JP2010255753A - Power transmission device - Google Patents

Power transmission device Download PDF

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Publication number
JP2010255753A
JP2010255753A JP2009106703A JP2009106703A JP2010255753A JP 2010255753 A JP2010255753 A JP 2010255753A JP 2009106703 A JP2009106703 A JP 2009106703A JP 2009106703 A JP2009106703 A JP 2009106703A JP 2010255753 A JP2010255753 A JP 2010255753A
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Japan
Prior art keywords
power transmission
portion
transmission device
rotating member
device according
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.)
Pending
Application number
JP2009106703A
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Japanese (ja)
Inventor
Takuya Okada
岡田  卓也
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Toyota Motor Corp
トヨタ自動車株式会社
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Priority to JP2009106703A priority Critical patent/JP2010255753A/en
Publication of JP2010255753A publication Critical patent/JP2010255753A/en
Application status is Pending legal-status Critical

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H41/00Rotary fluid gearing of the hydrokinetic type
    • F16H41/24Details
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0205Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221Combinations 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221Combinations 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
    • F16H2045/0252Combinations 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 having a damper arranged on input side of the lock-up clutch
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273Combinations 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
    • F16H2045/0294Single disk type lock-up clutch, i.e. using a single disc engaged between friction members

Abstract

A power transmission device capable of reducing a load on a bearing is provided.
A power transmission device includes a bearing that is interposed between an outer peripheral side of a first rotating member and an inner peripheral side of a second rotating member. A second portion 9b having a lower strength than the first portion 9a joined to the crankshaft 103 in the first rotating member 9 is provided between the one end 9c and the first portion 9a.
[Selection] Figure 1

Description

  The present invention relates to a power transmission device, and more particularly to a power transmission device mounted on a vehicle.

  Conventionally, for example, Japanese Patent Publication No. 2002-521624 (Patent Document 1), Japanese Patent Application Laid-Open No. 6-42548 (Patent Document 2), Japanese Patent No. 3455550 (Patent Document 3), Japanese Patent No. 3660924 (Patent Document 4) and Japanese Patent No. 3789494 (Patent Document 5).

JP-T-2002-521624 JP-A-6-42548 Japanese Patent No. 3455550 Japanese Patent No. 3660924 Japanese Patent No. 3789494

  In the prior art, when the output shaft of the engine and the input shaft of the transmission or the torque converter are inclined, there is a problem that a portion that can absorb this inclination is not provided and a load is applied to the power transmission device.

  Accordingly, the present invention has been made to solve the above-described problems, and an object thereof is to provide a power transmission device capable of reducing a load applied to the power transmission device.

  A power transmission device according to the present invention includes a crankshaft, a first rotating member connected to the crankshaft, a damper connected to the first rotating member, a second rotating member connected to the damper, A bearing interposed between the outer peripheral side of the rotating member and the inner peripheral side of the second rotating member. In the first rotating member, a second portion having a rigidity lower than that of the first portion joined to the crankshaft is provided between the contact portion with the bearing and the first portion.

  In the power transmission device configured as described above, in the first rotating member, the second rotating member having lower rigidity than the first portion joined to the crankshaft is between the first portion and the contact portion of the bearing. Is provided. Therefore, even if an inclination occurs between the first rotating member and the second rotating member during assembly, the inclination can be absorbed by the second portion having low rigidity. As a result, the load applied to the power transmission device can be reduced.

Preferably, the thickness of the second part is thinner than the thickness of the first part.
Preferably, the second portion extends with an inclination with respect to the rotation axis.

Preferably, the second portion extends perpendicular to the rotation axis.
Preferably, the second part is made of a material different from that of the first part.

Preferably, the second portion is provided with a through hole penetrating the first rotating member.
Preferably, the second part includes a recess.

  Preferably, a torque converter connected to the second rotating member is further provided.

It is sectional drawing of the power transmission device according to Embodiment 1 of this invention. It is a figure which shows the kind of bearing hold | maintained by the 1st rotation member in the power transmission mechanism according to Embodiment 1 of this invention in FIG. It is a figure which shows the kind of bearing hold | maintained by the 1st rotation member in the power transmission mechanism according to Embodiment 1 of this invention in FIG. It is a figure which shows the kind of bearing hold | maintained by the 1st rotation member in the power transmission mechanism according to Embodiment 1 of this invention in FIG. It is a figure for demonstrating the effect in the structure according to this invention. It is sectional drawing of the power transmission device according to Embodiment 2 of this invention. It is sectional drawing of the power transmission device according to Embodiment 3 of this invention. It is sectional drawing of the power transmission device according to Embodiment 4 of this invention. It is the top view of the 1st rotation member seen from the direction shown by arrow XI in FIG. It is sectional drawing of the power transmission device according to Embodiment 5 of this invention.

