WO2019141309A1 - Équipement d'amortisseur annulaire - Google Patents

Équipement d'amortisseur annulaire Download PDF

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Publication number
WO2019141309A1
WO2019141309A1 PCT/DE2019/100016 DE2019100016W WO2019141309A1 WO 2019141309 A1 WO2019141309 A1 WO 2019141309A1 DE 2019100016 W DE2019100016 W DE 2019100016W WO 2019141309 A1 WO2019141309 A1 WO 2019141309A1
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WO
WIPO (PCT)
Prior art keywords
mass
parts
ring
mass part
mass parts
Prior art date
Application number
PCT/DE2019/100016
Other languages
German (de)
English (en)
Inventor
Christian Dinger
Christian Gradolph
Stephan Maienschein
Toros GÜLLÜK
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2019141309A1 publication Critical patent/WO2019141309A1/fr

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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 Ringtilger adopted especially for a drive train of a motor vehicle with a rotatably mounted about a rotation axis arranged first mass portion and distributed over the circumference in the centrifugal force of the rotating about the axis rotating first mass part radially displaceable second mass parts and a limited compared to the first mass portion rotatable third mass part.
  • Drive trains of motor vehicles have a torsionally vibrating internal combustion engine, so that different torsional vibration isolation devices, for example torsional vibration dampers, centrifugal pendulum pendulums and / or other massile filters are known for their reassurance.
  • torsional vibration isolation devices for example torsional vibration dampers, centrifugal pendulum pendulums and / or other massile filters are known for their reassurance.
  • Centrifugal pendulum serve the speed-adaptive torsional vibration isolation.
  • the torsional vibration isolation takes place by pendulum masses suspended in the centrifugal force field on a support part and temporarily store energy entered as potential energy from torque peaks and then return it to the drive train.
  • one or more centrifugal pendulum pendulums can be attached to a torsional vibration damper according to document WO2014 / 114 280 A1 on a clutch disc according to document EP 2 600 030 A1 a hydrodynamic torque converter, be provided on a housing of a friction clutch or similar locations of the drive train.
  • the pendulum masses are arranged on a support part which can be rotated about an axis of rotation, for example a pendulum mass support, by means of two support elements. along a pendulum bearing provided by pendulum pendulum pendulum in the centrifugal force field of the rotating about the axis of rotation support member receiving pendulum.
  • the effectiveness of the torsional vibration isolation depends in addition to the mass of the pendulum masses substantially from their radius relative to the axis of rotation.
  • the publication DE 10 2011 101 977 A1 discloses a torsional vibration damper, in which an annular mass pendulum, which is mounted centrically to the axis of rotation, is provided, which is rotationally driven by a component of the torsional vibration damper over a limited angle of rotation by means of a tooth system.
  • the object of the invention is the development of a speed-adaptive torsional vibration damper.
  • a speed-adaptive torsional vibration damper is to be proposed, which offers sufficient torsional vibration isolation with small radial installation spaces.
  • the proposed Ringtilger serves the torsional vibration isolation in particular for a drive train of a motor vehicle with a mosschwingungsbe- attached internal combustion engine.
  • the ring filter device is preferably tuned to a main excitation frequency of the internal combustion engine with a predetermined Tilger für.
  • Ringtilger is a speed-adaptive torsional vibration damper, which has a higher tilgende mass and thus an improved torsional vibration isolation capacity compared to an ordinary centrifugal pendulum at substantially the same space requirement.
  • the ring-type filter device contains a carrier part, which is rotatable about an axis of rotation and driven directly or indirectly by the internal combustion engine, which is subsequently named as the first mass part.
  • the first mass part can for example be connected directly to a crankshaft of the internal combustion engine, integrated in a single flywheel, a torsional vibration damper, for example a dual mass flywheel, in the housing of a hydrodynamic torque converter or in another drive train device.
