JP2014074438A - Clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress radial expansion of a snap ring while regulating movement of an oil chamber defining member for defining an oil chamber together with a piston using the snap ring.SOLUTION: A lock-up clutch 8 of a launch device 1 includes a snap ring movement regulating member 95 that regulates movement of a flange member 85 for defining an engagement-side oil chamber 86 together with a lock-up piston 80 using a snap ring 90, is supported by the flange member 85 to be positioned outside the snap ring 90, and regulates radial movement of the snap ring 90. As a result, radial expansion of the snap ring 90 can be suppressed while the movement of the flange member 85 is regulated by the snap ring 90.

Description

  The present invention relates to a clutch that couples both an input member and an output member so that power is transmitted from the input member to the output member, and releases the connection between the input member and the output member.

  Conventionally, as this type of clutch, a first friction engagement plate fitted to a clutch hub provided on an input member, a second friction engagement plate fitted to a clutch drum provided on an output member, An oil chamber defining member that defines an engagement side oil chamber that moves in the axial direction and presses the first and friction engagement plates and an oil chamber that is disposed behind the piston and is supplied with hydraulic oil together with the piston. A lock-up clutch provided with a flange member) is known (for example, see Patent Document 1). In this lockup clutch, the oil chamber defining member is integrated with a clutch drum fixed to the input element of the damper mechanism.

  Further, as this type of clutch, there is also known an automatic transmission clutch that restricts movement in the axial direction of an oil chamber defining member that defines an engagement side oil chamber together with a piston by a snap ring (for example, a patent) Reference 2). In this clutch, the snap ring is mounted in a snap ring groove formed in a member that supports the piston and the oil chamber defining member, and is fitted in an annular groove (step portion) formed in the oil chamber defining member. It is. Thereby, it is suppressed that a snap ring expands in a radial direction and separates from a snap ring groove.

International Publication No. 2012/016650 US Patent Application Publication No. 2010/0178102

  In the clutch described in Patent Document 1, the oil chamber defining member cannot be moved to both the clutch drum side and the piston side in the axial direction of the piston. There is no specific disclosure of the structure. Further, in the clutch described in Patent Document 2, since the oil chamber defining member can move to the piston side by the stroke of the piston, the oil chamber defining member is moved to the piston side, and then the snap ring groove is formed. By attaching the snap ring and returning the oil chamber defining member to the snap ring side, the snap ring is fitted into an annular groove formed in the oil defining member. Therefore, as in the clutch described in Patent Document 1, if the oil chamber defining member cannot move to the piston side or if the movement amount to the piston side allowed by the oil chamber defining member is small, The snap ring cannot be fitted into the groove of the oil chamber defining member, and the expansion of the snap ring in the radial direction cannot be suppressed.

  Therefore, the main object of the present invention is to suppress expansion of the snap ring in the radial direction while restricting movement of the oil chamber defining member that defines the oil chamber together with the piston by the snap ring.

  The clutch according to the present invention employs the following means in order to achieve the main object.

The clutch according to the present invention comprises:
In the clutch that connects the two so that power is transmitted from the input member to the output member, and releases the connection between the input member and the output member,
A first friction engagement plate fitted to a clutch hub provided on the input member;
A second friction engagement plate fitted to a clutch drum provided on the output member;
A piston that moves in an axial direction and presses the first and second friction engagement plates;
An oil chamber defining member that is attached to the input member so as to rotate integrally with the input member and that defines an engagement side oil chamber to which hydraulic oil is supplied together with the piston;
A snap ring for restricting movement in the axial direction of the oil chamber defining member relative to the input member;
A snap ring movement restricting member that is supported by the oil chamber defining member so as to be located outside the snap ring and restricts movement of the snap ring in a radial direction;
It is characterized by providing.

