• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    This pendulum torsion damping device, intended to be connected to a main-order explosion engine N, comprises oscillating masses mounted movably on a support. The local order of the pendulum (OR) is under-adapted, and substantially less than N over a range of pendular deflection (DBT) close to the maximum deflection (C ***). This device makes it possible to obtain efficient pendular damping with a reduction of the saturation phenomena of the pendulum at low engine speed, without causing saturation phenomena at high engine speed.
    公开号:FR3014519A1
    申请号:FR1362299
    申请日:2013-12-09
    公开日:2015-06-12
    发明作者:Roel Verhoog；Herve Mahe；Olivier Marechal；Benoit Couturier
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a torsion damping device intended to be connected to a combustion engine, oscillating oscillator type. 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. In a motor vehicle transmission, 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. Indeed, 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.
    [0002] 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. Otherwise, vibrations entering the gearbox would cause in operation shocks, noises or noise particularly undesirable. This is one of the reasons for using one or more damping means capable of filtering vibrations at at least one determined frequency. Document US-2010/0122605 represents a pendulum type damping device.
    [0003] The damping device comprises at least one support, coupled in rotation to a motor shaft, and at least one oscillating mass, generally several oscillating masses distributed circumferentially on the support. The oscillations of these oscillating masses generate an oscillating torque which opposes the oscillating torque coming from the motor and thus absorbs part of the motor a-cycling. The support of the oscillating masses of the torsion damping device is typically integral with the box shaft. Each oscillating mass is generally constituted by a pair of flyweights, arranged on either side of the support, and integral with each other, either by a direct mechanical connection, typically through a recess of the support, or by means of a spacer. Such a set of two counterweights solidarity vis-à-vis, with or without spacer, is considered in the following as a single oscillating weight. Alternatively, each oscillating mass may be a single flyweight mounted on the support. The support can in this case optionally be formed by two elements, the oscillating masses being disposed movable between these two elements. Such an oscillating mass is very generally mounted movably on the support, by means of at least one rolling element, typically by two or more rolling elements.
    [0004] Typically, the center of mass of each oscillating mass is free to oscillate about an axis of oscillation substantially parallel to the axis of rotation of the drive shaft and driven in rotation about this axis of rotation. In response to rotational irregularities, the oscillating masses move in such a way that the center of mass of each of them oscillates around this axis of oscillation. Thereafter, the terms "damping device of twist "and" pendulum ". Pendulums comprising two rolling elements (or rollers) per oscillating weight, called "two-wire pendulums", are typically used, making it possible to obtain damping performances greater than those of a pendulum comprising a single rolling element per oscillating weight, called "Monofilar clock". During the pendulum movement, each oscillating mass of the pendulum therefore oscillates with a movement to the left and a right (possibly different) deflection around a neutral position proper to this mass. This neutral position corresponds to a position of equilibrium when the pendulum is driven at constant uniform speed sufficient for the oscillating masses to be driven radially outwards by the centrifugal force. The center of mass on the one hand, and the points of contact of each rolling element with the associated oscillating weight and with the support, on the other hand, each carry an oscillation movement around a neutral point corresponding to the neutral position. . The pendulum displacement, outside the neutral position, corresponds conventionally to the abscissa x of the center of mass in a given direction perpendicular to the radial direction passing through this center of mass in the neutral position (for example in the direction of rotation of the pendulum). Each value of the pendulum displacement corresponds in a one-to-one fashion to an abscissa of each point of contact of a rolling element with the support on the one hand, and with the oscillating mass on the other hand, this abscissa being calculated in the same way as previously, on the perpendicular to the radial direction passing through the corresponding neutral point. Thus, a given range of pendulum displacement (from the center of mass) also corresponds one-to-one to a range of variation of the abscissa of a point of contact of a rolling element with the oscillating mass, or with the support. The radial position of the center of mass of each of the oscillating masses with respect to the axis of rotation of the motor shaft, such as the distance of this center of mass with respect to the axis of oscillation, is established so