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
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
  • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
  • F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
• • 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
  • 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
  • F16F15/12306—Radially mounted 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
  • 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
  • F16F15/1232—Wound springs characterised by the spring mounting
  • F16F15/12326—End-caps for 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
  • 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
  • F16F15/1232—Wound springs characterised by the spring mounting
  • F16F15/12346—Set of springs, e.g. springs within springs

Definitions

• the invention relates to the field of torque transmission in motorized devices. It relates more particularly to a torsion damping device.
• Motorized devices may be provided with a torsion damping device on their transmission chain.
• a damping device can be included for example in a clutch disk or a torque limiter disposed between the engine and the gearbox of a vehicle.
• Such a torsion damping device allows the filtering of motor acyclisms and other torsional oscillations.
• These torsion damping devices allow, during the transmission of torque, a relative rotational movement of a first rotating element and a second rotating element, with one or more springs acting circumferentially between them.
• the patent application FR2732426 describes such a torsion damping device with a seat disposed on one end of the spring, this seat comprising a front face, adapted to cooperate with the end of the spring, and a back face adapted to support on the first and second rotating members via a pivot allowing pivoting of the seat relative to the first and second rotating elements.
• the object of the invention is to improve the torsion damping devices of the prior art.
• the invention provides a torsion damping device for a vehicle transmission chain comprising a first rotating element and a second rotating element movable in rotation relative to each other about an axis to against a spring intervening circumferentially between them, a seat being disposed on one end of the spring, this seat comprising: a front face adapted to cooperate with the end of the spring; a dorsal surface adapted to rest on the first and second rotating elements; the seat having a first axial guide arrangement providing axial guidance between the first rotating member and the seat and a second axial guide arrangement providing axial guidance between the second rotating member and the seat.
• the damping device may further comprise the following additional features, alone or in combination:
• the first axial guiding arrangement is adapted to ensure axial guidance only between the first rotating element and the seat, and the second axial guiding arrangement is adapted to ensure axial guiding only between the second rotating element and the seat;
• one of the first axial guide arrangement and the second axial guide arrangement is arranged only on a radially lower portion of the seat and the other of the first axial guide arrangement and the second axial guide arrangement. is arranged only on a radially upper part of the seat;
• the first axial guide arrangement comprises a cavity formed between two axially offset walls of the first axial guide arrangement and the second axial guide arrangement comprises a protuberance having two axially offset walls of the second axial guide arrangement, the two walls of the first arrangement.
• axial guide means being separate and radially spaced from the two walls of the second axial guide arrangement.
• the second rotating element comprising two lateral disks which are mutually integral in rotation, the protuberance of the second axial guiding arrangement being arranged axially between a wafer of one of the two lateral disks and a wafer of the other of the two lateral disks of so that the two side disks can bear against the walls of the second axial guide arrangement; and the first rotating member having a central disk coaxial with the side disks and arranged between the two side disks, a wafer of the central disk being arranged axially in the cavity of the first axial guiding arrangement so that the central disk can lean against the walls of the first axial guide arrangement.
• the first axial guide arrangement comprises two guide pads
• the seat has a hollow in which is arranged a part the first rotating member for providing axial guidance between the seat and the first rotating member;
• the second axial guide arrangement comprises a guide stud
• the two pads of the first axial guiding arrangement and the pad of the second axial guiding arrangement are radially spaced apart.
• two parts of the second rotating element are arranged axially on either side of the stud of the second axial guide arrangement to ensure axial guidance between the seat and the second rotating element;
• the seat is made of metal such as steel or sintered steel and the guide pads have dimensions making them suitable for being obtained by cold stamping.
• a first advantage is that it is possible to achieve the seat by a process of the type cold stamping, cold forming, cold forging, cold stamping .. Such methods are faster and less expensive than, for example, the molding in a context of industrial production. However, these methods are limited to certain part geometries and are not compatible with the seats of the state of the art.
• the freedom of dimensioning allowed by the invention for the guiding arrangements facilitates the sizing of guiding arrangements to make them compatible with this type of typing process.
• the guide ribs cooperate with both the first rotating element and the second rotating element. These first and second rotating elements must therefore be axially spaced at least from the thickness of the ribs guide.
• the guiding ribs of the seats of the damping devices of the prior art are generally interposed axially between the first and second rotating elements, which prevents axially bringing these elements together during the design of the torsion damper.
