JP6636972B2 - Torque converter - Google Patents

Description

  The present invention provides at least one damper in a torque transmission path for transmitting torque between a clutch component constituting a part of the lock-up clutch and an output shaft so as to rotate together with the pump impeller in a connected state of the lock-up clutch. And a torque converter provided with a dynamic damper.

  Patent Document 1 discloses a torque converter in which one damper is provided in a torque transmission path between a clutch piston and an output shaft of a lock-up clutch and a dynamic damper is additionally provided.

JP 2009-293671 A

  In the torque converter disclosed in Patent Document 1, the inertia plate of the dynamic damper is sandwiched between a pair of holding plates, and a long hole through which a connecting means for connecting the holding plates is inserted is formed in a radial direction of the inertia plate. It is necessary to secure a space for arranging a portion radially inward of the long hole of the inertial plate in the middle part along the inertia plate, which makes it difficult to downsize the torque converter along the radial direction.

  The present invention has been made in view of such circumstances, and has as its object to provide a torque converter that can be downsized in the radial direction.

  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. In a torque converter in which at least one damper is interposed in a transmission path and a dynamic damper is provided, the dynamic damper has at least an inertial rotating body having a ring-shaped inertial plate coaxial with the output shaft; A pair of holding plates that constitute a part of the torque transmission path and are arranged at intervals in the axial direction of the output shaft and sandwich the inertial plate therebetween; and the inertial plate held between the holding plates. And elasticity interposed between the pair of holding plates Material, and connecting means for connecting the pair of holding plates at a plurality of locations spaced apart in the circumferential direction so as to be relatively non-rotatable. The inner circumferential portion of the inertial plate includes the inertial plate and the pair of holding plates. A first feature is that a plurality of connecting means accommodating recesses for accommodating the connecting means while permitting relative rotation of the inertial plate are formed in the inner periphery of the inertial plate.

  Further, in addition to the configuration of the first feature, the present invention further includes a plurality of elastic members which respectively house a plurality of the elastic members arranged at intervals in a circumferential direction of the inertial plate on an inner peripheral portion of the inertial plate. A second feature is that the member accommodating recess is formed to be open to the inner periphery of the inertial plate.

  According to the present invention, in addition to the configuration of the first or second aspect, the coupling means accommodating concave portion and the elastic member accommodating concave portion may have their outer peripheral edges along the same virtual circle centered on the axis of the output shaft. A third feature is that the first and second electrodes are formed in an arc shape.

  The present invention provides, in addition to any one of the first to third features, the inertial plate and the inertial plate which are in contact with the connecting means at both ends of the connecting means accommodating recess along the circumferential direction of the inertial plate. A fourth feature is that a stopper for regulating the relative rotation limit of the holding plate is formed.

  According to the present invention, in addition to any one of the first to fourth features, the outer peripheral edge of the connection means housing recess and the connection means position the inertial plate relative to the pair of holding plates in the radial direction. A fifth feature is that the inertia plates are arranged so as to be close to or in contact with each other in a radial direction of the inertial plates so as to cooperate.

  The present invention, in addition to any one of the first to fifth features, further includes a first damper spring held by the clutch component between the clutch component and the pair of holding plates. A second damper spring, which forms part of a driven plate that rotates with the output shaft and a second damper that is interposed between the pair of holding plates, is disposed between the pair of holding plates. Is a sixth feature.

  Further, in the present invention, in addition to any one of the first to sixth features, a claw portion that engages with a first damper spring is provided on one of the pair of holding plates, and the inertial plate has A seventh feature is that a long hole extending long in the circumferential direction of the inertial plate is formed by inserting the claw portion.

  The clutch piston 43 of the embodiment corresponds to a clutch component of the present invention, and the dynamic damper spring 58 of the embodiment corresponds to an elastic member of the present invention.

  According to the first feature of the present invention, the connection means accommodating recess formed in the inner periphery of the inertia plate is opened to the inner periphery of the inertia plate so as to accommodate the connection means for connecting the pair of holding plates. Therefore, the inner diameter of the inertial plate can be set small while accommodating the connecting means, and the torque converter can be reduced in size in the radial direction.