  This clutch restricts the movement of the oil chamber defining member that defines the engagement side oil chamber together with the piston by the snap ring, and is supported by the oil chamber defining member so as to be positioned outside the snap ring. And a snap ring movement restricting member for restricting movement of the snap ring in the radial direction. As a result, even if the oil chamber defining member cannot move to the piston side or the amount of movement to the piston side allowed by the oil chamber defining member is small, the oil chamber defining member can be moved. While restricting by the snap ring, it is possible to suppress expansion of the snap ring in the radial direction.

  The input member may include a concave portion that is recessed in the axial direction, and a cylindrical portion that surrounds the concave portion, and a base end portion of the oil chamber defining member is formed in the concave portion of the input member. The piston may be inserted, and the piston may be supported by the cylindrical portion so as to be movable in the axial direction. Thereby, it becomes possible to suppress the increase in the dimension of the clutch in the axial direction. In this case, since the base end portion of the oil chamber defining member is located on the inner side of the piston, the dimension in the radial direction of the oil chamber defining member is increased. However, since the oil chamber defining member rotates integrally with the input member, even if the inertia during rotation of the oil chamber defining member increases, the oil chamber defining member and the input member are also increased. There is no adverse effect on the contact area. The base end portion of the oil chamber defining member may be inserted into the recess so that at least a part of the front end surface is in contact with the bottom surface of the recess.

  Further, at least one rotation restricting recess may be formed in the recess of the input member, and the base end portion of the oil chamber defining member is engaged with the rotation restricting recess of the input member. A rotation restricting convex portion may be formed. Accordingly, it is possible to reliably rotate both the oil chamber defining member and the input member while simplifying the configuration for integrally rotating the oil chamber defining member and the input member.

  The oil chamber defining member may include a movement restricting portion that restricts movement of the snap ring movement restricting member in the axial direction.

  Furthermore, the first and second friction engagement plates may be disposed outside the engagement side oil chamber. Thereby, it becomes possible to suppress the increase in the dimension of the clutch in the axial direction more favorably.

  The input member may be connected to a prime mover, the output member may be connected to an input shaft of a transmission, and the clutch may be a lockup that connects the input member and the output member. You may comprise as a lockup clutch which selectively performs cancellation | release of this lockup.

It is sectional drawing which shows the starting apparatus 1 which concerns on one Embodiment of this invention. 1 is an enlarged cross-sectional view showing a starting device 1. It is explanatory drawing for demonstrating the centerpiece 30 of the front cover 3. FIG. FIG. 10 is an explanatory diagram for explaining a support structure of a snap ring movement restriction member 95 in a flange member 85. 2 is a plan view showing a damper mechanism 10. FIG.

  Next, the form for implementing this invention is demonstrated, referring drawings.

  FIG. 1 is a cross-sectional view showing a starting device 1 according to an embodiment of the present invention, and FIG. 2 is an enlarged cross-sectional view showing the starting device 1. A starting device 1 shown in these drawings is mounted on a vehicle including an engine (internal combustion engine) (not shown) as a prime mover, and includes a front cover 3 as an input member connected to a crankshaft of the engine, A pump impeller (input side fluid transmission element) 4 fixed to the cover 3, a turbine runner (output side fluid transmission element) 5 that can rotate coaxially with the pump impeller 4, an automatic transmission (AT) or continuously variable (not shown). A turbine hub 7 as an output member fixed to an input shaft IS of a transmission which is a transmission (CVT), a lock-up clutch 8 which is a hydraulic multi-plate clutch, and a damper mechanism 10 connected to the turbine hub 7 including.

  The front cover 3 includes a center piece 30 and a cover body 33 fixed to the center piece 30 by welding. As shown in FIG. 2, the centerpiece 30 includes a large-diameter cylindrical portion (cylindrical portion) 301 located on the engine side (not shown), and the damper mechanism 10 inside the large-diameter cylindrical portion 301 rather than the large-diameter cylindrical portion 301. And a cylindrical small-diameter cylindrical portion 302 formed so as to protrude to the side. In the present embodiment, the small-diameter cylindrical portion 302 of the center piece 30 is formed so as to overlap with the end of the large-diameter cylindrical portion 301 on the damper mechanism 10 side as viewed from the radial direction. An annular recess 303 is formed which is surrounded by the diameter cylindrical portion 301 and is recessed in the axial direction and on the engine side.

