WO2008058499A2 - Roue d'entraînement comportant au moins une poulie d'entraînement - Google Patents

Roue d'entraînement comportant au moins une poulie d'entraînement Download PDF

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Publication number
WO2008058499A2
WO2008058499A2 PCT/DE2007/001878 DE2007001878W WO2008058499A2 WO 2008058499 A2 WO2008058499 A2 WO 2008058499A2 DE 2007001878 W DE2007001878 W DE 2007001878W WO 2008058499 A2 WO2008058499 A2 WO 2008058499A2
Authority
WO
WIPO (PCT)
Prior art keywords
drive
drive wheel
wheel according
input
input flange
Prior art date
Application number
PCT/DE2007/001878
Other languages
German (de)
English (en)
Other versions
WO2008058499A3 (fr
Inventor
Steffen Lehmann
Christian Fechler
Dimitri Sieber
Original Assignee
Luk Lamellen Und Kupplungsbau Beteiligungs 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 Luk Lamellen Und Kupplungsbau Beteiligungs Kg filed Critical Luk Lamellen Und Kupplungsbau Beteiligungs Kg
Priority to DE112007002507.7T priority Critical patent/DE112007002507B4/de
Publication of WO2008058499A2 publication Critical patent/WO2008058499A2/fr
Publication of WO2008058499A3 publication Critical patent/WO2008058499A3/fr

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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • 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
    • F16F15/1203—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 characterised by manufacturing, e.g. assembling or testing procedures for the damper units
    • 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
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
    • F16F15/1442—Elastomeric springs, i.e. made of plastic or rubber with a single mass
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F16H2055/366—Pulleys with means providing resilience or vibration damping

