JP2006105278A - Fluid type torque transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To facilitate management or the like of a turbine and a lock-up device in a fluid type torque transmission device. <P>SOLUTION: A torque converter 1 is provided with a front cover 2, an impeller 10, the turbine 11, and the lock-up device 4. The impeller 10 is fixed to the front cover 2 to form a fluid chamber. The turbine 11 is arranged in the fluid chamber so as to face the impeller 10. The lock-up device 4 is arranged between the front cover 2 and the turbine 11, and it is a device for mechanically outputting torque from the front cover 2. The turbine 11 has a turbine shell 20, and a plurality of turbine blades 21 fixed to the turbine shell 20. The lock-up device 4 has movable piston 41 which can be frictionally connected to the front cover 2. The piston 41 can not relatively turn with respect to the turbine shell 20. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a fluid torque transmission device, and more particularly to a fluid torque transmission device having a lock-up device that enables mechanical connection by movement of a piston.

  The torque converter is a device that has a torus (impeller, turbine, stator) composed of three types of impellers, and transmits power by a fluid inside the torus.

In the torque converter, a lockup device is provided in a space between the front cover and the torus. The lock-up device is a device for mechanically transmitting the torque of the front cover to the transmission side. The lockup device includes a clutch coupling portion and a damper mechanism. The clutch connecting portion is connected to or released from the front cover by a change in hydraulic pressure in the torque converter. Specifically, the clutch coupling part is composed of a front cover and a piston. The piston can move due to a change in hydraulic pressure in the fluid chamber, and moves toward and away from the piston. The damper mechanism is composed of a plurality of torsion springs, for example. The torsion spring has a function of absorbing and attenuating vibration in the torsional direction in a state where the lock-up device is connected (see, for example, Patent Document 1).
Japanese Patent Laid-Open No. 10-47453

  In the conventional lockup device, a retaining plate is fixed to the piston. The retaining plate is a member for holding the torsion spring on the piston. A driven plate is fixed to the turbine. The driven plate has claw portions that engage with both ends of the torsion spring in the circumferential direction. The claw portion is inserted into the elastic member from the axial direction and can be detached in the axial direction.

  In this way, the piston and the torsion spring constitute one assembly, which is a separate component from the turbine. For this reason, the turbine and the lock-up device usually need to be managed and transported separately and finally assembled to each other.

  An object of the present invention is to facilitate management and the like of a turbine and a lockup device in a fluid torque transmission device.

  The fluid torque transmission device according to a first aspect includes a front cover, an impeller, a turbine, and a lockup device. The impeller is fixed to the front cover to form a fluid chamber. The turbine is disposed in the fluid chamber and is opposed to the impeller. The lockup device is a device that is disposed between the front cover and the turbine and mechanically outputs torque from the front cover. The turbine has a turbine shell and a plurality of turbine blades fixed to the turbine shell. The lockup device has a piston that is movable and frictionally connectable to the front cover. The piston is non-rotatable relative to the turbine shell.

  In this fluid torque transmission device, since the piston is fixed to the turbine shell, management of the turbine and the piston is facilitated. In addition, for example, since the rigidity of the turbine shell and the damper mechanism is in series, the same effect as that of using a damper having a lower rigidity can be expected from the entire automatic transmission configured by the torque converter and the transmission. it can.

  According to a second aspect of the present invention, the piston is firmly fixed to the turbine shell.

  In this fluid torque transmission device, the piston is firmly fixed to the turbine shell, so that they are not separated from each other.

  According to a third aspect of the present invention, the fluid torque transmission device according to the second aspect further includes a plurality of fixing members for fixing the piston to the turbine shell.

  In this fluid type torque transmitting device, since the piston is fixed to the turbine by a plurality of fixing members, both are securely fixed.

  According to a fourth aspect of the present invention, in the fluid torque transmission device according to the second or third aspect, the turbine shell has a plurality of circumferentially formed inner circumferential portions and a connecting portion to which the piston is fixed.

