• 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:
    A torque fluctuation filtering mechanism comprises a secondary member (14) angularly oscillating with respect to a primary member (12) between forward (FCD) and retrograde (FCR) end-of-travel angular positions, and an energy accumulator resilient variable elastic stiffener (18) generating forces whose resultant on the secondary member (14) has no axial component, which accumulates elastic potential energy at least when the secondary member (14) s' moves in the direct direction of an intermediate angular position (R2) between the retrograde end (RCR) and forward end positions (FCD), and performs a work at least when the secondary member (14) is approaching in the retrograde direction of the angular position of inflection (R2), generating a negative angular stiffness (K2) negative between the angular positions of inflexion and direct end of travel (FCD).
    公开号:FR3031556A1
    申请号:FR1550221
    申请日:2015-01-12
    公开日:2016-07-15
    发明作者:Benoit Fleche；Roel Verhoog；Jerome Boulet
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] TECHNICAL FIELD OF THE INVENTION [0001] The invention relates to a filtering mechanism between two rotating members. PRIOR ART [0002] In order to attenuate the torque fluctuations between a heat engine and a gearbox, it is common to interpose a filtering mechanism with an elastic potential energy accumulator, and in particular a double damping flywheel having a primary flywheel and a secondary flywheel between which is interposed a resilient elastic spring energy accumulator, or a long-stroke damper having a primary flywheel, a ternary flywheel and a phasing washer forming a secondary flywheel between the primary flywheel and the ternary flywheel, a spring elastic potential energy accumulator being interposed between primary flywheel and secondary flywheel, and a second between secondary flywheel and ternary flywheel. With recent generations of engines and engines developing, there is an increase in engine torque at low speeds, which generates buzzing. Under these conditions, the performance of conventional filtering mechanisms find their limits. SUMMARY OF THE INVENTION [0004] The invention aims to overcome the drawbacks of the state of the art and to improve the filter performance when the torque is high, especially at low speed. For this purpose, according to a first aspect of the invention, a mechanism for filtering torque fluctuations around an axis of revolution, comprising: a primary member rotating about the axis of revolution, a secondary rotating member; around the axis of revolution and able to oscillate angularly with respect to the primary member in a direct direction of oscillation at least from a retrograde end-of-travel position to a direct end-of-travel angular position, and a reverse oscillation retrograde direction opposite to the direct direction of oscillation, from the direct end-of-travel angular position to the retrograde end-of-travel angular position, and a variable-stiffness elastic potential energy accumulator disposed between primary member and the secondary member so as to accumulate elastic potential energy at least when the secondary member moves in the direct direction of an angular position of inflection inte intermediate between the retrograde end position and the direct end position, and to perform a work at least 10 when the secondary member approaches in the retrograde direction of the angular position of inflection, generating an angular stiffness apparent K2 between the primary member and the secondary member, the apparent angular stiffness K2 being negative between the angular position of inflection and the angular position of direct end of stroke. In the context of the present application, it refers to the apparent angular stiffness of an energy accumulator to designate, at a given relative position 0 of the secondary member with respect to the primary member in an arbitrary reference frame. given, the slope of the function connecting said position to the algebraic torque C generated by said energy accumulator on the primary member (this torque being the opposite of the torque generated by the energy accumulator on the secondary member) . It is therefore the derivative dC (0) / d0 of the function C (0). This derivative can be constant or variable. [0006] The elastic potential energy accumulator with variable stiffness makes it possible to differentiate the stiffness for the low torques - corresponding to the small angular oscillations - and for the strong torques - corresponding to the strong angular oscillations. In this case, the stiffness characteristic chosen makes it possible to significantly and specifically reduce the stiffness for the strong torques, in the operating conditions where greater filtration is desired. Compared with a conventional filtering mechanism with constant stiffness, the device according to the invention makes it possible to reduce the stiffness over a wide operating range for the high torques, which can be obtained if necessary at the cost of an increase in the low torque stiffness. But, and this is also a teaching of the invention, the increase in stiffness in low torque or negative torque operating regimes is not disadvantageous. The potential elastic energy accumulator with variable stiffness can be achieved in different ways. In the context of the present application, the resilient variable elastic energy accumulator with variable stiffness is arranged to generate forces whose resultant on the secondary member has no axial component. The resulting mechanism is particularly compact in the axial direction. This can be achieved in particular by providing springs which are arranged and act parallel to a plane perpendicular to the axis of revolution. The elastic potential energy accumulator with variable stiffness can be of any type, and include in particular a compressed air piston, a spring box, a coil spring, and so on. According to one embodiment, the resilient potential energy accumulator 15 with variable stiffness has a guide element and a guided element cooperating with the guide element to move relative to the guide element. a guide path fixed with respect to the guide member, in a work direction to perform work and in a direction of accumulation to accumulate elastic potential energy. In this case, the elastic potential energy accumulator with variable stiffness may comprise at least one elastic potential energy storage element, preferably a mechanical or pneumatic spring acting between the guide element and the guided element. . The guide path may in particular be rectilinear. According to an alternative embodiment, the guide element is pivotally mounted on one of the primary and secondary members. More specifically, the guide member is pivotable about a pivot axis parallel to the axis of revolution. The guided element is then preferably pivotally mounted on the other of the primary and secondary members, preferably also about a pivot axis 3031556 4 parallel to that of the guide member, and preferably parallel to the axis of revolution. According to another variant embodiment, the guide element is fixedly mounted on one of the primary and secondary members, and preferably so that the guide path is radial with respect to the axis of rotation. revolution. The guided element can then form a probe equipped with a rolling roller on a cam fixed to the other of the primary and secondary members, which generates an orthoradial force component depending on the radial force and the angular position of the roller. . The accumulation of potential elastic potential energy and the restitution of elastic potential energy by the elastic potential energy accumulator with variable stiffness can be obtained by any means, and in particular by compressed air piston, control box. spring, coil spring, etc. It can in particular be made by one or more helical springs between guide element and guided element. According to a particularly advantageous embodiment, the mechanism further comprises a bidirectional elastic potential energy accumulator disposed between the primary member and the secondary member so as to accumulate elastic potential energy when the secondary organ moves away from an intermediate reference angular position between the retrograde end-of-stroke angular position and the direct end-of-stroke angular position, and to provide work when the secondary member approaches the angular reference position, in the direct direction of oscillation and in the retrograde direction of oscillation, by generating an apparent angular stiffness K1 between the primary member and the secondary member. [0015] The bidirectional elastic potential energy accumulator and the elastic potential energy accumulator with variable stiffness are placed in parallel between the primary member and the secondary member and thus have effects that add up to accumulate. elastic potential energy when the secondary member approaches the direct end position, and to provide work when the secondary member moves away from the direct end position and approaches the angular position reference and the angular position 30 of inflection, in the retrograde direction. But the overall apparent stiffness K3 of the filtering mechanism, equal to the algebraic sum of the apparent stiffnesses K1 and K2, is smaller than the positive apparent stiffness K1 between the direct end-of-travel position on the one hand and the first and second reference positions on the other hand. In this operating zone, which corresponds to significant deflections in the forward direction, and thus to high torques as encountered for example at low speeds, the overall apparent stiffness K3 of the filtering mechanism is smaller than the stiffness apparent Kl, therefore lower than the apparent stiffness