that that, under the effect of the centrifugal forces, the oscillation frequency of each of the oscillating masses is proportional to the speed of rotation of the motor shaft, this multiple being able for example to take a value close to the rank of the predominant harmonic of the has cyclismes. A pendulum is calculated to be adapted to a given engine, and in particular to the number of excitations per revolution related to the combustion in a cylinder of this engine. The order N of a combustion engine is thus classically defined as half the number of cylinders of the engine. For engines comprising between 1 and 12 cylinders, N can therefore vary between 0.5 and 6, and for example takes the value 2 for a 4-cylinder engine, generating two combustions per revolution. The pendulum associated with this engine must be adapted to the order of the engine, and the rules of the art lead to design the raceways on the pendulum masses and on the support accurately to obtain a pendulum order (this term will be explained later, in the description of Figure 1) which is very close to the order N of the engine, and typically slightly higher than this, for example equal to N x 1.04 to take account of the wear in time of the pendular system, due to friction. However, it is noted that the damping of a-cycling is not always perfect and that there are most often engine speeds leading to problems of pendular saturation vis-à-vis filtration a-cycling. One of the aims of the invention is to limit or even eliminate these phenomena of pendular saturation. For this purpose, an object of the invention is a twisting torsion damping device of the two-wire type, intended to be connected to a main-order explosion engine N, this device comprising a support movable in rotation around an axis of rotation, and a set of oscillating oscillating masses (6, 8) movably mounted on this support, each oscillating mass of the assembly being able to oscillate on two rolling elements associated with this oscillating mass, which are in rolling contact. with the support and with this oscillating mass, each of these rolling elements determining a trace on an edge of this oscillating mass and on an edge of the support, each of these traces being associated with a left-handed deflection and a pendulum displacement at right, on both sides of a neutral position, characterized in that the traces on the support and on each of these oscillating masses are configured so that there exists: - a first the range of the pendulum displacement on the left disposed beyond a position at 50% of a maximum pendulum displacement on the left, in which the local order of this set of pendular masses is bounded by a maximum value, namely G1max, at most equal to 0.99 x N, and preferably at 0.98 x N, or at most equal to 0.96 N, or 0.95 N; a first range of pendulum displacement to the right, disposed beyond a position at 50% of a maximum pendulum displacement to the right, in which the local order of the pendulum is limited by a maximum value, ie Dl max, to more than 0.99 x N, and preferably 0.98 x N, or at most equal to 0.96 N, or 0.95 N; the local order, OPlocal, of this set of pendular masses in a position of determined pendulum displacement, left or right, being defined conventionally as follows: For any rolling element in contact with an oscillating mass, the order local, identical for each rolling element, is equal to: OPloce = Rg - (Rbp + Rm - (r-bp + rn,)) Rbp + Rn, - (rbp + rn,) in which: - Rg is the distance between a center of mass of the oscillating mass and the axis of rotation; - Rbp is the radius of curvature of the trace on the support at a point of contact with the rolling element, - Rml is the radius of curvature of the trace on the oscillating mass at a point of contact with the rolling element - rbp is the radius of curvature of the rolling element at a point of contact with the support, - rm is the radius of curvature of the rolling element at a point of contact with the oscillating mass.
    [0005] It has been found that this feature, according to the invention, of the existence of a pendulum range, left and right, beyond the average pendulum deflection, in which the pendulum torsion damping device (or pendulum) has a relatively low order, which is sub-adapted with respect to the motor order N, makes it possible to reduce or eliminate pendulum saturations for large pendulum displacements, which correspond to a-cycling during phases of relatively low motor speed . According to a first embodiment of the device according to the invention, over the entire amplitude of the left and right pendulum movement, the local order is less than or equal to 0.99 × N, preferably 0.98 × N and most preferably belongs to the range [0.70 N; 0, 98 N], or even in the range [0.74 N; 0, 96 N], or even in the range [0.76 N; 0, 95 N]. It has been found that although this leads to an imperfect adaptation of the pendulum for relatively small pendulum displacements (corresponding to relatively high engine speeds), this imperfect adaptation does not lead to a saturation of the pendulum, which remains effective for the filtration of the pendulums. -cycling, including at high engine speeds. In particular, the local order may be substantially constant over the entire pendulum swing amplitude on the left and on the right. This configuration of the traces makes