  According to a fifth aspect of the present invention, the lockup device has an elastic member that is compressed in the rotational direction. The turbine shell includes a plurality of support portions that are alternately formed in the rotation direction with the plurality of connection portions and support the elastic member in the axial direction.

  In this fluid torque transmission device, the elastic member is supported in the axial direction by the support portion of the turbine shell, so the number of parts does not increase.

  In the fluid type torque transmission device according to claim 6, in claim 3, the lock-up device includes an input member, an output member, and an elastic member for elastically connecting the input member and the output member in the rotation direction. have. The plurality of fixing members can drive the input member in the rotational direction.

  In this fluid torque transmission device, the number of parts is reduced because the fixing member also has a function of driving the input member.

  The turbine-piston assembly according to claim 7 includes a front cover, an impeller fixed to the front cover and forming a fluid chamber, a turbine shell and a turbine blade disposed in the fluid chamber and facing the impeller. The present invention is used for a fluid torque transmission device including a turbine and a lockup device that is disposed between the front cover and the turbine and mechanically outputs torque from the front cover. The turbine / piston assembly includes a turbine, a piston, and a damper mechanism. The piston is a member that can be frictionally connected to the front cover and cannot rotate relative to the turbine. The damper mechanism is held by the turbine and the piston.

  In this turbine / piston assembly, since the piston is fixed to the turbine shell, it is easy to manage the turbine and the piston. In addition, for example, since the rigidity of the turbine shell and the damper mechanism is in series, the same effect as that of using a damper having a lower rigidity can be expected from the entire automatic transmission configured by the torque converter and the transmission. it can.

  In a turbine piston assembly according to an eighth aspect, in the seventh aspect, the piston is firmly fixed to the turbine shell.

  In this turbine / piston assembly, since the piston is firmly fixed to the turbine shell, they are not separated from each other.

  According to a ninth aspect of the present invention, the turbine-piston assembly according to the eighth aspect further comprises a plurality of fixing members for fixing the piston to the turbine shell.

  In this turbine / piston assembly, since the piston is fixed to the turbine by a plurality of fixing members, the both are securely fixed.

  A turbine-piston assembly according to a tenth aspect of the present invention is the turbine-piston assembly according to the eighth or ninth aspect, wherein a plurality of turbine shells are formed in a circumferential direction on the inner peripheral portion and have a connecting portion to which the piston is fixed.

  In a turbine-piston assembly according to an eleventh aspect, in the ninth aspect, the damper mechanism has a plurality of elastic members. The turbine shell includes a plurality of support portions that are alternately formed in the rotation direction with the plurality of connection portions and support the elastic member in the axial direction.

  In this turbine / piston assembly, since the elastic member is supported in the axial direction by the support portion of the turbine shell, the number of parts does not increase.

  The turbine-piston assembly according to claim 12, wherein the damper mechanism includes an input member, an output member, and a plurality of elastic members for elastically connecting the input member and the output member in the rotation direction. And have. The plurality of fixing members can drive the input member in the rotational direction.

  In this turbine / piston assembly, since the fixing member also has a function of driving the input member, the number of parts is reduced.

  In the fluid torque transmission device of the present invention, since the piston is fixed to the turbine shell, management of the turbine and the lockup device and the like are facilitated. In addition, for example, since the rigidity of the turbine shell and the damper mechanism is in series, the same effect as that of using a damper having a lower rigidity can be expected from the entire automatic transmission configured by the torque converter and the transmission. it can.

1. First Embodiment (1) Configuration 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 operation unit 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 end surface of the main body 5. An outer peripheral cylindrical portion 8 extending to the transmission side is integrally formed on the outer peripheral portion of the main body 5.

  An annular and flat friction surface 73 is formed on the outer peripheral portion inside the main body 5 of the front cover 2. The friction surface 73 faces the axial transmission side.

