JP2006300135A - Torque converter - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve a problem of contact of a turbine on a stator in a torque converter in which the outer peripheral edge of the torsion spring of a lockup device is positioned on the inner peripheral side of the inner peripheral edge of a fluid operating chamber. <P>SOLUTION: In this torque converter 1, the lockup device 4 disposed between a front cover 2 and a turbine 11 is a device for mechanically connecting the front cover to the turbine, and comprises a piston 41 connectable to the front cover 2 and the torsion spring 52 for absorbing/damping torsional vibration. The outer peripheral edge of the torsion spring 52 is positioned on the inner peripheral side of the inner peripheral edge of the fluid operating chamber 3. A turbine shell 20 comprises a first portion 20a to which a turbine blade 21 is fixed and a second portion 20b disposed in proximity to the axial engine side of a stator carrier 27. The torque converter 1 further comprises a washer 76 disposed between the stator carrier 27 and the second portion 20b. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a torque converter, particularly one 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).
EUROPEAN PATENT APPLICATION 0070662A1

  However, in the conventional torque converter, in the torque converter operating region (when lockup is OFF), the turbine tends to move to the impeller by the hydraulic pressure in the fluid working chamber. Therefore, the problem that a turbine blade contacts a stator blade may arise. Moreover, in order to suppress the deformation | transformation of a turbine shell, it is possible to improve the intensity | strength by increasing the plate | board thickness of a turbine shell, In that case, the weight of a turbine will become too large.

  An object of the present invention is to solve a contact problem between a turbine and a stator in a torque converter in which an outer peripheral edge of a torsion spring of a lockup device is located on an inner peripheral side from an inner peripheral edge of a fluid working chamber.

  The torque converter according to a first aspect includes a front cover, an impeller, a turbine, a stator, 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 and a turbine blade fixed to an impeller side surface of the turbine shell. The stator is a member that is disposed between the inner peripheral portion of the impeller and the inner peripheral portion of the turbine and constitutes a fluid working chamber together with the impeller and the turbine, and is provided on the outer peripheral surface of the annular stator carrier and the stator carrier. And a stator blade. The lock-up device is a device that is disposed between the front cover and the turbine to mechanically connect the two, a piston that can be connected to the front cover, and a torsion spring that absorbs and attenuates torsional vibration. And have. The outer peripheral edge of the torsion spring is located on the inner peripheral side from the inner peripheral edge of the fluid working chamber. The turbine shell has a first portion to which the turbine blade is fixed, and a second portion that is arranged close to the axial engine side of the stator carrier. The torque converter further includes an axial load support member disposed between the stator carrier and the second portion.

  In this torque converter, when the speed ratio during operation of the torque converter is small, the turbine moves so as to approach the impeller, but the second portion of the turbine shell is supported by the stator carrier via the axial load support member. For this reason, even if weight reduction is realized by reducing the plate thickness of the turbine shell, it is difficult for the turbine blade to contact the stator blade.

  According to a second aspect of the present invention, in the torque converter according to the first aspect, the axial load supporting member secures a gap in the axial direction with respect to at least one of the stator carrier and the second portion in a state where the speed ratio is large. . Therefore, it is difficult for the turbine shell and the stator carrier to slide.

  According to a third aspect of the present invention, in the torque converter according to the second aspect, the axial load supporting member is prevented from rotating on either the stator carrier or the second portion. Therefore, the frictional resistance is stabilized when the stator and the turbine rotate relative to each other and the axial load support member slides.

  According to a fourth aspect of the present invention, in the torque converter according to the second or third aspect, the axial load supporting member is held on the stator carrier or the second portion so as not to fall off in the axial direction. Therefore, even when the second portion of the turbine shell is farthest from the stator carrier, the axial load support member does not fall off the held member.

  According to a fifth aspect of the present invention, in the torque converter according to any one of the second to fourth aspects, the stator carrier and the second portion each have an annular plane opposed in the axial direction, and the axial load support member is an annular shape. Washer shape. Therefore, the axial load support member can stably support the axial load.

