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WO2017167329A1 - Dispositif pendulaire centrifuge et dispositif de transmission de couple - Google Patents

Dispositif pendulaire centrifuge et dispositif de transmission de couple Download PDF

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Publication number
WO2017167329A1
WO2017167329A1 PCT/DE2017/100240 DE2017100240W WO2017167329A1 WO 2017167329 A1 WO2017167329 A1 WO 2017167329A1 DE 2017100240 W DE2017100240 W DE 2017100240W WO 2017167329 A1 WO2017167329 A1 WO 2017167329A1
Authority
WO
WIPO (PCT)
Prior art keywords
pendulum
damping
centrifugal
masses
pendulum mass
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.)
Ceased
Application number
PCT/DE2017/100240
Other languages
German (de)
English (en)
Inventor
Peter Roland
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
Priority to DE112017001690.8T priority Critical patent/DE112017001690A5/de
Publication of WO2017167329A1 publication Critical patent/WO2017167329A1/fr
Anticipated expiration legal-status Critical
Ceased 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 device, in particular for a torque transmission device, the centrifugal pendulum device comprising a rotation axis, a pendulum mass carrier rotatable about the rotation axis, pendulum masses and rolling elements, the pendulum mass carrier having recesses, the pendulum masses each having an intermediate piece and two side parts, wherein the spacers each in a recess and the rolling elements are arranged to the displaceable arrangement of the pendulum masses radially outside between the intermediate pieces and the pendulum mass carrier.
  • the invention relates to a torque transmission device, in particular for a drive train of a motor vehicle driven by a combustion engine.
  • a centrifugal damping device in particular for a motor vehicle transmission, comprising at least one pendulum mass, of which a central part is movably mounted on a support element, suitable for pivoting about an axis, and comprising at least one roller, which is radially between the radially outer periphery of the central part and a radially outer part of the support member is mounted such that during operation, the central part of the pendulum mass and the roller radially outboard adjoin the roller and the support member in turn radially outboard adjoin one another, wherein the pendulum mass has two side parts, the fixed to the central part and are designed such that the center of gravity of the pendulum mass is located radially outside the contact areas between the central part of the pendulum mass and the roller.
  • each of the two side parts of a pendulum mass has a pin.
  • the support element has arcuate slots in an annular web.
  • the pins are guided in the arcuate oblong holes of the support element and limit in the end positions a displaceability of the pendulum mass by abutment at the peripheral ends of the elongated holes.
  • Each central part has elastically deformable damping means at its peripheral ends and its radially inner edge, which serve to abut against peripheral ends and a radially inner edge of a corresponding window. An impression of the damping means is limited by abutment of the pins at the peripheral ends of the slots.
  • the invention has for its object to improve a centrifugal pendulum device mentioned above structurally and / or functionally.
  • the invention has the object, structurally and / or functionally to improve a torque transmission device mentioned above.
  • centrifugal pendulum device with the features of claim 1.
  • the statements "axially”, “radially” and “in the circumferential direction” refer to an extension direction of the axis of rotation of the centrifugal pendulum device.
  • “Axial” then corresponds to an extension direction
  • “Radial” is then a direction perpendicular to the direction of extension of the axis of rotation of the centrifugal pendulum device and intersecting with the axis of rotation of the centrifugal pendulum means.
  • the centrifugal pendulum device can be used for arrangement on a torque transmission device, in particular in a drive train of a vehicle.
  • the centrifugal pendulum device can serve to eliminate torsional vibrations.
  • the centrifugal pendulum device can serve to improve an efficiency of a torsional vibration damper.
  • the pendulum mass carrier may have a disc-like or annular disk-like shape.
  • the pendulum mass carrier can be made in one piece.
  • the pendulum mass carrier may have a flange-like shape.
  • the pendulum mass carrier can carry a carrier have gerflansch.
  • the support flange can be used for bilateral arrangement of pendulum mass parts.
  • the recesses can serve for the displaceable arrangement of the pendulum masses on the pendulum mass carrier.
  • the pendulum mass carrier may have a recess for each pendulum mass.
  • the recesses can each serve to receive an intermediate piece of a pendulum mass.
  • the recesses can serve to receive the rolling elements.
  • the pendulum mass carrier may have web sections. The web sections can limit the recesses.
  • the recesses may each have an arcuate shape.
  • the recesses may each have an edge.
  • the recesses may each have a peripheral edge.
  • the edges of the recesses may each have an abutment portion.
