EP2547928A1 - Amortisseur d'oscillations de rotation - Google Patents

Amortisseur d'oscillations de rotation

Info

Publication number
EP2547928A1
EP2547928A1 EP11717930A EP11717930A EP2547928A1 EP 2547928 A1 EP2547928 A1 EP 2547928A1 EP 11717930 A EP11717930 A EP 11717930A EP 11717930 A EP11717930 A EP 11717930A EP 2547928 A1 EP2547928 A1 EP 2547928A1
Authority
EP
European Patent Office
Prior art keywords
raceways
flange
torsional vibration
damper
vibration damper
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Withdrawn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
EP11717930A
Other languages
German (de)
English (en)
Inventor
Frank Ferderer
Andreas Knoll
Markus Züfle
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 EP2547928A1 publication Critical patent/EP2547928A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses

Definitions

  • the invention relates to a torsional vibration damper in particular for a drive train of a motor vehicle with a rotatable about an axis of rotation flange and a plurality of circumferentially distributed, arranged on both sides of the flange and relative to these relatively displaceable absorber masses, wherein each two axially opposite, arranged on each side of the flange Tilgermassen by means of the flange axially spaced spacer elements are connected to each other to a Tilgermassenzip, the absorber masses of Tilgermassenschreibs each have two circumferentially spaced first raceways for each rolling element, which roll on to these complementary second raceways of the flange.
  • Generic torsional vibration damper are known as centrifugal pendulum or speed-adaptive absorber.
  • this flange parts are provided, for example, rotationally connected to the crankshaft or an output part of a torsional vibration damper and distributed over the circumference, relative to the flange relatively limited displaceable absorber masses have, depending on the speed of the flange and thus centrifugally dependent pendulum radially and circumferentially oscillate around a neutral point and pay off with appropriate adjustment of the resonance conditions such as pendulum length, mass, swing angle and the like torsional vibrations in the drive train.
  • a torsional vibration damper in conjunction with a torsional vibration damper in the form of a dual mass flywheel in which absorber masses are arranged on both sides of a flange part, wherein the absorber masses lying axially opposite are each connected to a damping mass pair.
  • the Tilgermassenrune are relative to the flange by means of two spaced-apart in the circumferential direction spaced rolling elements, each roll in a raceway of the flange and in raceways of the absorber masses, limited displaceable added to the flange.
  • the type and shape of the raceways specify the pendulum length and the swing angle.
  • the object of the invention is therefore to further develop generic torsional vibration damper such that at reduced production costs contact between the absorber masses and flange are largely excluded.
  • a torsional vibration damper in particular for a drive train of a motor vehicle with a flange rotatable about a rotation axis and a plurality of circumferentially distributed, disposed on both sides of the flange and relative to these relatively displaceable absorber masses, each two axially opposite, on one side of the Flange part arranged absorber masses are connected to each other by means of the flange axially spaced spacer elements to each Tilgermassenzip, the absorber masses of Tilgermassencrus each have two circumferentially spaced first raceways for each rolling element, which roll on to these complementary second raceways of the flange, and contact surfaces between rolling elements and raceways of a respective absorber mass pair are arranged radially within a center of gravity of the absorber mass pair.
  • the raceways are displaced radially inward on the flange part and on the absorber masses.
  • the structure of the proposed torsional vibration damper becomes simple and inexpensive to manufacture while improving vibration and noise performance.
  • this corresponds to a conventional torsional vibration damper with radially inside or at the same height as the center of gravity absorber arranged raceways a pendulum with unstable or indifferentem balance, while the proposed torsional vibration damper resembles a pendulum in a stable equilibrium, the pendulum masses such as absorber masses not against the weight force commute against the centrifugal force.
  • the tracks of the absorber masses are further displaced inwards, for example, arranged in the inner third of the radial extent of the absorber masses.
  • the center of gravity of the absorber masses may each be provided radially outside a first line connecting the two contact surfaces between the rolling elements and the first raceways.
  • the center of gravity of the absorber masses can each be provided radially outside a second line connecting the two contact surfaces between the rolling elements and the second raceways.