  A torque converter according to a sixth aspect is the torque converter according to the fifth aspect, wherein the axial load supporting member has a disc-shaped portion and a claw portion extending in the axial direction from the disc-shaped portion and stopped by the second portion. is doing.

  According to a seventh aspect of the present invention, in the torque converter according to the sixth aspect, the tip of the claw has a contact portion that contacts the surface of the second portion on the side of the axial engine.

  In the torque converter according to claim 8, in any one of claims 2 to 7, the stator carrier has a recess at a position corresponding to the torsion spring on the surface on the axial engine side, and the axial load support member. Is arranged close to the recess.

  In a torque converter according to a ninth aspect, in the eighth aspect, the second portion of the turbine shell has a shape along the vicinity of the recess.

(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. The outer peripheral side portion (the portion where the turbine blade 21 is fixed) of the turbine shell 20 is defined as a first portion 20a, and the inner peripheral side portion (particularly, the portion curved along the concave portion 27a of the stator carrier 27) is the second portion. 20b.

  The turbine hub 23 has a cylindrical boss 23a and a flange 23b extending from the cylindrical boss 23a to the outer peripheral side. The flange 23 b is fixed to the inner peripheral portion of the turbine shell 20 by a plurality of rivets 24. 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, an intermediate portion in the radial direction of the surface of the concave portion 27 a of the stator carrier 27 is located on the axial transmission side from the axial center position of the fluid working chamber 3.

  Further, the second portion 20 b of the turbine shell 20 (the portion where the turbine blade 21 is not fixed) is curved in the axial direction along the stator carrier 27, and the radial intermediate portion thereof is the center in the axial direction of the fluid working chamber 3. Since the axial position is located on the transmission side from the position C1, the axial dimension of the inner peripheral portion of the torque converter 1 can be sufficiently shortened.

  As described above, the stator carrier 27 and the turbine shell 20 are largely curved toward the axial transmission side to form a recess facing the axial engine side, thereby corresponding to the inner peripheral side of the fluid working chamber 3, particularly the turbine 11. A space for a later-described damper mechanism 42 is secured on the inner peripheral side of the portion.

  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 the lockup device The lockup device 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, and mechanically connects the front cover 2 and the turbine 11 by a change in hydraulic pressure in the space. It is a device for connecting / disconnecting to / from. 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. The piston 41 is a disk-like 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. More specifically, the damper mechanism 42 is disposed in an annular space corresponding to the concave portion of the second portion 20 b of the turbine shell 20.

  The damper mechanism 42 mainly includes a drive member 50, a driven member 51, and a torsion spring 52.

  The drive member 50 is a drive member for inputting torque to the torsion spring 52 and further has a function of holding the torsion spring 52 on the piston 41. The drive member 50 is a pair of plate members 54 and 55 extending in an annular shape, and is fixed to the surface of the piston 41 on the axial transmission side. The outer peripheral portions of the plate members 54 and 55 are bent to the axial engine side and are fixed to the piston 41 by rivets 56. The plate members 54 and 55 are formed with spring accommodating portions 54a and 55a each including a hole penetrating in the axial direction and a cut-and-raised portion.

  The torsion spring 52 is an elastic member for absorbing torsional vibration, and is composed of, for example, a coil spring. A plurality of torsion springs 52 are arranged side by side in the circumferential direction. The torsion spring 52 is disposed in the spring accommodating portions 54 a and 55 a of the drive member 50.

  The driven member 51 is a member for outputting torque from the torsion spring 52, and is disposed between the axial directions of the plate members 54 and 55. The driven member 51 has a window hole 51a at a position corresponding to the spring accommodating portions 54a and 55a. The inner peripheral edge of the driven member 51 has inner peripheral teeth 51 b that engage with outer peripheral teeth 23 d formed at the tip of the flange 23 b of the turbine hub 23. Accordingly, the driven member 51 is engaged with the turbine hub 23 so as to be movable in the axial direction but not relatively rotatable.

