JP2007113660A - Fluid type torque transmission device and lockup device used therefor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve responsiveness when operating a lockup device in the lockup device for a fluid type torque transmission device. <P>SOLUTION: This lockup device 5 has a clutch mechanism 6 and a damper mechanism 7. The clutch mechanism 6 has a lockup piston 61, a lockup hydraulic chamber 62, a lockup clutch plate 63, a lockup friction disc 64 and a lockup end plate 65. The lockup piston 61 can energize an inner peripheral part of the lockup clutch plate 63 in the axial direction, and an outer peripheral part of the lockup clutch plate 63 can frictionally engage with the lockup friction disc 64. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a fluid torque transmission device and a lockup device used therefor, and more particularly to a fluid torque transmission device such as a torque converter and a fluid coupling and a lockup device used therefor.

  A torque converter including a lockup device is known as a fluid torque transmission device. The torque converter is a device that has a torus (impeller, turbine, and stator) composed of three types of impellers and transmits torque via a fluid inside the torus. The impeller is fixed to a front cover as an input side rotating body. The turbine is disposed opposite the impeller in the fluid chamber. When the impeller rotates, hydraulic oil flows from the impeller to the turbine, and torque is output by rotating the turbine.

  The lockup device is disposed in a space between the turbine and the front cover, and is a mechanism for directly transmitting torque from the front cover to the turbine by mechanically connecting the front cover and the turbine. This type of lockup device has, for example, a clutch mechanism for mechanically connecting a front cover and a turbine (see, for example, Patent Documents 1 to 3).

The clutch mechanism described in Patent Documents 1 to 3 includes a piston, a hydraulic chamber, an end plate, and a friction disk. When pressure is supplied to the hydraulic chamber, the piston moves in the axial direction, and the friction disk is held between the piston and the end plate. As a result, torque is transmitted from the front cover to the turbine via the lockup device.
Japanese Patent Laid-Open No. 9-317848 JP 2000-2312 A JP 2000-110915 A

  However, in the lockup device described in Patent Document 1, since the friction disk is disposed on the outer peripheral side, the outer diameter of the piston is increased, and the piston is increased in size. Therefore, the response of the piston is lowered, and the response of the lockup device is lowered.

  Further, in the lockup device described in Patent Document 1, the clutch drum is in contact with the outer peripheral cylindrical portion of the front cover, and the friction disk is disposed in the dead zone at the corner portion of the front cover. For this reason, it is difficult for the working fluid to flow on a friction surface such as a piston or a friction disk disposed on the inner peripheral side of the clutch drum. Therefore, the cooling efficiency of the friction disk or the like by the working fluid is reduced, and the life of the friction disk or the like is shortened.

  Further, in the lockup devices described in Patent Documents 2 and 3, since the radius of the piston and the friction disk is reduced, the distance between the friction disk and the outer peripheral cylindrical portion of the front cover is increased. In this case, even if the working fluid discharged from the torus to the outer peripheral side flows on the outer peripheral side of the impeller and the front cover, the working fluid hardly flows around the friction disk. Therefore, similarly to Patent Document 1, the cooling efficiency of the friction disk or the like by the working fluid is reduced, and the life of the friction disk or the like is shortened.

  The subject of this invention is improving the responsiveness at the time of lockup apparatus operation | movement in the lockup apparatus for fluid type torque transmission apparatuses.

  Another object of the present invention is to improve the cooling efficiency of a friction disk in a lockup device for a fluid type torque transmission device.

  A lockup device for a fluid torque transmission device according to a first aspect is a device that is disposed between a front cover and a turbine and mechanically connects the front cover and the turbine. The lockup device includes a clutch mechanism and a damper mechanism. The clutch mechanism is a mechanism for mechanically connecting the front cover and the turbine by hydraulic pressure. The damper mechanism has a first damper mechanism coupled to the clutch mechanism, and a second damper mechanism disposed between the first damper mechanism and the turbine. The clutch mechanism includes a lockup piston, a lockup hydraulic chamber, a lockup end plate, at least one lockup friction disk, and a lockup clutch plate. The lockup piston is supported by the front cover so as to be relatively movable in the axial direction. The lockup hydraulic chamber is formed between the front cover and the lockup piston. The lockup end plate is disposed on the opposite side of the lockup piston in the axial lockup hydraulic chamber and is supported by the front cover so as to be integrally rotatable. The lock-up friction disk is disposed between the lock-up piston and the lock-up end plate, and is supported by a member on the damper mechanism side so as to be integrally rotatable and relatively movable in the axial direction. The lockup clutch plate is disposed between the lockup piston and the lockup friction disk. The lockup piston can bias the inner peripheral portion of the lockup clutch plate in the axial direction. The outer periphery of the lockup clutch plate can be frictionally engaged with the lockup friction disk.

  In this device, when the clutch mechanism is operated, the lockup piston urges the inner peripheral portion of the lockup clutch plate, and the outer peripheral portion of the lockup clutch plate frictionally engages with the lockup friction disk. That is, since this device has the lock-up clutch plate, the diameter of the lock-up piston can be reduced, and the lock-up piston can be reduced in size as compared with the prior art. Thereby, the operability of the lockup piston is improved, and the responsiveness of the lockup device is improved.

  According to a second aspect of the present invention, there is provided the lockup device for the fluid torque transmission device according to the first aspect, wherein the lockup clutch plate is supported by the front cover so as to be integrally rotatable, and has a support hole penetrating in the axial direction. The lock-up piston has a support protrusion to be inserted into the support hole.

  In this device, since the support protrusion of the lockup piston is inserted into the support hole of the lockup clutch plate, the lockup piston can be rotated integrally with the front cover via the lockup clutch plate. Can be supported. As a result, relative rotation between the lockup piston and the peripheral member can be suppressed, and wear of the lockup piston and the peripheral member can be prevented.

  According to a third aspect of the present invention, in the lockup device for a fluid torque transmission device according to the first or second aspect, the front cover has an outer peripheral cylindrical portion extending in the axial direction on the outer peripheral side, and the clutch mechanism is attached to the front cover. It further has an annular clutch drum that is fixed and arranged on the inner peripheral side of the outer peripheral cylindrical portion. The lockup end plate, the lockup friction disk, and the lockup clutch plate are arranged on the inner peripheral side of the clutch drum. A flow path is formed between the outer peripheral cylindrical portion and the clutch drum in the radial direction.

  In this apparatus, since the flow path is formed between the outer peripheral cylindrical portion and the clutch drum in the radial direction, the working fluid flowing on the outer peripheral side of the fluid chamber is guided to the periphery of the lockup friction disk via the flow path. It becomes easy. Thereby, the cooling efficiency of the friction disk for lockup can be improved.

  According to a fourth aspect of the present invention, there is provided a lockup device for a fluid torque transmission device, which is disposed between a front cover and a turbine and mechanically connects the front cover and the turbine. The lockup device includes a clutch mechanism and a damper mechanism. The clutch mechanism is a mechanism for mechanically connecting the front cover and the turbine by hydraulic pressure. The damper mechanism has a first damper mechanism coupled to the clutch mechanism, and a second damper mechanism disposed between the first damper mechanism and the turbine. The clutch mechanism includes a lockup piston, a lockup hydraulic chamber, a lockup end plate, at least one lockup friction disk, and a lockup clutch plate. The lockup piston is supported by the front cover so as to be relatively movable in the axial direction. The lockup hydraulic chamber is formed between the front cover and the lockup piston. The lockup end plate is disposed on the opposite side of the lockup piston in the axial lockup hydraulic chamber and is supported by the front cover so as to be integrally rotatable. The lock-up friction disk is disposed between the lock-up piston and the lock-up end plate, and is supported by a member on the damper mechanism side so as to be integrally rotatable and relatively movable in the axial direction. The lockup clutch plate is disposed between the lockup piston and the lockup friction disk. The front cover has an outer peripheral cylindrical portion extending in the axial direction on the outer peripheral side, and the clutch mechanism further includes an annular clutch drum fixed to the front cover and disposed on the inner peripheral side of the outer peripheral cylindrical portion. . The lockup end plate, the lockup friction disk, and the lockup clutch plate are arranged on the inner peripheral side of the clutch drum. A flow path is formed between the outer peripheral cylindrical portion and the clutch drum in the radial direction.