• the invention makes it possible, by decoupling the axial guides between the seat and the first rotating element on the one hand and between the seat and the second element on the other hand, to make the axial positions of these elements independent of each other, which can therefore be brought axially independently of the shape of the axial guide pads.
• axial guidance here designates the fact of limiting or even preventing the relative axial movement of the parts in the direction of the axis of rotation.
• the damping device may also include the following additional features, alone or in combination:
• the second rotating element comprises two lateral disks which are mutually integral in rotation, the guide pad of the second axial guide arrangement being arranged axially between a wafer of one of the two side disks and a slice of the other of the two disks.
• the first rotating element comprises a central disk coaxial with the side disks and arranged between the two side disks, a wafer of the central disk being arranged axially between the two guide pads of the first axial guide arrangement;
• the two guide pads of the first axial guiding arrangement each define a guiding surface, these two guiding surfaces being disposed axially facing one another and spaced apart by a distance substantially corresponding to the thickness of the disk; central so that these guide surfaces are adapted to axial guidance between the seat and the central disc;
• the guiding pad of the second guiding arrangement defines two guiding surfaces, these two guiding surfaces being spaced apart by a distance substantially corresponding to the spacing between the two lateral disks so that these guiding surfaces are adapted to axial guiding; between the seat and the two side discs;
• the back of the seat is adapted to rest on the first and second rotating elements via a pivot allowing pivoting of the seat relative to the first and second rotating members, the first axial guide arrangement and the second axial guide arrangement being disposed on either side of the pivot.
• the first axial guide arrangement is located radially outside the pivot and the second axial guide arrangement is located radially inside the pivot;
• the pivot comprises a portion of a cylinder projecting from the dorsal face of the seat and extending axially
• the device comprises, for each spring, a window in each of the lateral and central disks, these three windows being arranged substantially facing on the other hand so that the spring takes place in these windows, each of the windows having a pivoting notch adapted to cooperate with the seat pivot;
• the windows of the lateral disks each comprise a cavity vis-à-vis one of the guide pads of the first axial guiding arrangement, so that the two guide pads of the first axial guiding arrangement are at a distance side disks;
• the window of the central disk comprises a cavity facing the guide stud of the second axial guide arrangement, so that the guide pin of the second axial guide arrangement is away from the central disk whatever the angle; pivoting seat;
• the central disk window has a bearing surface on the guide pad of the second axial guide arrangement, so as to adjust the spring preload when the damper is at rest;
• the second axial guide arrangement comprises only a single guide pad.
• a rib extends between the single guide pad of the second axial guide arrangement and the pivot; - The single guide pad of the second axial guide arrangement is spaced from the pivot;
• the two guide pads of the first axial guide arrangement are spaced from the pivot;
• the seat comprises two notches arranged axially on either side of the single guide pad. Thus, a greater pivoting of the seat is possible;
• the two guide pads of the first axial guide arrangement each have a quarter disc profile protruding from the first surface, a portion of the edges of the guide pads forming portions of the contour of the seat.
• FIG. 1 shows a clutch disc provided with a damping device according to the invention
• FIG. 2 is a partial exploded view of the clutch disk of FIG. 1; - Figures 3 and 4 show in perspective one of the seats of the damping device of Figures 1 and 2, and show respectively its front face and its dorsal face;
• FIG. 5 is a schematic view showing the arrangement of the dorsal face of the seat of FIGS. 3 and 4;
• FIGS. 6 and 7 show the discs visible in FIG. 2, represented from the front;
• FIG. 12 illustrates an alternative embodiment of the seat of Figures 3 and 4.
• FIG. 1 illustrates an exemplary embodiment in which the damping device according to the invention is integrated in a clutch disk 1 intended to take place between the engine of a vehicle and its gearbox.
• the clutch disc 1 comprises a circular friction lining 2 and a central hub 3 provided with internal splines.
• the central hub 3 is intended to be coupled in rotation, thanks to its internal splines, to the input shaft of the gearbox of the vehicle and the friction lining 2 is intended to be coupled in rotation, thanks to a mechanism clutch, the engine flywheel of the vehicle engine. A torque is thus transmitted between the central hub 3 and the friction lining 2, or vice versa.
• the clutch disk 1 is provided with a torsion damping device allowing a relative rotational movement about the X axis between the central hub 3 and the friction lining 2 to allow damping of the torsional oscillations during of torque transmission.
• the torsion damping device comprises, in the present example, five springs 4 arranged circumferentially around the central hub 3.