Definitions

  • the invention relates to a drive wheel with at least one drive disk, in particular a pulley, and with a torsional vibration damping device which comprises an input part and an output part which is rotatable relative to the input part against the damping effect of at least one torsional vibration damping element, in particular of several torsional vibration damping elements.
  • the object of the invention is to provide a drive wheel according to the preamble of claim 1, which has a long life and is inexpensive to produce.
  • the object is in a drive wheel with at least one drive pulley, in particular a pulley, and with a torsional vibration damping device which comprises a themssteii and an output member, against the damping effect of at least one torsional vibration damping element, in particular of several torsional vibration damping elements, rotatable relative to the input part is achieved in that the torsional vibration damping device is optimized in terms of the life and / or the manufacturing cost of the drive wheel.
  • the drive wheel is preferably used to drive an accessory of a motor vehicle.
  • a preferred embodiment of the drive wheel is characterized in that the input part of the torsional vibration damping device comprises two input flanges which are rotatably connected to each other.
  • the two input flanges have a high rigidity. As a result, a high axial natural frequency can be provided.
  • the input flanges are formed of a hardened case steel. This can a high rigidity can be achieved. In addition, undesirable spring and spring wear can be reduced.
  • a further preferred embodiment of the drive wheel is characterized in that the two input flanges are rotatably connected to each other by the connecting elements.
  • the two input flanges are preferably pre-riveted before assembly.
  • a further preferred embodiment of the drive wheel is characterized in that a sliding bearing is arranged in the radial direction between the input flanges and the drive disk.
  • the sliding bearing is preferably made of plastic and positioned on both input flanges.
  • the sliding bearing has a collar which extends radially inwardly and which is clamped between a plate spring and one of the possiblesfiansche.
  • the plate spring By the plate spring, the sliding bearing is fixed in the axial direction.
  • the collar serves at the same time in the axial direction as a friction element for generating a friction damping.
  • the steel / plastic friction pairing leads to less wear than with a steel / steel friction pairing.
  • a further preferred embodiment of the drive wheel is characterized in that the plate spring is suspended in a plastic part which is fixed to the drive pulley. Preferably, the plastic part is pressed without play into the drive disk. This provides the advantage that even at low vibration amplitudes with high frequency no wear on the disc spring pad occurs.
  • a further preferred embodiment of the drive wheel is characterized in that the output part of the torsional vibration damping device comprises a drive plate, which is arranged in the axial direction between the input flanges.
  • the drive plate is limited rotatable relative to the input flanges.
  • the drive wheel is characterized in that the drive plate is coupled by bow springs with the input flanges.
  • the bow springs drive the torque from the input flanges to the driver transferred.
  • the drive plate is preferably formed of hardened steel case.
  • a further preferred embodiment of the drive wheel is characterized in that the drive plate is connected by spacers fixed to the drive pulley.
  • the drive plate is preferably riveted to the drive pulley. About the distance bolts, the torque is transmitted from the drive plate on the drive pulley.
  • the drive wheel is characterized in that the drive plate is integrally connected to a cover plate.
  • the drive disk is preferably connected to the cover disk via a laser beam welding connection.
  • the drive disc with the cover disc forms a damper housing, which is filled with grease and sealed by protective caps.
  • the drive disk and the cover disk are preferably formed from a weldable thermoforming steel.
  • the drive wheel according to the invention has, inter alia, the advantage that the drive disk and the cover disk have no frictional contact with other components. This can significantly reduce component wear.
  • a further preferred exemplary embodiment of the drive wheel is characterized in that the input part of the torsional vibration damping device comprises an input flange which can be fastened or fastened to a drive shaft or a drive disk hub.
  • the input flange is bolted to a drive disc hub.
  • a further preferred exemplary embodiment of the drive wheel is characterized in that the input flange carries a bearing device, in particular a roller bearing device, for the drive disk.
  • the bearing device allows a wear-free rotation of the drive disk relative to the input flange, and vice versa.
  • a bow spring channel in particular a plastic bow spring channel
  • the bow spring channel is preferably used to hold one half of a bow spring.
  • the torque is transmitted from the input flange on the partially arranged in the bow spring channel bow spring.
