JP2006300134A - Fluid type torque transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent wearing of a turbine shell by a torsion spring in a fluid type torque transmission device in which the torsion spring of a lockup device is positioned in proximity to the turbine shell. <P>SOLUTION: A torque converter 1 comprises a front cover 2, an impeller 10, a turbine 11, and the lockup device 4. The turbine 11 is disposed oppositely to the impeller 10 in a fluid chamber, and comprises the turbine shell 20, a turbine blade 21 fixed to the impeller side face of the turbine shell 20, and a turbine hub 23 receiving a torque from the turbine shell 20. The lockup device 4 comprises a piston 41 connectable to the front cover 2, a flange plate 51 connecting the turbine shell 20 to the turbine hub 23, a drive plate 54 fixed to the piston 41, and the torsion spring 55 for elastically connecting both plates to each other in the rotating direction. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a fluid torque transmission device, and more particularly to a device having a lock-up device.

  Generally, a torque converter can smoothly accelerate and decelerate in order to transmit power by a fluid. However, fluid loss causes energy loss, resulting in poor fuel consumption.

  Therefore, some conventional torque converters are provided with a lockup device that mechanically connects the input-side front cover and the output-side turbine. The lockup device is disposed in a space between the front cover and the turbine. The lock-up device mainly comprises a disk-shaped piston that is pressed against the front cover, a driven plate attached to the rear side of the turbine, and a torsion spring that elastically connects the piston and the driven plate in the rotational direction. Has been. An annular friction member is bonded to the piston at a position facing the flat friction surface of the front cover.

  In the conventional lockup device, the operation of the piston is controlled by a change in hydraulic pressure in the fluid chamber. Specifically, hydraulic oil is supplied from an external hydraulic circuit between the piston and the front cover when the lockup connection is released. The hydraulic oil flows radially outward in the space between the front cover and the piston, and further flows into the torque converter body on the outer peripheral side. At the time of lockup connection, the hydraulic fluid in the space between the front cover and the piston is drained from the inner peripheral side, and as a result, the piston moves to the front cover side due to the hydraulic pressure difference. As a result, the friction member provided on the piston is pressed against the friction surface of the front cover. In this way, the torque of the front cover is transmitted to the turbine side via the lockup device.

  On the other hand, there is a demand for higher performance of the damper mechanism by using the vehicle from a low speed and increasing torque. In recent years, there has been known a torque converter that transmits a torque by a fluid only at the time of starting, and connects a lock-up device at, for example, a speed of 20 km or more. In the structure in which the lockup region is increased as described above, it is required to improve the performance of the torsion spring so that the torsional vibration can be sufficiently absorbed and damped with respect to the torque fluctuation from the engine. Specifically, it is required to improve the vibration absorption / damping characteristics against torsional vibration by increasing the diameter of the torsion spring.

  However, since the torsion spring is disposed between the front cover and the turbine in the axial direction, if the torsion spring is increased in size, the entire torque converter is increased in size.

Therefore, a structure in which the torsion spring is enlarged by arranging the torsion spring of the lockup device on the inner peripheral side of the fluid working chamber is known (see, for example, Patent Document 1).
Japanese Patent Laid-Open No. 4-83954

  In the conventional torque converter, the torsion spring is disposed close to the turbine shell. The torsion spring is supported by a part of the turbine shell. In such a structure, it is necessary to perform an abrasion resistance process such as induction hardening of the turbine shell, and it becomes difficult to braze the turbine blade to the turbine shell subjected to the abrasion resistance process.

  An object of the present invention is to solve the problem of supporting a torsion spring in a fluid torque transmission device in which a torsion spring of a lockup device is close to a turbine shell.

  The fluid torque transmission device according to a first aspect includes a front cover, an impeller, a turbine, and a lockup device. Torque from the engine is input to the front cover. The impeller is connected to the front cover to form a fluid chamber. The turbine is disposed opposite to the impeller in the fluid chamber, and includes a turbine shell, a turbine blade fixed to an impeller side surface of the turbine shell, and a turbine hub that receives torque from the turbine shell. The lock-up device is a device that is disposed between the front cover and the turbine and mechanically connects the two, a piston that can be connected to the front cover, a first plate member that connects the turbine shell and the turbine hub, And a second plate member fixed to the piston, and a torsion spring for elastically connecting the first plate member and the second plate member in the rotational direction.

