JP4522220B2 - Damper disk assembly - Google Patents

Description

  The present invention relates to a damper disk assembly for transmitting torque and absorbing torsional vibration, and more particularly to a damper disk assembly having a pair of elastic members that are compressed in series in the rotational direction.

  The damper mechanism is used, for example, in a power transmission system, and is a mechanism for transmitting torque and absorbing / attenuating torsional vibration. The damper mechanism includes a first rotating member, a second rotating member, and a torsion spring and an elastic body that are disposed between the rotating members and are compressed in the rotating direction between the rotating members. For example, a coil spring is used as the torsion spring. Rubber or resin is used as the elastic body. As a device in which the damper mechanism is incorporated, there are a clutch disk assembly, a flywheel assembly, a torque converter lockup device, and the like.

  The coil spring used in the damper mechanism must have a low rigidity and a wide torsion angle in order to improve vibration absorption performance. Is being used. However, in the arc type coil spring, there is a problem that an intermediate portion of the coil spring moves outward in the radial direction due to a component force radially outward when the spring is compressed and slides with respect to other members. In such a case, the frictional resistance is increased and the vibration absorbing function of the damper mechanism is degraded.

In order to solve such a problem, a structure in which a pair of coil springs are arranged in series in the rotation direction instead of an arc type coil spring (hereinafter referred to as “series type”) is known. An intermediate float member is disposed between rotation direction ends of the pair of coil springs (see, for example, Patent Document 1).
Japanese Patent Laid-Open No. 11-141617

  In the conventional series type damper mechanism, the intermediate float member is positioned in the radial direction (centering) by the outer peripheral surface of the flange of the hub. Specifically, the inner peripheral surface of the annular ring portion of the intermediate float member is supported by the outer peripheral surface of the flange of the hub so as to be relatively rotatable and immovable in the radial direction.

  However, if a hub is used to support the intermediate float member, the hub becomes large, resulting in problems such as an increase in weight and cost.

  An object of the present invention is to improve the centering structure of an intermediate float member in a damper disk assembly that achieves low rigidity using a pair of elastic members.

A damper disk assembly according to a first aspect includes a first plate member, a second plate member, a pair of elastic members, and an intermediate float member. The second plate member is arranged to be rotatable relative to the first plate member. The pair of elastic members are arranged in the rotation direction so as to be compressed when the first plate member and the second plate member rotate relative to each other. The intermediate float member has an annular portion and a support portion that extends from the annular portion and is disposed between the rotation directions of the pair of elastic members. The intermediate float member is positioned radially by the second plate member. Here, the second plate member has a radial support portion that extends in the axial direction and supports the intermediate float member so as to be relatively rotatable and immovable in the radial direction, and the radial support portion is arranged in the circumferential direction. It has a cylindrical shape that extends. Further, a notch is formed in the radial support portion, and a part of the annular portion of the intermediate float member extends into the notch.

The damper disk assembly has a simple structure because the centering of the intermediate float member is realized by the plate member. Further, in this damper disk assembly, a part of the annular portion extends into the notch, so that the strength of the intermediate float member is improved.

According to a second aspect of the present invention , in the damper disk assembly according to the first aspect , the radial width of the portion extending into the notch in the annular portion is longer than the radial width of the portion supported by the radial support portion.

According to a third aspect of the present invention , in the damper disk assembly according to the first aspect, in the intermediate float member, the strength of the portion between the support portions is higher than the portion where the support portions are formed.

  In this damper disk assembly, since the strength of the portion between the support portions of the intermediate float member is increased, the strength of the intermediate float member can be effectively maintained without increasing the overall weight. This is because the portion between the support portions of the intermediate float member is a portion where stress concentration is likely to occur due to centrifugal force or a load from the spring.

According to a fourth aspect of the present invention , in the damper disk assembly according to the third aspect , in the intermediate float member, the radial width of the portion between the support portions is longer than the portion where the support portions are formed.

  In the damper disk assembly according to the present invention, since the centering of the intermediate float member is realized by the plate member, the structure is simple.

(1) Basic Structure of Torque Converter FIG. 1 is a schematic vertical sectional view of a torque converter 1 in which one embodiment of the present invention is adopted. The torque converter 1 is a device for transmitting torque from an engine crankshaft (not shown) to an input shaft (not shown) of a transmission. 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 FIG. The OO line shown in FIG. 1 is the rotating shaft of the torque converter 1.