  • the abutment portions of the edges of the recesses can each serve to swing angle limiting a pendulum mass.
  • the abutment portions of the edges of the recesses may each correspond to an abutment portion of an edge of an intermediate piece.
  • the edges of the recesses may each have at least one track section for a rolling element.
  • the path portions of the edges of the recesses may each have an arcuate shape.
  • the path portions of the edges of the recesses may serve to determine a pendulum track with.
  • the pendulum masses can be arranged eccentrically to the axis of rotation.
  • the pendulum masses may each have an arcuate shape.
  • the pendulum masses may each have two circumferentially directed ends.
  • the intermediate pieces can each be arranged between two side parts.
  • the side parts of a pendulum mass may each have two circumferentially directed ends.
  • the side parts of a pendulum mass can each have the same contours.
  • the side parts of a pendulum mass can each be larger than the spacers.
  • the side parts of a pendulum mass can each be designed without recesses for the representation of a pendulum track.
  • the side parts of a pendulum mass can each be carried out at least approximately completely closed.
  • the sides of a pendulum mass can each have a maximized mass.
  • the side parts and the intermediate piece of a pendulum mass can each firmly connected to each other, in particular riveted.
  • the pendulum masses can each be arranged with their spacers in the recesses of the pendulum mass carrier.
  • the Side parts can be arranged on both sides of the pendulum mass carrier.
  • the spacers may each have an edge.
  • the intermediate pieces may each have a peripheral edge.
  • the edges of the intermediate pieces may each have a contact portion.
  • the abutment sections of the edges of the intermediate pieces can each serve to limit the oscillation angle of a pendulum mass.
  • the abutment portions of the edges of the intermediate pieces can each correspond to a contact portion of a rim of a recess.
  • the edges of the intermediate pieces may each have at least one track section for a rolling element.
  • the track portions of the edges of the intermediate pieces may each have an arcuate shape.
  • the track sections of the edges of the intermediate pieces can serve to determine a pendulum track with.
  • the centrifugal pendulum device may have a plurality, for example four, pendulum masses.
  • the pendulum masses can each be connected to the pendulum mass carrier bifilar.
  • the pendulum masses can each be connected to the pendulum mass carrier monofilar.
  • the pendulum masses can each be displaced under centrifugal force in an operating position. In the operating position, the pendulum masses can be displaced under the action of torsional vibrations. In the operating position, the pendulum masses can each be displaced to eliminate torsional vibrations.
  • the pendulum masses can each be displaced starting from a middle position between two end positions.
  • the pendulum masses can each be displaceable along a pendulum track.
  • the rolling elements can each be arranged on a track section of a rim of a recess and on a track section of an edge of an intermediate piece.
  • the rolling elements can each have a disc-like shape.
  • the centrifugal pendulum device can have two rolling elements for each pendulum mass.
  • the at least one first damping element can be arranged at one end of a pendulum mass.
  • the at least one first damping element can be arranged on a side part.
  • the at least first damping element may be arranged at one end of a side part of a pendulum mass.
  • the pendulum masses may each have two first damping elements. On each side part can a first damping element may be arranged.
  • the first damping elements may be arranged in opposite directions in the circumferential direction.
  • the pendulum masses may each have at least one second damping element for system damping on the pendulum mass carrier.
  • the at least one second damping element can be arranged on the intermediate piece.
  • the pendulum masses may each have two second damping elements.
  • the second damping elements may be arranged on the intermediate piece in the circumferential direction end.
  • the damping elements can be elastic.
  • the damping elements may be made of an elastomer.
  • the damping elements may be fixed in force, shape and / or material fit.
  • the recesses may each have an edge with a contact portion.
  • the intermediate pieces may each have an edge with a contact portion.
  • "directly corresponding" means that the recess-side abutment section and the abutment-side abutment section can come into abutment without the interposition of a damping element may be made of a metal, in particular of a steel
  • the abutment-side abutment section may extend in the circumferential direction over a predominant length of the intermediate piece.
  • Axialabstandsetti can be arranged between the pendulum mass carrier and the side parts.
  • the Axialabstands institute can be arranged on the side parts and / or on the intermediate part.
  • the Axialabstandsetti can serve to reduce friction.
  • the Axialabstandsetti can each be made of a plastic.
  • the Axialabstandsetti can each be made of a material paired with steel has a lower coefficient of friction than steel on steel.
