WO2005012767A1 - ロックアップ装置のダンパー機構 - Google Patents
ロックアップ装置のダンパー機構 Download PDFInfo
- Publication number
- WO2005012767A1 WO2005012767A1 PCT/JP2004/010925 JP2004010925W WO2005012767A1 WO 2005012767 A1 WO2005012767 A1 WO 2005012767A1 JP 2004010925 W JP2004010925 W JP 2004010925W WO 2005012767 A1 WO2005012767 A1 WO 2005012767A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- window portion
- angle
- window
- damper mechanism
- coil spring
- Prior art date
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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
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- 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
- F16F15/121—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 using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/12313—Wound springs characterised by the dimension or shape of spring-containing windows
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- 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
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- 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
- F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
-
- 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members
Definitions
- the present invention relates to a damper mechanism, particularly to a damper mechanism of a lockup device.
- a damper mechanism is used in, for example, a power transmission system, and is a mechanism for absorbing and attenuating torsional vibration while transmitting torque.
- the damper mechanism includes a first rotating member, a second rotating member, and a spring or an elastic member (hereinafter, generically referred to as an elastic member) that is disposed between the two rotating members and is compressed between the two members when the two members rotate relative to each other.
- a coil spring is used as the spring.
- Rubber or resin is used as the elastic body.
- Devices incorporating the damper mechanism include a clutch disk assembly, a flywheel assembly, and a torque converter lock-up device (for example, see Patent Document 1).
- Patent Document 1 Japanese Patent Application Laid-Open No. 8-254246
- the elastic member is disposed inside a window provided in each of the first and second rotating members.
- the damper mechanism transmits torque from the first rotating member to the second rotating member, and also absorbs and attenuates torsional vibration.
- the end of the window in the rotation direction is linear, and is parallel to a straight line connecting the center of the damper and the center of the window rotation direction.
- the amount of movement of the rotation direction end of the window portion is larger on the outer circumferential side than on the inner circumferential side (see FIG. 4.
- ⁇ is the rotation center of the rotating member).
- C is the center of the window in the rotation direction
- ⁇ ⁇ is the relative rotation angle of the first and second rotating members when the elastic member is compressed most.
- the end of the window in the rotation direction should The shape of the window portion is trapezoidal by inclining with respect to a straight line connecting.
- both ends in the rotational direction of the outer peripheral edge of the window are located outside of both ends in the rotational direction of the inner peripheral edge in the rotational direction.
- the damper mechanism is required to have a low rigidity and a wide torsion angle of an elastic member in order to absorb vibration. For this reason, elastic members such as coil springs have become longer in the rotation direction, and their rigidity has been reduced. Therefore, it is considered that the above problem is more prominent in the damper mechanism of the lock-up device.
- An object of the present invention is to provide a damper mechanism of a lockup device that can extend the life of an elastic member.
- the damper mechanism of the lock-up device is a damper mechanism of a lock-up device for mechanically transmitting torque in a fluid torque transmission device, wherein the first rotation member and the second rotation member are provided. , And a plurality of elastic members.
- the first rotating member has a plurality of first windows arranged in the rotating direction.
- the second rotating member has a plurality of second windows provided so as to overlap the first window, and is disposed so as to be rotatable relative to the first rotating member.
- the elastic member is disposed in the first window portion and the second window portion overlapping each other, and is compressed in the rotation direction by the relative rotation of the first rotating member and the second rotating member.
- the maximum torsional angle at which the first rotating member and the second rotating member are relatively rotated and the elastic member is most compressed is ⁇ m.
- the first window portion and the second window portion each have a shape in which the outer peripheral edge is longer than the inner peripheral edge. Further, the angle formed between the ends of the first and second windows in the rotation direction with respect to a center line that is a straight line connecting the center of the damper mechanism and the centers of the first and second windows in the rotation direction. It is in the range of 0.05 to 0.60 times the maximum torsion angle ⁇ ⁇ .
- the pair of rotation ends of the first and second windows is a straight line connecting the center of the damper mechanism with the rotation center of the first and second windows. (Hereinafter referred to as the center line).
- the center line and the rotation are defined with respect to the maximum torsion angle ⁇ m, which is the torsion angle between the first and second rotating members. The angle between the end of the direction and the force 3 ⁇ 4 .05 times or more and 0.60 times or less.
