JP5282552B2 - Fluid transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic transmission device improving the performance of a lock-up means. <P>SOLUTION: The hydraulic transmission device includes the lock-up means 40 having a first engagement member 41, a second engagement member 42, and a hydraulic chamber 45, and applies a pressing force to the second engagement member 42 by a working fluid of the hydraulic chamber 45 for frictionally engaging the first engagement member 41 with the second engagement member 42 so as to transmit the driving force transmitted to a front cover 10 to an output shaft 50 via the second engagement member 42 and the first engagement member 41. In the lock-up means 40, a sealing means 48 is provided in the front cover 10 to prevent the working fluid from leaking between a radial inner section 42a of the second engagement member 42 relative to the radial direction perpendicular to the axial direction, and a facing portion 11a facing the radial inner end 42a of the second engagement member 42 in the radial direction. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a fluid transmission device, and more particularly to a fluid transmission device including a lock-up means.

  As a conventional fluid transmission device including a lock-up clutch as a lock-up means, for example, a fluid transmission device with a lock-up clutch described in Patent Document 1 includes a main member of a damper mass of a damper mechanism when the lock-up clutch is ON. The frictional engagement between the main member of the damper mass and the lockup piston provided between the turbine runner allows the driving force transmitted from the engine to the front cover to be transmitted to the lockup piston via the damper mechanism. Directly transmitted to the output shaft without oil. The lock-up piston engages with the main member of the damper mass according to the pressure difference between the working fluids on both axial sides. The fluid transmission device with a lock-up clutch described in Patent Document 1 is provided with a seal ring between the radially inner end of the lock-up piston and a hub as an output member. A seal ring is also provided between an annular protrusion formed at an intermediate portion between the radially outer end portion and the radially inner end portion of the member and a cylindrical portion protruding from the inner surface of the front cover. The two seal rings are provided in the hydraulic chamber between the main member of the damper mass and the front cover in order to prevent the main member of the damper mass and the lock-up piston from moving in the axial direction when hydraulic pressure is applied. The position in the radial direction is substantially the same so that the force acting on the main member due to the hydraulic pressure of the cylinder and the force acting on the lockup piston due to the hydraulic pressure in the space portion on the turbine runner side from the lockup piston are substantially balanced. It is provided to become.

JP-A-5-187518

  By the way, in the fluid transmission device with a lock-up clutch described in Patent Document 1 as described above, for example, a lock-up operation such as an increase in torque capacity that can be transmitted in the lock-up clutch and an improvement in responsiveness of the lock-up operation. A further improvement in clutch performance has been desired.

  Then, an object of this invention is to provide the fluid transmission apparatus which can improve the performance of a lockup means.

In order to achieve the above object, a fluid transmission device according to the first aspect of the present invention comprises a fluid transmission means capable of transmitting a driving force transmitted from a driving source to a front cover to an output shaft via a working fluid; A first engagement member provided on the fluid transmission means side of the cover and rotatable integrally with the output shaft, and connected to the front cover on the fluid transmission means side of the front cover along the axial direction of the output shaft A second engagement member movable relative to the first engagement member; and the second engagement member provided between the second engagement member and the front cover with respect to the axial direction by an internal working fluid. A hydraulic chamber that applies a pressing force to the engaging member toward the first engaging member, and the pressing force is applied to the second engaging member by the working fluid in the hydraulic chamber. Joint member and the second engaging portion And a lockup means capable of transmitting the driving force transmitted to the front cover to the output shaft via the second engagement member and the first engagement member. The lock-up means includes a radial inner end of the second engagement member with respect to a radial direction orthogonal to the axial direction, and the radial inner end of the second engagement member and the radial direction in the front cover. A sealing means for preventing leakage of the working fluid is provided between the first engaging member and the second engaging member with respect to the axial direction. A working fluid flow path formed between the first engagement member and the second engagement, and is formed so as to be able to communicate with the inside of the fluid transmission means and the outside of the hydraulic chamber in the radial direction. When the frictional engagement with the member, the fluid The working fluid flows from the inner side of the reaching means to the working fluid flow path side, and the first engaging member and the second engaging member are the first engaging member and the second engaging member. The first engagement member is located on the upstream side of the flow of the working fluid and the second engagement member is located on the downstream side, and the radial direction of the first engagement member Is set relatively long, the radial length of the second engagement member is set relatively short, and the radial length of the first engagement member is the second engagement. It is set longer than the radial length of the joint member .

  In the fluid transmission device according to a second aspect of the present invention, the radially inner end portion of the second engagement member is formed to protrude toward the front cover side along the axial direction, and the opposing portion of the front cover Is formed such that the radially inner end of the second engagement member can be inserted inside the front cover in the radial direction, and the sealing means is provided on the radially inner end of the second engagement member. It is provided in contact with an outer peripheral surface and an inner peripheral surface of the facing portion of the front cover.

In the fluid transmission device according to a third aspect of the present invention, the first engaging member is characterized in that a radially outer end in the radial direction is curved toward the second engaging member.

In the fluid transmission device according to a fourth aspect of the present invention, the first engagement member is provided to be movable relative to the second engagement member along the axial direction.

In the fluid transmission device according to the fifth aspect of the present invention, the guide that receives the flow of the working fluid from the working fluid flow path side in the hydraulic chamber and guides it toward the surface of the second engaging member on the hydraulic chamber side. Means are provided.

In the fluid transmission device according to the sixth aspect of the present invention, a plurality of elastic bodies provided between the second engagement member and the front cover with respect to the axial direction are held so as to be able to transmit a driving force and the second. A center holding member provided so that the engaging member can rotate integrally and relatively move in the axial direction, and the plurality of elastic members provided between the second engaging member and the center holding member with respect to the axial direction. A side holding member connected to the front cover so as to be able to rotate integrally with the front cover, the front cover and the second engagement member being interposed via the plurality of elastic bodies. Damper means to be connected is provided, and the guide means is provided at a radially outer end of the side holding member.

In the fluid transmission device according to the seventh aspect of the invention, the first engagement member covers the radially outer end of the second engagement member at the radially outer end with a predetermined interval in the radial direction. It has a cover part.

  According to the fluid transmission device of the present invention, the lockup means includes the radial inner end of the second engagement member with respect to the radial direction orthogonal to the axial direction, and the radial direction of the second engagement member at the front cover. Since the sealing means for preventing leakage of the working fluid is provided between the inner end portion and the opposing portion in the radial direction, the performance of the lockup means 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, the torque converter as the fluid transmission device is configured to be substantially symmetric with respect to the rotation axis X of the output shaft shown in FIG. 1 as the central axis. Therefore, in FIG. As a central axis, only one side is illustrated. Unless otherwise specified, only one side is described with the rotation axis X as the central axis, and the description on the other side is omitted as much as possible. In the following description, unless otherwise specified, the direction along the rotation axis X is referred to as the axial direction, the direction orthogonal to the rotation axis X, that is, the direction orthogonal to the axial direction is referred to as the radial direction, and the rotation axis The direction around 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.

  As shown in FIG. 1, a torque converter 1 as a fluid transmission device according to the first embodiment includes a front cover 10, a fluid transmission mechanism 20 as a fluid transmission means, a damper mechanism 30 as a damper means, and a lockup means. As a lock-up clutch mechanism 40 and an output shaft 50. The torque converter 1 is arranged in the order of the front cover 10, the damper mechanism 30, the lock-up clutch mechanism 40, and the fluid transmission mechanism 20 from the engine side to the output shaft side with respect to the axial direction.

  As shown in FIG. 1, the front cover 10 transmits a driving force of an engine (not shown) that is a driving source. The front cover 10 includes a main body portion 11, a flange portion 12, and a set block 13.

  The main body 11 is formed in a disk shape that is coaxial with the rotation axis X that is the central axis of the output shaft 50. The flange portion 12 is formed so as to protrude from the radially outer end portion of the main body portion 11 toward the output shaft. The flange portion 12 is formed in a cylindrical shape coaxial with the rotation axis X.

  The set block 13 is connected to a drive plate 100 that is an input member for driving force from the engine. A plurality of set blocks 13 are formed in the circumferential direction in the vicinity of the outer peripheral end of the surface of the main body 11 on the engine side. Each set block 13 is fastened to the drive plate 100 by screwing the bolts 14 inserted into the through holes of the drive plate 100.

  Here, the drive plate 100 is formed in a disk shape coaxial with the rotation axis X, and is fastened to an engine output shaft 110 of an engine (not shown) by a connecting member 120 (for example, a bolt). Therefore, the driving force of the engine is transmitted to the drive plate 100, and the driving force transmitted to the drive plate 100 is transmitted to the front cover 10. That is, the driving force of the engine is transmitted to the main body 11 through the set block 13 of the front cover 10.

  Further, the front cover 10 is formed with a connecting groove portion 12a. The connecting groove portion 12a constitutes a part of the connecting portion 60, and a portion of the front cover 10 that faces the connecting projection portion 32a at the radially outer end of the center holding plate 32, which will be described later, in the radial direction, that is, a flange. It is formed in the part 12.

  The connecting groove portion 12a has a shape in which the cross-sectional shape in the radial direction is recessed from the inner peripheral surface of the flange portion 12 toward the radially outer side, and from the end on the output shaft side of the flange portion 12 to the central portion in the axial direction of the flange portion 12 It is formed along the axial direction. A plurality of connecting groove portions 12 a are formed at equal intervals in the circumferential direction with respect to the front cover 10.

  The fluid transmission mechanism 20 is a fluid transmission means, and transmits the driving force transmitted to the front cover 10 to the output shaft 50 via the working fluid (hydraulic oil). The fluid transmission mechanism 20 includes a pump impeller 21, a turbine liner 22, a stator 23, a one-way clutch 24, and hydraulic oil that is a working fluid interposed between the pump impeller 21 and the turbine liner 22. .

  The pump impeller 21 transmits the driving force from the engine transmitted to the front cover 10, and transmits the transmitted driving force to the turbine liner 22 via hydraulic oil. The pump impeller 21 is configured such that the radially outer end portion of the pump shell 21b to which the plurality of pump blades 21a are fixed is fixed to the output shaft side end portion of the flange portion 12 of the front cover 10 by, for example, welding. 10 is fixed. That is, the pump impeller 21 rotates integrally with the front cover 10, and the driving force from the engine transmitted to the front cover 10 is transmitted to each pump blade 21a via the pump shell 21b. In the pump impeller 21, the radially inner end of the pump shell 21b is fixed to the sleeve 51 by, for example, welding. The sleeve 51 is connected to a device that operates by rotational movement, such as an oil pump (not shown).

  The turbine liner 22 transmits the driving force from the engine transmitted from the pump impeller 21 via the hydraulic oil to the output shaft 50. Here, the output shaft 50 is, for example, an input shaft of a transmission (not shown) disposed on the output shaft side. In the turbine liner 22, a radially inner end portion of a turbine shell 22b to which a plurality of turbine blades 22a facing the pump blade 21a in the axial direction is fixed is fixed to the hub 52 by, for example, rivets 52a.

  Here, the hub 52 is fixed to the output shaft 50 by, for example, spline fitting of splines formed on the inner peripheral surface of the hub 52 and the outer peripheral surface of the output shaft 50. That is, in the turbine liner 22, the turbine shell 22 b rotates integrally with the output shaft 50 via the hub 52, and the pump impeller 21 that configures the fluid transmission mechanism 20 by the turbine liner 22 rotating integrally with the output shaft 50. The driving force from the engine transmitted through the hydraulic oil and the turbine liner 22 is transmitted to the output shaft 50.