  Embodiments of the present invention will be described below with reference to the drawings. In the following embodiments, the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated. In addition, the embodiments can be combined.

(Embodiment 1)
FIG. 1 is a cross-sectional view of a power transmission device according to Embodiment 1 of the present invention. Referring to FIG. 1, a power transmission device 1 is a device for transmitting torque from a crankshaft 103 of an engine to an output shaft 6. The engine is arranged on the right side of FIG. 1, and the transmission is arranged on the left side of FIG. Both the crankshaft 103 and the output shaft 6 can rotate around the rotation shaft 60.

  The torque converter includes a fluid working chamber and a lock-up mechanism 170, and the fluid working chamber includes a turbine runner 40, a pump impeller 30, and a stator 23, which are three types of impellers. A disc-shaped front cover 3 is disposed on the front side of the torque converter, that is, on the side close to the engine, and the front cover 3 is positioned so as to extend from the rotating shaft 60 to the outer peripheral side, that is, to extend in the radial direction. . The front cover 3 acts as a front casing of the torque converter. A pump shell 33 is fixed to the front cover 3, and a predetermined space is constituted by the front cover 3 and the pump shell 33, and various elements of the torque converter 100 are arranged in this space. A space surrounded by the torque converter 100 and the impeller shell (pump shell) 33 is a substantially sealed space, and an automatic transmission fluid (ATF) as a working fluid is sealed in this space.

  The front cover 3 is a member that receives power from the engine. When power is input from the crankshaft 103 of the engine to the front cover 3 via the first rotating member 9, the damper 74, and the second rotating member 176, the front cover 3 3 rotates, and this rotational force is transmitted to the pump shell 33. The pump shell 33 constitutes the pump impeller 30, and the pump shell 33 is a component on the outside of the pump impeller 30. The pump impeller 30 is disposed so as to face the turbine runner 40, and can rotate around the rotation shaft 60 of the output shaft 6. The pump impeller 30 is provided with a blade 31 shaped to extrude ATF toward the turbine runner 40, and the ATF in the vicinity of the pump impeller 30 is rotated by the blade 31 by the turbine runner 40 as the pump impeller 30 rotates. Extruded toward.

  The stator 23 is interposed between the pump impeller 30 and the turbine runner 40 and functions to change the flow direction of ATF flowing from the turbine runner 40 to the pump impeller 30. The stator 23 is attached to a fixed shaft 39 via a one-way clutch 37 and can rotate only in one direction. As the one-way clutch 37, a structure using a roller, a sprag, or a ratchet mechanism can be adopted. The stator 23 is a blade for rectifying the flow of ATF returning from the turbine runner 40 to the pump impeller 30 and is made of resin or aluminum.

  The turbine runner 40 has a turbine shell 43 that constitutes a space for circulating the ATF, and is disposed so as to face the pump impeller 30. The turbine runner 40 receives the ATF sent out by the pump impeller 30, and a rotational force is applied by the ATF. The ATF transmitted to the turbine runner 40 moves to the inner peripheral side and is sent again to the pump impeller 30 via the stator 23. The turbine runner 40 can rotate independently of the pump impeller 30.

  The pump impeller 30 rotates integrally with the front cover 3, while the turbine runner 40 rotates integrally with the lockup piston 4. A power transmission member 44 is disposed so as to come into contact with the turbine shell 43. The power transmission member 44 is integrated with the turbine shell 43 at a fastening portion such as a rivet or a bolt, and rotates together with the turbine shell 43.

  Both the power transmission member 44 and the turbine shell 43 are fixed to the turbine hub 7. The power transmission member 44 and the turbine shell 43 can rotate with the output shaft 6 as the rotation shaft 60 together with the turbine hub 7. The turbine hub 7 is spline-fitted to the output shaft 6 and is located on the outer peripheral side of the output shaft 6. The turbine hub 7 connects the output shaft 6 and the turbine shell 43 and functions to transmit the rotation input to the turbine shell 43 to the output shaft 6.

  The blade 31 has tip portions 31 a and 31 b as tabs, and the tip portion 31 a is engaged with the pump shell 33. The tip portion 31 b is inserted into the pump core 32.

  The blade 41 has tip portions 41 a and 41 b as tabs, and the tip portion 41 a is inserted into the turbine shell 43. The tip portion 41 b is inserted into the turbine core 42.