  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 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 connected to an inner peripheral edge of the turbine shell 20 by a damper mechanism 42 described later.

  The turbine hub 23 has a cylindrical boss 23a and a flange 23b extending from the cylindrical boss 23a to the outer peripheral side. Splines 23c are formed on the inner peripheral surface of the boss 23a. A shaft (not shown) extending from the transmission side is engaged with the spline 23c. Thereby, the torque from the turbine hub 23 is output to a transmission input shaft (not shown). The outer peripheral surface 26 on the axial direction engine side of the boss 23a extends straight in the axial direction in cross section. On the outer peripheral edge of the flange 23b of the turbine hub 23, a plurality of engaging portions 23d arranged at intervals in the circumferential direction are provided. The engaging portion 23d is a claw-like protrusion that extends as if bent toward the axial engine side.

  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 at the time of start can be obtained. 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 by a fixed shaft (not shown) via a one-way clutch 30.

  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. 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. A third thrust bearing 34 is disposed between the stator carrier 27 and the impeller hub 18 in the axial direction. In the third thrust bearing 34, hydraulic oil can flow through both sides in the radial direction.

  In this embodiment, the first oil passage of the hydraulic circuit is connected between the impeller hub 18 and the stator 12 in the axial direction, and the second oil passage of the hydraulic circuit is connected between the stator 12 and the turbine hub 23 in the axial direction. The third oil passage of the hydraulic circuit is connected between the turbine hub 23 and the inner peripheral portion of the front cover 2. The first oil passage and the second oil passage are usually connected to a common hydraulic circuit, and both supply hydraulic fluid to the fluid operating section 3 or discharge hydraulic oil from the fluid operating section 3. The third oil passage is formed inside a shaft (not shown), and hydraulic oil can be supplied or discharged between the front cover 2 and the turbine hub 23.

  The lockup device 4 is disposed in an annular space 40 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. The lock-up device 4 has a piston function that is activated by a change in hydraulic pressure in the space 40 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 40 in the vicinity of the main body 5 side of the front cover 2. The piston 41 divides the space into a first space 43 on the front cover 2 side and a second space 44 on the turbine 11 side. An outer peripheral portion of the piston 41 is a friction coupling portion 49 disposed on the axial transmission side of the friction surface 73 of the front cover 2. The friction coupling portion 49 is an annular and flat plate-like portion, and an annular friction member 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 arranged 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 50, a turbine hub 23 as a driven member, a torsion spring 52, a first plate 53, and a second plate 54. In FIG. 2, the arrow R1 is the rotational direction drive side (the rotational direction first side), and the arrow R2 is the rotational direction reverse drive side (the rotational direction second side).

  The drive member 50 is a drive member for inputting torque to the torsion spring 52, and includes a rivet 57 and a sleeve 58. The rivet 57 is a rod-like member extending in the axial direction, and fixes the inner peripheral portion of the piston 41 and the plurality of protruding portions 20 a arranged in the circumferential direction at the inner peripheral portion of the turbine shell 20 to each other. The projecting portion 20a of the turbine shell 20 is a portion connected to the piston 41, and the turbine shell 20 and the piston 41 can move in the circumferential direction and the axial direction in synchronization. A spring support 20b raised on the axial transmission side is formed between the circumferential portions of the protrusions 20a on the inner peripheral edge of the turbine shell 20. The sleeve 58 is a cylindrical member disposed around the main body of the rivet 57. The sleeve 58 is made of a material harder than the rivet 57 and is fixed to the piston 41 by, for example, projection welding. The sleeve 58 includes a cylindrical portion 58a and a flange portion 58b disposed on the axial engine side. The flange portion 58b extends in the radial direction from the tubular portion 58a.