  • a torsional vibration damper for example a dual mass flywheel
  • absorber masses distributed over the circumference are arranged, which are subsequently designated as second mass parts.
  • a third mass part preferably designed as a ring part, which with the first and second mass parts forms a rotational speed adaptive torsional vibration damper system.
  • the mass parts are kinematically coupled to one another by means of self-aligning bearings and bearings, which are fixed in the axial direction and in the circumferential direction and can be rotated in the radial direction.
  • self-aligning bearings and bearings which are fixed in the axial direction and in the circumferential direction and can be rotated in the radial direction.
  • two different types of vibration are provided.
  • second mass parts are accommodated in a limited manner rotatably on the first mass part by means of the bearings.
  • the second mass parts are entrained by means of the bearing in the circumferential direction of the first mass part rotating around the axis of rotation and are held rotatably in a limited manner in the radial direction about the bearing.
  • the radial displacement is limited by means of self-aligning bearings which are formed between the third mass part serving as an additional dead mass by forming an inertial moment and in each case a second mass part.
  • the third mass may be accommodated on the first mass part in a limited rotatable centered manner.
  • a pendulum bearing is provided between the second mass parts and the third mass part, and the second mass parts are rotatably received on the first mass part.
  • the third mass part can be centered radially on the first mass part radially within the pendulum bearings.
  • a pendulum bearing is in each case formed between the first mass part and a second mass part.
  • the bearings enabling a radial movement of the second mass parts are respectively formed between the third mass part and a second mass part.
  • the third mass part serves as a synchronizing ring for isoradial displacement of the second mass parts.
  • the third mass portion serves as a mass filter by this is limited rotated relative to its moment of inertia at a radial displacement of the second mass parts.
  • the radially rotatable reception of the second parts of the mass on the first or second mass part can take place by means of a rolling or sliding bearing or a preferably radially prestressed joint socket connection, wherein the corresponding mass part forms corresponding joint sockets, on which a rolling contour of the second mass part rolling, be provided.
  • the first or second mass part can have radially expanded arms, which form the rotatable connection with arms of the second mass parts which are widened in the circumferential direction. Spaced in the circumferential direction, the pendulum bearings are provided between the second mass parts and the first or second mass part.
  • the mass portion forming the pendulum bearing with the second mass parts is disk-shaped.
  • second mass parts are arranged, wherein axially opposite second mass parts are interconnected.
  • the self-aligning bearings are in each case formed between the axially opposite second mass parts and the first or second mass part arranged axially between them.
  • the wings of the axially opposed second mass members flank the arms of the mass forming the bearings, a pivot bearing being provided between each of the wings of the axially opposed second mass members and the arms by means of the bearing previously described.
  • connecting means for example spacers, for example by riveting.
  • the first or third mass part forming the pendulum bearings relative to the second mass parts is formed from two axially spaced annular disk parts, wherein the second mass parts are arranged axially between the annular disk parts.
  • the self-aligning bearings are in each case formed between the annular disk parts and the second mass parts arranged axially between them.
  • the bearing between the second mass parts and the other mass part can, for example, by means of circumferentially übergrei- fender areas of the radially expanded arms of the other part of the mass and extended in the circumferential direction swinging the second mass parts, for example be formed a radially biased hinge connection or a rolling or sliding bearing.
  • the third mass part can radially overlap the second mass parts and have an additional mass radially on the outside.
  • the additional mass may be formed integrally with the third mass part.
  • an additional mass may be integrally formed on a disk-shaped third mass portion.
  • an additional mass in the form of a mass ring or mass segments distributed over the circumference can be provided, for example, in a radial extension to the second mass parts and limited to their axial space.
  • the second mass parts may have at least one additional mass.
  • additional masses may protrude radially beyond the first or third mass part.
  • the axially opposite second mass parts can be connected to one another radially outside of this mass part by means of an additional mass.
  • the annular disc parts may be formed across, on both sides of the second mass parts attached, for example, in radial extension to the annular disc parts and their axial space limited additional masses, for example with these can be riveted.
