WO2014006098A1 - Drehschwingungstilger - Google Patents
Drehschwingungstilger Download PDFInfo
- Publication number
- WO2014006098A1 WO2014006098A1 PCT/EP2013/064049 EP2013064049W WO2014006098A1 WO 2014006098 A1 WO2014006098 A1 WO 2014006098A1 EP 2013064049 W EP2013064049 W EP 2013064049W WO 2014006098 A1 WO2014006098 A1 WO 2014006098A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pendulum
- torsional vibration
- elastic element
- pendulum masses
- masses
- Prior art date
Links
- 239000006096 absorbing agent Substances 0.000 title claims abstract description 11
- 238000013016 damping Methods 0.000 claims abstract description 5
- 230000006835 compression Effects 0.000 claims description 10
- 238000007906 compression Methods 0.000 claims description 10
- 239000000463 material Substances 0.000 claims description 8
- 238000006073 displacement reaction Methods 0.000 claims description 4
- 230000002093 peripheral effect Effects 0.000 abstract 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000035882 stress Effects 0.000 description 1
- 239000006228 supernatant Substances 0.000 description 1
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
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2121—Flywheel, motion smoothing-type
- Y10T74/2128—Damping using swinging masses, e.g., pendulum type, etc.
Definitions
- the invention relates to a torsional vibration damper, in particular for use in the drive train of a motor vehicle.
- a torsional vibration damper In order to transmit torque in a drive train, for example, from a drive motor to a transmission, a torsional vibration damper is used.
- the torsional vibration damper has the task, in addition to the transmission of torque any torsional vibrations (torsional vibrations), which can be superimposed on the torque to pay off.
- the torsional vibration damper comprises a pendulum, on which a pendulum mass is slidably mounted. By means of a slotted guide, the pendulum mass is guided on the pendulum so that it moves radially inward during an acceleration of the pendulum flange about the axis of rotation, wherein the rotational torque of the torsional vibration damper is changed.
- the pendulum mass is a trapezoidal pendulum, which is guided biliquely on the pendulum flange.
- the pendulum mass performs a rotational movement in the plane of rotation of the pendulum flange about its own axis, whereby additional energy can be stored.
- the sliding movement and the rotational movement of the pendulum mass can be partially or completely coupled to each other by the link guide.
- pendulum masses are located on a circumference of the pendulum flange next to each other.
- the pendulum masses and their guides are chosen so that a collision of adjacent pendulum masses is possible.
- a collision can occur, for example, at a very low speed or very high torque fluctuations. Due to the collisions wear of the pendulum masses can be promoted and it can cause disturbing noises.
- a stop can be used which has a maximum limits the mobility of the pendulum mass relative to the pendulum flange.
- the pendulum mass is guided by means of two slotted guides on the pendulum, wherein a sliding block of a slotted guide is covered with an elastic element.
- the other link guide is dimensioned so that it limits a movement of the pendulum mass with respect to the pendulum when a predetermined compression of the elastic element is carried out on the other link guide.
- the pendulum mass can not comply with the intended theoretical path, but move freely in the context of a game of their leadership on the pendulum. These movements can lead to an unwanted stop between the elastic elements on the front sides of the pendulum masses.
- An inventive torsional vibration damper comprises a pendulum flange rotatable about a rotation axis with a recess, and two pairs of pendulum masses which are slidably mounted adjacent to the pendulum in the circumferential direction, and an elastic element for damping a mutual stop of adjacent pendulum mass pairs.
- the pendulum mass pairs each comprise two pendulum masses, which are opposite each other with respect to the pendulum flange and a bolt which passes through the recess and the pendulum masses axially together.
- an elastic element is attached to both pins, which is adapted to abut in the circumferential direction of the respective other elastic element.
- the elastic elements Due to the position of the elastic elements on the bolts, the elastic elements can be concealed and thus arranged protected on the torsional vibration damper.
- a Dämpfungsweg at a stop of the two pendulum masses together can be done between the two elastic elements and thus be longer than a Dämpfungsweg a stop of one of the pendulum mass pairs in the radial direction.
- An energy reduction in the attack can so in an improved way in the direction in which the greatest collision energy is expected.
- the elastic element protrudes in the circumferential direction of the torsional vibration damper only by a predetermined fraction of its dimensions over a limitation of the pendulum mass, so that a compression of the elastic elements can be limited by a mutual stop of adjacent pendulum masses.