  The stator 23 has a plurality of stator blades 23 a formed in the circumferential direction, and is disposed between the pump impeller 21 and the turbine liner 22. The stator 23 is for changing the flow of hydraulic fluid circulating between the pump impeller 21 and the turbine liner 22 and obtaining a predetermined driving force characteristic based on the driving force transmitted from the engine.

  The one-way clutch 24 supports the stator 23 so as to be rotatable in only one direction with respect to the housing 53 that houses the torque converter 1. The one-way clutch 24 is rotatably supported by bearings 25 and 26 with respect to the sleeve 51 and the hub 52, respectively.

  The damper mechanism 30 is damper means, and connects the front cover 10 and a lockup piston 42 of a lockup clutch mechanism 40 described later via a plurality of damper springs 31 as a plurality of elastic bodies. Here, since the rear holding plate 33 of the damper mechanism 30 is also used as the lock-up piston 42, the damper mechanism 30 includes the lock-up piston 42 also used as the rear holding plate 33 and the front cover 10. They are connected via a damper spring 31. Furthermore, the damper mechanism 30 connects the lockup piston 42, which is also used as the rear holding plate 33, via the plurality of damper springs 31 and the front cover 10 so as to be relatively rotatable.

  The damper mechanism 30 is housed inside the front cover 10 and includes a plurality of damper springs 31, a center holding plate 32, a rear holding plate 33, and a front holding plate 34. The damper mechanism 30 is arranged in the order of the front holding plate 34, the center holding plate 32, the plurality of damper springs 31, and the rear holding plate 33 from the engine side to the output shaft side in the axial direction. The damper mechanism 30 transmits the driving force transmitted from the engine to the front cover 10 to the rear holding plate 33 and the front holding plate 34 via the center holding plate 32 and the plurality of damper springs 31.

  The plurality of damper springs 31 are, for example, a plurality of coil springs, and are provided between the front cover 10 and a lockup plate 41 of a lockup clutch mechanism 40 described later in the axial direction. The damper spring 31 transmits the driving force of the engine transmitted from the front cover 10 to the center holding plate 32 to the rear holding plate 33 and the front holding plate 34. The plurality of damper springs 31 include an outer damper spring 31a and an inner damper spring 31b. In the outer damper spring 31a and the inner damper spring 31b, the outer damper spring 31a is disposed on the radially outer side, and the inner damper spring 31b is disposed on the radially inner side of the outer damper spring 31a.

  The center holding plate 32, the rear holding plate 33, and the front holding plate 34 are formed in an annular plate shape that is coaxial with the rotation axis X, and are arranged between the front cover 10 and a lockup plate 41 described later in the axial direction. Has been. The rear holding plate 33 is formed so that the inner diameter is smaller than the inner diameter of the front holding plate 34.

  The center holding plate 32 is provided on the front cover 10 so as to be able to rotate integrally and relatively move in the axial direction, and holds the outer damper spring 31a and the inner damper spring 31b so as to be able to transmit driving force. The center holding plate 32 has a connecting projection 32a, an outer center holding part 32b, and an inner center holding part 32c.

  The connecting projection 32 a is formed at the radially outer end of the center holding plate 32 (that is, the end on the outer peripheral surface side). The connecting projection 32a constitutes the connecting portion 60 together with the connecting groove 12a of the front cover 10 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 32.

  The connecting projection 32a is arranged in the radial direction of the center holding plate 32 so as to face the connecting groove 12a of the flange 12 in the radial direction in a state where the center holding plate 32 is inserted inside the flange 12 of the front cover 10. It is formed to protrude radially outward from the outer end. The protruding amount of the connecting projection 32a is set so that the connecting protrusion 32a is inserted into the connecting groove 12a in a state where the center holding plate 32 is inserted inside the flange portion 12.

  The center holding plate 32 is inserted into the inside of the flange portion 12 of the front cover 10, and the connecting projection portion 32 a forming the connecting portion 60 is inserted and engaged with the connecting groove portion 12 a, so that the center holding plate 32 is attached to the front cover 10. Relative rotation is restricted and relative movement along the axial direction is allowed. That is, the center holding plate 32 is connected to the front cover 10 so as to be integrally rotatable with the front cover 10 and to be movable in the axial direction at the connecting portion 60 constituted by the connecting protrusion 32a and the connecting groove 12a. The driving force is transmitted from the front cover 10 so as to be transmitted. Therefore, the driving force from the engine transmitted to the front cover 10 is transmitted to the center holding plate 32 of the damper mechanism 30 through the connecting portion 60. The opening end portion on the output shaft side of the connecting groove portion 12a is closed by fixing the radially outer end portion of the pump shell 21b to the flange portion 12 of the front cover 10. Further, the damper mechanism 30 moves in the axial direction with respect to the front cover 10 as a whole by connecting the center holding plate 32 so as to be movable in the axial direction with respect to the front cover 10 at the connecting portion 60. can do.

  The outer center holding part 32b and the inner center holding part 32c are inserted with an outer damper spring 31a and an inner damper spring 31b, respectively, and hold the outer damper spring 31a and the inner damper spring 31b. Both the outer center holding part 32 b and the inner center holding part 32 c are slits formed in an arc shape along the circumferential direction of the center holding plate 32. In the center holding plate 32, the outer center holding portion 32b and the inner center holding portion 32c are provided such that the outer center holding portion 32b is provided on the radially outer side, while the inner center holding portion 32c is provided on the radially inner side. The outer center holding portion 32b holds the outer damper spring 31a inserted therein. The inner center holding portion 32c holds the inner damper spring 31b inserted therein. A plurality of outer center holding portions 32 b and inner center holding portions 32 c are formed at equal intervals in the circumferential direction with respect to the center holding plate 32.

  Each outer center holding portion 32b has a circumferential length set to a length that can be held in a state where each outer damper spring 31a is urged. Therefore, when the outer damper spring 31a is held by the outer center holding portion 32b, both end portions in the circumferential direction of the outer center holding portion 32b come into contact with both end portions of the outer damper spring 31a. That is, the outer damper spring 31a contacts both ends in the circumferential direction of each outer center holding portion 32b and is held in a state of being biased between both ends. Each inner center holding portion 32c has a circumferential length set to a length that can be held in a state where each inner damper spring 31b is urged. Therefore, when the inner damper spring 31b is held by the inner center holding portion 32c, both end portions in the circumferential direction of the inner center holding portion 32c come into contact with both end portions of the inner damper spring 31b, respectively. That is, the inner damper spring 31b contacts both ends in the circumferential direction of each inner center holding portion 32c and is held in a state of being biased between the both ends.

  Accordingly, the center holding plate 32 includes an outer damper spring 31a, an inner damper spring 31b, and a circumferential end contact portion between the outer center holding portion 32b, the inner center holding portion 32c, the outer damper spring 31a, and the inner damper spring 31b. The driving force can be transmitted between the two.

  The rear holding plate 33 and the front holding plate 34 hold a part of the plurality of outer damper springs 31a and the plurality of inner damper springs 31b, which are held at the central portion in the axial direction by the center holding plate 32, so that the driving force can be transmitted. is there.

  The rear holding plate 33 and the front holding plate 34 are lateral to the axial direction of the center holding plate 32. Here, the rear holding plate 33 is a lockup plate 41 side (output shaft side), which will be described later, and the front holding plate 34 is a front cover. It is provided on the 10 side (engine side).

  In the rear holding plate 33 and the front holding plate 34, a center holding plate 32 is disposed together with a plurality of outer damper springs 31a and inner damper springs 31b in a space portion between the rear holding plate 33 and the front holding plate 34 with respect to the axial direction. The center holding plate 32 and the plurality of outer damper springs 31a and inner damper springs 31b are sandwiched and held. The rear holding plate 33 and the front holding plate 34 hold the center holding plate 32 so as to be relatively rotatable with both sides in the axial direction interposed therebetween.

  Here, the rear holding plate 33 and the front holding plate 34 are integrated with the center holding plate 32 sandwiched by, for example, rivets 61. A sleeve 62 is provided between the rear holding plate 33 and the front holding plate 34 integrated by the rivet 61. The sleeve 62 has a cylindrical shape, and the rivet 61 is provided so as to be inserted into the sleeve 62. The sleeve 62 acts as a spacer in the axial direction between the rear holding plate 33 and the front holding plate 34, and appropriately fixes the relative positional relationship between the rear holding plate 33 and the front holding plate 34 in the axial direction. The rear holding plate 33 and the front holding plate 34 are assembled so as to be rotatable relative to the center holding plate 32 on both sides in the axial direction of the center holding plate 32 via the rivets 61 and the sleeve 62. Thus, when the rear holding plate 33, the front holding plate 34, and the center holding plate 32 rotate relatively, the sleeve 62 is interposed between the rear holding plate 33 and the front holding plate 34, and the rear holding plate 33. By ensuring an appropriate clearance between the front holding plate 34 and the center holding plate 32, this relative rotation is performed smoothly.

  The rivet 61 and the sleeve 62 pass through the center holding plate 32. However, the center holding plate 32 is formed with a slide portion 32 d at the rivet 61 and the sleeve 62. The slide portion 32 d is formed through the center holding plate 32 as an arc-shaped slit at a portion corresponding to the rivet 61 and the sleeve 62 in the center holding plate 32. The slide portion 32d is provided in an arc shape at a position where the rivet 61 and the sleeve 62 can be inserted in the axial direction. As a result, the slide portion 32d allows the rear holding plate 33, the front holding plate 34, and the center holding plate 32 to move with respect to the rear holding plate 33, the front holding plate 34, and the center holding plate 32 when the rivet 61 and the sleeve 62 move. The plate 32 can be allowed to have a predetermined twist angle.

  The rear holding plate 33 has an outer rear holding portion 33a and an inner rear holding portion 33b, and the front holding plate 34 has an outer front holding portion 34a and an inner front holding portion 34b. The outer rear holding portion 33a and the inner rear holding portion 33b are provided on a wall surface of the rear holding plate 33 that faces the center holding plate 32, that is, a wall surface on the engine side. The outer front holding portion 34a and the inner front holding portion 34b are provided on the wall surface of the front holding plate 34 that faces the center holding plate 32, that is, the wall surface on the output shaft side.

  The outer rear holding portion 33a, the inner rear holding portion 33b, the outer front holding portion 34a, and the inner front holding portion 34b are respectively arranged in the outer damper springs 31a and inner damper springs 31b whose central portions in the axial direction are held by the center holding plate 32. A part of the container is accommodated and held.

  The outer rear holding portion 33a and the inner rear holding portion 33b are formed by recessing the engine-side wall surface of the rear holding plate 33 toward the output shaft side (the side opposite to the center holding plate 32 side). The outer rear holding portion 33 a and the inner rear holding portion 33 b are formed in an arc shape along the circumferential direction of the rear holding plate 33. In the rear holding plate 33, the outer rear holding portion 33a and the inner rear holding portion 33b are provided such that the outer rear holding portion 33a is provided on the radially outer side, while the inner rear holding portion 33b is provided on the radially inner side. A plurality of outer rear holding portions 33 a and inner rear holding portions 33 b are formed at equal intervals in the circumferential direction with respect to the rear holding plate 33.

  The outer front holding portion 34a and the inner front holding portion 34b are formed by recessing the wall surface on the output shaft side of the front holding plate 34 toward the engine side (the side opposite to the center holding plate 32 side). The outer front holding part 34 a and the inner front holding part 34 b are formed in an arc shape along the circumferential direction of the front holding plate 34. In the front holding plate 34, the outer front holding portion 34a and the inner front holding portion 34b are provided such that the outer front holding portion 34a is provided on the radially outer side, while the inner front holding portion 34b is provided on the radially inner side. A plurality of outer front holding portions 34 a and inner front holding portions 34 b are formed at equal intervals in the circumferential direction with respect to the front holding plate 34.

