EP3183470A1 - Pendule centrifuge et système d'entraînement muni d'un tel pendule centrifuge - Google Patents

Pendule centrifuge et système d'entraînement muni d'un tel pendule centrifuge

Info

Publication number
EP3183470A1
EP3183470A1 EP15766390.7A EP15766390A EP3183470A1 EP 3183470 A1 EP3183470 A1 EP 3183470A1 EP 15766390 A EP15766390 A EP 15766390A EP 3183470 A1 EP3183470 A1 EP 3183470A1
Authority
EP
European Patent Office
Prior art keywords
pendulum
section
angle
track
predefined
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP15766390.7A
Other languages
German (de)
English (en)
Inventor
David SCHNÄDELBACH
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3183470A1 publication Critical patent/EP3183470A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range

Definitions

  • the invention relates to a centrifugal pendulum according to claim 1 and a drive system according to claim 10.
  • centrifugal pendulum pendulum There are known drive systems with centrifugal pendulum pendulum, wherein the drive motor is torque-coupled with the centrifugal pendulum.
  • the drive motor is usually designed as a reciprocating engine and provides a tainted with torsional torque, the centrifugal pendulum partially eliminates the torsional vibrations.
  • the torsional vibrations can be so strong that the centrifugal pendulum can not repay them and a pendulum mass of the centrifugal pendulum abuts another component of the centrifugal pendulum.
  • an improved centrifugal pendulum can be provided in that the centrifugal pendulum can be mounted rotatably about an axis of rotation.
  • the centrifugal pendulum has a pendulum flange, a coupling device and a pendulum mass.
  • the pendulum mass is by the coupling device on the pendulum with respect to the pendulum from a rest position on a
  • the pendulum track is designed such that the centrifugal pendulum has a vibration-dependent Tilgerowski to attenuate an exciter order of a drive motor, at least partially.
  • the pendulum track has a first section below a predefined oscillation angle and a second section above the predefined oscillation angle.
  • the pendulum track is designed in the first section in such a way that the absorber order over the swing angle is substantially constant.
  • the pendulum track is designed in the second section such that, above the predefined oscillation angle, the absorber arrangement changes as a function of the oscillation angle.
  • the predefined oscillation angle has a value which lies in a range of 20 ° to 55 °, preferably in a range of 35 ° to 50 °.
  • the pendulum track has a maximum oscillation angle, which limits the pendulum track in at least one direction.
  • the predefined swing angle has a value that is greater than 50 percent of the maximum swing angle.
  • the predefined oscillation angle has a value which lies in a range of 50 to 80 percent of the maximum oscillation angle or in a range of 30 to 50 percent of the maximum oscillation angle.
  • the absorber arrangement decreases above the predefined oscillation angle above the predefined oscillation angle in a circle above the oscillation angle.
  • the pendulum track is configured in the second section in such a way that the absorber arrangement has a different pitch in the second section above the swing angle, preferably a decreasing and / or increasing pitch with increasing swing angle.
  • the slope has a value in the range of -0.05 to -0.001, in particular in a range of -0.01 to -0.002 or in a range of 0.001 to 0.05, in particular in a range of 0.002 to 0.01.
  • the pendulum track is designed such that at the maximum swing angle the absorber arrangement is reduced by at least 10 percent, preferably by at least 17 percent, in particular by at least 25 percent, compared to the absorber arrangement in the first section.
  • the pendulum track has a third section, wherein the rest section is arranged in the third section or adjacent to the third section, wherein the third section adjoins the first section at an upper section boundary, wherein the absorber arrangement is greater in the third section smaller than in the first section.
  • the upper section boundary has a value which lies in a range of 2 to 20 percent of the maximum oscillation angle.
  • the pendulum flange has a first pendulum flange part and a second pendulum flange part.
  • the two Pendelflanschwel are at least partially axially spaced from each other.
  • the pendulum mass is arranged axially between the first pendulum flange part and the second pendulum flange part. In this way, a particularly compact centrifugal pendulum can be provided.
  • the absorber arrangement decreases with increasing oscillation angle.
  • an improved drive system can be provided in that the drive system has a drive motor and a centrifugal pendulum, wherein the pendulum track is configured in the first section such that the absorber order is substantially constant over the swing angle and essentially corresponds to the exciter order, wherein the pendulum track is configured in the second section such that, above the predefined oscillation angle, the absorber arrangement changes as a function of the oscillation angle and deviates from the excitation order. This prevents the pendulum mass from being hit at its end stops.
  • FIG. 1 shows a half-longitudinal section through a drive system with a centrifugal pendulum
  • FIG. 2 shows a detail of a sectional view along a sectional plane A-A shown in FIG. 1 through the centrifugal force pendulum shown in FIG. 1;