  In this apparatus, since the flow path is formed between the outer peripheral cylindrical portion and the clutch drum in the radial direction, the working fluid flowing on the outer peripheral side of the fluid chamber is guided to the periphery of the lockup friction disk via the flow path. It becomes easy. Thereby, the cooling efficiency of the friction disk for lockup can be improved.

  According to a fifth aspect of the present invention, there is provided the lockup device for a hydraulic torque transmission device according to the third or fourth aspect, wherein the clutch drum has at least one drum groove extending in the axial direction on the inner peripheral side and at least one penetrating in the radial direction. And a drum communication hole.

  In this apparatus, since the clutch drum has the drum communication hole, the working fluid that has flowed into the flow path easily flows around the lockup friction disk through the drum communication hole. Thereby, the cooling efficiency of the friction disk for lockup can be improved more reliably.

  According to a sixth aspect of the present invention, in the lockup device for a fluid torque transmission device according to the fifth aspect, the drum communication hole is disposed between the axial direction of the lockup end plate and the lockup clutch plate.

  In this apparatus, since the drum communication hole is disposed between the lock-up end plate and the lock-up clutch plate in the axial direction, the working fluid can be reliably introduced around the lock-up friction disk.

  According to a seventh aspect of the present invention, there is provided the lockup device for a fluid type torque transmission device according to any one of the first to sixth aspects, wherein the lockup friction disk can rotate integrally with a member on the damper mechanism side and can relatively move in the axial direction. The lockup clutch plate and the end plate are supported by the clutch drum so as to be integrally rotatable and relatively movable in the axial direction.

  According to an eighth aspect of the present invention, in the lockup device for a fluid torque transmission device according to any of the third to seventh aspects, the clutch drum further includes at least one drum groove extending in the axial direction on the inner peripheral side. The lockup clutch plate has at least one first outer peripheral tooth that extends radially outward and engages the drum groove. The lock-up end plate has at least one second outer peripheral tooth that extends radially outward and engages the drum groove.

  A lockup device for a fluid torque transmission device according to a ninth aspect of the present invention is the lockup device according to any one of the third to eighth aspects, wherein a part of the damper mechanism is disposed on the opposite side of the clutch drum in the axial direction front cover. .

  In this apparatus, since a part of the damper mechanism is arranged on the opposite side of the clutch drum in the axial direction front cover, the working fluid discharged from the outer periphery of the torus is formed between the damper mechanism and the impeller or the front cover. It is possible to reliably guide the flow path on the outer peripheral side of the clutch drum through the gap. Thereby, the cooling efficiency of the friction disk for lockup can be further improved.

  A lockup device for a fluid torque transmission device according to a tenth aspect of the present invention is the lockup device according to any one of the first to ninth aspects, wherein the lockup friction disk has at least one inner peripheral tooth extending radially inward. The first damper mechanism is elastic between the pair of input side members, the intermediate member disposed so as to be relatively rotatable between the pair of input side members in the axial direction, and the pair of input side members and the intermediate member. And a plurality of first elastic members arranged in a deformable manner. One input-side member has at least one claw portion that extends in the axial direction and meshes with the inner peripheral tooth.

  A lockup device for a fluid torque transmission device according to an eleventh aspect is the lockup device for a fluid type torque transmission device according to any one of the third to tenth aspects, wherein the clutch drum is disposed between the front cover and the turbine in the axial direction and on the outer peripheral side of the turbine. Yes.

  In this apparatus, since the clutch drum is disposed between the front cover and the turbine in the axial direction and on the outer peripheral side of the turbine, the working fluid discharged from the torus to the outer peripheral side is between the outer cylindrical portion and the clutch drum. It becomes easy to flow into the flow path formed therebetween. Thereby, the cooling efficiency of the friction disk for lockup can be improved more.

  A fluid torque transmission device according to claim 12 is provided between a front cover, an impeller that forms a fluid chamber together with the front cover, a turbine disposed in the fluid chamber so as to face the impeller, and the front cover and the turbine. The lockup device according to any one of claims 1 to 11 is provided.

  Since this device includes the lockup device according to any one of claims 1 to 11, the responsiveness of the lockup device can be improved and the cooling efficiency of the lockup friction disk can be improved. Can do.

  In the lockup device for a fluid torque transmission device according to the present invention, since the lockup piston can be downsized, the responsiveness of the lockup piston can be improved, and the responsiveness of the lockup device can be improved. Can be improved.

  In the lockup device for a fluid torque transmission device according to the present invention, since the flow path is formed between the outer peripheral cylindrical portion of the front cover and the clutch drum in the radial direction, the working fluid that flows on the outer peripheral side of the fluid chamber Can be easily guided to the periphery of the friction disk for lockup through the flow path. Thereby, the cooling efficiency of the friction disk for lockup can be improved.

  Hereinafter, embodiments of a fluid torque transmission device and a lockup device according to the present invention will be described with reference to the drawings.

A. First Embodiment Overall Structure of Torque Converter FIG. 1 is a schematic longitudinal sectional view of a torque converter 1 in which a lockup device as a first embodiment of the present invention is adopted. An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure. Further, OO shown in FIG. 1 is a rotation axis of the torque converter 1.

  The torque converter 1 is a device for transmitting torque from an engine-side crankshaft (not shown) to an input shaft of a transmission, and includes a front cover 2 fixed to an input-side member and three types of impellers ( A torque converter main body 3 including a torus 8 including an impeller 9, a turbine 10, and a stator 11) and a lockup device 5 are included.

  The front cover 2 is an annular member fixed to a member on the engine side, and mainly includes a first cover member 21, a second cover member 22, and a third cover member 23.

  The first cover member 21 is a member that constitutes a main part of the front cover 2, and is a disc-shaped cover disc portion 21a and an outer periphery that is formed on the outer periphery of the cover disc portion 21a and protrudes toward the axial transmission side. And a cylindrical portion 21b. The outer peripheral cylindrical portion 21b is fixed to the impeller shell 12 of the impeller 9 described later by welding. A cylindrical third cylindrical support portion 21c extending in the axial direction is fixed to the cover disc portion 21a on the axial transmission side.

  The second cover member 22 is an annular member fixed to the inner peripheral portion of the first cover member 21, and has a first cylindrical support portion 22 b that protrudes to the axial transmission on the outer peripheral portion. The third cover member 23 is an annular member fixed to the inner peripheral portion of the second cover member 22, and has a second cylindrical support portion 23 b that protrudes toward the axial transmission side on the outer peripheral portion.

  The impeller 9 includes an impeller shell 12, a plurality of impeller blades 13 fixed inside the impeller shell 12, and a cylindrical impeller hub 24 disposed on the inner peripheral side of the impeller shell 12.

  The turbine 10 is disposed to face the impeller 9 in the fluid chamber. The turbine 10 includes a turbine shell 14, a plurality of turbine blades 15 fixed to the turbine shell 14, and a turbine hub 16 fixed to the inner peripheral side of the turbine shell 14. The turbine hub 16 has a flange 16a extending to the outer peripheral side, and an inner peripheral portion of the turbine shell 14 is fixed to the flange 16a by a plurality of rivets 17 (first fixing members) together with a driven plate 78 described later. ing. An input shaft of a transmission (not shown) is spline-engaged with the cylindrical portion 16b of the turbine hub 16. An annular flange portion 16d extending outward in the radial direction is formed at the tip of the cylindrical portion 16b on the axial engine side.

