JP2010144836A - Hydraulic transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic transmission device improving vibration reduction performances. <P>SOLUTION: This device includes a damper means 20 relatively rotatably connecting a first member 10 and a second member 30 through an elastic body 21 and transmitting drive force transmitted to the first member 10 form a drive source to the second member 30 through the elastic body 21, a hydraulic transmission means 40 provided at an opposite side to the damper means 20 over the second member 30 with respect to an axial direction of an output shaft 60 and transmitting drive force transmitted to the second member 30 to the output shaft 60 through working medium, and a reaction force means 100 applying reaction force F1 equivalent to pressing force F0 from the damper means 20 to the hydraulic transmission means 40 on which pressing force F0 to the damper means 20 side along an axial direction by pressure of working medium acts. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a fluid transmission device, and more particularly to a fluid transmission device capable of transmitting a driving force generated by a driving source via a working fluid.

  2. Description of the Related Art Conventionally, some automatic transmissions mounted on vehicles and the like use, for example, a torque converter as a fluid transmission device in order to smoothly shift a change in operating state such as start and stop. Such a torque converter includes, for example, a fluid transmission mechanism, a lockup clutch mechanism, and a damper mechanism. The torque converter transmits the driving force transmitted from the driving source to the front cover when the lockup clutch is turned off to the output shaft (for example, the input shaft of the transmission) via the working oil as the working fluid in the fluid transmission mechanism. On the other hand, the driving force transmitted to the front cover when the lock-up clutch is ON is transmitted directly to the output shaft via the engagement member of the lock-up clutch mechanism and not via the working fluid in the fluid transmission mechanism. At this time, the damper mechanism performs vibration reduction during driving force transmission.

  As such a conventional fluid transmission device, for example, a torque converter to which the lockup damper device described in Patent Document 1 is applied is a one-way clutch and a damper that idle when a damper spring of the lockup damper device is compressed and deformed. It is composed of a sliding member that generates sliding friction when the spring is extended, and is equipped with a damping mechanism that straddles between the input member and the output member, thereby reducing the impact torque and suppressing the occurrence of judder vibration. ing.

JP 2008-180305 A

  By the way, as the conventional fluid transmission device as described above, the damper mechanism provided on the opposite side of the front cover from the fluid transmission mechanism which is the main body of the torque converter, that is, between the drive source and the front cover. Some are provided with a so-called pre-damper mechanism. In a fluid transmission device having such a pre-damper mechanism, for example, in order to further improve fuel efficiency by expanding the rotation speed region in which the lockup clutch can be turned on by suppressing the occurrence of vibrations such as booming noise. Further reduction of vibration has been desired.

  Then, an object of this invention is to provide the fluid transmission apparatus which can improve vibration reduction performance.

  In order to achieve the above object, a fluid transmission device according to the present invention connects a first member and a second member through an elastic body so as to be relatively rotatable, and transmits a driving force transmitted from a driving source to the first member. Damper means capable of being transmitted to the second member via the elastic body, and provided on the opposite side of the damper means across the second member with respect to the axial direction of the output shaft and transmitted to the second member A fluid transmission means capable of transmitting the driving force to the output shaft via a working medium, and a fluid transmission means on which a pressing force toward the damper means along the axial direction acts due to the pressure of the working medium. Reaction force means for applying a reaction force equivalent to the pressing force from the damper means side.

  Further, in the fluid transmission device, the reaction force means is a reaction force that is provided on the damper means side of the second member with respect to the axial direction and causes the reaction force to be applied by pressure of a working medium supplied to the inside. It is preferable to have a pressure chamber.

  In the fluid transmission device, the fluid transmission means supplies or discharges the working medium through a supply / discharge opening provided on the fluid transmission means side of the second member with respect to the axial direction. In addition, the pressing force is applied by the pressure of the working medium acting on the pressing force acting surface opposite to the supply / discharge opening with respect to the axial direction, and the reaction force means is the reaction force pressure chamber in the reaction force pressure chamber. The area of the reaction force acting surface on which the reaction force due to the pressure of the working medium acts is set equal to the area of the supply / discharge opening, and the reaction force pressure chamber communicates with the fluid transmission means side of the second member. It is preferable to do.

  Further, in the fluid transmission device, the reaction force means includes the first member or the member of the damper means that rotates together with the first member, and the member of the damper means that rotates together with the second member or the second member. It is preferable to have a reaction force bearing portion that supports the two in a relatively rotatable manner.

  In the fluid transmission device, the holding member that rotates together with the second member and holds the elastic body of the damper means is connected to the second member at a radially outer end with respect to a radial direction orthogonal to the axial direction. In addition, a strength member may be extended radially inward from a radially inner end with respect to the radial direction, and a radially inner end of the strength member may be connected to a radially central portion of the second member. preferable.

  Further, in the above fluid transmission device, the damper means includes a center holding member that holds the elastic body, and the elastic body on a side opposite to the second member of the center holding member with respect to the axial direction. A first side holding member that holds the elastic body, a second side holding member that holds the elastic body on a side of the center holding member on the second member side with respect to the axial direction, and a center holding member It is preferable to have sealing means for preventing leakage of lubricant through the space between the first side holding member and the second side holding member on the outside in the radial direction.

  According to the fluid transmission device of the present invention, a reaction force equivalent to this pressing force is applied from the damper means side to the fluid transmission means in which the pressing force to the damper means side along the axial direction acts by the pressure of the working medium. Since the reaction force means is provided, fluctuations in the axial position of the fluid transmission means can be prevented, so that proper performance of the damper means can be ensured and vibration reduction performance can be improved.

  Hereinafter, an embodiment of a fluid transmission device according to the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily replaced by those skilled in the art or those that are substantially the same. In the following embodiment, an engine such as a gasoline engine, a diesel engine, or an LPG engine is used as a driving source for generating a driving force transmitted to the fluid transmission device. However, the present invention is not limited to this, and a motor or the like. These motors may be used as a drive source or in combination with an electric motor such as a motor.

(Embodiment 1)
FIG. 1 is a cross-sectional view of a main part of a torque converter according to Embodiment 1 of the present invention. In the following description, unless otherwise specified, a direction along the rotation axis X of the output shaft 60 is referred to as an axial direction, and a direction orthogonal to the rotation axis X, that is, a direction orthogonal to the axial direction is referred to as a radial direction. The direction around the rotation axis X is called the circumferential direction. Further, in the radial direction, the rotation axis X side is referred to as a radial inner side, and the opposite side is referred to as a radial outer side. Also, the side where the driving source is provided in the axial direction (the side where the driving force is input from the driving source) is referred to as the engine side, and the opposite side, that is, the side where the transmission is provided (the side where the driving force is output to the transmission). It is called the output shaft side.

  Here, the output shaft 60 is, for example, an input shaft of a transmission (transmission) arranged on the output shaft side.

  As shown in FIG. 1, a torque converter 1 as a fluid transmission device according to the first embodiment includes a drive plate 10 as a first member, a pre-damper mechanism 20 as a damper means, and a front cover 30 as a second member. A fluid transmission mechanism 40 as fluid transmission means, a lockup clutch mechanism 50 as lockup means, and an output shaft 60. Further, the torque converter 1 of the present embodiment also includes an inner damper mechanism 70 separately from the pre-damper mechanism 20. The torque converter 1 includes a drive plate 10, a pre-damper mechanism 20, a front cover 30, a lock-up clutch mechanism 50, an inner damper mechanism 70, and a fluid transmission mechanism 40 in the axial direction from the engine side to the output shaft side. Arranged in order.

  The torque converter 1 transmits the driving force transmitted from the driving source to the drive plate 10 to the front cover 30 via the pre-damper mechanism 20, and transmits the driving force from the front cover 30 to the fluid transmission mechanism 40 or the lockup clutch mechanism 50. Is. The torque converter 1 transmits the driving force transmitted to the fluid transmission mechanism 40 to the output shaft 60 via hydraulic oil as a working medium inside the fluid transmission mechanism 40, while being transmitted to the lockup clutch mechanism 50. The driving force is transmitted to the output shaft 60 via the lock-up piston 51 as an engaging member and the inner damper mechanism 70.

  That is, the torque converter 1 of the present embodiment is a so-called pre-damper mechanism 20 provided between the crankshaft 80 and the front cover 30 as a drive source output shaft of an engine that is a drive source in the axial direction. This is a pre-damper type torque converter. That is, the pre-damper mechanism 20 connects the drive plate 10 and the front cover 30 via a plurality of damper springs 21 as a plurality of elastic bodies.

The torque converter 1 is configured such that the pre-damper mechanism 20 is disposed on the downstream side of the drive plate 10 and the upstream side of the front cover 30 with respect to the direction in which the driving force is transmitted from the drive source. The balance between the inertial mass on the drive side (engine side) upstream from the spring 21 and the inertial mass on the driven side (output shaft (transmission) side) downstream from the damper spring 21 can be optimized. In other words, the torque converter 1 can optimize the balance between the inertial mass on the driving side and the inertial mass on the driven side, so that the resonance point between the driving side and the driven side can be lowered to effectively resonate. Therefore, it is possible to improve the damper performance such as prevention of the generation of a booming noise of the pre-damper mechanism 20. That is, since the vibration reduction performance can be improved, it is possible to suppress the occurrence of a booming noise and the like, and it is possible to expand the rotation speed region in which the lock-up clutch mechanism 50 can be turned on. In addition, since the lock-up clutch mechanism 50 can be turned on in the low rotational speed region, fuel efficiency can be improved.
Hereinafter, each structure of the torque converter 1 is demonstrated concretely.

  The drive plate 10 is a first member and transmits a driving force of an engine (not shown) as a driving source. The drive plate 10 is formed in an annular plate shape that is coaxial with the rotation axis X that is the central axis of the output shaft 60. The drive plate 10 is fixed to a crankshaft 80 that is a drive source output shaft of an engine (not shown) by a fixing member, for example, a bolt 81, on the radially inner end side. That is, a bolt hole 81a is formed in the end surface of the crankshaft 80, and the bolt 81 is inserted into a through hole 81b formed in the radially inner end of the drive plate 10, and the bolt 81 is a bolt hole. The crankshaft 80 is fastened by being screwed to 81a.

  Here, the crankshaft 80 can rotate relative to the output shaft 60 about the rotation axis X of the output shaft 60. That is, the drive plate 10 is fixed to the crankshaft 80 and can rotate integrally with the crankshaft 80 about the rotation axis X. Therefore, the driving force of the engine is transmitted from the crankshaft 80 to the drive plate 10 via the bolts 81. The drive plate 10 is provided with a so-called startering gear 82 at the radially outer end.

  The pre-damper mechanism 20 is damper means, and is provided on one side of the front cover 30 with respect to the axial direction, that is, on the engine side (crankshaft 80 side). The pre-damper mechanism 20 connects the drive plate 10 and the front cover 30 via a plurality of damper springs 21 as a plurality of elastic bodies. More specifically, the pre-damper mechanism 20 connects the drive plate 10 and the front cover 30 via a plurality of damper springs 21 so as to be relatively rotatable.

  The pre-damper mechanism 20 includes a plurality of damper springs 21 as a plurality of elastic bodies and a holding member 22. The holding member 22 of the present embodiment holds a plurality of damper springs 21, and includes a center holding plate 23 as a center holding member, a first side holding plate 24 as a first side holding member, and a second And a second side holding plate 25 as a side holding member. In the holding member 22 of this embodiment, the drive plate 10 described above is also used as the center holding plate 23. That is, the drive plate 10 is also a center holding plate 23 that constitutes a part of the pre-damper mechanism 20.

  The pre-damper mechanism 20 includes a first side holding plate 24, a drive plate 10 also used as a center holding plate 23, a plurality of damper springs 21, and a second side from the engine side to the output shaft side in the axial direction. The holding plates 25 are arranged in the order.

  The plurality of damper springs 21 are, for example, a plurality of coil springs. The damper spring 21 transmits the driving force transmitted to the drive plate 10 also serving as the center holding plate 23 to the first side holding plate 24 and the second side holding plate 25.

  The center holding plate 23, the first side holding plate 24, and the second side holding plate 25 hold the plurality of damper springs 21 and are formed in an annular plate shape coaxial with the rotation axis X. The center holding plate 23, the first side holding plate 24, and the second side holding plate 25 are disposed between the engine (not shown) and a front cover 30 described later in the axial direction.

  As described above, the center holding plate 23 also serves as the drive plate 10 as the first member, and can rotate integrally with the crankshaft 80 about the rotation axis X. That is, the drive plate 10 also functions as a center holding plate 23 that holds the plurality of damper springs 21. The center holding plate 23 may be formed by a member that is formed separately from the drive plate 10 and rotates integrally with the drive plate 10.

  As described above, the drive plate 10 that is also used as the center holding plate 23 is formed in an annular plate shape that is coaxial with the rotation axis X, and the radially inner end thereof is fixed to the crankshaft 80. Further, the center holding plate 23 (drive plate 10) has a center holding portion 23a at the radially outer end.

  The center holding part 23 a holds a part of the plurality of damper springs 21 in the center holding plate 23. The center holding portion 23 a is a slit formed in an arc shape along the circumferential direction of the center holding plate 23. The center holding portion 23 a holds the damper spring 21 with the damper spring 21 inserted therein. A plurality of center holding portions 23a are formed at equal intervals in the circumferential direction with respect to the center holding plate 23, and the damper springs 21 are held in each.