  A tip end portion of the crankshaft 103 as an input shaft is fastened to the first rotating member 9 by a bolt 179. A through hole 9 h for receiving the bolt 179 is provided in the first rotating member 9. A first portion 9a and a second portion 9b are provided between one end 9c of the first rotating member 9 and the through hole 9h. The first portion 9 a is a portion in the vicinity where the bolt 179 is attached and is pressed by the bolt 179. The second portion 9 b is a low-strength portion between the first portion 9 a and the one end 9 c that contacts the bearing 177, and extends so as to be inclined with respect to the rotation shaft 60. One end 9c holds the bearing 177.

  On the other end 9d side of the first rotating member 9, a through hole 9p is provided. Bolts 180 are inserted into the through holes 9p, and the bolts 180 join the outer damper support member 174 and the first rotating member 9 together. A damper 74 is provided between the outer damper support member 174 and the inner damper support member 175. The damper 74 is configured by a coil spring. One end of the coil spring is connected to the outer damper support member 174, and the other end of the coil spring is connected to the inner damper support member 175. Torque fluctuations can be mitigated by the expansion and contraction of the coil springs constituting the damper 74. Since the damper 74 exists, a rotation difference is generated between the first rotating member 9 provided on one end side of the damper 74 and the second rotating member 176 provided on the other end side. A bearing 177 is provided to absorb this difference. The bearing 177 is in contact with the inner peripheral side of the second rotating member 176, and the bearing 177 is in contact with the outer peripheral side of the first rotating member 9.

  The lock-up mechanism 170 is a device for directly transmitting the rotational force of the front cover 3 to the output shaft 6, and the facing force 76 as a friction member contacts the inner peripheral surface of the front cover 3, thereby rotating the front cover 3. Can be transmitted to the output shaft 6. The lockup mechanism 170 has a lockup piston 4 for attaching the facing 76. The lock-up piston 4 can move in the axial direction, that is, the direction approaching the front cover 3 and the direction away from the front cover 3, and the facing 76 can contact the front cover 3. The lock-up piston 4 has a disk shape extending in the radial direction of rotation (radial direction), and is disposed so as to face the front cover 3.

  A facing 76 is fixed to the outer peripheral side of the lockup piston 4, and the inner peripheral side of the lockup piston 4 is in contact with the turbine hub 7. A space between the front cover 3 and the lockup piston 4 is a first hydraulic chamber, and a space between the lockup piston 4 and the power transmission member 44 is a second hydraulic chamber. By changing the hydraulic pressure in the first hydraulic chamber and the second hydraulic chamber, the lock-up piston 4 can move in a direction approaching the front cover 3 and a direction moving away from the front cover 3.

  The operation of the lockup mechanism 170 will be described. When the torque amplification function of the torque converter 100 is not particularly required, the facing force is directly brought into contact with the front cover 3 to directly transmit the rotational force of the front cover 3 to the output shaft 6. Specifically, the ATF in the first hydraulic chamber is released through the through hole 6h. As a result, the hydraulic pressure in the first hydraulic chamber becomes lower than the hydraulic pressure in the second hydraulic chamber. As a result, the lock-up piston 4 moves toward the front cover 3 and the facing 76 and the front cover 3 come into contact with each other. Thereby, the power of the front cover 3 is transmitted to the output shaft 6 through the facing 76, the lock-up piston 4, the power transmission member 44, and the turbine hub 7. In this state, the power loss by the torque converter 100 hardly occurs.

  When the torque amplifying action of the torque converter 100 is required, ATF is fed into the first hydraulic chamber via the through hole 6h. As a result, the hydraulic pressure in the first hydraulic chamber is increased. As a result, a gap is generated between the front cover 3 and the facing 76, and the rotational force of the front cover 3 is not directly transmitted to the facing 76.

  2 to 4 are diagrams showing types of bearings held by the first rotating member in the power transmission mechanism according to the first embodiment of the present invention in FIG. 2 to 4, the shape of the bearing 177 held on the one end 9c side of the first rotating member 9 can be variously modified. A small bearing may be used as shown in FIG. 2, a medium bearing may be used as shown in FIG. 3, and a large bearing may be used as shown in FIG. Even if the size of the bearing 177 changes in this way, it is possible to support various bearings by changing the size and position of the one end 9c. In this embodiment, an example in which a ball bearing is used is shown, but the present invention is not limited to this, and it is also possible to use a bearing having another shape such as a roller bearing or a tapered roller bearing.

  As shown in FIG. 1, a portion of the torque converter 100 is supported by a support portion 81 on the case 80 side. ATF is supplied to the support portion 81, and the friction between the rotating member 70 and the case is reduced by the action of the ATF.