  In this device, the turbine is driven by the working fluid flowing from the impeller when the piston of the lockup device is separated from the front cover. Torque is transmitted from the turbine shell of the turbine to the turbine hub via the first plate member. In a state where the piston of the lockup device is connected to the front cover, torque is transmitted from the piston to the second plate member, and further output to the first plate member and the turbine hub via the torsion spring. Since the first plate member, which is a member different from the turbine shell, supports the torsion spring, the wear resistance treatment of the turbine shell becomes unnecessary.

  According to a second aspect of the present invention, in the first aspect, the first plate member includes a pair of first plates that sandwich the inner peripheral portion of the turbine shell in the axial direction.

  According to a third aspect of the present invention, in the fluid torque transmission device according to the first or second aspect, the first plate member has support portions that support both ends in the rotational direction of the torsion spring.

  In the fluid type torque transmission device according to a fourth aspect, in any one of the first to third aspects, the turbine shell has a plurality of protrusions extending radially inward from the inner peripheral edge, and the first plate member is It is fixed to the protrusion.

  According to a fifth aspect of the present invention, the second plate member has a plurality of contact portions disposed between the circumferential directions of the plurality of projecting portions. The plurality of abutting portions and projecting portions constitute a rotation direction stopper between the turbine shell and the second plate member.

  According to a sixth aspect of the present invention, in the fluid type torque transmission device according to the fifth aspect, the second plate member fixes the pair of second plates disposed on both sides in the axial direction of the first plate member and the pair of second plates. And a plurality of fixing portions. Furthermore, the fixed part functions as a contact part.

  In the fluid type torque transmission device according to claim 7, in any one of claims 1 to 5, the second plate member has a pair of second plates arranged on both sides in the axial direction of the first plate member. Yes.

  According to an eighth aspect of the present invention, in the fluid type torque transmission device according to the seventh aspect, the second plate member further includes a fixing portion that fixes the pair of second plates to each other.

  According to a ninth aspect of the present invention, in the eighth aspect, the pair of second plate members are fixed to the piston so as to rotate integrally with the fixed portion.

  According to a tenth aspect of the present invention, in the fluid type torque transmission device according to the eighth or ninth aspect, the fixed portion is movable in a circumferential direction within a hole provided in the first plate member.

  In the fluid torque transmission device according to the present invention, since the first plate member, which is a member different from the turbine shell, supports the torsion spring, the wear resistance treatment of the turbine shell becomes unnecessary.

(1) Configuration of Torque Converter FIG. 1 shows a torque converter 1 in which an embodiment of the present invention is adopted. In FIG. 1, the torque converter 1 mainly includes a torus-shaped fluid working chamber 3 including a front cover 2 and three kinds of impellers (impeller 10, turbine 11, stator 12) arranged concentrically with the front cover 2. And a lockup device 4 disposed in a space between the front cover 2 and the turbine 11 in the axial direction. The outer periphery of the front cover 2 and the impeller shell 15 of the impeller 10 are fixed by welding, and both form a fluid chamber filled with hydraulic oil.

  The front cover 2 is a member to which torque is input from an engine crankshaft (not shown). The front cover 2 is mainly composed of a disc-shaped main body 5. A center boss 6 is fixed to the center of the main body 5. A plurality of nuts 7 are fixed to the outer peripheral engine side surface of the main body 5. An outer peripheral cylindrical portion 8 extending toward the axial transmission side is integrally formed on the outer peripheral portion of the main body 5.

  An annular and flat friction surface 70 is formed on the outer peripheral portion inside the main body 5 of the front cover 2. The friction surface 70 faces the axial transmission side.

  The fluid working chamber 3 is disposed on the axial transmission side in the fluid chamber. Thereby, the fluid chamber is divided into a fluid working chamber 3 and a space formed between the main body 5 of the front cover 2 and the turbine 11.

  The impeller 10 includes an impeller shell 15, a plurality of impeller blades 16 fixed to the inside of the impeller shell 15, and an impeller hub 18 fixed to the inner peripheral edge of the impeller shell 15. The impeller blade 16 is significantly shorter in the radial direction than the conventional one and is fixed to the outer peripheral side portion of the impeller shell 15.