• the terms "external” and “internal” as well as the “axial” and “radial” orientations will be used to designate, according to the definitions given in the description, elements of the torsion damper.
• the X axis of rotation determines the "axial” orientation.
• An axial rotation is thus a rotation about the axis X and an axial guidance of a limit element, or even prevents the translation of this element along this axis X.
• the "radial" orientation is directed orthogonal to the axis X.
• the circumferential orientation is orthogonal to the X axis of rotation and orthogonal to the radial direction.
• the torsion damping device is adapted to compress the springs 4 between a first rotating element 5 and a second rotating element 6 to provide damping.
• FIG. 2 is an exploded and simplified view of the clutch disc of FIG. 1, in a partial perspective view centered on one of the springs 4 of the clutch disc 1 of FIG.
• the second rotating element consists of a pair of side disks, hereinafter called guide washers 6 which are integral in rotation with one another.
• the first rotating element here consists of a central disk, hereinafter referred to as web 5, placed between the two guide washers 6.
• the friction linings 2 are fixed on the web 5, for example by intermediate supports and rivets, and the two guide washers 6 are both fixed by rivets on the central hub 3, on both sides of the web 5.
• the guide washers 6 and the web 5 thus constitute an axial stack of three discs with a possible relative rotation between the web 5 and the guide washers 6 which corresponds to the possible rotation between the friction linings 2 and the central hub 3.
• the web 5 comprises a window 7 and the guide washers 6 each comprise a window 8.
• the corresponding spring 4 is mounted in the windows 7, 8 so that its ends each cooperate with an edge of the window 7 and an edge of each window 8.
• the ends of the spring 4 cooperate with the windows 7, 8 by means of two seats 9 each placed at one end of the spring 4. Each of the seats 9 thus bears against one edge of the window 8 and against one edge of each of the windows 8.
• Pivoting means are provided to allow pivoting of the seat 9 with respect to the web 5 and with respect to the guide washers 6. This pivoting is allowed around an axis extending axially and centered substantially on a diameter of the seat 9.
• the pivoting means consist of a pivot 10 that includes the seat 9, as well as a pivoting notch 1 1 made on the web 5 (the pivoting notch 1 1 is provided on the edge corresponding window 7), and a pivot notch 12 provided on each of the guide washers 6 (each pivoting notch 12 is provided on the corresponding edge of the window 8).
• the pivot 10 of the seat 9 here consists of a projecting surface of the seat 9, in the form of a transverse bar extending substantially along a diameter of the seat 9.
• the pivot 10 is supported on the three pivoting notches 1 1, 12 (The pivot notch 1 1 in the center and, on either side of the latter, the two pivoting notches 12).
• the housing created by the three pivoting notches 1 1, 12 thus receives the pivot 10 by allowing it to pivot about an axis extending axially, that is to say parallel to the axis X.
• each spring 4 when a relative axial rotation movement takes place between the web 5 and the two guide washers 6, one of the seats 9 is compressed only by the web 5 and deviates from the edges of the windows 8 of the guide washers 6, while the other seat 9, on the opposite end of the spring 4, bears only on the guide washers 6 while the edge of the window 7 of the web 5 moves away.
• the spring 4 is in this way compressed during the relative movements between the web 5 and the guide washers 6 to provide the torsional damping function.
• the cooperation of the ends of the spring 4 with the web 5 and the guide washers 6 is optimized and made reliable thanks to the seats 9 which allow a retention in place of the spring 4 and an interface avoiding that the ends of the spring 4 are degraded in contact with the sail 5 and guide washers 6.
• the seats 9 also allow optimal guidance of the spring 4 with the pivot 10 ensuring compression of the spring 4 without parasitic effort (the ends of the spring 4 remain substantially parallel to each other during its compression, thanks to the pivot 10).
• the seats 9 are further guided axially relative to the web 5 and the guide washers 6 by participating in the stop in axial translation of the web 5 and the guide washers 6.
• the seats 9 comprise for this purpose guiding arrangements, described below, comprising surfaces which maintain the relative positions, along the axial direction, between the seat 9 and the web 5 and between the seat 9 and the guide washers 6.
• the seat 9 comprises a front face 13, shown in FIG. 3, adapted to cooperate with one end of the spring 4.
• the seat 9 also comprises a dorsal face 14, shown in FIG. 4, intended to cooperate with the edges of the windows 7, 8 of the sail 5 and guide washers 6.
• the seat 9 comprises, on its front face 13, a circular bearing surface 15 intended to support the end turn of the spring 4 and a central peg 1 6 projecting for holding in place the spring 4.