- the limitation of the compression travel of the elastic elements can be ensured in this way regardless of whether the mutually facing ends of the pendulum mass pairs are deflected differently far radially on the pendulum.
- the elastic elements can thus be reduced in their load to a predetermined extent under all operating conditions of the torsional vibration damper. A life expectancy of the elastic elements can be reliably determined or assured by appropriate dimensioning of the elastic elements.
- the recess is dimensioned so that the elastic elements can also strike against radial boundaries of the recess.
- a radial movement of each pendulum mass pair with respect to the pendulum flange in the region of the predetermined by the recess end of the movement can be damped by the elastic ele- element.
- the pairs of pendulum masses can be performed bifilar on the pendulum flange, so that in addition to the displacement in the plane of rotation and a rotation about an axis of the pendulum mass pair is possible.
- Such an arrangement is also called trapezoidal pendulum.
- the pendulum mass pairs can each follow complex tracks, of which a section can indeed be taken rarely, but the improved a real taken by the pendulum masses curve improved. The described protection of the elastic elements against excessive compression can be played out here with particular advantage.
- the elastic elements are each mounted radially symmetrically to their associated bolts.
- the damping of a stop of the pendulum mass pair in its movement relative to the pendulum can succeed in all possible directions of movement.
- the elastic elements are each rotatably arranged with respect to the pendulum masses. Wear or aging of the elastic element due to stress can thus be distributed over the entire circumference of the elastic element, so that an increased load capacity or extended service life of the elastic element can be achieved.
- a contour of the pendulum masses in the region of the elastic elements can each follow a contour of the elastic element.
- the pendulum mass pair may have a shape in its circumferential end portions which simultaneously ensures the abutment of the elastic members and maximizes the size of the pendulum mass pairs.
- a torsional vibration damper comprises at least three of the pendulum mass pairs described, each slidably mounted adjacent the pendulum flange, each pendulum mass pair having in the region of each of its two circumferentially located ends a bolt with an elastic member attached thereto.
- the pendulum mass pairs used can be protected from collision by the corresponding elastic elements, while at the same time the elastic elements are protected against excessive compression.
- Due to the mass ratios of trapezoidal pendulums it has proven to be advantageous to arrange exactly three pairs of pendulum masses on a circumference about the axis of rotation on the pendulum flange.
- the outstanding over the limitation of the pendulum mass fraction of the elastic element is dimensioned depending on a material, a projected load change number, an expected maximum collision energy or a geometry of the elastic member.
- the projecting beyond the limitation of the pendulum mass fraction of the elastic element is about 40% of its material strength. With this value could be proven in experiments good durability of the elastic elements in the operation of the torsional vibration in the drive train of a motor vehicle.
- Figure 1 is a torsional vibration damper
- Figure 2 is a detail of the torsional vibration damper of Figure 1;
- FIG. 3 shows a detail from FIG. 2 in a first position
- Figure 4 illustrates the detail of Figure 2 in a second position.
- FIG. 1 shows a torsional vibration damper 100 for use in a drive train of a motor vehicle.
- the torsional vibration damper 100 is rotatably mounted about a rotation axis 105 and comprises a pendulum flange 1 10 and three pendulum masses 1 15, which are distributed on a circumference about the axis of rotation 105 on the pendulum flange 1 10.
- Each pendulum mass 1 15 comprises a first pendulum mass 120 and a second pendulum mass 125, and a bolt 130 and an elastic member 135.
- the pendulum masses 120 and 125 are aligned with each other on different axial sides of the pendulum 1 10, so that the rear in Figure 1 pendulum 125 is not visible.
- the bolt 130 connects the pendulum masses 120 and 125 rigidly together.
- the bolt 130 is guided by a recess 140 in the pendulum flange 1 10, which is dimensioned so that the pendulum mass 1 15 in the plane of rotation about the axis of rotation 105 on the pendulum 1 10 remains slidably.
- the elastic element 135 is attached to the bolt 130, relative to the axis of rotation 105 in the axial direction, between the pendulum masses 120 and 125 in the region of the recess 140 of the pendulum flange 1 10.
- the elastic element 135 may in particular comprise an elastic plastic or a rubber.
- the elastic member 135 rotates the bolt 130 about its longitudinal axis, which is parallel to the axis of rotation 105.
- a sleeve or a bearing 145 may be arranged.
- the elastic element 135 can be mounted rotatably with respect to the pendulum mass pair 15.