  • the Axialabstandsetti can each be a plug-like Form having a head portion and a shaft portion.
  • the side parts and / or the intermediate parts can each have recesses for receiving the axial spacing elements. The recesses can be executed like a blind hole.
  • the torque transmitting device can be used for arrangement in a drive train of a vehicle.
  • the torque transmission device may be a single-mass flywheel, a torsional vibration damper, in particular two-mass flywheel, a friction clutch device, a hydrodynamic torque converter, an accessory drive or a crankshaft of an internal combustion engine.
  • the invention provides, inter alia, a mass-optimized centrifugal pendulum.
  • the pendulum mass can be maximized while maintaining a space and a maximum surface pressure.
  • a total energy absorption capacity of damping elements in the centrifugal pendulum can be increased. Operating conditions in which rattling noises are generated due to steel / steel contacts, can be reduced or avoided.
  • the pendulum mass can be increased by reducing or eliminating cutouts for trajectories in the pendulum mass plates.
  • a total of available radial space can be used to maximize pendulum mass plates.
  • Pendulum tracks can be displayed in an intermediate piece.
  • the intermediate piece can be riveted to the pendulum mass plates. Due to its volume, the intermediate piece can contribute to increasing a moving hammer mass.
  • Rolling elements can be designed as disks, so that advantages with regard to surface pressure and component costs can be achieved. Cylindrical roller rims on the Wälzköpern can be omitted, so there is more axial space for a flange available. This allows a flange diameter for the same axial space be enlarged.
  • a pendulum package may have four damping elements.
  • a shuttle package may have two main damping elements.
  • a total energy absorption capacity can be increased by engaging all the damping elements of a shuttle package.
  • the main damping elements can each be mounted externally on an intermediate piece.
  • the main damping elements can be supported from a contact angle on the flange (left + right damping element).
  • a damping element can be mounted on the front side (on one side) on a pendulum mass sheet metal.
  • a reverse arrangement of the pendulum mass plates may result in a damping element on both sides of the pendulum package.
  • damping elements can ultimately be engaged at the same time per shuttle package. This results in a significantly increased energy absorption capacity.
  • the case that an actuation path of the damping elements is exceeded and thus an oscillation angle limit (end stop) of steel / steel occurs is significantly reduced. This reduces wear and noise during operation.
  • an end-cut can take place at block angle.
  • the intermediate piece can run radially inwards on the flange (steel / steel). The resulting large contact surface switches off wear.
  • the intermediate piece can be guided so closely in an associated flange window that falling out of the rollers is prevented.
  • An additional pin which prevents falling of the pendulum mass package and thus the possible falling out of the roles in the state, can thus be omitted.
  • Through the use of spacers friction can be significantly reduced at an axial start of the pendulum mass package on the flange. An uncontrolled waving of the pendulum masses at start / stop is prevented.
  • Pendulum masses can move uniformly due to limited movement possibilities.
  • the pendulum mass packages can abut each other at large oscillation angles and form a stable circular ring.
  • an eradication and / or damping of torsional vibrations is improved.
  • An isolation of torsional vibrations is improved.
  • An effective pendulum mass is increased.
  • a space utilization is improved.
  • a maximum surface pressure is limited. Noise is reduced.
  • An energy absorption capacity is increased. Driving comfort is increased.
  • FIG. 1 is a fragmentary view of a centrifugal pendulum device with a pendulum mass carrier, pendulum masses and damping elements for mutual system damping in a perspective view
  • Fig. 2 is a centrifugal pendulum device with a pendulum mass carrier, pendulum masses and damping elements for mutual system damping in exploded view
  • FIG. 3 shows a detail of a centrifugal pendulum device with a pendulum mass carrier, pendulum masses and damping elements for mutual damping in the middle position
  • FIG. 4 shows a detail of a centrifugal pendulum device with a pendulum mass carrier, pendulum masses and damping elements for mutual system damping in a damped end position and 5 a detail of a centrifugal pendulum device with a pendulum mass carrier, pendulum masses and damping elements for mutual system damping at swing angle limitation in an end position.
  • Fig. 1 shows a detail of a centrifugal pendulum device 100 with a pendulum mass carrier 102, pendulum masses, such as 104, and damping elements 106, 108, 1 10, 1 12 for mutual system damping in a perspective view.
  • Fig. 2 shows the centrifugal pendulum device 100 in an exploded view.
  • Fig. 1 shows a detail of a centrifugal pendulum device 100 with a pendulum mass carrier 102, pendulum masses, such as 104, and damping elements 106, 108, 1 10, 1 12 for mutual system damping in a perspective view.
