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
  • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
  • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
  • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range

Definitions

• the present invention relates to a pendulum damping device with stabilized rolling element.
• Known torsional damping devices also known as pendulum oscillators or pendulums, which are particularly but not exclusively used for transmitting a motor vehicle, are known in the state of the art.
• At least one torsion damping device is generally associated with a clutch capable of selectively connecting the engine to the gearbox, such as a friction clutch or a hydrokinetic coupling device comprising a locking clutch, in order to filter the vibrations due to motor acyclisms.
• a clutch capable of selectively connecting the engine to the gearbox, such as a friction clutch or a hydrokinetic coupling device comprising a locking clutch, in order to filter the vibrations due to motor acyclisms.
• an internal combustion engine has acyclisms due to successive explosions in the cylinder of the engine, these acyclisms varying in particular according to the number of cylinders.
• the damping means of a torsion damping device therefore have the function of filtering the vibrations generated by the acyclisms and intervene before the transmission of the engine torque to the gearbox.
• the damping device comprises a support, coupled in rotation to a motor shaft, and at least one pair of flyweights, generally several pairs of flyweights distributed circumferentially on the support.
• the pairs of weights are arranged around the axis of rotation of the drive shaft and each pair of weights is free to oscillate about an axis of oscillation substantially parallel to the axis of rotation of the drive shaft and rotated around this axis of rotation.
• the flyweights move so that the center of gravity of each of them oscillates around this axis of oscillation.
• the inertial effects of these weights reduce the motor acyclisms.
• SUBSTITUTE SHEET (RULE 26) relative to the axis of oscillation, are in particular established so that, under the effect of centrifugal forces, the oscillation frequency of each of the weights is proportional to the speed of rotation of the motor shaft, this multiple For example, it can take a value close to the rank of the overriding harmonic of the vibrations responsible for the strong irregularities of rotation in the vicinity of the slow motion.
• the support extends radially and comprises two opposite planar faces on which are mounted a plurality of pendulums.
• Each pendulum typically comprises two flyweights, each of these flyweights being movably mounted on one side of the support, typically by means of two rolling elements.
• Each rolling element is in rolling contact both with the support and with each of the weights, or possibly with a connecting element for the joining of these weights.
• the rolling elements and the weights are subjected to significant centrifugal forces resulting in localized forces, or high pressures at the points of contact with the support of a on the other hand, and with the weights, or connecting elements on the other hand. These forces, or pressures are further increased at the edges of the rolling elements due to a phenomenon called "edge effect".
• the object of the invention is notably to provide a pendulum damping device comprising one or more more stable rolling elements, thanks to an improved geometry.
• the subject of the invention is a pendular damping device intended to be connected to an explosion engine, this device comprising at least one support movable in rotation about an axis, called the axis of the support, at least one pendulum comprising a first weight (and optionally a second weight) mounted movably on the support, thanks to at least one rolling element, characterized in that said rolling element comprises at least one bearing surface, said stabilized, each bearing surface stabilized being symmetrical of revolution about the same axis, said bearing axis, and comprising:
• the rolling element Due to the existence of a central annular zone between the two bosses, in which the circumferential diameter is smaller than the maximum diameter, the rolling element can roll over two distinct contact zones, separated from each other and parallel, corresponding to the two zones of the same maximum diameter corresponding to the two bosses. This gives the rolling element a high stability, both axial and radial, in contrast to what happens with a "barrel" range profile: in the latter case, there may only be one point of contact, uncontrolled position, along the oval shaped barrel profile.
• Each of the bosses advantageously has an axial profile forming a continuous curve, and each of the maximum diameter zones of the two bosses separates the central annular zone from an annular end zone having a constant or evolving diameter smaller than the maximum diameter. It is understood that the diameter, or circumferential diameter, constant or evolutive, of a zone of axial revolution corresponds to the diameter of a circle of this surface disposed in a radial plane.
• each of the maximum diameter zones can be reduced to substantially a circle disposed in a radial plane.
• the central annular zone delimited by the two annular zones of maximum diameter is an area in which the circumferential diameter is only slightly less than the maximum diameter, the profile of the span being scalable in a very limited way, in order to allow contact more important during the elastic deformation of the bearing surfaces in contact, and as and when wear of the rolling element.