of a mechanism devoid of the second energy accumulator. [0016] The reference angular position and the angular position of inflection are fixed positions, and the angular position of inflection is preferably located between the retrograde end position and the reference angular position. This ensures the benefit of the apparent negative stiffness K2 of the second energy accumulator over the entire direct stroke between the reference angular position and the direct end position. Thus, the displacement capacity of the filtering mechanism for the direct pairs is increased in the operating regimes most frequently encountered, the retrograde pairs corresponding to much less frequent and more transient situations. The bidirectional elastic potential energy accumulator and the elastic potential energy accumulator with variable stiffness are preferably arranged in such a way that the bi-directional elastic potential energy accumulator generates a return torque Cl on the secondary member and the second accumulator generates a return torque C2 on the secondary member which, in the absence of rotation of the filter mechanism, equilibrates with the return torque Cl when the secondary member is in a position intermediate static balance 25 between the retrograde end position and the reference angular position, and preferably between the retrograde end position and the angular position of inflection. According to one embodiment, the apparent angular stiffness K1 is constant or varies by less than 10% when the secondary member passes from the retrograde end position 30 to the direct end position. The first energy accumulator may in particular comprise springs, for example curved springs or straight springs, working between the primary member and the secondary member. [0019] Preferably, the apparent angular stiffness K2 has an absolute value greater than 25% and preferably greater than 40% of the absolute value of the apparent angular stiffness K1 over a portion of at least 40% and preferably greater than 40% of the absolute value. at least 50% of the stroke between the angular position of inflection and the angular position of direct end of stroke, this portion preferably including the angular position of direct end of stroke. The compensation between the apparent angular stiffness K1 positive and the negative apparent angular stiffness is therefore important, which allows a significant decrease in the apparent stiffness of the filtering mechanism, and therefore a better filtering of the fluctuations in torque and speed between the primary organ and the secondary organ. According to a particularly advantageous embodiment, the elastic potential energy accumulator with variable stiffness is arranged in such a way as to accumulate elastic potential energy when the secondary member approaches the angular position of intermediate inflection. in the direct direction, and to perform a work when the secondary member moves away from the angular position of inflection in the retrograde direction, the apparent angular stiffness K2 being positive between the retrograde end position and the angular position 20 of inflection. The elastic potential energy accumulator with variable stiffness accumulates potential energy over the entire stroke from the retrograde end position to the direct forward end position, and provides work on the entire stroke from the direct end position to the retrograde end position in the retrograde direction. In other words, it exerts on the primary member and the secondary member a torque which, at any point of the stroke between the retrograde end position and the direct end position, recalls the secondary to the retrograde end position. But this moment decreases in the second part of its course, when the secondary member moves away from the angular position of inflection, in the direct direction, while it believes in the first part of the race, when the organ is approaching the angular position of inflection, in the direct direction. The angular position of inflection 3031556 7 is a position corresponding to a maximum of the torque C2 exerted by the second energy accumulator on the secondary member to recall the latter in the retrograde direction. [0021] Preferably, the apparent angular stiffness K2 decreases continuously between the retrograde end position and the angular position of inflection in the forward direction, and preferably between the retrograde end position and the angular position of the retrograde end position. reference. Preferably, the function K2 (0) has no slope break, which is to say that its derivative dK2 (0) / d0 is itself continuous over the entire race between the end position retrograde and end position 10 of direct stroke. This results in a filter mechanism whose apparent stiffness varies according to the applied torque. When the transmitted torque is low, the elastic potential energy accumulators maintain the secondary member in an area between the retrograde end position and the reference angular position. The apparent angular stiffness K3 of the mechanism is high, the sum of the apparent angular stiffness K1 and K2. The filtering performance of the mechanism in this area is therefore low, which is not disadvantageous, since there is no need to filter low amplitude couples. When the torque transmitted in the forward direction increases, the secondary member moves away from the angular position of inflection 20 in the forward direction. The apparent stiffness of the mechanism then decreases, due to the decrease in the apparent angular stiffness of the elastic potential energy accumulator with variable stiffness. This makes it possible to very well filter the fluctuations of the torque when the average torque in the forward direction is high. According to one embodiment, the resilient elastic energy accumulator with variable stiffness is dimensioned such that when the secondary member is in a zone of angular deflection of high stiffness between the end angular position of the retrograde stroke and the angular position of inflection, the mechanism has an apparent angular stiffness which may be punctually greater than 200% to even greater than 400% of a mean stiffness Km oyen defined as the ratio between on the one hand the difference between the maximum value of the return torque in the direct end position and the negative minimum value of the torque in the retrograde end position and, on the other hand, the angular difference between the end position of the end position direct and the angular end position retrograde. When the secondary member is in a second zone of low stiffness angular deflection covering at least 40% and preferably at least 50% of the stroke between the angular position of inflection and the end angular position of direct stroke, the mechanism has an apparent angular stiffness less than 80% of the average stiffness Km oyen- This zone of low stiffness angular deflection preferably includes the angular position of direct end of stroke. According to another aspect of the invention, it relates to a transmission kinematic chain comprising a driving member, a driven member, a clutch located between the driving member and the driven member, and a filtering mechanism. as previously described, kinematically interposed between the driving member and the clutch or between the clutch and the driven member. According to another aspect of the invention, this relates to a method of filtering torque fluctuations or rotational speed between a primary member rotating around an axis of revolution and a secondary member rotating around it. the axis of revolution relative to the primary member between at least one retrograde end position and a direct end angular position 20 passing through at least one angular position of inflection, the method including: an elastic potential energy accumulation by a bi-directional elastic potential energy accumulator when the secondary member moves away from an intermediate reference angular position between the retrograde end-of-stroke angular position and the end-of-stroke angular position direct, in the direct direction of oscillation and in the retrograde swing direction, and a supply of a work by the bi-elastic potential energy accumulator directional direction when the secondary member approaches the reference angular position, in the direct direction of oscillation and in the retrograde direction of oscillation, the first accumulation of elastic potential energy and the first work supply s' performing with apparent angular stiffness K1 between the primary member and the secondary member, and a second accumulation of potential elastic energy by an elastic potential energy accumulator with variable stiffness at least when the secondary member moves away in the direct direction of an angular position of intermediate inflexion between the retrograde end position and the direct end position, and a second supply of mechanical work by the elastic potential energy accumulator with stiffness variable at least when the secondary member approaches in the retrograde direction of the angular position of inflection, the second accumulation of elastic potential energy and the second supply of work being performed with an apparent angular stiffness K2 between the primary member and the secondary member, the apparent angular stiffness K2 being negative between the angular position of inflection and the angular position of direct end of race. The method, by putting in parallel the bi-directional elastic potential energy accumulator 20 of positive stiffness, and preferably constant, K1 with an elastic potential energy accumulator with variable stiffness of stiffness K2 negative, allows on a part at least the stroke, between the angular position of inflection and the direct end position, to reduce the overall stiffness K1 + K2.
