JP2008038951A - Fluid type torque transmitting apparatus - Google Patents

Fluid type torque transmitting apparatus Download PDF

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Publication number
JP2008038951A
JP2008038951A JP2006210824A JP2006210824A JP2008038951A JP 2008038951 A JP2008038951 A JP 2008038951A JP 2006210824 A JP2006210824 A JP 2006210824A JP 2006210824 A JP2006210824 A JP 2006210824A JP 2008038951 A JP2008038951 A JP 2008038951A
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JP
Japan
Prior art keywords
turbine
turbine runner
spring
torque transmission
fluid
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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
JP2006210824A
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Japanese (ja)
Inventor
Masahito Ichinose
Atsushi Inoue
Seiji Momoi
雅人 一之瀬
敦 井上
誠二 桃井
Original Assignee
Valeo Unisia Transmission Kk
ヴァレオユニシアトランスミッション株式会社
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.)
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Application filed by Valeo Unisia Transmission Kk, ヴァレオユニシアトランスミッション株式会社 filed Critical Valeo Unisia Transmission Kk
Priority to JP2006210824A priority Critical patent/JP2008038951A/en
Publication of JP2008038951A publication Critical patent/JP2008038951A/en
Pending legal-status Critical Current

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Abstract

When a driven claw constituting a damper is joined to a turbine shell by welding, the turbine shell is thermally deformed or a hole is formed, and the number of parts increases. On the other hand, a portion surrounded by the notch is cut out from the turbine shell. When the driven claw is integrally formed by bending, the fluid flows out from the notch portion, and the performance of the torque transmitting portion is lowered.
A U-shape is formed in a turbine shell 6a at a position that is radially inward of a portion of a torque transmission portion 8 formed by an impeller shell 3a and a turbine shell 6a and that does not affect the torque transmission portion 8. The notched portion 11a is formed, and the driven claw 11 is formed by bending the portion surrounded by the notched portion 11a outward in the radial direction.
[Selection] Figure 1

Description

  The present invention relates to a fluid torque transmission device, and is an improvement of a damper built in the fluid torque transmission device.

  An automobile is provided with a fluid torque transmission device that transmits torque without an impact between an engine crankshaft and a transmission. The hydrodynamic torque transmission device includes a fluid coupling having no stator and a torque converter having a stator.

  The fluid torque transmission device is provided with a lock-up clutch that directly connects the engine and the input shaft of the transmission without fluid when the operating state is in a predetermined state, and the torque fluctuation caused by the direct connection is provided. A damper is connected to the lockup clutch for absorption.

  As a conventional fluid-type torque transmission device, for example, the one described in Patent Document 1 is known. In this fluid torque transmission device, a damper is provided between a lock-up piston constituting a lock-up clutch and a turbine runner connected to the transmission, and the damper is a component of the coil spring in the circumferential direction. A driven plate having a locking portion for compressing to a turbine is welded to the outer peripheral surface of the turbine shell, which is a component of the turbine runner.

  However, the turbine shell and the driven plate are likely to be thermally deformed by the welding heat, and the thin turbine shell is likely to have a hole during welding, resulting in an increase in the number of parts.

On the other hand, as a fluid type torque transmission device which prevents thermal deformation, there is one described in Patent Document 2. This fluid torque transmitting device is formed by forming a notch in a portion corresponding to a spring in the turbine shell, and bending the position of the notch to form a damper abutting projection as a spring pressing portion.
JP 2001-295912 A Japanese Patent Laid-Open No. 2005-155821

  However, since a plurality of large notches are formed in a portion corresponding to the spring in the circumferential direction of the turbine shell, the fluid flows from the component portion of the torque transmission portion that transmits the rotational force via the fluid via the notch. It will flow out, and the performance of the torque transmission part will deteriorate.

  Then, an object of this invention is to provide the fluid type torque transmission device which solved said subject.