  The torque converter 1 includes a torus 6 composed of three types of impellers (impeller 18, turbine 19, stator 20) and a lockup device 7.

  The front cover 14 is a disk-shaped member, and is disposed close to the tip of the engine crankshaft. A center boss 15 is fixed to the inner periphery of the front cover 14 by welding. A plurality of nuts 11 are fixed at equal intervals in the circumferential direction on the outer peripheral side of the front cover 14 and the engine side.

  An outer peripheral cylindrical portion 16 extending toward the axial transmission side is formed on the outer peripheral portion of the front cover 14. The outer peripheral edge of the impeller shell 22 of the impeller 18 is fixed to the tip of the outer peripheral cylindrical portion 16 by welding. As a result, the front cover 14 and the impeller 18 form a fluid chamber filled with hydraulic oil (fluid). The impeller 18 mainly includes an impeller shell 22, a plurality of impeller blades 23 fixed to the inside of the impeller shell 22, and an impeller hub 24 fixed to the inner peripheral portion of the impeller shell 22.

  The turbine 19 is disposed to face the impeller 18 in the axial direction in the fluid chamber. The turbine 19 mainly includes a turbine shell 25 and a plurality of turbine blades 26 fixed to the surface of the turbine shell 25 on the impeller side. An inner peripheral portion of the turbine shell 25 is fixed to a flange of the turbine hub 27 by a plurality of rivets 28.

  The turbine hub 27 is connected to an input shaft (not shown) so as not to be relatively rotatable.

  The stator 20 is a mechanism for rectifying the flow of hydraulic oil returning from the turbine 19 to the impeller 18. The stator 20 is an integral member manufactured by casting with resin, aluminum alloy or the like. The stator 20 is disposed between the inner periphery of the impeller 18 and the inner periphery of the turbine 19. The stator 20 mainly includes an annular carrier 29 and a plurality of stator blades 30 provided on the outer peripheral surface of the carrier 29. The carrier 29 is supported by a fixed shaft (not shown) via a one-way clutch 35.

  A thrust bearing 39 is disposed between the impeller hub 24 and the carrier 29. A thrust bearing 40 is disposed between the carrier 29 and the turbine hub 27.

(2) Lock-up device Next, the lock-up device 7 will be described. The lockup device 7 is mainly composed of a piston member 44 and a damper disk assembly 45.

  The piston member 44 is a disk-shaped member that is disposed close to the axial engine side of the front cover 14. An inner peripheral cylindrical portion 48 extending toward the axial transmission side is formed on the inner peripheral portion of the piston member 44. The inner peripheral cylindrical portion 48 is supported on the outer peripheral surface of the turbine hub 27 so as to be capable of relative rotation and axial movement. The axial transmission side end of the inner peripheral cylindrical portion 48 abuts against the flange portion of the turbine hub 27, so that the movement toward the axial transmission side is limited to a predetermined position. A seal ring 49 is disposed on the outer peripheral surface of the turbine hub 27, and the seal ring 49 seals an axial space in the inner peripheral portion of the piston member 44.

  The outer peripheral portion of the piston member 44 functions as a clutch coupling portion. An annular friction facing 46 is fixed on the engine side of the outer periphery of the piston member 44. The friction facing 46 is opposed to an annular and flat friction surface formed on the inner surface of the outer peripheral portion of the front cover 14. A cylindrical portion 44a extending toward the axial transmission side is formed on the outer peripheral portion of the piston member 44, and a plurality of slots 47 are formed at equal angular intervals in the cylindrical portion 44a.

  The damper disk assembly 45 is a device for elastically connecting the turbine 19 from the piston member 44 in the rotational direction, and has a function of transmitting torque from the piston member 44 to the turbine 19 and absorbing torsional vibration. ing. The damper disk assembly 45 includes a drive member 52, a driven member 53 mainly composed of a pair of plate members 56, 57, and a plurality of torsion springs 58, 59, 60. In FIG. 2, a damper disk assembly 45 is shown on the left side of the alternate long and short dash line when the plate member 57 is removed. 1 is a cross-sectional view taken along the line AO in FIG. 2, and FIG. 3 is a cross-sectional view taken along the line OB in FIG.

