JP6660331B2 - Torque converter - Google Patents

Description

  The present invention relates to a clutch transmission device for transmitting torque between an output shaft and a clutch component constituting a part of the lock-up clutch by rotating together with a pump impeller in a connected state of the lock-up clutch. And a first damper having a first damper spring held by a pair of holding plates which form a part of the torque transmission path and are spaced apart in the axial direction of the output shaft. The present invention relates to a torque converter in which a second damper having a second damper spring is interposed, and a dynamic damper is attached to the torque transmission path between the first damper and the second damper.

  Patent Document 1 discloses a torque converter in which two dampers are provided in a torque transmission path between a clutch piston and an output shaft of a lock-up clutch, and a dynamic damper is provided in the torque transmission path between the dampers. Have been.

JP-A-2015-14363

  In the torque converter disclosed in Patent Document 1, a damper plate formed by extending one outer periphery of a pair of holding plates in a radially outward direction, and a pair of inertia rings sandwiching the outer periphery of the damper plate from both sides. Between them, and dynamic damper springs housed in recesses respectively formed on mutually facing surfaces of the inertia rings, there is a possibility that the inertia mass of the inertia rings cannot be sufficiently secured, The damping performance of the dynamic damper may be insufficient, and the shape of the inertia ring may be complicated, leading to an increase in manufacturing cost. Further, the damper plate has a cylindrical portion fitted to one of the inertia rings for positioning the inertia ring, and a shaft of the torque converter for securing the axial length of the fitted portion. It may be difficult to reduce the size in the direction.

  The present invention has been made in view of the above circumstances, and provides a torque converter that secures a sufficient inertial mass, enables a dynamic damper to be manufactured at low cost, and that can be downsized in the axial direction. With the goal.

  In order to achieve the above-mentioned object, the present invention provides a torque transmitting torque between a clutch component and an output shaft constituting a part of the lock-up clutch by rotating together with a pump impeller when the lock-up clutch is connected. A first damper having a first damper spring held by the clutch constituent member in the transmission path, and forming a part of the torque transmission path and arranged at an interval in the axial direction of the output shaft; A second damper having a second damper spring held by a pair of holding plates is interposed, and a torque is provided between the first damper and the second damper to a dynamic damper in the torque transmission path. In the converter, the dynamic damper is formed in a ring plate shape coaxial with the output shaft. An inertial rotator having a weight member attached to an outer peripheral portion of an inertial plate sandwiched between the pair of holding plates, and an elastic member provided between the inertial plate and the pair of holding plates; The first damper spring is engaged with the first damper spring by sandwiching the first damper spring between one of the plates and the holding plate disposed on the opposite side of the inertia plate from the clutch constituent member. A mating claw portion is provided, and an elongated hole is formed in the inertial plate and extends through the claw portion in the circumferential direction of the inertial plate.

  In addition, in addition to the configuration of the first feature, the present invention may be configured such that the outer peripheral edge of the elongated hole and the claw portion cooperate in positioning the inertial plate with respect to the pair of holding plates in the radial direction. A second feature is that the inertial plates are arranged so as to be close to or in contact with each other in a radial direction of the inertial plate.

  The present invention, in addition to the configuration of the first or second aspect, further comprises: the second damper spring included in the second damper rotates with the output shaft so as to be radially inward of the inertial plate. A third feature is that the driven plate is disposed between the driven plate and the pair of holding plates, and the inertial plate and the driven plate are formed of the same material and have the same thickness. .

  In the present invention, in addition to the configuration of the third aspect, the annular gap between the outer periphery of the driven plate and the inner periphery of the inertial plate is set to be 0.8 times or more the thickness of the inertial plate and the driven plate. This is a fourth feature.

  Further, according to the present invention, in addition to any one of the first to fourth features, the length of the elongated hole along the circumferential direction of the inertial plate is a relative rotation angle of the pair of the holding plate and the inertial plate. A fifth feature is that the claw portion is set so as to abut on the longitudinal end of the long hole as the value becomes a predetermined value.

  The clutch piston 43 of the embodiment corresponds to the clutch component of the present invention, the dynamic damper spring 58 of the embodiment corresponds to the elastic member of the present invention, and the first elongated hole 69 of the embodiment corresponds to the present invention. Corresponding to the long hole.