  • Another preferred embodiment of the drive wheel is characterized in that a counter-plate is connected by spacers fixed to the drive pulley.
  • the standoffs are preferably riveted to the mating disk and the drive disk. About the distance bolts, the torque is transmitted from the opposite pulley on the drive pulley.
  • the input flange has through holes for the standoffs.
  • the through-holes which are preferably also provided in the bow spring channels, serve to pass the spacer bolts.
  • the through holes are also referred to as bolt window openings. Due to the dimensions of the bolt window openings, the angle of rotation of the counter-disk is limited relative to the input flange. When the standoffs abut the bolt window openings, the relative movement between the input flange and the counterpart wheel is interrupted. As a result, any overshooting occurring during operation can be intercepted.
  • a further preferred exemplary embodiment of the drive wheel is characterized in that a further bow spring channel, in particular a further plastic bow spring channel, is attached to the counter disk.
  • the further bow spring channel is identical in construction to the bow spring channel which is attached to the input flange.
  • the further bow spring channel serves to receive the other half of the bow spring. The torque is transferred from the bow springs to the counter disk via the further bow spring channel.
  • a further preferred embodiment of the drive wheel is characterized in that the bow spring channel or the bow spring channels are formed from a material containing solid lubricants and / or reinforcing fibers. As a result, the wear occurring during operation can be significantly reduced.
  • a further preferred embodiment of the drive wheel is characterized in that the drive disk has the shape of a ring with a U-shaped cross section.
  • the U-shaped cross section defines an annular space which serves to receive the bearing means, a part of the input flange of the counter-disc and the bow spring channels.
  • Another preferred embodiment of the drive wheel is characterized in that the U-shaped cross-section has a base, emanating from the two legs. The two legs preferably extend in the axial direction.
  • a further preferred embodiment of the drive wheel is characterized in that the radially inner leg forms a bearing surface for the bearing device.
  • the bearing device can be used according to a further aspect of the invention for centering the drive pulley.
  • a further preferred embodiment of the drive wheel is characterized in that the radially outer leg forms a contact surface for a torque transmission means, in particular a belt.
  • the radially outer leg is preferably provided with a tooth profile.
  • a further preferred embodiment of the drive wheel is characterized in that the bow spring channel attached to the input flange has a bearing portion which is arranged in the radial direction between the input flange and the drive disk.
  • the bearing portion of the bow spring channel forms a radial sliding bearing.
  • a further preferred exemplary embodiment of the drive wheel is characterized in that the bow spring channel attached to the input flange has a friction section on which a disc spring rests. Due to the friction between the disc spring and the friction section of the bow spring channel, an additional frictional damping / hysteresis function can be provided.
  • a further preferred embodiment of the drive wheel is characterized in that the plate spring is suspended in a plastic part which is fixed to the drive pulley. Preferably, the plastic part is pressed without play into the drive disk. This provides the advantage that no wear occurs at the disc spring pad even at low vibration amplitudes with high frequency.
  • a further preferred embodiment of the drive wheel is characterized in that a drive shaft vibration damper is additionally attached to the input flange.
  • the drive shaft vibration damper is also called crankshaft vibration damper and preferably comprises a damper mass or absorber mass, which is attached by means of a rubber spring to the input flange.
  • a further preferred embodiment of the drive wheel is characterized in that the drive wheel comprises a further input flange, on which a drive shaft vibration damper is mounted.
  • the drive shaft vibration damper is also referred to as a crankshaft vibration damper and preferably comprises a damper mass or absorber mass, which is attached by means of a rubber spring to the other input flange.
  • a further preferred embodiment of the drive wheel is characterized in that a damper mass of the drive shaft vibration damper is arranged radially inside or radially outside of the input flange. Particularly preferably, the damper mass is arranged within the U-shaped cross section of the drive disk.
  • a further preferred embodiment of the drive wheel is characterized in that the drive shaft vibration damper is arranged in the axial direction overlapping to the drive disk.
  • a further preferred embodiment of the drive wheel is characterized in that the drive wheel comprises a further drive disk which is fixed to the input flange.
  • the two drive wheels provide the advantage that two different belt drives can be decoupled vibration technology.
  • Figure 1 is a drive wheel according to a first embodiment in section