  • FIG 3 is a functional view of the centrifugal pendulum shown in Figures 1 and 2;
  • Figure 4 is a diagram of a Tilgerix extract of the centrifugal pendulum shown in Figures 1 to 3 plotted against a swing angle;
  • Figure 5 is a diagram of several Tilger inchesen plotted against a swing angle in various interpretations of the centrifugal pendulum shown in Figures 1 to 3;
  • FIG. 6 is a diagram of several absorber orders plotted against a swing angle in various configurations of the centrifugal pendulum shown in Figures 1 to 3; and FIG. 7 shows a diagram of an absorber arrangement of a variant of the centrifugal force pendulum shown in FIGS. 1 to 3, plotted over an oscillation angle;
  • 1 shows a schematic half-longitudinal section through a drive system 10 with a centrifugal pendulum 15.
  • FIG. 2 shows a section of a sectional view along a sectional plane AA shown in FIG. 1 through the centrifugal pendulum 15 shown in FIG.
  • the drive system 10 is rotatably mounted about a rotation axis 20.
  • the drive system 10 includes a drive motor 25 and said centrifugal pendulum 15.
  • the centrifugal pendulum 15 is formed as an internal centrifugal pendulum 15 and has a pendulum flange 30 which is rotationally connected to the drive motor 25.
  • the centrifugal pendulum 15 is connected to another component of the drive system 10. It is also conceivable that the centrifugal pendulum 15 is designed as an external centrifugal pendulum.
  • the drive motor 25 provides a torque for driving a motor vehicle, which usually, in the embodiment of the drive motor 25 as a reciprocating engine, torsional vibrations having an excitation order.
  • the exciter order is dependent on the number of cylinders of the reciprocating engine in operation.
  • the excitation order is half the number of cylinders in operation.
  • a reciprocating engine with four cylinders, in which four cylinders are in operation has an exciter order of 2. If the reciprocating engine additionally has a cylinder deactivation, then the excitation order of the reciprocating piston engine during operation with cylinder deactivation also changes compared to operation without cylinder deactivation. If, for example, two cylinders are switched off during cylinder deactivation in the case of the reciprocating piston engine designed as a four-cylinder engine, the drive motor 25 has the excitation order in operation with cylinder deactivation of 1.
  • the centrifugal pendulum 15 has at least one pendulum mass 35 and a coupling device 36.
  • the pendulum flange 30 has a first pendulum flange part 40 and a second pendulum flange part 45.
  • the two Pendelflanschmaschine 40, 45 are axially spaced from each other.
  • the Pendelflanschmaschine 40, 45 are connected by means of a first connection 50, which is formed in the embodiment as a rivet connection.
  • the first connection 50 ensures both a torque transmission tion between the two Pendelflansch too 40, 45 and the axial location of the second Pendelflanschteils 45 relative to the first Pendelflanschteil 40.
  • the pendulum mass 35 is arranged.
  • the pendulum mass 35 has a center of gravity 51.
  • further pendulum masses 52 may be provided adjacent to the pendulum mass 35, which are also limited to the pendulum flange 30 movably coupled.
  • the coupling device 36 has a first recess 60 arranged axially opposite the pendulum flange parts 40, 45 and a second recess 65 arranged in the pendulum mass 35.
  • the first recess 60 has a first recess contour 66 and the second recess 65 has a second recess contour 67.
  • the first recess contour 66 is designed as an example kidney-shaped and has a first center of curvature 70, which is arranged radially inwardly to the first recess 60.
  • the second recess contour 66 is also designed as an example kidney-shaped.
  • the second recess 65 has a second center of curvature 75, which is arranged radially outside the second recess 65.
  • the coupling device 36 also has a coupling element 80.
  • the coupling element 80 is formed in the embodiment as a pendulum roller and extends axially through the recesses 60, 65th
  • the pendulum mass 35 is pulled radially outwardly by the centrifugal forces acting on the pendulum mass 35, so that the coupling element 80 rests radially on the inside on the second recess contour 67 and radially on the outside on the first recess contour 66. If a torsional vibration, initiated by the drive motor 25 via the pendulum flange 30, is introduced into the centrifugal force pendulum 15, the pendulum mass 35 serves as an energy store. In this case, the pendulum flange 30 relative to the pendulum mass 35 rotates relative.
  • the coupling device 36 guides the center of gravity 51 of the pendulum mass 35 along a (center of gravity) ) Pendulum 90 depending on the geometric configuration of the first and second recess contours 66, 67 in conjunction with the coupling element 80th
  • FIG. 3 shows a functional representation of the centrifugal pendulum 1 5 shown in FIGS. 1 and 2.
  • the centrifugal pendulum 1 5 has a suspension point 1 00.
  • the suspension point 1 00 is arranged over a radius n spaced from the axis of rotation 20.
  • the suspension point 1 00 has to the center of gravity 85 of the pendulum mass 35 a pendulum length r 2 .
  • the pendulum track 90 has a rest position 1 05 on.
  • the pendulum mass 35 is in the rest position 1 05, when the distance of the pendulum mass 35 to the axis of rotation 20 is greatest and the sum of the radius n and the pendulum length r 2 .