  According to the second feature of the present invention, the elastic member accommodating recess formed in the inner peripheral portion of the inertial plate is open to the inner periphery of the inertial plate so as to accommodate the elastic member. The inner diameter of the inertia plate can be set small while accommodating the torque converter, and the size of the torque converter in the radial direction can be further reduced.

  According to the third aspect of the present invention, since the connecting means accommodating concave portion and the elastic member accommodating concave portion are formed in an arc shape along the outer peripheral edge along the same virtual circle, the coupling means accommodating concave portion and the elastic member are accommodated together. The inner diameter of the inertia plate can be set smaller, and the torque converter can be made smaller in the radial direction.

  According to the fourth aspect of the present invention, since the relative rotation limit of the inertial plate and the holding plate is regulated by bringing the connecting means into contact with the stopper portion of the connecting means receiving recess, an excessive load acts on the elastic member. Can be prevented, and the life of the elastic member can be improved.

  According to the fifth aspect of the present invention, the radial position of the inertia plate with respect to the holding plate is achieved by the outer peripheral edge of the connecting means accommodating recess and the connecting means, so that the holding plate and the inertia can be maintained without increasing the number of parts. The relative position along the radial direction of the plate can be determined.

  According to the sixth aspect of the present invention, the first damper is provided between the clutch constituent member and the holding plate, and the second damper is provided between the driven plate rotating with the output shaft and the pair of holding plates. Therefore, the damping performance can be improved with the two dampers while avoiding an increase in the size of the torque converter. Since the damper spring of the second damper and the elastic member of the dynamic damper are held between the pair of holding plates, there is no need to dispose the elastic member on the inertial rotating body side, and the shape of the inertial rotating body is simplified. In addition, the inertial mass of the inertial rotating body can be sufficiently secured, and the damping performance of the dynamic damper can be sufficiently increased.

  Further, according to the seventh aspect of the present invention, the claw portion provided on one of the holding plates is inserted into the elongated hole formed on the inertia plate and engages with the first damper spring. In addition, the distance between the holding plates can be reduced in the axial direction, and the torque converter can be reduced in size in the axial direction.

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 at least the torque transmission path 46 One damper, in this embodiment, first and second dampers 47 and 48 are interposed, and a dynamic damper 49 is additionally provided.

  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 plurality of, for example, six connecting means 59 for connecting the pair of holding plates 50 and 51 constituting the spring holder 42 so as to be relatively non-rotatable.

  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, an elastic member accommodating recess 64 for accommodating the dynamic damper spring 58 is formed on 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 elastic member accommodating recess 64 along the circumferential direction of the inertia plate 61 are in contact with both ends of the dynamic damper spring 58.

  The connecting means 59 for connecting the pair of holding plates 50 and 51 so that they cannot rotate relative to each other includes a cylindrical first spacer 65 interposed between the holding plates 50 and 51 and the pair of holding plates 50 and 51. And a fourth rivet 66 that penetrates the first spacer 65 so as to connect the first and second spacers 65 so that they cannot rotate relative to each other. A plurality of connecting means accommodating recesses 67 for accommodating the connecting means 59 while permitting relative rotation of the plates 50 and 51 are arranged between the elastic member accommodating recesses 64 in the circumferential direction of the inertial plate 61 and the inertial plate It is formed so as to open to the inner periphery of 61.

  Moreover, the coupling means housing recess 67 and the elastic member housing recess 64 are formed in an arc shape so that the outer peripheral edge thereof follows the same virtual circle C (see FIG. 2) centered on the axis of the output shaft 27. You.

  Further, at both ends of the connection means housing recess 67 along the circumferential direction of the inertia plate 61, the spacer 65 of the connection means 59 is brought into contact with the spacers 65, and the relative rotation of the inertia plate 61 and the pair of holding plates 50, 51 is performed. A stopper 67a for limiting the limit is formed.

  Further, the outer peripheral edge of the coupling means housing recess 67 and the coupling means 59 are mutually positioned in the radial direction of the inertial plate 61 so as to position the inertial plate 61 relative to the pair of holding plates 50, 51 in the radial direction. They are arranged so as to be close to or in contact with each other.