    [0002] BRIEF DESCRIPTION OF THE FIGURES [0028] Other features and advantages of the invention will emerge on reading the description which follows, with reference to the appended figures, which illustrate: FIG. 1, a schematic view of a first embodiment of a transmission kinematic chain comprising a filtering mechanism according to the invention; FIG. 2 is a diagram illustrating the evolution of the torque (scale of the left-hand ordinates) and of the stiffness (right-hand ordinate scale) as a function of the relative angle between the secondary member and the primary member of a filtering mechanism. according to the invention; FIG. 3 is a schematic view of a second embodiment of a transmission kinematic chain comprising a filtering mechanism 10 according to the invention; FIG. 4 is a schematic view of a third embodiment of a transmission kinematic chain comprising a filtering mechanism according to the invention; FIG. 5, an isometric view, partly in section, of a filter mechanism according to one embodiment of the invention; - Figure 6, a front view, partially in section, of the filter mechanism of Figure 5; - Figure 7, a sectional section intersecting planes along the broken section line A-A of Figure 6; Figure 8 is a front view of a filter mechanism according to another embodiment of the invention; FIG. 9 is a diagram illustrating the evolution of the torque as a function of the relative angle between the secondary member and the primary member of the filtering mechanism according to FIG. 8; FIG. 10, a front view of a portion of a filtering mechanism according to another embodiment of the invention, in a retrograde end-of-travel position; FIG. 11 is a sectional view with intersecting planes along the broken cross-section line B-B of FIG. 10; - Figure 12, a front of a portion of the filter mechanism of Figure 10, in an intermediate reference angular position; Figure 13 is a sectional sectional plan view along the broken section line B-B of Figure 12; - Figure 14, a front of a portion of the filter mechanism of Figure 10, in a direct end position; FIG. 15, a cross-sectional sectional view along the broken cross-section line B-B of FIG. 14; FIG. 16 is a diagram illustrating the evolution of the torque as a function of the relative angle between the secondary member and the primary member of the filtering mechanism according to FIG. 10. For the sake of clarity, the identical or similar elements are identified by 15 identical reference signs throughout the figures. DETAILED DESCRIPTION OF EMBODIMENTS [0030] FIG. 1 schematically illustrates a transmission kinematic chain 1 between a crankshaft 2 (for example a three-cylinder internal combustion engine) and an input shaft 3. a gearbox. This transmission kinematic chain 1 comprises a clutch 5 of any type, here in direct contact with the input shaft 3 of the gearbox, and a double damping flywheel 10 arranged kinematically between the crankshaft 2 and the clutch 3. , here in direct contact with the crankshaft. The double damping flywheel 10 forms a mechanism for filtering the speed and torque fluctuations between the crankshaft 2 and the clutch 5, and comprises a primary rotating member 12 constituting a primary flywheel, a secondary rotating member 14 constituting a secondary flywheel, and a bi-directional resilient potential energy store 16 and a variable elastic resilient energy store 30 variable 18 disposed in parallel between the primary rotating member and the secondary rotating member. Remarkably, the elastic potential energy accumulator with variable stiffness 18 has a variable stiffness, as will be explained later. The double damping flywheel rotates about an axis of revolution 100 which is also the axis of revolution of the crankshaft, the clutch and the input shaft of the gearbox. A starter (not shown) can also be engaged with the primary member 12 of the double damping flywheel 10. Finally, the double damping flywheel 10 can also include fluid or solid friction energy dissipation members (not shown). disposed between the primary rotating member 10 and the secondary rotating member. In the diagram of Figure 2 have been plotted on the abscissa the current angular position of the secondary member 14 relative to the primary member 12 about the axis of revolution 100, between a retrograde end position position FCR, here -20 °, and a direct limit position FCD, here 100 °, and ordinate 15 different characteristic quantities of the filter mechanism, namely on the left scale the torque (in Nm) and on the right scale the stiffness (in Nm / s2). In practice, the direct end position positions FCD and retrograde limit switch FCR may be materialized by stops disposed between the primary member 12 and the secondary member 14, or by stops specific to one of the accumulators d. energy, for example by contacting turns of a helical spring with each other. The torque curve C1 of the bidirectional elastic potential energy store represents the resulting torque applied to the secondary member 14 by the first potential energy store 16, depending on the position of the secondary member 14. relative to the primary member 12. This curve is substantially linear, of positive slope between the retrograde end position and the direct end position, and crosses the abscissa axis to an intermediate position R1 (+ 40 °) located angularly midway between the end positions. This intermediate position R1 will be designated in the following reference angular position. The first potential energy accumulator 16 allows angular deflection of the same magnitude (60 °) on either side of this equilibrium position R1. The torque Cl, in the range between the reference angular position R1 3031556 13 and the direct end position FCD, is positive and tends to bring the secondary member in the retrograde direction towards the reference angular position R1. In the range between the reference angular position R1 and the retrograde end position FCR, the torque Cl is negative and tends to return the secondary member 5 in the direct direction to the reference angular position R1. At any point in the operating range between the two end-of-travel angular positions, the torque Cl is proportional to the deformation of the springs, therefore to the angular distance relative to the reference angular position R1, and the proportionality factor. constitutes the overall stiffness K1 of the bidirectional elastic potential energy store 10. The curve constituting the derivative of the curve C1 with respect to the angular position is plotted on the diagram of FIG. 2, the corresponding ordinates being plotted on the right scale in the figure. This curve is a horizontal line segment, because K1 is here constant. The torque curve C2 of the elastic potential energy accumulator with variable stiffness 18 represents the resulting torque applied to the secondary member 14 by the elastic potential energy accumulator with variable stiffness 18, as a function of the position of the secondary member 14 relative to the primary member 12. The resilient variable elastic energy accumulator 18 is active throughout the race between the retrograde end position FCR and the end position 20 FCD direct racing. On the entire race between the retrograde end position FCR and the direct end position FCD, the elastic potential energy accumulator with variable stiffness 18 tends to recall the secondary member 14 to the position of Retrograde limit switch FCR, so that the curve C2 takes ordinate positive values over the entire operating range. The value of the torque C2, however, varies non-linearly over the operating range, increasing continuously from a first minimum value, here a zero value, in the retrograde end-of-travel position FCR, to a maximum value corresponding to an angular position. R2, hereinafter referred to as the angular position of inflection, then decreasing continuously from this maximum value to a second minimum value, here also zero, reached in the direct end position position FCD. The angular position 3021556 14 of inflection R2 is here positioned between the retrograde end position FCR and the reference angular position R1. The resultant of the combined action of the bi-directional elastic potential energy accumulator 16 and the elastic potential energy accumulator with variable stiffness 18 is illustrated