  According to the first aspect of the present invention, the inertial rotating body of the dynamic damper is configured such that the weight member is attached to the outer peripheral portion of the inertial plate sandwiched between the pair of holding plates, so that a sufficient inertial mass is secured. And the shape is simple so that it can be manufactured at low cost. Further, a claw provided on one of the pair of holding plates on the opposite side of the inertia plate with respect to the clutch constituent member is inserted through an elongated hole formed in the inertia plate, and engages with the first damper spring. Therefore, the distance between the clutch constituent member and the one holding plate can be shortened in the axial direction, and the size of the torque converter in the axial direction can be reduced.

  According to the second feature of the present invention, the position of the inertial plate in the radial direction with respect to the pair of holding plates is determined by the cooperation of the outer peripheral edge of the long hole and the claw portion, thereby increasing the size in the axial direction. The relative positions of the holding plate and the inertial plate along the radial direction can be determined without causing the increase in the number of parts or the number of parts.

  According to the third aspect of the present invention, since the inertia plate and the driven plate located radially inward of the inertia plate are made of the same material and have the same thickness, the inertia plate and the driven plate can be made the same. , The material yield can be improved, and the cost can be reduced.

  According to the fourth aspect of the present invention, since the annular gap of 0.8 times or more the thickness of the inertial plate and the driven plate is formed between the driven plate and the inertial plate, the inertial plate and the driven plate are made of the same material. It is possible to use a general press method when cooperating with the same. In addition, it is not necessary to cut the inner periphery of the driven plate, and the cost can be further reduced.

  Further, according to the fifth aspect of the present invention, the relative rotation angle between the pair of holding plates and the inertia plate is prevented from becoming too large, and the elastic member interposed between the pair of holding plates and the inertia plate is oversized. It is possible to prevent a heavy load from acting, and to improve the life of the elastic member.

FIG. 3 is a longitudinal sectional view of the torque converter, which is a sectional view taken along line 1-1 in FIG. 2. It is sectional drawing which follows the 2-2 line of FIG. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2. It is a perspective view showing a claw part inserted in a long hole of an inertia plate.

  Hereinafter, an embodiment of the present invention will be described with reference to the attached FIGS. 1 to 4. First, in FIG. 1, the torque converter is disposed to face the pump impeller 11 and the pump impeller 11. A turbine runner 12 and a stator 13 disposed between the pump impeller 11 and an inner peripheral portion of the turbine runner 12 are provided. An arrow 14 is provided between the pump impeller 11, the turbine runner 12, and the stator 13. Thus, the circulation circuit 15 for circulating the working oil is formed.

  The pump impeller 11 includes a bowl-shaped pump shell 16, a plurality of pump blades 17 provided on the inner surface of the pump shell 16, a pump core ring 18 connecting the pump blades 17, and a pump shell 16. A pump hub 19 fixed to the periphery by, for example, welding is provided. An oil pump (not shown) for supplying working oil to the torque converter is interlocked and connected to the pump hub 19.

  A bowl-shaped transmission cover 20 that covers the turbine runner 12 from the outside is joined to the outer periphery of the pump shell 16 by welding, and a ring gear 21 is fixed to the outer periphery of the transmission cover 20 by welding. A drive plate 22 is fastened to the ring gear 21. The crankshaft 23 of the vehicle engine E is coaxially fastened to the drive plate 22, and rotational power is input to the pump impeller 11 from the vehicle engine E.

  The turbine runner 12 has a bowl-shaped turbine shell 24, a plurality of turbine blades 25 provided on the inner surface of the turbine shell 24, and a turbine coring 26 connecting the turbine blades 25.

  An end portion of the output shaft 27 that transmits the rotational power from the vehicle engine E to a transmission (not shown) is attached to a bottomed cylindrical support cylinder portion 20a that is integrated with the transmission cover 20 at a central portion thereof by a bearing bush 28. Supported through. The output shaft 27 is spline-coupled to an output hub 29 which is disposed at an axial distance from the pump hub 19, and a needle thrust bearing is provided between the output hub 29 and the transmission cover 20. 30 is interposed.

  The stator 13 includes a stator hub 31 disposed between the pump hub 19 and the output hub 29, a plurality of stator blades 32 provided on the outer circumference of the stator hub 31, and a stator core ring 33 connecting the outer circumferences of the stator blades 32. A thrust bearing 34 is interposed between the pump hub 19 and the stator hub 31, and a thrust bearing 35 is interposed between the output hub 29 and the stator hub 31.

  A one-way clutch 37 is interposed between the stator hub 31 and a stator shaft 36 that rotatably surrounds the output shaft 27 that rotates together with the output hub 29. The stator shaft 36 is connected to a transmission case ( (Not shown) so as not to rotate.

