JP6161047B2 - Torque converter - Google Patents

Description

  The present invention includes a pump impeller to which a transmission cover is liquid-tightly coupled, a turbine runner disposed to face the pump impeller, a stator disposed between the pump impeller and an inner peripheral portion of the turbine runner, An output member fixed to an output hub that rotates together with the output shaft, a clutch member that can be frictionally connected to the transmission cover, and a connection state in which the clutch member is frictionally connected to the transmission cover and a non-connection that is released from the frictional connection A lockup clutch whose state can be switched, a spring holder capable of rotating relative to the output member, a first damper spring held by the lockup clutch, and an interposition between the output member and the spring holder. And a second damper spring held by the spring holder, When the lock-up clutch is in the connected state, the first damper spring and the second damper between the clutch member and the output member according to an increase in the torsion angle between the pump impeller and the output member. A first transmission stage in which a damper spring operates in series; and a second transmission in which only the first damper spring of the first damper spring and the second damper spring is in an operating state between the clutch member and the output member. The present invention relates to a torque converter in which the clutch member and the output member are directly connected through stages.

  Such a torque converter is known from Patent Document 1.

Japanese Patent No. 5350702

  In the torque converter disclosed in Patent Document 1, the turbine runner is fixed to the output member, the first damper spring is held by the lockup clutch, and the spring has a pair of holding plates that hold the output member from both sides in the axial direction. A second damper spring is held by the holder, and one of the pair of holding plates is provided with an abutting portion that abuts the output member so as to restrict relative rotation within a set range with the output member, and the pair of holding plates On the other side, a claw portion that abuts against one end portion of the first damper spring is provided, so that it is necessary to increase the thickness of each of the pair of holding plates in order to ensure the strength, resulting in an increase in weight. As the plate thickness increases, it is necessary to secure a large space in the axial direction, which increases the size of the torque converter in the axial direction. Further, the claw portion of the other holding plate is formed so as to be bent in the axial direction so as to contact one end portion of the first damper spring, so that an axial space for arranging the claw portion is provided. It is necessary to ensure the vicinity of one end portion of the first damper spring, which also causes an increase in the axial size of the torque converter.

  This invention is made | formed in view of this situation, and it aims at providing the torque converter which enabled size reduction.

  In order to achieve the above object, the present invention provides a pump impeller to which a transmission cover is liquid-tightly coupled, a turbine runner disposed opposite to the pump impeller, an inner peripheral portion of the pump impeller and the turbine runner A connected state in which a stator disposed between the output member is fixed to an output hub that rotates together with the output shaft, and a clutch member that can be frictionally connected to the transmission cover and the clutch member is frictionally connected to the transmission cover And a lock-up clutch capable of switching the non-connected state in which the frictional connection is released, a spring holder capable of rotating relative to the output member, a first damper spring held by the lock-up clutch, and the output member And a second interposed between the spring holders and held by the spring holders And a first spring between the clutch member and the output member in accordance with an increase in torsion angle between the pump impeller and the output member in the connected state of the lockup clutch. A first transmission stage in which the damper spring and the second damper spring operate in series, and only the first damper spring of the first damper spring and the second damper spring operates between the clutch member and the output member. In the torque converter in which the clutch member and the output member are directly connected through the second transmission stage that is in a state, the spring holder has a pair of holding plates that sandwich the output member from both sides in the axial direction. And the first damper spring is interposed between the clutch member and the clutch member. The transmission member supported by the clutch member and capable of relative rotation at the first set rotation angle causes the spring holder and the output member to relatively rotate by a second set rotation angle smaller than the first set rotation angle. In accordance with the first feature, the first member is inserted into at least one of the pair of holding plates while being in contact with the output member and disabling relative rotation with the spring holder.

  According to the present invention, in addition to the configuration of the first feature, the retainer includes a first spring abutting portion that holds the first damper spring between the clutch member and abuts on one end portion of the first damper spring. Is fixed to the clutch member with a cylindrical collar interposed between the clutch member and the transmission member, a support plate portion disposed between the clutch member and the retainer, and the first damper spring. And a second spring contact portion projecting from the support plate portion so as to contact the other end portion of the support plate portion, and the support plate portion with respect to the clutch member and the retainer. A second feature is that a long hole for allowing the transmission member to relatively rotate by the first set rotation angle and through which the collar is inserted is provided.

  The third feature of the present invention is that, in addition to the configuration of the first or second feature, the turbine runner is fixed to the spring holder.

  In addition to the configuration of the first or second feature, the fourth feature of the present invention is that the turbine runner is fixed to the output hub.