- the angle ⁇ is in the above range with respect to ⁇ m, the force for pushing the elastic member outward in the radial direction can be suppressed, and the increase in the amount of compression of the outer peripheral portion of the elastic member can be suppressed. Thereby, the life of the elastic member can be extended.
- the damper mechanism of the lockup device according to claim 2 is the damper mechanism of the lockup device according to claim 1, wherein the angle ⁇ is 0.10 to 0.45 times the angle ⁇ m. It is in.
- the angle ⁇ is 0.10 times or more and 0.45 times or less of the angle ⁇ m. Since the angle ⁇ is in the above range with respect to ⁇ m, the force for pushing the elastic member outward in the radial direction can be suppressed, and the increase in the amount of compression on the outer peripheral side of the elastic member can be suppressed. This makes it possible to extend the life of the elastic member.
- the damper mechanism of the lockup device according to claim 3 is the damper mechanism of the lockup device according to claim 2, wherein the angle ⁇ is 0.20 to 0.40 times the angle ⁇ m. It is in.
- the angle ⁇ is 0.20 to 0.40 times the angle ⁇ ⁇ ⁇ ⁇ m.
- the angle ⁇ is in the above range with respect to ⁇ m, the force for pushing the elastic member outward in the radial direction can be suppressed, and the increase in the amount of compression of the outer peripheral portion of the elastic member can be suppressed. This makes it possible to further extend the life of the elastic member.
- the damper mechanism of the lockup device according to claim 4 is the damper mechanism of the lockup device according to any one of claims 1 to 3, wherein the elastic member is a coil spring formed of a spirally extending wire.
- the free length of the coil spring is 3. 0 times or more.
- a coil spring having a relatively elongated shape is described.
- the coil spring is easily distorted by a force acting perpendicular to the longitudinal direction of the coil. For this reason, the elastic member is weak against the force for pushing outward in the radial direction.
- the angle ⁇ at the end of the first and second windows in the rotation direction is appropriately set to ⁇ m, the increase in the historque even when a relatively elongated coil spring is used as the elastic member. And increase in wear can be suppressed.
- the life of the elastic member can be extended by appropriately setting the size of the angle ⁇ with respect to the angle ⁇ m.
- FIG. 1 is a sectional view of a torque converter according to the present invention.
- FIG. 2 is a plan view of a lockup device according to the present invention.
- FIG. 3 shows shapes of a first window portion and a second window portion according to the present invention.
- FIG. 4 is a schematic view showing an example of a conventional window shape (both ends of the window are parallel).
- FIG. 5 is an enlarged view of an end of a window.
- FIG. 1 is a schematic longitudinal sectional view of a torque converter 1 to which an embodiment of the present invention is applied.
- the torque converter 1 is a device for transmitting torque from an engine crankshaft (not shown) to an input shaft (not shown) of a transmission.
- An engine (not shown) is arranged on the left side of FIG. 1, and an unillustrated transmission is arranged on the right side of FIG.
- the torque converter 1 mainly includes a torus 6 including three types of impellers (an impeller 18, a turbine 19, and a stator 20), and a lock-up device 7.
- the front cover 14 is a disc-shaped member, and is arranged near the front end of a crankshaft of an engine (not shown).
- a center boss 15 is fixed to the inner peripheral portion of the front cover 14 by welding.
- a plurality of nuts 11 are fixed on the outer peripheral side of the front cover 14 and on the engine side in the rotation direction at equal intervals in the rotation direction.
- the impeller 18 mainly includes an impeller shenore 22, a plurality of impeller blades 23 fixed inside the impeller shell 22, and an impeller hub 24 fixed to the inner periphery of the impeller shell 22. Have been.
- the turbine 19 is disposed in the fluid chamber so as to face the impeller 18 in the axial direction.
- the turbine 19 mainly includes a turbine shell 25 and a plurality of turbine blades 26 fixed to a surface of the turbine shell 25 on one side of the impeller.
- the inner peripheral portion of the turbine shell 25 is fixed to a flange of the turbine hub 27 by a plurality of rivets 28.
- the turbine hub 27 is non-rotatably connected to an input shaft of the transmission, not shown.
- Stator 20 is a mechanism for rectifying the flow of hydraulic oil returning from turbine 19 to impeller 18.
- Stator 20 is an integral member made of resin, aluminum alloy, or the like.