by the curve C3 = C1 + C2. This curve crosses the abscissa axis at a point defining a PES stable equilibrium position for the positioning of the secondary member relative to the primary member under the combined stress of the two elastic potential energy accumulators. The stable equilibrium position PES is necessarily located between the position R1 and the retrograde end position. It is further located here between the retrograde end position FCR and the angular position of inflection R2. The curve K1 of FIG. 2 represents the equivalent stiffness introduced by the bi-directional elastic potential energy accumulator 16, which is the derivative dC1 / d0 of the torque C1 relative to the angular position, the corresponding ordinates being carried. on the right scale. This curve K1 is parallel to the abscissa axis, reflecting the fact that the stiffness K1 is constant. The constant value K1 also defines a value said in the context of the present application "average value", which is the ratio between, on the one hand, the difference of the torque values at the end of direct and retrograde end positions, and on the other hand From the angular difference between the direct and retrograde end positions: CMax - CMin = KMoyen = K1 ° FCD - ° FCR [0037] The curve K2 of Figure 2 represents the derivative of curve C2 with respect to the position angular. As can be seen, this derivative is positive between the retrograde end position FCR and the angular position of inflection R2, and then negative between the angular position of inflection R2 and the direct end position 25. The bi-directional elastic potential energy accumulator 16 and the resilient variable elastic energy accumulator 18 are arranged in parallel between the primary member 12 and the secondary member 14 of the filtering mechanism 10. The stiffness K3 resulting from the combined action of the two accumulators is therefore the sum of the stiffness K1 and K2. As illustrated in FIG. 2, the stiffness K3 is less than K1 over the entire portion of the operating range corresponding to negative values of K2, therefore between the angular position of the inflection R2 and the direct end position of the travel FCD. . dC Cma, - Cmin K3 (0) = G = 'Medium = uu uFCD ° FCR when ° R2 <61 <FCD [0039] It follows that in this operating zone, which corresponds to significant deflections in the forward direction, so at high torques as we meet them for example at low speed, the overall apparent stiffness K3 of the 10 filtering mechanism 10 is lower than the apparent stiffness K1, therefore lower than the apparent stiffness of a mechanism without the second energy accumulator 18. It can also define a low-angle angular deflection region covering at less than 50% of the stroke between the angular position of the inflection R2 and the angular position of the direct limit switch FCD, in which the mechanism has an apparent angular stiffness K3 of less than 80% of the average stiffness K1. In this case, this is true here in particular between the reference angular position R1 and the direct end position FCD. This advantageous reduction in the overall apparent stiffness resulting for the high torques is obtained at the cost of an increase in the stiffness in the operating zone between the retrograde end position and the angular position of inflection. In this region of high stiffness angular deflection, the mechanism has an apparent angular stiffness K3 (0) reach values greater than 200%, or in practice greater than 400% of the average stiffness KMoyen- But the increase in stiffness in this angular zone is not penalizing insofar as the corresponding pairs are weak. The same advantages on the filtration of high torque in the forward direction can be obtained in different configurations of the kinematic chain. FIG. 3 illustrates the integration of a filtering mechanism 10 according to the invention constituting a double damping flywheel positioned between the crankshaft 2 and a double clutch 5 situated upstream of a two-speed gearbox. input shafts 3.1 and 3.2. FIG. 4 illustrates the integration of a filter mechanism according to the invention with a torque converter 1 interposed between a crankshaft 2 and a gearbox input shaft 3. This converter In a manner known per se, a torque converter comprises a hydrokinetic converter 4 and a locking clutch 5 arranged in parallel between the crankshaft 2 and an input member 12 of a long-stroke damper 6 incorporating a fluctuation filtration mechanism. of the pair 10 according to the invention. More specifically, the long-stroke damper 6 comprises an intermediate secondary member 14 called a phasing washer and a ternary integral member 15 integral with the input shaft of the gearbox 3. The intermediate phasing member 15 is connected to the input member 12 by a bi-directional elastic potential energy accumulator 16 of constant stiffness K1 and, in parallel, by an elastic potential energy accumulator with variable stiffness 18 with variable stiffness K2. Furthermore, the intermediate phasing member 15 is connected to the ternary member 15 by an elastic potential energy accumulator 17. In this configuration also, it improves the filtration of the high value couples in the forward direction by providing that the stiffness K2 is negative over a substantial portion of the angular travel of the secondary member 14 relative to the primary member 12. [0043] Various embodiments of the invention will now be described structurally. FIGS. 5 to 7 show a first embodiment of a double damping flywheel 10 incorporating the filtering mechanism according to the invention and that can be used in particular in the configurations of FIGS. 1 and 3. The primary member 12 here consists essentially of two guide rings 12.1, 12.2 fixed to each other and integral with a drive ring 12.3 for meshing with a pinion (not shown) starter. One of the guide washers 12.2 is integral with a rocket 12.4 supporting an inner ring of a bearing 20 for guiding the secondary member. The outer race of the bearing is attached to a massive secondary flywheel 14.1, to which is attached a sail 14.2 extending between the two guide washers 12.1, 12.2. The guide washers 12.1, 12.2, comprise housing 12.5 delimited by support faces for accommodating coil springs 16.1, curved in a circular arc 5 in the volume defined by the guide rings 12.1, 12.2. The secondary web 14.2 has meanwhile radial arms 14.3, which interferes with the ends of the springs 16.1, so that each spring 16.1 is at one end bearing against a bearing face formed on the guide rings 12.1, 12.2 of the primary member 12, and the end opposite one of the arms 14.3 of the secondary veil 14.2. The number of springs 16.1 may vary depending on the chosen architecture. Between the primary member 12 and the secondary member 16 is disposed a mechanism with two cams 18.1 and two pushers 18.2 roller each associated with one of the cams 18.1, this mechanism constituting the potential energy accumulator 15 variable elastic stiffness 18. Each plunger 18.2 has a roller 18.21 fixed to the secondary flywheel 14.1 and having a thrust axis 200 radial to the axis of revolution, serving as an external guide element to a coil spring 18.22 and a guided element consisting of a roll holder 18.23 pushed radially inwards by the spring 18.22. The roll holder carries a roll 18.24 which rolls on the cam 18.1 formed on the guide washer 12.1 of the primary 12. The two cams 18.1, only one of which has been illustrated in the figures, have identical profiles and are symmetrical to the the roller pushers 18.2 are also diametrically opposed, so that the contributions of the two pushers 18.2 are identical and add up in all the angular positions of the secondary 14 by relative to the primary 12. The springs 16.1 together constitute the bi-directional elastic potential energy accumulator 16, which has an equilibrium position in which the couples exerted by the springs 16.1 on the secondary member 14 30 oppose and balance each other. This equilibrium position corresponds to the reference angular position R1 of FIG. 2. On either side of this position of reference R1, the two springs 16.1 allow an angular deflection of 60 °, ie an end position. stroke in a forward direction FCD at + 100 ° and a limit position in the retrograde direction FCR at -20 °. In each end