  • FIG. 3 shows a detail of the centrifugal pendulum device 100 in the middle position.
  • FIG. 4 shows, in detail, the centrifugal pendulum device 100 in a damped end position.
  • Fig. 5 shows a detail of the centrifugal pendulum device 100 at swing angle limitation in an end position.
  • the centrifugal pendulum device 100 serves to be arranged on a torque transmission device in order to eliminate torsional vibrations.
  • a flange part of an output part of a dual-mass flywheel serves as a pendulum mass carrier 102.
  • the flange part has an annular disk section and, extending radially outward from the annular disk section, extensions for supporting bow springs.
  • the pendulum mass carrier 102 has a recess for each pendulum mass 104, such as 1 14, on.
  • the pendulum mass 104 has an intermediate piece 1 16 and two side parts 1 18, 120.
  • the intermediate piece 1 16 is arranged in the recess 1 14.
  • the side parts 1 18, 120 are arranged axially on both sides of the pendulum mass carrier 102.
  • the intermediate piece 1 16 and the side parts 1 18, 120 are firmly connected to each other by means of rivets, such as 122.
  • the recess 1 14 has a peripheral edge with a contact portion 124 and two track sections 126, 128.
  • the contact portion 124 of the recess 1 14 is disposed radially inwardly of the recess 1 14, convex and extends in the circumferential direction over a predominant length of the recess 1 14.
  • the web portions 126, 128 of the recess 1 14 are arranged radially on the recess 1 14 on the outside and each arc-shaped concave.
  • the intermediate piece 1 16 has a peripheral edge with a contact portion 130 and two track sections 132, 134.
  • the abutment portion 130 of the intermediate piece 1 16 is radially inwardly disposed on the intermediate piece 1 16, convexly shaped and extends in the circumferential direction over a predominant length of the intermediate piece 1 16.
  • the track portions 132, 134 of the intermediate piece 1 16 are on the intermediate piece 1 16 radially outside arranged and concavely curved in each case.
  • the intermediate piece 1 16 is smaller than the recess 1 14, so that the intermediate piece 1 16 in the recess 1 14 is limited displaced.
  • the centrifugal pendulum device disk-shaped rolling elements 136, 138 on.
  • the rolling elements 136, 138 are arranged between the intermediate piece 1 16 and the pendulum mass carrier 102.
  • the intermediate piece 1 16 is guided with its track sections 132, 134 on the rolling elements 136, 138, which in turn roll on the track sections 126, 128 of the recess 1 14.
  • the pendulum mass 104 is displaced under the action of torsional vibrations, starting from a middle position along a pendulum track between two end positions in order to eliminate torsional vibrations.
  • the middle position is shown in FIG.
  • An end position is shown in FIGS. 4 and 5.
  • the side part 1 18 has at one end a first damping element 106.
  • the side part 120 has at one end a first damping element 108.
  • the damping elements 106, 108 are arranged at mutually circumferentially opposite ends of the side parts 1 18.
  • the first damping elements 106, 108 serve for mutual damping of adjacent pendulum masses 104.
  • the intermediate piece 1 16 has at each of its circumferentially opposite ends a second damping element 1 10, 1 12.
  • the second damping elements 1 10, 1 12 are used for damping the pendulum mass 104 on the pendulum mass carrier 102. In the end position of the pendulum mass 104 shown in Fig.
  • the pendulum masses 104 are in the circumferential direction with the interposition of the first damping elements 106, 108 to each other and form a stable circular ring.
  • the intermediate piece 1 16 is located with the interposition of the second damping element 1 12 at one end of the recess 1 14 at.
  • the abutment portion 130 of the intermediate piece 1 16 is spaced from the contact portion 124 of the recess 1 14.
  • the damping element 106, 108, 1 12 In a further displacement of the pendulum mass 104 soft the damping element 106, 108, 1 12 further, until the contact portion 130 of the intermediate piece 1 16 and the contact portion 124 of the recess 1 14, as shown in Fig. 5, come into abutment with each other.
  • the intermediate piece 1 16 and the pendulum mass carrier 102 are made of steel. Between the abutment portion 130 of the intermediate piece 16 and the abutment portion 124 of the recess 14, a steel-steel contact thus occurs. This achieves a swing angle limitation or limit switch-off.
  • the mutual contact of the abutment portion 130 of the intermediate piece 1 16 and the abutment portion 124 of the recess 1 14 is effected by means of the damping elements 106, 108, 1 12 damped. Also due to the large surface of the abutment sections 124, 130 a maximum occurring surface pressure is limited.
  • Axialabstands institute such as 140
  • the Axialabstands institute 140 each have a plug-like shape with a head portion and a shaft portion and are in blind hole-like recesses of the side parts 1 18, 120 inserted.
  • the Axialabstands institute 140 serve to friction reduction and are made of a plastic which paired with steel has a lower coefficient of friction than steel on steel. LIST OF REFERENCES