  Further, according to the present invention, in addition to the configuration of the first or second feature, an engagement member fixed to the turbine runner is engaged with either the spring holder or the output member so as not to be relatively rotatable. This is the fifth feature.

  According to the first aspect of the present invention, the transmission member supported by the clutch member with the first damper spring interposed between the clutch member and the output member according to the relative rotation of the spring holder and the output member. Since the relative rotation with respect to the spring holder is disabled through at least one of the pair of holding plates constituting the spring holder, the spring holder and the output member are relatively rotated by the second set rotation angle. Thus, the structure for improving the life of the second damper spring by operating the second damper spring only can be configured without increasing the thickness of the holding plate, and an increase in the weight of the spring holder can be avoided. At the same time, the axial size of the spring holder and thus the torque converter can be reduced. In addition, since the transmission member is supported by the clutch member, a relatively large space can be secured between the lock-up clutch and the turbine runner, and the space is attenuated without increasing the axial dimension of the torque converter. It is also possible to arrange an additional damping device for improving the performance.

  According to the second feature of the present invention, the retainer having the first spring contact portion that contacts the one end portion of the first damper spring is fixed to the clutch member with a collar interposed between the retainer and the clutch member, A support plate portion that is a part of a transmission member having a second spring contact portion that contacts the other end portion of the 1 damper spring is disposed so as to be capable of relative rotation between the clutch member and the retainer, and the collar is the support plate portion Since it is inserted through the long hole provided in the clutch member, only the relative rotation of the transmission member with respect to the clutch member at the first set rotation angle is possible, and the structure for improving the life of the first damper spring can be made compact. .

  According to the third feature of the present invention, the inertial mass of the spring holder and the transmission member constituting the power transmission system between the first and second damper springs can be increased by fixing the turbine runner to the spring holder. And the damping performance is further improved.

  According to the fourth aspect of the present invention, the turbine runner is fixed to the output hub, thereby contributing to improvement in damping performance when the inertia mass on the output side is relatively small.

  Further, according to the fifth feature of the present invention, the engaging member fixed to the turbine runner is engaged with either the spring holder or the output member so as not to be relatively rotatable. With this configuration, it can be added to the spring holder and the transmission member or the output member constituting the power transmission system between the first and second damper springs.

It is a longitudinal section of the torque converter of a 1st embodiment. It is sectional drawing which follows the 2-2 line | wire of FIG. 1 when a lockup clutch is in a non-connection state. It is a cross-sectional view showing the relative positions of the clutch piston, the retainer, the transmission member, and the output member in a state where the lockup clutch is connected and the second damper spring is compressed to the maximum, with the spring holder omitted. FIG. 4 is a cross-sectional view corresponding to FIG. 3 in a state in which the first damper spring is compressed to the maximum extent. It is a graph which shows the damper characteristic in a lockup clutch connection state. It is a longitudinal cross-sectional view of the torque converter of 2nd Embodiment. It is a longitudinal cross-sectional view of the torque converter of 3rd Embodiment. It is a longitudinal cross-sectional view of the torque converter of 4th Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  A first embodiment of the present invention will be described with reference to FIGS. 1 to 5. First, in FIG. 1, the torque converter includes a pump impeller 11 and a turbine runner disposed to face the pump impeller 11. 12A and a stator 13 disposed between the pump impeller 11 and the inner peripheral portion of the turbine runner 12A, and the pump impeller 11, the turbine runner 12A, and the stator 13 are indicated by an arrow 14 as shown in FIG. A 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 that connects the pump blades 17, and an inner portion of the pump shell 16. A pump hub 19 fixed to the peripheral portion by welding, for example, is provided, and an oil pump (not shown) that supplies hydraulic oil to the torque converter is linked and connected to the pump hub 19.

  A flange-shaped transmission cover 20 that covers the turbine runner 12A from the outside is joined to the outer peripheral portion of the pump shell 16 by welding, and a ring gear 21 is fixed to the outer peripheral portion of the transmission cover 20 by welding. A drive plate (not shown) connected to the crankshaft of the engine is fastened to the ring gear 21, and rotational power is input to the pump impeller 11 from the engine.

  The turbine runner 12 </ b> A includes a bowl-shaped turbine shell 22 </ b> A, a plurality of turbine blades 23 provided on the inner surface of the turbine shell 22 </ b> A, and a turbine core ring 24 that connects the turbine blades 23.

  The end portion of the output shaft 26 that transmits the rotational power from the engine to a transmission (not shown) is connected to the bottomed cylindrical support tube portion 20a that the transmission cover 20 integrally has at the center thereof via a bearing bush 27. Supported. The output shaft 26 is splined to an output hub 25A disposed at a position spaced apart from the pump hub 19 in the axial direction, and a needle thrust bearing is provided between the output hub 25A and the transmission cover 20. 28 is interposed.