  The drive member 52 is an annular and disk-shaped member, and has a plurality of protrusions 52a that protrude outward in the radial direction. The protrusion 52 a is engaged with a slot 47 formed in the cylindrical portion 44 a of the piston member 44, and serves as a torque input portion to which torque from the piston member 44 is input. By this engagement, the piston member 44 and the drive member 52 can move relative to each other in the axial direction, but rotate integrally in the rotational direction.

  A plurality of protrusions 52 b extending inward in the radial direction are formed on the inner peripheral edge of the drive member 52. Spaces in the radial direction between the protrusions 52 b are spring support holes 61 and 62. The first spring support holes 61 are spaces that are relatively long in the rotational direction and are formed at two locations facing each other in the radial direction. The second spring support holes 62 are spaces that are relatively short in the rotation direction, are formed between the rotation directions of the first spring support holes 61, and are arranged to face each other in the radial direction. The protrusion 52b has a mountain shape whose width in the rotational direction becomes narrower as it goes radially inward.

  The drive member 52 is further formed with a third spring support hole 63 and a stopper slit 64. The third spring support hole 63 is a hole whose radial position is formed radially outward from the first and second spring support holes 61 and 62. The third spring support hole 63 coincides with the second spring support hole 62 in the rotational direction position. The third spring support hole 63 has a shorter rotational direction length than the second spring support hole 62. The slit 64 is a hole whose radial position is formed radially outward from the first and second spring support holes 61 and 62. The slits 64 are formed at four locations side by side in the rotational direction, and have an arcuate shape that extends long in the rotational direction.

  The pair of plate members 56 and 57 constituting the driven member 53 are disposed on both sides in the axial direction of the drive member 52. The plate members 56 and 57 are formed with first to third spring support raising portions 71 to 73 corresponding to the first to third spring support holes 61 to 63 of the drive member 52. The first to third spring support raising portions 71 to 73 are window portions whose edges on both sides in the radial direction are raised outward in the axial direction. The first spring support raising portion 71 has the same length in the rotational direction as the first spring support hole 61. The second spring support raising portion 72 has a shorter rotation direction length than the second spring support hole 62, and the rotation direction end is located on the inner side in the rotation direction than the second spring support hole 62. The third spring support raising portion 73 is longer in the rotation direction than the third spring support hole 63, and the rotation direction end is located on the outer side in the rotation direction than the third spring support hole 63.

  The inner peripheral portions of both plate members 56 and 57 are in contact with each other, and are fixed to the flange of the turbine hub 27 together with the inner peripheral portion of the turbine shell 25 by the rivets 28 described above.

  As members constituting the elastic coupling portion of the damper disk assembly 45, there are provided a first torsion spring 58 (two sets in total of four), a second torsion spring 59 (two), and a third torsion spring 60 (two). ing. These torsion springs 58 to 60 are coil springs, and are compressed in the rotational direction between the drive member 52 and the driven member 53 when the drive member 52 and the driven member 53 are relatively rotated. The first torsion spring 58 is a parent-child type coil spring, but functions as a single coil spring. These springs may be single coil springs.

  The first torsion spring 58 is disposed in the first spring support hole 61 and the first spring support raising part 71, and both sides in the radial direction and the rotation direction are supported by both, and both sides in the axial direction are the first spring support raising part 71. Is supported by. A pair of first torsion springs 58A and 58B are arranged in the first spring support hole 61 and the first spring support raising portion 71 side by side in the rotational direction. The outer ends in the rotational direction of the pair of first torsion springs 58A and 58B are in contact with the protrusions 52b. The inner ends in the rotation direction of the pair of first torsion springs 58 </ b> A and 58 </ b> B are in contact with the support portion 68 b of the intermediate float member 68. The intermediate float member 68 is a disk-like and annular member disposed on the inner peripheral side of the drive member 52 between the axial directions of the pair of plate members 56 and 57. The intermediate float member 68 includes an annular portion 68a and a pair of support portions 68b extending radially outward from the outer peripheral edge thereof. The support portion 68b enters the intermediate position in the rotation direction of the first spring support hole 61 from the inside in the radial direction, and contacts the rotation direction inner ends of the pair of first torsion springs 58A and 58B. Note that the support portion 68b has a fan shape in which the width in the rotation direction increases toward the outer side in the radial direction. In summary, the support portion 68b is a member that is disposed between the pair of first torsion springs 58A and 58B in the rotation direction, and supports the rotation direction ends of the pair of first torsion springs 58A and 58B. Further, it can be considered that the support portions 68b are fixed to each other by the annular portion 68a and rotate together. Thus, since the support part 68b is supporting the rotation direction edge part of a pair of 1st torsion spring 58A, 58B, the attitude | position of a pair of 1st torsion spring 58A, 58B is correctly maintained.