position, direct or retrograde, the turns of the springs 16.1 are joined, and constitute a positive stop for the mechanism. The resulting torque applied to the secondary member 14 by the bi-directional resilient potential energy accumulator 16 follows the curve C1 of FIG. 2 as a function of the position 0 of the secondary member 14 with respect to the primary member 12. At any point 0 of the operating range between the two end-of-travel angular positions, the torque Cl is proportional to the deformation of the springs, and therefore to the angular distance (0 - OR!) With respect to the angular position of the reference OR !, and the proportionality factor constitutes the constant global stiffness K1 of the bidirectional elastic potential energy store. The cam and push mechanism 18 constitutes the elastic potential energy reservoir 15 with variable stiffness in parallel with the bidirectional resilient potential energy accumulator 16. For each angular position 0 of the secondary 14 relative to the primary 12 , the radial force of the springs 18.22 of the roller pushers 18.2 is transferred to the primary 12 with an orthoradial component defining a torque C2 around the axis of revolution, this component being a function of the spring tension and the angle of rotation. the cam in the angular position 0 considered. A torque of the same amplitude and of opposite direction is transmitted to the secondary by means of the cylinders 18.21 for guiding the springs 18.22. The retrograde end position FCR corresponds to a maximum compression of the springs 18.22 pushers 18.2, and the end position of 25 direct stroke FCD to a maximum extension of the springs 18.22. The angle between, on the one hand, the tangent to the surface of each cam 18.1 at the point of contact with the associated roller 18.24, and, on the other hand, a plane perpendicular to the axis of revolution 100 is zero in the end positions of direct race FCD and retrograde FCR. Between these two positions, the angle varies continuously, but without changing sign, so that the springs 18.24 continuously discharge from the direct end position FCD to the retrograde end position FCR. These continuous variations in the angle of the tangent to the point of contact and in the spring tension result in a continuous variation of the transmitted torque, which passes through a maximum in the angular position of inflection R2. The profile of the cam can thus be adapted, taking into account the diameter of the roller 18.24, so that the resulting torque C2 follows the curve of FIG. 2. [0050] FIG. 8 shows a double damping flywheel according to a variant of the mechanism of Figures 5 to 7, and intended to be incorporated, as the previous, a kinematic transmission chain of one of the types shown in Figures 1 and 3. The primary 12 is formed as for the previous embodiment 10 by guide washers, only one 12.1 has been shown, and between which is disposed a secondary web 14.2. A bi-directional elastic potential energy accumulator 16 consists, as in the first embodiment, of two curved coil springs 16.1 disposed between the guide washers and the web 14.2. [0051] On the guide ring 12.1 are formed two cams 18.1 turned radially inwards, symmetrical to each other with respect to the axis of revolution 100. The sail 14.2 is equipped with two opposed radial pushers 18.2, each associated with one of the cams 18.1. Each pusher 18.2 comprises a guide element constituted by a cylinder 18.21 whose axis 300 is radial with respect to the axis of revolution 100, acting as a guide for a compression spring preferably associated with a guided element constituted by a piston guide (not shown) sliding in the cylinder 18.21. The outer radial end of the pusher 18.2 is equipped with a roller 18.24, which bears against the associated cam 18.1. The two pushers 18.2 associated with the two cams 18.1 constitute a resilient variable elastic energy store with variable stiffness 18 in parallel with the bidirectional elastic potential energy store 16. The direct end position FCD corresponds to a maximum compression of the springs, and the retrograde end position FCR to a maximum extension of the springs. The angle between the tangent of each cam 18.1 at the point of contact with the associated roller 18.24 and the radial direction relative to the axis of revolution 100 varies depending on the angle between the secondary member 14 and the member This angle is a right angle in the retrograde end position, so that the force exerted by the pusher on the cam in this position is purely radial and generates no torque around the axis. of revolution. The same goes for the retrograde end position. Between the two end positions, the face of the cam 18.1 is always oriented so that the action of the pushers urges the mechanism towards the retrograde end position FCR and varies continuously. Continuous variation of the angle of the tangent at the point of contact and the concomitant variation of the tension of the springs 18.24 results in a continuous variation of the torque transmitted to the primary member 12 and the opposite torque transmitted to the secondary member 14 FIG. 9 illustrates, as a function of the angular position 0 of the secondary web 14.2 with respect to the guide ring 12.1 of the primary, the torque Cl due to the first energy accumulator 16, the pair C.sub.2 due to the second energy accumulator 18 and the resulting torque C3 = C1 + C2. The angle of the cam varies so that curve C2 passes through a maximum in an angular position of inflection R2, which in this example is substantially coincidental with R1. In the operating range between the intermediate reference position R2 and the direct end position FCD, the equivalent stiffness introduced by the second elastic energy accumulator 18 is negative, and the apparent stiffness resulting from the double damping flywheel, which is the derivative of the torque curve C3 = C1 + C2 is smaller than the stiffness of the first elastic energy accumulator. Figures 10 to 15 is illustrated a filter mechanism 10 according to a third embodiment of the invention, this time integrated with a long-stroke damper 6 according to the configuration of Figure 4. The primary member 12 here essentially consists of two guide rings 12.1, 12.2 fixed to one another. The guide washers 12.1, 12.2 are integral with a ring 12.3 slidably mounted on a hub 15.1 so as to rotate about the axis of revolution 100 relative to the hub. The hub 15.1 is integral with a web 15.2 extending between the two guide rings, and forms with the web 15.2 the ternary member 15 of Figure 4. A phasing washer 14.1, forming a secondary member 14 kinematically interposed between primary 12 and ternary 15, is also mounted between the guide washers 12.1, 12.2, so as to rotate about the axis of revolution 100, both with respect to the guide washers 12.1, 12.2 of the primary 12 and relative to the web 15.2 of the ternary 15. The guide washers 12.1, 12.2 are perforated by windows 12.5 5 for accommodating spiral springs 16.1, 17.1, curved in an arc in the volume defined by the washers of guidance 12.1, 12.2. The coil springs 16.1, 17.1 belong to two groups. A first group 16.1 operates between the guide washers 12.1, 12.2 and arms 14.3 of the phase 14.1 phasing washer 14, while the second group 17.1 works between the arms 14.3 of the phasing washer 14.1 and arms 15.3. ternary veil 15.2. Each spring of the first group is at one end bearing against a rim 12.6 of one of the windows 12.5 of the guide washers 12.1, 12.2 of the primary member 12, and the end opposite to on a bearing surface of one of the arms 14.3 of the phasing washer 14.1. Each spring 17.1 of the second group is at one end 15 bearing against an arm 14.3 of the phasing washer 14.2, and the opposite end against one of the arms 15.3 of the secondary web. In the illustrated example, each group 16, 17 comprises three pairs of springs 16.1, 17.1, each pair comprising a curved outer spring and an inner spring housed in the outer spring so as to work in parallel with the outer spring over the entire race. angular deflection between the end positions. The springs 16.1 of the first group work in parallel, as well as the springs 17.1 of the second group, and the springs 16.1 of the first group are in series with the springs 17.2 of the second group. It follows from