  The stator 13 includes a stator hub 29 disposed between the pump hub 19 and the output hub 25A, a plurality of stator blades 30 provided on the outer periphery of the stator hub 29, and a stator core ring 31 that connects the outer periphery of the stator blades 30. A thrust bearing 32 is interposed between the pump hub 19 and the stator hub 29, and a thrust bearing 33 is interposed between the output hub 25A and the stator hub 29.

  A one-way clutch 35 is interposed between the stator hub 29 and a stator shaft 34 that surrounds the output shaft 26 that rotates together with the output hub 25A in a relatively rotatable manner. A case (not shown) is supported 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 22A. The clutch chamber 38 is fixed to the outer periphery of the lockup clutch 40 and the output hub 25A. A disc-shaped output member 41A and a spring holder 42A coupled to the output member 41A while allowing relative rotation within a limited range are accommodated.

  The lock-up clutch 40 has a clutch piston 43 that is a clutch member that can be frictionally connected to the transmission cover 20, and is in a connected state in which the clutch piston 43 is frictionally connected to the transmission cover 20 and in a disconnected state in which the friction connection is released. The state can be switched, and the inner peripheral portion of the clutch piston 43 formed in a disc shape is supported by the output hub 25A so as to be slidable in an axial direction.

  The clutch chamber 38 is partitioned by the clutch piston 43 into an inner chamber 38a on the turbine runner 12A side and an outer chamber 38b on the transmission cover 20 side, adjacent to the needle thrust bearing 28. An oil groove 44 formed in the output hub 25A communicates with the outer chamber 38b, and the oil groove 44 communicates with the cylindrical output shaft 26. An oil passage 45 communicating with the inner periphery of the circulation circuit 15 is formed between the pump hub 19 and the stator shaft 34. The oil pump 44 and the oil reservoir (not shown) are alternately connected to the oil groove 44 and the oil passage 45.

  Referring also to FIG. 2, the clutch piston 43 of the lockup clutch 40 holds a coil-shaped first damper spring 46, and the spring holder 42A has the spring holder 42A and the output member 41A. A coiled second damper spring 47 interposed therebetween is held.

  A plurality of, for example, four first damper springs 46 are held on the clutch piston 43. An annular housing recess 48 is formed on the surface of the outer periphery of the clutch piston 43 opposite to the transmission case 20, and is accommodated in the housing recess 48 at equal intervals in the circumferential direction. A retainer 49 that holds the damper spring 46 between the clutch piston 43 is fixed to the clutch piston 43.

  The retainer 49 has an outer periphery substantially corresponding to the inner periphery of the housing recess 48 and is arranged coaxially with the clutch piston 43, and the first damper along the radial direction of the clutch piston 43. It is formed in an arc shape in cross section so as to cover the inner side of the spring 46, and is continuously provided at four locations at equal intervals in the circumferential direction of the outer periphery of the ring plate portion 49a and in the circumferential direction of the clutch piston 43. A spring cover portion 49b that is formed long along the spring cover portion 49b and a first spring contact portion 49c that is disposed between the spring cover portions 49b and that is continuous with the outer periphery of the ring plate portion 49a. It is formed.

  A cylindrical first collar 50 is interposed between the ring plate portion 49a and the clutch piston 43 at a plurality of, for example, eight places spaced apart in the circumferential direction of the clutch piston 43. The ring plate portion 49 a of the retainer 49 is fixed to the clutch piston 43 via the first collar 50 by first rivets 51 that respectively penetrate the first collar 50.

  The first spring contact portion 49c of the retainer 49 is disposed between the four first damper springs 46. When the lock-up clutch 40 is in a disconnected state, the first spring contact portion 49c is disposed between the four first damper springs 46. The contact portion 49c contacts the end portions of the first damper springs 46 on both sides thereof.

  The inner peripheral portion of the output member 41A is fixed to the outer periphery of the output hub 25A by welding or the like, and the spring holder 42A has a pair of holding plates 52A and 53A that sandwich the output member 41A from both sides in the axial direction. Configured as follows. Between the pair of holding plates 52A and 53A, second cylindrical shapes are respectively inserted through first elongated holes 54 provided at reciprocal locations, for example, six locations, spaced equidistantly in the circumferential direction of the output member 41A. The holding plate 52A, 53A having a second collar 55 interposed therebetween, and the holding plate arranged on the turbine runner 12A side of the holding plates 52A, 53A. The turbine shell 22 </ b> A having an inner peripheral portion superimposed on 52 </ b> A is fixed by a second rivet 56 that penetrates the second collar 55. Further, the outer peripheral portions of the holding plates 52A and 53 are fastened by third rivets 66 at a plurality of locations spaced in the circumferential direction.