- Stator 20 is arranged between the inner periphery of impeller 18 and the inner periphery of turbine 19.
- the stator 20 mainly includes an annular carrier 29 and an outer peripheral surface of the carrier 29. And a plurality of stator blades 30 provided.
- the carrier 29 is supported by a fixed shaft (not shown) via a one-way clutch 35.
- a thrust bearing 39 is arranged between the impeller hub 24 and the carrier 29.
- a thrust bearing 40 is disposed between the carrier 29 and the turbine hub 27.
- the lockup device 7 mainly includes a piston member 44 and a damper disk assembly 45.
- the piston member 44 is a disk-shaped member disposed close to the front cover 14 on the transmission side in the axial direction.
- An inner peripheral cylindrical portion 48 extending toward the transmission in the axial direction is formed on the inner peripheral portion of the piston member 44.
- the inner peripheral cylindrical portion 48 is rotatable relative to the outer peripheral surface of the turbine hub 27, and is further movably supported in the axial direction.
- the end of the inner peripheral cylindrical portion 48 on the axial transmission side is abutted on the flange portion of the turbine hub 27, so that movement toward the axial transmission side is restricted to a predetermined position.
- a seal ring 49 for sealing in the axial direction on the inner peripheral portion of the piston member 44 is disposed on the outer peripheral surface of the turbine hub 27.
- An annular friction facing 46 is fixed to an engine side of an outer peripheral portion of the piston member 44.
- the friction facing 46 faces an annular and flat friction surface formed on the inner surface of the outer peripheral portion of the front cover 14.
- a cylindrical portion 44a extending toward the transmission in the axial direction is formed on the outer peripheral portion of the piston member 44, and a plurality of slots are formed in the cylindrical portion 44a at equal angular intervals.
- the damper disk assembly 45 is a device for elastically connecting the turbine 19 from the piston member 44 in the rotational direction, and has a function of transmitting torque from the piston member 44 to the turbine 19 and absorbing torsional vibration. are doing.
- the damper disk assembly 45 includes a drive member 52 mainly composed of a pair of plate members 56 and 57, a driven member 53, and a plurality of coil springs 58 and 59.
- the damper disk assembly 45 when the plate member 57 is removed is shown on the left side of the dashed line.
- the pair of plate members 56 and 57 constituting the drive member 52 are annular and disk-shaped members, and are arranged side by side in the rotation axis direction.
- the pair of plate members 56 and 57 are fixed to each other by a plurality of rivets 60 on the outer peripheral portion, and are arranged at an interval on the inner peripheral portion.
- the drive member 52 has a plurality of protrusions protruding radially outward. The projection is engaged with a slot formed in the cylindrical portion 44a of the piston member 44, and serves as a tonnolek input portion to which torque from the piston member 44 is input. By this engagement, the piston member 44 and the drive member 52 can move relative to each other in the axial direction, and rotate together in the rotation direction.
- a plurality of cut-and-raised portions 56a, 56b and 57a, 57b arranged at equal intervals in the rotation direction are formed at six places at the center of a pair of plate members 56, 57 constituting the drive member 52.
- a first window 61 of the drive B material 52 is provided as a notch surrounding the cut-and-raised force 56a, 56b, 57a, 57b.
- the cut-and-raised portions 56a and 57a are radial ends on the outer peripheral side of the first window portion 61, respectively, and the cut-and-raised portions 56b and 57b are radially inner ends of the first window portion 61, respectively. Is at the end.
- the central portion in the rotation direction is cut and raised to be larger than both ends.
- a plurality of second cut-and-raised portions 56c and 57c arranged at equal intervals in the rotational direction are formed at three places on the outer peripheral portion of the plate members 56 and 57, and the second cut-and-raised portions 56c and 57c are formed.
- a small window 66 is formed.
- the driven member 53 is a ring-shaped and disk-shaped member, and is disposed in the inner peripheral portions of the pair of plate members 56 and 57 between the axial directions thereof.
- the driven member 53 is fixed to the turbine hub 27 by rivets 28. As a result, the driven member 53 and the turbine hub 27 rotate integrally.
- second windows 62 having the same shape as the first window 61 of the drive member 52 are formed correspondingly.
- a plurality of protrusions 68 are provided on the outer peripheral portion of the driven member 53 so that a gap 67 is arranged at a position corresponding to the small window 66 of the drive member 52.