  Each center holding portion 23a has a circumferential length set to a length that can hold the damper spring 21 in a biased state. Therefore, when the damper spring 21 is held by the center holding portion 23a, both end portions in the circumferential direction of the center holding portion 23a come into contact with both end portions of the damper spring 21, respectively. That is, the damper spring 21 is in contact with both ends in the circumferential direction of each center holding portion 23a and is held in a state of being biased between the both ends.

  Therefore, the drive plate 10 that is also used as the center holding plate 23 can transmit a driving force to the damper spring 21 at a circumferential end contact portion between each center holding portion 23 a and each damper spring 21. Become.

  The 1st side holding plate 24 and the 2nd side holding plate 25 hold | maintain a part of several damper spring 21 hold | maintained the axial center part by the center holding plate 23 so that a driving force can be transmitted.

  The 1st side holding plate 24 and the 2nd side holding plate 25 are each provided in the side of the center holding plate 23 with respect to the axial direction. Here, the first side holding plate 24 is provided on the side of the center holding plate 23 opposite to the front cover 30 (engine side) with respect to the axial direction, and the second side holding plate 25 is set in the axial direction. On the other hand, it is provided on the front cover 30 side (output shaft side) of the center holding plate 23. The first side holding plate 24 has a first side holding portion 24a, while the second side holding plate 25 has a second side holding portion 25a.

  Here, the second side holding plate 25 is fixed to the front cover 30 by fixing means such as welding. As a result, the second side holding plate 25 can rotate integrally with the front cover 30. The second side holding plate 25 of the present embodiment is formed of a member that is formed separately from the front cover 30 and is fixed to the front cover 30 as described above, so that the second side holding plate 25 rotates integrally with the front cover 30. Although described as an example, the front cover 30 itself may be used as the second side holding plate 25.

  The first side holding plate 24 and the second side holding plate 25 include a plurality of damper springs 21 and a center holding plate 23 in a space portion between the first side holding plate 24 and the second side holding plate 25 in the axial direction. The center holding plate 23 and the plurality of damper springs 21 are sandwiched and held. The first side holding plate 24 and the second side holding plate 25 hold the center holding plate 23 so as to be relatively rotatable with respect to both sides in the axial direction.

  Here, the first side holding plate 24 and the second side holding plate 25 are integrated with a central holding plate 23 sandwiched between connecting members, for example, bolts 26. A sleeve 27 is provided between the first side holding plate 24 and the second side holding plate 25 integrated by the bolt 26. The sleeve 27 has a cylindrical shape, and the bolt 26 is inserted into the through hole 24 b formed in the first side holding plate 24 and the sleeve 27. The bolts 26 are screwed into bolt holes 25b formed in the second side holding plate 25 to fasten and integrate the first side holding plate 24 and the second side holding plate 25 together. As a result, the first side holding plate 24 can rotate together with the second side holding plate 25 and the front cover 30.

  The sleeve 27 acts as a spacer in the axial direction between the first side holding plate 24 and the second side holding plate 25, and relative to the axial direction between the first side holding plate 24 and the second side holding plate 25. Proper positional relationship. The first side holding plate 24 and the second side holding plate 25 are assembled so as to be rotatable relative to the center holding plate 23 on both axial sides of the center holding plate 23 via the bolts 26 and the sleeves 27. Accordingly, when the first side holding plate 24, the second side holding plate 25, and the center holding plate 23 rotate relatively, a sleeve is provided between the first side holding plate 24 and the second side holding plate 25. 27 is interposed, and an appropriate clearance is secured between the first side holding plate 24, the second side holding plate 25, and the center holding plate 23, so that this relative rotation is performed smoothly.

  The bolt 26 and the sleeve 27 penetrate the center holding plate 23. However, the center holding plate 23 is formed with a slide portion 23b at the bolt 26 and sleeve 27 portions. The slide part 23 b is formed through the center holding plate 23 as an arc-shaped slit in a portion corresponding to the bolt 26 and the sleeve 27 in the center holding plate 23. The slide portion 23b is provided in an arc shape at a position where the bolt 26 and the sleeve 27 can be inserted into the axial direction. As a result, the slide portion 23b allows the first side holding plate 24, the second side holding plate 25 and the center holding plate 23 to move the bolt 26 and the sleeve 27 in accordance with the relative rotation between the first side holding plate 24 and the first side holding plate 24. The two-side holding plate 25 and the center holding plate 23 can be allowed to have a predetermined twist angle.

  The first side holding part 24a of the first side holding plate 24 and the second side holding part 25a of the second side holding plate 25 are provided by a part of each damper spring 21 in which the central part in the axial direction is held by the center holding plate 23. Contains and holds. The first side holding portion 24a is provided on the wall surface of the first side holding plate 24 that faces the center holding plate 23, that is, the wall surface on the output shaft side. The second side holding portion 25a is provided on the wall surface of the second side holding plate 25 facing the center holding plate 23, that is, the engine side wall surface.

  The first side holding portion 24a is formed by the depression of the wall surface on the output shaft side of the first side holding plate 24 on the engine side (the side opposite to the center holding plate 23 side). The first side holding portion 24 a is formed in an arc shape along the circumferential direction of the first side holding plate 24. A plurality of first side holding portions 24 a are formed at equal intervals in the circumferential direction with respect to the first side holding plate 24.

  The second side holding portion 25a is formed by recessing the engine side wall surface of the second side holding plate 25 to the output shaft side (the side opposite to the center holding plate 23 side). The second side holding portion 25 a is formed in an arc shape along the circumferential direction of the second side holding plate 25. A plurality of second side holding portions 25 a are formed at equal intervals in the circumferential direction with respect to the second side holding plate 25.

  The first side holding portions 24a and the second side holding portions 25a are both formed at positions facing the center holding portions 23a of the center holding plate 23 in the axial direction.

  Therefore, in the pre-damper mechanism 20, the center holding portion 23 a of the center holding plate 23 holds the center portion (center portion in the axial direction) of each damper spring 21, and the first side holding portion 24 a of the first side holding plate 24 The damper spring 21 receives and holds the engine side portion of the center holding portion 23a, while the second side holding portion 25a of the second side holding plate 25 receives and holds the output shaft side portion of the center holding portion 23a. To do.

  Then, both end portions in the circumferential direction of each first side holding portion 24a and each second side holding portion 25a are respectively connected to both end portions of the damper spring 21 in a state where each damper spring 21 is held in each center holding portion 23a. It faces in the circumferential direction and can be contacted. As a result, the first side holding plate 24 and the second side holding plate 25 are in contact with the damper spring 21 at the circumferential end contact portion between the first side holding portion 24a and the second side holding portion 25a and the damper spring 21. The driving force can be transmitted between them.

  That is, each damper spring 21 is held by the center holding portion 23a of the center holding plate 23, the first side holding plate 24, the first side holding portion 24a of the second side holding plate 25, and the second side holding portion 25a. The driving force can be transmitted between the holding plate 23, the first side holding plate 24, and the second side holding plate 25.

  The slide part 23b of the center holding plate 23, the through hole 24b of the first side holding plate 24, and the bolt hole 25b of the second side holding plate 25 are respectively arranged along the circumferential direction with the center holding part 23a and the first side holding. A plurality of portions 24a and second side holding portions 25a are alternately formed.

  The pre-damper mechanism 20 configured as described above transmits the driving force transmitted from the crankshaft 80 to the drive plate 10 also used as the center holding plate 23 from the circumferential end of the center holding portion 23a to the damper spring 21. To do. The pre-damper mechanism 20 transmits the driving force transmitted to the damper spring 21 to the first side holding plate 24 and the second side holding plate 25 through the circumferential ends of the first side holding portion 24a and the second side holding portion 25a. To communicate. Therefore, the first side holding plate 24 and the second side holding plate 25 are transmitted with the driving force from the engine transmitted to the drive plate 10 also serving as the center holding plate 23 via the damper spring 21, and the center holding plate. It rotates in the same direction as the drive plate 10 also used as 23. The pre-damper mechanism 20 transmits the driving force transmitted to the first side holding plate 24 and the second side holding plate 25 from the second side holding plate 25 to the front cover 30, and the front cover 30 holds the center. The drive plate 10, which is also used as the plate 23, the first side holding plate 24, and the second side holding plate 25 rotate in the same direction. Therefore, the pre-damper mechanism 20 can transmit the driving force transmitted from the engine to the drive plate 10 also used as the center holding plate 23 to the front cover 30 via the damper spring 21.

  During this time, the damper springs 21 respectively hold the first side holding plate 24 and the first side holding plate 25 in the circumferential direction of the center holding portion 23a of the center holding plate 23 that is also used as the drive plate 10 and the first side holding plate 25. It is elastically deformed according to the magnitude of the transmitted driving force while being held between the portion 24a and the circumferential end of the second side holding portion 25a.

  The front cover 30 is a second member that transmits the driving force from the pre-damper mechanism 20 and transmits the driving force transmitted from the pre-damper mechanism 20 to the fluid transmission mechanism 40 or the lockup clutch mechanism 50. is there. The front cover 30 includes a front cover main body portion 31, a front cover flange portion 32, and a front cover boss portion 33.

  The front cover body 31 is formed in a disk shape that is coaxial with the rotation axis X. The front cover main body 31 has a bulging portion 31a. The bulging portion 31a is formed such that the vicinity of the radially inner center portion of the front cover main body portion 31 protrudes toward the drive plate 10, that is, the engine side. The bulging part 31a is formed in a disk shape coaxial with the rotation axis X. The second side holding plate 25 is fixed to the radially outer end of the front cover main body 31.

  The front cover flange portion 32 is formed to protrude from the radially outer end portion of the front cover main body portion 31 toward the output shaft side. The front cover flange portion 32 is formed in a cylindrical shape coaxial with the rotation axis X.

  The front cover boss portion 33 is provided on the bulging portion 31a of the front cover main body portion 31 so as to protrude toward the drive plate 10, that is, toward the engine side. The front cover boss portion 33 is formed in a cylindrical shape coaxial with the rotation axis X. The front cover boss portion 33 is fixed to the bulging portion 31a by a fixing means such as welding. The front cover boss portion 33 is inserted into a fitting portion 81c formed on the end surface of the crankshaft 80, and is rotatably supported by, for example, a rolling bearing 83 with respect to the fitting portion 81c.

  In other words, the front cover 30 can be rotated relative to the crankshaft 80 about the rotation axis X by the front cover boss 33 being rotatably supported by the crankshaft 80 via the rolling bearing 83. Supported.

  The fluid transmission mechanism 40 is a fluid transmission means, and is provided on the other side of the front cover 30 with respect to the axial direction, that is, on the output shaft side. That is, the fluid transmission mechanism 40 is provided on the opposite side of the pre-damper mechanism 20 with the front cover 30 interposed therebetween in the axial direction. In other words, in the torque converter 1 of the present embodiment, the pre-damper mechanism 20 is provided in one space area with the front cover 30 as a boundary with respect to the axial direction, and the fluid transmission mechanism 40 is provided in the other space area. It is done.

  The fluid transmission mechanism 40 transmits the driving force transmitted to the front cover 30 to the output shaft 60 via the working fluid (hydraulic oil). The fluid transmission mechanism 40 includes a pump impeller 41, a turbine liner 42, a stator 43, a one-way clutch 44, and hydraulic oil that is a working fluid interposed between the pump impeller 41 and the turbine liner 42. .

  The pump impeller 41 transmits the driving force from the engine transmitted to the front cover 30, and transmits the transmitted driving force to the turbine liner 42 via hydraulic oil. The pump impeller 41 includes a plurality of pump blades 41a, a pump shell 41b, an inner core 41c, and a sleeve 41d. Each pump blade 41 a is a blade, and is provided at equal intervals in the circumferential direction of the torque converter 1. Each pump blade 41a has an inner core 41c attached to the inner periphery. The pump shell 41b has a ring shape coaxial with the rotation axis X and is recessed toward the output shaft. Each pump blade 41a is attached to the inner surface of the pump shell 41b formed by the recess. The pump shell 41b is fixed to the front cover 30 by fixing the radially outer end thereof to the output shaft side end of the front cover flange portion 32 of the front cover 30 by, for example, welding. That is, the pump impeller 41 rotates integrally with the front cover 30, and the driving force from the engine transmitted to the front cover 30 is transmitted to each pump blade 41a via the pump shell 41b. In the pump impeller 41, the radially inner end of the pump shell 41b is fixed to the sleeve 41d. The sleeve 41d is connected to a device that operates by rotational movement, such as an oil pump (not shown).

  The turbine liner 42 transmits the driving force from the engine transmitted from the pump impeller 41 via the hydraulic oil to the output shaft 60. The turbine liner 42 includes a turbine blade 42a, a turbine shell 42b, and an inner core 42c. Each turbine blade 42 a is a blade, and is provided at equal intervals in the circumferential direction of the torque converter 1. Each turbine blade 42a has an inner core 42c attached to the inner periphery. The turbine shell 42b is curved to the engine side in a ring shape coaxial with the rotation axis X, and each turbine blade 42a is attached to the inner surface of the curved turbine shell 42b. Here, the turbine liner 42 is disposed so as to face the pump impeller 41.

  In the turbine liner 42, the radially inner end of the turbine shell 42b is fixed to the hub 61 by, for example, rivets 61a.

  The hub 61 is a base portion of the turbine liner 42 and is disposed on the radially inner side of the turbine liner 42. The hub 61 is formed in an annular shape coaxial with the rotation axis X. The hub 61 is fixed to the turbine shell 42b by fixing the radially outer end thereof to the radially inner end of the turbine shell 42b with a rivet 61a or the like.