• the stiffness of the damping device can be increased by providing a second spring inside the spring 4, parallel and coaxial with the latter, the front face of the seat 9 then comprising a second circular bearing surface 17 and a second central pin 18, themselves protruding from the central pin 16 and coaxial with the latter.
• the presence or absence of additional springs inside the spring 4 modifies only the stiffness of the entire system and does not affect the operating mode of the seat 9.
• the circular bearing surface 15 also has two notches 19 which allow greater angular displacement of the seat 9 relative to the guide washers 6 (as explained below) at the cost of a slight reduction in the circular bearing surface 15 but without affecting the quality of the support for the end of the spring 4.
• the dorsal surface 14 of the seat 9 comprises the pivot 10 which is in the form of a bar extending transversely, substantially according to a diameter of the seat 9.
• the pivot 10 is made by a protruding surface of the dorsal face 14 of the seat 9, this projecting surface being substantially semi-cylindrical, except for its two lateral ends 20 which are bevelled.
• the pivot 10 separates the dorsal face 14 of the seat 9 into two surfaces: a first surface 21 which here has substantially a half-disk shape and which encompasses the entire surface of the dorsal face 14 which is above the pivot 10 (when the seat 9 is in its position shown in Figure 4); and a second surface 22 which encompasses the entire surface of the dorsal face 14 below the pivot 10 (when the seat 9 is in its position of Figure 4).
• the first surface 21 comprises a first axial guiding arrangement 23 intended for axial guidance between the web 5 and the seat 9.
• the second surface 22 comprises a second axial guiding arrangement 24 intended for axial guidance between the two guide washers 6 and the seat 9.
• the first axial guiding arrangement 23 is formed by two guide pads 25 projecting from the first surface 21.
• the two studs 25 each define an axial guiding surface 26 which is substantially perpendicular to the longitudinal axis 27 in which the pivot 10 extends (and which is therefore also the axis of rotation of the seat 9 the pivot 10 is mounted against the pivot notches 1 1, 12).
• the two axial guide surfaces 26, each disposed on one of the pads 25, are therefore parallel to each other and are arranged opposite one another, spaced apart. a distance corresponding substantially to the thickness of the web 5 to axially guide the latter.
• the spacing between the two axial guide surfaces is equal to the thickness of the web 5 increased by an operating clearance allowing the insertion of the web 5, by its edge, between the two surfaces 26.
• this operating clearance can be from 0.1 to 0.2 mm, for example.
• Each of the guide surfaces 26 further comprises a bevel 28 (or a rounded) facilitating the insertion of the web 5 by its edge between the two surfaces 26 during operation of the torsion damper. More specifically, it is the slice of the web 5, at the corresponding edge of the window 7 which is inserted between the two surfaces 26.
• the two studs 25 have, in the present example, substantially a salient quarter disc profile of the first surface 21, the semi-circular profile edges of the studs 25 coinciding with the edges of the seat 9.
• the second surface 22 of the dorsal face 14 of the seat 9 comprises a single stud 29 made by a protruding surface of the second surface 22.
• the single stud 29 defines two axial guiding surfaces 30 arranged on one side and on the other hand the single stud 29 and both perpendicular to the axis 27 of the pivot 10.
• the two axial guide surfaces 30 are therefore parallel to each other and are spaced apart by a distance corresponding substantially to the mutual spacing of the guide washers. 6 for the axial guidance of the seat.
• the mutual spacing of the guide washers 6 denotes in the present application the space available between the guide washers 6, that is to say the distance separating the inner faces of the guide washers 6.
• the distance between the two Guiding surfaces 30 is equal to this mutual spacing of the guide washers minus a running clearance (as previously, for example from 0.1 to 0.2 mm).
• the two guide washers 6 can therefore be arranged axially on either side of the single stud 29, the single stud 29 fitting in an adjusted manner between the two guide washers 6 so that the seat is guided axially between the respective inner surfaces of the guide washers 6, that is to say their surface facing the web 5.
• the seat is thus retained axially between the edges of the windows 12 of the guide washers 6.
• the two guide washers 6 being fixed relative to each other (by attaching each to the central hub 3), the assembly is suitably guided axially by means of a single guide surface 30 by guide washer 6 and by seat 9.
• the single stud 29 comprises two bevels 36 (or two rounded) facilitating the insertion of the two guide washers 6 on the other hand.