  The torsion spring 52 is disposed on the inner peripheral side of the fluid working chamber 3. More precisely, the outer peripheral side edge of the torsion spring 52 is located on the inner peripheral side of the inner peripheral side edge (the outer peripheral surface of the stator carrier 27) of the fluid working chamber 3. Further, a part of the torsion spring 52 enters the inner peripheral side of the fluid working chamber 3, and the axial transmission side edge of the torsion spring 52 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. Further, since the driven member 51 is arranged in an annular shape corresponding to the torsion spring 52, the damper mechanism 42 is downsized in the radial direction.

  As described above, the coil diameter of the torsion spring 52 is significantly larger than that of the conventional one without increasing the axial dimension of the entire torque converter 1. Since the coil diameter of the torsion spring 52 can be increased in this way, it is easy to improve the performance of the torsion spring 52. 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.

(3) Configuration of Axial Load Support Mechanism Next, the axial load support mechanism 75 will be described with reference to FIGS. 2 and 3. The axial load support mechanism 75 is a mechanism that supports a load generated between the turbine 11 and the stator 12 when they approach each other. The axial load support mechanism 75 is disposed between the second portion 20 b of the turbine shell 20 of the turbine 11 and the stator carrier 27. The axial load support mechanism 75 is mainly composed of a single washer 76. The washer 76 is a flat annular and disk-shaped member, and is made of, for example, a copper alloy or a resin. The washer 76 is attached to the second portion 20 b of the turbine shell 20, and a slight gap can be secured in the axial direction with respect to the stator carrier 27. The disc-shaped main body 76a of the washer 76 is in close contact with the annular flat surface 20d (surface perpendicular to the axis) on the axial transmission side of the second portion 20b. An annular flat surface 27b is formed at a position corresponding to the washer 76 in the concave portion 27a of the stator carrier 27, and a slight gap is secured between the washer 76 and the annular flat surface 27b. A plurality of protrusions 76b extending toward the axial direction engine are formed on the outer peripheral edge of the disc-shaped main body 76a. The protrusion 76b extends through the hole 20c formed in the second portion 20b, and the circumferential ends are in contact with each other and are prevented from rotating. Further, the outer peripheral side surface of the protrusion 76b is close to or in contact with the outer peripheral side surface (the surface facing the inner peripheral side) of the hole 20c, and as a result, the washer 76 is positioned in the radial direction with respect to the second portion 20b. Further, an abutting portion 76c extending radially outward from the tip of the main body portion of the protrusion 76b is formed. The contact portion 76c is in contact with the axial engine side surface of the second portion 20b. As described above, the washer 76 is immovable in the axial direction with respect to the second portion 20b.

(4) 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. In the initial stage of operation of the torque converter (when the rotational speed difference between the impeller 10 and the turbine 11 is large), the turbine 11 is moved to the axial transmission side, that is, to the impeller 10 side by the hydraulic pressure in the fluid working chamber 3. Then, in the axial load support mechanism 75, the washer 76 comes into contact with the annular flat surface 27b of the stator carrier 27, and the movement of the turbine 11 is stopped. From the above, the turbine blade 21 is unlikely to interfere with the stator blade 28. In particular, since it is not necessary to increase the plate thickness of the turbine shell 20, an increase in the weight of the turbine 11 can be suppressed.

  When the speed ratio of the torque converter 1 increases, the turbine 11 eventually moves to the axial direction engine side. Therefore, in the axial load support mechanism 75, the washer 76 is separated from the stator carrier 27 as shown in FIGS. 2 and 3.

  Further, 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 50, the torsion spring 52, and the driven member 51, and is output to the turbine hub 23.