  Each outer rear holding portion 33a and each outer front holding portion 34a are formed at positions that face the outer center holding portion 32b of the center holding plate 32 in the axial direction. Each inner rear holding portion 33b and each inner front holding portion 34b are formed at positions facing the inner center holding portion 32c of the center holding plate 32 in the axial direction.

  Therefore, in the damper mechanism 30, the outer center holding portion 32b of the center holding plate 32 holds the center portion (the center portion in the axial direction) of each outer damper spring 31a, and the outer rear holding portion 33a of the rear holding plate 33 is each outer side. The damper spring 31a accommodates and holds the output shaft side portion from the outer center holding portion 32b, while the outer front holding portion 34a of the front holding plate 34 receives and holds the engine side portion from the outer center holding portion 32b. In the damper mechanism 30, the inner center holding portion 32c of the center holding plate 32 holds the center portion (the center portion in the axial direction) of each inner damper spring 31b, and the inner rear holding portion 33b of the rear holding plate 33 is each inner damper spring. 31b accommodates and holds the output shaft side portion from the inner center holding portion 32c, while the inner front holding portion 34b of the front holding plate 34 receives and holds the engine side portion from the inner center holding portion 32c.

  Then, both end portions in the circumferential direction of each outer rear holding portion 33a and each outer front holding portion 34a are both end portions of the outer damper spring 31a in a state where each outer damper spring 31a is held by each outer center holding portion 32b. In the circumferential direction and can be contacted. Both end portions in the circumferential direction of each inner rear holding portion 33b and each inner front holding portion 34b are respectively connected to both end portions of the inner damper spring 31b in a state where each inner damper spring 31b is held in each inner center holding portion 32c. It faces in the direction and can be contacted. As a result, the rear holding plate 33 and the front holding plate 34 are arranged around the outer rear holding portion 33a, the inner rear holding portion 33b, the outer front holding portion 34a, the inner front holding portion 34b, the outer damper spring 31a, and the inner damper spring 31b. The driving force can be transmitted between the outer damper spring 31a and the inner damper spring 31b in the direction end portion contact portion.

  That is, the outer damper springs 31a and the inner damper springs 31b are respectively arranged at the outer center holding part 32b, the inner center holding part 32c of the center holding plate 32, the outer rear holding part 33a of the rear holding plate 33, the inner rear holding part 33b and the front. The holding plate 34 is held by the outer front holding portion 34a and the inner front holding portion 34b, and the driving force can be transmitted between the center holding plate 32, the rear holding plate 33, and the front holding plate 34.

  The damper mechanism 30 configured as described above transmits the driving force from the engine transmitted to the front cover 10 to the center holding plate 32 through the connecting portion 60. The damper mechanism 30 transmits the driving force transmitted to the center holding plate 32 to the outer damper spring 31a and the inner damper spring 31b from the circumferential ends of the outer center holding portion 32b and the inner center holding portion 32c. The damper mechanism 30 applies the driving force transmitted to the outer damper spring 31a and the inner damper spring 31b to the outer end portions of the outer rear holding portion 33a, the inner rear holding portion 33b, the outer front holding portion 34a, and the inner front holding portion 34b in the circumferential direction. To the rear holding plate 33 and the front holding plate 34. Therefore, the driving force from the engine transmitted to the front cover 10 is transmitted to the rear holding plate 33 and the front holding plate 34 via the outer damper spring 31a and the inner damper spring 31b, and rotates in the same direction as the front cover 10. .

  During this time, the outer damper springs 31a and the inner damper springs 31b are respectively connected to the circumferential end of the outer center holding portion 32b of the center holding plate 32, the rear holding plate 33, the outer rear holding portion 33a of the front holding plate 34, and the outer side. Between the circumferential end portion of the front holding portion 34a or the circumferential end portion of the inner center holding portion 32c of the center holding plate 32 and the rear holding plate 33, the inner rear holding portion 33b of the front holding plate 34, and the inner front holding portion. It is elastically deformed according to the magnitude of the transmitted driving force while being held between the circumferential ends of the portion 34b.

  The lockup clutch mechanism 40 is a lockup means, and transmits the driving force transmitted to the front cover 10 to the output shaft 50 via the lockup piston 42 and the lockup plate 41. That is, the lockup clutch mechanism 40 directly transmits the driving force from the engine transmitted to the front cover 10 to the output shaft 50 without using the working fluid of the fluid transmission mechanism 20.

  The lockup clutch mechanism 40 includes a lockup plate 41 as a first engagement member, a lockup piston 42 as a second engagement member, a friction engagement surface 43, a working fluid flow path 44, and a hydraulic chamber. Piston hydraulic chamber 45. In the present embodiment, the friction engagement surface 43 of the lockup clutch mechanism 40 includes a friction material 46 provided on the lockup plate 41 and an opposing wall surface 47 that is a wall surface facing the friction material 46 in the axial direction in the lockup piston 42. It consists of.

  Here, the lock-up piston 42 of the lock-up clutch mechanism 40 is also used as the rear holding plate 33 of the damper mechanism 30 as described above. In other words, the lock-up piston 42 is also the rear holding plate 33 that constitutes a part of the damper mechanism 30.

  The lock-up clutch mechanism 40 includes a lock-up piston 42 (rear holding plate 33), an opposing wall surface 47 that forms one surface of the friction engagement surface 43, a friction engagement member from the engine side to the output shaft side with respect to the axial direction. The friction material 46 that forms the other surface of the mating surface 43 and the lock-up plate 41 are arranged in this order.

  The lockup plate 41 is a first engagement member, and is provided on the fluid transmission mechanism 20 side of the front cover 10 and can rotate integrally with the output shaft 50. The lockup plate 41 is formed in an annular plate shape coaxial with the rotation axis X, and is disposed between the turbine liner 22 and the rear holding plate 33 of the damper mechanism 30 that is also used as the lockup piston 42 in the axial direction. Has been. That is, the lockup plate 41 is provided in a space defined by the front cover 10 and the pump shell 21b of the fluid transmission mechanism 20 and filled with the working fluid (working oil). The lock-up plate 41 is fixed to the hub 52 by, for example, a rivet 52a along with the radially inner end of the turbine shell 22b at the radially inner end (that is, the inner circumferential end). Therefore, the lockup plate 41 is fixed to the output shaft 50 via the hub 52 and can rotate together with the hub 52 and the output shaft 50.

  In addition, the lockup plate 41 has a radially outer end (that is, an end on the outer peripheral surface side) 41a in the radial direction with respect to the inner peripheral surface of the pump shell 21b, here, the inner peripheral surface of the pump shell 21b. It extends to a position at a predetermined interval. The lock-up plate 41 is curved so that the radially outer end 41a is bent toward the rear holding plate 33 that also serves as the lock-up piston 42, that is, toward the engine.

  The lock-up piston 42 is a second engaging member, and is connected to the front cover 10 via a plurality of damper springs 31 and a center holding plate 32 of the damper mechanism 30 on the fluid transmission mechanism 20 side of the front cover 10. In addition, it can move relative to the lockup plate 41 along the axial direction. As described above, the lock-up piston 42 serves as the rear holding plate 33 of the damper mechanism 30 and is defined by the front cover 10 and the pump shell 21b of the fluid transmission mechanism 20, and is filled with a working fluid (working oil). Is provided.

  That is, the lock-up piston 42 that is also used as the rear holding plate 33 is formed in an annular plate shape that is coaxial with the rotation axis X, and is formed between the lock-up plate 41 and the center holding plate 32 of the damper mechanism 30 in the axial direction. Arranged between. The lock-up piston 42 that is also used as the rear holding plate 33 faces the lock-up plate 41 in the axial direction. In the present embodiment, the lock-up piston 42 that is also used as the rear holding plate 33 moves in the axial direction with the damper mechanism 30 as a whole as described above, so that the lock-up plate 41 is moved along the axial direction. Can be approached or separated.

  The lock-up piston 42 (rear holding plate 33) is formed as a radially inner projecting portion 42a having a radially inner end bent toward the front cover 10 side. The radially inner projecting portion 42a is a portion that is formed in a cylindrical shape coaxial with the rotational axis X by projecting the radially inner end portion of the lockup piston 42 along the axial direction toward the front cover 10 side.

  Here, the front cover 10 is formed by forming a step portion 11 a as a facing portion on the main body portion 11. The step portion 11a is a portion formed in a cylindrical shape coaxial with the rotation axis X by projecting the radially inner portion of the main body portion 11 toward the engine side. In other words, the step portion 11a is a portion where the surface on the lockup piston 42 side of the radially inner portion of the main body portion 11 is recessed toward the engine side.

  The lock-up piston 42 (rear holding plate 33) has a radially inner protruding portion 42a inserted into a step portion 11a formed on the radially inner portion of the front cover 10, and is axially directed to the step portion 11a. It is slidably supported by. That is, the lockup piston 42 that is also used as the rear holding plate 33 can slide in the axial direction with respect to the front cover 10 in the entire damper mechanism 30, and the relative distance to the lockup plate 41 can be changed. .

  The lock-up piston 42 (rear holding plate 33) has a radially outer end portion (that is, an end portion on the outer peripheral surface side) 42b in the vicinity of the inner peripheral surface of the flange portion 12 of the front cover 10, here, It is formed to extend to a position spaced apart from the peripheral surface in the radial direction.

  Here, the lock-up plate 41 and the lock-up piston 42 (rear holding plate 33) have a relatively large outer diameter φD1, which is the length in the radial direction of the lock-up plate 41, so that the lock-up piston The outer diameter φD2, which is the length in the radial direction of 42, is set to be relatively small. That is, the lockup plate 41 has an outer diameter φD1 larger than the outer diameter φD2 of the lockup piston 42, in other words, the lockup piston 42 has an outer diameter φD2 smaller than the outer diameter φD1 of the lockup plate 41. The

  As described above, the friction engagement surface 43 includes the friction material 46 provided on the lockup plate 41 and the opposing wall surface 47 of the lockup piston 42 (rear holding plate 33). The opposing wall surface 47 is a wall surface facing the lockup plate 41 in the axial direction in the lockup piston 42. That is, the opposing wall surface 47 is a wall surface on the opposite side to the wall surface on which the outer rear holding portion 33a and the inner rear holding portion 33b are provided in the lock-up piston 42 also used as the rear holding plate 33. The friction material 46 is provided in the lockup plate 41 in the radial outer end of the wall surface facing the lockup piston 42 in the axial direction, that is, in the vicinity of the radial outer end 41a. The friction material 46 is provided in a flat portion on the radially inner side of the curved portion of the radially outer end portion 41 a in the lockup plate 41. The friction material 46 is formed in an annular plate shape coaxial with the rotation axis X. The friction engagement surface 43 can be frictionally engaged when the opposing wall surface 47 forming one surface of the friction engagement surface 43 and the friction material 46 forming the other surface of the friction engagement surface 43 are in contact with each other. That is, the lock-up plate 41 and the lock-up piston 42 can be frictionally engaged.

  As described above, the lockup piston 42 that is also used as the rear holding plate 33 can slide in the axial direction in the entire damper mechanism 30 with respect to the front cover 10, and the relative distance to the lockup plate 41 can be increased. Can be changed. Furthermore, the lockup piston 42 can change the relative distance of the opposing wall surface 47 with respect to the friction material 46 by approaching and separating from the lockup plate 41 by moving in the axial direction. Thus, the opposing wall surface 47 and the friction material 46 can be brought into contact with each other and frictionally engaged, and the opposing wall surface 47 and the friction material 46 can be brought into non-contact to release the frictional engagement.