  • Figure 2 shows a drive wheel according to another embodiment in section
  • FIG. 3 is an exploded view of the drive wheel of Figure 2;
  • FIG. 4 shows the drive wheel from FIGS. 2 and 3 with an additional drive disk;
  • Figure 5 shows a drive wheel according to another embodiment in section
  • Figure 6 shows a drive wheel according to another embodiment in section
  • FIGS. 1 to 9 show various embodiments of a drive wheel according to the invention with an integrated torsional vibration damping device.
  • the drive wheel is used to drive a (not shown) auxiliary unit of a motor vehicle.
  • the drive wheel is rotatably mounted on a drive shaft of an auxiliary unit of an internal combustion engine, for example an alternator or a generator.
  • a drive wheel 1 is shown in section, which includes a drive pulley 3, which is also referred to as a pulley.
  • the axis of rotation of the drive wheel 1 is designated 2 in FIG.
  • the belt pulley 3 comprises a torque transmission section 4 extending in the axial direction, that is to say parallel to the rotation axis 2.
  • the torque transmission section 4 is equipped on the outside with a toothed profile, which in the circumferential direction is partially looped around by a belt during operation.
  • the pulley 3 further includes a radial portion 5 extending radially inward from the torque transmitting portion 4.
  • spacers 7 are fixed. In the sectional view shown in Figure 1, only one of a plurality of standoffs 7 is visible.
  • the standoffs 7 are riveted at one end to the radial portion 5 of the pulley 3.
  • the other end of the spacer bolt 7 is riveted to a drive plate 8.
  • the spacer bolt 7 has a spacer section 9 which has a larger diameter than the ends of the spacer bolt 7.
  • the spacer section 9 serves to hold the driver disk 8 at a defined distance from the radial section 5 of the belt pulley 3.
  • the drive wheel 1 further comprises two input flanges 11, 12, which are rotatably connected in the installed state of the drive wheel 1 with a drive shaft, in particular a crankshaft of an internal combustion engine.
  • the input flanges 11, 12 are also referred to as Teii- flansche and are connected radially on the outside by connecting rivets 14 firmly.
  • the two input flanges 11, 12 are preferably formed of a hardened case steel.
  • the kausniet 14 extends through a window 16 which is recessed in the drive plate 8. Due to the size of the window 16 in the circumferential direction of the angle of rotation is defined by which the drive plate 8 relative to the input flanges 11; 12 can twist.
  • the two input flanges 11, 12 are coupled via bow springs 17 with the drive plate 8.
  • the bow springs 17 are received in windows which are recessed in the drive plate 8 and the input flanges 11, 12.
  • a bearing portion 19 of a sliding bearing 18 is disposed between the drive plate 8 and the input flanges 11, 12 and the torque transmission section 4 of the pulley 3.
  • the sliding bearing 18, which is also referred to as a plain bearing bush, is made of plastic. From the bearing portion 19 of the sliding bearing 18, a collar 20 extends radially inwardly.
  • the collar 20 is clamped in the axial direction between a plate spring 22 and a radially outer portion of the input flange 12.
  • the plate spring 22 serves as a friction element for generating a desired during operation friction damping.
  • the plate spring 22 is preferably formed of spring steel. The steel / plastic friction pairing results in less wear than conventional steel / steel friction pairings.
  • the plate spring 22 is mounted with an oversize in a plastic part 24. The plastic part 24 in turn is pressed into the pulley 3 without play.
  • the drive wheel 1 is filled with grease 25 inside. Therefore, a central opening of the radial portion 5 of the pulley 3 is closed by a protective cap 26 made of plastic. Furthermore, a cover plate 27 is fastened to the torque transmission section 4 on the side facing away from the radial section 5. The cover plate 27 is welded to, for example, the torque transmission section 4. An opening between the cover plate 27 and the input flange 11 is closed by a further protective cap 28 made of plastic.
  • a drive wheel 41 is shown in various views. The drive wheel 41 is rotatable in the assembled state about a rotation axis 42 and comprises an axially extending torque transmission portion 44. From the torque transmitting portion 44, a radial portion 45 extends radially inwardly.
  • a spacer bolt 47 is fixed.
  • a counter-disc 48 is attached.
  • a bow genfederkanal 49 made of plastic is inserted or inserted.
  • the bow spring channel 49 serves to receive one half of a bow spring 50.
  • the other half of the bow spring 50 is received in a bow spring channel 52 which is inserted or inserted into an input flange 54.
  • the input flange 54 is fixed in the mounted state of the drive wheel 41 on a drive shaft, in particular a crankshaft of an internal combustion engine of a motor vehicle, for example screwed thereto.
  • the input flange 54 includes a bearing portion 55 extending in the axial direction. Between the bearing portion 55 of the input flange 54 and a likewise extending in the axial direction leg 56 which is angled from the radial portion 45 of the pulley 43, a bearing means 58 is arranged.