  • the pendulum mass 35 Upon initiation of torsional vibrations in the pendulum 30, the pendulum mass 35 is deflected from the rest position 1 05, so that a distance between the center of gravity 51 and the rotation axis 20 is smaller than the distance of the rest position 1 05 to the rotation axis 20.
  • the coupling device 36 guides the pendulum mass 35 in deflection along the pendulum track 90.
  • a deflected position in a deflected position, as shown by dashed lines in the example in Figure 3, includes the center of gravity 51 of the deflected pendulum mass 35 to the rest position 1 05 a swing angle ⁇ a.
  • the value of the oscillation angle ⁇ is dependent on the configuration of the pendulum track 90 and a magnitude of the torsional vibration introduced via the pendulum flange 30.
  • the pendulum track 90 also has a maximum swing angle ⁇ .
  • the pendulum track 90 is limited so that, for example, the pendulum mass 35 strikes against one end of the coupling device 36.
  • the maximum oscillation angle c MA x can also be limited by the configuration of the pendulum track 90.
  • the pendulum track 90 also has a predefined oscillation angle ⁇ . Below the predefined oscillation angle ⁇ , the pendulum track 90 has a first section 1 1 0 between the rest position 1 05 and the predefined oscillation angle ⁇ and a second section 1 15 above the predefined oscillation angle qv. In the first section 1 1 0, the pendulum 90 is designed epicycloid. In the second section 1 1 5, the pendulum track 90 is designed circular, wherein the pendulum track 90 has a suspension point 1 00 different section center 1 20. In the embodiment, for example, the section center 1 20 is arranged radially outward to the suspension point 1 00. Of course, it is also conceivable that the section center 120 is arranged at a different position, for example radially inward to the suspension point 1 00.
  • the predefined vibration angle ⁇ has a value which is in a range of 20 ° to 55 °, preferably in a range of 35 ° to 50 °.
  • the predefined oscillation angle ⁇ has a value which lies in a range of 50 to 80 percent of the maximum oscillation angle (MAX or in a range of 30 to 50 percent of the maximum oscillation angle.. that the predefined
  • Oscillation angle ⁇ has a value that is greater than 50 percent of the maximum swing angle ⁇ .
  • the pendulum 90 sets in conjunction with a mass of the pendulum mass 35 a
  • the pendulum track 90 is thus designed such that the centrifugal pendulum 1 5 a from
  • Oscillation angle ⁇ dependent Tilgerowski q has to dampen on the one hand, an excitation order of a drive motor 25 at least partially effective and the Others to avoid striking the pendulum mass in the maximum oscillation angle (MAX.
  • FIG. 4 shows a diagram of the absorber order q plotted over the oscillation angle ⁇ .
  • the graph 195 shows an oscillation behavior of the centrifugal force pendulum 15 shown in FIGS. 1 to 3 above the oscillation angle ⁇ .
  • the oscillation angle ⁇ corresponds to the value 0 ° of the rest position 105.
  • the maximum oscillation angle ⁇ is by way of example 80 °. Of course, other values for the maximum swing angle ⁇ are conceivable.
  • the predefined swing angle ⁇ 23 °. Due to the epicycloid configuration of the pendulum 90 in the first section 1 10 is the
  • Tilger eleven q over the swing angle ⁇ in the first section 1 10 is substantially constant and substantially corresponds to the excitation order of the drive motor 25.
  • the graph 195 has a break point 225 on.
  • a slope of the graph 195 changes. It has turned out to be particularly advantageous if, in the second section 11, the absorber order q has a different pitch, preferably a decreasing and / or an increasing pitch, over the swing angle ⁇ .
  • the slope has a value in the range of -0.05 to -0.001, in particular in a range of -0.01 to -0.002 or in a range of 0.001 to 0.05, in particular in a range of 0.002 to 0.01.
  • the absorber order q decreases from the value 2 in the predefined oscillation angle ⁇ to the maximum oscillation angle ⁇ along a circular path, so that the
  • a maximum deviation Aq max in the maximum swing angle (PMAX 12 percent relative to the Tilger instruct q in the first section 1 10 is particularly advantageous if the pendulum track 90 is designed such that at maximum swing angle ⁇ the Tilger instruct q by at least 5 percent, preferably by at least 10 percent, in particular by at least 15 percent, reduced compared to the Tilger instruct q in the first section 1 10 and the exciter order is.
  • the deviation Aq in the Tilger eleven q to the exciter order causes a striking of the pendulum mass 35 is avoided at other pendulum masses 52 and / or at the end of the coupling device 36, so that attack noises can be reliably avoided as well. Furthermore, can be dispensed with additional stop buffer, so that the number of components of the centrifugal pendulum pendulum 15 can be reduced overall.
  • FIG. 5 shows a diagram of a plurality of absorber orders q plotted over the
  • Vibration angle ⁇ in various interpretations of the centrifugal pendulum shown in Figures 1 to 3.
  • Several graphs 195, 200, 210, 215, 220 are shown in the diagram, which have different line configurations for ease of distinctness. In this case, each graph 195, 200, 210, 215, 220 corresponds to a different design of the pendulum track 90th
  • a first graph 200 shows a profile of the absorber order q over the oscillation angle ⁇ when the pendulum track 90 is completely circular and deviates from the pendulum track 90 shown in FIG.