  The second torsion spring 59 is disposed in the second spring support hole 62 and the second spring support raising portion 72, and both sides in the radial direction and the rotation direction are supported by both, and both sides in the axial direction are supported by the second spring support raising portion 72. Is supported by. The rotation direction end of the second torsion spring 59 is in contact with the rotation direction of the two spring support raising portion 72, but is separated from the rotation direction end of the second spring support hole 62 in the rotation direction. In the figure, the first rotation direction gap 91 (θ1) is defined between the rotation direction end of the second torsion spring 59 on the rotation direction R2 side and the protrusion 52b on the rotation direction R2 side, and the rotation direction R1 of the second torsion spring 59 A fourth rotation direction gap 92 (θ1 ′) is defined between the rotation direction end on the rotation side and the protrusion 52b on the rotation direction R1 side.

  The third torsion spring 60 is disposed in the third spring support hole 63 and the third spring support raising portion 73, both sides in the radial direction and the rotation direction are supported by both, and both sides in the axial direction are third spring support raising portions. 73. The rotation direction end of the third torsion spring 60 is in contact with the rotation direction of the third spring support hole 63, but is separated from the rotation direction end of the third spring support raising portion 73 in the rotation direction. In the figure, the second rotational direction gap 93 (θ2) is defined between the rotational direction end of the third torsion spring 60 on the rotational direction R2 side and the end of the third spring support raising portion 73 on the rotational direction R2 side. A space between the rotation direction end of the torsion spring 60 on the rotation direction R1 side and the end of the third spring support raising portion 73 on the rotation direction R1 side is defined as a fifth rotation direction gap 94 (θ2 ′).

  The plate member 56 and the plate member 57 are fixed to each other by a plurality of stopper pins 51 on the outer peripheral side. Thereby, the plate members 56 and 57 rotate integrally, and the axial position of both is determined.

  The stopper pin 51 passes through the slit 64 of the drive member 52. The stopper pin 51 can move inside the slit 64 to both sides in the rotational direction. When the stopper pin 51 comes into contact with the rotation direction end of the slit 64, the relative rotation between the drive member 52 and the driven member 53 stops. In other words, the stopper mechanism of the damper disk assembly 45 is realized by the stopper pin 51 and the slit 64. In the figure, the gap between the stopper pin 51 and the end of the slit 64 in the rotation direction R2 side is the third rotation direction gap 95 (θ3), and the gap between the stopper pin 51 and the slit 64 in the rotation direction R2 side is the sixth rotation direction. The gap is 96 (θ3 ′).

  The angles θ1 to θ3 of the first to third rotational direction gaps 91, 93, and 95 need to have a relationship of θ1 <θ2 <θ3. Further, the angles θ1 ′ to θ3 ′ of the fourth to sixth rotational direction gaps 92, 94, and 96 need to have a relationship of θ1 ′ <θ2 ′ <θ3 ′. Note that θ1 and θ1 ′, θ2 and θ2 ′, and θ3 and θ3 ′ may be different from each other or the same.

(3) Centering portion Next, the centering portion 81 for positioning the intermediate float member 68 in the radial direction will be described. As shown in FIGS. 1 to 4, the plate member 56 has an axial extension 56 a that extends on the axial transmission side (to the plate member 57 side). The axially extending portion 56a is a portion formed by drawing and has a cylindrical shape. Further, the plate member 56 has a disk-like portion 56c fixed together with the second plate member 57 by the rivet 28 on the inner peripheral side from the axially extending portion 56a. Furthermore, a cutout 56b is formed in the axially extending portion 56a. The notch 56b is a hole that penetrates the axially extending portion 56a in the radial direction. For this reason, if another expression is used, the plate member 56 is provided with the axially extending portion 56a and the notch 56b continuously in the circumferential direction. In this embodiment, the notches 56b are provided at two places, and they are opposed to each other in the radial direction. Therefore, as shown in FIG. 4, the two axial extensions 56a and the two notches 56b are alternately arranged in the circumferential direction, and each has an arc shape having a predetermined angle in the circumferential direction. On the other hand, the annular portion 68a of the intermediate float member 68 has a first portion 68A and a second portion 68B. A support portion 68b is provided on the outer peripheral edge of the first portion 68A. The inner peripheral edge of the first portion 68A is supported in contact with the outer peripheral surface of the axially extending portion 56a. Thus, the axially extending portion 56a functions as a radial support portion, and the centering portion 81 is realized. Here, since the intermediate float member 68 is centered by the plate member 56, the structure is simple. Further, the weight reduction and cost reduction of the turbine hub 27 are realized.