  That is, the turbine runner 12A is fixed to the spring holder 42A. The spring holder 42A can rotate relative to the output member 41A within a limited range in which the second collar 55 moves within the first elongated hole 54.

  Spring holding portions 52a and 53a for receiving the second damper spring 47 are provided at a plurality of, for example, eight places at equal intervals in the circumferential direction of the holding plates 52A and 53A. A spring that accommodates a part of the second spring 47 in a portion corresponding to the spring accommodating portions 52a and 53a of the output member 41A that is formed so as to face and is disposed between the holding plates 52A and 53A. The housing hole 57 is formed so that both ends of the spring housing hole 57 along the circumferential direction of the output member 41 </ b> A are in contact with both ends of the second damper spring 47 when the lockup clutch 40 is not connected. Is done.

  A transmission member 58 that interposes the first damper spring 46 between the clutch piston 43 and the clutch piston 43 is supported by the clutch piston 43 so as to be capable of relative rotation at a first set rotation angle. The transmission member 58 is in contact with the output member 41A in response to the relative rotation of the spring holder 42A and the output member 41A by a second set rotation angle smaller than the first set rotation angle. At least one of the holding plates 52A and 53A constituting the spring holder 42A, in this embodiment, is inserted into the two holding plates 52A and 53A so that relative rotation is impossible.

  The transmission member 58 is equidistant in the circumferential direction of a ring plate-like support plate portion 58a disposed between the ring plate portion 49a of the retainer 49 and the clutch piston 43 and an inner peripheral portion of the support plate portion 58a. A connecting arm portion 58b protruding toward the spring holder 42A from a plurality of locations, for example, four locations, and a second spring connected to the outer peripheral portion of the support plate portion 58a at a portion corresponding to the connecting arm portion 58b. It forms so that it may have the contact part 58c integrally.

  The second spring contact portion 58c is disposed between the first damper springs 46 in the radial direction of the transmission member 58 and outward of the first spring contact portion 49c of the retainer 49. When the up clutch 40 is in a non-connected state, it abuts with the first spring abutting portions 49c on the end portions of the first damper springs 46 on both sides of the second spring abutting portion 58c.

  A second length through which the first collar 50 is inserted into the support plate portion 58a to allow the transmission member 58 to rotate relative to the clutch piston 43 and the retainer 49 by a first set rotation angle. A hole 59 is provided.

  By the way, when the lock-up clutch 40 is in a non-connected state, the first collar 50 is at the center in the longitudinal direction of the second long hole 59. At this time, the first and second spring contact portions 49c, 58c is in contact with the ends of the first damper springs 46 on both sides thereof.

  The connecting arm portion 58b is in contact with the output member 41A in response to the relative rotation of the spring holder 42A and the output member 41A by a second set rotation angle smaller than the first set rotation angle. It is inserted into at least one of the pair of holding plates 52A and 53A so that it cannot be rotated relative to the spring holder 42A. In this embodiment, the output member 41A is spaced by 4 in the circumferential direction. A concave portion 60 extending in the circumferential direction at a location is formed so as to allow the connecting arm portion 58b to be inserted therethrough, and rectangular insertion holes 61 and 62 for allowing the connecting arm portion 58b to be inserted are provided in the holding plates 52A and 53A.

  When the engine is idling or in an extremely low speed operation region, 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 is more The pressure is higher than that of the inner chamber 38a, the clutch piston 43 is pushed away from the inner surface of the transmission cover 20, and the lockup clutch 40 is in a disconnected state. In this state, relative rotation of the pump impeller 11 and the turbine runner 12A is allowed, and the hydraulic oil in the circulation circuit 15 is pumped as indicated by an arrow 14 as the pump impeller 11 is rotationally driven by the engine. The impeller 11, the turbine runner 12A, and the stator 13 are circulated in the circulation circuit 15 in this order, and the rotational torque of the pump impeller 11 is transmitted to the output shaft 26 via the turbine runner 12A, the output member 41A, and the output hub 25A. Is done.

  In a state where a torque amplifying action is generated between the pump impeller 11 and the turbine runner 12 </ b> A, the accompanying reaction force is borne by the stator 13, and the stator 13 is fixed by the locking action of the one-way clutch 35. When the torque amplification operation is finished, the stator 13 rotates in the same direction together with the pump impeller 11 and the turbine runner 12A while idling the one-way clutch 35 by reversing the torque direction received by the stator 13.