  • the absorber arrangement q exclusively in the rest position 105, the absorber order q, which corresponds to the excitation order of the drive motor 25 (in the embodiment by way of example 2).
  • the oscillation angle ⁇ With increasing oscillation angle ⁇ , the oscillation angle ⁇ has a greater deviation Aq from the exciter order. This causes the centrifugal pendulum 15 is only slightly excited, but also the effect of the centrifugal pendulum 15 with increasing
  • a second graph 195 corresponds to the graph 195 shown in FIG. 4.
  • a third graph 210, a fourth graph 215 and a fifth graph 220 show variants of the centrifugal force pendulum 15 shown in FIGS. 1 to 3.
  • the pendulum run 90 To that effect by a geometric adjustment of the recess contours 66, 67 varies that the predefined swing angle and thus the break point 225 of the third, fourth and fifth graph 210, 215, 220 is shifted in the direction of the maximum swing angle ⁇ .
  • the pendulum track 90 and the third to fifth graphs 210, 215, 220 have a broader first section 110 than shown in FIG.
  • the pendulum track 90 of the second, third and fourth graphs 205, 210, 215 is designed by way of example so that with increasing oscillation angle ⁇ in the second section 1 15, the slope decreases. The slope can also increase in the second section 1 15 alternatively. If a value is selected for the predefined oscillation angle ⁇ which is above 50 ° (see fifth graph 220), the absorber order q in the first section 110 leads to a substantially constant absorber order q towards the predefined oscillation angle predefined
  • Oscillation angle ⁇ ⁇ increases.
  • the absorber order q decreases over the oscillation angle ⁇ .
  • the slope of the fifth graph 220 thus has a change in sign in the inflection point from positive to negative.
  • FIG. 6 shows a diagram of the absorber order q plotted against the oscillation angle ⁇ .
  • numerous graphs 300, 305, 310, 315, 320, 325, 330 are shown.
  • the pendulum track 90 of the centrifugal pendulum pendulum 15 is designed epicycloid in the first section 1 10, so that the absorber order q is substantially constant over the oscillation angle ⁇ and is tuned to the exciter order of the drive motor 25.
  • the graphs 300, 305, 310, 315, 320, 325, 330 have a different course, so that the pendulum track 90 is configured above the predefined oscillation angle ⁇ such that the absorber order q changes as a function of the oscillation angle ⁇ ,
  • the pendulum track 90 can be tuned such that, as for the first, second, third, fourth, fifth, sixth graphs 300, 305, 310, 315, 320, 325, with increasing
  • Oscillation angle ⁇ Tilger himself q decreases substantially linearly. It is also conceivable that in the second section 1 15 the pendulum track 90 is configured such that, as in the fifth and sixth graphs 320, 325, the pendulum track 90 and the Tilgerowski q is circular. In this case, the pitch can increase and / or decrease with increasing oscillation angle ⁇ , whereby in the fifth and sixth graphs 320, 325 the slope first increases until the absorber order has reached a global maximum and then decreases.
  • FIG. 7 shows a diagram of an absorber order q plotted over the oscillation angle ⁇ .
  • the pendulum track 90 of the centrifugal pendulum 15 is similar to that in Figure 3 and their vibration behavior (see Figure 4) configured.
  • the pendulum track 90 is modified relative to the pendulum track 90 shown in FIG. 3 such that the pusher track 90 and also the absorber arrangement q have a third additional section 400.
  • the third section 400 adjoins the rest position 105.
  • the rest position 105 is arranged in the third section and the third section 400 extends on both sides of the rest position 105.
  • the first section 1 10 is arranged on a side facing away from the rest position 105 side.
  • the third section 400 adjoins the first section 110 at an upper section boundary 405, which adjoins above, ie with increasing oscillation angle ⁇ .
  • the pendulum track 90 is designed in the third section 400 such that the absorber arrangement q is smaller than in the first section 1 10 and thus smaller than the excitation order.
  • the pendulum track 90 is designed such that in the third section 400, the Tilgerowski q greater (dashed lines in Figure 7 shown) than in the first section 1 10 and thus is greater than the excitation order.
  • the upper section boundary 405 has a value which lies in a range of 2 to 20 percent of the maximum oscillation angle ⁇ . Due to the incorrect design in the third section 400, it is avoided that the centrifugal pendulum 15 is excited to strong oscillations with small torsional vibrations. As a result, wear of the coupling device 36 can be minimized.
  • the predefined oscillation angle ⁇ 30 ° and the maximum oscillation angle is 80 °.
  • the absorber order q 1, 9, so that the incline of the pendulum track 90 in the second ab- cut 1 is 15 -0.002.
  • the predefined oscillation angle ⁇ 40 °.
  • the absorber order q 1, 8, so that the slope of the pendulum track 90 in the second section 1 is 15 -0.005.
  • the predefined oscillation angle ⁇ 50 °.
  • the absorber order q 1, 6, so that the slope of the pendulum track 90 in the second section 1 is 15-0.013.
  • Oscillation angle ⁇ 50 °.
  • the tilt order q 1, 6, so that the slope of the pendulum track 90 in the second section 1 is 15 -0.04.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