  Here, the radially inner projecting portion 42a of the lockup piston 42 also used as the rear holding plate 33 and the stepped portion 11a of the front cover 10 are, as described above, the radially inner projecting portion 42a being located on the inner side of the stepped portion 11a. As a result, the outer peripheral surface of the radially inner projecting portion 42a and the inner peripheral surface of the stepped portion 11a face each other in the radial direction. The lockup clutch mechanism 40 is provided with a seal member 48 as a sealing means between the outer peripheral surface of the radially inner projecting portion 42a and the inner peripheral surface of the step portion 11a. The seal member 48 is, for example, a seal ring, is formed in an annular shape coaxial with the rotation axis X, and is provided in contact with the outer peripheral surface of the radially inner projecting portion 42a and the inner peripheral surface of the step portion 11a. The seal member 48 seals between the radially inner projecting portion 42a and the stepped portion 11a and prevents leakage of working fluid (working oil) from between the radially inner projecting portion 42a and the stepped portion 11a. it can.

  Therefore, the torque converter 1 includes a clutch in which the fluid transmission mechanism space A where the fluid transmission mechanism 20 is located and the friction engagement surface 43 of the lockup clutch mechanism 40 are located by the lockup plate 41 and the lockup piston 42. It is partitioned into a space B and a damper mechanism space C where the damper mechanism 30 is located. The fluid transmission mechanism space A is a space closer to the output shaft than the lockup plate 41 in the axial direction, that is, a space defined by the lockup plate 41 and the pump shell 21b. The clutch space B is a space between the lockup plate 41 and the lockup piston 42 in the axial direction, that is, a space defined by the lockup plate 41 and the lockup piston 42. The damper mechanism space C is a space closer to the engine than the lockup piston 42 in the axial direction, that is, a space defined by the lockup piston 42 and the front cover 10. The fluid transmission mechanism space portion A, the clutch space portion B, and the damper mechanism space portion C are arranged on the friction engagement surface 43 side in the radially outer end portion 41a of the lockup plate 41 and the lockup piston 42 (rear holding plate 33). Communication is possible via a communication portion between the radially outer end 42b, the inner peripheral surface of the pump shell 21b, and the inner peripheral surface of the flange portion 12.

  The working fluid flow path 44 is formed as a space through which the working fluid (working oil) can pass between the lockup plate 41 and the lockup piston 42 (rear holding plate 33) in the axial direction. Here, the clutch space B functions as the working fluid flow path 44. The friction engagement surface 43 is provided at a radially outer portion in the clutch space B that functions as the working fluid flow path 44. The working fluid flow path 44 has a radial outer end 41a of the lockup plate 41 and a radial outer end 42b of the lockup piston 42 as described above according to the axial position of the lockup piston 42. The fluid transmission mechanism space part A and the damper mechanism space part C are formed so as to be able to communicate with each other via a communication portion between the inner peripheral surface of the pump shell 21b and the inner peripheral surface of the flange portion 12.

  The piston hydraulic chamber 45 is for generating a hydraulic pressing force for moving the lock-up piston 42 (rear holding plate 33) in the axial direction. Here, the damper mechanism space C functions as the piston hydraulic chamber 45. A damper mechanism space C that functions as the piston hydraulic chamber 45 is formed between the lockup piston 42 and the front cover 10. The damper mechanism space C functioning as the piston hydraulic chamber 45 applies a pressing force toward the lockup plate 41 to the lockup piston 42 by an internal working fluid (working oil).

  The lockup clutch mechanism 40 configured as described above is also used as the rear holding plate 33 by the hydraulic pressure (hydraulic pressure) of the working fluid (hydraulic oil) supplied to the damper mechanism space C that functions as the piston hydraulic chamber 45. A pressing force is applied to the lock-up piston 42, and the lock-up piston 42 is moved integrally toward the lock-up plate 41 along the axial direction in the damper mechanism 30 as a whole. 47 and the friction material 46 come into contact with each other and frictionally engage with each other, whereby the lockup clutch mechanism 40 is turned on. When the lock-up clutch mechanism 40 is turned on, the lock-up piston 42 that also serves as the rear holding plate 33 and the lock-up plate 41 rotate together, so that the lock-up clutch mechanism 40 is transmitted to the front cover 10. The driving force from the engine is directly passed through the center holding plate 32 of the damper mechanism 30, the plurality of damper springs 31, the lockup piston 42 also used as the rear holding plate 33, the friction material 46 and the lockup plate 41 in order. It is transmitted to the hub 52 and transmitted to the output shaft 50.

  Here, the torque converter 1 is formed between the lock-up plate 41 and the pump shell 21b and functions as a piston hydraulic chamber 45 or between the lock-up plate 41 and the lock-up piston 42. One of the clutch spaces B that is formed and functions as the working fluid flow path 44 is supplied with working oil as working fluid from a hydraulic control means (not shown).

  The hydraulic control means is also used as a pressure difference between the hydraulic pressure of the damper mechanism space C that functions as the piston hydraulic chamber 45 and the hydraulic pressure of the clutch space B that functions as the working fluid flow path 44, that is, as the rear holding plate 33. The pressing force acting in the axial direction on the pressure-receiving surface 42c on the engine side of the lockup piston 42 (the surface on the side where the outer rear holding portion 33a and the inner rear holding portion 33b are provided) can be controlled.

  The hydraulic control means supplies hydraulic fluid to the fluid transmission mechanism space A when the lock-up clutch mechanism 40 is turned on, and the clutch space B from the fluid transmission mechanism space A, which is the inner side of the fluid transmission mechanism 20. The hydraulic oil is allowed to flow through and is discharged to the outside of the torque converter 1 from the clutch space B that functions as the working fluid flow path 44, thereby reducing the hydraulic pressure of the clutch space B that functions as the working fluid flow path 44. The hydraulic pressure of the damper mechanism space C that functions as the chamber 45 is made larger than the hydraulic pressure of the clutch space B. As a result, the lockup piston 42 that is also used as the rear holding plate 33 is moved to the side approaching the lockup plate 41 (output shaft side), and the opposing wall surface 47 of the lockup piston 42 is moved to the friction material 46 of the lockup plate 41. The lockup piston 42 and the lockup plate 41 are frictionally engaged through the friction engagement surface 43, and the lockup piston 42 and the lockup plate 41 are integrally rotated.

  The hydraulic control means supplies hydraulic oil to the clutch space B that functions as the working fluid flow path 44 when the lock-up clutch mechanism 40 is turned off, and operates from the clutch space B side to the fluid transmission mechanism space A. A damper mechanism space in which the hydraulic pressure of the clutch space B that functions as the working fluid flow path 44 functions as the piston hydraulic chamber 45 by flowing oil and discharging the hydraulic oil from the fluid transmission mechanism space A to the outside of the torque converter 1. It is greater than or equal to the hydraulic pressure of part C. As a result, the lockup piston 42 that is also used as the rear holding plate 33 is moved to the side away from the lockup plate 41 (engine side), and the opposing wall surface 47 that is frictionally engaged with the friction material 46 is moved to the friction material 46. The frictional engagement is released, and the integral rotation of the lockup piston 42 and the lockup plate 41 is released.

  Next, the operation of the torque converter 1 according to this embodiment will be described. When the engine generates driving force and the engine output shaft 110 rotates, the driving force from the engine is transmitted to the front cover 10 via the drive plate 100. The driving force from the engine transmitted to the front cover 10 is transmitted to the pump shell 21b of the pump impeller 21 connected to the front cover 10, and the pump impeller 21 rotates. When the pump impeller 21 rotates, the hydraulic oil in the fluid transmission mechanism space A circulates among the pump blade 21a, the turbine blade 22a, and the stator blade 23a of the stator 23, and acts as a fluid coupling. Accordingly, the driving force from the engine transmitted to the front cover 10 is transmitted to the turbine liner 22 via the pump impeller 21 and the hydraulic oil, and the turbine liner 22 rotates in the same direction as the front cover 10. At this time, the stator 23 changes the flow of the hydraulic oil that circulates between the pump blade 21a and the turbine blade 22a via the stator blade 23a, whereby the torque converter 1 obtains a predetermined torque characteristic. Can do.

  Further, as described above, the driving force transmitted from the engine to the front cover 10 is transmitted to the center holding plate 32 through the connecting portion 60, and the lock-up piston 42 from the center holding plate 32 through the damper spring 31. Are transmitted to a rear holding plate 33 and a front holding plate 34 which are also used as That is, a part of the driving force transmitted from the engine to the front cover 10 is transmitted to the rear holding plate 33 that is also used as the lockup piston 42 of the lockup clutch mechanism 40 via the damper mechanism 30, and this lockup is performed. The rear holding plate 33 that is also used as the piston 42 rotates in the same direction as the front cover 10.

  When the lockup clutch mechanism 40 is OFF, the frictional engagement between the friction material 46 provided on the lockup plate 41 and the opposing wall surface 47 of the lockup piston 42 also used as the rear holding plate 33 is released. . Therefore, the driving force from the engine transmitted to the turbine liner 22 via the hydraulic oil as described above is transmitted to the output shaft 50 via the hub 52. That is, when the lockup clutch mechanism 40 is OFF, the driving force from the engine transmitted to the front cover 10 is transmitted to the output shaft 50 via the fluid transmission mechanism 20.

  On the other hand, when the lock-up clutch mechanism 40 is ON, the friction material 46 provided on the lock-up plate 41 and the opposing wall surface 47 of the lock-up piston 42 that also serves as the rear holding plate 33 are frictionally engaged, thereby The up plate 41 and the lock-up piston 42 rotate integrally. Therefore, the driving force from the engine transmitted to the lockup piston 42 of the lockup clutch mechanism 40 via the damper mechanism 30 is transmitted to the lockup plate 41 via the friction engagement surface 43. The driving force transmitted to the lockup plate 41 is transmitted to the output shaft 50 via the hub 52. That is, when the lockup clutch mechanism 40 is ON, the driving force from the engine transmitted to the front cover 10 is transmitted to the output shaft 50 via the damper mechanism 30 and the lockup clutch mechanism 40.

  When the lock-up clutch mechanism 40 is switched from OFF to ON or from ON to OFF, when the driving force from the engine changes, or when the resistance force transmitted from the road surface to the output shaft 50 changes. In this case, the force transmitted between the front cover 10 and the output shaft 50 (the driving force from the engine and the driven force transmitted from the road surface) fluctuates, and the front located on the driving side with the damper mechanism 30 interposed therebetween. The cover 10 and the output shaft 50 positioned on the driven side tend to rotate relatively. At this time, the outer damper springs 31a and the inner damper springs 31b of the damper mechanism 30 are moved to the front cover 10 side in accordance with the relative rotation between the driving front cover 10 and the driven output shaft 50. According to the fluctuation of the force transmitted between the output shaft 50 side, the center holding plate 32, the rear holding plate 33, and the front holding plate 34 are elastically deformed, respectively. Thereby, for example, each damper spring 31 absorbs vibration caused by the explosion of the engine, so that vibration such as a booming noise during transmission of the driving force via the damper mechanism 30 can be reduced.

  By the way, the lockup clutch mechanism 40 of the torque converter 1 is a lockup piston that is also used as the rear holding plate 33 by the hydraulic pressure of the damper mechanism space C that functions as the piston hydraulic chamber 45 when the lockup clutch mechanism 40 is ON-controlled. A pressing force is applied to the pressure receiving surface 42c of 42 in the axial direction, and the opposing wall surface 47 of the lockup piston 42 and the friction material 46 are frictionally engaged. Here, in the lockup clutch mechanism 40, as described above, the seal member 48 for forming the damper mechanism space C that functions as the piston hydraulic chamber 45 is provided in the radial direction of the lockup piston 42 (rear holding plate 33). It is provided between the outer peripheral surface of the inner protrusion 42 a and the inner peripheral surface of the step portion 11 a of the front cover 10.