  According to a first aspect of the present invention, there is provided a front cover coupled to an engine crankshaft, a pump impeller disposed coaxially with the front cover and forming a fluid chamber between the front cover, and coaxial with the interior of the fluid chamber. A turbine runner that constitutes a torque transmitting portion at an outer peripheral portion of a portion that is disposed and faces the pump impeller, a turbine hub that is coupled to an axial center position of the turbine runner and is spline-coupled to an input shaft of the transmission, the turbine runner, and the turbine runner A lockup piston that is coaxially disposed between the front cover and is rotated by being pressed against the inner wall surface of the front cover, a spring that receives a compression load, and a spring that is coupled to the lockup piston and accommodates the spring along a circumferential direction. A spring formed with a housing portion for restricting the spring in the radial direction, the axial direction and the circumferential direction. In the hydrodynamic torque transmitting device, comprising: a lud plate; and a spring pressing portion that is integrally formed with the turbine runner and protrudes toward the hold plate and compresses the spring accommodated in the spring accommodating portion in a circumferential direction. The spring pressing portion is formed by notching and bending a part of the turbine runner on the radially inner side of a portion constituting the torque transmission portion in the turbine runner.

  According to the present invention, the spring pressing portion formed integrally with the turbine runner is formed by cutting out and bending the inner side in the radial direction from the portion constituting the torque transmission portion in the turbine runner. The notched portion is disengaged from the portion constituting the torque transmitting portion. Therefore, there is no problem that the performance of the torque transmission unit is deteriorated.

  The invention according to claim 2 is the fluid torque transmission device according to claim 1, wherein the turbine hub is press-fitted into the turbine runner, and the turbine hub is caulked into the turbine runner. It is characterized by being connected.

  According to the present invention, since the turbine runner and the turbine hub are joined by press-fitting and caulking, no new parts are separately required for joining the two.

  The invention according to claim 3 is the fluid torque transmission device according to claim 1, wherein a flange portion is integrally formed with the turbine hub, and the flange portion is coupled to the turbine runner via a rivet. Features.

  According to this invention, since the flange part formed in the turbine hub and the turbine runner are coupled via the rivet, the coupling strength is high. Therefore, even if the transmission torque is high, it can be dealt with. Also, since they are connected by rivets, slip does not occur between the turbine runner and the turbine hub, and it is necessary to increase the frictional resistance between the two by increasing the plate thickness as in the case of press-fitting to prevent slippage. Therefore, the thickness of the turbine runner can be reduced.

  According to the fluid type torque transmission device according to the present invention, the spring pressing portion is formed by cutting and bending a part of the turbine runner, so that it is not necessary to weld the spring pressing portion to the turbine runner, and by welding. It is possible to avoid thermal deformation of the turbine runner and the spring pressing portion and generation of holes generated in the turbine runner during welding.

  Moreover, since it is not the structure which provides a spring press part separately and couple | bonds with a turbine runner, the number of parts is reduced, the weight of a fluid type torque transmission device becomes small, and the dimension of an axial direction is suppressed.

  Furthermore, a spring pressing part is formed by cutting and bending a part of the turbine runner, but the inner side in the radial direction is cut away from the part constituting the torque transmission part, so the efficiency of the torque transmission part is reduced due to fluid leakage. Is avoided.