  The hub 61 has an output shaft 60 inserted inward in the radial direction. In the hub 61, for example, a spline formed in the axial direction on the inner peripheral surface of the radially inner end of the hub 61 and a spline formed in the axial direction on the outer peripheral surface of the output shaft 60 are spline-fitted. The output shaft 60 is provided. As a result, the hub 61 and the output shaft 60 are configured to be able to transmit driving force to each other.

  That is, the turbine shell 42b rotates integrally with the output shaft 60 via the hub 61, and the turbine liner 42 rotates integrally with the output shaft 60, so that the pump impeller 41, the hydraulic oil, and the fluid constituting the fluid transmission mechanism 40 are rotated. The driving force from the engine transmitted through the turbine liner 42 is transmitted to the output shaft 60.

  The stator 43 has a plurality of stator blades 43 a formed in the circumferential direction, and is disposed between the pump impeller 41 and the turbine liner 42. The stator 43 is for changing the flow of hydraulic fluid circulating between the pump impeller 41 and the turbine liner 42 and obtaining a predetermined torque characteristic based on the driving force transmitted from the engine.

  The one-way clutch 44 supports the stator 43 so as to be rotatable in only one direction with respect to the housing 62 that houses the torque converter 1. The one-way clutch 44 is rotatably supported by bearings 45 and 46 with respect to the sleeve 41d and the hub 61, respectively.

  The lockup clutch mechanism 50 is a lockup means, and transmits the driving force transmitted to the front cover 30 to the output shaft 60 via a lockup piston 51 as an engaging member. That is, the lockup clutch mechanism 50 transmits the driving force from the engine transmitted to the front cover 30 directly to the output shaft 60 without using the working fluid of the fluid transmission mechanism 40.

  The lockup clutch mechanism 50 includes a lockup piston 51 as an engagement member, a friction engagement surface 52, a working fluid flow path 53, and a piston hydraulic chamber 54. In the present embodiment, the friction engagement surface 52 of the lockup clutch mechanism 50 is constituted by the friction material 55 provided on the lockup piston 51 and the front cover inner wall surface 34 of the front cover 30.

  The lockup clutch mechanism 50 includes a front cover inner wall surface 34 of the front cover 30 that forms one surface of the friction engagement surface 52 and the other of the friction engagement surfaces 52 from the engine side to the output shaft side in the axial direction. The friction material 55 and the lock-up piston 51 are arranged in this order.

  The lock-up piston 51 is an engaging member and is provided on the fluid transmission mechanism 40 side of the front cover 30. That is, the lock-up piston 51 is provided in a space that is partitioned by the front cover 30 and the pump shell 41b of the fluid transmission mechanism 40 and is filled with the working fluid (working oil). Further, the lock-up piston 51 is provided on the fluid transmission mechanism 40 side of the front cover 30 so as to be movable relative to the front cover 30 in the axial direction.

  The lockup piston 51 is formed in an annular plate shape coaxial with the rotation axis X, and is disposed between the front cover 30 and the turbine liner 42 in the axial direction so as to face the front cover 30 in the axial direction. Has been. More specifically, the lockup piston 51 is disposed between the front cover body 31 of the front cover 30 and the turbine shell 42b and the hub 61 of the turbine liner 42 with respect to the axial direction. The lock-up piston 51 includes a radially outer protruding portion 51a, a radially inner protruding portion 51b, and a connecting cutout portion 51c.

  The radially outer protrusion 51a is formed such that the radially outer end of the lockup piston 51 is bent toward the turbine liner 42 side. That is, the radially outer protruding portion 51a is a portion that protrudes toward the turbine liner 42 and is formed in a cylindrical shape that is coaxial with the rotation axis X.

  The radially inner protruding portion 51b is formed such that the radially inner end portion of the lockup piston 51 is bent toward the front cover 30 side. That is, the radially inner protruding portion 51b is a portion that protrudes toward the front cover 30 and is formed in a cylindrical shape that is coaxial with the rotation axis X.

  The connection notch 51c constitutes a part of the connection 90 and is formed in the radially outer protrusion 51a. The connecting portion 90 connects the lockup piston 51 and a center holding plate 73 of the inner damper mechanism 70 described later so as to be capable of rotating integrally and relatively movable in the axial direction.

  The connection notch 51c is a portion of the lockup piston 51 that faces the connection protrusion 73a provided at the radially outer end of the center holding plate 73 of the inner damper mechanism 70, which will be described later, that is, a radially outward protrusion. It is formed in the part 51a. The connection cutout 51c is formed by cutting out the end on the output shaft side of the radially outer protrusion 51a along the axial direction toward the engine side. The connection notch 51c is formed penetrating from the outer peripheral surface to the inner peripheral surface of the radially outer protruding portion 51a with respect to the radial direction. A plurality of connection notches 51c are formed at equal intervals in the circumferential direction with respect to the radially outer protrusion 51a.

  In the lock-up piston 51, a connection protrusion 73a provided at a radially outer end of a center holding plate 73 of the inner damper mechanism 70 described later is inserted into the connection notch 51c, and the connection notch 51c and the connection protrusion 73a are connected. By engaging, it is relatively movable in the axial direction with respect to the center holding plate 73 of the inner damper mechanism 70, and is supported so as to be integrally rotatable with the center holding plate 73. That is, the lock-up piston 51 is connected to the center holding plate 73 so as to be integrally rotatable and relatively movable in the axial direction by the connection notch 51c and the connection protrusion 73a forming the connection 90. Therefore, the lock-up piston 51 is connected to the center holding plate 73 of the inner damper mechanism 70 so that the driving force transmitted to the lock-up piston 51 can be transmitted, and is also moved relative to the front cover 30 in the axial direction. In other words, the front cover 30 can be approached and separated in the axial direction.

  The lock-up piston 51 is connected to a center holding plate 73 of an inner damper mechanism 70 described later via a connecting portion 90 so as to be integrally rotatable and relatively movable in the axial direction. It faces the front cover flange portion 32 with a predetermined distance in the radial direction. The lock-up piston 51 is connected to the center holding plate 73 of the inner damper mechanism 70 via the connecting portion 90 so as to be integrally rotatable and relatively movable in the axial direction. The outer peripheral surface (the surface on the side opposite to the surface in contact with the output shaft 60) of the radially inner end portion 61 is in contact with the outer peripheral surface and is supported to be slidable in the axial direction.

  The friction engagement surface 52 is constituted by the friction material 55 provided on the lockup piston 51 and the front cover inner wall surface 34 of the front cover 30 as described above. The front cover inner wall surface 34 is a wall surface facing the lock-up piston 51 in the axial direction in the front cover body portion 31 of the front cover 30. Here, the wall surface on which the second side holding plate 25 is provided in the front cover body portion 31. It is the wall surface of the back side. The friction material 55 is provided in the radially outer end of the wall surface of the lockup piston 51 that faces the front cover body 31 in the axial direction, that is, in the vicinity of the radially outer protrusion 51a. The friction material 55 is formed in an annular plate shape coaxial with the rotation axis X. The friction engagement surface 52 is opposed to the front cover inner wall surface 34 forming one surface of the friction engagement surface 52 and the friction material 55 provided on the lock-up piston 51 forming the other surface of the friction engagement surface 52. Thus, the frictional engagement is possible by contacting, that is, the radially outer end of the lockup piston 51 and the front cover 30 can be frictionally engaged.

  As described above, the lock-up piston 51 moves relative to the center holding plate 73 of the inner damper mechanism 70 in the axial direction so as to approach and separate from the front cover body 31 of the front cover 30. Thus, the relative distance of the friction material 55 to the front cover inner wall surface 34 can be changed. The axial movement of the lock-up piston 51 allows the friction material 55 to come into contact with the front cover inner wall surface 34 to be in frictional engagement, and to be in non-contact with the front cover inner wall surface 34 so that the friction engagement is achieved. It can be canceled.

  In addition, the outer peripheral surface of the radial inner end of the hub 61 and the outer peripheral surface of the hub 61 slide on the outer peripheral surface between the radially inner protruding portion 51b of the lockup piston 51 and the outer peripheral surface of the hub 61 in the radial direction. A seal member S1 that suppresses leakage of working fluid (working oil) from between the radially inner projecting portion 51b is disposed. Therefore, the interior of the torque converter 1 defined by the front cover 30 and the pump shell 41b of the fluid transmission mechanism 40 is separated from the fluid transmission mechanism space A in which the fluid transmission mechanism 40 is located by the lockup piston 51, and the lockup clutch. It is partitioned into a clutch space B where the friction material 55 of the mechanism 50 is located. The fluid transmission mechanism space A is a space closer to the output shaft than the lockup piston 51 in the axial direction, that is, a space defined by the lockup piston 51 and the pump shell 41b in the axial direction, a clutch space B Is a space defined by the front cover 30 and the lock-up piston 51 in the axial direction. The fluid transmission mechanism space A and the clutch space B can communicate with each other via a communication portion between the radially outer projecting portion 51a and the front cover flange portion 32 on the friction engagement surface 52 side.

  The working fluid flow path 53 is formed as a space part through which the working fluid (working oil) can pass between the lockup piston 51 and the front cover 30 with respect to the axial direction. Here, the clutch space B in which the friction material 55 is located inside the torque converter 1 functions as the working fluid channel 53. The friction engagement surface 52 is provided at a radially outer portion in the clutch space B that functions as the working fluid flow path 53. As described above, the working fluid flow path 53 is configured so that the fluid in the fluid transmission mechanism 40 is connected to the friction engagement surface 52 via the communication portion between the radially outer protrusion 51a and the front cover flange portion 32. It is formed to be able to communicate with the transmission mechanism space A.

  The piston hydraulic chamber 54 is for generating a hydraulic pressing force for moving the lockup piston 51 in the axial direction. Here, the fluid transmission mechanism space A in which the fluid transmission mechanism 40 is located inside the torque converter 1 functions as the piston hydraulic chamber 54. As described above, the fluid transmission mechanism space A that functions as the piston hydraulic chamber 54 is formed as a space through which the working fluid (hydraulic oil) can pass between the lockup piston 51 and the pump shell 41b. . The fluid transmission mechanism space A, which functions as the piston hydraulic chamber 54, applies a pressing force toward the front cover 30 to the lockup piston 51 by internal hydraulic oil.

  In the lockup clutch mechanism 50 configured as described above, the lockup piston 51 is moved by the hydraulic pressure (hydraulic pressure) of the working fluid (hydraulic oil) supplied to the fluid transmission mechanism space A that functions as the piston hydraulic chamber 54. The friction material 55, which forms the friction engagement surface 52 of the lock-up clutch mechanism 50, and the front cover inner wall surface 34 of the front cover main body 31 come into contact with each other and frictionally engage. As a result, the lockup clutch mechanism 50 is turned ON. When the lock-up clutch mechanism 50 is turned on, the front cover 30 and the lock-up piston 51 rotate together. Therefore, the lock-up clutch mechanism 50 uses the driving force transmitted from the engine transmitted to the front cover 30 to the front. The cover inner wall surface 34, the friction material 55, and the lock-up piston 51 are sequentially transmitted to the center holding plate 73 of the inner damper mechanism 70 described later.

  Here, the torque converter 1 is formed between the lockup piston 51 and the fluid transmission mechanism space A or the front cover 30 that is formed between the lockup piston 51 and the pump shell 41 b and functions as the piston hydraulic chamber 54. Then, hydraulic oil as the working fluid is supplied to one of the clutch spaces B functioning as the working fluid flow path 53 from the hydraulic control device 91 as the hydraulic control means.

  The hydraulic control device 91 controls the flow rate or hydraulic pressure of hydraulic oil supplied to each part of the transmission including the torque converter 1. The hydraulic control device 91 is electrically connected to the ECU 92, and the ECU 92 executes opening / closing control of each valve of the hydraulic control device 91.

  The hydraulic control device 91 then determines the pressure difference between the hydraulic pressure of the fluid transmission mechanism space A that functions as the piston hydraulic chamber 54 and the hydraulic pressure of the clutch space B that functions as the working fluid flow path 53, that is, a lock-up clutch mechanism. The pressing force acting in the axial direction on the pressure receiving surface 51d, which is the output shaft side surface of the 50 lockup pistons 51, can be controlled.

  The hydraulic control device 91 supplies hydraulic oil to the fluid transmission mechanism space A that functions as, for example, the piston hydraulic chamber 54 when the lockup clutch mechanism 50 is turned on, and this fluid transmission that is inside the fluid transmission mechanism 40 is performed. Clutch space that functions as the working fluid flow path 53 by flowing hydraulic oil from the mechanism space A side to the clutch space B and discharging it from the clutch space B that functions as the working fluid flow path 53 to the outside of the torque converter 1. The hydraulic pressure of the portion B is reduced, and the hydraulic pressure of the fluid transmission mechanism space A that functions as the piston hydraulic chamber 54 is made larger than the hydraulic pressure of the clutch space B. As a result, the hydraulic control device 91 moves the lock-up piston 51 to the side closer to the front cover 30 (engine side) to bring the friction material 55 into contact with the inner wall surface 34 of the front cover, and through the friction engagement surface 52. Thus, the front cover 30 and the lockup piston 51 are frictionally engaged, and the front cover 30 and the lockup piston 51 are integrally rotated.