  The stator 11 is a mechanism for rectifying the working oil (working fluid) that is disposed between the impeller 9 and the inner peripheral portion of the turbine 10 and returns from the turbine 10 to the impeller 9. The stator 11 is mainly composed of an annular stator carrier 18 and a plurality of stator blades 19 arranged on the outer peripheral surface thereof. The stator carrier 18 is supported by a fixed shaft (not shown) via a one-way clutch 20. A first thrust bearing 31 is disposed between the third cover member 23 of the front cover 2 and the turbine hub 16 in the axial direction, and a second thrust bearing 32 is disposed between the turbine hub 16 and the stator 11 in the axial direction. The third thrust bearing 33 is disposed between the stator 11 and the impeller shell 12 in the axial direction. Each thrust bearing 31 to 33 is formed with a port through which hydraulic oil can flow in the radial direction.

2. Structure of Lock-Up Device 5 FIG. 2 shows a schematic longitudinal sectional view around the lock-up device 5. The lockup device 5 is a device for mechanically connecting the front cover 2 and the turbine 10 as necessary, and is disposed between the front cover 2 and the turbine 10 as shown in FIG. The lockup device 5 has a function as a clutch mechanism 6 that can be connected to the front cover 2 and a function as a damper mechanism 7 that elastically connects the clutch mechanism 6 and the turbine 10 in the rotational direction.

(1) Clutch mechanism 6
As shown in FIG. 2, the clutch mechanism 6 mainly includes a lock-up piston 61, a lock-up hydraulic chamber 62, a clutch drum 67, a lock-up end plate 65, a lock-up clutch plate 63, And a lock-up friction disk 64.

  The lock-up piston 61 is a member for biasing the lock-up friction disk 64 via a lock-up clutch plate 63 described later, and is supported on the front cover 2 so as to be relatively movable in the axial direction. The lock-up piston 61 has a disk-like piston main body 61a and a first support protrusion 61b. The first support protrusion 61b protrudes from the outer peripheral portion of the piston body 61a toward the axial transmission. The lock-up piston 61 is inserted between the aforementioned third cylindrical support portion 21c and the first cylindrical support portion 22b in the radial direction, and the inner peripheral surface of the third cylindrical support portion 21c and the first cylinder. Is in contact with the outer peripheral surface of the support 22b in the radial direction.

  The lockup hydraulic chamber 62 is an annular space to which hydraulic pressure is supplied when the lockup piston 61 is driven, and is formed between the front cover 2 and the lockup piston 61. The lockup hydraulic chamber 62 is sealed by seal members 61c and 22c.

  The clutch drum 67 is a member for supporting the lock-up clutch plate 63 and the lock-up end plate 65 so as to be integrally rotatable with the front cover 2, and is on the inner peripheral side of the outer peripheral cylindrical portion 21 b of the front cover 2. Is arranged. More specifically, the clutch drum 67 is disposed between the front cover 2 and the turbine 10 in the axial direction and on the outer peripheral side of the turbine 10. The clutch drum 67 has a drum body 67a, a plurality of drum grooves 67c, and a plurality of drum communication holes 67b. The drum body 67a is a cylindrical portion that extends toward the axial transmission side. The drum groove 67c is an axially formed groove formed on the inner peripheral side of the drum main body 67a. The drum communication hole 67b is a hole formed in the drum main body 67a and penetrating in the axial direction. The drum communication hole 67 b is disposed between the lock-up end plate 65 and the lock-up clutch plate 63 in the axial direction, for example. As shown in FIG. 2, a channel 68 is formed between the clutch drum 67 and the outer peripheral cylindrical portion 21b in the radial direction.

  The lockup clutch plate 63 is a member for biasing a lockup friction disk 64 described later, and is disposed between the lockup piston 61 and a lockup friction disk 64 described later. The lockup clutch plate 63 extends further from the outer peripheral portion of the lockup piston 61 to the outer peripheral side, and is disposed on the inner peripheral side of the clutch drum 67.

  The lockup clutch plate 63 includes a clutch plate main body 63a, a first pressing portion 63b, a plurality of first outer peripheral teeth 63d, a first support hole 63c, and an inner peripheral portion 63e. The first pressing portion 63b is an annular portion formed on the outer peripheral side of the clutch plate main body 63a, and is a portion that frictionally engages a lockup friction disk 64 described later. The first outer peripheral teeth 63d are portions extending radially outward from the first pressing portion 63b, and are engaged with the drum groove 67c. The first support hole 63c is a hole formed in the inner peripheral portion of the clutch plate main body 63a and penetrating in the axial direction, and the first support protrusion 61b of the lockup piston 61 is inserted into the first support hole 63c. The inner peripheral portion 63e is a portion formed on the inner peripheral side of the lock-up friction disk 64, and is disposed so as to be able to contact the lock-up piston 61 in the axial direction.

  The lockup end plate 65 is a member for receiving an urging force from the lockup piston 61, and is disposed on the axial transmission side of the lockup clutch plate 63 and on the inner peripheral side of the clutch drum 67. Yes. The lock-up end plate 65 has an end plate main body 65a and a plurality of second outer peripheral teeth 65b. The end plate main body 65a is a portion that frictionally engages with the lock-up friction disk 64. The second outer peripheral teeth 65b are portions that protrude radially outward from the end plate main body 65a, and are engaged with the drum grooves 67c. The lock-up end plate 65 is immovable to the axial transmission side by a fixing ring 66 fixed to the clutch drum 67.

  The lockup friction disk 64 is a member for frictional engagement with the lockup clutch plate 63 and the lockup end plate 65, and includes a friction disk body 64a, a plurality of first inner peripheral teeth 64c, and a pair. And a friction facing 64b. The first inner peripheral teeth 64c are portions that protrude radially inward from the friction disk main body 64a, and are engaged with a retaining plate 72 (member on the damper mechanism side) of the first damper mechanism 70 described later so as to be integrally rotatable. Match. The friction facing 64b is an annular plate fixed on both axial sides of the friction disk main body 64a, and faces the lockup clutch plate 63 and the lockup end plate 65 in the axial direction.

  As described above, the lockup piston 61 is supported by the front cover 2 via the lockup clutch plate 63 and the clutch drum 67 so as to be integrally rotatable. The lock-up clutch plate 63 is supported by the front cover 2 via the clutch drum 67 so as to be integrally rotatable and relatively movable in the axial direction. When the pressure is supplied to the lockup hydraulic chamber 62 and the lockup piston 61 is moved to the axial transmission side, the lockup friction disk is interposed between the lockup clutch plate 63 and the lockup end plate 65. 64 is pinched. As a result, torque is transmitted to the damper mechanism 7 by the frictional force generated on the friction surface of the friction facing 64b of the lockup friction disk 64.

(2) Damper mechanism 7
As shown in FIG. 2, the damper mechanism 7 mainly includes a first damper mechanism 70 and a second damper mechanism 71.

  The first damper mechanism 70 is a mechanism for transmitting the torque input from the clutch mechanism 6 to the second damper mechanism 71 and absorbing / damping the input torsional vibration, and between the clutch mechanism 6 and the turbine 10. Is arranged. The first damper mechanism 70 mainly includes a pair of retaining plates 72 and 73 (input side members), a first center plate 74 (intermediate member), a second center plate 82, and a plurality of first coil springs 77. (First elastic member). FIG. 3 shows a plan view of the retaining plate and the center plate as viewed from the axial engine side.

  As shown in FIGS. 2 and 3, the pair of retaining plates 72 and 73 are members on the input side of the first damper mechanism 70, and a plurality of stop pins 75 are maintained at a constant interval in the axial direction. It is connected by (connecting member). The pair of retaining plates 72 and 73 are inserted into the outer peripheral side of the cylindrical portion 16b of the turbine hub 16, and are supported by the cylindrical portion 16b so as to be relatively rotatable.

  The retaining plates 72 and 73 have a plurality of accommodating portions 72a and 73a. The accommodating portions 72a and 73a accommodate the first coil spring 77 between the axial directions. The accommodating portions 72a and 73a support the end portion of the first coil spring 77 in the rotation direction. The retaining plate 72 has a plurality of first claw portions 72b extending in the axial direction on the outer peripheral side, and the first claw portions 72b mesh with the first inner peripheral teeth 64c of the friction disk 64 for lockup. That is, the torque from the clutch mechanism 6 is input to the retaining plate 72 via the lockup friction disk 64.