  FIG. 5 is a diagram for explaining the effect in the structure according to the present invention. As shown in FIG. 5, when the damper unit 110 and the torque converter 100 are assembled in contact with each other, the rotating shaft of the damper unit 110 may be inclined with respect to the rotating shaft of the torque converter 100. This inclination occurs due to a manufacturing intersection between the torque converter 100 and the damper unit 110. Even in this case, the second portion 9b having low rigidity exists, and the second portion 9b is deformed, whereby the bearing 177 can be held at an appropriate position. As a result, it is possible to reduce the load on the power transmission device caused by the inclination.

  That is, the load caused by the misalignment is absorbed by the low rigidity second portion 9b. As a result, adverse effects on the damper unit 110 can be reduced. Further, the second rotating member 176 and the inner damper support member 175 are fitted with splines, but the spline fitting is not adversely affected. Furthermore, since the spline diameter can be increased, the axial length of the spline can be reduced.

  Furthermore, there is no restriction | limiting in the magnitude | size of the bearing 177, and ensuring of intensity | strength becomes easy. Further, compatibility with the torque converter 100 having a different structure is improved. That is, various torque converters 100 can be combined regardless of the shape of the crankshaft 103.

  The torque converter 100 is supported by a front bearing 177 and a rear support part 81 with a structure in which the damper part 110 is arranged on the front side of the torque converter 100, and a second rotating member 176 and a support part 81 supported by the bearing 177. There is no damper between. Bearings 177 are arranged on the outer peripheral side of the first rotating member 9 connected to the crankshaft 103 and on the inner peripheral side of the second rotating member 176 supported by the torque converter 100.

  That is, the power transmission device 1 includes a crankshaft 103, a first rotating member 9 connected to the crankshaft 103, a damper 74 connected to the first rotating member 9, and a second rotating member connected to the damper 74. 176. A bearing 177 is interposed between the outer peripheral side of the first rotating member 9 and the inner peripheral side of the second rotating member 176. In the first rotating member 9, a second portion 9b having a lower strength than the first portion 9a connected to the crankshaft 103 is provided between the first portion 9a and one end 9c which is a contact portion with the bearing. Yes.

(Embodiment 2)
FIG. 6 is a cross-sectional view of a power transmission device according to the second embodiment of the present invention. Referring to FIG. 6, in power transmission device 1 according to the second embodiment of the present invention, second portion 9 f is made of a material different from that of the other portion of first rotating member 9. Thus, it is different from the power transmission device 1 according to the first embodiment. As a material constituting the low-rigidity second portion 9f, a specific element can be removed from the iron constituting the first rotating member 9 to reduce the strength of the second portion 9f. Further, the second portion 9f may be formed by joining low-strength members by welding. The power transmission device 1 according to the second embodiment configured as described above has the same effects as the power transmission device 1 according to the first embodiment.

(Embodiment 3)
FIG. 7 is a cross-sectional view of the power transmission device according to the third embodiment of the present invention. Referring to FIG. 7, in the power transmission device 1 according to the third embodiment of the present invention, the second portion 9 b is in accordance with the first embodiment in that the second portion 9 b extends in a direction orthogonal to the rotation shaft 60. Different from the power transmission device 1. The thickness of the first portion 9a, which is a thick portion, is a, and the thickness of the second portion 9b, which is a thin portion, is b. The power transmission device according to the third embodiment as shown in FIG. 7 has the same effect as the power transmission device according to the first embodiment.

(Embodiment 4)
FIG. 8 is a cross-sectional view of a power transmission device according to Embodiment 4 of the present invention. FIG. 9 is a plan view of the first rotating member viewed from the direction indicated by the arrow XI in FIG. With reference to FIGS. 8 and 9, in power transmission device 1 according to the fourth embodiment of the present invention, second portion 9b is provided with through hole 9y, and through hole 9y, second portion 9b is The rigidity is lower than that of the portion 9a. As shown in FIG. 9, the through holes 9 y may be provided at equal intervals in the first rotating member 9. Further, the through holes 9y may be provided at unequal intervals instead of as shown in FIG.

  The power transmission device according to the fourth embodiment configured as described above has the same effects as the power transmission device according to the first embodiment. Moreover, since the through-hole 9y can be processed by a press, it is possible to realize this with almost no increase in cost.