  The hydraulic control device 91 supplies hydraulic oil to the clutch space B that functions as the working fluid flow path 53, for example, when the lockup clutch mechanism 50 is turned off, and the fluid transmission mechanism space from the clutch space B side. The hydraulic oil is allowed to flow through A, and the hydraulic oil is discharged from the fluid transmission mechanism space A that functions as the piston hydraulic chamber 54 to the outside of the torque converter 1. It is greater than or equal to the hydraulic pressure of the fluid transmission mechanism space A that functions as the piston hydraulic chamber 54. As a result, the hydraulic control device 91 moves the lock-up piston 51 to the side away from the front cover 30 (output shaft side), and causes the friction material 55 that has been frictionally engaged with the front cover inner wall surface 34 to move to the front cover inner wall surface. 34, the frictional engagement is released, and the integral rotation of the lockup piston 51 and the front cover 30 is released.

  The inner damper mechanism 70 connects the front cover 30 and the output shaft 60 so as to be relatively rotatable. Here, the front cover 30 and the output shaft 60 are coupled so as to be relatively rotatable via the lock-up piston 51, the inner damper mechanism 70, and the hub 61 of the lock-up clutch mechanism 50 when the lock-up clutch mechanism 50 is ON-controlled. The The inner damper mechanism 70 is housed in a space defined by the front cover 30 and the pump shell 41b, more specifically, in a fluid transmission mechanism space A defined by the lockup piston 51 and the pump shell 41b. It is provided between the turbine shell 42b and the lockup piston 51 with respect to the axial direction.

  The inner damper mechanism 70 includes a plurality of damper springs 71 as a plurality of elastic bodies and a holding member 72. The holding member 72 of the present embodiment holds a plurality of damper springs 71 and includes a center holding plate 73, a first side holding plate 74, and a second side holding plate 75.

  The inner damper mechanism 70 includes a first side holding plate 74, a center holding plate 73, a plurality of damper springs 71, and a second side holding plate 75 in this order from the engine side to the output shaft side with respect to the axial direction. Has been placed.

  The inner damper mechanism 70 of the present embodiment is transmitted from the engine that is transmitted through the front cover 30, the front cover inner wall surface 34, the friction material 55, and the lockup piston 51 in order when the lockup clutch mechanism 50 is ON-controlled. Is input to the center holding plate 73, and the driving force input to the center holding plate 73 is output from the damper spring 71, the first side holding plate 74, and the second side holding plate 75 to the output shaft 60 via the hub 61. Can be communicated to.

  The plurality of damper springs 71 are, for example, a plurality of coil springs. The damper spring 71 transmits the engine driving force transmitted from the front cover 30 to the center holding plate 73 to the first side holding plate 74 and the second side holding plate 75. The plurality of damper springs 71 include an outer damper spring 71a and an inner damper spring 71b. In the outer damper spring 71a and the inner damper spring 71b, the outer damper spring 71a is disposed on the radially outer side, and the inner damper spring 71b is disposed on the radially inner side of the outer damper spring 71a.

  The center holding plate 73, the first side holding plate 74, and the second side holding plate 75 hold a plurality of outer damper springs 71a and inner damper springs 71b, and are formed in an annular plate shape coaxial with the rotation axis X. Is done. The center holding plate 73, the first side holding plate 74, and the second side holding plate 75 are disposed between the lockup piston 51 and the turbine shell 42b with respect to the axial direction.

  As described above, the center holding plate 73 is provided so that the lock-up piston 51 can be integrally rotated and can be relatively moved in the axial direction, and holds the outer damper spring 71a and the inner damper spring 71b so as to be able to transmit driving force. . The center holding plate 73 includes the above-described connecting projection 73a, an outer center holding portion 73b, and an inner center holding portion 73c.

  The connecting protrusion 73a is formed on the radially outer end of the center holding plate 73 (that is, the end on the outer peripheral surface side). The connection protrusion 73a constitutes a part of the connection part 90, that is, the connection part 90 together with the connection notch 51c of the lock-up piston 51 described above. A plurality of connection protrusions 32 a are formed at equal intervals in the circumferential direction with respect to the center holding plate 73.

  The connection protrusion 73a is opposed to the connection notch 51c of the radially outer protrusion 51a in the radial direction in a state where the center holding plate 73 is inserted inside the radially outward protrusion 51a of the lockup piston 51. The center holding plate 73 is formed to protrude radially outward from the radially outer end. The protruding amount of the connecting projection 73a is set so that the connecting protrusion 73a is inserted into the connecting notch 51c in a state where the center holding plate 73 is inserted inside the radially outer protruding portion 51a.

  The center holding plate 73 is inserted into and engaged with the connection notch 51c in the state where the center holding plate 73 is inserted inside the radially outward projecting portion 51a of the lock-up piston 51. The relative rotation with respect to the up-piston 51 is restricted, and the relative movement of the lock-up piston 51 along the axial direction is allowed. That is, the center holding plate 73 supports the lock-up piston 51 at the connecting portion 90 so as to be capable of relative movement in the axial direction and to rotate integrally with the center holding plate 73. Therefore, the center holding plate 73 is connected to the lockup piston 51 by the connecting portion 90 so as to be able to transmit the driving force. When the lock-up clutch mechanism 50 is ON-controlled, the center holding plate 73 receives the driving force from the engine through the front cover 30, the front cover inner wall surface 34, the friction material 55, and the lock-up piston 51 in order. . That is, the driving force from the engine transmitted to the front cover 30 is transmitted from the lockup piston 51 to the center holding plate 73 at the connecting portion 90 when the lockup clutch mechanism 50 is ON-controlled.

  In addition, this connection part 90 may comprise not only what comprises the notch engagement by the connection projection part 73a and the connection notch part 51c, but may comprise spline fitting, for example. In this case, the connecting portion 90 is constituted by splines formed over the entire circumference of the inner peripheral surface of the radially outer protruding portion 51 a of the lockup piston 51 and the outer peripheral surface of the radially outer end of the center holding plate 73. That's fine.

  The outer center holding part 73b and the inner center holding part 73c hold a part of the plurality of outer damper springs 71a and inner damper springs 71b in the center holding plate 73, respectively. Both the outer center holding part 73 b and the inner center holding part 73 c are slits formed in an arc shape along the circumferential direction of the center holding plate 23. In the center holding plate 73, the outer center holding portion 73b and the inner center holding portion 73c are provided such that the outer center holding portion 73b is provided on the radially outer side, while the inner center holding portion 73c is provided on the radially inner side. The outer center holding portion 73b holds the outer damper spring 71a with the outer damper spring 71a inserted therein. The inner center holding part 73c holds the inner damper spring 71b with the inner damper spring 71b inserted therein. A plurality of outer center holding portions 73b and inner center holding portions 73c are formed at equal intervals in the circumferential direction with respect to the center holding plate 73, and hold the outer damper spring 71a and the inner damper spring 71b, respectively.

  Each outer center holding portion 73b has a circumferential length set to a length that can be held in a state where each outer damper spring 71a is urged. Therefore, when the outer damper spring 71a is held by the outer center holding portion 73b, both end portions in the circumferential direction of the outer center holding portion 73b come into contact with both end portions of the outer damper spring 71a, respectively. That is, the outer damper spring 71a contacts both ends in the circumferential direction of each outer center holding portion 73b and is held in a state of being biased between the both ends. Each inner center holding portion 73c has a circumferential length that is set to a length that can hold the inner damper spring 71b in a biased state. Therefore, when the inner damper spring 71b is held by the inner center holding portion 73c, both end portions in the circumferential direction of the inner center holding portion 73c come into contact with both end portions of the inner damper spring 71b, respectively. That is, the inner damper spring 71b is in contact with both ends in the circumferential direction of each inner center holding portion 73c and is held in a state of being biased between the both ends.

  Therefore, the center holding plate 73 includes an outer damper spring 71a, an inner damper spring 71b, and a circumferential end contact portion between the outer center holding portion 73b, the inner center holding portion 73c, the outer damper spring 71a, and the inner damper spring 71b. The driving force can be transmitted between the two.

  The first side holding plate 74 and the second side holding plate 75 hold a part of the plurality of outer damper springs 71a and inner damper springs 71b whose center portions in the axial direction are held by the center holding plate 73 so that the driving force can be transmitted. Is.

  The first side holding plate 74 and the second side holding plate 75 are respectively provided on the sides of the center holding plate 73 with respect to the axial direction. Here, the first side holding plate 74 is provided on the side of the center holding plate 73 on the lock-up piston 51 side (engine side) with respect to the axial direction, and the second side holding plate 75 is set with respect to the axial direction. The center holding plate 73 is provided on the turbine shell 42b side (output shaft side). The first side holding plate 74 has a first outer side holding part 74a and a first inner side holding part 74b, while the second side holding plate 75 is a second outer side holding part 75a and a second inner side holding part 75b. Have

  The first side holding plate 74 and the second side holding plate 75 are set such that the inner diameter of the second side holding plate 75 is smaller than the inner diameter of the first side holding plate 74. The second side holding plate 75 has a radially inner end portion (that is, an end portion on the inner peripheral surface side) fixed to the hub 61 by, for example, a rivet 61a together with a radially inner end portion of the turbine shell 42b. Therefore, the second side holding plate 75 is fixed to the output shaft 60 via the hub 61 and can rotate together with the hub 61 and the output shaft 60.

  The first side holding plate 74 and the second side holding plate 75 include a plurality of outer damper springs 71a and inner dampers in a space portion between the first side holding plate 74 and the second side holding plate 75 in the axial direction. A center holding plate 73 is disposed together with the spring 71b, and the center holding plate 73, the plurality of outer damper springs 71a, and the inner damper spring 71b are sandwiched and held. The first side holding plate 74 and the second side holding plate 75 hold the center holding plate 73 so as to be relatively rotatable across both axial sides of the center holding plate 73.

  Here, the first side holding plate 74 and the second side holding plate 75 are integrated with the center holding plate 73 sandwiched by, for example, rivets 76. A sleeve 77 is provided between the first side holding plate 74 and the second side holding plate 75 integrated by the rivet 76. The sleeve 77 has a cylindrical shape, and the rivet 76 is provided so as to be inserted into the sleeve 77. Thus, the first side holding plate 74 can rotate together with the second side holding plate 75, the hub 61, and the output shaft 60.

  The sleeve 77 acts as a spacer in the axial direction between the first side holding plate 74 and the second side holding plate 75 similarly to the sleeve 27 described above, and the first side holding plate 74 and the second side holding plate. The relative positional relationship with respect to the axial direction with respect to 75 is fixed appropriately. Further, the rivet 76 and the sleeve 77 penetrate the center holding plate 73 through a slide portion 73 d formed on the center holding plate 73, similarly to the pre-damper mechanism 20 described above.

  The first outer side holding portion 74a and the first inner side holding portion 74b of the first side holding plate 74 and the second outer side holding portion 75a and the second inner side holding portion 75b of the second side holding plate 75 are the center holding plate. A part of each of the outer damper springs 71a and the inner damper springs 71b, in which the central part in the axial direction is held by 73, is accommodated and held. The first outer side holding portion 74a and the first inner side holding portion 74b are provided on the wall surface facing the center holding plate 73 of the first side holding plate 74, that is, the wall surface on the output shaft side. The second outer side holding portion 75a and the second inner side holding portion 75b are provided on the wall surface facing the center holding plate 73 of the second side holding plate 75, that is, the engine side wall surface.

  The first outer side holding portion 74a and the first inner side holding portion 74b are formed by recessing the wall surface on the output shaft side of the first side holding plate 74 on the engine side (the side opposite to the center holding plate 73 side). The The first outer side holding portion 74 a and the first inner side holding portion 74 b are formed in an arc shape along the circumferential direction of the first side holding plate 74. A plurality of first outer side holding portions 74 a and first inner side holding portions 74 b are formed at equal intervals in the circumferential direction with respect to the first side holding plate 74.

  The second outer side holding portion 75a and the second inner side holding portion 75b are formed by recessing the engine side wall surface of the second side holding plate 75 to the output shaft side (the side opposite to the center holding plate 73 side). The The second outer side holding part 75 a and the second inner side holding part 75 b are formed in an arc shape along the circumferential direction of the second side holding plate 75. A plurality of second outer side holding portions 75 a and second inner side holding portions 75 b are formed at equal intervals in the circumferential direction with respect to the second side holding plate 75.

  Each first outer side holding portion 74a and each second outer side holding portion 75a are formed at positions that face the outer center holding portion 73b of the center holding plate 73 in the axial direction. Each first inner side holding portion 74b and each second inner side holding portion 75b are formed at positions that face the inner center holding portion 73c of the center holding plate 73 in the axial direction.

  Therefore, in the inner damper mechanism 70, the outer center holding portion 73b of the center holding plate 73 holds the center portion (the center portion in the axial direction) of each outer damper spring 71a, and the first outer side holding portion of the first side holding plate 74 is maintained. The portion 74a accommodates and holds a portion of each outer damper spring 71a on the engine side than the outer center holding portion 73b, while the second outer side holding portion 75a of the second side holding plate 75 has an output shaft from the outer center holding portion 73b. Holds and holds the side part. Further, in the inner damper mechanism 70, the inner center holding portion 73c of the center holding plate 73 holds the center part (the center part in the axial direction) of each inner damper spring 71b, and the first inner side holding part of the first side holding plate 74 is maintained. The portion 74b accommodates and holds the engine side portion of the inner damper spring 71b from the inner center holding portion 73c, while the second inner side holding portion 75b of the second side holding plate 75 is output shaft from the inner center holding portion 73c. Holds and holds the side part.