• the single stud 29 In this embodiment, the single stud 29 is connected to the pivot 10.
• Figure 5 is a schematic representation showing the dorsal face 14 of the seat 9 cooperating with the web 5 and the guide washers 6 (schematized in profile, dashed). This view illustrates the parts of the web 5 and the guide washers 6 which are in contact with the seat 9 and thus illustrates the mutual axial guidance of these elements 5, 6, 6.
• the web 5 whose profile shown in dashed lines in FIG. 5 corresponds to its thickness, cooperates only with the two studs 25. As indicated above, the distance 31 separating the two axial guiding surfaces 26 defined by the two studs 25 , is equal to the thickness 32 of the web 5 plus a set of operation. The operating clearance is illustrated by a gap between the thickness of the web 32 and the two axial guide surfaces 26, which gap is exaggerated in Figure 5 for a better readability of the figure.
• the distance 33 separating the two guide washers 6 is equal to the distance 40 separating the two axial guidance 30 defined by the single stud 29, added the operating clearance, which is also exaggerated in Figure 5.
• Figures 6 and 7 respectively show the web 5 and a guide ring 6, viewed from the front, that is to say viewed in an axial direction. These figures show the arrangement of the windows 1 1, 12 which allow the web 5 to cooperate only with the two studs 25 and the guide washers 6 to cooperate only with the single stud 29.
• the web 5 has as many windows 7 as there are springs 4 in the damping device.
• Each window 7 has two edges each cooperating with one end of the spring 4.
• Each edge of a window 7 has the pivoting notch 1 1 previously described and also has an internal cavity 34 positioned radially internal to the notch pivoting 1 1.
• the internal cavity 34 allows the web 5 to circumvent, with or without play, the single stud 29.
• the window 7 On the other side of the pivoting notch 1 1, ie in the radially external position with respect to the pivoting notch 1 1, the window 7 has, on each edge, an external guide zone 35.
• the external guide zone 35 is intended to penetrate between the two axial guide surfaces 26 defined by the two studs 25 of the seat 9.
• the overall axial guidance of the web 5 is thus made by all the external guide zones 35 bordering the windows 7. and distributed circumferentially on the web 5.
• the guide ring 6 comprises, as previously, as many windows 1 1 as there are springs 4 in the damping device.
• a single guide washer 6 is here described with reference to Figure 7, it being understood that the two guide washers 6 are identical.
• Each edge of a window 8 comprises the pivoting notch 12 intended to cooperate with the pivot 10 of the corresponding seat 9.
• Each edge of a window 8 also has an external cavity 37 positioned radially external to the pivoting notch 12.
• This external cavity 37 is intended to bypass the stud 25 of the seat 9 in front of which the cut 37 will be positioned.
• the two guide washers 6 in fact being positioned on either side of the single stud 29, each guide washer 6 will be positioned, at its cavity 37, in front of one of the studs 25.
• the cavity 37 is intended to circumvent, with a game, the corresponding pad 25, that is to say that the guide ring 6, through the cavity 37, always remains away from the pad 25 corresponding.
• the two studs 25 are away from the guide washers 6 whatever the pivoting angle of the seat 9. That the seat 9 is therefore in one or other of the extreme angular positions allowed by the pivot 10 the guide washers 6 will not come into contact with the seat 9.
• the guide washer 6 further comprises, at the edges of the windows 8, a guide zone 38 disposed radially inwardly relative to the pivoting notch 12. This internal guide zone 38 is intended to cooperate with one of the two axial guide surfaces 30 defined single pad 29.
• each single stud 29 of a seat 9 is thus surrounded by two internal guide zones 38 each belonging to a guide washer 6 for axial guidance between the seat 9 and the guide washers 6.
• Figures 8 and 9 show a spring 4 mounted in a window 7 of the web 5.
• the guide washers 6 have not been shown to show more clearly the cooperation of the seats 9 with the edges of the window 7 of the veil 5.
• the pivot 10 of the seat 9 appears mounted in the pivot notch 1 1.
• the radially inner cavity 34 actually bypasses the single stud 29.
• a clearance 39 (shown in bold lines in FIG. 8) is provided between the cavity 34 and the single stud 29, so that these two elements do not come into contact with each other. with each other.
• the spring 4 can be prestressed at rest by providing contact between the cavity 34 and the single stud 29 and by dimensioning the window 7 so that the spring 4 is pre-compressed by a certain distance the cavity 34 then forms, according to this variant, a bearing surface support surface for the single stud 29.