- the plurality of coil springs 58 are housed inside the first window 61 and the second window 62.
- Each coil spring 58 is a spring member extending in the rotational direction, and has relatively low rigidity.
- the coil spring 58 is elongated in the rotation direction, and And the free length is 3.0 times or more.
- the coil spring 58 has a free length substantially equal to the length of the first window 61 and the second window 62 in the rotation direction. Both ends in the rotation direction of the coil spring 58 are supported by rotation ends 61a, 62a of the first window 61 and the second window 62. Further, the moving force S in the vehicle direction is limited by the cut-and-raised portions 56a, 56b, 57a and 57b up to the coil spring 58f.
- the coil spring 58 is compressed and deformed by the ends of the first window 61 and the second window 62 in the rotation direction, and the first spring 61 and the second window 62 are deformed.
- the rotation direction ends 61a and 62a are at a predetermined angle with respect to a straight line (hereinafter referred to as a center line) connecting the rotation centers O and O of the first window part 61 and the second window part 62 with respect to the rotation direction. (See Figure 3).
- the shape of the first window 61 and the second window 62 is trapezoidal or fan-shaped. That is, both ends of the outer peripheral edges of the first window portion 61 and the second window portion 62 in the rotational direction are located outside the rotational ends of the inner peripheral edge in the rotational direction.
- the end of the coil spring 58 in the rotation direction has a shape conforming to the shape of the rotation direction ends 61a, 62a of the first window 61 and the second window 62. Therefore, both ends in the rotation direction of the coil spring 58 do not apply a force load that is in contact with or close to the rotation direction ends 61 a and 62 a of the first window portion 61 and the second window portion 62. Therefore, wear is less likely to occur on the rotation direction ends 61a, 62a of the first window portion 61 and the second window portion 62 and the coil spring 58.
- the torsion angle between the drive member 52 and the driven member 53 in the state where the drive member 52 and the driven member 53 rotate relative to each other and the coil spring 58 is compressed most is defined as the maximum torsion angle ⁇ m.
- the aforementioned angle ⁇ is in the range of 0.05-0.60 times the maximum torsion angle ⁇ m.
- the angle ⁇ is preferably in the range of 0.10 to 0.45 times, and more preferably in the range of 0.20 to 0.40 times.
- the coil spring 59 is housed inside the small window 66 and the void 67.
- the coil spring 59 has a free length substantially the same as the length of the small window 66 in the rotation direction. Both ends in the rotation direction of the coil spring 59 are supported by the rotation direction ends of the second cut-and-raised portions 56c and 57c. Further, the coil spring 59 is prevented from moving in the axial direction by the second cut-and-raised portions 56c and 57c. Limited. Since the length of the coil spring 59 is shorter than the distance between the protrusions 68, when the drive member 52 and the driven member 53 rotate sufficiently relative to each other, the coil springs are formed by the second cut-and-raised portions 56c, 57c and the protrusion 68. 59 is compressed.
- Engine torque (not shown) is transmitted from the crankshaft (not shown) to the front cover 14 and the impeller 18.
- the hydraulic oil driven by the impeller blades 23 of the impeller 18 rotates the turbine 19.
- the torque of the turbine 19 is output to an input shaft of a transmission (not shown) via a turbine hub 27.
- the hydraulic oil flowing from the turbine 19 to the impeller 18 flows through the passage of the stator 20 to the impeller 18 side.
- the first window 61 of the drive member 52 and the second window of the driven member 53 which are characterized by their shapes, extend the life of the coil spring 58.
- the free length of this coil spring 58 is 3.2 times or more with respect to its diameter, and the rigidity is very low. Therefore, the coil spring 58 is weak against a force acting in the lateral direction.
- the coil spring 58 When the drive member 52 and the driven member 53 rotate relative to each other, the coil spring 58 is compressed by the rotation direction ends 61a and 62a of the first window 61 and the second window 62.
- the inclination angle of the ends 61a and 62a in the rotation direction ⁇ force is the predetermined value or more with respect to the maximum torsion angle ⁇ m
- the coil spring 58 When the coil spring 58 is compressed, it is possible to suppress an increase in the amount of radius on the outer peripheral side of the coil spring 58, and it is also possible to suppress the stress generated due to this.