Hereinafter, embodiments of the fluid torque transmission device according to the present invention will be described as first to third embodiments. Embodiments 1 to 3 show cases where the fluid torque transmission device is a torque converter having a stator.
(A) Embodiment 1
First, the configuration of the first embodiment of the fluid torque transmission device is shown in FIG. An engine crankshaft (not shown) is provided on the left side of the torque converter 1. A front cover 2 on the left side of the torque converter 1 is coupled to the crankshaft via a plurality of bolts 5 coupled to the front cover 2 and a drive plate (not shown). A pump impeller 3 is coaxially arranged with respect to the front cover 2, and a converter housing 4 having a fluid chamber is configured by welding the outer peripheral portions of the front cover 2 and the pump impeller 3 together. The pump impeller 3 is composed of an impeller shell 3a, a core 3b, and a plurality of blades 3c. The impeller shell 3a is rotated to an oil pump of a transmission (not shown) located to the right of the torque converter 1 at the axial center position. The flange portion of the sleeve 7 for transmitting force is welded. A turbine runner 6 is coaxially arranged inside the converter housing 4, and a torque transmission portion 8 is formed on the outer peripheral portion of the portion where the turbine runner 6 and the pump impeller 3 face each other. The turbine runner 6 includes a turbine shell 6a, a core 6b, and a plurality of blades 6c. A turbine hub 9 is provided at the axial center of the turbine runner 6, and the turbine hub 9 is coupled to the turbine runner 6. The coupling between the turbine runner 6 and the turbine hub 9 is as follows. The turbine shell 6a constituting the turbine runner 6 is press-fitted into the outer peripheral portion of the turbine hub 9, and the turbine hub 9 is coupled to the turbine shell 6a by caulking the turbine hub 9 to form a caulking portion 9a. Has been. The turbine hub 9 is splined to an input shaft (not shown) of the transmission.

  A lock-up piston 19 is provided to directly connect the front cover 2 and the turbine runner 6 when the operating state of the torque converter 1 is in a predetermined state. The cylindrical portion on the inner peripheral side of the lockup piston 19 is provided on the outer peripheral surface of the cylindrical portion of the turbine hub 9 so as to be movable in the axial direction via a seal ring 23. A friction material 14 is bonded to a position where it contacts the inner wall surface. The lockup piston 19 and the turbine runner 6 are connected via a damper 20.

  The damper 20 is coupled to the lockup piston 19 via the rivet 10 and holds the spring 24. The spring 24 receives the compression load. The damper 20 projects toward the hold plate 21 and presses and compresses the spring 24. It is comprised with the driven nail | claw 11 as a spring press part. The holding plate 21 is formed with an accommodating portion 12 that accommodates a spring 24 along the circumferential direction. The spring 24 accommodated in the accommodating portion 12 is compressed between the hold plate 21 and the driven claw 11. .

  The accommodating portion 12 regulates the spring 24 in the radial direction, the axial direction, and the circumferential direction, and forms a plurality of notches along the circumferential direction of one ring-shaped plate, and the notches As shown in FIG. 1, the inner side in the radial direction is bent in an arc shape to the left side in the circumferential direction to form the inner circumferential side restricting portion 12a, while the outer side in the radial direction of the notch is in the circumferential direction. The outer peripheral side restricting portions 12b and 12c are formed by bending one side to the right side and the other side to the left side in an arc shape. The spring 24 is regulated in the radial direction and the axial direction by the inner circumferential side regulating portion 12a and the outer circumferential side regulating portions 12b and 12c.

  The configuration of the driven claw 11 will be described below. As shown in FIG. 2, the turbine shell 6 a constituting the turbine runner 6 is bent in such a manner that a part of the turbine shell 6 a is notched and bent radially inward from the portion constituting the torque transmission portion 8. Thus, a plurality of driven claws 11 are formed. That is, six substantially U-shaped cutout portions 11a are formed at substantially equal intervals along the circumferential direction of the turbine shell 6a, and the portion surrounded by the cutout portions 11a is raised outward to protrude in the axial direction. A driven claw 11 is formed. The driven claw 11 is provided on the radially outer side of the turbine shell 6a with respect to the cutout portion 11a. In other words, the opening formed by the formation of the cutout portion 11a exists on the radially inner side of the driven claw 11. A plurality of slits 6d are formed along a circular arc on the inner side in the radial direction and on the outer side in the radial direction in the ring-shaped portion of the turbine shell 6a that forms the torque transmission unit 8. This is for fitting or bending or brazing convex portions formed in the vicinity of both ends of the blade 6b. Three communication holes 6e are formed at substantially equal intervals in the circumferential direction at the center of the turbine shell 6a. This is for smooth movement of the pressure oil between the turbine shell 6 a and the lock-up piston 19 and smooth movement of the lock-up piston 19.