• the difference in value between the maximum diameter on the one hand, and the minimum diameter of the central annular zone on the other hand is generally between 1 and 80 micrometers, often between 8 and 80 micrometers, preferably between 20 and 60 microns. micrometers, and very preferably between 40 and 50 micrometers.
• the maximum radial distance between the bearing surface and the complementary bearing surface is generally between 16 and 160 microns, and preferably between 40 and 80 microns. This makes it possible to have no edge effect, while maintaining a low profile, maximizing the contact as wear of the rolling element.
• the stabilized bearing surface and the complementary bearing surface typically each comprise at least one axial end circle, these two circles being arranged facing each other in the same radial plane, said axial end plane of these surfaces. worn vis-à-vis.
• the smallest distance between a point belonging to one or the other of the two zones of maximum diameter and this axial end plane is between 200 and 800 microns, and preferably between 400 and 500 microns.
• the two bosses are sufficiently far from the edges of the scope, but nevertheless maintain a substantial distance between them, for example between 1 and 8 millimeters, and preferably between 2.5 and 6.5 millimeters, which confers high stability at the steady running range.
• the device comprises a second flyweight, the first flyweight and the second flyweight being movably mounted vis-a-vis on two opposite faces of the support, and the rolling element comprises first and second bearing surfaces. stabilized, in rolling contact with the first and second flyweights respectively, the maximum diameters of the bosses being substantially identical for these two stabilized bearing surfaces.
• the device may also comprise a second flyweight, the first weight and the second flyweight being mounted movable vis-à-vis on two opposed faces of the support, and integral with each other by means of at least one connecting element, the two bosses being in rolling contact both with a first complementary bearing surface belonging to the support and with a second bearing surface (which could also be described as complementary) belonging to the link element.
• the rolling element further comprises a third stabilized bearing surface in rolling contact with the support, the maximum diameter of the bosses of this third stabilized bearing surface being preferably greater than the maximum common diameter of the first and second surfaces of stabilized reach.
• This type of rolling element is sometimes called a "two-diameter roller".
• all the rolling elements for all clocks, have stabilized bearing surfaces, both for contacts with the weights associated with them and for contact with the support.
• Another object of the invention is finally a clutch, simple, double, or multiple comprising a pendular damping device as previously defined.
• FIG. 1 shows in perspective a partial view of a pendulum damping device according to a first embodiment of the invention, comprising a pendulum support and several pendular weights mounted on this support.
• Figure 2 shows in perspective another partial view of the device of Figure 1, showing a rolling element.
• FIG. 3 represents a sectional view, along the line III-III of FIG. 2, of the stabilized bearing surface of the rolling element of FIG. 2.
• FIG. 4 represents a sectional view of the stabilized bearing surface of the rolling element of FIG. 2, according to a variant of the embodiment of this rolling element represented in FIG. 3.
• Figure 5 shows a sectional view of a rolling element of a pendulum damping device according to a second embodiment of the invention.
• FIGS. 1 to 4 show, partially, a pendular damping device 1 according to a first embodiment of the invention, in which two flyweights are made integral by means of at least one connecting element 8 which cooperates with each other. with one or more rolling elements (there is then no direct cooperation between the flyweights and a rolling element).
• the device 1 comprises a support 2 for a plurality of pendulums distributed circumferentially on the support 2, which is for example a phasing washer of a clutch.
• the support 2 has a generally planar, annular, radially extending shape.
• FIG. 1 represents two first flyweights 4, and two second flyweights 6, each first flyweight being disposed on one face of the support 2, and associated with a second flyweight disposed on a second face of the support 2 opposite to the first face.
• Two weights 4 and 6 associated vis-à-vis are integral with each other, each being integral with two connecting elements 8, nested in recesses arranged in these weights.
• the connecting elements each extend typically axially, that is to say parallel to the axis of the support 2.
• FIG. 2 is a perspective view of another partial view of the device of FIG. 1, showing the support 2, a connecting element 8, and a rolling element 10 formed by a cylindrical roller of circular section, comprising a stabilized bearing surface. , able to roll on a bearing surface 8A of the connecting element 8 on the one hand, and on a complementary bearing surface disposed on an edge 2A of the support 2 on the other hand.
• the stabilized bearing surface and the complementary bearing surface are referenced in FIG. 3.
• the edge 2A delimits a recess of the support 2 allowing the passage of the connecting element 8 and of the rolling element 10.
• the connecting element 8 could alternatively be integrated with the first flyweight 4 or the second flyweight 6.
• the assembly formed by a first flyweight 4, a second flyweight 6 associated with the first flyweight, and the two corresponding connecting elements 8 constitutes a pendulum capable of oscillating on the support 2.