L'invention concerne un pendule centrifuge (15) qui peut être monté à rotation sur un axe de rotation (20), comprenant un flasque de pendule (30), un dispositif d'accouplement (36) et une masse pendulaire (35). La masse pendulaire est accouplée par le dispositif d'accouplement au flasque de pendule de façon à pourvoir être déviée d'une position de repos (105) par rapport audit flasque de pendule,d'un angle d'oscillation (φ) le long d'une trajectoire pendulaire (90). La trajectoire pendulaire est conçue de telle sorte que le pendule centrifuge présente un degré d'amortissement (q), fonction de l'angle d'oscillation, pour amortir au moins partiellement un degré d'excitation d'un moteur d'entraînement (25). La trajectoire pendulaire comporte une première partie (110) au-dessous d'un angle d'oscillation du pendule prédéfini (φ v ) et une seconde partie (115) au-dessus de l'angle d'oscillation prédéfini. Dans la première partie, la trajectoire pendulaire est conçue de sorte que le degré d'amortissement est sensiblement constant sur l'angle d'oscillation. Dans la seconde partie, la trajectoire pendulaire est configurée sorte que, au-dessus de l'angle d'oscillation prédéfini, le degré d'amortissement varie en fonction de l'angle d'oscillation.
EP15766390.7A 2014-08-22 2015-08-19 Pendule centrifuge et système d'entraînement muni d'un tel pendule centrifuge Withdrawn EP3183470A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014216750 2014-08-22
PCT/DE2015/200441 WO2016026494A1 (fr) 2014-08-22 2015-08-19 Pendule centrifuge et système d'entraînement muni d'un tel pendule centrifuge