  The first center plate 74 is a member on the output side of the first damper mechanism 70 and is disposed so as to be relatively rotatable between the axial directions of the retaining plates 72 and 73. The first center plate 74 includes a first center plate main body 74a (intermediate member main body), a plurality of second claw portions 74b, a plurality of locking groove portions 74c, and a plurality of first locking portions 74d. Yes. The first center plate main body 74a is a part constituting the main part of the first center plate 74, and is an annular part disposed on the outer peripheral side of the first coil spring 77 described later. The second claw portion 74b is a portion that extends radially outward and axially from the outer periphery of the first center plate main body 74a, and supports the end of the second coil spring 79 of the second damper mechanism 71 in the rotational direction. Yes. The second claw portion 74 b is inserted between the end portions of the second coil spring 79 from the axial direction. The locking groove portion 74c is a recess formed on the inner peripheral side, and the stop pin 75 is disposed in the locking groove portion 74c so as to be able to contact in the rotation direction. The relative rotation between the retaining plates 72 and 73 and the first center plate 74 is restricted within a certain angle range by the locking groove 74 c and the stop pin 75. The first locking portion 74d is a portion extending radially inward from the first center plate main body 74a, and supports the end portion of the first coil spring 77 in the rotational direction.

  A pair of friction washers 76 (friction members) are sandwiched between the axial directions of the retaining plates 72 and 73 and the first center plate 74. When the retaining plates 72, 73 and the first center plate 74 are rotated relative to each other, the plates 72, 73, 74 and the friction washer 76 slide in the rotational direction, and hysteresis torque is generated.

  The second center plate 82 is an annular member disposed on the inner peripheral side of the first center plate 74 so as to be relatively rotatable, and has a second center plate body 82a and a plurality of second locking portions 82b. ing. The second center plate main body 82a is an annular portion disposed on the inner peripheral side of the first coil spring 77 described later. The second locking portion 82b is a portion extending radially outward from the second center plate main body 82a, and supports the end portion of the first coil spring 77 in the rotational direction.

  The first coil spring 77 elastically connects the retaining plates 72 and 73 and the first center plate 74 in the rotational direction, and is accommodated in the accommodating portions 72a and 73a so as to be elastically deformable in the rotational direction.

  As described above, the first damper mechanism 70 is supported by the cylindrical portion 16b of the turbine hub 16 so as to be relatively rotatable. The torque input to the retaining plate 72 is output to the first center plate 74 via the retaining plates 72 and 73 and the stop pin 75, and the torsional vibration input to the retaining plate 72 is the first coil spring 77 and Absorbed and attenuated by the friction washer 76.

  The second damper mechanism 71 is a mechanism for transmitting torque input from the first damper mechanism 70 to the turbine 10 and absorbing / damping torsional vibration, and is disposed between the first damper mechanism 70 and the turbine 10. Has been. The second damper mechanism 71 mainly has a driven plate 78 (output side member), a plurality of second coil springs 79 (second elastic members), and a support plate 80 (support member).

  The driven plate 78 is a member on the output side of the second damper mechanism 71, and an inner peripheral portion thereof is fixed to the turbine hub 16 by the rivet 17 together with the turbine shell 14. The driven plate 78 is a disk-shaped member disposed between the first damper mechanism 70 and the turbine 10, and includes a plurality of axial projections 78a, a plurality of holding portions 78c, and a plurality of holding projections 78b. have. The axial protrusion 78a is a protrusion formed by, for example, pressing, and is in contact with the retaining plate 73 in the axial direction. Further, the inner peripheral edge of the retaining plate 72 is in contact with the flange portion 16 d of the turbine hub 16 in the axial direction. That is, the first damper mechanism 70 is sandwiched between the flange portion 16 d of the turbine hub 16 and the axial projection 78 a of the driven plate 78. Thereby, the axial positioning of the first damper mechanism 70 can be performed by the turbine hub 16 via the driven plate 78.

  The holding portion 78 c is a portion that holds the second coil spring 79 in the radial direction and the axial direction, and is bent according to the shape of the second coil spring 79. The holding projection 78b is a portion for supporting the second coil spring 79 in the rotation direction, and extends radially outwardly disposed at both ends of the holding portion 78c and the second coil spring 79 in the rotation direction.

  The second coil spring 79 is for elastically connecting the first center plate 74 and the driven plate 78 in the rotational direction, and is accommodated in the holding portion 78c so as to be elastically deformable in the rotational direction. As shown in FIG. 2, the second coil spring 79 and the holding portion 78 c of the driven plate 78 are disposed on the axial transmission side of the clutch drum 67 described later, and are located on the inner peripheral side of the second coil spring 79. The turbine 10 is arranged on the axial transmission side.

  The support plate 80 is an annular member for supporting the second coil spring 79 in the axial direction, and is fixed to the driven plate 78 by rivets 81. A second coil spring 79 is sandwiched between the holding portion 78 c and the support plate 80. The support plate 80 has a plurality of protrusions 80a extending in the axial direction on the outer peripheral side. The protrusion 80a is disposed between the second claw portions 74b so as to be able to contact the second claw portion 74b in the rotation direction.

  As described above, the torque input from the first damper mechanism 70 to the second damper mechanism 71 is transmitted to the turbine 10 via the support plate 80 and the driven plate 78, and the torsional vibration is absorbed and damped by the second coil spring 79. The

(3) Friction generating mechanism 4
The lockup device 5 further includes a friction generating mechanism 4. FIG. 4 is a schematic longitudinal sectional view around the friction generating mechanism 4. The friction generating mechanism 4 is a mechanism for generating a frictional resistance between the front cover 2 and the turbine 10, and is between the front cover 2 and the turbine 10 as shown in FIG. It is arranged on the inner peripheral side, more specifically, on the inner peripheral side of the clutch mechanism 6 and the damper mechanism 7. The friction generating mechanism 4 mainly includes a friction generating piston 41, a friction generating hydraulic chamber 42, a friction generating clutch plate 43, a friction generating end plate 45, and a friction generating friction disk 44. Yes.

  The friction generating piston 41 is a member for urging a friction generating friction disk 44 via a friction generating clutch plate 43 described later, and is supported on the front cover 2 so as to be relatively movable in the axial direction. 2 and 4, the friction generating piston 41 is disposed on the inner peripheral side of the lockup hydraulic chamber 62 described above. The friction generating piston 41 includes a plurality of second support protrusions 41a and a second pressing portion 41c. The second support protrusion 41 a is a portion protruding from the inner peripheral portion of the friction generating piston 41 toward the axial transmission side. The 2nd press part 41c is a part which protrudes from the outer peripheral part of the piston 41 for friction generation to the axial direction transmission side, for example, has an annular shape. The friction generating piston 41 is inserted between the first cylindrical support portion 22b and the second cylindrical support portion 23b in the radial direction, and the inner peripheral surface of the first cylindrical support portion 22b and the second cylinder. In contact with the outer peripheral surface of the support 23b in the radial direction.

  The friction generating hydraulic chamber 42 is an annular space to which hydraulic pressure is supplied when the friction generating piston 41 is driven, and is formed between the front cover 2 and the friction generating piston 41. The friction generating hydraulic chamber 42 is sealed by seal members 41d and 23c. The friction generating hydraulic chamber 42 communicates with the lockup hydraulic chamber 62 through a first communication hole 22 c formed in the first cylindrical support portion 22 b of the second cover member 22. The friction generating hydraulic chamber 42 communicates with a space on the inner peripheral side of the turbine hub 16 through a second communication hole 23 c formed in the second cylindrical support portion 23 b of the third cover member 23. As a result, the hydraulic pressure is supplied to the lockup hydraulic chamber 62 via the friction generating hydraulic chamber 42, and the pressures in both the hydraulic chambers 62, 42 become substantially the same.

  The friction generating clutch plate 43 is a member for urging a friction generating friction disk 44 described later, and is disposed between the axial direction of the friction generating piston 41 and a friction generating friction disk 44 described later. . The friction generating clutch plate 43 is arranged on the outer peripheral side of the second cylindrical support portion 23b.