  When such a torque converter enters a coupling state or approaches a coupling state, hydraulic oil is supplied from the oil passage 45 to the outer chamber 38b, and the hydraulic oil is led out from the oil groove 44. As described above, 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 has a higher pressure than the outer chamber 38b, and the clutch piston 43 is pressed toward the transmission cover 20 by the pressure difference, and the outer periphery of the clutch piston 43 is in the transmission case. 20 is brought into pressure contact with the inner surface of the transmission case 20 and frictionally connected to the transmission case 20 so that the lock-up clutch 40 is connected.

  When the lock-up clutch 40 is engaged and the clutch piston 43 and the retainer 49 rotate relative to the transmission member 58 in the clockwise direction of FIG. 2, as shown in FIG. The second spring abutting portion 58 c that abuts against the other end of the first damper spring 46 compresses the first damper spring 46 with the portion 49 c abutting against one end of the first damper spring 46. The spring holder 42A connected to the transmission member 58 to which power is transmitted from the first damper spring 46 so as not to rotate relative thereto compresses the second damper spring 47 with the output member 41A. And rotate relative to the transmission member 58. That is, the first damper spring 46 and the second damper spring 47 operate in series between the clutch piston 43 and the output member 41A.

  The series operation state of the first and second damper springs 46 and 47 ends when the connecting arm portion 58b that has been displaced in the recess 60 abuts against one end in the circumferential direction of the recess 60, In the next stage, as shown in FIG. 4, the first spring contact portion 49 c is kept in contact with one end portion of the first damper spring 46 and is in contact with the other end portion of the first damper spring 46. The second spring contact portion 58c moves to further compress the first damper spring 46, and the output member 41A rotates together with the transmission member 58 to which power is transmitted from the first damper spring 46. That is, only the first damper spring 46 of the first damper spring 46 and the second damper spring 47 is operated between the clutch piston 43 and the output member 41A. When the end abuts against the first collar 50, the relative rotation of the clutch piston 43 and the transmission member 58 is prevented, and the clutch piston 43 and the output member 41A are directly connected.

  That is, in the connected state of the lockup clutch 40, as shown in FIG. 5, the clutch piston 43 and the output member as the torsion angle between the pump impeller 11 and the output member 41A increases. A first transmission stage in which the first damper spring 46 and the second damper spring 47 operate in series between 41 A, and only the first damper spring 46 of the first damper spring 46 and the second damper spring 47. The clutch piston 43 and the output member 41A are directly connected through the second transmission stage in which the clutch piston 43 and the output member 41A are activated.

  Next, the operation of this embodiment will be described. The spring holder 42A is configured to have a pair of holding plates 52A and 53A that sandwich the output member 41A from both sides in the axial direction, and the first damper spring 46 is connected to the clutch piston 43. And a transmission member 58 that is supported by the clutch piston 43 so as to be capable of relative rotation at a first set rotation angle, the second of which the spring holder 42A and the output member 41A are smaller than the first set rotation angle. At least one of the pair of holding plates 52A and 53A (in this embodiment) is made incapable of relative rotation with the spring holder 42A while making contact with the output member 41A according to relative rotation by a set rotation angle. The spring holder 42A and the output member 41A are A structure for improving the life of the second damper spring 47 by operating the second damper spring 47 only during relative rotation by the set rotation angle can be configured without increasing the thickness of the holding plates 52A and 53A. Thus, an increase in the weight of the spring holder 42A can be avoided, and the spring holder 42A and thus the torque converter can be reduced in the axial direction. Moreover, since the transmission member 58 is supported by the clutch piston 43, a relatively large space can be secured between the lockup clutch 40 and the turbine runner 12A, and without increasing the axial dimension of the torque converter, It is also possible to arrange an additional vibration control device for improving the damping performance in the space.

  A retainer 49 having a first spring abutting portion 49 c that holds the first damper spring 46 between the clutch piston 43 and abuts against one end of the first damper spring 46 is provided between the clutch piston 43 and the clutch piston 43. The transmission member 58 is fixed to the clutch piston 43 with a cylindrical first collar 50 interposed therebetween, and the transmission member 58 is disposed between the clutch piston 43 and the retainer 49, and the first damper. A second spring contact portion 58c protruding from the support plate portion 58a so as to contact the other end portion of the spring 46 is integrally formed. The support plate portion 58a includes the clutch piston 43 and The transmission member 58 can be rotated relative to the retainer 49 by the first set rotation angle so that the first coupling can be performed. Since the second long hole 59 through which the first through hole 50 is inserted is provided, only the relative rotation of the transmission member 58 with respect to the clutch piston 43 at the first set rotation angle is possible, and the life of the first damper spring 46 is improved. Can be configured compactly.