  Then, both end portions in the circumferential direction of each first outer side holding portion 74a and each second outer side holding portion 75a are respectively outer damper springs in a state where each outer damper spring 71a is held by each outer center holding portion 73b. It faces both ends of 71a in the circumferential direction and can be contacted. Both end portions of each first inner side holding portion 74b and each second inner side holding portion 75b in the circumferential direction of the inner damper spring 71b are in a state where each inner damper spring 71b is held by each inner center holding portion 73c. It faces both ends in the circumferential direction and can be contacted. As a result, the first side holding plate 74 and the second side holding plate 75 are connected to the first outer side holding part 74a, the second outer side holding part 75a, the first inner side holding part 74b, and the second inner side holding part 75b. Driving force can be transmitted between the outer damper spring 71a and the inner damper spring 71b at the circumferential end contact portion between the outer damper spring 71a and the inner damper spring 71b.

  That is, the outer damper springs 71 a and the inner damper springs 71 b are formed by the outer center holding part 73 b, the inner center holding part 73 c of the center holding plate 73, the first outer side holding part 74 a and the first inner side holding part 74 of the first side holding plate 74. The center holding plate 73, the first side holding plate 74, and the second side holding plate 75 are held by the side holding portion 74 b and the second outer side holding portion 75 a and the second inner side holding portion 75 b of the second side holding plate 75. The driving force can be transmitted between the two.

  The inner damper mechanism 70 configured as described above transmits the driving force from the engine transmitted to the lockup piston 51 to the center holding plate 73 at the connecting portion 90. The inner damper mechanism 70 transmits the driving force transmitted to the center holding plate 73 to the outer damper spring 71a and the inner damper spring 71b from the circumferential ends of the outer center holding portion 73b and the inner center holding portion 73c. The inner damper mechanism 70 includes a first outer side holding portion 74a, a first inner side holding portion 74b, a second outer side holding portion 75a, and a second inner side that transmit the driving force transmitted to the outer damper spring 71a and the inner damper spring 71b. It transmits to the 1st side holding plate 74 and the 2nd side holding plate 75 via the circumferential direction edge part of the holding | maintenance part 75b. Accordingly, the first side holding plate 74 and the second side holding plate 75 transmit the driving force from the engine transmitted to the lockup piston 51 via the outer damper spring 71a and the inner damper spring 71b. And rotate in the same direction. Then, the inner damper mechanism 70 transmits the driving force transmitted to the first side holding plate 74 and the second side holding plate 75 from the second side holding plate 75 to the output shaft 60 via the hub 61. The output shaft 60 rotates in the same direction as the first side holding plate 74 and the second side holding plate 75. Therefore, the inner damper mechanism 70 can transmit the driving force transmitted to the center holding plate 73 to the output shaft 60 via the damper spring 71.

  During this time, the outer damper springs 71a and the inner damper springs 71b are respectively connected to the outer center holding portion 73b of the center holding plate 73, the circumferential end of the inner center holding portion 73c, the first side holding plate 74, and the second side holding. The plate 75 is transmitted while being held between the first outer side holding part 74a, the first inner side holding part 74b, the second outer side holding part 75a, and the circumferential end of the second inner side holding part 75b. Elastically deforms according to the magnitude of the driving force.

  In the torque converter 1, the drive plate 10, which is also used as the center holding plate 23, is supported and fixed to the end surface of the crankshaft 80 by a bolt 81 so as to be rotatable together with the crankshaft 80 about the rotation axis X. And is positioned with respect to the radial direction. Further, the torque converter 1 is supported so as to be rotatable relative to the crankshaft 80 about the rotation axis X by the front cover 30 being rotatably supported by the rolling bearing 83 via the front cover boss portion 33. It is positioned with respect to the radial direction. As a result, the torque converter 1 appropriately maintains the relative positional relationship between the drive plate 10 and the front cover 30 in the radial direction, and performs centering of the drive plate 10 and the front cover 30. Therefore, the torque converter 1 can accurately align the rotation center of the drive plate 10 and the pre-damper mechanism 20 and the rotation center of the front cover 30 and the fluid transmission mechanism 40 with the rotation axis X. As a result, the torque converter 1 can prevent the rotation center of the drive plate 10 and the pre-damper mechanism 20 and the front cover 30 and the rotation center of the fluid transmission mechanism 40 from being eccentric with respect to the rotation axis X. As a result, vibration can be prevented from occurring during rotation, performance can be stabilized, and reliability can be improved.

  Next, the basic operation of the torque converter 1 according to this embodiment will be described. In the torque converter 1, when the engine generates driving force and the crankshaft 80 rotates, the driving force from the engine is transmitted to the pre-damper mechanism 20 via the drive plate 10, and from the engine transmitted to the pre-damper mechanism 20. Is transmitted to the front cover 30.

  At this time, when the driving force transmitted to the drive plate 10 is transmitted to the front cover 30 via the pre-damper mechanism 20 regardless of whether the lockup clutch mechanism 50 is ON or OFF, it is also used as the center holding plate 23. The driving force transmitted to the drive plate 10 is transmitted to the damper spring 21 from the circumferential end of the center holding portion 23a. The driving force transmitted to the damper spring 21 is transmitted to the first side holding plate 24 and the second side holding plate 25 via the circumferential ends of the first side holding portion 24a and the second side holding portion 25a, The driving force transmitted to the first side holding plate 24 and the second side holding plate 25 is transmitted from the second side holding plate 25 to the front cover 30.

  When the lockup clutch mechanism 50 is switched from OFF to ON or from ON to OFF, when the driving force from the engine varies, or when the resistance force transmitted from the road surface to the output shaft 60 varies. In this case, the force transmitted between the drive plate 10 also serving as the center holding plate 23 and the front cover 30 (the driving force transmitted from the engine and the driven force transmitted from the road surface) varies, and the pre-damper mechanism 20 The drive plate 10 located on the drive side and the front cover 30 located on the driven side tend to rotate relative to each other. At this time, each damper spring 21 of the pre-damper mechanism 20 is rotated with the drive plate 10 along with the relative rotation of the drive plate 10 also used as the driving-side center holding plate 23 and the driven-side front cover 30. Each of the first side holding plate 24, the second side holding plate 25, and the center holding plate 23 is elastically deformed in accordance with fluctuations in the force transmitted to the front cover 30. Thereby, for example, each damper spring 21 absorbs vibration caused by the explosion of the engine, so that vibration such as a booming sound during transmission of the driving force via the pre-damper mechanism 20 can be reduced.

  The driving force from the engine transmitted to the front cover 30 via the pre-damper mechanism 20 is transmitted to the pump shell 41b of the pump impeller 41 connected to the front cover 30, and the pump impeller 41 rotates. When the pump impeller 41 rotates, the hydraulic oil in the fluid transmission mechanism space A circulates between the pump blade 41a, the turbine blade 42a, and the stator blade 43a of the stator 43, and acts as a fluid coupling. As a result, the driving force transmitted from the engine to the front cover 30 is transmitted to the turbine liner 42 via the pump impeller 41 and the hydraulic oil, and the turbine liner 42 rotates in the same direction as the front cover 30. At this time, the stator 43 changes the flow of the working oil that circulates between the pump blade 41a and the turbine blade 42a via the stator blade 43a, whereby the torque converter 1 obtains a predetermined torque characteristic. Can do.

  When the lockup clutch mechanism 50 is OFF, the frictional engagement between the front cover inner wall surface 34 of the front cover 30 and the friction material 55 provided on the lockup piston 51 is released. Therefore, the driving force from the engine transmitted to the turbine liner 42 via the hydraulic oil as described above is transmitted to the output shaft 60 via the hub 61. That is, when the lockup clutch mechanism 50 is OFF, the driving force from the engine transmitted to the front cover 30 is transmitted to the output shaft 60 via the fluid transmission mechanism 40.

  On the other hand, when the lock-up clutch mechanism 50 is ON, the front cover 30 and the lock-up piston 51 are engaged by frictional engagement between the front cover inner wall surface 34 of the front cover 30 and the friction material 55 provided on the lock-up piston 51. And rotate together. Therefore, the driving force transmitted to the front cover 30 via the pre-damper mechanism 20 is transmitted to the lockup piston 51 via the friction engagement surface 52. The driving force from the engine transmitted to the lockup piston 51 is input from the lockup piston 51 to the center holding plate 73 of the inner damper mechanism 70 via the connecting portion 90, and the driving force input to the center holding plate 73. Is transmitted to the outer damper spring 71a and the inner damper spring 71b from the circumferential ends of the outer center holding portion 73b and the inner center holding portion 73c. The driving force transmitted to the outer damper spring 71a and the inner damper spring 71b is the circumference of the first outer side holding portion 74a, the first inner side holding portion 74b, the second outer side holding portion 75a, and the second inner side holding portion 75b. The driving force transmitted to the first side holding plate 74 and the second side holding plate 75 via the end portions in the direction is transmitted to the first side holding plate 74 and the second side holding plate 75. To the hub 61. That is, when the lock-up clutch mechanism 50 is ON, the driving force transmitted from the engine to the front cover 30 is directly passed through the lock-up clutch mechanism 50, the inner damper mechanism 70, and the hub 61 without using hydraulic oil. It is transmitted to the output shaft 60.

  At this time, when the lockup clutch mechanism 50 is switched from OFF to ON or from ON to OFF, or when the driving force from the engine fluctuates, the resistance force from the road surface transmitted to the output shaft 60 fluctuates. In some cases, the force transmitted between the front cover 30 and the output shaft 60 (the driving force transmitted from the engine and the driven force transmitted from the road surface) fluctuates. The front cover 30 located and the output shaft 60 located on the driven side tend to rotate relatively. That is, the center holding plate 73 that rotates integrally with the front cover 30 and the lockup piston 51, the first side holding plate 74 that rotates together with the hub 61 and the output shaft 60, and the second side holding plate 75 will rotate relatively. And The outer damper springs 71a and the inner damper springs 71b of the inner damper mechanism 70 include a front cover 30 on the driving side, a lockup piston 51, a center holding plate 73, an output shaft 60 on the driven side, a hub 61, The center holding plate is respectively changed in accordance with the fluctuation of the force transmitted between the front cover 30 side and the output shaft 60 side with the relative rotation of the first side holding plate 74 and the second side holding plate 75. 73, the first side holding plate 74, and the second side holding plate 75 are elastically deformed. Thereby, when the lockup clutch mechanism 50 is ON, the front cover 30 and the output shaft 60 are connected to each other by the inner damper mechanism 70 via the plurality of damper springs 71 so as to be relatively rotatable. Since each damper spring 71 absorbs the vibration caused by the above, vibration such as a booming noise during transmission of the driving force via the inner damper mechanism 70 can be reduced.

  Here, the torque converter 1 of the present embodiment functions as an internal space of the torque converter 1 in which the hydraulic control device 91 is partitioned by the front cover 30 and the pump shell 41b as described above, and more specifically, as the piston hydraulic chamber 54. By controlling the supply and discharge of hydraulic fluid to / from the fluid transmission mechanism space A or the clutch space B functioning as the working fluid flow path 53, the lockup clutch mechanism 50 can be turned ON / OFF or the lockup clutch mechanism 50 can be controlled. Slip control (control in which the hydraulic pressure in the fluid transmission mechanism space A and the clutch space B is maintained at a predetermined balance and the friction engagement surface 52 is in a slip state (half-engagement state)) is executed. At this time, in the torque converter 1, hydraulic oil is supplied or discharged through a supply / discharge opening 93 provided on the fluid transmission mechanism 40 side of the front cover 30 with respect to the axial direction.

  The supply / discharge opening 93 is formed as a circular opening around the rotation axis X at one end in the axial direction of the cylindrical portion of the sleeve 41d, here the end on the output shaft side. The supply / discharge opening 93 communicates with the internal space of the sleeve 41d. In the sleeve 41d, the output shaft 60 and a part of the housing 62 described above are inserted inside the cylindrical portion, and the inner space portion functions as the supply / discharge passage 94. That is, the supply / discharge passage 94 communicates with the supply / discharge opening 93 and is an internal space of the torque converter 1 defined by the front cover 30 and the pump shell 41b, that is, a fluid transmission mechanism space that functions as the piston hydraulic chamber 54. A or the clutch space B functioning as the working fluid flow path 53 communicates. More specifically, the supply / discharge passage 94 has one end portion on the output shaft side in the axial direction opened by the supply / discharge opening portion 93, and the other end portion on the engine side is closed by the front cover main body portion 31 of the front cover 30. In addition, the fluid transmission mechanism space portion A and the clutch space portion B communicate with each other in the radial direction on the other end side. The hydraulic fluid supplied through the supply / discharge opening 93 is supplied to the fluid transmission mechanism space A or the clutch space B through the supply / discharge passage 94, and the fluid transmission mechanism space A, the clutch The hydraulic oil discharged from the space B is discharged from the supply / discharge opening 93 through the supply / discharge passage 94.