  The friction generating clutch plate 43 includes a clutch plate main body 43a, a second support hole 43c, a second pressing portion 43b, and a plurality of second inner peripheral teeth 43d. The second pressing portion 43b is an annular portion formed on the outer peripheral side of the clutch plate main body 43a, and is a portion that frictionally engages a friction generating friction disk 44 described later. The second inner peripheral teeth 43d are portions extending radially inward from the clutch plate main body 43a, and are engaged with the outer peripheral grooves 23d of the second cylindrical support portion 23b. The second support hole 43c is a hole formed in the inner peripheral portion of the clutch plate main body 43a and penetrating in the axial direction. The second support protrusion 41a of the friction generating piston 41 is inserted into the second support hole 43c.

  The friction generating end plate 45 is a member for receiving a biasing force from the friction generating piston 41, and is on the axial transmission side of the friction generating clutch plate 43 and on the outer peripheral side of the second cylindrical support portion 23b. Has been placed. The friction generating end plate 45 includes an end plate main body 45a, an annular protrusion 45b, a plurality of through holes 45c, and a plurality of third inner peripheral teeth 45d. The third inner peripheral teeth 45d are portions that protrude outward in the radial direction, and are engaged with the outer peripheral grooves 23d. The friction generating end plate 45 is immovable to the axial transmission side by a fixing ring 46 fixed to the second cylindrical support portion 23b.

  The friction generating friction disk 44 is a member for frictional engagement with the friction generating clutch plate 43 and the friction generating end plate 45, and is disposed on the inner peripheral side of the tubular portion 16 b of the turbine hub 16. The friction generating friction disk 44 includes a friction disk main body 44a, a plurality of third outer peripheral teeth 44c, and a pair of friction facings 44b. The third outer peripheral teeth 44c are portions that protrude radially outward from the friction disk main body 44a, and are engaged with the inner peripheral grooves 16c of the cylindrical portion 16b. The friction facing 44b is an annular plate fixed on both axial sides of the friction disk main body 44a, and faces the friction generating clutch plate 43 and the friction generating end plate 45 in the axial direction.

  FIG. 6 is a cross-sectional view taken along the line AA in FIG. As shown in FIG. 6, a minute clearance 47 and a corresponding minute twist angle θ are secured between the third outer peripheral teeth 44c and the inner peripheral groove 16c in the radial direction. That is, a minute gap 47 is formed between the rotation direction of the front cover 2 and the turbine 10 in the operating state of the friction generating mechanism 4, and both the members 2 and 10 can be relatively rotated by a minute torsion angle θ. Yes. As a result, high hysteresis torque is not generated only within the range of the minute torsional angle θ with respect to torsional vibration caused by fluctuations in the rotation of the engine, so that it is possible to reduce the humming noise and the like.

  As described above, the friction generating piston 41 is supported by the front cover 2 through the friction generating clutch plate 43 and the clutch drum 67 so as to be integrally rotatable. The friction generating clutch plate 43 is supported by the front cover 2 via the clutch drum 67 so as to be integrally rotatable and relatively movable in the axial direction. When a pressure is supplied to the friction generating hydraulic chamber 42 and the friction generating piston 41 is moved to the axial transmission side, a friction generating friction disk is interposed between the friction generating clutch plate 43 and the friction generating end plate 45. 44 is pinched. As a result, the torsional vibration transmitted between the front cover 2 and the turbine 10 can be effectively absorbed and attenuated by the frictional force generated on the friction surface of the friction facing 44b of the friction generating friction disk 44.

4). Operation of Torque Converter 1 Next, the operation of the torque converter 1 will be described.

  Torque from a crankshaft (not shown) on the engine side is input to the front cover 2. As a result, the impeller 9 rotates and the hydraulic oil flows from the impeller 9 to the turbine 10. The turbine 10 rotates by the flow of the hydraulic oil, and the torque of the turbine 10 is output to an input shaft (not shown).

  When the speed ratio of the torque converter 1 increases and the input shaft reaches a constant rotational speed, the hydraulic pressure is supplied to the lockup hydraulic chamber 62 through the oil passage inside the input shaft. As a result, the lockup piston 61 moves toward the axial transmission side, and the lockup clutch plate 63 is biased toward the axial transmission side. As a result, the lockup friction disk 64 is held between the lockup clutch plate 63 and the lockup end plate 65, and the torque input to the front cover 2 is transmitted to the turbine 10 via the lockup device 5. Is output.

  When torsional vibration is input to the front cover 2 when the lockup device 5 is connected, the lockup friction disk 64 and the driven plate 78 rotate relative to each other, and the first coil spring 77 and the second coil spring are rotated. 79 is compressed in the direction of rotation. At this time, since the first coil spring 77 and the second coil spring 79 act in series via the first center plate 74, a wide twist angle can be secured.

  When the lockup device 5 is connected, the hydraulic pressure is supplied to the lockup hydraulic chamber 62, so the hydraulic pressure is also supplied to the friction generating hydraulic chamber 42 communicating with the hydraulic chamber 62. At this time, the pressures in the hydraulic chambers 62 and 42 are substantially equal. As a result, the lockup piston 61 moves in the axial direction, the friction generating piston 41 also moves in the axial direction, and the friction generating hydraulic chamber 42 is biased toward the axial transmission side. The friction generating friction disk 44 is sandwiched between the friction generating clutch plate 43 and the friction generating end plate 45, and a friction force is generated on the friction surface of the friction facing 44b. Thereby, in the friction generating mechanism 4, since a hysteresis torque is generated between the front cover 2 and the turbine 10, the torsional vibration input to the front cover 2 can be effectively absorbed and attenuated.

  At this time, the front cover 2 and the turbine 10 are connected by the lockup device 5 and the friction generating mechanism 4, but the effective radius of the friction disk main body 44 a of the friction generating mechanism 4 and the hydraulic chamber 42 is the clutch mechanism of the lockup device 5. 6 and the pressures in the hydraulic chambers 42 and 62 are approximately the same, the friction force generated in the friction generating mechanism 4 is smaller than the friction force generated in the clutch mechanism 6. . Therefore, as shown in FIG. 5, a desired high hysteresis torque (DC hysteresis) can be obtained in the friction generation mechanism 4 by adjusting the dimensions of the respective members of the friction generation mechanism 4.

  Since the friction generating mechanism 4 obtains an urging force by hydraulic pressure, a larger urging force can be obtained as compared with the conventional friction generating mechanism. Therefore, this friction generating mechanism 4 can obtain a larger hysteresis torque than the conventional one, and can absorb and attenuate torsional vibrations more effectively.

  Further, in this friction generating mechanism 4, since a minute gap 47 is secured between the members, when a minute torsional vibration is inputted, friction is generated between the friction generating disc 44 and the friction disk 44 within the range of the minute torsion angle θ. The clutch plate 43 and the friction generating end plate 45 rotate integrally and do not slide. That is, as shown in FIG. 5, when the minute torsional vibration is input within the range of the minute torsion angle θ, the friction generating mechanism 4 does not operate and no high hysteresis torque is generated.

  In this case, the minute torsional vibration is absorbed by the first coil spring 77 and the second coil spring 79 of the damper mechanism 7, but if the retaining plates 72 and 73 and the first center plate 74 rotate relative to each other at this time, The plates 72, 73, 74 and the friction washer 76 slide to generate hysteresis torque. This hysteresis torque can be set smaller than the hysteresis torque generated by the friction generating mechanism 4. As a result, only the low hysteresis torque (AC hysteresis) of the friction washer 76 acts within the range of the minute torsion angle θ, so that minute torsional vibration can be effectively absorbed and attenuated. The AC hysteresis here means a hysteresis torque generated by other than the friction generating mechanism 4.