  A clutch chamber 38 communicating with the circulation circuit 15 is formed between the transmission cover 20 and the turbine shell 24. In the clutch chamber 38, a lock-up clutch 40, an inertial rotating body 41, and the inertial rotating body A spring holder 42 that holds the inner peripheral portion of the inertial rotator 41 from both sides so as to enable relative rotation within a limited range with respect to the spring 41 is accommodated.

  The lock-up clutch 40 has a clutch piston 43 that can be frictionally connected to the transmission cover 20 and switches between a connected state in which the clutch piston 43 is frictionally connected to the transmission cover 20 and a disconnected state in which the frictional connection is released. The inner peripheral portion of the clutch piston 43 formed in a disk shape is slidably supported by the output hub 29 so as to be movable in the axial direction.

  The inside of the clutch chamber 38 is partitioned by the clutch piston 43 into an inner chamber 38 a on the turbine runner 12 side and an outer chamber 38 b on the transmission cover 20 side, and is adjacent to the needle thrust bearing 30. An oil groove 44 formed in the output hub 29 communicates with the outer chamber 38b, and the oil groove 44 communicates with the inside of the cylindrical output shaft 27. An oil passage 45 is formed between the pump hub 19 and the stator shaft 36 and communicates with the inner periphery of the circulation circuit 15. The oil pump and the oil reservoir (not shown) are alternately connected to the oil groove 44 and the oil passage 45.

  When the vehicle engine E is idling or in an extremely low speed operation range, hydraulic oil is supplied from the oil groove 44 to the outer chamber 38b, and hydraulic oil is led out from the oil passage 45. In this state, the outer chamber 38b Has a higher pressure than the inner chamber 38a, the clutch piston 43 is pushed to the side away from the inner surface of the transmission cover 20, and the lock-up clutch 40 is not connected. In this state, the relative rotation of the pump impeller 11 and the turbine runner 12 is allowed, and when the pump impeller 11 is rotationally driven by the vehicle engine E, the operating oil in the circulation circuit 15 is indicated by an arrow 14. As described above, the pump impeller 11, the turbine runner 12, and the stator 13 circulate in the circulation circuit 15 in this order, and the rotational torque of the pump impeller 11 is output through the turbine runner 12, the spring holder 42, and the output hub 29. The power is transmitted to the shaft 27.

  In a state where a torque amplifying action is generated between the pump impeller 11 and the turbine runner 12, a corresponding reaction force is borne by the stator 13, and the stator 13 is fixed by the locking action of the one-way clutch 37. When the torque amplifying operation is completed, the stator 13 rotates together with the pump impeller 11 and the turbine runner 12 in the same direction while idling the one-way clutch 37 due to the reversal of the torque direction received by the stator 13.

  When such a torque converter enters the coupling state or approaches the coupling state, hydraulic oil is supplied from the oil passage 45 to the inner chamber 38a, and hydraulic oil is led out from the oil groove 44. Thus, the connection state between the oil groove 44 and the oil passage 45 and the oil pump and the oil reservoir is switched. As a result, in the clutch chamber 38, the inner chamber 38a becomes higher in pressure than the outer chamber 38b, and the pressure difference pushes the clutch piston 43 toward the transmission cover 20 so that the outer periphery of the clutch piston 43 is The inner cover 20 is in pressure contact with the transmission cover 20 and frictionally connected to the transmission cover 20, and the lock-up clutch 40 is connected.

  When the lock-up clutch 40 is in the connected state, the torque transmitted from the vehicle engine E to the transmission cover 20 forms a part of the lock-up clutch 40 and rotates together with the pump impeller 11. It is mechanically transmitted to the output shaft 27 via a torque transmission path 46 including the clutch piston 43 as a member, the spring holder 42, and the output hub 29, and the torque transmission path 46 A first damper 47 having a first damper spring 55 held by the clutch piston 43 and a second damper spring 70 held by the spring holder 42 forming a part of the torque transmission path 46. A second damper 48, and the first damper 47 and the second Dynamic damper 49 in the torque transmission path 46 between the damper 48 is attached.

  The spring holder 42 is formed by a pair of holding plates 50 and 51 arranged at intervals in the axial direction of the output shaft 27 and arranged coaxially with the output hub 29 so as to be relatively non-rotatable with each other. And is formed so as to be sandwiched between the pair of holding plates 50 and 51 and partially project radially inward from the holding plates 50 and 51 to constitute a part of the torque transmission path 46. A plurality of first rivets are attached to the output hub 29 so that an inner peripheral portion of the ring plate driven plate 52 and an inner peripheral portion of the turbine shell 24 of the turbine runner 12 rotate together with the output hub 29. Fixed at 53.

