 comprising a web 6 coupled by elastic members to the guide washers 4,5.
• the presence of the phasing washer is not compulsory.
• the arms 60 are arranged symmetrically in the notches 86.
• the arms 60 can be arranged in a non-symmetrical manner.
• the organs 70, 71 can consist of concentric springs of different lengths.
• the torsional damper can belong to a friction disc.
• the web is secured to a grooved hub for its rotational connection with an input shaft, while the guide washers mesh with grooves made at the outer periphery of a friction disc.
• the torsion damper intervenes between a first torque transmission element (the piston 2 for example) and a second torque transmission element (the hub 106 for example) of the driving or driven type. All the shock absorber configurations described in document FR-A-2 393 199 are conceivable.
• the legs 51 may have another shape to facilitate the deformation of their folds at 90 °.
• the windows 53, 54 form housings, as well as the notches 86, for the elastic members.
• these housings 53, 54 can have another shape and consist, for example, of stampings.
• the tongues 40 can also be stamped.
• the number of legs 41, 51 depends on the applications, in particular the torque to be transmitted.
• the extent of the stamped areas 58, 50, 58 depends on the applications, in particular on the relative angular movement between the guide washers 4.5 and the phasing washer 8.
• the folds 90 can be seen in dotted lines before their folding, as well as the reduction in thickness given to the folds for carrying out the hot crushing 150.
• a tab 151 is formed by means of a semi-circular notch 152. It is the tab 151 which is deformed when hot to fix the tab 41 by crimping to the tab 51.
• the tabs 51 are more taller than the legs 41 so that the folds 59 can be produced as shown in FIG. 5.
• the arms 60 can be provided with 90 ° folds like the legs 51 so that the folds of the arms 60 replace the lugs 83.
• the torsion damper 3 can comprise three pairs of members elastic 70.71 and three windows due to the fact that we can finally obtain a significant torque.
• the springs 7 can alternatively be mounted with play in the windows 84 and without play in the windows 54.
• the folds 59 can be made more robust so that a smaller number of legs 51 can participate in the transmission of the torque.
• legs 51 are offset axially relative to the stamped areas 58.50 so that the bottom of the grooves 22 of the skirt 23 of the piston 2 is distant from the transverse part of the piston as visible in FIG. 1.
• the skirt 23 is robust, a ring of substantial material existing between the bottom of the grooves 22 and the rounded area connecting the skirt 23 to the transverse part of the piston 2 here carrying the friction lining 21.
• a first pair of springs 7 can be mounted in the windows 84, 54 with a play that is different from that of the second pair of springs 7. Certain springs 7 can therefore act in delayed mode.
• the folds 59 of the legs 51 may belong to a torsion damper devoid of phasing washers.
• the ears 81 may belong to the web 6, the phasing washer, the lower part of the guide washers 4,5 and the springs 70,71 being eliminated.

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

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• 1997
  • 1997-12-23 FR FR9716371A patent/FR2772862B1/fr not_active Expired - Lifetime
• 1998
  • 1998-12-22 DE DE19882160T patent/DE19882160B4/de not_active Expired - Lifetime
  • 1998-12-22 JP JP53457799A patent/JP2001513182A/ja not_active Ceased
  • 1998-12-22 KR KR1019997007569A patent/KR100572275B1/ko not_active IP Right Cessation
  • 1998-12-22 WO PCT/FR1998/002815 patent/WO1999034129A1/fr active IP Right Grant

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