  Further, since the turbine runner 12A is fixed to the spring holder 42A, the inertia mass of the spring holder 42A and the transmission member 58 constituting the power transmission system between the first and second damper springs 46 and 47 can be increased. Damping performance is further improved.

  A second embodiment of the present invention will be described with reference to FIG. 6, but the parts corresponding to the first embodiment are only given the same reference numerals, and the detailed description will be given. Omitted.

  The torque converter includes a pump impeller 11, a turbine runner 12 </ b> A disposed to face the pump impeller 11, and a stator 13 disposed between the pump impeller 11 and the inner peripheral portion of the turbine runner 12 </ b> A.

  The end of the output shaft 26 is supported via a bearing bush 27 on a bottomed cylindrical support cylinder 20a integrally formed in the center of the transmission cover 20, and the output shaft 26 is splined to the output hub 25B. Is done.

  The disc-shaped output member 41B is fixed to the outer periphery of the output hub 25B, and the spring holder 42B is connected to the output member 41B while allowing relative rotation within a limited range. The clutch piston 43 of the lockup clutch 40 holds a coiled first damper spring 46, and the spring holder 42B has a coiled first damper interposed between the spring holder 42B and the output member 41B. 2 The damper spring 47 is held.

  The inner peripheral portion of the output member 41B is fixed to the outer periphery of the output hub 25B by welding or the like, and the spring holder 42B has a pair of holding plates 52B and 53B that sandwich the output member 41B from both sides in the axial direction. The inner peripheral portion of the turbine shell 22A of the turbine runner 12A is fixed to the flange portion 25a provided on the outer periphery of the output hub 25B and projecting radially outward by a fourth rivet 63. .

  A transmission member 58 that interposes the first damper spring 46 between the clutch piston 43 and the clutch piston 43 is supported by the clutch piston 43 so as to be capable of relative rotation at a first set rotation angle. The connecting arm portion 58b which the transmission member 58 has integrally with the output member 41B in response to the relative rotation of the spring holder 42B and the output member 41B by a second set rotation angle smaller than the first set rotation angle. While being in contact with each other, at least one of the holding plates 52B and 53B constituting the spring holder 42B, in this embodiment, is inserted into the two holding plates 52B and 53B so that relative rotation is impossible, and the outer periphery of the output member 41B At four locations spaced in the circumferential direction, recesses 60 through which the connecting arm portions 58b are inserted are formed so as to extend long in the circumferential direction.

  According to the second embodiment, similarly to the first embodiment, the structure for improving the life of the second damper spring 47 is configured without increasing the thickness of the holding plates 52B and 53B. Thus, an increase in the weight of the spring holder 42B can be avoided, and the spring holder 42B and thus the torque converter can be reduced in the axial direction. Moreover, since the transmission member 58 is supported by the clutch piston 43, a relatively large space can be secured between the lockup clutch 40 and the turbine runner 12A, and without increasing the axial dimension of the torque converter, It is also possible to arrange an additional vibration control device for improving the damping performance in the space.

  Further, by fixing the turbine runner 12A to the output hub 25B, it is possible to contribute to an improvement in damping performance when the inertial mass of the output side, that is, the mission side rotating member is relatively small.

  A third embodiment of the present invention will be described with reference to FIG. 7, but the portions corresponding to the first and second embodiments are only shown with the same reference numerals and shown in detail. Detailed explanation is omitted.

  The torque converter includes a pump impeller 11, a turbine runner 12B arranged to face the pump impeller 11, and a stator 13 arranged between the pump impeller 11 and the inner peripheral portion of the turbine runner 12B.

  The end of the output shaft 26 is supported via a bearing bush 27 on a bottomed cylindrical support cylinder portion 20a which the transmission cover 20 has integrally in the center thereof, and the output shaft 26 is splined to the output hub 25A. Is done.

  A disc-shaped output member 41A is fixed to the outer periphery of the output hub 25A, and a spring holder 42C coupled to the output member 41A while allowing relative rotation within a limited range is not relatively rotatable with respect to the turbine runner 12B. Connected to The clutch piston 43 of the lockup clutch 40 holds a coiled first damper spring 46, and the spring holder 42C has a coiled first damper interposed between the spring holder 42C and the output member 41A. 2 The damper spring 47 is held.