  The first damper 47 includes a plurality of coil-shaped first damper springs 55 which are held by the clutch piston 43 and are arranged at equal intervals in a circumferential direction. The first damper spring 55 includes the clutch piston 43 and the spring holder. 42.

  On the surface of the outer periphery of the clutch piston 43 on the side opposite to the transmission cover 20, an annular housing recess 56 is formed, and the annular housing recess 56 is housed in the housing recess 56 at equal intervals in the circumferential direction. A spring holding member 54 that holds the first damper spring 55 between the clutch piston 43 and the damper spring 55 is fixed to the clutch piston 43.

  The spring holding member 54 has an outer periphery substantially corresponding to the inner periphery of the housing recess 56, and a ring plate portion 54 a disposed coaxially with the clutch piston 43. One damper spring 55 is formed in a circular arc shape in cross section so as to cover the inner side, and is continuously provided at four locations at equal intervals in the circumferential direction of the outer periphery of the ring plate portion 54a. A spring cover portion 54b formed long in the circumferential direction; and the ring plate portion 54a disposed between the spring cover portions 54b and protruding radially outward from the spring cover portion 54b. The ring plate 54a is formed integrally with a spring contact portion 54c continuously provided on the outer periphery of the second rivet 5. In is fixed to the clutch piston 43.

  The spring contact portion 54c is disposed between the plurality of first damper springs 55, and when the lock-up clutch 40 is in the disconnected state, the spring contact portion 54c is located on both sides thereof. The first damper spring 55 comes into contact with an end of the first damper spring 55.

  2 and 3, the dynamic damper 49 includes a spring holder 42, an inertial rotating body 41, and a plurality of, for example, six, interposed between the spring holder 42 and the inertial rotating body 41. And a coil-shaped dynamic damper spring 58 as an elastic member.

  The inertial rotating body 41 has a ring-shaped inertial plate 61 sandwiched between outer peripheral portions of the pair of holding plates 50 and 51, and a ring-shaped inertial plate 61 fixed to the inertial plate 61 by a plurality of third rivets 63. And a weight member 62. The inertial plate 61 is formed such that its outer peripheral portion projects radially outward from the pair of holding plates 50 and 51, and the weight member 62 is fixed to the outer peripheral portion of the inertial plate 61. . The dynamic damper spring 58 is held by the pair of holding plates 50 and 51, and is disposed between the inertial plate 61 forming a part of the inertial rotating body 41 and the pair of holding plates 50 and 51. It is interposed in.

  Spring holding portions 50a and 51a for holding the dynamic damper spring 58 are provided at a plurality of places, for example, six places, at equal intervals in the circumferential direction of the pair of holding plates 50 and 51, and one of the dynamic damper springs 58 is provided. It is formed so that the part faces the outside. On the other hand, a spring accommodating recess 64 for accommodating the dynamic damper spring 58 is formed in an inner peripheral portion of the inertial plate 61 corresponding to the spring holding portions 50a and 51a so as to open to the inner peripheral portion of the inertial plate 61. When the lock-up clutch 40 is not connected, both ends of the spring accommodating recess 64 along the circumferential direction of the inertia plate 61 abut on both ends of the dynamic damper spring 58.

  A cylindrical first spacer 65 is interposed between the pair of holding plates 50 and 51, and a fourth rivet 66 penetrating through the first spacer 65 is provided between the pair of holding plates 50 and 51. They are connected so that they cannot rotate relative to each other. A plurality of spacer accommodating recesses 67 for accommodating the first spacer 65 while permitting relative rotation of the inertial plate 61 and the pair of holding plates 50 and 51 are provided in an inner peripheral portion of the inertial plate 61. It is arranged between the spring receiving recesses 64 in the circumferential direction of the plate 61 and is formed so as to open to the inner periphery of the inertial plate 61.

  The inertial plate 61 and the driven plate 52 disposed radially inward of the inertial plate 61 are formed of the same material, for example, the same steel plate and have the same thickness t. An annular gap d between the outer periphery of the inertial plate 52 and the inner periphery of the inertial plate 61 is set to be 0.8 times or more the thickness t of the inertial plate 61 and the driven plate 52.