- the rotatability of the elastic member 135 can also be made by the bolt 130 being rotatably attached to the pendulum masses 120 and 125, respectively.
- a bolt 130 with the elastic element 135 is connected to each pendulum mass pair 1 15 at both ends lying around the rotation axis 105 in the circumferential direction. brought.
- the displaceability of the pendulum mass pair 1 15 with respect to the pendulum flange 1 10 can be defined by the described arrangement of the attached to the pendulum masses 120 and 125 bolts 130 with the elastic members 135 in conjunction with the recess 140.
- the movement may additionally be defined by one or more slotted guides 150.
- each pendulum mass pair 1 15 with respect to the pendulum flange 1 10 is set such that a displacement or Verschwen- kung of a pendulum mass 1 15 about the axis of rotation 105 associated with a rotation of the pendulum mass 1 15 to another, parallel to the rotation axis 105 axis of rotation so that the lying in the circumferential direction, mutually opposite ends of the pendulum mass pair 1 15 occupy different radial distances from the axis of rotation 105.
- Such an arrangement is called trapezoidal pendulum.
- FIG. 2 shows a detail of the torsional vibration damper 100 from FIG. 1.
- the elastic member 135 extends radially symmetrically about the bolt 130.
- the circumferentially located ends of the pendulum masses 120 and 125 are formed so that only a predetermined fraction of the elastic member 135 protrudes beyond the boundary of the pendulum masses 120 and 125.
- This projection of the elastic element taking into account a material, for example with respect to its tensile strength or yield strength, a required number of load cycles, which may be, for example, in the order of 300,000, a maximum expected energy when striking two pendulum masses 1 15 against each other in the range of 700 mJ, a geometry of the elastic element 135 or a combination thereof.
- the supernatant amount to a maximum of 40% of the material thickness.
- the material thickness corresponds to the depth of the elastic member 135 in the radial direction with respect to the bolt 130th
- a contour of the pendulum masses 120 and 125 in the region of the elastic element 135 follows its contour at a distance which defines the above-described projection.
- the final contour of the pendulum masses 120 and 125 describes the significant waveform in FIG.
- FIG. 3 shows the detail of torsional vibration absorber 100 from FIG. 2 in a first position.
- the view is as in Figure 1 parallel to the axis of rotation 105.
- the elastic members 135 of the two pendulum mass pairs 1 15 shown in Figure 3 touch each other without the pendulum masses 120, 125 of the two pendulum masses 1 15 touching each other.
- this position represents only one possible operating state of the torsional vibration damper 100, in other operating states the two ends can also have equal radial distances from the axis of rotation 105 taking.
- FIG. 4 shows the detail of torsional vibration absorber 100 from FIG. 2 in a second position.
- the ends of the pendulum mass pairs 1 15 in the circumferential direction about the rotation axis 105 have moved further toward each other, wherein the elastic members 135 have been compressed accordingly.
- the compression of the elastic elements 135 finds its limit in the stop of the mutually facing ends of the pendulum masses 120 and 125 of the two adjacent pendulum mass pairs 125th
- this limitation of the compression of the elastic elements 135 only occurs in the event of a collision of two adjacent pendulum mass pairs 125 by this stop of the pendulum masses 120 and 125 to each other. If a radial movement of a pendulum mass pair 125 is attenuated outwardly or inwardly by the elastic element 135 at a boundary of the recess 140, then no stop is provided which restricts the compression of the elastic element 135. In one embodiment, however, such a stop may be otherwise provided, such as through the slotted guides 150.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Dampers (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112013003394.1T DE112013003394B4 (de) | 2012-07-06 | 2013-07-03 | Drehschwingungstilger |