this provision that when the veil 15.2 of the ternary rotates 25 relative to the guide washers 12.1, 12.2 of the primary around the axis of revolution 100 between two ternary end positions, the phasing washer 14.1 has an angular stroke relative to the guide washers 12.1, 12.2 of the primary, on both sides of a reference position R1 corresponding to the balance of the torque resulting from the action of the springs 16.1 of the first group on the 30 phasing washer 14.1 and the antagonistic torque resulting from the action of the springs 17.1 of the second group on the phasing washer 14.1. The two groups of 3031556 22 springs are preferably identical, so that this reference position R1 is located midway between a retrograde end of travel position FDR and a direct end position FCD of the phasing washer 14.1 relative to the guide washers 12.1, 12.2 of the primary. Moreover, the fact that the springs 16.1, 17.1 of the two groups are identical also has the consequence that the amplitude of the angular stroke of the secondary 14 relative to the primary 12 is half the amplitude of the angular stroke between ternary In practice, for an angular stroke between ternary and primary of ± 30 °, the angular stroke of the phasing washer 14.1 relative to the primary 12 is ± 15 ° 10 only. Between the primary member 12 and the secondary member 14 are articulated jacks or telescopic rods 118, here three in number. Each telescopic link comprises a guide element consisting of a cylindrical housing 118.1 articulated with respect to the secondary phasing washer 14.1 around an oscillation axis 14.10 parallel to the axis of revolution, a guided element constituted by a piston 118.2 sliding in the housing 118.1 and hinged to the primary guide ring 12.1 about an axis of oscillation 12.10 parallel to the axis of revolution 100 and a compressible fluid 118.3 compressed in the cylindrical housing 118.1 and urging the housing 118.1 and the piston 118.2 so as to move the oscillation axes 12.10, 14.10 away from one another to an extended position. When the angle between primary 12 and secondary 14 varies, each telescopic rod 118 extends or retracts pivotally relative to the primary 12 and the secondary 14, the movement of the telescopic rods 118 being planar, that is to say always parallel to the same plane perpendicular to the axis of revolution 100. It is thus possible to define for each telescopic rod 118, in a plane perpendicular to the axis of revolution 100, a rod axis 118.10 which is secant with the two axes of oscillation 12.10, 14.10. The first group of coil springs 16.1 constitutes a bi-directional elastic potential energy store between the guide washers 12.1, 12.2 of the primary 12 and the phase washer 14.1, which has an equilibrium position in which the stresses exerted by the springs of the first group on the secondary phasing washer oppose and balance each other. This equilibrium position is illustrated in FIGS. 12 and 13 and corresponds to the reference angular position R1 of FIG. 2. On either side of this equilibrium position, the springs 16.1 allow an angular deflection of 15 °. ie, a limit position in a direct direction FDC at + 15 ° illustrated in Figs. 14 and 15 and a limit position in the backward direction at -15 °, illustrated in Figs. (not shown) ensure the end of the race. In the diagram of FIG. 16, the current angular position of the secondary member 14 with respect to the primary member 12 around the axis of revolution has been plotted in a manner similar to FIG. 2. , between the retrograde end position FCR, here -15 °, and the direct end position FCD, here + 15 °, and on the ordinate the torque (in Nm). The resulting torque applied to the secondary member 14 by the bi-directional elastic potential energy accumulator 16 constituted by the springs 16.1 of the first group, follows the curve C1 of FIG. 17 as a function of the position of the secondary member 14 relative to the primary member 12. At any point in the operating range between the two end-of-travel angular positions, the torque Cl is proportional to the deformation of the springs 16.1, and therefore to the angular distance from each other. at the angular position of reference R1, and the proportionality factor constitutes the overall stiffness K1 of the bi-directional elastic potential energy accumulator 16. The three telescopic rods 118.1 together constitute the elastic potential energy accumulator at variable stiffness 18 of FIG. 4, in parallel with the bi-directional resilient potential energy accumulator 16. The direct end-of-travel position FCD i 11 and 15 correspond to a maximum contraction of the telescopic rods 118.1 and to a maximum compression of the compressible fluid 118.3, therefore to a maximum of elastic potential energy, and the retrograde end position FCR of FIGS. 10 and 11 at a maximum extension of the telescopic rods 118.1 and an expansion of the compressible fluid 118.3, therefore to a minimum of elastic potential energy. In the direct end position FCD, the axes 118.10 of the telescopic rods 3031556 24 118.1 are oriented radially, so that the resulting forces at the phasing washer 14.1 and the guide washers 12.1, 12.2 engender no torque around the axis of revolution 100. In the retrograde end position FCR on the contrary, the angle of the rods 118.10 is favorable to the transmission 5 of a couple, but it is low or zero because the compressible fluid 118.10 is expanded and the rods 118.1 are at the end of extension stroke. Between the two extreme positions, the torque generated by the telescopic rods 118.1 on the primary 12 and on the secondary 14 varies, depending on the compression of the compressible fluid 118.3 and the orientation of the rod axes 118.10, but always solicits the filter mechanism 10 to the retrograde end position FCR. By sizing the amount of compressible fluid, the surface area and the stroke of the piston 118.2, a torque curve C2 having the characteristic illustrated in FIG. 17 can be obtained, passing through a maximum in an intermediate position of reference R2 situated between the position of Retrograde limit switch FCR and the first intermediate reference position R1. As a result, as discussed with regard to FIG. 2, the second energy accumulator 18 constituted by the telescopic rods 118.1 has a negative apparent stiffness K2 on the portion of the stroke between the angular position of the inflection R2 and the position FCD direct limit switch with the beneficial effects on the damping of the strong couples discussed above. It should be noted that in the embodiment of FIGS. 10 to 15, the compression chambers formed between the cylindrical housings 118.1 and the pistons 118.2 can be connected to a given fixed volume reservoir, for the case where appropriate to increase the active volume of compressible fluid. As a variant, it is also possible to use an incompressible fluid and a reservoir with elastically deformable walls. It is also possible to replace the articulated cylinders with telescopic rods containing a spring, for example a spring working in compression. Of course, many other variations are possible. In all embodiments, it is possible to choose for the second elastic energy accumulator compressible fluid cylinders or springs, which may be helical or not, variable pitch or not. Other elastic elements are also conceivable, in particular elements combining a non-compressible fluid and a chamber of variable volume according to an elastic law. It is also possible to combine compressible fluid elements and spring elements. The different structures illustrated for the second elastic energy accumulator are interchangeable and can be used both for dual damping flywheels and for long-stroke dampers. The mechanisms and the filtering method according to the invention can be implemented with kinematic transmission chains which differ from those illustrated in FIGS. 1 to 4. For example, it is possible to envisage use in installations without clutch 5. [ 0064] The first elastic energy accumulator does not necessarily have a constant stiffness characteristic K1. In particular, it may have a stiffness characteristic which decreases with the increase in deflection relative to the reference angular position R1, which has an additional beneficial effect on the overall characteristic of the filtering mechanism.