  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 an annular space formed by the inner peripheral portion of the piston 41 and the spring support portion 20 b of the turbine shell 20. A concave portion 41 a that is recessed toward the axial direction engine side is formed in the inner peripheral portion of the piston 41, and supports the axial direction engine side of the torsion spring 52. The spring support portion 20 b is disposed corresponding to the torsion spring 52. Since the torsion spring 52 is supported in the axial direction by the spring support portion 20b of the turbine shell 20, the number of parts does not increase. The inner peripheral portion of the piston 41 and the spring support portion 20b of the turbine shell 20 only support both axial sides of the torsion spring 52, and do not have a portion for transmitting torque with the torsion spring 52.

  The first plate 53 and the second plate 54 are members for compressing the torsion spring 52 in the rotational direction by being driven by both when the drive member 50 and the turbine hub 23 rotate relative to each other. The drive member 50 drives the first plate 53 during the forward drive, and drives the second plate 54 during the reverse drive.

  The first plate 53 and the second plate 54 are plate-like members arranged so as to overlap in the axial direction. The first plate 53 is disposed on the axial transmission side, and the second plate 54 is disposed on the axial engine side. The first plate 53 and the second plate 54 are members having substantially the same shape and are symmetrically arranged in plan view. In particular, the first plate 53 and the second plate 54 are symmetrical with respect to the center line of the spring.

  As shown in FIGS. 5 and 6, the first plate 53 is mainly composed of an inner peripheral annular portion 53 a and a plurality of first support portions 53 b extending outward in the radial direction therefrom. Further, the first plate 53 further includes an outer peripheral side annular portion 53c that connects the radially outer ends of the first support portions 53b. The first support portion 53 b is a portion for supporting the rotational direction end surface of the torsion spring 52. The end surface 60 on the rotation direction R1 side of the first support portion 53b is arranged such that the radially outer end is shifted from the radially inner end toward the rotation direction R1. As shown in FIG. 6, a radially outer portion 60a of the end surface 60 and a part 53e of the inner peripheral surface of the outer peripheral side annular portion 53c continuous therefrom have a plate surface structure that is bent and extends in the axial direction. The plate surface portions (60a, 53e) extend toward the axial engine side. For this reason, the contact area of the contact portion between the torsion spring 52 and the first plate 53 is large. As described above, the torsion spring 52 and the first support portion 53b are not easily worn or damaged.

  As shown in FIGS. 7 and 8, the second plate 54 is mainly composed of an inner peripheral side annular portion 54 a and a plurality of second support portions 54 b extending radially outward therefrom. Further, the second plate 54 further includes an outer peripheral annular portion 54c that connects the radially outer ends of the second support portions 54b. The second support portion 54 b is a portion for supporting the rotational direction end surface of the torsion spring 52. The rotation direction R2 side end surface 66 of the second support portion 54b is arranged such that the outer side in the radial direction is shifted from the inner end in the radial direction toward the rotation direction R2. As shown in FIG. 8, a radially outer portion 66a of the end surface 66 and a part 54e of the inner peripheral surface of the outer peripheral side annular portion 54c continuous therefrom have a plate surface structure that is bent and extends in the axial direction. The plate surface portions (66a, 54e) extend toward the axial engine side. For this reason, the contact area of the contact portion between the torsion spring 52 and the second plate 54 is increased. As described above, the torsion spring 52 and the second support portion 54b are not easily worn or damaged.

  Both the outer circumferential side annular portion 53 c of the first plate 53 and the outer circumferential side annular portion 54 c of the second plate 54 extend while being inclined toward the axial engine side so as to follow the shape of the turbine shell 20. In other embodiments, the outer peripheral side annular portions of both plates may be linearly extended to the outer peripheral side.