  • the bearing device 58 is a rolling bearing, which serves to allow a possible wear-free rotation between the input flange 54 and the pulley 43.
  • the input flange 54 has a window 60. Similar windows 61, 64 are provided in the bow spring channels 52, 49. The windows 60, 61, 64 serve to pass through spacer bolts 65. The windows 60, 61, 64, which are also referred to as bolt window openings, limit the angle of rotation of the input flange 54 by abutment with the spacer bolts 65.
  • the input flange 54 transmits a torque from the drive shaft via the bow spring channel 52 to the bow springs 50.
  • the bow springs 50 transmit the torque to the bow spring channel 49, which is inserted into the counter disk 48. About the distance bolts 65, the torque is transmitted from the counter pulley 48 to the pulley 43.
  • FIG. 2 shows the delivery state of the drive wheel 1.
  • FIG. 4 shows that the drive wheel 1 can also be equipped with a second drive disk 70.
  • the second drive plate 70 includes an axially extending torque transmitting portion 71 from which a radial portion 72 extends radially inwardly.
  • the torque-transmitting portion 71 is partially enclosed in the installed state by a belt that drives, for example, a supercharger of an internal combustion engine.
  • a crankshaft vibration damper comprising a rubber spring 74 and a damper mass 75.
  • the rubber spring 74 and the damper mass 75 are disposed radially inside the torque transmission portion 71.
  • a drive wheel 81 is shown in section, which is rotatable about a rotation axis 82 in the mounted state.
  • the drive wheel 81 includes a drive pulley 83, which is also referred to as a pulley.
  • the pulley 83 includes a torque transmitting portion 84 extending in the axial direction. From the torque transmitting portion 84, a radial portion 85 extends radially inwardly. At the radial portion 85, one end of a spacer bolt 87 is fixed. At the other end of the spacer bolt 87, a counter-disc 88 is attached. In the counter-disc 88 a bow spring channel 89 is inserted. The bow spring channel 89 serves to receive one half of a bow spring 90.
  • the other half of the bow spring 90 is accommodated in a bow spring channel 92 which is inserted into an input flange 94.
  • the input flange 94 is in the mounted state of the drive wheel 81 rotatably connected to a drive shaft, in particular with a crankshaft of an internal combustion engine, connected.
  • the Bogenfederkanal 92 is connected radially outwardly in one piece with a bearing portion 100 which extends in the axial direction.
  • the bearing portion 100 is disposed in the radial direction between the input flange 94 and the torque transmitting portion 84 of the pulley 83.
  • the bearing portion 100 forms a radial sliding bearing for the pulley 83 on the input flange 94.
  • the bow spring channel 92 is integrally connected to the bearing portion 100 through a friction portion 101.
  • the friction portion 101 extends in the radial direction.
  • At the friction portion 101 is a plate spring 102 at.
  • the plate spring 102 is suspended with oversize in a Kunststoffteii 104.
  • the plastic part 104 is pressed into the pulley 83 without play.
  • FIG. 6 shows a similar drive wheel 81 as in FIG. 5 in section. To denote the same parts, the same reference numerals are used. To avoid repetition, reference is made to the preceding description of FIG. In the following, only the differences with respect to the embodiment shown in FIG. 5 will be discussed.
  • a cover disk 124 is fastened to the torque transmission section 84 of the belt pulley 83 with the aid of a laser weld seam 121. Between the radially inner end of the cover plate 124 and the input flange 94, a plastic element 126 is provided for sealing purposes. The interior of the pulley 83 is filled with grease 128.
  • a further input flange 140 is fastened to the input flange 54.
  • the further input flange 140 has a fastening section 141, which is arranged radially inwardly and in the vicinity of the torque transmission section 44 of the belt pulley 43.
  • Radially inside a rubber spring 144 is attached to the mounting portion 141.
  • a damper mass 145 is attached, which is also referred to as absorber mass.
  • the further input flange 140 radially outward on a mounting portion 151 which is disposed radially inwardly and spaced from the torque transmitting portion 44 of the pulley 43.
  • a rubber spring 154 and a damper mass 155 are disposed in an annular space between the mounting portion 150 and the torque transmitting portion 44.
  • the damper mass 155 which is also referred to as absorber mass, is attached to the attachment portion 151 with the interposition of the rubber spring 154.
  • a fastening section 158 which extends in the axial direction in the vicinity of the torque transmission section 44 extends radially outward from the input flange 54.
  • a rubber spring 159 Radially inside a rubber spring 159 is attached to the mounting portion 158, to which in turn a damper mass 160 is attached.
  • a damper mass 160 it is also possible to provide the damper mass with the rubber spring radially outside of the mounting portion.
  • the fixing portion 158 is further to be arranged inside to provide in the radial direction between the fixing portion 158 and the torque transmitting portion 44, an annular space for receiving the rubber spring with the damper mass.