  For this reason, in this lockup clutch mechanism 40, for example, the seal member 48 has a radially inner projecting portion 42a as compared with a case where a seal member for forming a piston hydraulic chamber is provided in a radially intermediate portion of the lockup piston. By providing them, the area of the pressure receiving surface 42c facing the piston hydraulic chamber 45 in the lockup piston 42 can be made relatively large. Thereby, in this lockup clutch mechanism 40, since the area of the pressure receiving surface 42c of the lockup piston 42 can be relatively increased, for example, a seal member for forming a piston hydraulic chamber is used as the diameter of the lockup piston. Compared with the case where it is provided at the intermediate portion in the direction, even if the hydraulic pressure of the hydraulic fluid in the damper mechanism space C that functions as the piston hydraulic chamber 45 is equivalent, the pressing force acting on the lockup piston 42 is relatively Can be bigger. As a result, since the pressing force acting on the lockup piston 42 can be relatively increased, the torque capacity that can be transmitted on the friction engagement surface 43 of the lockup clutch mechanism 40 can be increased. The performance of the lockup clutch mechanism 40 can be improved. In other words, since the area of the pressure receiving surface 42c of the lockup piston 42 can be relatively large without increasing the torque converter 1 in the radial direction, an appropriate pressing force can be obtained with a more compact configuration. Therefore, the apparatus can be made compact and the performance of the lock-up clutch mechanism 40 can be improved. Further, the lockup piston 42 can be relatively increased by increasing the area of the pressure receiving surface 42c of the lockup piston 42 without increasing the hydraulic pressure of the hydraulic fluid in the damper mechanism space C functioning as the piston hydraulic chamber 45 more than necessary. Since the pressing force acting on can be relatively increased, deformation of the torque converter 1 can be suppressed.

  Here, in the lockup clutch mechanism 40 of the torque converter 1, when the ON control of the lockup clutch mechanism 40 is started, as described above, the working fluid is introduced from the fluid transmission mechanism space A side that is the inner side of the fluid transmission mechanism 20. The hydraulic oil flows into the clutch space B that functions as the flow path 44. In other words, the lock-up clutch mechanism 40 has an outer diameter of the lock-up plate 41 located on the upstream side of the flow of hydraulic oil when the lock-up plate 41 and the lock-up piston 42 (rear holding plate 33) are frictionally engaged. φD1 is set to be relatively large, and the outer diameter φD2 of the lockup piston 42 (rear holding plate 33) located on the downstream side is set to be relatively small. Thus, when the ON control of the lockup clutch mechanism 40 is started, the working fluid flow path 44 from the fluid transmission mechanism space A side by the radially outer end 41a of the lockup plate 41 located on the upstream side of the flow of hydraulic oil. It is possible to suppress the flow of the hydraulic oil toward the end from hitting the radially outer end 42b of the lockup piston 42 (rear holding plate 33) located on the downstream side. That is, when starting the ON control of the lockup clutch mechanism 40, the lockup plate 41 positioned on the upstream side of the flow of hydraulic oil avoids the hydraulic oil with respect to the lockup piston 42 (rear holding plate 33) positioned on the downstream side. Function as. As a result, it is possible to suppress the flow of hydraulic oil from hitting the lock-up piston 42 (rear holding plate 33), and therefore, it is opposite to the pressing force acting from the damper mechanism space C functioning as the piston hydraulic chamber 45. It is possible to prevent the force in the direction, in other words, the force that inhibits the movement of the lockup piston 42 (rear holding plate 33) toward the lockup plate 41 from acting on the lockup piston 42 (rear holding plate 33). it can. Therefore, when the ON control of the lockup clutch mechanism 40 is started, the responsiveness of the operation in which the lockup piston 42 approaches the lockup plate 41 side can be improved, so that the responsiveness of the lockup operation can be improved. it can. Therefore, the performance of the lockup clutch mechanism 40 can be improved. And since the responsiveness of lockup operation | movement can be improved, the excessive engine blow-up can be prevented and a fuel consumption can be improved.

  According to the torque converter 1 according to the embodiment of the present invention described above, the fluid transmission mechanism 20 capable of transmitting the driving force transmitted from the engine to the front cover 10 to the output shaft 50 via the hydraulic oil, and the front cover. 10 is provided on the fluid transmission mechanism 20 side and is rotatable together with the output shaft 50. The front cover 10 is connected to the front cover 10 on the fluid transmission mechanism 20 side of the front cover 10 and extends along the axial direction of the output shaft 50. A lock-up piston 42 that can move relative to the lock-up plate 41, and a lock-up plate 41 that is provided between the lock-up piston 42 and the front cover 10 with respect to the axial direction. A piston hydraulic chamber 45 for applying a pressing force to the side, and hydraulic oil in the piston hydraulic chamber 45 Therefore, by applying a pressing force to the lock-up piston 42 and frictionally engaging the lock-up plate 41 and the lock-up piston 42, the driving force transmitted to the front cover 10 is applied to the lock-up piston 42 and the lock-up plate 41. A lock-up clutch mechanism 40 that can transmit to the output shaft 50 via the radial inner projecting portion 42a of the lock-up piston 42 with respect to the radial direction orthogonal to the axial direction, and the front cover 10. A seal member 48 is provided between the radially inner projecting portion 42a of the lock-up piston 42 and the step portion 11a opposed in the radial direction to prevent hydraulic fluid from leaking.

  Therefore, since the seal member 48 is provided between the radially inner projecting portion 42a of the lockup piston 42 and the step portion 11a of the front cover 10, the area of the pressure receiving surface 42c of the lockup piston 42 is relatively large. Since the pressing force acting on the lockup piston 42 from the piston hydraulic chamber 45 can be relatively increased, the torque capacity that can be transmitted on the friction engagement surface 43 of the lockup clutch mechanism 40 is increased. And the performance of the lock-up clutch mechanism 40 can be improved.

  Furthermore, according to the torque converter 1 according to the embodiment of the present invention described above, the radially inner projecting portion 42a of the lockup piston 42 is formed to project toward the front cover 10 along the axial direction. The stepped portion 11a is formed so that the radially inner protruding portion 42a of the lockup piston 42 can be inserted in the radially inner side of the front cover 10, and the seal member 48 is formed on the radially inner protruding portion 42a of the lockup piston 42. It is provided in contact with the outer peripheral surface and the inner peripheral surface of the step portion 11 a of the front cover 10. Therefore, the seal member 48 is configured such that the outer peripheral surface of the radial inner protrusion 42a and the inner peripheral surface of the step 11a in a state where the radial inner protrusion 42a of the lockup piston 42 is inserted into the step 11a of the front cover 10. Since the piston hydraulic chamber 45 is formed between the lockup piston 42 and the front cover 10, it is possible to reliably prevent the hydraulic oil from leaking.

  Furthermore, according to the torque converter 1 according to the embodiment of the present invention described above, the lock-up plate 41 and the lock-up piston 42 are operated when the lock-up plate 41 and the lock-up piston 42 are frictionally engaged. The lockup plate 41 is positioned upstream of the fluid flow, the lockup piston 42 is positioned downstream, and the outer diameter φD1 that is the radial length of the lockup plate 41 is set relatively large. The outer diameter φD2, which is the length of the up piston 42 in the radial direction, is set to be relatively small. Therefore, the outer diameter φD1 of the lockup plate 41 located on the upstream side of the hydraulic oil flow is set relatively large, and the outer diameter φD2 of the lockup piston 42 (rear holding plate 33) located on the downstream side is relatively large. Therefore, when the ON control of the lockup clutch mechanism 40 is started, the flow of hydraulic oil collides with the lockup piston 42 (rear holding plate 33) by the radially outer end 41a of the lockup plate 41. Therefore, the responsiveness of the lockup operation in which the lockup piston 42 approaches the lockup plate 41 side can be improved, and the performance of the lockup clutch mechanism 40 can be improved.

  Furthermore, according to the torque converter 1 which concerns on embodiment of this invention demonstrated above, as for the lockup plate 41, the radial direction outer side edge part 41a is curving to the lockup piston 42 side. Therefore, since the flow of the working oil from the fluid transmission mechanism space A side toward the working fluid flow path 44 can be stabilized, the responsiveness of the lock-up operation can be further improved.

  Furthermore, according to the torque converter 1 according to the embodiment of the present invention described above, the lock-up clutch mechanism 40 is formed between the lock-up plate 41 and the lock-up piston 42 in the axial direction and is a fluid transmission mechanism. 20 and a hydraulic fluid passage 44 formed so as to be able to communicate with the piston hydraulic chamber 45 on the outside in the radial direction, and a fluid transmission mechanism when the lock-up plate 41 and the lock-up piston 42 are frictionally engaged. The working fluid flows from the inner side of 20 to the working fluid flow path 44 side. Therefore, when the lock-up clutch mechanism 40 is ON-controlled, the hydraulic oil is supplied to the fluid transmission mechanism space A, the hydraulic oil is allowed to flow from the fluid transmission mechanism space A side to the clutch space B, and the torque from the hydraulic fluid channel 44 is increased. By discharging to the outside of the converter 1, the hydraulic pressure of the working fluid channel 44 can be reduced, and the hydraulic pressure of the piston hydraulic chamber 45 can be made larger than the hydraulic pressure of the working fluid channel 44. As a result, a pressing force is applied to the lockup piston 42 to move the lockup piston 42 closer to the lockup plate 41 (output shaft side), and the lockup piston 42 and the lockup plate 41 can be frictionally engaged.

(Embodiment 2)
FIG. 2 is a cross-sectional view of main parts of a torque converter according to Embodiment 2 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 the first engagement member is also movable in the axial direction. Is different. 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 according to the second embodiment includes a lock-up clutch mechanism 240 as lock-up means. The lock-up clutch mechanism 240 of this embodiment includes a lock-up plate 241 as a first engagement member, a lock-up piston 42 as a second engagement member, a friction engagement surface 243, and a working fluid channel 44. And a piston hydraulic chamber 45 as a hydraulic chamber.

  And the lockup plate 241 of this embodiment becomes a structure which can move relatively with respect to the lockup piston 42 along an axial direction.

  The lockup plate 241 is formed in an annular plate shape coaxial with the rotation axis X, and is disposed between the turbine shell 22b and the lockup piston 42 in the axial direction. The lock-up plate 241 is formed as a radially inner projecting portion 241a having a radially inner end bent to the front cover 10 side. The radially inner projecting portion 241a is a portion in which the radially inner end portion of the lockup plate 241 projects toward the front cover 10 along the axial direction and is formed in a cylindrical shape coaxial with the rotation axis X. The radially inner projecting portion 241 a has an inner peripheral surface that is in contact with the outer peripheral surface of the radially inner end (boss portion) of the hub 52 in a radial direction and is supported so as to be slidable in the axial direction.

  In the lockup clutch mechanism 240, a seal member 248 is provided between the inner peripheral surface of the radially inner protruding portion 241 a of the lockup plate 241 and the outer peripheral surface of the hub 52 in the radial inner end. The seal member 248 is, for example, a seal ring, and is formed in an annular shape coaxial with the rotation axis X. The seal member 248 is an outer periphery of the inner peripheral surface of the radially inner protruding portion 241a of the lockup plate 241 and the radially inner end of the hub 52. Provided in contact with the surface. The seal member 248 can seal the gap between the radially inner protruding portion 241a and the radially inner end of the hub 52 and prevent leakage of the working fluid (hydraulic oil).