  The shape of the first window hole 53d will be described. As shown in FIG. 5, the first window hole 53d is a notch-shaped portion punched in the axial direction. 53 d of 1st window holes are the spaces between the circumferential directions of each 1st support part 53b, and are further enclosed by the inner peripheral side annular part 53a and the outer peripheral side annular part 53c. An end surface on the rotation direction R1 side of the first window hole 53d is an end surface 61 on the rotation direction R2 side of the first support portion 53b, and an end surface on the rotation direction R2 side is an end surface 60 on the rotation direction R1 side of the first support portion 53b. On the inner peripheral surface of the first window hole 53d, the rotation direction R2 side portion is a notch or first recess 64 that is further recessed inward in the radial direction as compared with the rotation direction R1 side portion. The first concave portion 64 includes a stopper end surface 60b continuously extending from the radially outer portion 60a of the end surface 60 in the first support portion 53b, a curved shape portion 62 continuous therefrom, and a first end surface 63 continuous therefrom. It is configured. The first recess 64 extends further inward in the radial direction than the end surface 60 and the first end surface 63. The stopper end surface 60b is linearly continuous from the radially outer portion 60a and opposes the first end surface 63 in the circumferential direction (same radial position). The first end face 63 is disposed approximately at the center in the rotational direction in the first window hole 53d. In summary, the first window hole 53d is a portion that accommodates the torsion spring 52, and includes an end surface 60 facing the rotation direction R1, an end surface 61 facing the rotation direction R2 and supporting the drive member 50, and the rotation direction. The first end surface 63 that faces the R2 side and supports the engaging portion 23d is formed, and a first recess 64 is formed between the end surface 60 and the first end surface 63.

  The shape of the second window hole 54d will be described. As shown in FIG. 7, the second window hole 54d is a notch-shaped part punched in the axial direction. The second window hole 54d is a space between the circumferential directions of the second support portions 54b, and is further surrounded by an inner peripheral annular portion 54a and an outer peripheral annular portion 54c. An end surface on the rotation direction R2 side of the second window hole 54d is an end surface 67 on the rotation direction R1 side of the second support portion 54b, and an end surface on the rotation direction R1 side is an end surface 66 on the rotation direction R2 side of the second support portion 54b. On the inner peripheral surface of the second window hole 54d, the rotation direction R1 side portion is a notch or second recess 70 that is further recessed inward in the radial direction as compared with the rotation direction R2 side portion. The second recess 70 includes a stopper end surface 66b continuously extending from the radially outer portion 66a of the end surface 66 in the second support portion 54b, a curved shape portion 68 continuous therefrom, and a second end surface 69 continuous therefrom. It is configured. The second recess 70 extends further inward in the radial direction than the end surface 66 and the second end surface 69. The stopper end surface 66b is linearly continuous from the radially outer portion 66a and faces the second end surface 69 in the circumferential direction (same radial position). The second end surface 69 is disposed approximately at the center in the rotational direction in the second window hole 54d. In summary, the second window hole 54d is a part that accommodates the torsion spring 52, a part (66) that contacts the torsion spring 52, a part (67) that contacts the drive member 50 for driving, and The driven member is provided with a portion (69) with which the turbine hub 23 contacts.

  The relationship between the first window hole 53d of the first plate 53 and the second window hole 54d of the second plate 54 is as shown in FIG. Most of the first window hole 53d and the second window hole 54d overlap each other, but the first window hole 53d is shifted to the rotation direction R1 side with respect to the second window hole 54d. Therefore, the rotation direction R2 side end surface 61 of the first support portion 53b is separated from the rotation direction R2 side end surface 66 of the second support portion 54b (and therefore also from the rotation direction R1 side end surface of the torsion spring 52) toward the rotation direction R1. Are arranged. Further, the rotation direction R1 side end surface 67 of the second support portion 54b is separated from the rotation direction R1 side end surface 60 of the first support portion 53b (and therefore also from the rotation direction R2 side end surface of the torsion spring 52) toward the rotation direction R2. Are arranged. Therefore, the rotation direction first side end of the first window hole 53d and the second rotation direction second side end of the second window hole 54d on the rotation direction first side overlap each other. Further, the plate surface portions (60a, 53e) of the first window hole 53d are arranged so as to enter the second window hole 54d, and are movable in the rotation direction R1 side. The plate surface portions (66a, 54e) of the second window hole 54d are arranged so as to enter the first window hole 53d, and are movable in the rotation direction R1 side. Further, the first end face 63 and the second end face 69 are opposed to each other with a predetermined angle in the rotation direction.