  The turbine 11 is disposed to face the impeller 10 in the fluid chamber. The turbine 11 includes a turbine shell 20, a plurality of turbine blades 21 fixed to the turbine shell 20, and a turbine hub 23 fixed to the inner peripheral edge of the turbine shell 20. The turbine blade 21 is significantly shorter in the radial direction than the conventional one and is fixed to the outer peripheral side portion of the turbine shell 20. As shown in FIGS. 2, 4 and 5, a plurality of protrusions 20 a extending radially inward are formed on the inner peripheral edge of the turbine shell 20.

  As shown in FIGS. 1 and 12 to 14, the turbine hub 23 includes a cylindrical boss 23 a and a flange 23 b extending from the cylindrical boss 23 a to the outer peripheral side. A plurality of protrusion engaging portions 23d are formed on the surface of the flange 23b on the axial engine side. Further, a spline 23c is formed on the inner peripheral surface of the boss 23a. A main drive shaft 71 extending from the transmission side is engaged with the spline 23c. As a result, torque from the turbine hub 23 is output to the main drive shaft 71.

  The stator 12 is disposed between the inner periphery of the impeller 10 and the inner periphery of the turbine 11. The stator 12 is a mechanism for rectifying the hydraulic oil returning from the turbine 11 to the impeller 10 and realizing a torque amplifying function in the torque converter 1. Due to this torque amplification action, excellent acceleration performance can be obtained at the start. The stator 12 includes a stator carrier 27 and a plurality of stator blades 28 provided on the outer peripheral surface thereof.

  The stator carrier 27 is supported on a stator shaft (not shown) via a one-way clutch 30. The stator shaft is a cylindrical member disposed around the main drive shaft 71. The stator carrier 27 is a recess 27a that extends longer in the radial direction than in the prior art and is recessed on the entire axial engine side. Specifically, the radial intermediate portion of the surface of the concave portion 27 a of the stator carrier 27 is located on the axial transmission side with respect to the axial center position C <b> 1 of the fluid working chamber 3. By forming the concave portion 27 a facing the axial engine side in the stator carrier 27, a space for a damper mechanism 42 described later is secured on the inner peripheral side of the fluid working chamber 3.

  A flange plate 51 is provided between the turbine shell 20 and the turbine hub 23. As shown in FIGS. 2, 3, 4, 11, and 12, the flange plate 51 is a substantially disk-shaped member, and includes a pair of first plates 52 and 53. The first plates 52 and 53 have annular portions 52a and 53a and a plurality of projecting portions 52b and 53b extending radially outward therefrom. As shown in FIGS. 3 and 4, the annular portions 52a and 53a are in close contact with each other in the axial direction. The protrusions 52 b and 53 b are arranged corresponding to the protrusion 20 a of the turbine shell 20. Between the circumferential directions of the protrusions 52b and 53b, spaces 52e and 53e are provided for storing torsion springs (described later). As shown in FIG. 4, the protrusion 52 b and the protrusion 53 b sandwich the protrusion 20 a from both sides in the axial direction, and are fixed to each other by a rivet 60. In this way, the flange plate 51 is firmly fixed to the turbine shell 20 and operates integrally. As shown in FIG. 10, a hole 52 c that is elongated in the circumferential direction is formed in the annular portion 52 a of the first plate 52. Further, a plurality of protrusions 52d protruding inward in the radial direction are formed on the inner peripheral edge of the annular portion 52a. As shown in FIG. 1, a protrusion engaging portion 23d of the turbine hub 23 is fitted between the circumferential directions of the protrusions 52d. By this lug fitting, the flange plate 51 can move in the axial direction with respect to the turbine hub 23, but is integrated in the rotational direction.

  A first washer 32 is disposed between the main body 5 of the front cover 2 and the turbine hub 23 in the axial direction. The first washer 32 is formed with a plurality of grooves extending in the radial direction, and the hydraulic oil can flow through both sides of the first washer 32 in the radial direction. Between the axial direction of the inner peripheral part of the front cover 2, and the turbine hub 23, the 1st port 66 which can communicate hydraulic fluid in radial direction is formed. The first port 66 communicates an oil passage 72 provided in the main drive shaft 71 and a front chamber 81 between the front cover 2 and the piston 41.

  A second thrust bearing 33 is disposed between the turbine hub 23 and the one-way clutch 30. In the second thrust bearing 33, hydraulic oil can flow through both sides in the radial direction. Between the turbine hub 23 and the inner peripheral portion of the stator 12 (specifically, the innermost peripheral portion of the stator carrier 27), second ports 67 capable of communicating hydraulic oil are formed on both sides in the radial direction. That is, the second port 67 communicates the fluid passage between the main drive shaft 71 and the stator shaft and the fluid working chamber 3.