  • axially opposed second mass parts can have additional masses between them on the radial upper part of the pendulum bearing.
  • additional masses may be provided, which are extended on one side in the circumferential direction and the storage to form the corresponding mass part, for example, the third, disc-shaped mass part this forming on both sides, while the pendulum bearings are formed between the first mass part and the second mass parts.
  • the second mass parts and the third mass part are in this case arranged at the same axial height, wherein the first mass portion is formed of two arranged on both sides of this annular disc parts.
  • FIG. 1 shows the upper part of a ring-type sealing device arranged about an axis of rotation with pendulum bearings arranged between the third and the second mass parts
  • FIG. 2 shows the ring-type filter device of FIG. 1 in a view
  • FIG. 3 shows the upper part of a relative to the ring filter device of Figures 1 and 2 modified Ringtilger adopted with additional masses on the third mass part in section,
  • Cut, 5 shows the upper part of a relative to the ring filter device of Figure 4 modified Ringtilger adopted with arranged on radial fleas of pendulum bearings on the second mass parts additional masses in section,
  • FIG. 7 shows the upper part of a ring filter device modified relative to the ring filter device of FIG. 1 with an additional mass arranged radially on the outside of the third mass part, in section, FIG.
  • FIG. 9 shows a ring-type filter device which can be rotated about an axis of rotation and has pendulum bearings arranged between the first mass part and the second mass parts,
  • Figure 10 shows the upper part of a arranged around a rotation axis, with respect to the
  • FIG. 11 shows the ring filter device of FIG. 10 in partial view
  • FIG. 12 is a sectional view of the upper part of a ring filter device modified relative to the ring-type filter devices of FIGS. 9 to 11;
  • FIG. 13 is a sectional view of the upper part of a ring filter device modified relative to the ring-type filter devices of FIGS. 9 to 12;
  • FIG. 14 is a sectional view of the upper part of a ring filter device modified relative to the ring-type filter devices of FIGS. 9 to 13;
  • FIG. 15 is a sectional view of the upper part of a ring filter device modified relative to the ring-type filter devices of FIGS. 9 to 14;
  • FIG. 16 is a sectional view of the upper part of a ring filter device modified relative to the ring-type filter devices of FIGS. 9 to 15;
  • FIG. 17 is a sectional view of the upper part of a ring filter device modified relative to the ring-type filter devices of FIGS. 9 to 16;
  • FIG. 18 is a sectional view of the upper part of a ring filter device modified relative to the ring-type filter devices of FIGS. 9 to 17.
  • Figures 1 and 2 show in sync the ring filter device 1.
  • the figure 1 shows the upper part of the rotatable about the rotation axis d ring Ringer 1 in section along the leading through the pendulum bearing 6 section line.
  • FIG. 2 shows a view of the ring filter device 1.
  • the ring filter device 1 has the first mass part 2 arranged around the rotation axis d and designed as a carrier part, on which the third mass part 3 designed as a ring part is received and centered in a limited manner in a rotatable manner. Between the first mass portion 2 and the third mass portion 3 are arranged distributed over the circumference arranged, designed as absorber masses second mass parts 4 are effectively arranged. In this case, the second mass parts 4 are rotatably coupled by means of the bearing 5 to the first mass part 2 and by means of the self-aligning bearings 6 to the third mass part 3. The third mass part 3 is received centered on the first mass part 2 by means of the centering surface 7 on the Gegenzentrier constitutional 8 and stored axially. This is after the centering of the third mass part 3, the holding plate 9 is connected to the first mass part 2.
  • the second mass parts 4 have circumferentially extended wings 10, which are rotatably received on the radially expanded arms 11 of the first mass part 2 by means of the bearings 5.