  A stator 15 is provided between the pump impeller 3 and the turbine runner 6 in the axial direction, and the stator 15 is set to be rotatable only in one direction. A configuration in the vicinity of the stator 15 will be described. An outer race 18 is press-fitted inside the stator 15, and an inner race 16 is provided inside the outer race 18 via a one-way clutch 17. The inner race 16 is splined to a hollow fixed shaft (not shown) whose rotation is restricted. On both sides of the stator 15, there are provided thrust bearings 13 as thrust bearings for receiving axial axial thrust force between the stator 15 and the turbine shell 6 a and between the stator 15 and the sleeve 7.

  The operation of the torque converter 1 having the above configuration will be described. When torque is input to the converter housing 4 from a crankshaft (not shown), the torque is transmitted to the turbine runner 6 via the torque transmission portion 8 and is transmitted from the turbine hub 9 to the transmission via an input shaft (not shown). In an operating state where the difference in rotational speed between the pump impeller 3 and the turbine runner 6 is large, the torque amplification action by the stator 15 works, and the turbine runner 6 is rotated with a large torque. When the difference in rotational speed between the pump impeller 3 and the turbine runner 6 is reduced, the torque amplification action is lost, and power is merely transmitted from the pump impeller 3 to the turbine runner 6 via the torque transmission unit 8.

  When the operating state of the torque converter 1 becomes a predetermined condition, the lock-up piston 19 moves to the left, the friction material 14 is pressed against the inner wall surface of the front cover 2, and the lock-up piston 19 is directly connected to the front cover 2. The Therefore, the rotational torque of the front cover 2 is directly transmitted to the turbine hub 9 via the lockup piston 19 and the damper 20 without passing through the torque transmission unit 8. When torque fluctuation occurs and the turbine shell 6a rotates relative to the hold plate 21 constituting the damper 20, the spring 24 housed in the housing portion 12 of the hold plate 21 is watched by the driven claw 11 integrated with the turbine shell 6a. Compressed from the direction or counterclockwise, torque fluctuations are absorbed.

  According to this invention, the driven claw 11 formed integrally with the turbine shell 6a is formed by cutting out and bending the inner side in the radial direction from the portion constituting the torque transmitting portion 8 in the turbine shell 6a. The notched portion of the turbine shell 6 a is out of the portion constituting the torque transmission unit 8. Therefore, the problem that the performance of the torque transmission part 8 falls does not arise.

According to the present invention, since the turbine shell 6a and the turbine hub 9 are joined by press-fitting and caulking, no new parts are separately required to join them.
(B) Embodiment 2
Next, Embodiment 2 is shown in FIG. Since this embodiment is obtained by changing a part of the first embodiment, description of the same part is omitted, and only a different part will be described.

  As can be seen from a comparison between FIG. 1 and FIG. 3, the configuration of the driven claw 11 formed on the turbine shell 6a is different. In FIG. 1, a U-shaped notch 11a is formed, and a driven claw 11 is formed by bending a portion surrounded by the notch 11a radially outward. In FIG. 3, a U-shaped notch is formed. The driven claw 11 is formed by reversing the direction of 11a and bending the portion surrounded by the notch 11a inward in the radial direction.

Since other configurations and operations are the same as those of the first embodiment, description thereof is omitted.
(C) Embodiment 3
Finally, Embodiment 3 is shown in FIG. Since this embodiment is obtained by changing a part of the first embodiment, description of the same part is omitted, and only a different part will be described.