  Further, when the lockup device 5 is disconnected, the supply of hydraulic pressure to the lockup hydraulic chamber 62 and the friction generating hydraulic chamber 42 is stopped. As a result, the urging force to the lockup friction disk 64 and the friction generating friction disk 44 is released. At the same time, hydraulic pressure is supplied from the inner peripheral side of the stator 11 to the torus 8. As a result, the pressure in the hydraulic chamber on the axial transmission side of the lockup piston 61 and the friction generating piston 41 rises through the communication hole 16e of the turbine hub 16, and the lockup piston 61 and the friction generating piston 41 It is biased toward the axial engine side. As a result, the mechanical connection between the front cover 2 and the turbine 10 is completely released in the clutch mechanism 6 of the lockup device 5, and the generation of high hysteresis torque is completely stopped in the friction generating mechanism 4.

  Thus, in this torque converter 1, the friction generating mechanism 4 is activated by the operating pressure of the clutch mechanism 6 when the lockup device 5 is operated, and the torque converter main body 3 is not operated when the lockup device 5 is not operated. The friction generating mechanism 4 is deactivated by the operating pressure. As a result, the operation / non-operation state of the friction generating mechanism 4 can be switched by the operating pressure of the clutch mechanism 6 or the operating pressure of the torque converter body 3, and hydraulic control for the friction generating mechanism 4 is not required.

5. Operational Effects The operational effects of the torque converter 1 according to the present invention are summarized below.

(1) Function and Effect of Structure 1) Function and Effect of Lockup Device 5 In this torque converter 1, when the clutch mechanism 6 is operated, the lockup piston 61 biases the inner peripheral portion of the lockup clutch plate 63 in the axial direction. Then, the first pressing portion 63 b of the lockup clutch plate 63 is frictionally engaged with the lockup friction disk 64. That is, since the lock-up clutch plate 63 is provided, the diameter of the lock-up piston 61 can be reduced, and the lock-up piston 61 can be reduced in size compared to the prior art. Accordingly, the operability of the lockup piston 61 is improved, and the responsiveness of the lockup device 5 can be improved.

  In this torque converter 1, since the first support protrusion 61 b of the lockup piston 61 is inserted into the first support hole 63 c of the lockup clutch plate 63, the lockup piston 61 is locked via the lockup clutch plate 63. The piston 61 is supported by the front cover 2 so as to be integrally rotatable. As a result, relative rotation between the lock-up piston 61 and the peripheral member (for example, the second cylindrical support portion 23b and the third cylindrical support portion 21c) can be suppressed, and the lock-up piston 61 and the peripheral member can be suppressed. Can be prevented.

  In this torque converter 1, since the flow path 68 is formed between the outer peripheral cylindrical portion 21b of the front cover 2 and the clutch drum 67 in the radial direction, the hydraulic oil flowing on the outer peripheral side of the fluid chamber as shown in FIG. Is guided to the periphery of the lockup friction disk 64 through the flow path 68. Thereby, the cooling effect of the friction disk 64 for lockup can be improved. Further, in this torque converter 1, since the clutch drum 67 has the drum communication hole 67b, the hydraulic oil that has flowed into the flow path 68 easily flows around the lockup friction disk 64 through the drum communication hole 67b. Thereby, the cooling effect of the friction disk 64 for lockup can be improved more reliably. Further, in this torque converter 1, since the drum communication hole 67b is disposed between the lockup clutch plate 63 and the lockup end plate 65 in the axial direction, the hydraulic oil is reliably introduced around the lockup friction disk 64. can do.

  In this torque converter 1, a part of the damper mechanism 7, more specifically the second coil spring 79, the holding portion 78 c of the driven plate 78, and the like are disposed on the axial transmission side of the clutch drum 67. The hydraulic oil discharged from the damper can be reliably guided to the flow path 68 on the outer peripheral side of the clutch drum 67 through a gap formed between the damper mechanism 7 and the impeller 9 or the front cover 2. Thereby, the cooling effect of the friction disk 64 for lockup can further be improved.

2) Action Effect of Damper Mechanism In this torque converter 1, the second claw portion 74 b that is a part of the first center plate 74 is inserted between the end portions of the second coil spring 79 from the axial direction. That is, the first and second damper mechanisms 70 and 71 are connected only by the second claw portion 74 b of the first center plate 74. Therefore, the first and second damper mechanisms 70 and 71 can be handled as separate assemblies. Thereby, assembly and disassembly of the lockup device 5 are facilitated. Thereby, assembly and disassembly of the lockup device 5 are facilitated. Further, the degree of freedom of arrangement of the second coil spring 79 is increased, and the space in the fluid chamber can be effectively used.

  In this torque converter 1, since the first damper mechanism 70 has the friction washer 76, when the retaining plates 72, 73 and the first center plate 74 rotate relative to each other, the members slide to each other, and the retaining plate A frictional resistance in the rotational direction, that is, a hysteresis torque is generated between the first center plate 74 and the first center plate 74. Thereby, the torsional vibration can be effectively absorbed and damped in the damper mechanism 7.

  In this torque converter 1, since the first damper mechanism 70 is supported on the outer peripheral side of the cylindrical portion 16b of the turbine hub 16, the radial positioning of the first damper mechanism 70 can be performed by the turbine hub. Further, since the first damper mechanism 70 is sandwiched between the flange portion 16d of the turbine hub 16 and the driven plate 78 of the second damper mechanism 71 between the axial directions, the driven plate 78 is used to position the first damper mechanism 70 in the axial direction. Via the turbine hub 16.

  In this torque converter 1, the first center plate 74 and the stop pin 75 are disposed so as to be able to contact in the rotational direction, and therefore the operating angle of the first damper mechanism 70 is determined by both members 74 and 75. Accordingly, the operating angle of the first damper mechanism 70 can be determined with a simple structure, and an increase in the number of parts can be prevented. In addition, since the support plate 80 of the second damper mechanism 71 and the retaining plate 73 of the first damper mechanism 70 are disposed so as to be able to contact in the rotation direction, the operating angle of the second damper mechanism 71 is such that the two plates 80 and 73 are operated. Determined by. Thereby, the operating angle of the second damper mechanism can be determined with a simple structure, and an increase in the number of parts can be prevented. Furthermore, since the driven plate 78 is fixed to the turbine hub 16 together with the turbine shell 14 by the rivets 81, there is no need to provide a member for fixing the driven plate 78, and the number of parts can be reduced.

  Further, since the first center plate 74 is disposed between the first coil spring 77 and the second coil spring 79 so as to be elastically deformable, the first coil spring 77 and the second coil spring 79 act in series. . Thereby, the rigidity of the damper mechanism 7 can be reduced and the torsion angle can be increased.

3) Effects of Friction Generation Mechanism 4 As described above, in this torque converter 1, since the biasing force of the friction generation friction disk 44 is obtained by the friction generation piston 41 and the hydraulic chamber 42, an elastic member is used as in the prior art. The urging force to the friction generating friction disk 44 can be set higher than in the case of using. As a result, the torque converter 1 can generate a larger hysteresis torque than the conventional one and can absorb and attenuate torsional vibrations more reliably. Further, even if the diameter of the friction generating friction disk 44 is reduced, a sufficient hysteresis torque can be obtained, so that the friction generating mechanism 4 can be made smaller than before. Further, the friction generating mechanism 4 is arranged to operate between the rotation directions of the front cover 2 and the turbine 10. That is, the friction generating mechanism 4 is configured to act in parallel with the damper mechanism 7. As a result, the friction generating mechanism 4 can be disposed separately from the first coil spring 77 and the second coil spring 79 of the damper mechanism 7, and the structure of the lockup device 5 can be simplified.

  In this torque converter 1, the operation / non-operation state of the friction generating mechanism 4 can be switched by the operating pressure of the lockup device 5 or the operating pressure of the torque converter 1. This eliminates the need for hydraulic control for the friction generating mechanism 4 and simplifies the structure. In addition, since the friction generating hydraulic chamber 42 communicates with the lockup hydraulic chamber 62, if hydraulic pressure is supplied to the lockup hydraulic chamber 62 when the lockup device 5 is operated, the friction generating hydraulic chamber 42 is also supplied to the friction generating hydraulic chamber 42. Hydraulic pressure is supplied. As a result, the friction generating mechanism 4 can be operated by the operating pressure of the lock-up device 5, and hydraulic control for the friction generating mechanism 4 becomes unnecessary.