By the way, in the torque converter 1 of the present embodiment, when hydraulic oil is supplied to the supply / discharge passage 94 via the supply / discharge opening 93, the supply / discharge opening 93 in the axial direction in the front cover main body 31 of the front cover 30. The hydraulic pressure of the working oil acts on the pressing force acting surface 95 that faces the fluid, and the pressing force toward the pre-damper mechanism 20 along the axial direction acts on the fluid transmission mechanism 40 via the front cover 30. The pressing force acting on the pressing force acting surface 95 is the hydraulic pressure of the working oil acting on the inner wall side of the front cover 30 and the pump shell 41b from the inside of the torque converter 1 partitioned by the front cover 30 and the pump shell 41b. This corresponds to the hydraulic pressure that is the difference between the component toward the output shaft and the component toward the engine along the axial direction of the engine. That is, the hydraulic component toward the output shaft corresponds to the opening area of the supply / discharge opening 93. It occurs when it becomes relatively smaller than the hydraulic component. Therefore, the pressing force acting on the pressing force acting surface 95 basically has a value corresponding to the opening area of the supply / discharge opening 93. That is, when the diameter along the radial direction of the supply / discharge opening 93 is φD1 and the hydraulic pressure of the hydraulic oil in the supply / discharge passage 94 is P0, the pressing force F0 acting on the pressing force acting surface 95 is expressed by the following formula (1 ).

F0≈ (π / 4) × P0 × φD1 (1)

  In other words, the torque converter 1 acts as a whole on the pre-damper mechanism together with the front cover 30 via the front cover 30 with respect to the fluid transmission mechanism 40 by the pressing force F0 acting on the pressing force acting surface 95 of the front cover 30. A pressing force F0 that moves to the 20 side acts. A part of the pressing force F 0 acts on the pressing force acting surface 95 via the hub 61. The pressing force F0 fluctuates due to fluctuations in the hydraulic pressure P0 of the hydraulic oil in the supply / discharge passage 94, in other words, the hydraulic pressure in the fluid transmission mechanism space portion A and the clutch space portion B. For this reason, the front cover 30, the axial position of the fluid transmission mechanism 40 also tends to change according to the change in the hydraulic pressure P0 of the hydraulic oil in the supply / discharge passage 94.

  At this time, in the case of the conventional torque converter, when a force that moves the fluid transmission mechanism together with the front cover is applied to the fluid transmission mechanism by the pressing force F0, the drive plate receives this force, that is, the pressing force F0. However, when the pre-damper mechanism 20 is provided on the opposite side of the fluid transmission mechanism 40 with respect to the front cover 30 as in the torque converter 1 of the present embodiment, the front cover 30 and the fluid transmission mechanism due to this pressing force F0. With the movement of 40 toward the pre-damper mechanism 20, for example, the gaps between the first side holding plate 24, the second side holding plate 25 and the center holding plate 23 of the pre-damper mechanism 20 are narrowed to ensure an appropriate clearance. When it becomes impossible, smooth relative rotation of the 1st side holding plate 24, the 2nd side holding plate 25, and the center holding plate 23 may be inhibited. That is, since it becomes impossible to secure an appropriate clearance between the first side holding plate 24, the second side holding plate 25, and the center holding plate 23, for example, the first side holding plate 24, the second side holding plate 25, As a result, the first holding plate 24, the second holding plate 25, and the holding plate 23 increase in friction when the first holding plate 24 and the second holding plate 25 and the center holding plate 23 rotate relative to each other. Accordingly, the pre-damper mechanism 20 becomes unstable, the vibration reduction performance is lowered, and the damper performance of the pre-damper mechanism 20 such as prevention of booming noise may be lowered. . Further, for example, when the first side holding plate 24, the second side holding plate 25, and the center holding plate 23 are in contact with each other, wear deterioration of the contact portion is promoted, and as a result, durability may be deteriorated. .

  Therefore, the torque converter 1 according to the present embodiment includes the reaction force unit 100 as a reaction force unit that causes the reaction force F1 to act on the fluid transmission mechanism 40 from the pre-damper mechanism 20 side, whereby the front cover 30 and the fluid transmission mechanism 40 are provided. This prevents fluctuations in the axial position and improves vibration reduction performance.

  The reaction force unit 100 applies a reaction force F1 equivalent to the pressing force F0 from the pre-damper mechanism 20 side to the fluid transmission mechanism 40 on which the pressing force F0 to the pre-damper mechanism 20 side along the axial direction acts due to the hydraulic pressure of the hydraulic oil. Is to act. The reaction force part 100 of this embodiment has a reaction force hydraulic chamber 110 as a reaction force pressure chamber.

  The reaction force hydraulic chamber 110 is provided on the side of the pre-damper mechanism 20 of the front cover 30 in the axial direction, and causes the reaction force F1 of the pressing force F0 to act on the hydraulic oil supplied to the inside. The reaction force hydraulic chamber 110 of this embodiment is a space formed by the front cover boss portion 33 and a fitting portion 81c formed on the end surface of the crankshaft 80, and hydraulic oil is supplied to the inside.

  Here, as described above, the front cover boss portion 33 is formed in a cylindrical shape coaxial with the rotation axis X as a whole, and an annular projecting portion 33b is provided at the central portion in the axial direction of the cylindrical portion 33a. The annular projecting portion 33 b is an annular portion formed so that the outer peripheral surface of the columnar portion 33 a of the front cover boss portion 33 projects radially outward, and is formed coaxially with the rotation axis X.

  The reaction force hydraulic chamber 110 is provided such that the front cover boss portion 33 of the front cover 30 is inserted into a fitting portion 81c formed on the end surface of the crankshaft 80, and is fitted to the outer peripheral surface of the annular projecting portion 33b. By disposing the seal member S2 between the inner peripheral surface of the joint portion 81c, the outer peripheral surface of the front cover boss portion 33 and the end surface facing the bottom portion of the fitting portion 81c in the front cover boss portion 33 in the axial direction. It is defined between the (end surface on the engine side), the inner peripheral surface of the fitting portion 81c, and the bottom portion of the fitting portion 81c. Here, the seal member S2 suppresses leakage of working fluid from between the outer peripheral surface of the annular projecting portion 33b and the inner peripheral surface of the fitting portion 81c. The rolling bearing 83 described above is disposed in the reaction force hydraulic chamber 110.

  The reaction force hydraulic chamber 110 causes the reaction force F1 to act on the reaction force acting surface 111 of the front cover boss portion 33 by the hydraulic pressure of the hydraulic oil supplied to the inside. Here, the reaction force acting surface 111 is an end surface in the axial direction of the front cover boss 33, that is, a surface that intersects the axial direction substantially perpendicularly, and is an end surface on the engine side that contacts the reaction force hydraulic chamber 110. Here, the reaction force acting surface 111 is an end surface on the axial direction engine side of the cylindrical portion 33a and the annular projecting portion 33b.

  The reaction force hydraulic chamber 110 causes a reaction force F1 equivalent to the pressing force F0 to act on the reaction force acting surface 111 by adjusting the oil pressure of the hydraulic oil supplied to the inside to a predetermined oil pressure. Thereby, the reaction force hydraulic chamber 110 is equivalent to the pressing force F0 from the pre-damper mechanism 20 side to the front cover 30 and the fluid transmission mechanism 40 via the front cover boss portion 33 provided with the reaction force acting surface 111. The reaction force F1 can be applied.

  In the reaction force unit 100 of the present embodiment, the area of the reaction force acting surface 111 is set to be equal to the area of the supply / discharge opening 93, and the reaction force hydraulic chamber 110 communicates with the fluid transmission mechanism 40 side. That is, the reaction force acting surface 111 is set such that the diameter φD2 along the radial direction is set substantially equal to the diameter along the radial direction of the supply / discharge opening 93, whereby the area of the reaction force acting surface 111 and the supply / discharge opening are reduced. The area of the portion 93 is set to be equal. The reaction force hydraulic chamber 110 is connected to the fluid transmission mechanism 40 side of the front cover 30 via a communication path 31b formed in the front cover body 31 of the front cover 30 and a communication path 33c formed in the front cover boss 33. In other words, it communicates with an internal space defined by the supply / discharge passage 94, the front cover 30 and the pump shell 41b. Thereby, the reaction force part 100 is communicated from the space part of the front cover 30 on the fluid transmission mechanism 40 side, that is, from the internal space defined by the supply / discharge passage 94, the front cover 30 and the pump shell 41b, to the communication passage 31b, The hydraulic oil is introduced into the reaction force hydraulic chamber 110 through 33c, and the hydraulic pressure of the hydraulic oil in the reaction hydraulic chamber 110 becomes equal to the hydraulic pressure of the hydraulic fluid on the fluid transmission mechanism 40 side of the front cover 30.

  When the hydraulic oil is supplied to the supply / discharge passage 94 through the supply / discharge opening 93, the torque converter 1 configured as described above is operated by the hydraulic pressure of the hydraulic oil acting on the pressing force acting surface 95. A pressing force F0 toward the pre-damper mechanism 20 along the axial direction to the fluid transmission mechanism 40 via the cover 30, that is, a pressing force that moves the entire fluid transmission mechanism 40 together with the front cover 30 to the pre-damper mechanism 20 side. F0 acts.

  At this time, the reaction force section 100 is connected to the communication path 31b and the communication path 33c from the space part (the internal space defined by the front cover 30 and the pump shell 41b) of the front cover 30 on the fluid transmission mechanism 40 side. By introducing the hydraulic oil into the reaction force hydraulic chamber 110 via the hydraulic pressure, the hydraulic oil pressure in the reaction force hydraulic chamber 110 is equal to the hydraulic pressure of the hydraulic fluid on the fluid transmission mechanism 40 side of the front cover 30. Become. The reaction force unit 100 is configured such that the area of the reaction force acting surface 111 is set equal to the area of the supply / discharge opening 93 and the hydraulic pressure of the hydraulic oil inside the reaction force hydraulic chamber 110 is the fluid transmission mechanism of the front cover 30. Since it is equivalent to the hydraulic pressure of the hydraulic oil on the 40 side, the reaction force F1 due to the hydraulic pressure of the hydraulic oil in the reaction force hydraulic chamber 110 can be applied to the reaction force acting surface 111 with a magnitude equivalent to the pressing force F0.

  Therefore, in the torque converter 1, the reaction force hydraulic chamber 110 that forms the reaction force portion 100 generates a reaction force against a pressing force F0 that moves the entire fluid transmission mechanism 40 together with the front cover 30 to the pre-damper mechanism 20 side. Since the force F1 can be applied to the front cover 30 and the fluid transmission mechanism 40 from the pre-damper mechanism 20 side with the same magnitude as the pressing force F0, fluctuations in the axial position of the front cover 30 and the fluid transmission mechanism 40 are prevented. can do. As a result, the torque converter 1 can prevent the front cover 30 and the fluid transmission mechanism 40 from moving toward the pre-damper mechanism 20 due to the pressing force F0, so that the first side holding plate 24 of the pre-damper mechanism 20 and the first It is possible to prevent the gap between the two-side holding plate 25 and the center holding plate 23 from becoming narrow, and accordingly, the first side holding plate 24, the second side holding plate 25, and the center holding plate 23 are always appropriate. A sufficient clearance can be secured, and the smooth relative rotation of the first side holding plate 24, the second side holding plate 25 and the center holding plate 23 can be prevented from being hindered.

  As a result, the torque converter 1 can prevent the first side holding plate 24, the second side holding plate 25, and the center holding plate 23 from coming into contact with each other. It is possible to prevent an increase in friction (friction) when the side holding plate 25 and the center holding plate 23 rotate relative to each other, and to prevent an appropriate elastic deformation of the damper spring 21 from being hindered. Can do. Therefore, the torque converter 1 can stabilize the performance of the pre-damper mechanism 20, can reliably ensure proper damper performance, and can improve vibration reduction performance. And since the torque converter 1 can further improve the vibration reduction performance by the pre-damper mechanism 20, it can further suppress generation | occurrence | production of a booming noise etc., and can turn on the lockup clutch mechanism 50. FIG. The rotational speed region can be expanded, and the lockup clutch mechanism 50 can be turned on in a relatively low rotational speed region, so that fuel efficiency can be further improved.

  Further, since the torque converter 1 can prevent the first side holding plate 24, the second side holding plate 25 and the center holding plate 23 from coming into contact with each other, it suppresses wear deterioration of each member constituting the pre-damper mechanism 20. As a result, durability can also be improved.

  According to the torque converter 1 according to the embodiment of the present invention described above, the drive force transmitted from the engine to the drive plate 10 by connecting the drive plate 10 and the front cover 30 via the damper spring 21 so as to be relatively rotatable. Is provided on the opposite side of the pre-damper mechanism 20 across the front cover 30 with respect to the axial direction of the output shaft 60. A fluid transmission mechanism 40 capable of transmitting the transmitted driving force to the output shaft 60 via hydraulic oil, and a fluid transmission mechanism in which a pressing force F0 to the pre-damper mechanism 20 side along the axial direction acts by the hydraulic pressure of the hydraulic oil. 40 includes a reaction force portion 100 that applies a reaction force F1 equivalent to the pressing force F0 from the pre-damper mechanism 20 side.

  Therefore, the torque converter 1 causes the reaction force portion 100 to apply a reaction force F1 equivalent to the pressing force F0 from the pre-damper mechanism 20 side to the fluid transmission mechanism 40, so that the axial position of the front cover 30 and the fluid transmission mechanism 40 is reduced. Therefore, it is possible to prevent an increase in friction (friction) in the pre-damper mechanism 20 and an inhibition of an appropriate elastic deformation of the damper spring 21, and thus vibration reduction performance can be improved. .