  The inner peripheral portion of the output member 41A is fixed to the outer periphery of the output hub 25A by welding or the like, and the spring holder 42C has a pair of holding plates 52C and 53B that sandwich the output member 41A from both sides in the axial direction. Of the pair of holding plates 52C and 53B, the outer peripheral portion of the holding plate 52C disposed on the turbine runner 12B side is formed to protrude radially outward from the outer periphery of the other holding plate 53B. Is done.

  An engaging member 64A is fixed to the outer peripheral portion of the turbine shell 22B in the turbine runner 12B by welding, and the engaging member 64A is provided at a plurality of locations spaced in the circumferential direction of the outer peripheral portion of the holding plate 52C. The engaging recess 65 is formed so as not to be relatively rotatable.

  The clutch piston 43 is supported by a transmission member 58 for interposing the first damper spring 46 between the clutch piston 43 and the clutch piston 43 so as to allow relative rotation at a first set rotation angle. The transmission arm 58 integrally has a connecting arm portion 58b that is connected to the output member 41A in response to the relative rotation of the spring holder 42C and the output member 41A by a second set rotation angle smaller than the first set rotation angle. While making contact, at least one of the holding plates 52C and 53B constituting the spring holder 42C, in this embodiment, is inserted into the two holding plates 52C and 53B so that relative rotation is impossible.

  According to the third embodiment, as in the first and second embodiments, the structure for improving the life of the second damper spring 47 is made thicker in the holding plates 52C and 53B. The weight of the spring holder 42C can be avoided, and the spring holder 42C and thus the torque converter can be reduced in the axial direction. Moreover, since the transmission member 58 is supported by the clutch piston 43, a relatively large space can be secured between the lockup clutch 40 and the turbine runner 12B, and without increasing the axial dimension of the torque converter, It is also possible to arrange an additional vibration control device for improving the damping performance in the space.

  In addition, since the engaging member 64A fixed to the turbine runner 12B is engaged with the spring holder 42C so as not to rotate relative thereto, the inertia mass of the turbine runner 12B can be set to the first and second damper springs 46, 47 with a simple configuration. It can be added to the spring holder 42C and the transmission member 58 constituting the power transmission system between them.

  A fourth embodiment of the present invention will be described with reference to FIG. 8, but the parts corresponding to the first to third embodiments are indicated by the same reference numerals and shown in detail. Detailed explanation is omitted.

  The torque converter includes a pump impeller 11, a turbine runner 12B arranged to face the pump impeller 11, and a stator 13 arranged between the pump impeller 11 and the inner peripheral portion of the turbine runner 12B.

  The end of the output shaft 26 is supported via a bearing bush 27 on a bottomed cylindrical support cylinder portion 20a which the transmission cover 20 has integrally in the center thereof, and the output shaft 26 is splined to the output hub 25A. Is done.

  A disc-shaped output member 41C is fixed to the outer periphery of the output hub 25A, and a spring holder 42D is connected to the output member 41C while allowing relative rotation within a limited range. The clutch piston 43 of the lockup clutch 40 holds a coiled first damper spring 46, and the spring holder 42D has a coiled first damper interposed between the spring holder 42D and the output member 41C. 2 The damper spring 47 is held.

  The inner peripheral portion of the output member 41C is fixed to the outer periphery of the output hub 25A by welding or the like, and the spring holder 42D has a pair of holding plates 52D and 53C that sandwich the output member 41C from both sides in the axial direction. The engaging protrusions 67 projecting radially outward from the outer periphery of the holding plates 52D and 53C are integrally projected at a plurality of locations spaced in the circumferential direction of the outer periphery of the output member 41C. Established.

  An engaging member 64B is fixed to the outer peripheral portion of the turbine shell 22B in the turbine runner 12B by welding, and a plurality of the engaging members 64B are spaced in the direction of the peripheral member of the outer periphery of the output member 41C. A plurality of locking recesses 68 are formed for engaging the engaging protrusions 67 protruding at the locations so as not to be relatively rotatable. That is, the engaging member 68B is engaged with the output member 41C so as not to be relatively rotatable.

  The clutch piston 43 is supported by a transmission member 58 for interposing the first damper spring 46 between the clutch piston 43 and the clutch piston 43 so as to allow relative rotation at a first set rotation angle. The connecting arm portion 58b which the transmission member 58 integrally has is connected to the output member 41C according to the relative rotation of the spring holder 42D and the output member 41C by a second set rotation angle smaller than the first set rotation angle. While making contact, at least one of the holding plates 52D and 53C constituting the spring holder 42B, in this embodiment, the two holding plates 52D and 53C are inserted into the two holding plates 52D and 53C so that relative rotation is impossible. The output member 41C is formed with a through hole 69 through which the connecting arm portion 58b is inserted so as to extend in the circumferential direction.