(Embodiment 5)
10 is a cross-sectional view of a power transmission device according to a fifth embodiment of the present invention. Referring to FIG. 5, power transmission device 1 according to the fifth embodiment of the present invention is different from the power transmission device according to the first embodiment in that concave portion 9z is provided in second portion 9b. . As shown in FIG. 9, the recesses 9z may be provided at equal intervals in the circular portion of the first rotating member 9, or may be provided at unequal intervals. The presence of the recess 9z can reduce the strength of the second portion 9b.

  The power transmission device according to the sixth embodiment configured as described above has the same effects as the power transmission device 1 according to the first embodiment.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  DESCRIPTION OF SYMBOLS 1 Power transmission device, 3 Front cover, 4 Lockup piston, 6 Output shaft, 6h Through-hole, 7 Turbine hub, 9c One end, 9d The other end, 9z Recessed part, 9 First rotation member, 9a First part, 9b Second Part, 9y through hole, 23 stator, 30 pump impeller, 31 blade, 31a, 31b tip part, 32 pump core, 33 pump shell, 37 one-way clutch, 39 fixed shaft, 40 turbine runner, 41 blade, 42 turbine core, 43 turbine Shell, 44 Power transmission member, 60 Rotating shaft, 70 Rotating member, 74 Damper, 76 Facing, 80 Case, 81 Support, 100 Torque converter, 103 Crankshaft, 110 Damper, 170 Lock-up mechanism, 174 Outside Damper support member 175 inside the damper supporting member, 176 the second rotary member 177 bearings.

Claims (8)

  1. A crankshaft,
    A first rotating member connected to the crankshaft;
    A damper connected to the first rotating member;
    A second rotating member connected to the damper;
    A bearing interposed between an outer peripheral side of the first rotating member and an inner peripheral side of the second rotating member;
    In the first rotating member, a power transmission device in which a second portion having a lower strength than the first portion joined to the crankshaft is provided between a contact portion with the bearing and the first portion.
  2.   The power transmission device according to claim 1, wherein a thickness of the second portion is thinner than a thickness of the first portion.
  3.   The power transmission device according to claim 1, wherein the second portion extends while being inclined with respect to the rotation axis.
  4.   The power transmission device according to claim 1, wherein the second portion extends perpendicular to the rotation axis.
  5.   The power transmission device according to claim 1, wherein the second portion is made of a material different from that of the first portion.
  6.   The power transmission device according to claim 1, wherein the second portion is provided with a through-hole penetrating the second rotating member.
  7.   The power transmission device according to claim 1, wherein the second portion is provided with a recess.
  8.   The power transmission device according to claim 1, further comprising a torque converter connected to the second rotating member.
JP2009106703A 2009-04-24 2009-04-24 Power transmission device Pending JP2010255753A (en)

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Cited By (14)

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JP2012167788A (en) * 2011-02-16 2012-09-06 Toyota Motor Corp Device for reducing torsional vibration
WO2012144010A1 (en) * 2011-04-18 2012-10-26 トヨタ自動車株式会社 Vehicle torque converter
WO2012144009A1 (en) * 2011-04-18 2012-10-26 トヨタ自動車株式会社 Vehicle torque converter
JP2012225379A (en) * 2011-04-18 2012-11-15 Toyota Motor Corp Device for reducing torsional vibration
JP2012225378A (en) * 2011-04-18 2012-11-15 Toyota Motor Corp Torsional vibration reducing device
EP2574822A2 (en) 2011-09-29 2013-04-03 Aisin Seiki Kabushiki Kaisha Torque fluctuation absorber
WO2013045994A1 (en) * 2011-09-29 2013-04-04 Toyota Jidosha Kabushiki Kaisha Vehicular fluid power transmitting device
WO2013046008A1 (en) * 2011-09-29 2013-04-04 Toyota Jidosha Kabushiki Kaisha Vehicular fluid power transmitting device
WO2013046006A1 (en) * 2011-09-29 2013-04-04 Toyota Jidosha Kabushiki Kaisha Vehicular fluid power transmitting device
JP2013076416A (en) * 2011-09-29 2013-04-25 Toyota Motor Corp Vehicular hydraulic transmission apparatus
JP2013160275A (en) * 2012-02-02 2013-08-19 Toyota Motor Corp Damper device for vehicle
JP2013242004A (en) * 2012-05-21 2013-12-05 Toyota Motor Corp Power transmission device
JP2014009705A (en) * 2012-06-27 2014-01-20 Aisin Seiki Co Ltd Power transmission device
CN107407388A (en) * 2015-03-25 2017-11-28 舍弗勒技术股份两合公司 Torque transmitter

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JP2002195378A (en) * 2000-12-26 2002-07-10 Exedy Corp Lockup device for fluid type torque transmission device
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