it possible to use in particular constant radii of curvature (traces forming portions of a circle), which is relatively easier to implement in the manufacture of the pendulum, than traces of variable radius of curvature . According to a second embodiment of the invention, the traces on the support and on each of these oscillating masses are configured so that there exists: a second range of left-handed deflection extending from the neutral position within the first left swing range, in which the local order is bounded by a minimum value of G2min, at least 0.95 N, and less than 1.10 N; a second range of pendulum displacement to the right extending from the neutral position, below the first range of pendulum displacement to the right, in which the local order is bounded by a minimum value, namely D2min, at least equal to at 0.95 N, and below 1.10 N; and wherein: Glmax is less than G2min by a value between 2% and 30% G2min, and preferably between 3% and 25% G2min; - Dl max is less than D2min of a value between 2% and 30% of D2min, and preferably between 3% and 25% of D2min; Thus, for the relatively low motor rotation speeds, corresponding to relatively high pendulum deflections, the radius of curvature of the trace is relatively high, the OPiocai local order is relatively small, which leads to reducing or eliminating saturation effects. of the pendulum. This corresponds to the first swing range on the left and right. On the other hand, for the relatively high engine rotation speeds, corresponding to relatively small pendulum displacements, the radius of curvature of the trace is relatively small, the OPlocal order is relatively high, which leads to a good filtration of the a-cycling . This corresponds to the second swing range, left and right. The first swing range on the left can be the same as the first swing range on the right. The second pendulum swing range on the left can also be identical to the second right swing range, with respect to the neutral point corresponding to the neutral position. The first swinging range on the left, respectively on the right, extends to a position of maximum displacement on the left, respectively on the right, on a pendulum swing interval which is preferably between 10% and 49%, and preferably between 15% and 35% of an overall range of pendulum displacement to the left, respectively to the right. The second left swinging range, respectively on the right, extends from the neutral position on a pendulum swing interval which is preferably between 50% and 90%, and preferably between 65% and 80% the overall range of pendulum deflection on the left, respectively on the right. The first and the second pendulum swing range on the left, respectively on the right, are advantageously separated by a transition range for the local order, preferably a transition range with continuity of the local order. According to a preferred embodiment of the second embodiment of the invention, the local order on the left, respectively on the right, varies non-decreasingly, preferably substantially continuously, from the neutral position to the maximum pendulum displacement position at left, respectively to the right, so that the ratio of the local order to the maximum point of deflection on the left, respectively on the right, on the local order at the neutral position on the left, respectively neutral on the right, is included in the interval [0.70; 0.95], and preferably in the range [0.80; 0.90]. According to a third embodiment of the invention, the local order is strictly decreasing from the neutral position to the maximum pendulum displacement position left and right. Advantageously, for each oscillating mass, the curve portion representing, as a function of a direction on the left, respectively on the right, the evolution of the radius of curvature of the trajectory of the center of mass (CM) in the first range of the pendulum deflection on the left, respectively on the right, forms a portion of clothoid, the direction on the left, respectively on the right, being considered according to a perpendicular to a radial direction passing through the position of the center of mass (CM) in the neutral position. Another object of the invention is finally a clutch, simple, double, or multiple comprising a torsion damping device, as previously defined. It has been discovered that the invention will be better understood on reading the following description, which is given by way of example only and with reference to the drawings in which: FIG. 1 is a simplified axial view of a part of a torsion damping device according to the prior art, belonging to a clutch, comprising a pendulum support and an oscillating weight mounted on this support, in a neutral position.
    [0006] Figure 2 is a view similar to that of Figure 1, the damping device being in a different configuration of its operation, corresponding to a position of maximum displacement to the left. FIG. 3 schematically represents a part of a pendulum, making it possible to precisely define the parameter of the local order of the pendulum. Figure 4 shows three traces on the right on an oscillating weight, one of which corresponds to the prior art, and the other two respectively to a first and a second embodiment of the invention. FIG. 5 represents the evolution of the radius of curvature of the traces of FIG. 4.