  On the other hand, the lock-up plate 241 is formed as a radially outer protruding portion 241b having a radially outer end bent to the turbine shell 22b side. The radially outer projecting portion 241b is a portion that is formed in a cylindrical shape coaxial with the rotational axis X by projecting the radially outer end of the lockup plate 241 toward the turbine shell 22b along the axial direction. And this radial direction outside protrusion part 241b is connected with the turbine shell 22b via the connection member 249 so that a movement to an axial direction is possible.

  The lock-up plate 241 is provided with a connection notch 241c on the radially outer protrusion 241b. The connection cutout portion 241c is formed by cutting out the end portion on the output shaft side of the radially outer projecting portion 241b along the axial direction toward the engine side. The connection notch 241c is formed so as to penetrate from the outer peripheral surface to the inner peripheral surface of the radially outer protrusion 241b with respect to the radial direction. A plurality of the connection notches 241c are formed at equal intervals in the circumferential direction with respect to the radially outer protrusion 241b.

  The connecting member 249 is provided in the vicinity of the radially outer end of the turbine shell 22b. The connecting member 249 is formed in an annular plate shape coaxial with the rotation axis X, and the inner peripheral surface side is fixed to the outer peripheral surface of the turbine shell 22b by, for example, welding. The connecting member 249 is provided with a connecting protrusion 249a at the radially outer end.

  The connection protrusion 249a is connected to the connection notch 241c of the lockup plate 241 in the radial direction in a state where the lockup plate 241 is disposed between the turbine shell 22b and the lockup piston 42. It is formed to project radially outward from the radially outer end of 249a. The protruding amount of the connecting protrusion 249a is set so that the connecting protrusion 249a is inserted into the connecting notch 241c in a state where the lock-up plate 241 is disposed between the turbine shell 22b and the lock-up piston 42. A plurality of connection protrusions 249 a are formed at equal intervals in the circumferential direction with respect to the connection member 249.

  When the lock-up plate 241 is disposed between the turbine shell 22b and the lock-up piston 42, the connection protrusion 249a is inserted into and engaged with the connection notch 241c, so that the lock-up plate 241 rotates relative to the connection member 249. And the relative movement along the axial direction is allowed. In other words, the lock-up plate 241 is coupled to the coupling member 249 so as to be rotatable integrally with the coupling member 249 and to be movable in the axial direction by the coupling notch 241c and the coupling projection 249a, whereby the turbine shell 22b. The turbine shell 22b is connected to the turbine shell 22b so as to be capable of rotating integrally with the turbine shell 22b and to be movable in the axial direction. Accordingly, the lockup plate 241 is connected to the output shaft 50 via the turbine shell 22 b and the hub 52, and can rotate together with the turbine shell 22 b, the hub 52 and the output shaft 50. As described above, the lockup plate 241 can slide in the axial direction with respect to the turbine shell 22b, and the relative distance to the lockup piston 42 can be changed.

  The lockup clutch mechanism 240 of this embodiment further has a plate hydraulic chamber 245. The plate hydraulic chamber 245 is for generating a hydraulic pressing force for moving the lockup plate 241 in the axial direction. Here, the fluid transmission mechanism space A functions as the plate hydraulic chamber 245. The fluid transmission mechanism space A that functions as the plate hydraulic chamber 245 is formed between the lockup plate 241 and the pump shell 21b. The fluid transmission mechanism space A that functions as the plate hydraulic chamber 245 applies a pressing force toward the lockup piston 42 to the lockup plate 241 by the internal working fluid (hydraulic oil).

  In the present embodiment, the friction engagement surface 243 of the lockup clutch mechanism 240 is opposed to the friction material 46 provided on the lockup piston 42 and the wall surface of the lockup plate 241 that faces the friction material 46 in the axial direction. And a wall surface 247. The friction material 46 is provided on the wall surface of the lockup piston 42 that faces the lockup plate 241 in the axial direction via a support member 46a. The friction material 46 and the support member 46a are set to have an outer diameter substantially equal to the outer diameter φD2 of the lockup piston 42 (rear holding plate 33).

  The lock-up clutch mechanism 240 configured as described above supplies hydraulic oil to the fluid transmission mechanism space A when the lock-up clutch mechanism 240 is turned on, and this fluid transmission mechanism that is inside the fluid transmission mechanism 20 is provided. The hydraulic oil is allowed to flow from the space A side to the clutch space B and discharged from the clutch space B to the outside of the torque converter 201, thereby reducing the hydraulic pressure of the clutch space B that functions as the working fluid flow path 44. The hydraulic pressure of the fluid transmission mechanism space A that functions as the hydraulic chamber 245 and the damper mechanism space C that functions as the piston hydraulic chamber 45 is made larger than the hydraulic pressure of the clutch space B. As a result, the lock-up piston 42 also used as the rear holding plate 33 is moved to the side approaching the lock-up plate 241 (output shaft side), and the lock-up plate 241 is approached to the lock-up piston 42 (engine side). ), The opposing wall surface 247 of the lockup plate 241 and the friction material 46 of the lockup piston 42 are brought into contact with each other, and the lockup piston 42 and the lockup plate 241 are frictionally engaged via the friction engagement surface 243. Thus, the lockup piston 42 and the lockup plate 241 are integrally rotated. Therefore, the lock-up clutch mechanism 240 of the present embodiment can move the lock-up piston 42 and the lock-up plate 241 in the axial direction so as to approach each other when the lock-up clutch mechanism 240 starts ON control. In addition, the responsiveness of the lockup operation can be improved.

  And according to the torque converter 201 which concerns on embodiment of this invention demonstrated above, the sealing member 48 is provided between the radial direction inner side protrusion part 42a of the lockup piston 42, and the level | step-difference part 11a of the front cover 10. FIG. As a result, the area of the pressure receiving surface 42c of the lockup piston 42 can be made relatively large, and the pressing force acting on the lockup piston 42 from the piston hydraulic chamber 45 can be made relatively large. The torque capacity that can be transmitted on the friction engagement surface 243 of the clutch mechanism 240 can be increased, and the performance of the lockup clutch mechanism 40 can be improved.

  Furthermore, according to the torque converter 201 according to the embodiment of the present invention described above, the outer diameter φD1 of the lockup plate 241 located on the upstream side of the flow of hydraulic oil is set relatively large, and the position is located on the downstream side. Since the outer diameter φD2 of the lockup piston 42 (rear holding plate 33) to be set is set relatively small, the lockup plate 241 locks up the flow of hydraulic oil when the lockup clutch mechanism 240 starts ON control. Since collision with the piston 42 (rear holding plate 33) can be suppressed, the responsiveness of the lock-up operation in which the lock-up piston 42 approaches the lock-up plate 241 can be improved.

  Furthermore, according to the torque converter 201 according to the embodiment of the present invention described above, the lockup plate 241 is provided to be movable relative to the lockup piston 42 along the axial direction. Therefore, the lockup clutch mechanism 240 can move the lockup piston 42 and the lockup plate 241 in the axial direction so as to approach each other when the lockup clutch mechanism 240 starts ON control. Responsiveness can be improved. When the lock-up clutch mechanism 240 starts ON control, the flow of hydraulic oil hits the lock-up plate 241 in a direction that promotes the lock-up operation in which the lock-up plate 241 approaches the lock-up piston 42 side. The responsiveness of the operation can be further improved.

  In the present embodiment, the center holding plate 32 of the damper mechanism 30 has a radially inner projecting portion 232e as a radially inner end that can rotate integrally with the connecting groove 211b in the main body 11 of the front cover 10 and in the axial direction. They are linked so that they can move relative to each other. The center holding plate 32 can be integrally rotated with the front cover 10 at two locations, namely, a connecting portion 60 including a connecting protrusion portion 32a and a connecting groove portion 12a, and a connecting portion 264 including a radially inner protruding portion 232e and a connecting groove portion 211b. Further, by being connected so as to be relatively movable in the axial direction, for example, the axial width can be made thinner, that is, thinner than the center holding plate 32 (see FIG. 1) of the first embodiment.

(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 is different from the fluid transmission device according to the first embodiment in that it includes guide means. 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. 3, the torque converter 301 as the fluid transmission device according to the third embodiment includes a hydraulic oil guide portion 370 as guide means. The hydraulic oil guide 370 receives the flow of hydraulic oil from the hydraulic fluid flow path 44 side in the piston hydraulic chamber 45 of the lockup clutch mechanism 340 and receives the hydraulic oil flow 45 from the piston hydraulic chamber 45 of the lockup piston 342 as the second engagement member. It is guided toward the pressure receiving surface 342c which is the side surface.

  In the torque converter 1 (see FIG. 1) of the first embodiment described above, the lock-up piston 42 (see FIG. 1) as the second engagement member is the rear holding plate of the damper mechanism 30 (see FIG. 1). Although described as being also used as 33 (see FIG. 1), the lock-up piston 342 of this embodiment is configured separately from the rear holding plate 333 of the damper mechanism 330 serving as damper means.

  First, the damper mechanism 330 of the present embodiment includes a plurality of damper springs 31, a center holding plate 332 as a center holding member, and a rear holding plate 333 as a side holding member.

  The damper mechanism 330 of the present embodiment does not include the front holding plate 34 (see FIG. 1) as the side holding member on the front cover 10 side described in the first embodiment, and instead, the driving force of the engine Is also used as a member corresponding to the front holding plate 34. That is, the damper mechanism 330 is arranged in the order of the front cover 10, the center holding plate 332, the plurality of damper springs 31, and the rear holding plate 333 from the engine side to the output shaft side with respect to the axial direction. The damper mechanism 330 transmits the driving force transmitted from the engine to the front cover 10 from the front cover 10 and the rear holding plate 333 to the center holding plate 332 via the plurality of damper springs 31.

  The center holding plate 332 is provided between the front cover 10 and the lock-up piston 342 as the second engaging member in the axial direction, and holds the plurality of damper springs 31 so that the driving force can be transmitted. The center holding plate 332 includes an outer center holding portion 32b and an inner center holding portion 32c, holds the outer damper spring 31a via the outer center holding portion 32b so as to be able to transmit a driving force, and the inner center holding portion 32c. The inner damper spring 31b is held so as to be able to transmit the driving force.

  The center holding plate 332 is provided so that the lock-up piston 342 can rotate integrally and can be relatively moved in the axial direction. Specifically, the center holding plate 332 is provided with a spline 332e at the radially inner end 332d.

  The spline 332e is formed as a groove along the axial direction on the inner peripheral surface of the radially inner end 332d of the center holding plate 332. In the spline 332e, a plurality of grooves along the axial direction are formed at predetermined intervals along the circumferential direction on the inner peripheral surface of the center holding plate 332.

  On the other hand, the lock-up piston 342 is provided with a spline 342e on the cylindrical protrusion 342d. The cylindrical protrusion 342d is formed in the lockup piston 342 so as to protrude toward the engine at a position radially inward from the spline 332e of the center holding plate 332. The cylindrical protrusion 342d is formed in a cylindrical shape coaxial with the rotation axis X, and the outer peripheral surface thereof faces the inner peripheral surface of the radially inner end 332d of the center holding plate 332 with respect to the radial direction.

  The spline 342e is formed as a groove along the axial direction on the outer peripheral surface of the cylindrical protrusion 342d of the lockup piston 342. In the spline 342e, a plurality of grooves along the axial direction are formed at predetermined intervals along the circumferential direction on the outer peripheral surface of the cylindrical protrusion 342d.