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

Abstract

Roue d'entraînement comportant au moins une poulie d'entraînement, notamment une poulie à courroie, et un dispositif d'amortissement d'oscillations rotatives présentant une partie d'entrée et une partie de sortie pouvant tourner par rapport à la partie d'entrée contre l'effet amortisseur d'au moins un élément d'amortissement d'oscillations rotatives, notamment de plusieurs éléments d'amortissement d'oscillations rotatives. L'invention est caractérisée en ce que le dispositif d'amortissement d'oscillations rotatives est optimisé en ce qui concerne la durée de vie et/ou les coûts de fabrication de la poulie d'entraînement.
PCT/DE2007/001878 2006-11-15 2007-10-22 Roue d'entraînement comportant au moins une poulie d'entraînement WO2008058499A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112007002507.7T DE112007002507B4 (de) 2007-10-22 2007-10-22 Triebrad mit mindestens einer Triebscheibe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006053766.1 2006-11-15
DE102006053766 2006-11-15

Publications (2)

Publication Number Publication Date
WO2008058499A2 true WO2008058499A2 (fr) 2008-05-22
WO2008058499A3 WO2008058499A3 (fr) 2008-09-25

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Family Applications (1)

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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102128245A (zh) * 2010-01-20 2011-07-20 龙口市汽车风扇离合器厂 永磁缓冲皮带轮
DE102013206444A1 (de) 2012-04-24 2013-10-24 Schaeffler Technologies AG & Co. KG Triebrad
WO2015161845A1 (fr) * 2014-04-24 2015-10-29 Schaeffler Technologies AG & Co. KG Amortisseur de vibrations de torsion
DE102015210164B3 (de) * 2015-06-02 2016-11-03 Schaeffler Technologies AG & Co. KG Riemenscheibenentkoppler mit Gleitschalen
WO2016191888A1 (fr) 2015-06-03 2016-12-08 Litens Automotive Partnership Dispositif d'isolation amélioré
WO2017139870A1 (fr) * 2016-02-18 2017-08-24 Litens Automotive Partnership Dispositif d'isolation amélioré
US9797498B2 (en) 2013-05-23 2017-10-24 Litens Automotive Partnership Isolator with double acting spring system with reduced noise
WO2018132925A1 (fr) * 2017-01-22 2018-07-26 Litens Automotive Partnership Dispositif amélioré d'isolation
US10041578B2 (en) 2013-07-25 2018-08-07 Litens Automotive Partnership Spring assembly for isolator
US10060502B2 (en) 2012-10-12 2018-08-28 Litens Automotive Partnership Isolator for use with engine that is assisted or started by an MGU or a motor through an endless drive member
US10125856B2 (en) 2013-11-10 2018-11-13 Litens Automotive Partnership Isolator with dual springs
US10267405B2 (en) 2013-07-24 2019-04-23 Litens Automotive Partnership Isolator with improved damping structure
DE102009039989B4 (de) 2008-09-15 2019-07-04 Schaeffler Technologies AG & Co. KG Riemenscheibe mit Federdämpfereinrichtung
DE102019104813A1 (de) * 2019-02-26 2020-08-27 Schaeffler Technologies AG & Co. KG Riemenscheibenentkoppler mit Schmierstofffluss in Vorzugsrichtung
DE102017113043B4 (de) * 2017-06-14 2021-02-04 Schaeffler Technologies AG & Co. KG Triebrad mit Drehschwingungsdämpfungseinrichtung
WO2022111748A1 (fr) 2020-11-30 2022-06-02 Schaeffler Technologies AG & Co. KG Roue motrice
DE102021102018A1 (de) 2020-12-07 2022-06-09 Schaeffler Technologies AG & Co. KG Triebrad
DE102022101297A1 (de) 2021-10-28 2023-05-04 Schaeffler Technologies AG & Co. KG Triebrad

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DE19530938A1 (de) * 1995-08-23 1997-02-27 Freudenberg Carl Fa Drehschwingungsdämpfer
DE19652730A1 (de) * 1995-12-22 1997-06-26 Luk Lamellen & Kupplungsbau Triebscheibe
EP1382886A1 (fr) * 2002-07-16 2004-01-21 DAYCO EUROPE S.r.l. Poulie avec un amortisseur d'oscillation de torsion integré
WO2004007992A1 (fr) * 2002-07-16 2004-01-22 Dayco Europe S.R.L. Ensemble amortisseur de torsion a poulie integree
WO2005085680A1 (fr) * 2004-03-03 2005-09-15 Dayco Europe S.R.L. Con Unico Socio Ensemble poulie
WO2005111468A1 (fr) * 2004-05-14 2005-11-24 Dayco Europe S.R.L. Con Unico Socio Ensemble poulie
EP1645783A1 (fr) * 2003-07-11 2006-04-12 Fukoku Co. Ltd. Poulie amortisseuse d'isolation et procede de fabrication de celle-ci

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Publication number Priority date Publication date Assignee Title
WO1996025611A1 (fr) * 1995-02-17 1996-08-22 Holset Engineering Co. Ltd. Dispositifs d'entrainement
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