    [0007] FIG. 6 represents the evolution of the order of oscillating masses, corresponding to the traces of FIG. 4. FIG. 7 represents the evolution of the order of the oscillating masses, for a device according to a third embodiment of FIG. invention. FIG. 8 represents the evolution of the radius of curvature of a trace, for a device according to a third embodiment of the invention. FIG. 9 represents an alternative embodiment making it possible to prevent blockage of the rolling elements. FIG. 10 is an enlarged view of part of FIG. 9. FIG. 11 shows the trajectory of the center of mass CM of the oscillating mass during the oscillation of this oscillating mass for a device according to a fourth embodiment of FIG. 'invention. FIG. 12 represents the evolution of the radius of curvature of the curve of FIG. 11. Reference is now made to FIG. 1, on which is schematically and partially shown a torsion damping device 2 comprising a support 4, comprising a peripheral portion of generally flat annular shape, on which are mounted movable a plurality of oscillating oscillating masses distributed circumferentially on the support 4. In Figure 1, there is shown only two spacers 6 connecting two weights belonging to a same oscillating mass, these two flyweights being disposed on either side of the support 4. The two weights and the spacers 6 belong to the same oscillating mass. The oscillating mass rolls on the support 4 by means of two rolling elements 8, these rolling elements each extending in a contour cutout 10 in the support 4. The oscillating weight is represented in FIG. point of contact of the mass with each rolling element being at neutral point NE. In Figure 1, there is shown a rolling contact of the oscillating mass with the support 4, made at the spacers 6. In other configurations, the rolling contact can be at the two weights, not at the level spacers that solidarize these two weights. The end point C of the trace on the right has also been represented on the oscillating mass (with respect to the neutral point), this trace on the right being represented by the arc NE-C, which corresponds to the set of the contact points d a rolling element between the neutral point and a point of contact in a position of maximum displacement to the left of the mass (relative to the neutral position). This position of maximum displacement to the left of the mass is shown in Figure 2, the spacers 6 of the oscillating mass having in this figure a deflection to the left relative to the support in comparison with the neutral position of Figure 1.
    [0008] The deflection, or pendulum deflection, is the distance between the position of the center of mass of the oscillating mass and the position of this center of mass in neutral position. Similarly, traces are defined on the support, each corresponding to all the points of contact of a rolling element with the support.
    [0009] All the oscillating masses typically have on the one hand the same traces on the left (of the neutral point), identical for the two rolling elements, and on the other hand the same traces on the right (of the neutral point) on the mass, identical for the two rolling elements. On the other hand, the traces on the right may be different from the traces on the left.
    [0010] It is the same for the traces on the support. Referring now to Figure 3, which more generally shows traces 12 on the oscillating weight, and 14 on the support. FIG. 3 corresponds to a pendulum configuration different from that of FIGS. 1 and 2, the rolling element 8 having a first zone 16 of radius of curvature rm in contact with the oscillating mass, and a second zone 18 of radius of different curvature rbp in contact with the support. Figures 1 and 2 correspond to the particular case in which rm = rbp. The point CR represents the center of rotation, passing through the axis of rotation of the pendulum (without the distances being representative). The local order of the pendulum in a determined position, OPiccal is conventionally defined by the following formula: OPioce = Rg - (Rbp Rm - (rbp + Rbp + Rm - (rbp + rm) in which: - R9 is the distance between the center of mass of the oscillating mass and the axis of rotation of the pendulum - Rbp is the radius of curvature of the trace on the support at the point of contact with the rolling element, - Rmi is the radius of curvature of the trace on the oscillating mass at the point of contact with the rolling element, - rbp is the radius of curvature of the rolling element at a point of contact with the support, - rm is the radius of curvature of the rolling element. bearing at a point of contact with the oscillating mass Referring now to FIG. 4, which shows three traces to the right on an oscillating weight, one of which corresponds to a pendulum according to the prior art, and the other two respectively to a first and a second embodiment of a pendulum according to The direction to the right, represented by the abscissa x, is considered perpendicular to a radial direction passing through the position of the neutral point of the trace, corresponding to the neutral position for the pendulum movement. The y-axis extends in the radial direction from the neutral point NE.All right-hand traces on the different masses are assumed to be identical to each other, and identical to the traces left on these masses, and it is the same for the traces on the support. The first trace on the right: the upper trace corresponding to the points NE (neutral point), M (middle point of abscissa), A, and C corresponds to a trace (right) conventional, of substantially uniform radius of curvature R, and in the case of a four-stroke engine, of order OM = 2, the corresponding local order of the pendulum, OR is constant and typically close to 2.04. It has been found that such a pendulum is satisfactory at median and high engine speeds, but in saturation state during strong acceleration at low engine speed, typically less than 1500 beats per minute, and then no longer fulfills its filtering function. brutal accelerations.