  According to the fourth embodiment, as in the first to third embodiments, the structure for improving the life of the second damper spring 47 is made thicker in the holding plates 52D and 53C. The weight of the spring holder 42D can be avoided, and the spring holder 42D and thus the torque converter can be reduced in the axial direction. Moreover, since the transmission member 58 is supported by the clutch piston 43, a relatively large space can be secured between the lockup clutch 40 and the turbine runner 12B, and without increasing the axial dimension of the torque converter, It is also possible to arrange an additional vibration control device for improving the damping performance in the space.

  Further, since the engaging member 64B fixed to the turbine runner 12B is engaged with the output member 41C so as not to be relatively rotatable, the inertial mass of the turbine runner 12B can be added to the output member 41C with a simple configuration.

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

11 ... pump impellers 12A, 12B ... turbine runner 13 ... stator 20 ... transmission cover 40 ... lock-up clutches 41A, 41B, 41C ... output members 42A, 42B, 42C, 42D ..Spring holder 43 ... Clutch piston 46 as clutch member ... First damper spring 47 ... Second damper spring 49 ... Retainer 49c ... First spring contact portion 50 ... Color 52A, 52B, 52C, 52D, 53A, 53B, 53C ... Holding plate 58 ... Transmission member 58a ... Support plate 58c ... Second spring contact portion 59 ... Slot

Claims (5)

  A pump impeller (11) to which a transmission cover (20) is liquid-tightly coupled, a turbine runner (12A, 12B) disposed opposite to the pump impeller (11), the pump impeller (11), and the turbine A stator (13) disposed between the inner peripheral portions of the runners (12A, 12B), an output member (41A, 41B, 41C) fixed to the output hub (25A, 25B) rotating together with the output shaft (26) A clutch member (43) that can be frictionally connected to the transmission cover (20), and a clutch member (43) that is frictionally connected to the transmission cover (20) and a non-connection state that releases the frictional connection. A lock-up clutch (40) that can be switched, and a spring holder that can rotate relative to the output members (41A to 41C) 2A, 42B, 42C, 42D), the first damper spring (46) held by the lock-up clutch (40), and the output member (41A-41C) and the spring holder (42A-42D). A second damper spring (47) that is mounted and held by the spring holder (42A to 42D), and in the connected state of the lockup clutch (40), the pump impeller (11) and the output member ( 41A to 41C), the first damper spring (46) and the second damper spring between the clutch member (43) and the output members (41A to 41C) in accordance with an increase in the twisting angle between them. A first transmission stage (47) operating in series, the first damper spring (46) and the second damper; Of the ring (47), only the first damper spring (46) is sequentially subjected to the second transmission stage in which the clutch member (43) and the output members (41A to 41C) are activated, and the clutch member (43 ) And the output member (41A to 41C) are directly connected to each other, the spring holder (42A to 42D) is a pair of holding plates that sandwich the output member (41A to 41C) from both sides in the axial direction. 52A to 52D; 53A, 53B, 53C), and the first damper spring (46) is interposed between the clutch member (43) and the first set rotation angle can be relatively rotated. The transmission member (58) supported by the clutch member (43) includes the spring holder (42A to 42D) and the output member. The spring holders (42A to 41C) are brought into contact with the output members (41A to 41C) in response to the relative rotation of the force members (41A to 41C) by a second set rotation angle smaller than the first set rotation angle. 42D) is made impossible to rotate relative to 42D) and is inserted into at least one of the pair of holding plates (52A to 52D; 53A to 53C).   A retainer (49) having a first spring contact portion (49c) that holds the first damper spring (46) between the clutch member (43) and abuts against one end portion of the first damper spring (46). Is fixed to the clutch member (43) with a cylindrical collar (50) interposed between the clutch member (43), and the transmission member (58) is connected to the clutch member (43) and the retainer. (49) and a second spring contact portion projecting from the support plate portion (58a) so as to contact the other end portion of the first damper spring (46). (58c) are integrally formed, and the transmission member (58) is formed on the support plate portion (58a) with respect to the clutch member (43) and the retainer (49) in the first set rotation. Corner The torque converter of claim 1, wherein a long hole for inserting the collar (50) as allowing the relative rotation (59) is provided only.   The torque converter according to claim 1 or 2, wherein the turbine runner (12A) is fixed to the spring holder (42A).   The torque converter according to claim 1 or 2, wherein the turbine runner (12A) is fixed to the output hub (25B).   The engagement member (64A, 64B) fixed to the turbine runner (12B) is engaged with either one of the spring holder (42C) and the output member (41C) so as not to be relatively rotatable. The torque converter according to claim 1 or 2.

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