  As shown in FIG. 4, the second portion 68B has a shorter inner diameter than the first portion 68A. In other words, the inner peripheral portion of the second portion 68B extends radially inward from the inner peripheral portion of the first portion 68A. More specifically, the inner diameter of the first portion 68A is constant, and the inner diameter of the second portion 68B gradually decreases from the first portion 68A, and is the shortest at the intermediate portion in the rotational direction. The inner diameters of both sides in the circumferential direction of the second portion 68B are set so as to allow relative rotation with the outer peripheral surface of the axially extending portion 56a up to a predetermined angle. Further, the inner diameter R2 of the second portion 68B (particularly, the inner diameter of the intermediate portion in the rotational direction) is shorter than the inner diameter R1 of the first portion 68A. As a result, the inner peripheral portion of the second portion 68B extends into the notch 56b of the plate member 56. Therefore, the radial position of a part of the inner peripheral edge of the second portion 68B is closer to the inner peripheral side than the radial position of the axial extension portion 56a. As a result, the radial width of the second portion 68B is larger than the radial width of the first portion 68A. As described above, the strength of the second portion 68B (portion between the support portions 68b) of the intermediate float member 68 is higher than the strength of the first portion 68A (portion where the support portion 68b is formed). The strength of the intermediate float member 68 can be effectively maintained without increasing the weight of the intermediate float member 68. This is because the second portion 68B of the intermediate float member 68 is a portion where stress concentration is likely to occur due to centrifugal force or a load from the spring. In the present embodiment, the outer diameter of the second portion 68B is also longer than the outer diameter of the first portion 68A.

(4) Operation Torque is transmitted from the crankshaft of the engine (not shown) to the front cover 14 and the impeller 18. The hydraulic oil driven by the impeller blades 23 of the impeller 18 rotates the turbine 19. The torque of the turbine 19 is output to an input shaft (not shown) via the turbine hub 27. The hydraulic fluid that flows from the turbine 19 to the impeller 18 flows through the passage of the stator 20 toward the impeller 18.

  When the hydraulic fluid in the space between the front cover 14 and the piston member 44 is drained from the inner peripheral side, the piston member 44 moves to the front cover 14 side due to the hydraulic pressure difference, and the friction facing 46 is the friction surface of the front cover 14. Pressed against. As a result, torque is transmitted from the front cover 14 to the turbine hub 27 via the lockup device 7.

  Next, the torsional characteristics of the damper disk assembly 45 of FIG. 6 will be described using the mechanical circuit diagram of FIG. FIG. 5 is a diagram for explaining the torsional characteristic positive side (the right half of FIG. 6).

  The driven member 53 is twisted with respect to the drive member 52 in the rotational direction R2 side from the neutral state of FIG. At this time, the drive member 52 is twisted with respect to the driven member 53 in the rotational direction R1, that is, in the rotational direction drive side. In the region up to the twist angle θ1, there are two pairs of springs 58A and 58B compressed in series, and each pair is compressed in parallel in the rotational direction. Since the pair of first torsion springs 58A and 58B are compressed between the rotation directions of the members 52 and 53, a relatively low rigidity characteristic is obtained. The operation in each set will be described in detail. A pair of first torsion springs are arranged between the end of the first spring support raising portion 71 in the rotational direction R1 and the end of the first spring support hole 61 in the rotational direction R2. 58A and 58B (two sets) are compressed in the rotational direction via the intermediate float member 68. At this time, the intermediate float member 68 rotates relative to the drive member 52 and the driven member 53 as the pair of first torsion springs 58A and 58B are compressed.

  When the twist angle reaches θ1, the compression of the two second torsion springs 59 is then started. Specifically, the second torsion spring 59 is compressed in the rotational direction between the rotation direction R1 side end of the second spring support raising portion 72 and the rotation direction R2 side end of the second spring support hole 62. As a result, the pair of first torsion springs 58A and 58B (two sets) and the second torsion springs 59 (two) are compressed in parallel in the rotation direction between the rotation directions of the members 52 and 53, and a relatively high torsional rigidity is achieved. Is obtained.