  • the third mass part 3 has recesses 12 through which the cranked arms 11 pass, so that the third mass part 3 and the arms 11 are arranged substantially axially on the same line. In this manner, the second mass parts 4 arranged on both sides of the third mass part 3 can be accommodated without space being extended axially relative to the third mass part 3, the third mass part 3 being aligned with the axial flange region 13 of the first mass part 2.
  • the axially opposite second mass parts 4 are connected to each other by rivets 14 and spacers, not shown, for example, as stepped rivets 14.
  • the self-aligning bearings 6 are each formed on recesses 15, 16 of the second mass parts 4 and the third mass part 3 provided raceways 17, 18, on each of which the recesses 15, 16 axially overlapping spherical roller 19 rolls.
  • the raceways 17, 18 are formed radially complementary complementary arcuate, so that sets a maximum Radi- usus of the second mass parts 4 and a neutral position of the third mass part 3 in the absence of torsional vibrations. If two torsional vibrations occur at the first part of the mass, this will be delayed or accelerated depending on the direction of the torque. In this case, a relative rotation of the third mass part 3 with respect to the first mass part 2 occurs due to its moment of inertia and the second mass parts 4 are against the centrifugal force due to the given by the tracks 17, 18 pendulum track radially inward forced to a smaller radius.
  • an eradication effect takes place, which is adapted to the rotational speed and, due to the ratio of the moment of inertia of the third mass part 3 to the mass of the second mass parts 4 as well as the given pendulum path of the second mass parts 4, is designed for a predetermined absorber order.
  • the axially extended, one-piece on the third Mass part 3 provided, for example, molded toastmas- se 20 is provided.
  • the additional mass 20 is extended axially on both sides with respect to the third mass part 3 and is limited to the axial space of the second mass parts 4 or the pendulum roller 19. For reasons of space for installation in a corresponding environment with a predetermined space, the fontmas se se 20 on one side the Flattening 21 on.
  • FIG. 3 shows the upper part of the ring-type filter device 1 a, which is rotatable about the axis of rotation d, in section, of which only the third mass part 3a and the second mass parts 4a are shown omitting the first mass part.
  • the additional mass 20a is formed by the two ground rings 22a which are connected, for example riveted, to the third mass portion 3a.
  • the mass rings 22a have substantially the same axial space as the second mass parts 4a, so that the overall structure of the ring filter device 1a is not expanded with respect to its axial installation space.
  • FIG. 4 shows the upper part of the ring-type sealing device 1b arranged around the axis of rotation d in the representation corresponding to FIG.
  • the second mass parts 4 b are provided with additional masses 20 b in order to shift the ratio J / M in favor of the masses of the second mass parts 4 b.
  • the respectively axially opposite second mass parts 4b are radially widened with respect to the third mass part 3b.
  • the additional masses 20b are in each case arranged between axially opposite second mass parts 4b, for example riveted to them.
  • the thickness of the additional masses 20b is slightly larger than the thickness of the third mass part 3b, so that an axial gap 23b can be set between the second mass parts 4b and the third mass part 3b.
  • the additional masses 20c are displaced radially inwardly between axially spaced-apart second mass parts 4c.
  • the additional masses 20c form the connecting means 14c between the axially opposite second mass parts 4c and are arranged in the recesses 12c of the third mass part 3c.
  • the additional masses 20c also form by their thickness the axial gaps 23c between the second mass parts 4c and the third mass part 3c.
  • FIGS. 6 to 8 each show in section the upper part of the ring filter devices 1 d, 1 e, 1 f arranged around the axis of rotation d, omitting the first mass part similar in principle to the ring filter devices 1, 1 a, 1 b, 1 c.
  • the third mass part 3d, 3e, 3f formed in two parts.
  • the third mass part 3d, 3e, 3f is formed of two axially spaced annular disc parts 24d, 24e, 24f, which are axially between them over the circumference distributed arranged second mass parts 4d, 4e, 4f record.
  • the annular disc parts 24d, 24e, 24f are preferably connected to each other in a preferred manner, wherein one or both annular disc parts 24d, 24e, 24f are centered on the first mass part and axially mounted.