  • the center of gravity is arranged outside of a recording of the absorber masses on the flange even if, for example, in the stationary state of the flange without centrifugal force, the absorber masses located radially above the pivot point of the flange due to weight radially outwardly supported on the rolling elements.
  • a renewed acceleration of the flange occurs immediately a stabilization of the absorber masses without passage of an indifferent or unstable position of these absorber masses by the resulting centrifugal force, so that even at very low speeds, a stop the absorber masses can be avoided on the flange.
  • the absorber masses are designed so that the center of gravity is provided in the circumferential direction between the circumferentially spaced raceways of a Tilgermassencrus. Ideally, the absorber masses are formed symmetrically to a radial section through the center of gravity.
  • the rolling elements are secured against loss in the recesses for the formation of the raceways of the absorber masses by providing captive securing devices for these on the sides of the absorber masses facing away from the flange part.
  • These may be formed by cover plates, which are provided with opposite the opening surfaces of the raceways narrowed opening surfaces or have no openings.
  • the cover plates may be formed from sheet metal, so that the Tilgermassenforme are formed exclusively of metal.
  • Particularly advantageous may be a material deformation, for example, as a molded nose in the outer surface of the absorber mass, which secure the rolling elements axially before emigrating. In this way, the number of parts can be further reduced, so that a self-stabilized and provided with a captive Tilgermassencovercover from only six parts - two absorber masses, two rolling elements and two spacers can be formed.
  • a torsional vibration damper with two mutually counteracting the effect of circumferentially effective energy storage relatively rotatable damper parts, which is formed with the proposed torsional vibration, wherein one of the two damper parts, an input part or an output part of the torsional vibration damper forms the flange of the torsional vibration damper.
  • the torsional vibration damper may for example be a dual-mass flywheel, wherein the flange preferably from the formed with the secondary flywheel damper part for acting on the energy storage as bow springs is formed.
  • the flange part can have radially outwardly extended arms, which act on the output side of the end faces of the bow springs in the circumferential direction.
  • FIG. 2 is a view of the torsional vibration damper of FIG. 1;
  • FIG. 3 is an exploded view of the torsional vibration damper of FIGS. 1 and 2;
  • Figure 4 is a partial view of the torsional vibration damper according to the invention.
  • FIG. 1 shows the upper half of a torque transmission device 1 arranged about an axis of rotation 2, which is arranged in a drive train of a motor vehicle between an internal combustion engine (not shown) and a transmission (also not shown).
  • the torque transmission device 1 comprises a dual-mass flywheel 3, on the secondary flywheel 4 of the torsional vibration damper 5 is arranged in function of a centrifugal pendulum.
  • the torsional vibration damper 5 is formed according to the prior art and is to explain the typical structure and function of such torsional vibration damper and their example, use in a drive train of a motor vehicle of the invention shown in Figure 5 in partial view torsional vibration damper 5a closer.
  • the secondary flywheel 4 also receives a friction clutch 6, which is designed as a three-disc clutch.
  • the friction clutch 6 builds radially smaller at a high transmittable torque compared with a two-disc clutch, so that the torsional vibration damper 5 can be arranged axially adjacent to the energy accumulators 7 of the dual-mass flywheel 3 approximately at the same radial height.
  • torsional vibration dampers can be arranged radially inside the energy store 7.
  • the flange portion 8 of the torsional vibration damper 5 is formed as a ring member 9 and received by means distributed over the circumference rivets 10 on the friction clutch 6.
  • the pitch of the rivets 10 is adjusted over the circumference so that they are synchronous to the bolt circle of the friction clutch 6.
  • the rivets 10 can be used at the same time for riveting the friction clutch 6 with the secondary flywheel 4.
  • the rivets 10 may be riveted circumferentially adjacent the riveting of the friction clutch 6 to the secondary flywheel 4 in separate mounting holes of the secondary flywheel.
  • Figure 2 shows the torsional vibration damper 5 in view.
  • Flange part 8 takes in the embodiment shown six distributed over the circumference Tilgermassencovere 12, which are each formed of two axially opposing absorber masses 11. Between the Tilgermassencoveren 12, the axially aligned rivets 10 are provided, which are riveted to the secondary flywheel 4 ( Figure 1), so that the riveting of the centrifugal pendulum takes place at the same radial height as the absorption of the absorber mass pairs 12 on the flange 8. In this way, a torsional vibration damper 5 can be proposed with low radial space requirements.