  When the twist angle becomes θ2 (when the twist angle θ1 is twisted by the magnitude of θ2-θ1), the compression of the two third torsion springs 60 is started. Specifically, the third torsion spring 60 is compressed in the rotational direction between the rotation direction R1 side end of the third spring support raising portion 73 and the rotation direction R2 side end of the third spring support hole 63. As a result, a pair of first torsion springs 58A and 58B (two sets), a second torsion spring 59 (two pieces), and a third torsion spring 60 (two pieces) are arranged in parallel between the rotation directions of the members 52 and 53. And the second stage characteristics are obtained.

  When the twist angle becomes θ3 (when twisted by the magnitude of θ3-θ2 from the twist angle θ2), the stopper pin 51 comes into contact with the rotation direction R2 side end of the slit 64, and as a result, the driven member 53 with respect to the drive member 52 The twisting operation ends.

  The characteristics on the negative side of the torsional characteristic (the left half in FIG. 6) for twisting the driven member 53 in the rotational direction R1 side with respect to the drive member 52 are the same, and the description thereof is omitted.

  As is apparent from the above description, a pair of first torsion springs 58A and 58B are compressed in series with each other up to the first stage up to the torsion angle θ1, so that a low rigidity characteristic can be obtained. In the second stage from the angles θ1 to θ2, the second torsion spring 59 is compressed in parallel with the pair of first torsion springs 58A and 58B, whereby the second stage rigidity can be obtained. In particular, by realizing the characteristics of the second stage, which is a region where the torsion angle is large, the first stage, which is a region where the torsion angle is small, can be made to have lower rigidity than the conventional one.

(5) Other Embodiments The present invention is not limited to the above-described embodiment, and various modifications or corrections can be made without departing from the scope of the present invention.

  For example, the structure of the lockup device is not limited to the above embodiment.

  In the embodiment, two pairs of the first elastic members are provided, but three or more pairs may be provided. In that case, three or more second elastic members may be provided.

  The present invention is not limited to a torque converter lock-up device, and can be applied to other devices such as a clutch disk assembly and a flywheel assembly.

  The driven member is composed of a single plate member, and a radial support portion may be formed on the plate member.

  Further, in the intermediate float member, the support portion may extend radially inward.

  The member that supports the intermediate float member may be a member on the input side.

1 is a schematic cross-sectional view of a torque converter that employs a lock-up device as one embodiment of the present invention. Top view of damper disk assembly of lock-up device It is sectional drawing of a lockup apparatus, and sectional drawing of O-III of FIG. The top view which shows the relationship between an intermediate | middle float member and a plate member. The mechanical circuit diagram of the damper disk assembly of a lockup apparatus. The torsional characteristic diagram of the damper disk assembly of the lockup device.

45 Damper disk assembly 52 Drive member (first plate member)
53 Driven member 56 Plate member (second plate member)
56a Axial extension (radial support)
56b Notch 57 Plate member 58 First torsion spring (elastic member)
68 Intermediate float member 68a Annular portion 68b Support portion 68A First portion 68B Second portion 81 Centering portion

Claims (4)

A first plate member;
A second plate member disposed so as to be rotatable relative to the first plate member;
A pair of elastic members arranged in a rotational direction so as to be compressed when the first plate member and the second plate member are relatively rotated ;
A ring-shaped portion, and an intermediate float member having a supporting portion disposed between the rotation direction of the pair of elastic members extending from the annular portion,
The intermediate float member is positioned radially by a second plate member ;
The second plate member has a radial support portion that extends in the axial direction and supports the intermediate float member so as to be relatively rotatable and immovable in the radial direction.
The radial support portion has a cylindrical shape extending in the circumferential direction,
The radial support portion is formed with a notch,
A portion of the annular portion of the intermediate float member extends into the notch,
Damper disk assembly. 2. The damper disk assembly according to claim 1 , wherein a radial width of a portion of the annular portion extending into the notch is longer than a radial width of a portion supported by the radial support portion. Prior Symbol intermediate float member, wherein as compared with the support portion is formed partially, the strength of the portion between between the support portion is high, the damper disk assembly according to claim 1. The damper disk assembly according to claim 3 , wherein, in the intermediate float member, a radial width of a portion between the support portions is longer than a portion where the support portions are formed.

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