  In the torsion spring 52, both ends of the first window hole 53d and the second window hole 54d overlapped with each other in the circumferential direction at the rotation direction R1 side end surface 60 of the first support portion 53b of the first plate 53 and the second plate 54. The second support portion 54b is supported in contact with or close to the end surface 66 on the rotation direction R2 side.

  The drive member 50 is in contact with the surface facing the rotational direction R2 side of the first plate 53 (specifically, the concave portion 61a of the end surface 61 on the rotational direction R2 side of the first support portion 53b) in the rotational direction. The second plate 54 is in contact with the surface facing the rotation direction R1 (specifically, the recess 67a of the end surface 67 on the rotation direction R1 side) in the rotation direction. The engaging portion 23d is in contact with the surface (specifically, the first end surface 63) facing the rotational direction R2 side of the first plate 53 in the rotational direction, but is the surface facing the R1 side (specifically, another surface). A clearance is secured in the rotational direction in the stopper end surface 60b of the first support portion 53b in the rotational direction R1 side end surface 60, and the second plate 54 faces the rotational direction R1 side (specifically, the first end portion 60b). 2 in the rotational direction but a surface facing the R2 side (specifically, a stopper end surface 66b of the rotational direction R2 side end surface 66 of another second support portion 54b) ensures a clearance in the rotational direction. is doing. A portion of the drive member 50 corresponding to the first plate 53 and the second plate 54 is a cylindrical portion 58 a of the sleeve 58.

  The turbine 11, the piston 41, and the damper mechanism 42 constitute a turbine / piston assembly 71. Since the piston 41 is fixed to the turbine shell 20 in the turbine / piston assembly 71, the management of the turbine 11 and the piston 41 is facilitated. Moreover, since the piston 41 is firmly fixed to the turbine shell 20, the two are not separated from each other. Furthermore, since the piston 41 is fixed to the turbine 11 by the plurality of drive members 50, both are securely fixed.

Since the drive member 50 has a function of fixing the piston 41 to the turbine shell 20 and a function of inputting torque to the first plate 53 or the second plate 54, the number of parts of the lockup device 4 is reduced. .
(3) Operation The clutch coupling operation will be described. The hydraulic oil in the space between the front cover 2 and the piston 41 is drained from the third oil passage. Thus, due to the hydraulic pressure difference, the piston 41 moves to the axial engine side, and the friction connecting portion 49 contacts the friction surface 73 of the front cover 2.

  In this state, torque from the piston 41 is transmitted from the drive member 50 to the turbine hub 23 through the first plate 53 or the second plate 54, the torsion spring 52, the second plate 54 or the first plate 53. .

  The operation during driving will be described. The drive member 50 is moved to the rotation direction R1 side with the turbine hub 23 fixed first. Then, the drive member 50 drives the first plate 53 in the rotation direction R1 side in a state where the drive member 50 is in contact with the recess 61a. At this time, the second plate 54 is prohibited from moving in the rotational direction R1 side by the engaging portion 23d of the turbine hub 23 in contact with the second end surface 69. Therefore, the torsion spring 52 is compressed in the rotational direction between the first support portion 53 b of the first plate 53 and the second support portion 54 b of the second plate 54. As the torsional angle increases, as shown in FIG. 11, the stopper end surface 60b of the end surface 60 on the rotation direction R1 side of the first support portion 53b contacts the engaging portion 23d from the rotation direction R2 side. As a result, the relative rotation of the first plate 53 and the second plate 54 stops.