  • the rivets 10 may have annular discs 14, which may serve as a stop buffer 15, and may be made of elastic material such as rubber, rubber such as HNBR, NBR or the like.
  • Figure 3 shows the torsional vibration damper 5 in an exploded view with the flange 8, the rivets 10 with the annular discs 14 and the absorber masses 11 and spacers 16 as spacers, by means of which the axially opposing absorber masses 11 are interconnected.
  • the Tilgermassensectione 12 thus formed (Figure 2) are received limited pivotally on the flange 8.
  • the rolling elements 13 designed as cylindrical rollers 17 roll on the raceways 18, 19 formed by cutouts in the absorber masses 11 and in the flange part. Between the cutouts, a single opening 20 is provided for the spacer elements 16.
  • the spacer elements 16 can therefore be arranged closer to one another, so that the opening 20 requires less installation space than a plurality of individual openings, as a result of which the cutouts of the raceways 18 are closer to one another. can be arranged and thus the number of absorber masses 11 can be increased over the circumference can be increased.
  • the spacer elements 16 receive between them the stop buffer 21, which can be used alternatively or in addition to the annular discs and formed from the same material. In an additional arrangement, for example, multi-stage impact behavior can be achieved.
  • the spacing of the absorber masses 11 from the flange part 8 takes place through the cover disks 22.
  • Figure 4 shows the torsional vibration damper 5a according to the invention, which can replace the torsional vibration damper 5 of Figures 1 to 3 in the embodiment shown and is also suitable for other embodiments, in partial view.
  • the center of gravity S of the absorber masses 11a is arranged radially outside the raceways 18a of the flange part 8a and the hidden raceways 19a of the absorber masses 11a, which are therefore only shown in dashed lines.
  • the center of gravity S results essentially from the shape of the absorber masses 11a.
  • the raceways 18a, 19a are therefore displaced inwardly so that both the drawn between the radially outer contact surfaces 29 of the arranged in the flange portion raceways 18a first line 23 and drawn between the radially inner contact surfaces 30 of the provided in the absorber masses 11a raceways second Line 24 lies radially within the center of gravity S.
  • a stable pendulum balance is attained when starting the flange part 8a for an absorber mass pair 12a which is supported inwardly over the raceway 19a by self-stabilizing it by the center of gravity S provided radially outside the raceways 19a is.
  • the flange part 8a As an output-side flange part of a dual-mass flywheel with energy stores arranged radially outside the absorber masses 11a, the flange part 8a has radially expanded arms 28 for acting on these.
  • the absorber masses have an integrally formed as embossed nose 31, which serves as a captive 32 for the rolling elements 13a.
  • an absorber mass pair 12a can be formed entirely of metal and only of two absorber masses 11a, the spacer elements 16a and the rolling bodies 13a.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un amortisseur d'oscillations de rotation en particulier pour une chaîne cinématique d'un véhicule automobile, comprenant une partie flasque pouvant être mise en rotation autour d'un axe de rotation, et plusieurs masselottes d'amortissement réparties sur la circonférence, disposées des deux côtés de la partie flasque et susceptibles de se déplacer relativement à cette partie, deux masselottes d'amortissement mutuellement opposées dans la direction axiale, disposées chacune d'un côté de la partie flasque étant reliées l'une à l'autre au moyen d'éléments entretoises qui traversent la partie flasque dans la direction axiale pour former une paire de masselottes d'amortissement, les masselottes d'amortissement d'une paire de masselottes d'amortissement présentant chacune deux premiers chemins de roulement espacés l'un de l'autre dans la direction circonférentielle, et destinés chacun à un corps roulant, les corps roulants roulant contre des deuxièmes chemins de roulement de la partie flasque qui sont complémentaires des premiers. Pour améliorer la stabilité de l'amortisseur d'oscillations de rotation et abaisser ses coûts de fabrication, il est proposé de disposer les surfaces de contact entre le corps roulants et chemins de roulement de chaque paire de masselottes d'amortissement radialement à l'intérieur par rapport au centre de gravité de la paire de masselottes d'amortissement.
EP11717930A 2010-03-15 2011-02-24 Amortisseur d'oscillations de rotation Withdrawn EP2547928A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010011449 2010-03-15
PCT/DE2011/000181 WO2011113410A1 (fr) 2010-03-15 2011-02-24 Amortisseur d'oscillations de rotation