• FIG. 3 shows a sectional view of a stabilized bearing surface of the rolling element 10 in contact with the support, in the axial plane of the rolling element comprising the line III-III shown in FIG. FIG. 2.
• the stabilized bearing surface 12 of the rolling element 10 extends between the points A and B, facing a complementary plane bearing surface 14 disposed on the support 2, extending between points C and D.
• This stabilized span surface 12 with symmetry of revolution about the rolling axis 16 forms, in the axial plane of FIG. 3, an evolutionary profile passing through the points A, E, F, G, and B.
• Each of the points E and G corresponds, in the plane of FIG. 3, to the point of a circumferential radial boss 17 for which the circumferential diameter D M is maximum.
• the portion of the profile between E and G forms a bowl including in particular the low point F, corresponding to a minimum circumferential diameter D1.
• the profile of the bowl is the axial profile of a central annular surface 18 belonging to the stabilized bearing surface, delimited by two circles arranged in two radial planes and respectively comprising the points E and G for which the circumferential diameter D M is maximum.
• the circumferential diameter is smaller than the maximum diameter D M.
• the presence of the two circumferential bosses 17 ensures a privileged rolling contact between the rolling element 10 and the support 2 (as well as between the rolling element 10 and the connecting element 8, as represented in FIG. 2). along the two aforementioned circles, corresponding in an axial plane to a privileged support between the two remote points E and G.
• the profile of the stabilized bearing surface 12 is only slightly evolutive, so that at the end points A and B, for which the distance between the stabilized bearing surface 12 and the complementary bearing surface 14 on the support 2 is maximum, (at least as regards the areas facing each other which are outside the central annular surface 18), the circumferential diameter D 2 remains close to the maximum diameter D M.
• the slightly evolutive profile around the points A and C avoids edge effects, while ensuring a significant contact with the wear of the rolling element 10, which leads to a reduction of the curvature of the profile of the bosses, or a partial flattening of the top of the bosses.
• FIG. 4 shows, also in an axial plane with respect to the axis 16 of the rolling element, an alternative profile of a stabilized bearing surface of a device according to the invention, this profile comprising two segments H1 and JK of points for which the circumferential diameter D M is maximum, each of these segments generating an annular zone 19 of maximum diameter D M around the rolling element 10. This increases the contact of the rolling element with the support 2 when the rolling element is new.
• the surfaces of maximum diameter 19 also define two annular end zones 20 whose profile extends respectively between A and H on the one hand, and K and B on the other hand.
• FIGS. 5 and 6 show rolling elements of pendular damping devices according to a second and a third embodiment of the invention respectively, in which there is no cooperation between a connecting element between two flyweights and a rolling element, but direct cooperation between each of these two flyweights and the rolling element.
• FIG. 5 shows a rolling element 10 of a device according to a second embodiment of the invention, comprising two non-stabilized barrel profile bearing surfaces 21, for contact with the flyweights, and a stabilized bearing surface. comprising two bosses 17 for contact with the support.
• FIG. 6 finally shows a rolling element of a device according to a third embodiment of the invention (preferred embodiment), comprising three stabilized bearing surfaces: a first stabilized bearing surface comprising two bosses 17 for contact with the support, a second stabilized bearing surface comprising two bosses 22, for contact with the first flyweight, and a third stabilized bearing surface comprising two bosses 24, for contact with the second flyweight.
• Such a rolling element has a maximum stability.
• the maximum diameter D M i of the rolling element 10, at the level of the first stabilized bearing surface, is greater than the maximum diameters D M 2 and D M 3 corresponding to the bearing surfaces in contact with the flyweights. which makes it possible to increase the contact with the support, this one being subjected to the inertial effects of all the two weights.
• the diameters D M 2 and D M 3 are typically identical.
• the devices of Figures 5 and 6 comprise three bearing surfaces, one with the support and two with the weights, and not a single bearing surface in contact with both the support and with a connecting element 8 between the weights.

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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)
• Vibration Prevention Devices (AREA)
• Rolling Contact Bearings (AREA)
• Support Of The Bearing (AREA)
• Mechanical Operated Clutches (AREA)

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• 2012
  • 2012-06-12 FR FR1255488A patent/FR2991739B1/fr not_active Expired - Fee Related
• 2013
  • 2013-04-26 JP JP2015516520A patent/JP6275705B2/ja active Active
  • 2013-04-26 CN CN201380031005.4A patent/CN104350302B/zh not_active Expired - Fee Related
  • 2013-04-26 DE DE112013002908.1T patent/DE112013002908T5/de active Pending
  • 2013-04-26 KR KR1020147034669A patent/KR102182369B1/ko active Active
  • 2013-04-26 WO PCT/EP2013/058775 patent/WO2013185974A1/fr not_active Ceased
• 2018
  • 2018-01-12 JP JP2018003782A patent/JP6588997B2/ja active Active

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