US14/410,953 US9709126B2 (en) | 2012-07-06 | 2013-07-03 | Torsional vibration damper |
CN201380035786.4A CN104520608B (zh) | 2012-07-06 | 2013-07-03 | 扭振减振器 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012211820 | 2012-07-06 | ||
DE102012211820.9 | 2012-07-06 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014006098A1 true WO2014006098A1 (de) | 2014-01-09 |
Family
ID=48790395
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2013/064049 WO2014006098A1 (de) | 2012-07-06 | 2013-07-03 | Drehschwingungstilger |
Country Status (4)
Country | Link |
---|---|
US (1) | US9709126B2 (de) |
CN (1) | CN104520608B (de) |
DE (2) | DE112013003394B4 (de) |
WO (1) | WO2014006098A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015152032A (ja) * | 2014-02-10 | 2015-08-24 | 本田技研工業株式会社 | 遠心振子式制振装置 |
WO2015165455A1 (de) * | 2014-04-30 | 2015-11-05 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendel |
KR20160125086A (ko) * | 2015-04-21 | 2016-10-31 | 한국파워트레인 주식회사 | 진자를 이용한 차량용 토크 컨버터의 진동 저감 장치 |
DE102021106045A1 (de) | 2021-03-12 | 2022-09-15 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendel mit Zwischenmasse aufweisend Zusatzfunktion für einen Schutz der Anschlagspuffer |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112014002737B4 (de) * | 2013-08-09 | 2021-02-04 | Aisin Aw Co., Ltd. | Zentrifugalpendel-Schwingungs-Absorbtionseinrichtung |
US9546706B2 (en) * | 2014-04-16 | 2017-01-17 | Ford Global Technologies, Llc | Pendulum absorber with sliding joint |
KR101673741B1 (ko) * | 2015-01-30 | 2016-11-07 | 현대자동차주식회사 | 알터네이터 풀리 진동 저감 장치 |
FR3036762B1 (fr) * | 2015-06-01 | 2017-06-02 | Valeo Embrayages | Dispositif d'amortissement d'oscillations de torsion |
DE102015212737A1 (de) * | 2015-07-08 | 2017-01-12 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendeleinrichtung |
KR101694049B1 (ko) * | 2015-08-24 | 2017-01-09 | 현대자동차주식회사 | 차량용 진동 저감 장치 |
DE112017005660A5 (de) * | 2016-11-10 | 2019-08-22 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendel |
FR3070737B1 (fr) * | 2017-09-06 | 2019-08-23 | Valeo Embrayages | Dispositif damortissement pendulaire |
DE102018107812A1 (de) * | 2018-04-03 | 2019-10-10 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendel und Antriebssystem mit solch einem Fliehkraftpendel |
JP7095515B2 (ja) * | 2018-09-14 | 2022-07-05 | トヨタ自動車株式会社 | 捩り振動低減装置 |
US11396923B2 (en) * | 2020-09-15 | 2022-07-26 | Schaeffler Technologies AG & Co. KG | Centrifugal pendulum absorber with radial travel stop |
FR3130343B1 (fr) * | 2021-12-10 | 2024-02-09 | Valeo Embrayages | Dispositif d’amortissement pendulaire |
US11879515B1 (en) * | 2022-10-07 | 2024-01-23 | Schaeffler Technologies AG & Co. KG | Centrifugal pendulum absorber bumper |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007029609A1 (de) * | 2007-06-27 | 2009-01-08 | Bayerische Motoren Werke Aktiengesellschaft | Zweimassenschwungrad |
DE102011103471A1 (de) * | 2010-06-29 | 2011-12-29 | Schaeffler Technologies Gmbh & Co. Kg | Fliehkraftpendel |
WO2012083920A1 (de) * | 2010-12-23 | 2012-06-28 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendeleinrichtung |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1744074A3 (de) * | 2005-07-11 | 2008-10-01 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Drehmomentübertragungseinrichtung |
DE112010001152B4 (de) * | 2009-03-16 | 2018-11-15 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendel |
WO2011110150A1 (de) * | 2010-03-11 | 2011-09-15 | Schaeffler Technologies Gmbh & Co. Kg | Fliehkraftpendeleinrichtung |
JP5783542B2 (ja) | 2010-03-11 | 2015-09-24 | シェフラー テクノロジーズ アー・ゲー ウント コー. カー・ゲーSchaeffler Technologies AG & Co. KG | 遠心振り子装置 |
DE112011100859B4 (de) * | 2010-03-11 | 2016-11-10 | Schaeffler Technologies AG & Co. KG | Torsionsschwingungsdämpfer |