  In this torque converter 1, the friction generating mechanism 4 is disposed on the inner peripheral side of the lockup device 5, and the friction generating piston 41 is disposed on the inner peripheral side of the lockup piston 61. Thereby, the enlargement of the torque converter 1 whole can be prevented.

  In this torque converter 1, the friction generating friction disk 44 and the turbine 10 relatively rotate within the range of the minute gap 47, so that a large hysteresis torque is not generated in the friction generating mechanism 4. Thus, when minute torsional vibration due to engine rotation fluctuation is transmitted from the front cover 2 to the lockup device 5, the engine rotation fluctuation is sufficiently absorbed and attenuated within the range of the minute gap 47, and is different during vehicle travel. Sound is less likely to occur. Further, between the rotation direction of the inner peripheral groove 16 c of the turbine hub 16 and the third outer peripheral teeth 44 c of the friction generating friction disk 44, the outer periphery of the third inner peripheral teeth 45 d of the friction generating end plate 45 and the third cover member 23. Since the minute gap 47 is secured between the rotation direction with the groove 23d, a so-called AC His mechanism in which high hysteresis torque is not generated can be realized with a simple structure.

  In this torque converter 1, since the friction generating friction disk 44 is disposed on the outer peripheral side of the annular protrusion 45b of the friction generating end plate 45, the friction generating friction disk 44 is positioned in the radial direction by the annular protrusion 45b. Can be performed. Further, in this torque converter 1, since the friction generating end plate 45 has the through holes 45c, the working fluid easily flows around the friction generating friction disk 44, and the cooling effect of the friction generating friction disk 44 is improved. Can be made. Further, since the friction generating piston 41 is supported by the friction generating clutch plate 43 so as to be integrally rotatable, the friction generating piston 41 can be integrally rotated with respect to the front cover 2 via the friction generating clutch plate 43. Can be supported. As a result, it is possible to prevent wear of the friction generating piston 41 and its peripheral members (for example, the first cylindrical support portion 22b, the second cylindrical support portion 23b, etc.). Further, since the second support protrusion 41 a of the friction generating piston 41 is inserted into the second support hole 43 c of the friction generating clutch plate 43, relative rotation between the friction generating piston 41 and the friction generating clutch plate 43 is performed. Can be prevented by a simple structure.

(2) Effects of Torsional Characteristics As described above, when the torsional angle of torsional vibration is large, for example, low frequency vibration, the friction generating friction disk 44 is connected to the friction generating clutch plate 43 and the friction generating end plate 45. The friction generating mechanism 4 generates a high hysteresis torque. Thereby, the low frequency vibration input to the front cover 2 is quickly absorbed and attenuated by the lockup device 5 and the friction generating mechanism 4.

  On the other hand, when the torsional angle of the torsional vibration is small, the friction generating friction disk 44 does not slide within the range of the minute gap 47 arranged between the friction generating friction disk 44 and the turbine hub 16, and the minute torsion is caused. No high hysteresis torque is generated within the range of the angle θ. As a result, minute torsional vibrations caused by engine rotation fluctuations are sufficiently absorbed and attenuated by the lock-up device 5, and abnormal noise during running is unlikely to occur.

B. Second Embodiment An embodiment in which the configuration of each part of the first embodiment described above is slightly changed will be described. FIG. 8 shows a schematic longitudinal sectional view of a torque converter 101 as a second embodiment of the present invention. The same components as those in the first embodiment are denoted by the same reference numerals. Since the main components are the same as those in the first embodiment, detailed description thereof is omitted.

  The torque converter 101 according to the second embodiment is different from the first embodiment in the clutch mechanism 106 of the lockup device 105. Specifically, the lockup piston 161 extends to the outer peripheral side, and has a pressing portion 161d on the outer peripheral side. Further, the lock-up clutch plate 163 has the same inner diameter as the lock-up end plate 165.

  Further, in the first embodiment, the operating angle of the second damper mechanism 71 is determined by the support plate 80 and the first center plate 74, but in the torque converter 101 of the second embodiment as shown in FIG. The operating angle of the second damper mechanism 71 is determined by the support plate 180 and the retaining plate 173. More specifically, the support plate 180 has a plurality of protrusions 180a extending on the inner peripheral side toward the axial engine side, and the retaining plate 173 has a plurality of outer peripheral protrusions 173a extending radially outward on the outer peripheral side. Have. The protrusion 180a and the outer peripheral protrusion 173a are engaged with each other.

  Furthermore, in the first embodiment, the third outer peripheral teeth 44c of the friction generating friction disk 44 mesh with the inner peripheral groove 16c formed on the inner peripheral side of the tubular portion 16b of the turbine hub 16, but the second In the torque converter 101 of the embodiment, the turbine 10 includes a locking member 190 that is a separate member from the turbine hub 16. The locking member 190 is disposed on the inner peripheral side of the tubular portion 116 b of the turbine hub 116. The locking member 190 has a fixed portion 190c and a cylindrical locking portion 190a. The fixing portion 190 c is a disk-shaped portion, and is fixed to the flange 116 a of the turbine hub 116 by a rivet 117. The cylindrical locking portion 190a is a cylindrical portion extending from the outer peripheral portion of the fixed portion 190c to the axial engine side, and a friction generating friction disk 144 is disposed on the inner peripheral side. The cylindrical locking part 190a has a plurality of locking protrusions 190b. The locking projection 190b is a portion extending in the axial direction formed at the distal end portion of the cylindrical locking portion 190a, and meshes with the first outer peripheral teeth 144c of the friction generating friction disk 144. A minute gap (not shown) is formed between the rotation direction of the locking projection 190b and the first outer peripheral tooth 144c.

  In this torque converter 101, since the friction disc 144 for generating friction is supported by a locking member 190 which is a member different from the turbine hub 116, an inner circumferential groove or the like is formed in the turbine hub 116 as in the first embodiment. There is no need to form it, and the structure can be simplified. Further, in the torque converter 101, the friction generating mechanism 104 does not generate a large hysteresis torque because the friction generating friction disk 144 and the turbine 110 relatively rotate within the range of the minute gap. As a result, when a minute torsional vibration due to engine rotation fluctuation is transmitted from the front cover 2 to the lockup device 5, the engine fluctuation fluctuation is sufficiently absorbed and attenuated within the range of the minute gap, and abnormal noise is generated when the vehicle travels. Is less likely to occur. In addition, since a minute gap is formed between the locking protrusion 190b of the locking member 190 and the first outer peripheral teeth 144c of the friction generating friction disk 144, AC that does not generate high hysteresis torque with a simple structure. A His mechanism can be realized.

  In the first embodiment, the driven plate 78 has the inner peripheral portion of the turbine shell 14 fixed to the flange 16a of the turbine hub 16 by a plurality of rivets 17 together with the driven plate 78 described later. In the converter 101, a driven plate 178 is directly connected to the turbine shell 114. Specifically, as shown in FIG. 8, the driven plate 178 does not extend to the inner peripheral side to the turbine hub 116, and extends radially inward only to the axial transmission side of the second coil spring 79. The inner peripheral portion of the driven plate 178 is fixed to the turbine shell 114 by a rivet 191 (second fixing member). Thereby, the axial direction dimension around the flange 116a of the turbine hub 116 can be shortened.

C. Other Embodiments Although the embodiments of the present invention have been described with reference to the drawings, the specific configuration is not limited to these embodiments and can be changed without departing from the scope of the invention.

(1) Micro Gap In the above-described embodiment, the micro gap 47 is secured between the friction generating friction disk 44 and the turbine hub 16 in the rotational direction, but the friction generating clutch plate 43 and the friction generating end plate 45 A case where the minute gap 47 is formed between the rotation directions with the third cover member 23 is also conceivable. A minute gap is formed between the rotational direction of the friction generating friction disk 44 and the turbine hub 16 and between the rotational direction of the friction generating clutch plate 43 and the friction generating end plate 45 and the third cover member 23. It is also conceivable. Even in these cases, the same effects as those of the first embodiment can be obtained. The same applies to the second embodiment.