    [0011] The second trace on the right: the dotted lower trace NE-C *, corresponds to a pendulum according to a first embodiment of the invention: The radius of curvature of the trace is also substantially uniform, but with a value R1> R , and the corresponding local order is also constant, but substantially less than 2.04, for example equal to 1.8. The order of the pendulum (or a set of oscillating masses) is thus under-adapted to that of the engine, equal to 2. As a result, at low engine speed, corresponding to relatively high pendulum displacements, the Pendulum has much lower or no saturation ranges. It has, however, been found that its median and high engine speed behavior, corresponding to relatively small pendulum deflections, is surprisingly only slightly degraded compared to a conventional uniform pendulum 2.04, so that there is no evidence of pendular saturation. Thus, this first embodiment of a pendulum torsion damping device of the two-wire type according to the invention (or pendulum) makes it possible to significantly reduce or eliminate the phenomena of pendular saturation. The third trace on the right, median, corresponding to the points NE, M, A, B, and C ** corresponds to a second embodiment of the invention: The part NE-A of the trace is identical and common with the part corresponding to the first trace according to the prior art, with a radius of curvature R. On the other hand, the end portion of this trace, namely B - C ** has a radius of curvature R1> R. It follows that the order of the pendulum (or of a set of oscillating masses) in this terminal part, corresponding to a first range of swinging movement on the left (a displacement on the left corresponds to a trace portion on the right on the oscillating mass), is lower than that on the bow. NE - A which corresponds to a second range of swinging motion on the left, from neutral point NE, corresponding to zero travel. The second swing range to the left therefore extends from the NE point of the neutral position, below the first left swing range. The local order in this second range is equal to 2.04, and therefore is bounded by a minimum value, G2min, at least 0.95 N, and less than 1.10 N, with N = 2. The first left-handed swinging range extends between the point B and the point C- and the local order of the set of oscillating masses (advantageously all oscillating masses of the pendulum) is limited thereto by a maximum value, let G1max be 1.7. Between points A and B, the radius of curvature R2 (x) increases with the abscissa x, so as to ensure a continuous transition between the first and second left swing range. The operation of the pendulum is further improved with respect to the first embodiment: - For the relatively low engine rotation speeds, corresponding to relatively high pendulum displacements, the radius of curvature of the trace is relatively high, the OPiocai local order is relatively low, which leads to reduce or eliminate the effects of saturation of the pendulum. - Conversely, for relatively high engine rotation speeds, corresponding to relatively small pendulum deflections, the radius of curvature of the trace is relatively low, the OP-local order is relatively high, which leads to good filtration of acyclic. Referring now to FIGS. 5 and 6, FIG. 5 shows the evolution of the radius of curvature of the traces of FIG. 4. For the first trace on the right (upper curve of FIG. 4), corresponding to the prior art, the radius of curvature is constant and equal to R.
    [0012] For the second trace on the right (lower and dotted curve of FIG. 4), corresponding to the first embodiment of the invention, the radius of curvature is constant and equal to R1, with R1> R. For the third trace to right (middle), corresponding to the second embodiment of the invention, the radius of curvature, starting from the neutral point NE first takes the value R to the point A, as in the prior art (trace to the right upper of Figure 4), then takes an increasing value R2 (x) in the transition zone between A and B, to reach and maintain the constant value R1 to the point of maximum deflection on the left C. The radius of curvature takes therefore a first value R, starting from the neutral point NE, then, after a transition zone, takes a higher value R1 when one progresses towards the point of maximum displacement to the left C **. In this embodiment: the first range of the pendulum displacement on the left corresponds to the trace portion B-C **; The second range of left-hand deflection corresponds to the trace portion NE-A. Analogous characteristics are typically used for left-hand tracks on the ground, which correspond to a right-hand swing, and on the right and left tracks on the support. Each of these traces typically comprises different radii of curvature, in a first range of pendular deflection (relatively high radius of curvature, relatively low local order) and a second range of pendulum deflection (relatively small radius of curvature, relatively high local order) , defined in a similar way.