Publications (1)

Publication Number Publication Date
EP2547928A1 true EP2547928A1 (fr) 2013-01-23

Family

ID=44169568

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11717930A Withdrawn EP2547928A1 (fr) 2010-03-15 2011-02-24 Amortisseur d'oscillations de rotation

Country Status (4)

Country Link
EP (1) EP2547928A1 (fr)
CN (1) CN102713342B (fr)
DE (2) DE102011012276A1 (fr)
WO (1) WO2011113410A1 (fr)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2981714B1 (fr) * 2011-10-19 2013-11-01 Valeo Embrayages Systeme d'amortissement de type oscillateur pendulaire comportant un dispositif de guidage perfectionne
FR2989753B1 (fr) * 2012-04-20 2014-04-18 Valeo Embrayages Dispositif d'amortissement pendulaire, en particulier pour une transmission de vehicule automobile
DE112013003490A5 (de) 2012-07-12 2015-03-19 Schaeffler Technologies Gmbh & Co. Kg Drehzahladaptiver Schwingungstilger und Drehschwingungsdämpfer mit diesem
DE102012218926B4 (de) * 2012-10-17 2021-01-14 Zf Friedrichshafen Ag Drehschwingungsdämpfungsanordnung mit Vorspannung
DE102014207229A1 (de) * 2013-05-06 2014-11-06 Schaeffler Technologies Gmbh & Co. Kg Fliehkraftpendel
FR3006731B1 (fr) * 2013-06-11 2016-01-01 Valeo Embrayages Transmission comportant un dispositif de filtration de type oscillateur pendulaire et module pour une transmission
DE102014213598A1 (de) * 2013-07-22 2015-01-22 Schaeffler Technologies Gmbh & Co. Kg Berstschutzeinrichtung mit einem Rotationszentrum für eine Reibkupplung
FR3010162B1 (fr) * 2013-08-27 2015-08-21 Valeo Embrayages Dispositif d'amortissement, notamment pour une transmission de vehicule automobile
FR3010469B1 (fr) * 2013-09-10 2016-12-09 Valeo Embrayages Dispositif d'absorption de vibrations
US10240658B2 (en) * 2014-01-08 2019-03-26 Toyota Jidosha Kabushiki Kaisha Torsional vibration damping device
US10443681B2 (en) * 2014-04-01 2019-10-15 Schaeffler Technologies AG & Co. KG Centrifugal pendulum
FR3021080B1 (fr) 2014-05-16 2020-02-21 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
FR3021082B1 (fr) 2014-05-16 2016-05-13 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
DE102014211728A1 (de) * 2014-06-18 2015-12-24 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
FR3031369B1 (fr) * 2015-01-07 2017-10-20 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
FR3033858B1 (fr) * 2015-03-16 2017-10-20 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion pour systeme de transmission de vehicule
JP6508710B2 (ja) * 2015-03-23 2019-05-08 本田技研工業株式会社 遠心振子式制振装置
DE102015216161A1 (de) * 2015-08-25 2017-03-02 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
CN108027008B (zh) * 2015-09-18 2020-04-14 舍弗勒技术股份两合公司 扭矩传递装置
DE102018103612A1 (de) * 2017-03-22 2018-09-27 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung
FR3090779B1 (fr) 2018-12-19 2021-04-23 Valeo Embrayages Dispositif d'amortissement pendulaire
DE102019101960A1 (de) * 2019-01-28 2020-07-30 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung mit Endanschlag
CN113124101B (zh) * 2019-12-31 2022-12-09 惠州比亚迪电池有限公司 扭转减震器

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JP4797176B2 (ja) 2001-06-12 2011-10-19 シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト トルク伝達装置
JP4455858B2 (ja) * 2003-09-30 2010-04-21 アイシン精機株式会社 トーションダンパ
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DE102006028556B4 (de) * 2005-07-11 2019-10-10 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung
EP1780434A3 (fr) * 2005-10-29 2009-01-14 LuK Lamellen und Kupplungsbau Beteiligungs KG Dispositif d'embrayage
DE102006028552B4 (de) * 2005-10-29 2024-05-08 Schaeffler Technologies AG & Co. KG Kupplungseinrichtung mit Kupplungsscheibe
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JP5283095B2 (ja) * 2008-06-02 2013-09-04 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト 遠心力振り子を備えるトーショナルバイブレーションダンパ
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Also Published As

Publication number Publication date
WO2011113410A1 (fr) 2011-09-22
DE102011012276A1 (de) 2011-09-15
CN102713342A (zh) 2012-10-03
CN102713342B (zh) 2015-01-14
DE112011100918A5 (de) 2013-01-03

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