  The first damper spring 55 of the first damper 47 includes the spring contact portion 54c of the spring holding member 54 fixed to the clutch piston 43 and a pair of the holding plates 50 forming the spring holder 42. , 51, in this embodiment, the lock-up clutch 40 is interposed between the clutch piston 43 and a holding plate 50 on the opposite side to the clutch piston 43. A plurality of claw portions 68 are provided integrally so as to sandwich the damper spring 55 between the spring contact portion 53c of the spring holding member 54.

  With reference to FIG. 4 as well, a first elongated hole 69 extending long in the circumferential direction of the inertial plate 61 by inserting the claw portion 68 formed in a bifurcated shape into the inertial plate 61 so as to pass therethrough. Is formed. In this embodiment, the outer peripheral portion of the holding plate 50 is formed so as to be bent so as to expand toward the opposite side to the first damper spring 55, and the same number as the number of the first damper springs 55. A certain claw portion 68 is provided integrally with the holding plate 50 so as to extend from the outer peripheral bent portion of the holding plate 50 in a direction along the axis of the output shaft 27.

  In addition, the outer peripheral edge of the first elongated hole 69 and the claw portion 68 cooperate to position the inertial plate 61 with respect to the pair of holding plates 50 and 51 in the radial direction, so that the inertial plate 61 is moved. They are arranged radially close to or in contact with each other.

  The length L of the first elongated hole 69 along the circumferential direction of the inertia plate 61 is determined by the relative rotation angle of the pair of holding plates 50 and 51 and the inertia plate 61 becoming a predetermined value. The claw portion 68 is set to abut on the longitudinal end of the first long hole 69.

  The second damper 48 is provided between the pair of holding plates 50 and 51 and the driven plate 52 that rotates together with the output shaft 27, and a part of the second damper 48 is provided. A plurality of, for example, six second damper springs 70 are held between the pair of holding plates 50 and 51.

  Spring holding portions 50b and 51b for holding the second damper spring 70 are provided at a plurality of places, for example, six places at equal intervals in the circumferential direction of the pair of holding plates 50 and 51, and the second damper The spring 70 is formed so that a part thereof faces the outside. On the other hand, a spring accommodating hole 71 for accommodating the second damper spring 70 is formed in an inner peripheral portion of the driven plate 52 corresponding to the spring holding portions 50b and 51b.

  Along the radial direction of the pair of holding plates 50, 51, on the inner side of the spring receiving hole 71, between the pair of holding plates 50, 51, an equal interval is provided in the circumferential direction of the driven plate 52. Cylindrical second spacers 73 are provided at a plurality of locations, for example, at six locations, and are respectively inserted into second elongated holes 72 extending long in the circumferential direction. The pair of holding plates 50 and 51 are provided with a pair of the holding plates 50 and 51. The second spacers 73 are connected by a plurality of fifth rivets 74 respectively penetrating therethrough. That is, the driven plate 52 can rotate relative to the spring holder 42 within a limited range in which the second spacer 73 moves within the second long hole 72.

  Next, the operation of this embodiment will be described. A dynamic damper 49 attached to a torque transmission path 46 between the clutch piston 43 and the output shaft 27 which constitutes a part of the lock-up clutch 40 is coaxial with the output shaft 27. An inertial rotating body 41 having a weight member 62 attached to an outer peripheral portion of an inertial plate 61 formed between a pair of holding plates 50 and 51 and having an inertia plate 61 and a pair of the holding plates Since the dynamic damper spring 58 provided between 50 and 51 is provided, a sufficient inertial mass can be secured by the inertial rotating body 41 and the shape is simple, so that it can be manufactured at low cost.

  A first damper spring 55 is provided between one of the pair of holding plates 50 and 51 on one of the holding plates 50 disposed on the side opposite to the clutch piston 43 with respect to the inertia plate 61. A claw portion 68 that engages with the first damper spring 55 is provided so as to sandwich the first damper spring 55, and a first elongated hole 69 that extends through the inertia plate 61 in the circumferential direction of the inertia plate 61 by inserting the claw portion 68. Is formed, the distance between the clutch piston 43 and the one holding plate 50 can be shortened in the axial direction, and the size of the torque converter in the axial direction can be reduced.

  Further, the outer peripheral edge of the first elongated hole 69 and the claw portion 68 cooperate with each other to position the inertial plate 61 with respect to the pair of holding plates 50 and 51 along the radial direction. Since they are arranged so as to be close to or in contact with each other in the radial direction, the holding plates 50, 51 and the inertial plate 61 can be arranged along the radial direction without increasing the size in the axial direction or increasing the number of components. The relative position can be determined.