    [0013] FIG. 6 represents the evolution of the order of the oscillating masses, corresponding to the traces of FIG. 4, as a function of the travel DBT. For the first trace on the right (upper) of FIG. 4, corresponding to the prior art, the local order OPlocal is constant and equal to 2.04 up to point C. For the second trace on the right (lower curve and in dotted line of FIG. 4), corresponding to the first embodiment of the invention, the local order OPlocal is constant and equal to 1.7 up to the point R1, with R1> R. For the third trace on the right ( median), corresponding to the second embodiment of the invention, the local order OPlocal, starting from the neutral point NE first takes the value 2.04 to the point A, as in the prior art (trace to upper right of Figure 4), then decreases in the transition zone between A and B, to reach and keep the constant value 1.7 to the point of maximum left clearance C **. The maximum left deflection points C, C *, and C ** corresponding to the different traces on the right of the mass that have been considered can have the same abscissa x or different abscissa. FIG. 7 represents the evolution of the order of the oscillating masses as a function of the DBT clearance, for a device according to a third embodiment of the invention. In this third embodiment, the local order OPlocal decreases continuously from the conventional value of 2.04 to the neutral point, up to the value 1.7. Correlatively, the radius of curvature increases continuously from the neutral point NE to the point of maximum travel C ***, as shown in Figure 8. The third embodiment allows an even better adaptation of the pendulum: Plus l ' X abscissa, and the DBT travel increase (which corresponds to decreasing rotation speeds), the greater the radius of curvature increases, and correlatively, the lower the OPlocal local order decreases, thus promoting a filtration of acyclisms adapted to the speed of rotation . Figures 4 to 8, described above correspond to traces to the right on the oscillating weight, that is to say at the locus of the contact points of the oscillating mass with any of the rolling elements. We also have the same characteristics, and similar curves for traces left on the mass, or traces on the right on the support, or traces left on the support. Referring now to Figures 9 and 10, which show an alternative embodiment, with respect to the pendulum partially shown in Figures 1 and 2, to prevent blockage of the rolling elements 8. Figure 10 shows an enlarged way a part of Figure 9. To avoid a possible escape of one or more rolling elements, beyond the point of maximum deflection, it has extended the raceways on the oscillating masses (here on the spacers 6) beyond points of maximum travel C (or C **, or C ***). Such a configuration can occur in particular when starting the engine, when the oscillating masses are not yet centrifuged. The extensions of the real traces correspond to the CD arcs. The radius of curvature of these extensions may advantageously be between the diameter DIA of the rolling element 8 and 1.5 times this diameter DIA.
    [0014] The oscillating masses and the cuts on the support are designed so that when the mass is in radial internal abutment (shown in FIGS. 9 and 10 by the contacts of the spacers 6 with the radially inner flat portion of the cutout (at the points T on the contour 10), the distances H1, H2, and H3 in FIG. 10 satisfy the relation: H3 = H1 - H2 <DIA, in which: H1 is the maximum radial height of the recess of the contour in which passes l spacer H2 is the maximum radial height of the spacer, and DIA is the diameter of the rolling element 8 in contact with the spacer 6. Thus, the rolling elements 8 can not, even during transient phases, escape to the right beyond the spacers 6 and lock in the straight portions of the contours 10. Referring now to Figures 11 and 12, which correspond to a fourth embodiment of the invention. 11 the trajectory the center of mass CM of the oscillating mass during the oscillation of this oscillating mass. Only the path to the right, relative to the neutral position, is represented. The direction to the right, represented by the abscissa x, is considered perpendicular to a radial direction, passing through the position of the center of mass CM in the neutral position. The ordinate axis y extends in the radial direction passing through the center of mass in the neutral position. Zone B C ** corresponds to the first range of angular deflection on the right. The area AB corresponds to the transition zone, and the area between the zero abscissa point and the point A corresponds to the second range of angular deflection to the right. FIG. 12 represents the evolution of the radius of curvature of this trajectory to the right of the center of mass CM. According to the fourth embodiment of the invention, the radius of curvature is firstly constant (in the second range of angular deflection, to point A. Then, it begins to increase, in the transition zone AB, then further increases in the first range of angular deflection, up to the point C ** of maximum deflection to the right, very preferably this curve is a portion of clothoid between the points A and point C. In particular the curve portion representing the radius of curvature R in the first angular deflection range on the right BC ** is therefore also a portion of the clothoid, which is typically the same for the evolution of the radius of curvature of the trajectory of the center of mass on the left. It has been found that this makes it possible to very greatly reduce or eliminate the risk of sliding of the rolling element 8 on the mass and / or on the support, more generally, the person skilled in the art can, without leaving the Within the scope of the invention, implement this invention according to various embodiments or variants known from the state of the art, which are compatible with the invention.