    权利要求:
    Claims (2)
    [0001]
    REVENDICATIONS1. Mechanism for filtering torque fluctuations around an axis of revolution (100), comprising: a primary member (12) revolving around a revolution of revolution, a secondary member (14) rotating around the axis of revolution (100) and capable of oscillating angularly with respect to the primary member (12) in a direct direction of oscillation at least from a retrograde end-of-travel angular position (FCR) to a direct end-of-travel angular position (FCD) , and in a retrograde direction of oscillation opposite to the direct direction of oscillation, from the direct end-of-travel angular position (FCD) to the retrograde end-of-travel angular position (RCR), and characterized in that the mechanism comprises furthermore: a variable elastic resilient energy accumulator (18) disposed between the primary member (12) and the secondary member (14) so as to accumulate elastic potential energy at least when the organ secondary (14) moves away in the direction directly from an angular position of inflection (R2) intermediate between the retrograde end position (RCR) and the direct end position 20 (FCD), and to perform a work at least when the secondary member ( 14) approaches in the retrograde direction of the angular position of inflection (R2), by generating an apparent angular stiffness K2 between the primary member and the secondary member, the apparent angular stiffness K2 being negative between the angular position of inflection and the direct end-of-travel angular position, the resilient variable-elastic energy accumulator (18) being arranged to generate forces, the resultant of which on the secondary member (14) does not have axial component. 30
    [0002]
    2. Filtering mechanism according to claim 1, characterized in that the resilient variable elastic energy accumulator (18) is arranged to accumulate elastic potential energy when the secondary member (14) is 3031556 273 4. approximates the intermediate angular position (R2) in the forward direction, and performs a work when the secondary member (14) moves away from the angular position of in the retrograde direction (R2), the apparent angular stiffness K2 being positive between the retrograde end position (RCR) and the angular position (R2). Filtering mechanism according to the preceding claim, characterized in that the apparent angular stiffness K2 decreases continuously between the retrograde end position (RCR) and the second reference angular position (R2) in the forward direction. Filtering mechanism according to one of the preceding claims, characterized in that the variable elastic resilient energy accumulator (18) comprises a guide element (18.21, 118.1) and a guided element (18.23, 118.2), cooperating with the guide member (18.21, 118.1) to move relative to the guide member (18.21, 118.1) on a fixed guide path (200, 300, 118.10) relative to the guide member ( 18.21, 118.1), in a working direction to perform work and in a direction of accumulation to accumulate elastic potential energy. Filtering mechanism according to the preceding claim, characterized in that the resilient variable elastic energy accumulator (18) comprises an elastic potential energy storage element, preferably a mechanical spring (18.22) or a pneumatic spring (118.3 ) acting between the guide element (18.21, 118.1) and the guided element (18.23, 118.2). Filtering mechanism according to any one of claims 4 or 5, characterized in that the guide path (200, 300, 118.10) is rectilinear. Filtering mechanism according to any one of claims 4 to 6, characterized in that the guide element (118.1) is pivotally mounted on one of the primary and secondary members. A filter mechanism according to claim 7, characterized in that the guide member (118.1) pivots about a pivot axis (14.10) parallel to the axis of revolution (100). The filtering mechanism according to any one of claims 7 or 8, characterized in that the guided element (118.2) is pivotally mounted on the other of the primary and secondary members. 10. Filtering mechanism according to any one of claims 4 to 6, characterized in that the guide element (18.21) is fixedly mounted on one of the primary and secondary members. 11. Filtering mechanism according to claim 10, characterized in that the guide path (200, 300) is radial with respect to the axis of revolution. 12. Filtering mechanism according to any one of claims 10 or 11, characterized in that the guided element (18.23) cooperates with a cam (18.1) attached to the other of the primary and secondary members. 13. Filtering mechanism according to any one of the preceding claims, characterized in that it further comprises: a bidirectional elastic potential energy accumulator (16) disposed between the primary member (12) and the secondary member ( 14) to accumulate elastic potential energy when the secondary member (14) moves away from a reference angular position (R1) intermediate the retrograde end position (RCR) and the angular position of direct limit switch (FCD), and to provide a work when the secondary member approaches the angular position of reference (R1), in the direct direction of oscillation and in the retrograde direction of oscillation, generating a stiffness apparent angular K1 between the primary member and the secondary member, 14. Filter mechanism according to claim 13, characterized in that the angular position of inflection (R2) is located between the angular position Retrograde end of stroke (RCR) and reference angular position (R1). 15. The filtering mechanism as claimed in claim 13, characterized in that the bidirectional elastic potential energy accumulator (16) generates a return torque C1 on the secondary member (14) and variable elastic resilient energy accumulator with variable stiffness (18) generates a return torque C2 on the secondary member (14) which, in the absence of rotation of the mechanism, equilibrates with the return torque C1 when the secondary member is in a static equilibrium position (PES) intermediate the retrograde end position (RCR) and the reference angular position (R1), and preferably between the retrograde end position (FCR) ) and the angular position of inflection (R2). 16. Filtering mechanism according to any one of claims 13 to 15, characterized in that the apparent angular stiffness K1 is constant or varies less than 10% when the secondary member (14) passes from the end position of 20 retrograde stroke (FCR) at the direct end position (FCD). 17. Filtering mechanism according to any one of claims 13 to 16, characterized in that the apparent angular stiffness K2 has an absolute value greater than 25% and preferably greater than 40% of the absolute value of the apparent angular stiffness. K1 over a portion of at least 40% and preferably at least 50% of the stroke between the angular position of inflection (R2) and the angular position of direct end of travel (FCD). 18. Filtering mechanism according to claim 17, characterized in that the portion of the stroke between the angular position of inflection (R2) and the angular position of direct end of travel (FCD) includes the angular position of end of stroke. direct (FCD). 19. A filter mechanism according to any one of claims 13 to 18, characterized in that the bi-directional elastic potential energy store (16) comprises springs (16.1) working between the primary member (12). and the secondary organ (14). 20. Kinematic transmission chain comprising a driving member, a driven member, a clutch located between the driving member and the driven member, characterized in that it further comprises a filtering mechanism according to any one of the claims. previous, kinematically interposed between the driving member and the clutch or between the clutch and the driven member. 15
    类似技术:
    公开号 | 公开日 | 专利标题
    EP2607743B1|2015-02-25|Damping device withfriction damping means.