  The operation during reverse driving will be described. With the turbine hub 23 fixed first, the drive member 50 is moved to the rotation direction R2 side. Then, the drive member 50 drives the second plate 54 in the rotational direction R2 side while being in contact with the recess 66a. At this time, the first plate 53 is prohibited from moving in the rotational direction R2 side by the engaging portion 23d of the turbine hub 23 in contact with the first end surface 63. Therefore, the torsion spring 52 is compressed in the rotational direction between the first support portion 53 b of the first plate 53 and the second support portion 54 b of the second plate 54. As the torsional angle increases, the stopper end surface 66b of the rotation direction R2 side end surface 66 of the second support portion 54b comes into contact with the engagement portion 23d from the rotation direction R1 side. As a result, the relative rotation of the first plate 53 and the second plate 54 stops.

  In any case, the first support portion 53b of the first plate 53 receives a load only from the rotation direction R1 side from the torsion spring 52, and the second support portion 54b of the second plate 54 from the rotation direction R2 side from the torsion spring 52. Only receive the load. As mentioned above, since the load which acts on the 1st support part 53b and the 2nd support part 54b is from one direction, not a double swing stress but a single swing stress generate | occur | produces. For this reason, the intensity | strength of the 1st support part 53b and the 2nd support part 54b can be reduced compared with the past. For example, the circumferential width of each support portion can be shortened, and the circumferential length of the torsion spring can be increased. In this case, the torsional characteristics can be widened and the rigidity can be reduced. Alternatively, it is possible to reduce the weight by reducing the thickness of each plate.

  The problem of the stress of the plate that functions as the input side member in the damper mechanism 42 will be described. Since the radial position of the drive member 50 corresponds to the first support portion 53b and the second support portion 54d, when the drive member 50 drives the first plate 53 or the second plate 54, Is compressed in the circumferential direction in the first support portion 53b (between the rotation direction R1 side end surface 60 and the rotation direction R2 side end surface 61), or in the second support portion 54d (in the rotation direction R1 side). Only a compressive force is generated in the circumferential direction (between the end face 67 and the end face 66 on the rotation direction R2 side). Therefore, stress concentration that damages the spring support portion hardly occurs. In this embodiment, the drive member 50 is at a radial position corresponding to the outer peripheral side portions of the first support portion 53b and the second support portion 54d, but may be further radially outward or radially inner than this. Preferably, the drive member 50 receives the radially outer portion 60a (the portion that receives the end surface of the spring) of the end surface 60 of the first support portion 53b and the radially outer portion 66a (the end surface of the spring) of the end surface 66 of the second support portion 54d. Part) is preferably at least partially overlapping the radial region, and more preferably within the radial region.

  The problem of the stress of the plate functioning as the output side member in the damper mechanism 42 will be described. For example, in the first plate 53, the load from the torsion spring 52 acts on the rotation direction R2 side with respect to the rotation direction R1 side end surface 60, and at the same time from the engagement portion 23d of the turbine hub 23 with respect to the first end surface 63. A load acts on the rotation direction R1 side. For this reason, it is conceivable that stress concentration occurs particularly in the portion of the first window hole 53d where the end surface 60 and the first end surface 63 are connected. When a load from the torsion spring 52 to the rotation direction R2 side acts on the end surface 60 of the first window hole 53d, a load from the turbine hub 23 to the rotation direction R1 side acts on the first end surface 63. For this reason, a force is exerted on the first plate 53 to push and spread between the end surface 60 and the first end surface 63. However, in the present invention, since the first recess 64 is formed, the end surface 60 (the portion where the load acts on the rotation direction R2 side) and the first end surface 63 (the portion where the load acts on the rotation direction R1 side). Even if a large load is applied to push the gap between the two, stress concentration is unlikely to occur at the connecting portion between the two.

  The above embodiment is merely an example of the present invention, and various modifications can be made without departing from the gist of the present invention. For example, the damper mechanism according to the present invention can be employed in a clutch disc assembly and a flywheel assembly.