    权利要求:
    Claims (11)
    [0001]
    REVENDICATIONS1. A two-wire type torsion damping device (2) designed to be connected to a main-order explosion engine N, this device comprising a support (4) rotatable about an axis of rotation, and a set of oscillating oscillating masses movably mounted on this support (4), each oscillating mass of the assembly being able to oscillate on two rolling elements (8) associated with this oscillating mass, which are in rolling contact with the support and with this oscillating mass, each of these rolling elements determining a trace on an edge of the oscillating mass and on an edge of the support, each of these traces being associated with a pendulum displacement on the left and a pendulum movement on the right side, and other of a neutral position, characterized in that the traces on the support (4) and on each of these oscillating masses are configured so that there exists: - a first range of the deflection left-hand position, disposed beyond a position at 50% of a maximum pendulum displacement on the left, in which the local order of this set of pendular masses is bounded by a maximum value, ie G1max, at most equal to 0.99 x N, and preferably 0.98 x N; a first range of pendulum displacement to the right, disposed beyond a position at 50% of a maximum pendulum displacement to the right, in which the local order of the pendulum is limited by a maximum value, namely D1max, at most is 0.99 x N, and preferably 0.98 x N; the local order, OPIpbah of this set of pendulum masses in a position of pendulum displacement determined, left or right, being conventionally defined as follows: For any rolling element in contact with an oscillating mass, the local order , identical for each rolling element, is equal to Rg - (Rbp Rm - (rbp + rr)) OPiocal Rbp Rni - (rbp + rff,) in which: Rg is the distance between a center of mass of the oscillating mass and the axis of rotation; Rbp is the radius of curvature of the trace on the support at a point of contact with the rolling element, Rn, 'is the radius of curvature of the trace on the oscillating mass at a point of contact with the rolling element - rbp is the radius of curvature of the rolling element at a point of contact with the support, rb, is the radius of curvature of the rolling element at a point of contact with the oscillating mass.
    [0002]
    2. Device according to claim 1, wherein over the entire amplitude of the pendulum movement to the left and right, the local order is less than or equal to 0.99 x N, preferably 0.98 x N, and very preferred way belongs to the interval [0.70 N; 0, 98 N];
    [0003]
    3. Device according to claim 2, wherein over the entire amplitude of the pendulum movement to the left and right, the local order belongs to the interval [0.74 N; 0, 96 N]; and preferably belongs to the range [0.78 N; 0, 92 N].
    [0004]
    4. Device according to claim 2 or 3, wherein the local order is substantially constant over the entire pendulum swing amplitude left and right.
    [0005]
    5. Device according to claim 1, wherein the traces on the support and on each of these oscillating masses are configured so that there exists: a second range of pendulum displacement on the left extending from the neutral position, within the first left swing range, in which the local order is bounded by a minimum value of G2min, at least 0.95 N, and less than 1.10 N; a second range of pendulum displacement on the right extending from the neutral position, below the first range of pendulum displacement on the right, in which the local order is limited by a minimum value, ie D2min, at least 25; equal to 0.95 N, and less than 1.10 N And in which: G1max is less than G2min of a value of between 2% and 30% of G2min, and preferably of between 3% and 25% of G2min ; - D1max is less than D2min by a value between 2% and 30% of D2min, and preferably between 3% and 25% of D2min;
    [0006]
    6. Device according to claim 45, wherein: the first left swinging range is identical to the first right swing range relative to the neutral point; The second range of swinging movement on the left is identical to the second swing range on the right with respect to the neutral point; 10
    [0007]
    7. Device according to any one of claims 4-5 to 6, wherein: - The first left swinging range on the right, respectively, extends to a position of maximum movement to the left, respectively to the right , over a range of pendulum travel of between 10% and 49%, and preferably between 15% and 35% of an overall range of pendulum movement to the left, respectively to the right; - The second left swinging range on the right, respectively extends from the neutral position on a pendulum swing interval of between 50% and 90%, and preferably between 65% and 80% of the overall range of pendulum deflection on the left, respectively on the right; the first and the second pendulum swing range on the left, respectively on the right, being separated by a transition range for the local order, preferably a transition range with continuity of the local order;
    [0008]
    8. Device according to any one of claims 1, 5, 6, 7, wherein the local order on the left, respectively on the right, varies non-decreasingly, preferably substantially continuously, from the neutral position to the position of maximum pendulum displacement on the left, respectively on the right, so that the ratio of the local order to the point of maximum displacement on the left, respectively on the right, on the local order in the neutral position on the left, respectively neutral on the right is in the range [0.70; 0.95], and preferably in the range [0.80; 0.90].
    [0009]
    9. Device according to claim 8, wherein the local order is strictly decreasing from the neutral position to the maximum pendulum swing position to the left, or right.