DE102012220887A1 (de) | 2011-11-30 | 2013-06-06 | Schaeffler Technologies AG & Co. KG | Massetilger |
-
2013
- 2013-07-03 CN CN201380035786.4A patent/CN104520608B/zh active Active
- 2013-07-03 DE DE112013003394.1T patent/DE112013003394B4/de active Active
- 2013-07-03 US US14/410,953 patent/US9709126B2/en active Active
- 2013-07-03 DE DE102013213008.2A patent/DE102013213008A1/de not_active Withdrawn
- 2013-07-03 WO PCT/EP2013/064049 patent/WO2014006098A1/de active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007029609A1 (de) * | 2007-06-27 | 2009-01-08 | Bayerische Motoren Werke Aktiengesellschaft | Zweimassenschwungrad |
DE102011103471A1 (de) * | 2010-06-29 | 2011-12-29 | Schaeffler Technologies Gmbh & Co. Kg | Fliehkraftpendel |
WO2012083920A1 (de) * | 2010-12-23 | 2012-06-28 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendeleinrichtung |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015152032A (ja) * | 2014-02-10 | 2015-08-24 | 本田技研工業株式会社 | 遠心振子式制振装置 |
WO2015165455A1 (de) * | 2014-04-30 | 2015-11-05 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendel |
CN106255841A (zh) * | 2014-04-30 | 2016-12-21 | 舍弗勒技术股份两合公司 | 离心力摆 |
CN106255841B (zh) * | 2014-04-30 | 2019-01-01 | 舍弗勒技术股份两合公司 | 离心力摆 |
KR20160125086A (ko) * | 2015-04-21 | 2016-10-31 | 한국파워트레인 주식회사 | 진자를 이용한 차량용 토크 컨버터의 진동 저감 장치 |
KR101695653B1 (ko) | 2015-04-21 | 2017-01-13 | 한국파워트레인 주식회사 | 진자를 이용한 차량용 토크 컨버터의 진동 저감 장치 |
DE102021106045A1 (de) | 2021-03-12 | 2022-09-15 | Schaeffler Technologies AG & Co. KG | Fliehkraftpendel mit Zwischenmasse aufweisend Zusatzfunktion für einen Schutz der Anschlagspuffer |
Also Published As
Publication number | Publication date |
---|---|
US9709126B2 (en) | 2017-07-18 |
CN104520608B (zh) | 2016-08-24 |
DE112013003394A5 (de) | 2015-03-19 |
DE102013213008A1 (de) | 2014-02-20 |
DE112013003394B4 (de) | 2021-09-02 |
CN104520608A (zh) | 2015-04-15 |
US20150204416A1 (en) | 2015-07-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2014006098A1 (de) | Drehschwingungstilger | |
EP2679865B2 (de) | Baureihe von Antriebseinrichtungen | |
EP2912340B2 (de) | Torsionsschwingungsdämpfer | |
WO2018215018A1 (de) | Torsionsschwingungsdämpfer mit drehmomentbegrenzer | |
DE102009037481B4 (de) | Drehzahladaptiver Tilger, insbesondere Fliehkraftpendeleinrichtung | |
DE102013217089A1 (de) | Tilgersystem | |
DE112011100857B4 (de) | Fliehkraftpendeleinrichtung | |
EP3377784B1 (de) | Dämpfungsanordnung für wenigstens eine tilgermasse | |
DE102013217090A1 (de) | Tilgersystem | |
DE102013214155A1 (de) | Fliehkraftpendel und Reibungskupplung mit Fliehkraftpendel | |
EP2912341A1 (de) | Torsionsschwingungsdämpfer | |
DE102013208430A1 (de) | Fliehkraftpendel | |
WO2014012546A1 (de) | Fliehkraftpendel | |
DE102012220887A1 (de) | Massetilger | |
EP3123057A1 (de) | Fliehkraftpendel mit federanordnung | |
DE102011014922A1 (de) | Elektromechanische Lenkung für ein Fahrzeug und elastischer Endanschlag dazu | |
DE102013212271A1 (de) | Fliehkraftpendel | |
DE102011079603A1 (de) | Kupplungsscheibe für eine Reibungskupplung | |
DE102013221356A1 (de) | Schaltvorrichtung | |
DE202013011950U1 (de) | Schaltvorrichtung | |
DE102016223635A1 (de) | Kupplungsscheibe | |
DE102016208493A1 (de) | Fliehkraftpendeleinrichtung mit Anschlag für Pendelrollen | |
EP3111106A1 (de) | Fliehkraftpendel | |
DE102019204261A1 (de) | Kupplungsanordnung für einen Antriebsstrang eines Fahrzeugs | |
DE102013214956B4 (de) | Schaltvorrichtung für ein Getriebe |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 13736840 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14410953 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120130033941 Country of ref document: DE Ref document number: 112013003394 Country of ref document: DE |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: R225 Ref document number: 112013003394 Country of ref document: DE Effective date: 20150319 |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 13736840 Country of ref document: EP Kind code of ref document: A1 |