  In the recess 303 of the center piece 30, as shown in FIG. 3, a plurality (six in this embodiment) of rotation restricting recesses 304 are formed at equal intervals (60 ° in this embodiment). . The turbine hub 7 is rotatably fitted inside the small diameter cylindrical portion 302 of the center piece 30, and a seal member such as an O-ring is disposed between them, and the end surface of the small diameter cylindrical portion 302 and the turbine hub 7 are disposed. A washer is placed between the two. The cover body 33 of the front cover 3 includes a side wall portion 34 extending in the radial direction and an outer cylinder portion 35 extending from the outer periphery of the side wall portion 34 in the axial direction of the starting device 1. A set block 36 connected to a drive plate (not shown) attached to a crankshaft of an engine (not shown) is fixed to the outer peripheral portion of the side wall 34 of the cover body 33 by welding or the like.

  The pump impeller 4 includes a pump shell 40 that is tightly fixed to the outer cylinder portion 35 of the front cover 3, and a plurality of pump blades 41 that are disposed on the inner surface of the pump shell 40. The turbine runner 5 includes a turbine shell 50 and a plurality of turbine blades 51 disposed on the inner surface of the turbine shell 50. As shown in FIGS. 1 and 2, the turbine shell 50 is fitted to the turbine hub 7 and fixed to the turbine hub 7 via a rivet 55. The pump impeller 4 and the turbine runner 5 face each other, and a stator 6 that rectifies the flow of hydraulic oil (working fluid) from the turbine runner 5 to the pump impeller 4 is coaxially disposed between the pump impeller 4 and the turbine runner 5.

  The stator 6 has a plurality of stator blades 60, and the rotation direction of the stator 6 is set in only one direction by the one-way clutch 61. The pump impeller 4, the turbine runner 5, and the stator 6 form a torus (annular flow path) for circulating hydraulic oil, and function as a torque converter (fluid transmission device) having a torque amplification function. However, in the starting device 1, the stator 6 and the one-way clutch 61 may be omitted, and the pump impeller 4 and the turbine runner 5 may function as a fluid coupling.

  As shown in FIG. 2, the turbine hub 7 includes a large-diameter aligning portion 71 into which the turbine shell 50 is fitted and a small-diameter cylindrical portion 302 as an axial end portion of the center piece 30. A small-diameter aligning portion 72 having an annular shape and an annular recess 73 in which a thrust bearing 65 that rotatably supports the stator 6 is disposed are formed. The outer peripheral surface of the large-diameter aligning portion 71 is formed as a cylindrical surface whose center of curvature is the axis of the starting device 1. The outer peripheral surface of the small-diameter aligning portion 72 is formed as a cylindrical surface having a curvature radius smaller than the curvature radius of the outer peripheral surface of the large-diameter aligning portion 71 with the axis center of the starting device 1 as the center of curvature. . The recess 73 is formed in the turbine hub 7 so as to be located inside the large diameter aligning portion 71 and the rivet 55.

  The lock-up clutch 8 is a lock-up mechanism that mechanically connects (via the damper mechanism 10) the pump impeller 4 and the turbine runner 5, that is, the front cover 3 and the input shaft IS of the transmission fixed to the turbine hub 7. The release of the lock-up is selectively performed, and is disposed between the damper mechanism 10 and the side wall portion 34 of the front cover 3 as shown in FIGS. 1 and 2. The lock-up clutch 8 includes a lock-up piston 80 supported by the center piece 30 of the front cover 3 so as to be movable in the axial direction, and a side wall 34 of the front cover 3 (cover body 33) so as to face the lock-up piston 80. An annular clutch hub 81 fixed to the clutch, a clutch drum 82 coupled to the input shaft IS of the transmission via the damper mechanism 10, and a plurality of first gears fitted to splines formed on the outer periphery of the clutch hub 81. 1 friction engagement plate 83 (separator plate), a plurality of second friction engagement plates (plate bodies having friction material on both surfaces) 84 fitted to splines formed on the inner periphery of the clutch drum 82, and a lock It is attached to the center piece 30 of the front cover 3 so as to be positioned closer to the damper mechanism 10 than the up piston 80. An annular flange member (oil chamber defining member) and a 85.