    [0010]
    10. Device according to claim 9, wherein, for each oscillating weight, the curve portion representing, as a function of a direction to the left, respectively to the right, the evolution of the radius of curvature of the trajectory of the center of mass ( CM) in the first range of the pendulum displacement on the left, respectively on the right, forms a clothoid portion, the direction on the left, respectively on the right, being considered according to a perpendicular to a radial direction passing through the position of the center of mass (CM ) in the neutral position.,
    [0011]
    11. Clutch, characterized in that it comprises a torsion damping device according to any one of claims 1 to 10.
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    同族专利:
    公开号 | 公开日
    WO2015086944A1|2015-06-18|
    CN105814336B|2019-05-28|
    KR20160096088A|2016-08-12|
    FR3014519B1|2016-10-07|
    EP3080479A1|2016-10-19|
    KR102341575B1|2021-12-22|
    CN105814336A|2016-07-27|
    引用文献:
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    DE102008005138A1|2007-02-12|2008-08-14|Luk Lamellen Und Kupplungsbau Beteiligungs Kg|Centrifugal pendulum device|
    DE102011085400A1|2010-11-08|2012-05-10|Schaeffler Technologies Gmbh & Co. Kg|centrifugal pendulum|
    DE102011076790A1|2011-05-31|2012-12-06|Zf Friedrichshafen Ag|Drive system for a vehicle|
    DE102012215078A1|2011-09-19|2013-03-21|Schaeffler Technologies AG & Co. KG|centrifugal pendulum|FR3059749A1|2016-12-06|2018-06-08|Valeo Embrayages|PENDULAR DAMPING DEVICE|
    FR3064324A1|2017-03-22|2018-09-28|Valeo Embrayages|PENDULAR DAMPING DEVICE|US6318527B1|1999-12-03|2001-11-20|Sikorsky Aircraft Corporation|Inertial vibration isolator spring for helicopter|
    JP2004340170A|2003-05-13|2004-12-02|Nok Corp|Damper|
    DE502005007124D1|2004-08-11|2009-06-04|Luk Lamellen & Kupplungsbau|Torsional vibration damping device|
    DE102010046319A1|2009-09-28|2011-03-31|Schaeffler Technologies Gmbh & Co. Kg|Torsional vibration damper for damping torsional vibrations in dual mass flywheel of internal combustion engine, has energy storage elements arranged between damper parts so that one element is released when parts rotate in same direction|
    FR2981714B1|2011-10-19|2013-11-01|Valeo Embrayages|PENDULUM OSCILLATOR TYPE DAMPING SYSTEM WITH IMPROVED GUIDE DEVICE|FR3038682B1|2015-07-06|2017-07-28|Valeo Embrayages|TORSION OSCILLATION DAMPING DEVICE|
    FR3052835B1|2016-06-16|2018-06-08|Valeo Embrayages|PENDULAR DAMPING DEVICE|
    法律状态:
    2015-12-31| PLFP| Fee payment|Year of fee payment: 3 |
    2016-12-29| PLFP| Fee payment|Year of fee payment: 4 |
    2018-01-02| PLFP| Fee payment|Year of fee payment: 5 |
    2019-12-31| PLFP| Fee payment|Year of fee payment: 7 |
    2020-12-31| PLFP| Fee payment|Year of fee payment: 8 |
    2021-12-31| PLFP| Fee payment|Year of fee payment: 9 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1362299A|FR3014519B1|2013-12-09|2013-12-09|TORSION DAMPING DEVICE WITH IMPROVED FILTRATION EFFICIENCY PENDULUM|FR1362299A| FR3014519B1|2013-12-09|2013-12-09|TORSION DAMPING DEVICE WITH IMPROVED FILTRATION EFFICIENCY PENDULUM|
    CN201480067746.2A| CN105814336B|2013-12-09|2014-11-26|Swing type torsional vibration damper with improved filter efficiency|
    KR1020167015130A| KR102341575B1|2013-12-09|2014-11-26|Pendulum torsion damping device with improved effectiveness of filtration|
    EP14814964.4A| EP3080479A1|2013-12-09|2014-11-26|Pendulum torsion damping device with improved effectiveness of filtration|
    PCT/FR2014/053048| WO2015086944A1|2013-12-09|2014-11-26|Pendulum torsion damping device with improved effectiveness of filtration|
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