  • the self-aligning bearings 6d, 6e, 6f are in each case formed between recesses and tracks of the annular disk parts 24d, 24e, 24f and the spherical rollers 19d, 19e, 19f which axially overlap these recesses and roll on the raceways. It is understood that depending on the intended additional functions of the third mass part 3e, the annular disc parts 24d, 24e, 24f may be formed as identical parts or different.
  • the ring-type filter device 1 e of FIG. 7 has radially outside the additional mass 20 e assigned to the third mass part 3 e.
  • the annular disc parts 24e are radially widened.
  • the additional mass 20e is arranged between the annular disk parts 24e, for example, as a mass ring 22e and connected to these, for example, riveted.
  • the additional mass 20e can represent the connection of the annular disk parts 24e to each other and adjust the axial gaps 23e between the second mass parts 4e and the annular disk parts 24e by means of their thickness.
  • the additional masses 20f of the ring-type filter device 1f are assigned to the second mass parts 4f.
  • the second mass parts 4f are widened radially relative to the annular disk parts 24f of the third mass part 3f and have additional masses 20f on both sides, for example mass elements which extend over the entire or a part circumference of the second mass parts 4f and are connected to the second mass parts 4f , for example, are netted on.
  • FIG. 9 shows the annular filter device 1 g rotatably arranged about the rotation axis d in a view. In the ring filter device 1 g are in contrast to the
  • the bearings 5g for the radially rotatable mounting of the second mass parts 4g are arranged on the third mass part 3g designed as a ring part or synchronizing ring.
  • the first mass part 2g is disk-shaped, on both sides of which the circumferentially distributed second mass parts 4g are accommodated.
  • the third mass part 3g is arranged axially adjacent to the first mass part 2g and is housed substantially radially inside the second mass parts 4g and, together with the circumferentially widened rockers 10g, forms the bearings 5g on its radially expanded arms 11g.
  • the arms 11g are axially brought to the same height as the second mass parts 4g, so that the rockers 10g of a respective second mass part 4g form a bearing 5g on both sides on an arm 11g.
  • a self-aligning bearing 6g is formed between the axially oppositely arranged, interconnected second mass parts 4g and the first mass part 2g.
  • Figures 10 and 11 show the opposite the ring filter device 1 g of Figure 9 modified Ringtilger adopted 1 h in the form of the upper part in section ( Figure 10) and in partial view ( Figure 11).
  • the first mass part 2h designed as a carrier part contains the two axially spaced and interconnected ring disk parts 24h, between which the second mass parts 4h arranged around the circumference and the third mass part 3h are arranged.
  • the upper ring disk part is removed for the sake of clarity. men.
  • the self-aligning bearings 6h are each formed between the annular disk parts 24h and a second mass part 4h.
  • the bearings 5h are between the
  • the rockers 10h are arranged on both sides of the second mass parts 4h, connected thereto, riveted here by means of the rivet 25h, and form additional masses 20h to increase the mass of the second mass parts 4h.
  • additional masses 22h are provided on both sides of the second mass parts 4h radially inward.
  • FIG. 12 shows the upper part of the ring-type filter device 1 i rotatably arranged about the rotation axis d, which is similar to the ring-type filter device 1 h of FIGS. 10 and 11 with self-aligning bearings 6i formed between the ring-disk parts 24i of the first mass part 2i and the second mass parts 4i.
  • the second mass parts 4i provided between the annular disk parts 24i of the first mass part 2i with an increased thickness are provided.
  • the thickness is increased in relation to the thickness of the third mass part 3i, so that connecting means with respect to the clasps of the second mass parts 4i for forming the bearing can be provided on both sides of the arms of the third mass part 3i in a manner not shown.
  • FIG. 13 schematically shows the upper part of the ring-type filter device 1 j arranged around the rotation axis d, which is similar to the ring-type filter device of FIG.