BRIEF DESCRIPTION OF THE DRAWINGS The longitudinal cross-sectional schematic of the torque converter by which 1st Embodiment of this invention was employ | adopted. The partial top view of a damper mechanism. The longitudinal cross-sectional schematic of a damper mechanism. The longitudinal cross-sectional schematic of a damper mechanism. The top view of a 1st plate. It is VI-VI sectional drawing of FIG. 5, and sectional drawing of a 1st plate. The top view of the 2nd plate. It is VIII-VIII sectional drawing of FIG. 5, and sectional drawing of a 2nd plate. The top view of a turbine hub. It is XX sectional drawing of FIG. 9, and sectional drawing of a turbine hub. The figure which shows the maximum twist state at the time of a positive drive.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Torque converter 2 Front cover 4 Lockup apparatus 10 Impeller 11 Turbine 20 Turbine shell 20a Protrusion part (connection part)
20b Spring support (support)
21 Turbine blade 41 Piston 42 Damper mechanism 52 Torsion spring 53 First plate 54 Second plate 71 Turbine / piston assembly

Claims (12)

A front cover;
An impeller fixed to the front cover to form a fluid chamber;
A turbine disposed within the fluid chamber and disposed opposite the impeller;
A lockup device disposed between the front cover and the turbine for mechanically outputting torque from the front cover;
The turbine includes a turbine shell and a plurality of turbine blades fixed to the turbine shell,
The lockup device has a piston that can be frictionally connected to the front cover;
The piston is non-rotatable relative to the turbine shell;
Fluid torque transmission device.   The hydrodynamic torque transmitting device according to claim 1, wherein the piston is firmly fixed to the turbine shell.   The fluid torque transmission device according to claim 2, further comprising a plurality of fixing members that fix the piston to the turbine shell.   4. The fluid torque transmission device according to claim 2, wherein a plurality of the turbine shells are formed in a circumferential direction at an inner peripheral portion and have a connecting portion to which the piston is fixed. 5. The lock-up device has an elastic member that is compressed in the rotational direction,
The hydrodynamic torque transmitting device according to claim 4, wherein the turbine shell includes a plurality of support portions that are alternately formed in the rotation direction with the plurality of connection portions and support the elastic member in the axial direction. The lockup device includes an input member, an output member, and an elastic member for elastically connecting the input member and the output member in a rotation direction,
The fluid torque transmission device according to claim 3, wherein the plurality of fixing members can drive the drive member in a rotation direction. A front cover; an impeller fixed to the front cover to form a fluid chamber; a turbine having a turbine shell and a turbine blade disposed in the fluid chamber and opposed to the impeller; the front cover and the turbine; A fluid torque transmission device including a lock-up device that is disposed between the front cover and mechanically outputs torque from the front cover;
The turbine;
A piston that is frictionally connectable to the front cover and is not rotatable relative to the turbine;
A damper mechanism held by the turbine and the piston;
Turbine and piston assembly with   The turbine piston assembly of claim 7, wherein the piston is rigidly secured to the turbine shell.   The turbine and piston assembly according to claim 8, further comprising a plurality of fixing members for fixing the piston to the turbine shell.   10. The turbine / piston assembly according to claim 8, wherein a plurality of the turbine shells are formed in a circumferential direction at an inner peripheral portion and have a connecting portion to which the piston is fixed. The damper mechanism has a plurality of elastic members,
The turbine / piston assembly according to claim 10, wherein the turbine shell has a plurality of support portions that are alternately formed in the rotation direction with the plurality of connection portions and support the elastic member in the axial direction. The damper mechanism includes an input member, an output member, and a plurality of elastic members for elastically connecting the input member and the output member in a rotation direction,
The turbine piston assembly according to claim 9, wherein the plurality of fixing members are capable of driving the input member in a rotational direction.

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