Publications (1)

Publication Number Publication Date
EP3183470A1 true EP3183470A1 (fr) 2017-06-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP15766390.7A Withdrawn EP3183470A1 (fr) 2014-08-22 2015-08-19 Pendule centrifuge et système d'entraînement muni d'un tel pendule centrifuge

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Country Link
EP (1) EP3183470A1 (fr)
DE (1) DE112015003839A5 (fr)
WO (1) WO2016026494A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016221576A1 (de) * 2016-11-03 2018-05-03 Schaeffler Technologies AG & Co. KG Fliehkraftpendel und Antriebssystem
DE102016222468A1 (de) * 2016-11-16 2018-05-17 Schaeffler Technologies AG & Co. KG Fliehkraftpendel und Antriebssystem
DE102017213309A1 (de) 2017-08-01 2019-02-07 Zf Friedrichshafen Ag Tilgersystem
FR3077858A1 (fr) * 2018-02-14 2019-08-16 Valeo Embrayages Dispositif d'amortissement pendulaire
DE102019215909A1 (de) * 2019-10-16 2021-04-22 Zf Friedrichshafen Ag Tilgersystem
DE102020214062A1 (de) * 2020-11-10 2022-05-12 Zf Friedrichshafen Ag Drehmomentübertragungseinrichtung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112008000220A5 (de) * 2007-02-12 2009-10-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Fliehkraftpendeleinrichtung
DE112011103700B4 (de) * 2010-11-08 2020-10-15 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
FR2986593B1 (fr) * 2012-02-07 2017-09-15 Valeo Embrayages Dispositif d'amortissement pendulaire
EP2872796B2 (fr) * 2012-07-12 2023-06-21 Schaeffler Technologies AG & Co. KG Dispositif amortisseur d'oscillations adaptatif en fonction de la vitesse de rotation et amortisseur d'oscillations de rotation le comprenant

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WO2016026494A1 (fr) 2016-02-25
DE112015003839A5 (de) 2017-05-18

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