  Also, a second damper spring 70 of the second damper 48 is rotated with the output shaft 27 so as to be rotated radially inward of the inertia plate 61, and a pair of the holding plates 50. , 51, and the inertia plate 61 and the driven plate 52 are formed of the same material so as to have the same plate thickness t, so that the inertia plate 61 and the driven plate 52 are made of the same material. In this way, the material yield can be improved, and the cost can be reduced.

  Further, the annular gap d between the outer periphery of the driven plate 52 and the inner periphery of the inertia plate 61 is set to be 0.8 times or more the thickness t of the inertia plate 61 and the driven plate 52, so that the inertia plate 61 When the driven plate 52 is co-produced from the same material, a general pressing method can be used. Further, it is not necessary to cut the inner periphery of the driven plate 52, so that the cost can be further reduced.

  Further, the length L of the first elongated hole 69 along the circumferential direction of the inertial plate 61 is determined by the relative rotation angle of the pair of holding plates 50 and 51 and the inertial plate 61 becoming a predetermined value. Since the claw portion 68 is set to abut on the longitudinal end of the first elongated hole 69, the relative rotation angle of the pair of holding plates 50, 51 and the inertial plate 61 is prevented from becoming too large. Thus, it is possible to prevent an excessive load from acting on the dynamic damper spring 58 provided between the pair of holding plates 50 and 51 and the inertia plate 61, and to improve the life of the dynamic damper spring 58.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the claims. Is possible.

11 Pump impeller 27 Output shaft 40 Lock-up clutch 41 Inertial rotator 43 Clutch piston 46 as a clutch constituent member Torque transmission path 47 First , A second damper 49, a dynamic damper 50, 51, a holding plate 55, a first damper spring 58, a dynamic damper spring 61 as an elastic member, an inertia plate. 62 weight member 68 claw 69 elongated hole 70 second damper spring 52 driven plate d annular gap L elongated hole length t ..Sheet thickness

Claims (5)

  When the lock-up clutch (40) is connected to the pump impeller (11) and rotates together with the pump impeller (11), torque is generated between the clutch component (43) and a part of the lock-up clutch (40) and the output shaft (27). A first damper (47) having a first damper spring (55) held by the clutch component (43) in a torque transmission path (46) for transmission, and a part of the torque transmission path (46); And a second damper (48) having a second damper spring (70) held by a pair of holding plates (50, 51) arranged at intervals in the axial direction of the output shaft (27). ), And a dynamic damper (4) is provided in the torque transmission path (46) between the first damper (47) and the second damper (48). ), The dynamic damper (49) is formed in a ring plate shape coaxial with the output shaft (27), and is inserted between the pair of holding plates (50, 51). An inertial rotating body (41) having a weight member (62) attached to the outer periphery of the inertial plate (61); and an elastic member (58) provided between the inertial plate (61) and the pair of holding plates (50, 51). And the first holding plate (50) of the pair of holding plates (50, 51) disposed on the side opposite to the clutch component (43) with respect to the inertia plate (61). Claw portion (68) that engages with the first damper spring (55) by sandwiching the damper spring (55) between the clutch member (43) and the first damper spring (55). Provided, the inertia plate (61), a torque converter, wherein a circumferentially extending long elongated hole of the inertia plate by inserting the claw portion (68) (61) (69) is formed.   The outer peripheral edge of the long hole (69) and the claw portion (68) cooperate in positioning the inertial plate (61) with respect to the pair of holding plates (50, 51) along the radial direction. The torque converter according to claim 1, wherein the torque converter is arranged so as to be close to or in contact with each other in a radial direction of the inertial plate.   A driven plate that is disposed radially inward of the inertial plate (61) such that the second damper spring (70) of the second damper (48) rotates with the output shaft (27). (52) and a pair of the holding plates (50, 51), and the inertial plate (61) and the driven plate (52) are formed of the same material and have the same plate thickness. The torque converter according to claim 1 or 2, wherein   The annular gap (d) between the outer circumference of the driven plate (52) and the inner circumference of the inertia plate (61) is 0.8 times the thickness (t) of the inertia plate (61) and the driven plate (52). 4. The torque converter according to claim 3, wherein the torque converter is set to twice or more.   The length (L) of the elongated hole (69) along the circumferential direction of the inertial plate (61) is such that the relative rotation angle of the pair of holding plates (50, 51) and the inertial plate (61) is a predetermined value. 5. The device according to claim 1, wherein the claw portion is set so as to abut on a longitudinal end of the slot. 6. Torque converter.