A third thrust bearing 34 is disposed between the stator carrier 27 and the inner peripheral portion of the impeller shell 15 in the axial direction. In the third thrust bearing 34, hydraulic oil can flow through both sides in the radial direction. Between the axial direction of the stator 12 (specifically, the stator carrier 27) and the impeller 10, a third port 68 capable of communicating hydraulic oil is formed on both sides in the radial direction. That is, the third port 68 communicates the fluid passage between the stator shaft and the impeller hub 18 and the fluid working chamber 3.
Each oil passage is connected to a hydraulic circuit (not shown), and hydraulic oil can be supplied to and discharged from the first to third ports 66 to 68 independently.

(2) Configuration of Lock-up Device The lock-up device 4 is disposed in an annular space formed between the main body 5 of the front cover 2 and the turbine 11 in the axial direction. This is a device for mechanically connecting / disconnecting the turbine 11. The lock-up device 4 has a piston function that operates due to a change in hydraulic pressure in the space, and a damper function that absorbs and attenuates torsional vibration in the rotational direction. The lockup device 4 is mainly composed of a piston 41 and a damper mechanism 42.

  As shown in FIGS. 1, 2, 3, 6 and 7, the piston 41 is a disk-shaped member disposed in the space in the vicinity of the main body 5 side of the front cover 2. The piston 41 divides the space into a front chamber 81 on the front cover 2 side and a rear chamber 82 on the turbine 11 side. The outer peripheral portion of the piston 41 is a friction coupling portion 49 disposed on the axial transmission side of the friction surface 70 of the front cover 2. The friction coupling portion 49 is an annular and flat plate-like portion, and an annular friction facing 46 is attached to the axial direction engine side.

  An inner peripheral cylindrical portion 47 is formed on the inner peripheral edge of the piston 41. The inner peripheral cylindrical portion 47 extends from the inner peripheral edge of the piston 41 to the axial transmission side. The inner peripheral surface of the inner peripheral cylindrical portion 47 is supported by the outer peripheral surface 26 of the turbine hub 23 so as to be movable in the axial direction and the rotational direction. The axial transmission side of the inner peripheral cylindrical portion 47 can contact the flange 23 b of the turbine hub 23. This restricts the movement of the piston 41 toward the axial transmission side. An annular groove is formed on the outer peripheral surface 26, and a seal ring 48 is disposed in the groove. The seal ring 48 is in contact with the inner peripheral surface of the inner peripheral cylindrical portion 47. The seal ring 48 seals both axial sides of the inner periphery of the piston 41.

The damper mechanism 42 is a mechanism for transmitting torque from the piston 41 to the turbine hub 23 and absorbing / damping torsional vibration. The damper mechanism 42 is disposed between the radial intermediate portion of the piston 41 and the inner peripheral portion of the turbine shell 20.
The damper mechanism 42 mainly includes a drive member 54 and a torsion spring 55.

  The drive member 54 is a drive member for inputting torque to the torsion spring 55, and further has a function of holding the torsion spring 55 on the piston 41. The drive member 54 is mainly composed of a pair of second plates 56 and 57 extending in an annular shape, and is disposed on both axial sides of the flange plate 51. The second plates 56 and 57 are generally disk-shaped as shown in FIGS. The inner peripheral parts of the second plates 56 and 57 are firmly fixed to each other by a plurality of rivets 58. That is, the second plates 56 and 57 are disposed apart from each other by a predetermined distance in the axial direction and rotate integrally. The axial direction between the inner peripheral portions of the second plates 56 and 57 is set to be larger than the axial thickness of the annular portions 52a and 53a of the first plates 52 and 53. Further, the second plate 56 is in contact with the inner peripheral portion of the piston 41 from the axial direction.

  The rivet 58 is disposed in holes 52c and 53c formed in the plates 52 and 53, and can move within a predetermined angle range in the circumferential direction. That is, the rivet 58 and the holes 52c and 53c are connected to the input side member (piston 41, second plates 55 and 56 of the drive member 54) and the output side member (first plates 52 and 53 of the flange plate 51) of the lockup device 4. ) To configure the rotation direction stopper. Further, the second plates 56 and 57 are firmly fixed to the piston 41 by rivets 58. The second plates 56 and 57 are formed with spring accommodating portions 56a and 57a each having a hole penetrating in the axial direction and a cut and raised portion, respectively. Further, outer circumferential portions 56b and 57b arranged apart from each other in the axial direction are formed between the circumferential directions of the spring accommodating portions 56a and 57a.