• FIG. 9 is a perspective view at an angle showing the cavity 34 which bypasses the single stud 29, and the guide zone 35 which is inserted in the space between the two studs 25.
• FIGS. 10 and 11 are views similar to FIGS. 8 and 9 in which, however, the guide washers 6 have been represented in addition to the web 5.
• FIGS. 10 and 11 are therefore an enlarged view of FIG. 1, centered on one of the springs 4.
• the window 8 of a guide washer 6 appears in the foreground.
• the insertion of the pivot 10 of each seat 9 in the pivoting notch 12 of the guide washer 6 is visible here.
• the radially outer cavity 37 of the guide washer 6 is also visible on each edge of the window 8 and effectively bypasses the stud 25 in front of which it is mounted.
• the web 5 In this zone, there is, behind the guide ring 6 in the foreground, the web 5 and more precisely the guide zone 35 of the web 5 inserted between the two studs 25.
• the second guide washer 6, disposed behind the web 5 is not visible in this view of Figure 10.
• the radially inner guide zone 38 of the foreground guide washer 6 is here visible and covers the single stud 29, the profile of which is shown in dotted lines.
• the guide zone 38, visible in FIG. 10, is positioned against one of the axial guide surfaces 30 of the single stud 29.
• FIG. 10 also shows the role of the two notches 19 of the circular bearing surface 15 which allow a greater angular displacement of the seat 9 without pivoting the latter 9 without the latter touching the windows 8 of the guide washers 6.
• Figure 1 1 is a perspective view illustrating the face that is not seen in Figure 10.
• Figure 10 is a front view
• Figure 1 1 is a rear view.
• Figure 1 1 thus shows the same guide ring 6 that visible in the foreground of Figure 10, seen from behind.
• FIG. 11 does not represent the web 5 and the other washer 6 so as to make visible the cooperation of the single stud 29 and of the guide zone 38 of the guide washer 6.
• FIG. 11 is the edge of the guide zone 38 which disappears behind the single stud 29 and which is therefore represented in dashed lines.
• FIG 12 illustrates a variant of the seat 9, the common elements have the same numbers as before.
• the single stud 29 is not attached to the pivot 10 but, on the contrary, it is removed.
• the single stud 29 nevertheless has the two axial guide surfaces 30 intended to cooperate with the two guide washers 6.
• the first axial guiding arrangement 23 is independent of the second axial guiding arrangement 24 so that the shape and the dimensions of the two studs 25 and the single stud 29 can be modified. without influencing one another.
• the web 5 and the guide washers 6, which cooperate with the independent guide surfaces 21, 22, 30, can be moved closer axially closer to each other, beyond what is allowed when the same form is used to ensure both the guiding between the web 5 and the seat 9 and between the seat 9 and the guide washers 6.
• the seat 9 is metallic and the pads 25, 29 and the pivot 10 have been chosen to allow production by striking, especially cold.
• the shapes of the studs 25, 29 and the pivot 10 are thus slightly protruding from the first surface 21 and second surface 22 with respect to their other dimensions, that is to say that their dimensions taken perpendicular to the plane of the surface of the dorsal face 14 are smaller than their dimensions taken parallel to this plane.
• This raised aspect of the seat 9, which also increases its robustness, is allowed by the decoupling of the guiding functions.
• Other embodiments of the damping device according to the invention can be implemented without departing from the scope of the invention.
• the damping device may be provided in any type of torque transmission devices such as, for example, other types of clutch discs, torque limiters, dual damper wheels, or any other device comprising a torsion damper.
• the web 5 and the guide washers 6 may also have reverse functions with respect to the torque transmission, which does not change the guide between the seat 9 and the web 5 and between the seat 9 and the guide washers 6
• the web 5 may for example be fixed to the central hub 3 and the guide washers 6 may be fixed to the circular friction lining 2.
• the first rotating element and the second rotating element may also consist of a different number of disc than those presented here, for example, two discs for each item.
• the radially outer and radially inner elements may be inverted, the two studs 25 may for example be in a radially internal position and the single stud 29 may then be in a radially external position, with an adaptation of the guide zones and corresponding cavities.

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• Aviation & Aerospace Engineering (AREA)
• Mechanical Operated Clutches (AREA)

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• 2018
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  • 2019-03-28 WO PCT/EP2019/057927 patent/WO2019185835A1/fr active Application Filing
  • 2019-03-28 EP EP19713485.1A patent/EP3775613A1/de active Pending
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