  Further, according to the torque converter 1 according to the embodiment of the present invention described above, the reaction force portion 100 is provided on the pre-damper mechanism 20 side of the front cover 30 with respect to the axial direction, and is supplied to the inside. Has a reaction force hydraulic chamber 110 for applying a reaction force F1. Therefore, the reaction force unit 100 generates the reaction force F1 by the hydraulic pressure of the hydraulic oil supplied to the reaction force hydraulic chamber 110, and causes the reaction force F1 to act on the fluid transmission mechanism 40 from the pre-damper mechanism 20 side. Therefore, fluctuations in the axial position of the front cover 30 and the fluid transmission mechanism 40 can be prevented by the hydraulic pressure of the hydraulic oil supplied into the reaction force hydraulic chamber 110.

  Furthermore, according to the torque converter 1 according to the embodiment of the present invention described above, the fluid transmission mechanism 40 includes the supply / discharge opening 93 provided on the fluid transmission mechanism 40 side of the front cover 30 with respect to the axial direction. The hydraulic oil is supplied or discharged through the hydraulic pressure of the hydraulic oil acting on the pressing force acting surface 95 that faces the supply / discharge opening 93 in the axial direction, and the reaction force portion 100 acts. The area of the reaction force acting surface 111 on which the reaction force F1 due to the hydraulic pressure of the hydraulic oil in the reaction force hydraulic chamber 110 acts is set equal to the area of the supply / discharge opening 93, and the reaction force hydraulic chamber 110 is set to the front cover 30. It communicates with the fluid transmission mechanism 40 side. Therefore, in the reaction force unit 100, the area of the reaction force acting surface 111 is set to be equal to the area of the pressing force acting surface 95, and the hydraulic pressure of the working oil in the reaction force hydraulic chamber 110 is the fluid transmission mechanism of the front cover 30. Since it is equivalent to the hydraulic pressure of the hydraulic oil on the 40 side, the reaction force F1 due to the hydraulic pressure of the hydraulic oil in the reaction force hydraulic chamber 110 can be applied to the reaction force acting surface 111 with a magnitude equivalent to the pressing force F0. Further, the torque converter 1 can react even when the hydraulic pressure of the hydraulic fluid on the fluid transmission mechanism 40 side of the front cover 30 varies and the pressing force F0 varies according to ON / OFF of the lockup clutch mechanism 50. The hydraulic pressure of the hydraulic oil in the hydraulic chamber 110 also fluctuates following this fluctuation, and the reaction force F1 also fluctuates. Therefore, the reaction force hydraulic chamber 110 that forms the reaction force portion 100 always pushes from the pre-damper mechanism 20 side reliably. A reaction force F1 equivalent to the pressure F0 can be applied.

  In the above description, the reaction force portion 100 has an area of the reaction force acting surface 111 set equal to the area of the supply / discharge opening 93, and the reaction force hydraulic chamber 110 is connected to the reaction force hydraulic chamber 110 via the communication passage 31b and the communication passage 33c. By setting the hydraulic pressure of the internal hydraulic oil equal to the hydraulic pressure of the hydraulic oil on the fluid transmission mechanism 40 side of the front cover 30, the reaction force F1 due to the hydraulic pressure of the hydraulic oil in the reaction force hydraulic chamber 110 is equal to the pressing force F0. However, the present invention is not limited to this. That is, in the reaction force unit 100, for example, the hydraulic pressure of the hydraulic fluid introduced into the reactive hydraulic chamber 110 without providing the communication passage 31b and the communication passage 33c is the hydraulic pressure of the hydraulic fluid on the fluid transmission mechanism 40 side of the front cover 30. May be adjusted separately so that the reaction force F1 due to the hydraulic pressure of the hydraulic fluid in the reaction force hydraulic chamber 110 is set to a magnitude equivalent to the pressing force F0.

(Embodiment 2)
FIG. 2 is a cross-sectional view of a main part of the torque converter according to the second embodiment of the present invention. The fluid transmission device according to the second embodiment has substantially the same configuration as the fluid transmission device according to the first embodiment, but is different from the fluid transmission device according to the first embodiment in that a reaction force bearing portion is provided. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

  As shown in FIG. 2, the torque converter 201 as the fluid transmission device of the present embodiment is configured such that the reaction force portion 100 further includes a reaction force bearing portion 220.

  The reaction force bearing portion 220 is, for example, a thrust bearing that receives a load acting in the axial direction. The reaction force bearing portion 220 supports the drive plate 10 or the member of the pre-damper mechanism 20 that rotates together with the drive plate 10 and the front cover 30 or the member of the pre-damper mechanism 20 that rotates together with the front cover 30 so as to be relatively rotatable. To do.

  The reaction force bearing portion 220 is provided between the drive plate 10 and the second side holding plate 25 as a member of the pre-damper mechanism 20 that rotates together with the front cover 30 in the axial direction. The reaction force bearing portion 220 supports the drive plate 10 and the second side holding plate 25 so as to be relatively rotatable.

  The torque converter 201 configured as described above has a reaction force hydraulic chamber 110 that forms a reaction force portion 100 against a pressing force F0 that moves the entire fluid transmission mechanism 40 together with the front cover 30 to the pre-damper mechanism 20 side. Is applied to the front cover 30 and the fluid transmission mechanism 40 from the pre-damper mechanism 20 side with the same magnitude as the pressing force F0. When the pressure F0 is not completely equal, the reaction force bearing portion 220 can receive the pressing force that cannot be canceled by the reaction force F1. In other words, the reaction force bearing portion 220 that forms the reaction force portion 100 supports the drive plate 10 and the second side holding plate 25 so as to be relatively rotatable, thereby allowing a reaction force corresponding to [pressing force F0−reaction force F1]. Can be applied to the front cover 30 and the fluid transmission mechanism 40 from the pre-damper mechanism 20 side. As a result, the torque converter 201 can reliably prevent fluctuations in the axial position of the front cover 30 and the fluid transmission mechanism 40 by the reaction force hydraulic chamber 110 and the reaction force bearing portion 220 forming the reaction force portion 100.

  According to the torque converter 201 according to the embodiment of the present invention described above, the torque converter 201 causes the reaction force portion 100 to apply a reaction force F1 equivalent to the pressing force F0 to the fluid transmission mechanism 40 from the pre-damper mechanism 20 side. Therefore, fluctuations in the axial position of the front cover 30 and the fluid transmission mechanism 40 can be prevented, thereby preventing increase in friction (friction) in the pre-damper mechanism 20 and inhibition of proper elastic deformation of the damper spring 21. Therefore, vibration reduction performance can be improved.

  Furthermore, according to the torque converter 201 according to the embodiment of the present invention described above, the reaction force unit 100 generates the reaction force F1 by the hydraulic pressure of the hydraulic oil supplied to the reaction force hydraulic chamber 110, and the fluid Since the reaction force F <b> 1 can be applied to the transmission mechanism 40 from the pre-damper mechanism 20 side, the front cover 30 and the axial position of the fluid transmission mechanism 40 can be adjusted by the hydraulic pressure of the hydraulic oil supplied into the reaction force hydraulic chamber 110. Variations can be prevented.

  Furthermore, according to the torque converter 201 according to the embodiment of the present invention described above, the reaction force unit 100 includes the drive plate 10 and the second side holding plate 25 of the pre-damper mechanism 20 that rotates together with the front cover 30. It has the reaction force bearing part 220 supported so that relative rotation is possible. Therefore, in the torque converter 201, for example, the reaction force hydraulic chamber 110 is generated by the reaction force bearing portion 220 forming the reaction force portion 100 supporting the drive plate 10 and the second side holding plate 25 so as to be relatively rotatable. When the reaction force F1 and the pressing force F0 are not completely equal, it is possible to receive a pressing force that cannot be canceled by the reaction force F1, so the axial direction of the front cover 30 and the fluid transmission mechanism 40 can be received. Position fluctuations can be reliably prevented.

  In the above description, the reaction force bearing portion 220 is provided between the drive plate 10 and the second side holding plate 25 and supports the drive plate 10 and the second side holding plate 25 so as to be relatively rotatable. Although not limited to this, the drive plate 10 or the member of the pre-damper mechanism 20 that rotates together with the drive plate 10 and the front cover 30 or the member of the pre-damper mechanism 20 that rotates together with the front cover 30 are relatively rotated. Any support is possible.

  For example, the reaction force bearing portion 220 may be one that rotatably supports the drive plate 10 and the front cover 30. Further, for example, when the hydraulic pressure of the hydraulic fluid in the reaction force hydraulic chamber 110 is adjusted separately from the hydraulic pressure of the hydraulic fluid on the fluid transmission mechanism 40 side of the front cover 30, the reaction force hydraulic chamber 110 is generated. The reaction force F1 to be caused may be larger than the pressing force F0. In this case, the torque converter 201 includes, for example, a reaction force bearing portion 220 between the drive plate 10 and the first side holding plate 24, and the reaction force bearing portion 220 connects the drive plate 10 and the first side holding plate 24. By being configured to support relative rotation, the positional relationship between the first side holding plate 24, the second side holding plate 25, and the drive plate 10 can be properly held. The performance can be stabilized, the proper damper performance can be ensured, and the vibration reduction performance can be improved.

  In the above description, the reaction force portion 100 has been described as including the reaction force hydraulic chamber 110 and the reaction force bearing portion 220. However, the present invention is not limited to this. For example, only the reaction force bearing portion 220 is included. You may make it comprise by.

(Embodiment 3)
FIG. 3 is a cross-sectional view of a main part of a torque converter according to Embodiment 3 of the present invention. The fluid transmission device according to the third embodiment has substantially the same configuration as the fluid transmission device according to the first embodiment, but differs from the fluid transmission device according to the first embodiment in that a strength member is provided on the holding member. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected.

  In the torque converter 301 as the fluid transmission device of the present embodiment, a strength member 330 is provided on the holding member 22 of the pre-damper mechanism 20. The strength member 330 is provided on the first side holding plate 24 that rotates together with the front cover 30 in the holding member 22.

  As described above, the first side holding plate 24 is connected to the front cover 30 via the second side holding plate 25 and the bolt 26 at the radially outer end, and from the radially inner end to the radial direction. A strength member 330 is extended inside.

  The strength member 330 includes an annular plate-shaped portion 331 and a connecting portion 332. The annular plate portion 331 is formed in an annular plate shape coaxial with the rotation axis X, and the radially outer end portion is fixed to the radially inner end portion of the first side holding plate 24. The connecting portion 332 is formed along the axial direction, one end in the axial direction is fixed to the radially outer end of the annular plate-shaped portion 331, and the other end is the central portion in the radial direction of the front cover 30. Connected to A plurality of connecting portions 332 are formed at equal intervals in the circumferential direction with respect to the annular plate-like portion 331. That is, in the strength member 330, the radially inner end portion of the annular plate-shaped portion 331 is connected to the radially central portion of the front cover 30 by the connecting portion 332. The annular plate-like portion 331 and the connecting portion 332 of the strength member 330 and the first side holding plate 24 are all integrally formed of the same member.

  The connecting portion 332 of the strength member 330 passes through the drive plate 10 that is also used as the center holding plate 23. However, the drive plate 10 has a slide portion 10 a formed at the connecting portion 332. The slide portion 10 a is formed through the drive plate 10 as an arc-shaped slit at a portion corresponding to the connecting portion 332 in the drive plate 10. The slide portion 10a is provided in an arc shape at a position where the connecting portion 332 can be inserted into the axial direction. As a result, the slide portion 10 a causes the first side holding plate 24, the second side holding plate 25, and the movement of the connecting portion 332 accompanying the relative rotation of the drive plate 10 also used as the center holding plate 23 to the first side holding plate 24. It is possible to allow the holding plate 24, the second side holding plate 25, and the drive plate 10 serving as the center holding plate 23 to have a predetermined twist angle.

  In the torque converter 301 configured as described above, the strength member 330 extended from the first side holding plate 24 contacts the surface of the front cover 30 on the pre-damper mechanism 20 side, so that the pre-damper of the front cover 30 is provided. The rigidity of the front cover 30 can be increased against deformation toward the mechanism 20 side. As a result, the torque converter 301 is pre-dampered to the front cover 30 by, for example, the fluid transmission mechanism 40 expanding due to the hydraulic pressure of the hydraulic oil in the internal space of the torque converter 301 defined by the front cover 30 and the pump shell 41b. When an axial load is applied to the mechanism 20 side, the strength member 330 supports the front cover 30 to suppress deformation of the front cover 30, for example, deformation to the pre-damper mechanism 20 side. Can do. As a result, the torque converter 301 is deformed so as to deteriorate the damper performance of the pre-damper mechanism 20, for example, the gap between the first side holding plate 24, the second side holding plate 25, and the center holding plate 23 is narrowed. It is possible to reduce deformation that makes it impossible to secure a clearance. As a result, in the torque converter 301, friction (friction) when the first side holding plate 24, the second side holding plate 25, and the center holding plate 23 rotate relative to each other due to the deformation of the pre-damper mechanism 20 increases. This can be prevented, and proper elastic deformation of the damper spring 21 can be prevented from being inhibited.

  According to the torque converter 301 according to the embodiment of the present invention described above, the torque converter 301 causes the reaction force portion 100 to apply the reaction force F1 equivalent to the pressing force F0 to the fluid transmission mechanism 40 from the pre-damper mechanism 20 side. Therefore, fluctuations in the axial position of the front cover 30 and the fluid transmission mechanism 40 can be prevented, thereby preventing increase in friction (friction) in the pre-damper mechanism 20 and inhibition of proper elastic deformation of the damper spring 21. Therefore, vibration reduction performance can be improved.