  The second plates 56 and 57 respectively have contact portions 56c and 57c that are disposed in contact with each other. The contact portions 56c and 57c are provided on the outermost peripheral portion, and are specifically disposed on the outer peripheral sides of the spring accommodating portions 56a and 57a, respectively. More specifically, the contact portions 56c and 57c are located at the centers of the spring housing portions 56a and 57a in the rotational direction, respectively. The contact portions 56 c and 57 c are fixed to each other by a rivet 59. The rivets 59 are disposed between the circumferential directions of the projecting portions 20a of the turbine shell 20, more specifically at the center in the circumferential direction, and can contact the rotational direction. That is, the rivet 59 and the protruding portion 20a (particularly the base portion) of the turbine shell 20 serve as a rotation direction stopper between the turbine 11 and the input side member (piston 41, second plates 56, 57) of the lockup device 4. It is composed.

  The torsion spring 55 is an elastic member for absorbing torsional vibration, and is composed of, for example, a coil spring. A plurality of torsion springs 55 are arranged side by side in the circumferential direction. The torsion spring 55 is disposed in the spring accommodating portions 56 a and 57 a of the drive member 54 and in the spring accommodating portion 52 e of the flange plate 51. The rotation direction end of the torsion spring 55 is supported by both ends (outer peripheral portions 56b and 57b) of the spring accommodating portions 56a and 57a in the rotation direction. Furthermore, the rotation direction end of the torsion spring 55 is supported by both ends (projections 52b) of the spring accommodating portion 52e in the rotation direction. The inner peripheral portion 41 a of the piston 41 is recessed so as to protrude toward the axial engine side in correspondence with the torsion spring 55.

  The torsion spring 55 is disposed on the inner peripheral side of the fluid working chamber 3. More precisely, the outer peripheral side edge of the torsion spring 55 is located on the inner peripheral side from the inner peripheral side edge (the outer peripheral surface of the stator carrier 27) of the fluid working chamber 3. Further, the torsion spring 55 partially enters the inner peripheral side of the fluid working chamber 3, and the axial transmission side edge of the torsion spring 55 exceeds the axial transmission side edge of the turbine blade 21 of the turbine 11 and It is close to the axial center position C1. As described above, the torsion spring 55 has a significantly larger coil diameter than the conventional one without increasing the axial dimension of the entire torque converter 1. Since the coil diameter of the torsion spring 55 can be increased in this way, it is easy to improve the performance of the torsion spring 55. As a result, it is possible to use the fluid torque transmission by the torus of the torque converter 1 only at the time of starting of the vehicle, and thereafter use it in a mechanical torque transmission state in which the lockup device 4 is connected.

  As described above, when the torus is downsized, it is considered that the torque transmission performance by the fluid is lowered. However, in a torque converter that performs torque transmission by a fluid only at the time of starting and connects a lock-up device at, for example, 20 km / h or more, a decrease in torque transmission performance by the fluid is not a problem.

(2) Operation Next, the operation will be described.
Torque from the crankshaft on the engine side is input to the front cover 2 via the flexible plate. As a result, the impeller 10 rotates and hydraulic oil flows from the impeller 10 to the turbine 11. The turbine 11 is rotated by the flow of the hydraulic oil, and the torque of the turbine 11 is output to the main drive shaft 71.

  When the main drive shaft 71 reaches a constant rotational speed, the hydraulic oil in the front chamber 81 is drained from the first port 66. As a result, the piston 41 is moved to the front cover 2 side. As a result, the friction facing 46 is pressed against the friction surface 70 of the front cover 2, and the torque of the front cover 2 is output to the lockup device 4. In the lockup device 4, torque is transmitted in the order of the piston 41, the drive member 54, the torsion spring 55, and the flange plate 51, and is output to the turbine hub 23.