    EP3063431B1|2017-10-25|Mechanism for filtering torque fluctuations of a secondary member
    FR3031556A1|2016-07-15|FILTRATION MECHANISM FOR VARIABLE RAINFIT TORQUE FLUCTUATIONS
    FR2846369A1|2004-04-30|I.c. engine with variable compression ratio has unidirectional clutch between supporting shaft and engine housing
    WO2017072338A1|2017-05-04|Vibration damper
    EP1653053B1|2012-02-22|Two stiffness device for assembling a bearing on the shaft of a rotary engine
    EP0446091A1|1991-09-11|Rotary shock absorber with viscous fluid
    EP3377743A1|2018-09-26|Variable compression ratio engine
    EP0360350A1|1990-03-28|Fluid film bearing and method of making the same
    FR3013414A1|2015-05-22|IMPROVED PULLEY TORSION DAMPING DEVICE
    WO2018055317A1|2018-03-29|Filtering mechanism between two rotating parts
    FR3043155A1|2017-05-05|VIBRATION ABSORBER, DAMPING MECHANISM AND ASSOCIATED PROPULSION ASSEMBLY
    FR3031555A1|2016-07-15|MECHANISM FOR FILTRATION OF TORQUE FLUCTUATIONS
    EP3685071A1|2020-07-29|Torsional vibration damper with a main damper and an additional damper
    FR3020848A1|2015-11-13|MECHANISM FOR FILTRATION OF TORQUE FLUCTUATIONS OF A SECONDARY ORGAN
    FR3046440B1|2019-07-05|AUBES BLOW MODULE WITH VARIABLE SHIFT FOR A TURBOMACHINE
    WO2015173086A1|2015-11-19|Mechanism for filtering torque fluctuations
    WO2019058057A1|2019-03-28|Torsional vibration damper with a main damper and an additional damper
    FR3046433A1|2017-07-07|AUBES BLOW MODULE WITH VARIABLE SHIFT FOR A TURBOMACHINE
    FR3046432A1|2017-07-07|AUBES BLOW MODULE WITH VARIABLE SHIFT FOR A TURBOMACHINE
    FR3049019A1|2017-09-22|CAM PATH TORSION FILTRATION MECHANISM
    FR2659407A1|1991-09-13|Rotary damper with viscous fluid
    FR3012554A1|2015-05-01|MECHANISM FOR FILTRATION OF TORQUE FLUCTUATIONS OF A SECONDARY ORGAN
    FR3062188A1|2018-07-27|BALANCING ARRANGEMENT AND BALANCING SYSTEM FOR BALANCING AN INTERNAL COMBUSTION ENGINE
    FR3053424A1|2018-01-05|TORSION DAMPER
    同族专利:
    公开号 | 公开日
    FR3031556B1|2018-05-25|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE3926384A1|1989-08-10|1991-02-14|Fichtel & Sachs Ag|Torsional oscillation damper in vehicle drive-line - has input and output part, with two torsional spring arrangements and stops|
    WO2006053525A1|2004-11-20|2006-05-26|Luk Lamellen Und Kupplungsbau Beteiligungs Kg|Torsional vibration damper|
    DE102007014308A1|2006-04-15|2007-10-18|Luk Lamellen Und Kupplungsbau Beteiligungs Kg|Torsional vibration damper e.g. split flywheel, has input part, is connected in rotationally fixed manner to drive shaft of internal combustion engine and other energy storage device consists of magnetic device|
    DE102012221269A1|2011-12-14|2013-06-20|Schaeffler Technologies AG & Co. KG|Torque transmission device for use in powertrain of motor car, has spring unit for interconnecting with another spring unit to flatten portion of spring curve that works between sides against spring curve of latter spring unit|WO2018055317A1|2016-09-26|2018-03-29|Valeo Embrayages|Filtering mechanism between two rotating parts|
    WO2019122638A1|2017-12-21|2019-06-27|Valeo Embrayages|Torque transmission device|
    FR3075904A1|2017-12-21|2019-06-28|Valeo Embrayages|TORQUE TRANSMISSION DEVICE|
    法律状态:
    2016-02-01| PLFP| Fee payment|Year of fee payment: 2 |
    2016-07-15| PLSC| Publication of the preliminary search report|Effective date: 20160715 |
    2017-01-31| PLFP| Fee payment|Year of fee payment: 3 |
    2018-01-31| PLFP| Fee payment|Year of fee payment: 4 |
    2020-01-31| PLFP| Fee payment|Year of fee payment: 6 |
    2021-01-28| PLFP| Fee payment|Year of fee payment: 7 |
    2022-01-31| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1550221A|FR3031556B1|2015-01-12|2015-01-12|FILTRATION MECHANISM FOR VARIABLE RAINFIT TORQUE FLUCTUATIONS|
    FR1550221|2015-01-12|FR1550221A| FR3031556B1|2015-01-12|2015-01-12|FILTRATION MECHANISM FOR VARIABLE RAINFIT TORQUE FLUCTUATIONS|
    DE102016100450.2A| DE102016100450A1|2015-01-12|2016-01-12|Mechanism for filtering torque fluctuations|
    [返回顶部]