- the inclination angle of the rotation direction ends 61a and 62a is less than a predetermined value with respect to the maximum torsion angle ⁇ m, the force for pushing the coil spring 58 radially outward by the rotation direction ends 61a and 62a (coil spring 58). (Force acting orthogonally to the longitudinal direction of the substrate) is suppressed. Therefore, even if the coil spring 58 having a relatively elongated shape is used, it is possible to suppress hiss torque of the torque converter 1 and wear of the elastic member.
- the structure of the lockup device is not limited to the above embodiment.
- the present invention can be applied not only to the torque converter but also to other fluid torque transmission devices. Industrial applicability
- the lock-up device according to the present invention can be used for a fluid torque transmission device such as a tonnole converter of a vehicle.
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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)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003-284659 | 2003-08-01 | ||
JP2003284659A JP4395343B2 (ja) | 2003-08-01 | 2003-08-01 | ロックアップ装置のダンパー機構 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005012767A1 true WO2005012767A1 (ja) | 2005-02-10 |
Family
ID=34101105
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/010925 WO2005012767A1 (ja) | 2003-08-01 | 2004-07-30 | ロックアップ装置のダンパー機構 |
Country Status (3)
Country | Link |
---|---|
US (1) | US7108112B2 (ja) |
JP (1) | JP4395343B2 (ja) |
WO (1) | WO2005012767A1 (ja) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004278744A (ja) * | 2003-03-18 | 2004-10-07 | Exedy Corp | ダンパー機構及びダンパーディスク組立体 |
JP2007009991A (ja) * | 2005-06-29 | 2007-01-18 | Exedy Corp | ダンパー機構及び流体式トルク伝達装置のロックアップ装置 |
US7658679B2 (en) | 2005-09-08 | 2010-02-09 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Series-parallel multistage torque converter damper |
EP1966518A2 (de) * | 2005-12-19 | 2008-09-10 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Statorseitenplatte für einen drehmomentwandler |
JP5078477B2 (ja) * | 2007-07-20 | 2012-11-21 | 株式会社エクセディ | ロックアップダンパー |
JP5078535B2 (ja) * | 2007-10-10 | 2012-11-21 | 株式会社エクセディ | ロックアップ装置およびそれを備えた流体式トルク伝達装置 |
JP2009243536A (ja) * | 2008-03-29 | 2009-10-22 | Aisin Aw Industries Co Ltd | ダンパ装置 |
JP5619015B2 (ja) * | 2008-10-17 | 2014-11-05 | 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Schaeffler Technologies AG & Co. KG | ダブルパストーショナルダンパ |
FR2947025B1 (fr) * | 2009-06-18 | 2011-07-15 | Valeo Embrayages | Amortisseur, notamment pour un dispositif de couplage en rotation de vehicule automobile |
JP4932934B2 (ja) * | 2010-10-19 | 2012-05-16 | 株式会社エクセディ | 流体式動力伝達装置のロックアップ装置 |
FR2974871B1 (fr) * | 2011-05-04 | 2013-05-17 | Valeo Embrayages | Dispositif d'amortissement de torsion comportant des organes elastiques dont chacun est maintenu individuellement en position par une rondelle de phasage |
CN102588459A (zh) * | 2012-03-21 | 2012-07-18 | 江苏名豪汽车零部件有限公司 | 一种汽车离合器从动盘总成减振盘的结构 |
CN104067018B (zh) * | 2012-03-27 | 2016-08-17 | 爱信艾达工业株式会社 | 减震器装置 |
EP2895235B8 (en) | 2012-09-14 | 2019-02-27 | Bal Seal Engineering, Inc. | Connector housings, use of, and method therefor |
DE102013219162A1 (de) * | 2013-09-24 | 2015-03-26 | Zf Friedrichshafen Ag | Kupplungsanordnung mit Schwingungstilger |