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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)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un dispositif pendulaire centrifuge (100), notamment pour un dispositif de transmission de couple, le dispositif pendulaire centrifuge (100) présentant un axe de rotation, un support de masse de pendule (102) rotatif autour de l'axe de rotation, une masse de pendule (104) et un corps de roulement (136, 138), le support de masse de pendule (102) présentant des cavités (114), les masses de pendule (104) présentant respectivement une pièce intermédiaire (116) et deux pièces latérales (118, 120), les pièces intermédiaires (116) étant disposées respectivement dans une cavité (114) et le corps de roulement (136, 138) pour une disposition mobile des masses de pendule (104), radialement côté externe entre les pièces intermédiaires (116) et le support de masse de pendule (102), les masses de pendule (104) présentant respectivement au moins un premier élément d'amortissement (106, 108) pour l'amortissement mutuel de l'installation, et un dispositif de transmission de couple, notamment pour un groupe motopropulseur d'un véhicule automobile entraîné par un moteur à combustion interne, le dispositif de transmission de couple présentant un tel dispositif pendulaire centrifuge (100).
PCT/DE2017/100240 2016-04-01 2017-03-24 Dispositif pendulaire centrifuge et dispositif de transmission de couple Ceased WO2017167329A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112017001690.8T DE112017001690A5 (de) 2016-04-01 2017-03-24 Fliehkraftpendeleinrichtung und Drehmomentübertragungseinrichtung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016205420.1 2016-04-01
DE102016205420.1A DE102016205420A1 (de) 2016-04-01 2016-04-01 Fliehkraftpendeleinrichtung und Drehmomentübertragungseinrichtung