(2) Quantity of protrusions and the like In the above-described embodiment, a plurality of protrusions and grooves are formed in each part, but the number of protrusions and grooves is not limited to this and may be one.

(3) Friction discs In the above-described embodiment, the number of the lock-up friction discs 64 and the friction generating friction discs 44 is described as one. However, the present invention is not limited to this, and a plurality of friction discs are arranged in the axial direction. You may be arranged in parallel. In this case, for example, an intermediate disk or the like is disposed between the friction disks like a multi-plate clutch.

(4) Damper mechanism 7
In the above-described embodiment, the plurality of first coil springs 77 are arranged in series in the first damper mechanism 70 of the damper mechanism 7, but they may be arranged in parallel. In the second damper mechanism 71, the plurality of second coil springs 79 are arranged in series, but may be arranged in parallel.

(5) Configuration of Each Part In the first and second embodiments described above, the configuration of each part is slightly different, but is not limited to the configuration shown in each embodiment. For example, a part of the configuration shown only in the second embodiment can be applied to the first embodiment, and vice versa.

BRIEF DESCRIPTION OF THE DRAWINGS The longitudinal cross-sectional schematic of the torque converter 1 as 1st Embodiment of this invention. The longitudinal cross-sectional schematic of the lockup apparatus 5 periphery. The top view of the retaining plate 72, the 1st center plate 74, and the 2nd center plate 82. FIG. The longitudinal cross-sectional schematic diagram of the friction generation mechanism 4 periphery. FIG. 6 is a torsional characteristic diagram of the damper mechanism 7; AA sectional drawing of FIG. The figure which shows the flow of the hydraulic oil around the clutch drum 67. FIG. The longitudinal cross-sectional schematic of the torque converter 101 as 2nd Embodiment of this invention.

Explanation of symbols

1 Torque converter (fluid torque transmission device)
2 Front cover 4 Friction generating mechanism 5 Lock-up device 6 Clutch mechanism 7 Damper mechanism 9 Impeller 10 Turbine 41 Friction generating piston 42 Friction generating hydraulic chamber 43 Friction generating clutch plate 44 Friction generating friction disk 45 Friction generating end plate 44 Friction facing 45 Friction generating end plate 61 Lock-up piston 62 Lock-up hydraulic chamber 63 Lock-up clutch plate 64 Lock-up friction disk 65 Lock-up end plate 70 First damper mechanism 71 Second damper mechanism

Claims (12)

A lockup device for a fluid torque transmission device, which is disposed between a front cover and a turbine, and mechanically connects the front cover and the turbine;
A clutch mechanism for mechanically connecting the front cover and the turbine by hydraulic pressure;
A damper mechanism having a first damper mechanism coupled to the clutch mechanism, and a second damper mechanism disposed between the first damper mechanism and the turbine;
The clutch mechanism includes a lockup piston supported by the front cover so as to be relatively movable in the axial direction, a lockup hydraulic chamber formed between the front cover and the lockup piston, and the lock An axial direction of the piston for the lockup, and a lockup end plate disposed on the opposite side of the lockup hydraulic chamber and supported by the front cover so as to be integrally rotatable, and the lockup piston and the lockup end plate At least one lockup friction disk disposed between and supported by a member on the damper mechanism side so as to be integrally rotatable and relatively movable in the axial direction, and the lockup piston and the lockup friction disk And a clutch plate for lock-up arranged between
The lockup piston can bias the inner peripheral portion of the lockup clutch plate in the axial direction;
The outer peripheral portion of the lockup clutch plate is frictionally engageable with the lockup friction disk.
Lock-up device for fluid torque transmission device. The lockup clutch plate is supported by the front cover so as to be integrally rotatable, and has a support hole penetrating in the axial direction.
The lockup piston has a support protrusion to be inserted into the support hole.
The lockup device for a fluid type torque transmission device according to claim 1. The front cover has an outer peripheral cylindrical portion extending in the axial direction on the outer peripheral side,
The clutch mechanism further includes an annular clutch drum fixed to the front cover and disposed on the inner peripheral side of the outer peripheral cylindrical portion,
The lock-up end plate, the lock-up friction disk, and the lock-up clutch plate are arranged on the inner peripheral side of the clutch drum,
Between the outer peripheral cylindrical portion and the clutch drum in the radial direction, a flow path is formed,
The lockup device for a fluid type torque transmission device according to claim 1 or 2. A lockup device for a fluid torque transmission device, which is disposed between a front cover and a turbine, and mechanically connects the front cover and the turbine;
A clutch mechanism for mechanically connecting the front cover and the turbine by hydraulic pressure;
A damper mechanism having a first damper mechanism coupled to the clutch mechanism, and a second damper mechanism disposed between the first damper mechanism and the turbine;
The clutch mechanism includes a lockup piston supported by the front cover so as to be relatively movable in the axial direction, a lockup hydraulic chamber formed between the front cover and the lockup piston, and the lock An axial direction of the piston for the lockup, and a lockup end plate disposed on the opposite side of the lockup hydraulic chamber and supported by the front cover so as to be integrally rotatable, and the lockup piston and the lockup end plate At least one lockup friction disk disposed between and supported by a member on the damper mechanism side so as to be integrally rotatable and relatively movable in the axial direction, and the lockup piston and the lockup friction disk And a clutch plate for lock-up arranged between
The front cover has an outer peripheral cylindrical portion extending in the axial direction on the outer peripheral side,
The clutch mechanism further includes an annular clutch drum fixed to the front cover and disposed on the inner peripheral side of the outer peripheral cylindrical portion,
The lock-up end plate, the lock-up friction disk, and the lock-up clutch plate are arranged on the inner peripheral side of the clutch drum,
Between the outer peripheral cylindrical portion and the clutch drum in the radial direction, a flow path is formed,
Lock-up device for fluid torque transmission device. The clutch drum has at least one drum communication hole penetrating in the radial direction.
The lockup device for a fluid type torque transmission device according to claim 3 or 4. The drum communication hole is disposed between axial directions of the lock-up end plate and the lock-up clutch plate.
The lockup device for a fluid type torque transmission device according to claim 5. The lock-up friction disk is supported by the member on the damper mechanism side so as to be integrally rotatable and relatively movable in the axial direction,
The lockup clutch plate and the end plate are supported by the clutch drum so as to be integrally rotatable and relatively movable in the axial direction.
The lockup device for a fluid type torque transmission device according to any one of claims 3 to 6. The clutch drum further has at least one drum groove extending in the axial direction on the inner peripheral side,
The lockup clutch plate has at least one first outer peripheral tooth extending radially outward and engaging with the drum groove;
The lock-up end plate has at least one second outer peripheral tooth that extends radially outward and engages the drum groove;
The lockup device for a fluid type torque transmission device according to any one of claims 3 to 7. A part of the damper mechanism is disposed on the side opposite to the front cover in the axial direction of the clutch drum.
A lockup device for a fluid torque transmission device according to any one of claims 3 to 8. The lock-up friction disk has at least one inner peripheral tooth extending radially inward,
The first damper mechanism includes a pair of input-side members, an intermediate member disposed so as to be relatively rotatable between axial directions of the pair of input-side members, the pair of input-side members, and the intermediate member. A plurality of first elastic members arranged so as to be elastically deformable between,
One of the input side members has at least one claw portion extending in the axial direction and meshing with the inner peripheral tooth,
The lockup device for a fluid type torque transmission device according to any one of claims 1 to 9. The clutch drum is disposed between the front cover and the turbine in the axial direction and on the outer peripheral side of the turbine.
The lockup device for a fluid type torque transmission device according to any one of claims 3 to 10. A front cover;
An impeller that forms a fluid chamber with the front cover;
A turbine disposed opposite the impeller in the fluid chamber;
The lockup device according to any one of claims 1 to 11 disposed between the front cover and the turbine;
A fluid-type torque transmission device.

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