(5) Effects of the Present Invention In this torque converter, when the torque converter is operated, the turbine 11 moves so as to approach the impeller 10, but the second portion 20 b of the turbine shell 20 is supported by the stator carrier 27 via the washer 76. The For this reason, even if the plate thickness of the turbine shell 20 is reduced to achieve weight reduction, the turbine blade 21 is unlikely to contact the stator blade 28.

  The washer 76 secures a gap in the axial direction with respect to the stator carrier 27 when the speed ratio increases. That is, in the high speed ratio state (for example, the lockup operation state), the turbine shell 20 and the stator carrier 27 are difficult to slide.

  Since the washer 76 is prevented from rotating around the second portion 20b, the frictional resistance is stabilized when the stator 12 and the turbine 11 rotate relative to each other and the washer 76 slides on the annular flat surface 27b.

  Since the washer 76 is held in the second portion 20b so as not to fall off in the axial direction, the washer 76 does not fall off from the second portion 20b even when the second portion 20b of the turbine shell 20 is farthest from the stator carrier 27.

Since the stator carrier 27 and the second portion 20b have annular planes 27b and 20d that face each other in the axial direction, and the axial load support member has an annular washer shape, the washer 76 carries an axial load. Supports stably.
(6) 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 washer may be secured to the turbine blade by other methods. For example, it may be fixed by welding or the like.

  The washer may be fixed to the stator carrier side. For example, it can be integrally formed with the stator carrier.

  Instead of the washer, a thrust washer composed of a plurality of rolling elements may be used.

The longitudinal cross-sectional schematic of the torque converter as one Embodiment of this invention. The longitudinal cross-sectional schematic of an axial direction load support mechanism. The longitudinal cross-sectional schematic of an axial direction load support mechanism.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Torque converter 4 Lockup apparatus 11 Turbine 20 Turbine shell 20b 2nd part 27 Stator carrier 41 Piston 42 Damper mechanism 75 Axial load support mechanism 76 Washer

Claims (9)

A front cover to which torque from the engine is input,
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 and a turbine blade fixed to an impeller side surface of the turbine shell;
A member that is disposed between the inner peripheral portion of the impeller and the inner peripheral portion of the turbine and forms a fluid working chamber together with the impeller and the turbine, and is provided on the outer peripheral surface of the annular stator carrier and the stator carrier A stator having a stator blade formed,
A device that is disposed between the front cover and the turbine and mechanically connects the two, and includes a piston that can be connected to the front cover and a torsion spring that absorbs and attenuates torsional vibration. A lockup device having
The outer peripheral edge of the torsion spring is located on the inner peripheral side from the inner peripheral edge of the fluid working chamber,
The turbine shell has a first portion to which the turbine blade is fixed, and a second portion that is disposed close to the axial engine side of the stator carrier,
An axial load support member disposed between the stator carrier and the second portion;
Torque converter.   The torque converter according to claim 1, wherein the axial load support member secures a gap in the axial direction with respect to at least one of the stator carrier and the second portion in a state where the speed ratio is large.   3. The torque converter according to claim 2, wherein the axial load support member is prevented from rotating on either the stator carrier or the second portion.   4. The torque converter according to claim 2, wherein the axial load support member is held on one of the stator carrier and the second portion so as not to fall off in the axial direction. 5. The stator carrier and the second part each have an annular plane opposed in the axial direction;
The torque converter according to any one of claims 2 to 4, wherein the axial load support member has an annular washer shape.   6. The torque converter according to claim 5, wherein the axial load support member includes a disk-shaped portion and a claw portion that extends in the axial direction from the disk-shaped portion and is prevented from rotating around the second portion. .   The torque converter according to claim 6, wherein a tip of the claw portion has a contact portion that contacts the surface of the second portion on the axial direction engine side. The stator carrier has a recess at a position corresponding to the torsion spring on the surface on the axial engine side,
The axial load support member is disposed proximate to the recess,
The torque converter in any one of Claims 2-7.   The torque converter according to claim 8, wherein the second portion of the turbine shell has a shape along the vicinity of the recess.

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