FR3013089B1 (fr) * | 2013-11-12 | 2017-04-07 | Valeo Embrayages | Support pour dispositif d'amortissement pour systeme de transmission de vehicule |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5975922U (ja) * | 1982-11-12 | 1984-05-23 | 株式会社大金製作所 | ダンパ−組立体のスプリング抜け防止構造 |
JPS6152423A (ja) * | 1984-08-21 | 1986-03-15 | Aisin Seiki Co Ltd | トルク変動吸収装置 |
JPH0545257U (ja) * | 1991-11-25 | 1993-06-18 | 株式会社大金製作所 | ダンパーデイスク |
JP2000505870A (ja) * | 1996-12-23 | 2000-05-16 | ヴァレオ | 改良されたトーションダンパ、およびこのトーションダンパを備えるダンピング装置 |
JP2000179645A (ja) * | 1998-12-18 | 2000-06-27 | Exedy Corp | トルクコンバータのロックアップダンパー |
JP2003202035A (ja) * | 2002-01-08 | 2003-07-18 | Exedy Corp | 捩じり振動ダンパーに用いられるコイルスプリング、ダンパーディスク組立体 |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5975922A (ja) | 1982-10-23 | 1984-04-28 | Denki Kagaku Kogyo Kk | エポキシ樹脂系成形材料 |
JPS624630U (ja) | 1985-06-24 | 1987-01-12 | ||
WO1989002551A1 (en) * | 1987-09-11 | 1989-03-23 | Kabushiki Kaisha Daikin Seisakusho | Lockup damper for torque converters |
FR2648883B1 (fr) | 1989-06-27 | 1993-01-22 | Valeo | Dispositif amortisseur de torsion, notamment friction d'embrayage pour vehicules automobiles |
US5052664A (en) | 1989-11-01 | 1991-10-01 | Barnes Group Inc. | Arcuate spring |
JPH03282043A (ja) * | 1990-03-28 | 1991-12-12 | Aisin Seiki Co Ltd | 直結クラッチ付トルクコンバータ |
JP2723393B2 (ja) | 1991-08-13 | 1998-03-09 | 株式会社クボタ | 屋根材踏割試験装置 |
US5246399A (en) * | 1991-12-11 | 1993-09-21 | Borg-Warner Automotive Transmission & Engine Components Corporation | Two-stage torsional vibration damper |
JPH08254246A (ja) | 1995-03-17 | 1996-10-01 | Exedy Corp | コイルスプリング及びダンパー装置 |
US6241614B1 (en) * | 1998-03-30 | 2001-06-05 | Exedy Corporation | Clutch disk assembly having a two stage dampening mechanism having a further vibration dampening mechanism that functions in both stages of dampening |
JP2000130555A (ja) * | 1998-10-26 | 2000-05-12 | Exedy Corp | トルクコンバータのロックアップ装置 |
JP2000179654A (ja) | 1998-12-16 | 2000-06-27 | Tsubakimoto Chain Co | 分割伝動輪 |
JP3848508B2 (ja) * | 1999-07-19 | 2006-11-22 | 株式会社エクセディ | ダンパー機構 |
JP2002106639A (ja) * | 2000-09-29 | 2002-04-10 | Exedy Corp | ダンパー機構 |
-
2003
- 2003-08-01 JP JP2003284659A patent/JP4395343B2/ja not_active Expired - Lifetime
-
2004
- 2004-07-26 US US10/898,203 patent/US7108112B2/en active Active
- 2004-07-30 WO PCT/JP2004/010925 patent/WO2005012767A1/ja not_active Application Discontinuation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5975922U (ja) * | 1982-11-12 | 1984-05-23 | 株式会社大金製作所 | ダンパ−組立体のスプリング抜け防止構造 |
JPS6152423A (ja) * | 1984-08-21 | 1986-03-15 | Aisin Seiki Co Ltd | トルク変動吸収装置 |
JPH0545257U (ja) * | 1991-11-25 | 1993-06-18 | 株式会社大金製作所 | ダンパーデイスク |
JP2000505870A (ja) * | 1996-12-23 | 2000-05-16 | ヴァレオ | 改良されたトーションダンパ、およびこのトーションダンパを備えるダンピング装置 |
JP2000179645A (ja) * | 1998-12-18 | 2000-06-27 | Exedy Corp | トルクコンバータのロックアップダンパー |
JP2003202035A (ja) * | 2002-01-08 | 2003-07-18 | Exedy Corp | 捩じり振動ダンパーに用いられるコイルスプリング、ダンパーディスク組立体 |
Also Published As
Publication number | Publication date |
---|---|
JP2005054845A (ja) | 2005-03-03 |
JP4395343B2 (ja) | 2010-01-06 |
US20050023103A1 (en) | 2005-02-03 |
US7108112B2 (en) | 2006-09-19 |
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