  By the way, 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 forming the spring holder 42. In this embodiment, one of the lock plates 50 and 51 is interposed between the clutch piston 43 of the lock-up clutch 40 and the holding plate 50 on the opposite side. A plurality of claw portions 68 respectively engaging with the plurality of first damper springs 55 are provided integrally so as to sandwich the damper spring 55 with the spring contact portion 54c of the spring holding member 54.

  Referring also to FIG. 4, the inertial plate 61 is formed with a long hole 69 that extends in the circumferential direction of the inertial plate 61 by inserting the claw portion 68 formed in a bifurcated shape. You. 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.

  The second damper 48 is interposed 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. 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 elongated holes 72 that extend long in the circumferential direction. A pair of holding plates 50 and 51 hold the second spacers 73 together. They are connected by a plurality of fifth rivets 74 that respectively penetrate. 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 elongated 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 a part of the lock-up clutch 40 and the output shaft 27 is coaxial with the output shaft 27. An inertial rotating body 41 having at least a ring-shaped inertial plate 61 and a part of the torque transmission path 46, which are arranged at intervals in the axial direction of the output shaft 27, and A dynamic damper spring 58 interposed between the inertial plate 61 and the pair of holding plates 50, 51 while being held between the holding plates 50, 51; Between the pair of holding plates 50 and 51 at a plurality of locations spaced apart from each other. Connecting means 59 for connecting the inertial plate 61 and the pair of holding plates 50 and 51 in the inner peripheral portion of the inertial plate 61 while allowing the relative rotation of the inertial plate 61 and the pair of holding plates 50 and 51. Since the connecting means housing recess 67 is formed open to the inner periphery of the inertial plate 61, the inner diameter of the inertial plate 61 can be set small while housing the connecting means 59, and the radial direction of the torque converter can be reduced. Can be reduced in size.

  Further, a plurality of elastic member accommodating recesses 64 accommodating a plurality of the dynamic damper springs 58 arranged at intervals in a circumferential direction of the inertial plate 61 are provided on an inner peripheral portion of the inertial plate 61. The inner diameter of the inertia plate 61 can be set small while accommodating the dynamic damper spring 58, so that the torque converter can be further downsized in the radial direction.

  Further, since the connecting means housing recess 67 and the elastic member housing recess 64 are formed in an arc shape so that the outer peripheral edge thereof follows the same virtual circle C centered on the axis of the output shaft 27, the connection is made. The inner diameter of the inertia plate 61 can be set smaller while accommodating both the means 59 and the dynamic damper spring 58, and the torque converter can be further reduced in the radial direction.

  Further, stoppers are provided at both ends of the connection means accommodating recess 67 along the circumferential direction of the inertia plate 61 to abut against the connection means 59 to restrict the relative rotation limit of the inertia plate 61 and the pair of holding plates 50 and 51. Since the portion 67a is formed, the relative rotation limit of the inertial plate 61 and the pair of holding plates 50 and 51 is regulated by bringing the connecting means 59 into contact with the stopper 67a of the connecting means receiving recess 67, so that dynamic By preventing an excessive load from acting on the damper spring 58, the life of the dynamic damper spring 58 can be improved.

  The radius of the inertial plate 61 is set so that the outer peripheral edge of the connecting means receiving recess 67 and the connecting means 59 cooperate to position the inertial plate 61 with respect to the pair of holding plates 50 and 51 in the radial direction. Since they are arranged so as to be close to or in contact with each other in the directions, the relative positions along the radial direction of the pair of holding plates 50 and 51 and the inertial plate 61 can be determined without increasing the number of components.

  A first damper 47 having a first damper spring 55 held by the clutch piston 43 is interposed between the clutch piston 43 and the pair of holding plates 50, 51, and rotates together with the output shaft 27. Since the second damper 48 is interposed between the driven plate 52 and the pair of holding plates 50, 51, the damping performance can be improved by the two dampers 47, 48 while avoiding an increase in the size of the torque converter. it can. Moreover, since the second damper spring 70 that constitutes a part of the second damper 48 is held between the pair of holding plates 50 and 51, the second damper spring 70 and the dynamic damper 49 Since the damper spring 58 is held between the pair of holding plates 50 and 51, there is no need to dispose the dynamic damper spring 58 on the inertial rotating body 41 side, and the shape of the inertial rotating body 41 is simplified. In addition, the inertial mass of the inertial rotating body 41 can be sufficiently secured, and the damping performance of the dynamic damper 49 can be sufficiently increased.