  As can be seen from a comparison between FIG. 1 and FIG. 4, this embodiment is different in the configuration of the coupling portion between the turbine shell 6 a and the turbine hub 9. That is, in FIG. 1, the turbine hub 9 is coupled to the turbine shell 6 a via press-fitting and caulking, but in FIG. 4, a flange portion 9 b is formed on the turbine hub 9, and the flange portion 9 b is connected to the turbine shell via the rivet 22. This is a combination of 6a. Then, a cutting line along the radial direction is formed on the inner peripheral portion of the turbine shell 6a, and a driven claw 11 is formed by bending a portion sandwiched between the cutting lines outward in the radial direction.

  In the first and second embodiments, the communication hole 6e formed in the turbine shell 6a is formed as a communication hole 9c in the flange portion 9b in this embodiment. In addition, a fitting hole 9d for fitting and positioning a part of the thrust bearing 13 disposed between the flange portion 9b and the stator 15 is formed on the radially inner side of the communication hole 9c. . In addition, if the rigidity of the flange portion 9b is insufficient, uneven wear of the thrust bearing 13 occurs. Therefore, it is desirable to set the thickness of the flange portion 9b to a value that provides sufficient rigidity.

  According to the present invention, since the flange portion 9b formed on the turbine hub 9 and the turbine shell 6a are coupled via the rivet 22, the coupling strength is high. Therefore, even if the transmission torque is high, it can be dealt with. Further, since they are connected by the rivet 22, no slip occurs between the turbine shell 6a and the turbine hub 9, and the frictional resistance between the two is increased by increasing the plate thickness as in the case of being press-fitted and connected. Therefore, it is not necessary to prevent slippage between the two, so that the thickness of the turbine shell 6a can be reduced.

  Since other configurations and operations are the same as those of the first embodiment, description thereof is omitted.

  Although the first to third embodiments have described the case where the fluid torque transmission device is a torque converter having a stator, a fluid coupling not having a stator may be used.

Sectional drawing of a torque converter (Embodiment 1). The front view of a turbine shell (embodiment 1). Sectional drawing of a torque converter (Embodiment 2). Sectional drawing of a torque converter (Embodiment 3).

Explanation of symbols

1 ... Torque converter (fluid torque transmission device)
DESCRIPTION OF SYMBOLS 2 ... Front cover 3 ... Pump impeller 3a ... Impeller shell 6 ... Turbine runner 6a ... Turbine shell 8 ... Torque transmission part 9 ... Turbine hub 9a ... Caulking part 9b ... Flange part 11 ... Driven claw 12 ... Housing part 19 ... Lock-up piston 21 ... Hold plate 22 ... Rivet 24 ... Spring

Claims (3)

  1. A front cover connected to the crankshaft of the engine, a pump impeller arranged coaxially with the front cover and forming a fluid chamber between the front cover, and coaxially arranged inside the fluid chamber and facing the pump impeller A turbine runner that constitutes a torque transmission portion on the outer periphery of the portion, a turbine hub that is coupled to an axial center position of the turbine runner and is splined to an input shaft of the transmission;
    A lock-up piston that is coaxially disposed between the turbine runner and the front cover and is rotated by being pressed against an inner wall surface of the front cover, a spring that receives a compression load, and a spring coupled to the lock-up piston. A holding plate formed with a receiving portion for holding the spring along a direction and restricting the spring in a radial direction, an axial direction, and a circumferential direction; and the spring receiving portion formed integrally with the turbine runner and projecting toward the hold plate A fluid torque transmission device having a spring pressing portion that compresses the spring accommodated in the circumferential direction,
    The fluid pressure torque is characterized in that the spring pressing portion is formed by notching and bending a part of the turbine runner on a radially inner side than a portion constituting the torque transmitting portion in the turbine runner. Transmission device.
  2. The fluid torque transmission device according to claim 1,
    The hydrodynamic torque transmitting device, wherein the turbine hub is press-fitted into the turbine runner, and the turbine hub is coupled to the turbine runner by caulking the turbine hub.
  3. The fluid torque transmission device according to claim 1,
    A fluid torque transmission device, wherein a flange portion is integrally formed with the turbine hub, and the flange portion is coupled to the turbine runner via a rivet.
JP2006210824A 2006-08-02 2006-08-02 Fluid type torque transmitting apparatus Pending JP2008038951A (en)