  Therefore, the center holding plate 332 and the lock-up piston 342 are coupled to each other so that the spline 332e and the spline 342e are spline-fitted so as to be integrally rotatable and relatively movable in the axial direction. That is, the lock-up piston 342 is supported by the center holding plate 332 so as to be integrally rotatable and relatively movable in the axial direction. Therefore, the lock-up piston 342 can change the relative distance with respect to the lock-up plate 41 by moving relative to the lock-up plate 41 in the axial direction.

  Further, the front cover 10 of the present embodiment is configured to hold a part of the plurality of outer damper springs 31a and the plurality of inner damper springs 31b, whose center portions in the axial direction are held by the center holding plate 32, so that the driving force can be transmitted. is there. The front cover 10 has a front holding portion 311 c on the surface of the main body portion 11 on the output shaft side, that is, the surface facing the center holding plate 332.

  The front holding portion 311c is provided in a region where the set block 13 is not provided on the back side of the wall surface of the main body portion 11 facing the center holding plate 332. The front holding portion 311c is a main body in a region between a plurality of set blocks 13 formed in the circumferential direction on the back surface of the wall surface facing the center holding plate 332 of the main body portion 11, that is, on the engine side surface of the main body portion 11. A wall surface facing the center holding plate 332 of the portion 11 is formed as a space portion by being recessed toward the engine side. Each front holding portion 311 c is formed in an arc shape along the circumferential direction of the front cover 10. That is, the front cover 10 is formed so that each front holding portion 311c protrudes to the engine side in the inter-block space between the set blocks 13 in the circumferential direction.

  Each front holding portion 311c is formed at a position facing the outer center holding portion 32b and the inner center holding portion 32c of the center holding plate 332 in the axial direction. Therefore, both ends in the circumferential direction of each front holding portion 311c are in a state where the outer damper spring 31a and the inner damper spring 31b are held by each outer center holding portion 32b and each inner center holding portion 32c of the center holding plate 332, respectively. The outer damper spring 31a and the inner damper spring 31b can be opposed to and contacted with each other in the circumferential direction. As a result, the front cover 10 transmits the driving force between the outer damper spring 31a and the inner damper spring 31b at the circumferential end contact portion between the front holding portion 311c, the outer damper spring 31a, and the inner damper spring 31b. It becomes possible.

  The rear holding plate 333 is provided between the lock-up piston 342 and the center holding plate 332 in the axial direction, and holds the plurality of damper springs 31 so that the driving force can be transmitted. The rear holding plate 333 has a plurality of outer rear holding portions 33a, a plurality of inner rear holding portions 33b, and a connecting projection portion 333c.

  Each outer rear holding portion 33a is formed at a position facing the outer center holding portion 32b of the center holding plate 332 in the axial direction, and each inner rear holding portion 33b is axially connected to the inner center holding portion 32c of the center holding plate 332 Is formed at a position opposite to. Therefore, both ends in the circumferential direction of each outer rear holding portion 33a and each inner rear holding portion 33b are respectively connected to each outer center holding portion 32b and each inner center holding portion 32c of the center holding plate 332, and each outer damper spring 31a and inner side. In a state where the damper spring 31b is held, both ends of the outer damper spring 31a and the inner damper spring 31b are opposed to each other in the circumferential direction, and can be contacted. As a result, the rear holding plate 333 has the outer damper spring 31a, the inner damper spring 31b, and the outer damper spring 31a at the circumferential end contact portion between the outer rear holding portion 33a, the inner rear holding portion 33b, the outer damper spring 31a, and the inner damper spring 31b. The driving force can be transmitted between the two.

  That is, each outer damper spring 31 a and each inner damper spring 31 b are a front holding portion 311 c of the front cover 10, an outer rear holding portion 33 a of the rear holding plate 333, an inner rear holding portion 33 b, and an outer center holding portion of the center holding plate 332. 32b, which is held by the inner center holding portion 32c, allows the driving force to be transmitted between the front cover 10, the rear holding plate 333 and the center holding plate 332.

  The rear holding plate 333 of the present embodiment is coupled to the front cover 10 so that the coupling protrusion 333c at the radially outer end is rotatable together.

  The connecting projection 333 c is formed on the radially outer end of the rear holding plate 333 (that is, the end on the outer peripheral surface side). The connection protrusion 333 c constitutes the connection portion 360 together with the connection groove portion 12 a of the front cover 10 described above. A plurality of connection protrusions 333 c are formed at equal intervals in the circumferential direction with respect to the rear holding plate 333.

  The connecting projection 333 c is arranged in the radial direction of the rear holding plate 333 so as to face the connecting groove 12 a of the flange 12 in the radial direction in a state where the rear holding plate 333 is inserted inside the flange 12 of the front cover 10. It is formed to protrude radially outward from the outer end. The protruding amount of the connecting projection 333c is set so that the connecting protrusion 333c is inserted into the connecting groove 12a in a state where the center holding plate 332 is inserted inside the flange portion 12.

  Therefore, in a state where the rear holding plate 333 is inserted inside the flange portion 12 of the front cover 10, the connecting projections 333c forming the connecting portions 360 are respectively inserted and engaged with the connecting groove portions 12a, whereby the rear holding plate 333 is engaged. Is restricted from rotating relative to the front cover 10. That is, the rear holding plate 333 is connected to the front cover 10 so as to be rotatable together with the front cover 10 by the connecting portion 360 formed by the connecting protrusion 333c and the connecting groove portion 12a, and is connected so that the driving force can be transmitted from the front cover 10. .

  In the rear holding plate 333 of this embodiment, the connecting protrusion 333c is inserted into and engaged with the connecting groove 12a, and the connecting protrusion 333c is connected to the axial wall surface of the connecting groove 12a and the diameter of the pump shell 21b. By being clamped between the outer end portions in the direction, the relative movement in the axial direction with respect to the front cover 10 is restricted. In other words, the rear holding plate 333 is connected to the front cover 10 so as to be integrally rotatable and not relatively movable in the axial direction.

  The front cover 10 and the rear holding plate 333 configured as described above are centrally held together with a plurality of outer damper springs 31a and inner damper springs 31b in a space portion between the front cover 10 and the rear holding plate 333 with respect to the axial direction. A plate 332 is disposed, and the center holding plate 332, the plurality of outer damper springs 31a, and the inner damper spring 31b are sandwiched and held. The front cover 10 and the rear holding plate 333 hold the center holding plate 332 so as to be relatively rotatable with both sides in the axial direction interposed therebetween.

  The damper mechanism 330 configured as described above transmits a part of the driving force from the engine transmitted to the front cover 10 to the rear holding plate 333 through the connecting portion 360. The damper mechanism 330 transmits the driving force transmitted to the front cover 10 and the driving force transmitted to the rear holding plate 333 from the circumferential end of the front holding portion 311c, the outer rear holding portion 33a, and the inner rear holding portion 33b to the outer damper. This is transmitted to the spring 31a and the inner damper spring 31b. The damper mechanism 330 transmits the driving force transmitted to the outer damper spring 31a and the inner damper spring 31b to the center holding plate 332 via the circumferential end portions of the outer center holding portion 32b and the inner center holding portion 32c. Therefore, the driving force from the engine transmitted to the front cover 10 is transmitted to the center holding plate 332 via the outer damper spring 31a and the inner damper spring 31b, and rotates in the same direction as the front cover 10. The damper mechanism 330 transmits the driving force transmitted to the center holding plate 332 to the lockup piston 342 via the spline 332e and the spline 342e.

  During this time, the outer damper springs 31a and the inner damper springs 31b are respectively connected to the front end portion 311c of the front cover 10, the outer rear holding portion 33a of the rear holding plate 333, and the circumferential end portions of the inner rear holding portion 33b. While being held between the outer center holding portion 32b of the holding plate 332 and the circumferential end of the inner center holding portion 32c, the holding plate 332 is elastically deformed according to the magnitude of the transmitted driving force.

  Here, the lockup piston 342 and the lockup plate 41 described above have a relatively large outer diameter φD1 which is the radial length of the lockup plate 41, and the radial length of the lockup piston 342. The outer diameter φD2 is set relatively small. The lock-up plate 41 of the present embodiment is formed such that the radially outer end 41a is bent toward the turbine shell 22b, that is, toward the output shaft, and the distal end of the radially outer end 41a is the turbine. It extends to a predetermined position spaced apart from the radially outer end of the shell 22b.

  And the torque converter 301 of this embodiment is provided with the hydraulic fluid guide part 370 as mentioned above. The hydraulic oil guide part 370 includes a receiving part 371 and a guide part 372. Here, the hydraulic oil guide portion 370 also serves as a portion in the vicinity of the radially outer end portion of the rear holding plate 333 of the damper mechanism 330.

  The receiving portion 371 is a portion of the rear holding plate 333 in the vicinity of the connecting projection 333 c and is formed in an annular shape coaxial with the rotation axis X. Specifically, in the rear holding plate 333, the receiving portion 371 is located radially inward from the inner peripheral surface of the front cover 10 (or the pump shell 21b) in the piston hydraulic chamber 45 of the lockup clutch mechanism 340. It is a protruding part. That is, the receiving portion 371 is a wall surface formed substantially perpendicular to the rotation axis X at the radially outer end of the rear holding plate 333. In other words, the receiving portion 371 is positioned in the radial direction at the radial outer end 41a of the lockup plate 41, the radial outer end 42b of the lockup piston 342, the inner peripheral surface of the pump shell 21b, and the flange portion 12. Of the rear holding plate 333 formed so as to protrude radially inward from the inner peripheral surface of the front cover 10 (or the pump shell 21b) so as to be in a position substantially equivalent to the communicating portion between the inner peripheral surface and the inner peripheral surface. It is a part.

  The guide portion 372 is a portion of the rear holding plate 333 that extends from the radially inner end of the receiving portion 371 toward the surface of the lockup piston 342 on the piston hydraulic chamber 45 side, that is, toward the pressure receiving surface 342c.

  Here, the outer rear holding portion 33a of the rear holding plate 333 is formed by recessing the engine-side wall surface of the rear holding plate 333 toward the output shaft. In other words, the outer rear holding portion 33a is formed such that the surface of the rear holding plate 333 on the lockup piston 342 side protrudes toward the lockup piston 342 side. The rear holding plate 333 has a shape in which a portion where the outer rear holding portion 33a and the above-described connecting projection portion 333c continue is inclined toward the pressure receiving surface 342c of the lockup piston 342 at the radially outer end portion. It has become. The hydraulic oil guide portion 370 of the present embodiment is a wall surface portion that forms the outer rear holding portion 33a in the rear holding plate 333, and the wall portion of this inclined portion that faces the pressure receiving surface 342c from the connecting projection portion 333c is guided to the guide portion 372. It is also used as. That is, the guide portion 372 is a wall surface portion that forms the outer rear holding portion 33a in the rear holding plate 333, and the diameter gradually decreases toward the pressure receiving surface 342c (from the engine side to the output shaft side). It is a part of such a cylindrical shape (conical truncated cylinder shape). The hydraulic oil guide portion 370 is formed with a portion that is also used as the receiving portion 371 from the end portion on the large diameter side (end portion on the engine side) of the guide portion 372 toward the radially outer side.

  Therefore, the hydraulic oil guide 370 supplies hydraulic oil to the fluid transmission mechanism space A when the lockup clutch mechanism 340 is turned on, and from the fluid transmission mechanism space A side, which is the inner side of the fluid transmission mechanism 20. When the working oil flows into the clutch space B that functions as the working fluid flow path 44, the radially outer end 41a of the lockup plate 41, the radially outer end 42b of the lockup piston 342, and the pump shell 21b The receiving portion 371 receives the flow of hydraulic fluid that passes through the communication portion between the inner peripheral surface and the inner peripheral surface of the flange portion 12 and flows into the damper mechanism space portion C that functions as the piston hydraulic chamber 45. it can.