  Further, one of the pair of holding plates 50, 51 is provided with a claw portion 68 which engages with the first damper spring 55, and the claw portion 68 is inserted through the inertia plate 61 to thereby maintain the inertia. Since the long hole 72 extending in the circumferential direction of the plate 61 is formed, the distance between the clutch piston 43 and the pair of holding plates 50 and 51 can be shortened in the axial direction, and the torque converter can be downsized in the axial direction. Becomes possible.

  The embodiments of the present invention have been described above. However, 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 that is a clutch constituent member Torque transmission paths 47 and 48 Damper 49 Dynamic dampers 50, 51 Holding plate 52 Driven plate 55 First damper spring 58 Dynamic damper spring 59 as an elastic member Connecting means 61 · Inertial plate 64 · · · Elastic member accommodating concave portion 67 · · · Connecting means accommodating concave portion 67a · · · Stopper portion 68 · · · Claw portion 69 ··· Long hole 70 ··· Second damper spring C ··· Virtual circle

Claims (7)

  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). In a torque converter in which at least one damper (47, 48) is interposed in a torque transmission path (46) for transmitting and a dynamic damper (49) is attached, the dynamic damper (49) is connected to the output shaft ( An inertia rotating body (41) having at least a ring-shaped inertia plate (61) coaxial with the shaft (27), and a part of the torque transmission path (46), which is spaced in the axial direction of the output shaft (27); And a pair of holding plates (50, 51) which are arranged with a space therebetween and sandwich the inertial plate (61) therebetween. An elastic member (58) interposed between the inertial plate (61) and the pair of holding plates (50, 51) while being held between the holding plates (50, 51); Connecting means (59) for connecting the pair of holding plates (50, 51) so as to be relatively non-rotatable at a plurality of places with a gap between the inner plate and the inertial plate (61). ) And a plurality of connecting means accommodating recesses (67) for accommodating the connecting means (59) while permitting relative rotation of the pair of holding plates (50, 51) are opened to the inner periphery of the inertial plate (61). A torque converter characterized by being formed as follows.   A plurality of elastic member accommodating recesses (64) for accommodating a plurality of the elastic members (58) arranged at intervals in a circumferential direction of the inertial plate (61) in an inner peripheral portion of the inertial plate (61). The torque converter according to claim 1, wherein the torque converter is formed to be open to an inner periphery of the inertial plate.   The coupling means accommodating recess (67) and the elastic member accommodating recess (64) are formed in an arc shape such that the outer peripheral edge thereof follows the same virtual circle (C) centered on the axis of the output shaft (27). The torque converter according to claim 1, wherein the torque converter is formed.   The two ends of the inertia plate (61) and the holding plates (50, 51) are brought into contact with the connection means (59) at both ends of the connection means housing recess (67) along the circumferential direction of the inertia plate (61). The torque converter according to any one of claims 1 to 3, wherein a stopper portion (67a) for limiting a relative rotation limit is formed.   The outer peripheral edge of the coupling means receiving recess (67) and the coupling means (59) cooperate to position the inertial plate (61) with respect to the pair of holding plates (50, 51) in the radial direction. 5. The torque converter according to claim 1, wherein the inertia plates are arranged so as to be close to or in contact with each other in a radial direction of the inertial plate.   A first damper (47) having a first damper spring (55) held by the clutch component (43) is provided between the clutch component (43) and the pair of holding plates (50, 51). A second plate constituting a part of a second damper (48) interposed between the driven plate (52) rotating with the output shaft (27) and the pair of holding plates (50, 51). The torque converter according to any one of claims 1 to 5, wherein the damper spring (70) is held between the pair of holding plates (50, 51).   One of the pair of holding plates (50, 51) is provided with a claw (68) that engages with the first damper spring (55). The claw (68) is attached to the inertial plate (61). The torque converter according to any one of claims 1 to 6, wherein an elongated hole (69) extending in a circumferential direction of the inertial plate (61) is formed by being inserted.