Priority Applications (1)

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JP2006210824A JP2008038951A (en) 2006-08-02 2006-08-02 Fluid type torque transmitting apparatus

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015014358A (en) * 2013-06-04 2015-01-22 株式会社エクセディ Lock-up device of torque converter
WO2016134896A1 (en) * 2015-02-25 2016-09-01 Zf Friedrichshafen Ag Hydrodynamic coupling assembly having axial support for a turbine wheel
US9732835B2 (en) 2013-07-11 2017-08-15 Exedy Corporation Lockup device for torque converter
US9784352B2 (en) 2013-06-04 2017-10-10 Exedy Corporation Lock-up device for torque converter
US10030740B2 (en) 2013-06-04 2018-07-24 Exedy Corporation Lock-up device for torque converter
DE102009029496B4 (en) * 2009-09-16 2020-03-19 Zf Friedrichshafen Ag Hydrodynamic torque converter

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000002312A (en) * 1998-05-06 2000-01-07 Luk Getriebe Syst Gmbh Power transmission device
JP2001295912A (en) * 2000-04-14 2001-10-26 Exedy Corp Lockup damper for torque converter
WO2002036990A1 (en) * 2000-11-02 2002-05-10 Valeo Hydrokinetic coupling apparatus, in particular for motor vehicle
JP2003278881A (en) * 2002-03-25 2003-10-02 Aisin Seiki Co Ltd Torque converter
JP2005023945A (en) * 2003-06-30 2005-01-27 Valeo Unisia Transmission Kk Torque converter
JP2005061532A (en) * 2003-08-13 2005-03-10 Valeo Unisia Transmission Kk Torque converter
JP2005155821A (en) * 2003-11-27 2005-06-16 Honda Motor Co Ltd Hydraulic power transmission
JP2006064065A (en) * 2004-08-26 2006-03-09 Exedy Corp Hydraulic torque transmitting device

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000002312A (en) * 1998-05-06 2000-01-07 Luk Getriebe Syst Gmbh Power transmission device
JP2001295912A (en) * 2000-04-14 2001-10-26 Exedy Corp Lockup damper for torque converter
WO2002036990A1 (en) * 2000-11-02 2002-05-10 Valeo Hydrokinetic coupling apparatus, in particular for motor vehicle
JP2004513304A (en) * 2000-11-02 2004-04-30 ヴァレオValeo Hydrodynamic coupling device for motor vehicles.
JP2003278881A (en) * 2002-03-25 2003-10-02 Aisin Seiki Co Ltd Torque converter
JP2005023945A (en) * 2003-06-30 2005-01-27 Valeo Unisia Transmission Kk Torque converter
JP2005061532A (en) * 2003-08-13 2005-03-10 Valeo Unisia Transmission Kk Torque converter
JP2005155821A (en) * 2003-11-27 2005-06-16 Honda Motor Co Ltd Hydraulic power transmission
JP2006064065A (en) * 2004-08-26 2006-03-09 Exedy Corp Hydraulic torque transmitting device

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009029496B4 (en) * 2009-09-16 2020-03-19 Zf Friedrichshafen Ag Hydrodynamic torque converter
JP2015014358A (en) * 2013-06-04 2015-01-22 株式会社エクセディ Lock-up device of torque converter
US9784352B2 (en) 2013-06-04 2017-10-10 Exedy Corporation Lock-up device for torque converter
US10030740B2 (en) 2013-06-04 2018-07-24 Exedy Corporation Lock-up device for torque converter
US9732835B2 (en) 2013-07-11 2017-08-15 Exedy Corporation Lockup device for torque converter
WO2016134896A1 (en) * 2015-02-25 2016-09-01 Zf Friedrichshafen Ag Hydrodynamic coupling assembly having axial support for a turbine wheel

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