  The hydraulic oil guide section 370 guides the flow of hydraulic oil received by the receiving section 371 toward the pressure receiving surface 342c of the lockup piston 342 along the guide section 372, so that the ON control of the lockup clutch mechanism 240 is performed. At the start, the flow of hydraulic oil hits the pressure receiving surface 342c of the lockup piston 342 in a direction that promotes the lockup operation in which the lockup piston 342 approaches the lockup plate 41 side. Thereby, the kinetic energy of the hydraulic oil can be used for the lock-up operation in which the lock-up piston 342 approaches the lock-up plate 41, so that the responsiveness of the lock-up operation can be further improved.

  And according to the torque converter 301 which concerns on embodiment of this invention demonstrated above, the sealing member 48 is provided between the radial direction inner side protrusion part 42a of the lockup piston 342, and the level | step-difference part 11a of the front cover 10. FIG. Therefore, the area of the pressure receiving surface 342c of the lockup piston 342 can be relatively increased, and the pressing force acting on the lockup piston 342 from the piston hydraulic chamber 45 can be relatively increased. The torque capacity that can be transmitted on the friction engagement surface 43 of the clutch mechanism 340 can be increased, and the performance of the lockup clutch mechanism 340 can be improved.

  Furthermore, according to the torque converter 301 according to the embodiment of the present invention described above, the outer diameter φD1 of the lockup plate 41 located on the upstream side of the flow of hydraulic oil is set relatively large, and the position is located on the downstream side. Since the outer diameter φD2 of the lockup piston 342 is set to be relatively small, when the lockup clutch mechanism 340 starts ON control, the lockup plate 41 causes the hydraulic oil flow to collide with the lockup piston 342. Since it can suppress, the responsiveness of the lockup operation | movement in which the lockup piston 342 approaches the lockup plate 41 side can be improved.

  Furthermore, according to the torque converter 301 according to the embodiment of the present invention described above, the piston hydraulic chamber 45 of the lockup piston 342 receives the flow of hydraulic oil from the working fluid flow path 44 side in the piston hydraulic chamber 45. A hydraulic oil guide portion 370 for guiding toward the pressure receiving surface 342c on the side is provided. Therefore, when the lockup clutch mechanism 340 is ON-controlled, the hydraulic oil is supplied to the fluid transmission mechanism space A and functions as the working fluid flow path 44 from the fluid transmission mechanism space A side which is the inside of the fluid transmission mechanism 20. When the hydraulic oil flows into the clutch space B, the flow of the hydraulic oil flowing into the piston hydraulic chamber 45 is guided by the hydraulic oil guide portion 370 toward the pressure receiving surface 342c of the lockup piston 342. Since the kinetic energy of the hydraulic oil can be used for a lock-up operation in which the lock-up piston 342 approaches the lock-up plate 41, the responsiveness of the lock-up operation can be further improved.

  Furthermore, according to the torque converter 301 according to the embodiment of the present invention described above, a plurality of damper springs 31 provided between the lock-up piston 342 and the front cover 10 in the axial direction can be transmitted. A center holding plate 332 that holds the lock-up piston 342 so as to be integrally rotatable and is capable of relative movement in the axial direction, and a plurality of dampers provided between the lock-up piston 342 and the center holding plate 332 in the axial direction. A rear holding plate 333 that holds the spring 31 so as to be able to transmit a driving force and is connected to the front cover 10 so as to rotate integrally therewith is connected, and the front cover 10 and the lockup piston 342 are connected via a plurality of damper springs 31. And a hydraulic oil guide 37. It is provided on the radially outer end of the rear support plate 333. Therefore, since the radially outer end of the rear holding plate 333 is also used as the hydraulic oil guide 370, the flow of the hydraulic oil flows toward the pressure receiving surface 342c of the lockup piston 342 without providing a separate guide means. As a result, weight reduction and size reduction can be achieved.

(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 is different from the fluid transmission device according to the third embodiment in that a cover portion is provided on the first engagement member. Is different. 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 a torque converter 401 as a fluid transmission device according to the fourth embodiment, a cover 441a is provided on a lock-up plate 41 as a first engagement member.

  The cover portion 441 a is provided at a radially outer end portion of the lockup plate 41 as a part of the lockup plate 41. The cover portion 441a is a portion that is formed in a cylindrical shape that is coaxial with the rotation axis X, with the radially outer end of the lockup plate 41 protruding toward the lockup piston 342 as the second engagement member along the axial direction. is there. The cover portion 441a is formed to cover the radially outer end portion 42b of the lockup piston 342 with a predetermined interval in the radial direction.

  In the present embodiment, the cover portion 441a is configured separately from the main body portion of the lockup plate 41 and is fixed by, for example, welding. However, the present invention is not limited thereto, and the lockup plate 41 including the cover portion 441a is not limited thereto. May be configured integrally. Further, the outer diameter φD1 of the lockup plate 41 is a length along the radial direction from the rotation axis X to the outer peripheral surface of the cover portion 441a.

  As described in the third embodiment, the torque converter 401 configured as described above supplies hydraulic oil to the fluid transmission mechanism space A during the ON control of the lockup clutch mechanism 340, so that the inside of the fluid transmission mechanism 20 When the hydraulic fluid flows from the fluid transmission mechanism space A, which is the side, into the clutch space B that functions as the hydraulic fluid flow path 44, the flow of the hydraulic fluid flowing into the piston hydraulic chamber 45 is changed to the hydraulic fluid guide portion. By guiding to the pressure receiving surface 342c of the lockup piston 342 by 370, the kinetic energy of the hydraulic oil can be used for the lockup operation in which the lockup piston 342 approaches the lockup plate 41 side. The responsiveness of the up operation can be further improved.

  Further, according to the torque converter 401 according to the embodiment of the present invention described above, the lock-up plate 41 has the radially outer end portion 42b of the lock-up piston 342 at the radially outer end portion. A cover portion 441a is provided to cover with a gap. Therefore, a part of the flow of the hydraulic oil guided toward the pressure receiving surface 342c of the lockup piston 342 by the hydraulic oil guide portion 370 is guided to the clutch space portion B that functions as the hydraulic fluid flow path 44 by the cover portion 441a. Therefore, the flow of the hydraulic oil to the working fluid flow path 44 can be stabilized, and the responsiveness of the lockup operation can be further 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.

  In the above description, the first engagement member and the second engagement member are set such that the radial length of the first engagement member is relatively long, and the radial length of the second engagement member is Although described as being set relatively short, it is not limited to this and may be equivalent.

  In the above description, the guide means is described as being provided on the side holding member of the damper means. However, the guide means is not limited thereto, and for example, the guide means may be provided separately from the side holding member of the damper means. .

  As described above, the fluid transmission device according to the present invention can improve the performance of the lockup means, and is suitable for application to various fluid transmission devices including the lockup means.

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 Front cover 11a Step part (opposite part)
20 Fluid transmission mechanism (fluid transmission means)
30 Damper mechanism 31 Damper spring (elastic body)
31a Outer damper spring 31b Inner damper spring 32 Center holding plate 33 Rear holding plate 34 Front holding plates 40, 240, 340 Lock-up clutch mechanism (lock-up means)
41, 241 Lock-up plate (first engaging member)
42, 342 Lock-up piston (second engaging member)
42a Radial inner protrusion (radial inner edge)
42c, 342c Pressure receiving surface 43, 243 Friction engagement surface 44 Working fluid flow path 45 Piston hydraulic chamber (hydraulic chamber)
46 friction material 47, 247 opposing wall surface 48 sealing member (sealing means)
50 Output shaft 52 Hub 245 Plate hydraulic chamber 330 Damper mechanism (damper means)
332 Center holding plate (center holding member)
333 Rear holding plate (side holding member)
370 Hydraulic oil guide (guide means)
371 Receiving portion 372 Guide portion 441a Cover portion A Fluid transmission mechanism space portion B Clutch space portion C Damper mechanism space portion X Rotation axis

Claims (7)

Fluid transmission means capable of transmitting the driving force transmitted from the driving source to the front cover to the output shaft via the working fluid;
A first engagement member provided on the fluid transmission means side of the front cover and rotatable integrally with the output shaft; and connected to the front cover on the fluid transmission means side of the front cover in the axial direction of the output shaft. A second engagement member that is movable relative to the first engagement member along the axial direction, and is provided between the second engagement member and the front cover with respect to the axial direction by an internal working fluid. A hydraulic chamber that applies a pressing force to the second engaging member toward the first engaging member, and the operating fluid in the hydraulic chamber causes the pressing force to act on the second engaging member. The output shaft transmits the driving force transmitted to the front cover via the second engagement member and the first engagement member by frictionally engaging the first engagement member and the second engagement member. And a lock-up means capable of transmitting to
The lock-up means includes a radial inner end of the second engagement member with respect to a radial direction orthogonal to the axial direction, and the radial inner end of the second engagement member and the radial direction in the front cover. A sealing means for preventing leakage of the working fluid is provided between the facing portion and the facing portion ,
Further, the lock-up means is formed between the first engagement member and the second engagement member with respect to the axial direction, and inside the fluid transmission means and outside of the hydraulic chamber and the radial direction. A working fluid channel formed so as to be able to communicate, and when the first engagement member and the second engagement member are frictionally engaged, from the inside of the fluid transmission means to the working fluid channel side The working fluid flows;
The first engagement member and the second engagement member are arranged on the upstream side of the flow of the working fluid when the first engagement member and the second engagement member are frictionally engaged. The joint member is located and the second engagement member is located downstream, and the radial length of the first engagement member is set to be relatively long, and the radial direction of the second engagement member The radial length of the first engagement member is set to be longer than the radial length of the second engagement member .
Fluid transmission device. The radially inner end of the second engagement member is formed to protrude toward the front cover along the axial direction,
The opposed portion of the front cover is formed such that the radially inner end portion of the second engagement member can be inserted on a radially inner side of the front cover.
The sealing means is provided in contact with an outer peripheral surface of the radially inner end portion of the second engagement member and an inner peripheral surface of the facing portion of the front cover,
The fluid transmission device according to claim 1. The first engaging member is characterized in that a radially outer end in the radial direction is curved toward the second engaging member.
The fluid transmission device according to claim 1 or 2 . The first engagement member is provided to be movable relative to the second engagement member along the axial direction.
The fluid transmission device according to any one of claims 1 to 3 . And a guide means for receiving the flow of the working fluid from the working fluid flow path side in the hydraulic chamber and guiding the flow toward the surface of the hydraulic chamber side of the second engagement member,
The fluid transmission device according to any one of claims 1 to 4 . A plurality of elastic bodies provided between the second engagement member and the front cover with respect to the axial direction are held so as to be able to transmit a driving force, and the second engagement member can rotate integrally and in the axial direction. A center holding member provided to be relatively movable, and provided between the second engagement member and the center holding member with respect to the axial direction to hold the plurality of elastic bodies so as to be able to transmit a driving force and A side holding member connected to the cover so as to be integrally rotatable, and a damper means for connecting the front cover and the second engagement member via the plurality of elastic bodies,
The guide means is provided at a radially outer end of the side holding member,
The fluid transmission device according to claim 5 . The first engagement member has a cover portion that covers a radially outer end portion of the second engagement member at a predetermined interval in the radial direction at a radially outer end portion.
The fluid transmission device according to claim 5 or 6 .

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