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WO2017167329A1 true WO2017167329A1 (fr) 2017-10-05

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PCT/DE2017/100240 Ceased WO2017167329A1 (fr) 2016-04-01 2017-03-24 Dispositif pendulaire centrifuge et dispositif de transmission de couple

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110242699A (zh) * 2018-03-08 2019-09-17 博格华纳公司 扭矩传递装置、具有其的驱动系和用于其的离心摆装置
WO2020157169A1 (fr) * 2019-01-31 2020-08-06 Valeo Embrayages Dispositif d'amortissement pendulaire
KR20220030297A (ko) * 2019-08-09 2022-03-10 발레오 카펙 토크 컨버터스 (난징) 씨오., 엘티디. 원심 진자, 원심 진자를 포함하는 토크 전달 장치, 및 차량

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DE102016124814A1 (de) 2016-12-19 2018-06-21 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung und Drehmomentübertragungseinrichtung
DE102016125380A1 (de) 2016-12-22 2018-06-28 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung und Drehmomentübertragungseinrichtung
DE102017113054A1 (de) 2017-06-14 2018-12-20 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung und Drehmomentübertragungseinrichtung
JP7024598B2 (ja) * 2017-09-07 2022-02-24 日本精工株式会社 遠心振り子ダンパ及びトルク伝達装置
DE102018120943A1 (de) * 2018-08-28 2020-03-05 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
DE102022108250A1 (de) 2022-04-06 2023-10-12 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung mit Anschlag für die Pendelmassen

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WO2013156733A1 (fr) 2012-04-20 2013-10-24 Valeo Embrayages Dispositif d'amortissement pendulaire, en particulier pour une transmission de véhicule automobile
DE102013214155A1 (de) * 2012-08-06 2014-02-06 Schaeffler Technologies AG & Co. KG Fliehkraftpendel und Reibungskupplung mit Fliehkraftpendel
FR3009853A1 (fr) * 2013-08-23 2015-02-27 Valeo Embrayages Procede de montage d'un dispositif d'amortissement pendulaire
WO2015150651A1 (fr) * 2014-04-04 2015-10-08 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
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EP3101312A1 (fr) * 2015-06-01 2016-12-07 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion

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FR3010467B1 (fr) * 2013-09-10 2016-12-09 Valeo Embrayages Dispositif d'absorption de vibrations
FR3013415B1 (fr) * 2013-11-15 2016-05-27 Valeo Embrayages Dispositif simplifie d'amortissement de torsion a pendule

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Publication number Priority date Publication date Assignee Title
DE102009042812A1 (de) * 2008-11-24 2010-05-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torsionsdämpfungseinrichtung
WO2013156733A1 (fr) 2012-04-20 2013-10-24 Valeo Embrayages Dispositif d'amortissement pendulaire, en particulier pour une transmission de véhicule automobile
DE102013214155A1 (de) * 2012-08-06 2014-02-06 Schaeffler Technologies AG & Co. KG Fliehkraftpendel und Reibungskupplung mit Fliehkraftpendel
FR3009853A1 (fr) * 2013-08-23 2015-02-27 Valeo Embrayages Procede de montage d'un dispositif d'amortissement pendulaire
WO2015150651A1 (fr) * 2014-04-04 2015-10-08 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion
US20150362041A1 (en) * 2014-06-16 2015-12-17 Valeo Embrayages Torsional vibration damper for hydrokinetic torque coupling device
EP3101312A1 (fr) * 2015-06-01 2016-12-07 Valeo Embrayages Dispositif d'amortissement d'oscillations de torsion

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110242699A (zh) * 2018-03-08 2019-09-17 博格华纳公司 扭矩传递装置、具有其的驱动系和用于其的离心摆装置
WO2020157169A1 (fr) * 2019-01-31 2020-08-06 Valeo Embrayages Dispositif d'amortissement pendulaire
FR3092375A1 (fr) * 2019-01-31 2020-08-07 Valeo Embrayages Dispositif d’amortissement pendulaire
CN113454362A (zh) * 2019-01-31 2021-09-28 法雷奥离合器公司 摆式阻尼装置
KR20210118090A (ko) * 2019-01-31 2021-09-29 발레오 앙브라이아쥐 진자 댐핑 장치
US11680623B2 (en) 2019-01-31 2023-06-20 Valeo Embrayages Pendular damping device
KR102879864B1 (ko) 2019-01-31 2025-10-31 발레오 앙브라이아쥐 진자 댐핑 장치
KR20220030297A (ko) * 2019-08-09 2022-03-10 발레오 카펙 토크 컨버터스 (난징) 씨오., 엘티디. 원심 진자, 원심 진자를 포함하는 토크 전달 장치, 및 차량
KR102683356B1 (ko) 2019-08-09 2024-07-08 발레오 카펙 토크 컨버터스 (난징) 씨오., 엘티디. 원심 진자, 원심 진자를 포함하는 토크 전달 장치, 및 차량

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