(3) Manufacturing Method As shown in FIGS. 3 and 4, the turbine 11 and the lockup device 4 constitute one assembly assembled together. A method for manufacturing the turbine lockup device assembly will be described.
First, the flange plate 51 is fixed to the inner peripheral portion of the turbine shell 20 by the rivet 60. Subsequently, the torsion spring 55 is disposed between the rotation portions of the support portions 52 and 53 of the flange plate 51, and the second plates 56 and 57 of the drive member 54 are disposed on both axial sides of the flange plate 51 in this state. Then, the rivet 59 is caulked, and one end of the rivet 58 is further caulked to fix both. Finally, the remaining end of the rivet 58 is crimped to fix the piston 41 to the drive member 54.

(4) Effects of the Present Invention Since the flange plate 51, which is a separate member from the turbine shell 20, supports the torsion spring, the wear resistance treatment of the turbine shell 20 becomes unnecessary. Therefore, the turbine blade can be brazed to the turbine shell.

The drive member 54 and the flange plate 51 of the damper mechanism 42 are symmetrical in the axial direction. Specifically, the plates 52 and 53 are the same type, and the plate members 56 and 57 are the same type. In other words, the types of molds are reduced compared to the asymmetric structure. For this reason, production costs can be reduced.
Since the damper mechanism 42 includes the flange plate 51 and the drive member 54 that are adjacent to each other in the axial direction, the axial dimension of the damper mechanism 42 is shortened.

(5) Other Embodiments Modifications and the like are possible without departing from the spirit of the present invention, and the present invention is not limited to the above-described embodiments.

The longitudinal cross-sectional schematic of the torque converter as one Embodiment of this invention. The top view of a turbine lockup apparatus assembly. The longitudinal cross-sectional view of a turbine lockup apparatus assembly. The longitudinal cross-sectional view of a turbine lockup apparatus assembly. The top view of a turbine shell. The partial top view of a piston. The longitudinal cross-sectional view of a piston. The top view of the plate of a drive member. The longitudinal cross-sectional view of a drive member. The top view of a flange plate. The longitudinal cross-sectional view of a flange plate. The top view of a turbine hub. The longitudinal cross-sectional view of a turbine hub. The bottom view of a turbine hub.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Torque converter 4 Lockup apparatus 11 Turbine 20 Turbine shell 27 Stator carrier 41 Piston 42 Damper mechanism 51 Flange plate (1st plate member)
54 Drive member (second plate member)
55 Torsion spring 58 Rivet (fixed part)
59 Rivet (contact part, fixed part)

Claims (10)

A front cover that receives torque from the engine;
An impeller coupled to the front cover to form a fluid chamber;
A turbine disposed in the fluid chamber facing the impeller and having a turbine shell, a turbine blade fixed to an impeller side surface of the turbine shell, and a turbine hub receiving torque from the turbine shell;
A device disposed between the front cover and the turbine for mechanically connecting the two, a piston connectable to the front cover, and a first plate member for connecting the turbine shell and the turbine hub; A lockup device comprising: a second plate member fixed to the piston; and a torsion spring for elastically connecting the first plate member and the second plate member in a rotational direction;
A fluid-type torque transmission device.   2. The hydrodynamic torque transmitting device according to claim 1, wherein the first plate member includes a pair of first plates that sandwich an inner peripheral portion of the turbine shell in an axial direction.   The fluid torque transmission device according to claim 1, wherein the first plate member has support portions that support both ends of the torsion spring in the rotation direction.   The fluid according to claim 1, wherein the turbine shell has a plurality of protrusions extending radially inward from an inner peripheral edge, and the first plate member is fixed to the protrusion. Type torque transmission device. The second plate member has a plurality of abutting portions arranged between the plurality of protruding portions in the circumferential direction,
The hydrodynamic torque transmitting device according to claim 4, wherein the plurality of abutting portions and the protruding portion constitute a rotation direction stopper between the turbine shell and the second plate member. The second plate member has a pair of second plates disposed on both axial sides of the first plate member, and a plurality of fixing portions that fix the pair of second plates,
The fluid torque transmission device according to claim 5, wherein the fixing portion functions as the contact portion.   The fluid torque transmission device according to claim 1, wherein the second plate member has a pair of second plates disposed on both sides in the axial direction of the first plate member.   The fluid torque transmission device according to claim 7, wherein the second plate member further includes a fixing portion that fixes the pair of second plates to each other.   The hydrodynamic torque transmitting device according to claim 8, wherein the pair of second plate members are fixed to the piston so as to rotate integrally with the fixing portion.   The fluid torque transmission device according to claim 8 or 9, wherein the fixed portion is movable in a circumferential direction within a hole provided in the first plate member.

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