  • the disk-shaped first mass part 2j receives by means of the self-aligning bearings 6j on both sides the circumferentially distributed second mass parts 4j.
  • the third mass part 3j arranged radially inside the second mass part 4j axially adjacent to the first mass part 2j forms a bearing on the respectively axially opposite, interconnected second mass parts 4j only on one side. Due to the rigid connection of the interconnected, axially opposite In the process, all second parts of the mass 4j are radially synchronized by means of the third mass part 3j.
  • FIG. 14 shows the upper part of the ring-type filter device 1 k arranged around the axis of rotation d, similar to the ring-ringing device 1 h of FIGS. 10 and 11, in section.
  • the second mass parts 4k are extended radially outwards beyond the annular disk parts 24k of the first mass part 2k and carry additional masses 20k on both sides, which lie within the axial space of the annular disk parts 24k with respect to their axial installation space.
  • the third mass part 3k is arranged radially inside the second mass parts 4k and between the annular disk parts 24k and synchronizes them radially at the bearings to the second mass parts 4k.
  • FIG. 15 shows a schematic representation of the upper part of the ring-type filter device 11, which is rotatable about the axis of rotation d and is similar to the ring-type filter device 1 j of FIG.
  • the second mass parts 4I arranged on both sides on the first mass part 2I are widened radially beyond the first mass part 2I.
  • the additional mass 20I is arranged, which also serves as a connecting means between them.
  • FIG. 16 shows the upper part of the ring-type annealing device 1 m arranged around the axis of rotation d in section.
  • the second mass parts 4m arranged on both sides on the disk-shaped first mass part 2m are arranged radially outwardly flush therewith and have at the radial height and in the circumferential direction offset from the pendulum bearings, not shown, between them first mass part 2m and axially oppositely disposed second mass parts 4m additional masses 20m, which also serve as a connecting means between them.
  • FIG. 16 shows the upper part of the ring-type annealing device 1 m arranged around the axis of rotation d in section.
  • the second mass parts 4m arranged on both sides on the disk-shaped first mass part 2m are arranged radially outwardly flush therewith and have at the radial height and in the circumferential direction offset from the pendulum bearings, not shown, between them first mass part 2m and axially oppositely disposed second mass parts 4m additional masses
  • the additional masses 20n are not arranged on the second mass parts 4n but on the third mass part 3n.
  • the third mass part 3n arranged in alignment with the second mass parts 4n between the annular disk parts 24n of the first mass part 2n in the circumferential direction to the recesses 26n in the region of the second mass parts 4n has the radial extension 27n on which the additional masses 20n are arranged on both sides are.
  • the axial width of the additional masses 22n is limited to the axial width of the annular disc parts 24n.
  • FIG. 18 shows the upper part of the ring filter device 1 p in section, which is similar to the ring-type filter device 1 j of FIG. In contrast to this, the third mass part 3p, the radially opposite the disc-shaped first mass portion 2p radially expanded and the two axially opposite second mass parts 4p axially overlapping, for example, annular additional mass 20p.

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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)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un équipement d'amortisseur annulaire (1), en particulier pour une chaîne cinématique d'un véhicule automobile, pourvu d'une première partie de masse (2) agencée de manière à pouvoir tourner autour d'un axe de rotation (d) et de deuxièmes parties de masse (4) agencées de manière répartie sur la périphérie dans le champ de force centrifuge de la première partie de masse (2) tournant autour de l'axe de rotation (d) ainsi que d'une troisième partie de masse (3) pouvant tourner de manière limitée par rapport à la première partie de masse (2). Pour une configuration avantageuse de l'équipement d'amortisseur annulaire (1), un palier oscillant (6) est installé respectivement entre les deuxièmes parties de masse (4) et la première ou la troisième partie de masse (3) et les deuxièmes parties de masse (4) sont logées de manière à pouvoir tourner dans la direction radiale contre la première partie de masse (2) ou la troisième partie de masse (3) ne constituant pas de palier oscillant.