  Furthermore, according to the torque converter 301 according to the embodiment of the present invention described above, the first side holding plate 24 that is the holding member 22 that rotates together with the front cover 30 and holds the damper spring 21 of the pre-damper mechanism 20 is A radially outer end with respect to a radial direction orthogonal to the axial direction is coupled to the front cover 30, and a strength member 330 extends radially inward from a radially inner end with respect to the radial direction. The inner end portion in the direction is connected to the central portion in the radial direction of the front cover 30. Therefore, in the torque converter 301, the strength member 330 is brought into contact with the surface of the front cover 30 on the pre-damper mechanism 20 side, so that the rigidity of the front cover 30 is reduced against the deformation of the front cover 30 toward the pre-damper mechanism 20 side. Since it can raise, the deformation | transformation which deteriorates the damper performance of the pre-damper mechanism 20 can be reduced. As a result, the torque converter 301 can further improve the damper performance, such as prevention of the generation of a booming noise in the pre-damper mechanism 20, and can further reduce vibration and improve fuel efficiency.

(Embodiment 4)
FIG. 4 is a cross-sectional view of a main part of a torque converter according to Embodiment 4 of the present invention. The fluid transmission device according to the fourth embodiment has substantially the same configuration as the fluid transmission device according to the third embodiment, but differs from the fluid transmission device according to the third embodiment in that a sealing unit is provided. In addition, about the structure, effect | action, and effect which are common in embodiment mentioned above, while overlapping description is abbreviate | omitted as much as possible, the same code | symbol is attached | subjected. Note that the fluid transmission device of the present embodiment also includes the reaction force bearing portion described in the second embodiment.

  In the torque converter 401 as the fluid transmission device of the present embodiment, the pre-damper mechanism 20 is provided with a seal member S3 as a sealing means.

  As described above, the pre-damper mechanism 20 of the present embodiment includes the center holding plate 23, the first side holding plate 24, and the second side holding plate 25 as the holding member 22 that holds the damper spring 21.

  Here, the second side holding plate 25 of the present embodiment is formed such that the radially outer end 25c is bent toward the first side holding plate 24 side. The radially outer end 25c protrudes toward the first side holding plate 24 and is formed in a cylindrical shape coaxial with the rotation axis X. And this radial direction outer side edge part 25c is extended toward the engine side along the axial direction. The radially outer end 25c extends to a position that covers the radially outer side of the center holding plate 23 and the first side holding plate 24. Similarly, the first side holding plate 24 is formed such that the radially outer end 24c is bent toward the engine. The radially outer end 24c protrudes toward the engine and is formed in a cylindrical shape coaxial with the rotation axis X. The inner peripheral surface of the radially outer end portion 25c and the outer peripheral surface of the radially outer end portion 24c are opposed to each other in the radial direction. The startering gear 82 of the present embodiment is provided at the radially outer end 25c of the second side holding plate 25.

  Here, the pre-damper mechanism 20 is disposed in the vicinity of the center holding plate 23, the first side holding plate 24, the center holding portion 23a of the second side holding plate 25, the first side holding portion 24a, and the second side holding portion 25a. A lubricant such as grease for lubricating the sliding portion of the pre-damper mechanism 20 is filled.

  The seal member S3 contacts between the inner peripheral surface of the radially outer end 25c of the second side holding plate 25 and the outer peripheral surface of the radially outer end 24c of the first side holding plate 24, respectively. To be provided. The seal member S3 is formed in an annular shape that is coaxial with the rotation axis X. Thus, the seal member S3 can prevent the leakage of the lubricant through the space between the first side holding plate 24 and the second side holding plate 25 on the radially outer side of the center holding plate 23.

  The torque converter 401 configured as described above prevents the lubricant from leaking between the first side holding plate 24 and the second side holding plate 25 on the radially outer side of the center holding plate 23 by the seal member S3. Therefore, it is possible to prevent the lubricant from leaking radially outward due to the centrifugal force accompanying the rotation of the center holding plate 23, the first side holding plate 24, and the second side holding plate 25. Further, the torque converter 401 prevents the leakage of the lubricant through the space between the first side holding plate 24 and the second side holding plate 25 on the radially outer side of the center holding plate 23 by the seal member S3. It is possible to prevent the lubricant from leaking from the lower side in the vertical direction while the rotation of the center holding plate 23, the first side holding plate 24, and the second side holding plate 25 is stopped.

  Therefore, the torque converter 401 can appropriately hold the lubricant for lubricating the sliding portion of the pre-damper mechanism 20 and can prevent the lubricant from being insufficient. Even if the plate 24, the second side holding plate 25, and the center holding plate 23 are in contact with each other, the friction (friction) occurs when the first side holding plate 24, the second side holding plate 25, and the center holding plate 23 rotate relative to each other. ) Can be suppressed from increasing. Therefore, the torque converter 401 can stabilize the performance of the pre-damper mechanism 20, can ensure the appropriate damper performance reliably, and can improve the vibration reduction performance.

  According to the torque converter 401 according to the embodiment of the present invention described above, the torque converter 401 causes the reaction force portion 100 to apply a reaction force F1 equivalent to the pressing force F0 from the pre-damper mechanism 20 side to the fluid transmission mechanism 40. Therefore, fluctuations in the axial position of the front cover 30 and the fluid transmission mechanism 40 can be prevented, thereby preventing increase in friction (friction) in the pre-damper mechanism 20 and inhibition of proper elastic deformation of the damper spring 21. Therefore, vibration reduction performance can be improved.

  Furthermore, according to the torque converter 401 according to the embodiment of the present invention described above, the pre-damper mechanism 20 includes the center holding plate 23 that holds the damper spring 21 and the front cover of the center holding plate 23 with respect to the axial direction. The first side holding plate 24 that holds the damper spring 21 on the side opposite to the side 30, and the second side that holds the damper spring 21 on the side on the front cover 30 side of the center holding plate 23 with respect to the axial direction. A holding plate 25 and a seal member S3 for preventing leakage of lubricant through the space between the first side holding plate 24 and the second side holding plate 25 on the outer side in the radial direction of the center holding plate 23 are provided. Therefore, the torque converter 401 prevents the lubricant from leaking between the first side holding plate 24 and the second side holding plate 25 on the radially outer side of the center holding plate 23 by the seal member S3. It is possible to suppress an increase in friction (friction) when the first side holding plate 24, the second side holding plate 25, and the center holding plate 23 rotate relative to each other, and prevent the pre-damper mechanism 20 from generating a booming noise. The damper performance such as the above can be further improved, and the vibration can be further reduced and the fuel consumption can be improved.

  In addition, the fluid transmission device according to the above-described embodiment of the present invention is not limited to the above-described embodiment, and various modifications can be made within the scope described in the claims. The fluid transmission device according to the embodiment of the present invention may be configured by combining a plurality of the embodiments described above. For example, the strength member of the present invention may be provided in the fluid transmission device of the second embodiment.

  In the above description, the fluid transmission unit has been described as including the inner damper mechanism 70 separately from the pre-damper mechanism 20 as the damper unit. However, the present invention is not limited to this, and the inner damper mechanism 70 is not included. There may be.

  In the above description, the second side holding member has been described as being formed separately from the front cover 30, but it may be shared by the front cover 30 as the second member.

  In the above description, the lock-up clutch mechanism 50 includes the friction material 55 provided on the lock-up piston 51 as the engagement member and the front cover inner wall surface 34 of the front cover 30 as the second member. Although described as being configured, the friction material 55 is provided on the inner wall surface 34 of the front cover, and the friction engagement surface 52 is configured by the friction material 55 in the lockup piston 51 and the wall surface facing the friction material 55 in the axial direction. You may do it.

  In the above description, the lock-up piston 51 as the engaging member of the lock-up clutch mechanism 50 is supported so as to be relatively movable along the axial direction with respect to the inner damper mechanism 70, so that the front cover 30 is supported. Although it has been described that it can approach and separate and can be frictionally engaged via the frictional engagement surface 52, it is not limited thereto. For example, the lock-up piston 51 of the lock-up clutch mechanism 50 is integrated with the entire inner damper mechanism 70 because the entire inner damper mechanism 70 is supported so as to be movable relative to the hub 61 along the axial direction. Alternatively, the front cover 30 may be moved closer to and away from the front cover 30 and frictionally engaged via the friction engagement surface 52.

  In the above description, the lockup clutch mechanism 50 has been described as being provided between the front cover 30 and the inner damper mechanism 70 in the axial direction, but is not limited thereto. For example, the lockup clutch mechanism 50 may be provided between the inner damper mechanism 70 and the turbine shell 42b of the fluid transmission mechanism 40 in the axial direction. In this case, the lock-up clutch mechanism 50 includes, for example, a first engagement member fixed to the hub 61 so as to be integrally rotatable, and a second engagement connected to the second side holding plate 75 of the inner damper mechanism 70. The member may be configured to be relatively movable in the axial direction, and the first engagement member and the second engagement member may be configured to frictionally engage with each other via the friction engagement surface.

  In the above description, the inner damper mechanism 70 has been described as a damper means in which an elastic body is provided in the transmission path of the driving force, but is not limited thereto. That is, the inner damper mechanism 70 may be a so-called dynamic damper (dynamic vibration absorber).

  As described above, the fluid transmission device according to the present invention can improve the vibration reduction performance, and can be applied to various fluid transmission devices that can transmit the driving force generated by the driving source via the working fluid. It is suitable to apply.

It is principal part sectional drawing of the torque converter which concerns on Embodiment 1 of this invention. It is principal part sectional drawing of the torque converter which concerns on Embodiment 2 of this invention. It is principal part sectional drawing of the torque converter which concerns on Embodiment 3 of this invention. It is principal part sectional drawing of the torque converter which concerns on Embodiment 4 of this invention.

Explanation of symbols

1, 201, 301, 401 Torque converter (fluid transmission device)
10 Drive plate (first member)
20 Pre-damper mechanism (damper means)
21 Damper spring (elastic body)
22 holding member 23 center holding plate (center holding member)
24 1st side holding plate (1st side holding member)
25 Second side holding plate (second side holding member)
30 Front cover (second member)
31 Front cover body 31a bulging part 31b communication path 32 front cover flange part 33 front cover boss part 33a columnar part 33b annular projecting part 33c communication path 34 front cover inner wall surface 40 fluid transmission mechanism (fluid transmission means)
41 Pump impeller 42 Turbine liner 43 Stator 44 One-way clutch 50 Lock-up clutch mechanism 51 Lock-up piston 52 Friction engagement surface 53 Working fluid flow path 54 Piston hydraulic chamber 55 Friction material 60 Output shaft 61 Hub 70 Inner damper mechanism 71 Damper spring 72 Holding member 73 Center holding plate 74 First side holding plate 75 Second side holding plate 80 Crankshaft 91 Hydraulic control device 92 ECU
93 Supply / discharge opening 94 Supply / discharge passage 95 Pressing force acting surface 100 Reaction force part (reaction force means)
110 Reaction force hydraulic chamber (Reaction force pressure chamber)
111 Reaction force action surface 220 Reaction force bearing portion 330 Strength member 331 Ring plate-like portion 332 Connection portion A Fluid transmission mechanism space portion B Clutch space portion S3 Seal member (sealing means)

Claims (6)

A damper means that connects the first member and the second member so as to be relatively rotatable via an elastic body, and is capable of transmitting a driving force transmitted from a driving source to the first member to the second member via the elastic body. When,
A fluid transmission that is provided on the opposite side of the damper means with respect to the axial direction of the output shaft and that can transmit the driving force transmitted to the second member to the output shaft via a working medium. Means,
Reaction force means for applying a reaction force equivalent to the pressing force from the damper means side to the fluid transmission means to which a pressing force to the damper means side along the axial direction acts due to the pressure of the working medium. Characterized by comprising,
Fluid transmission device. The reaction force means has a reaction force pressure chamber that is provided on the damper means side of the second member with respect to the axial direction and applies the reaction force by the pressure of a working medium supplied to the inside.
The fluid transmission device according to claim 1. The fluid transmission means supplies or discharges the working medium through a supply / discharge opening provided on the fluid transmission means side of the second member with respect to the axial direction, and the axial direction with respect to the axial direction. The pressing force acts by the pressure of the working medium acting on the pressing force acting surface facing the supply / discharge opening,
The reaction force means has an area of a reaction force acting surface on which the reaction force due to the pressure of the working medium in the reaction force pressure chamber is set equal to an area of the supply / discharge opening, and the reaction force pressure chamber. Communicates with the fluid transmission means side of the second member,
The fluid transmission device according to claim 2. The reaction force means supports the member of the damper means that rotates together with the first member or the first member and the member of the damper means that rotates together with the second member or the second member so as to be relatively rotatable. Having a reaction force bearing,
The fluid transmission device according to any one of claims 1 to 3. The holding member that rotates together with the second member and holds the elastic body of the damper means is connected to the second member at the radially outer end with respect to the radial direction orthogonal to the axial direction, and to the radial direction. A strength member extends radially inward from the radially inner end, and a radially inner end of the strength member is connected to a radially central portion of the second member.
The fluid transmission device according to any one of claims 1 to 4. The damper means includes a center holding member that holds the elastic body, and a first side holding that holds the elastic body on a side opposite to the second member of the center holding member with respect to the axial direction. A member, a second side holding member that holds the elastic body at a side of the center holding member on the second member side with respect to the axial direction, and the first side at a radially outer side of the center holding member Sealing means for preventing leakage of the lubricant between the side holding member and the second side holding member,
The fluid transmission device according to any one of claims 1 to 5.

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