PCT/DE2019/100016 2018-01-17 2019-01-09 Équipement d'amortisseur annulaire WO2019141309A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018100926.7 2018-01-17
DE102018100926 2018-01-17

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WO2019141309A1 true WO2019141309A1 (fr) 2019-07-25

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Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1000629A (fr) * 1946-03-14 1952-02-14 Perfectionnements aux dispositifs destinés à produire des oscillations mécaniques et, notamment, aux amortisseurs dynamiques d'oscillations
FR2857073A1 (fr) * 2003-07-04 2005-01-07 Eric Antoinon Andre Doremus Perfectionnement aux volants d'inertie, en particulier pour vehicule automobile
DE102011101977A1 (de) 2010-05-31 2011-12-01 Schaeffler Technologies Gmbh & Co. Kg Drehschwingungsdämpfer
EP2600030A2 (fr) 2011-12-01 2013-06-05 Schaeffler Technologies AG & Co. KG Convertisseur de couple
WO2014023303A1 (fr) 2012-08-06 2014-02-13 Schaeffler Technologies AG & Co. KG Pendule à force centrifuge et embrayage à friction à pendule à force centrifuge
WO2014114280A1 (fr) 2012-12-20 2014-07-31 Schaeffler Technologies AG & Co. KG Pendule centrifuge
DE102013201981A1 (de) 2013-02-07 2014-08-07 Audi Ag Drehschwingungsdämpfer
DE102013204713A1 (de) * 2013-03-18 2014-09-18 Zf Friedrichshafen Ag Tilgerschwingungsdämpfer
US20150167779A1 (en) * 2012-08-27 2015-06-18 Bayerische Motoren Werke Aktiengesellschaft Centrifugal Pendulum
EP2702296B1 (fr) * 2011-04-28 2016-02-10 ZF Friedrichshafen AG Ensemble de transmission de couple de rotation
DE102015205754A1 (de) * 2015-03-31 2016-10-06 Schaeffler Technologies AG & Co. KG Pendelmasse und Fliehkraftpendeleinrichtung

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1000629A (fr) * 1946-03-14 1952-02-14 Perfectionnements aux dispositifs destinés à produire des oscillations mécaniques et, notamment, aux amortisseurs dynamiques d'oscillations
FR2857073A1 (fr) * 2003-07-04 2005-01-07 Eric Antoinon Andre Doremus Perfectionnement aux volants d'inertie, en particulier pour vehicule automobile
DE102011101977A1 (de) 2010-05-31 2011-12-01 Schaeffler Technologies Gmbh & Co. Kg Drehschwingungsdämpfer
EP2702296B1 (fr) * 2011-04-28 2016-02-10 ZF Friedrichshafen AG Ensemble de transmission de couple de rotation
EP2600030A2 (fr) 2011-12-01 2013-06-05 Schaeffler Technologies AG & Co. KG Convertisseur de couple
WO2014023303A1 (fr) 2012-08-06 2014-02-13 Schaeffler Technologies AG & Co. KG Pendule à force centrifuge et embrayage à friction à pendule à force centrifuge
US20150167779A1 (en) * 2012-08-27 2015-06-18 Bayerische Motoren Werke Aktiengesellschaft Centrifugal Pendulum
WO2014114280A1 (fr) 2012-12-20 2014-07-31 Schaeffler Technologies AG & Co. KG Pendule centrifuge
DE102013201981A1 (de) 2013-02-07 2014-08-07 Audi Ag Drehschwingungsdämpfer
DE102013204713A1 (de) * 2013-03-18 2014-09-18 Zf Friedrichshafen Ag Tilgerschwingungsdämpfer
DE102015205754A1 (de) * 2015-03-31 2016-10-06 Schaeffler Technologies AG & Co. KG Pendelmasse und Fliehkraftpendeleinrichtung

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