  The lock-up piston 80 is fitted into the large-diameter cylindrical portion 301 of the center piece 30 and has an inner peripheral portion 80a facing the inner surface of the front cover 3 (such as the side wall portion 34 of the cover main body 33) and an inner peripheral portion 80a. It has a cylindrical portion 80b extending from the outer peripheral portion toward the damper mechanism 10 and in the axial direction, and a pressing portion 80c extending outward from the cylindrical portion 80b toward the front cover 3. As shown in FIG. 1, the inner peripheral portion 80 a of the lockup piston 80 is in sliding contact with the outer peripheral surface of the large-diameter cylindrical portion 301 of the center piece 30 through a seal member such as an O-ring. Further, as shown in FIG. 1, the cylindrical portion 80b of the lock-up piston 80 is spline-fitted to the inner peripheral portion of the clutch hub 81 fixed to the front cover 3 (cover body 33). A part thereof is disposed inside the clutch hub 81 and is supported by the large-diameter cylindrical portion 301 of the front cover 3 so as to be movable in the axial direction of the starting device 1. Further, the pressing portion 80 c of the lock-up piston 80 is one of the plurality of first friction engagement plates 83 fitted to the clutch hub 81, one of which is located closest to the damper mechanism 10 (the outer periphery and the inner periphery). And the central part of the head.

  The clutch hub 81 is fixed to the inner surface of the side wall 34 of the cover main body 33 by welding, and the clutch hub 81 and the clutch drum 82 are arranged in a region on the outer peripheral side in the front cover 3 as shown in the figure. As shown in FIG. 1, the clutch drum 82 includes a cylindrical annular portion (axially extending portion) 82a extending in the axial direction on the side opposite to the front cover 3, and an end portion of the annular portion 82a. A fastening portion 82b extending radially inward. Further, the side wall 34 of the cover body 33 is formed by press molding so as to protrude in the axial direction toward the lockup piston 80, and among the plurality of first friction engagement plates 83 supported by the clutch hub 81. 1 has an annular contact portion 34a (see FIG. 1) that contacts one substantially central portion (the central portion between the outer periphery and the inner periphery) located closest to the front cover 3 side. Thus, the so-called backing plate (end plate) is omitted by forming the abutting portion 34a that abuts one of the first and second friction engagement plates 83, 84 on the front cover 3 (side wall portion 34). Thus, the number of parts can be reduced.

  The flange member 85 is formed by press-molding a plate material, and a base end portion 85a fitted to the small-diameter cylindrical portion 302 of the center piece 30 and a cylindrical portion of the lockup piston 80 via a seal member such as an O-ring. A cylindrical outer peripheral portion 85b that slides in contact with the inner peripheral surface of 80b and guides the movement of the lockup piston 80 in the axial direction, and the outer periphery of the outer peripheral portion 85b from the outer edge on the lockup piston 80 side and in the radial direction (axial direction) And a piston movement restricting portion 85c having an annular surface extending in a direction orthogonal to the direction. The base end portion 85 a of the flange member 85 is formed with a rotation restricting convex portion 854 that engages with a corresponding one of the plurality of rotation restricting concave portions 304 formed in the concave portion 303 of the center piece 30.

  As shown in FIG. 2, the base end portion 85 a of the flange member 85 has each rotation restricting projection 854 engaged with the corresponding rotation restricting recess 304 of the center piece 30, and its distal end surface 850 is in contact with the bottom surface of the recess 303. It inserts in the said recessed part 303 so that it may contact | abut. Therefore, the movement of the flange member 85 toward the front cover 3 side, that is, the lock-up piston 80 side (left side in the figure) is restricted by the bottom surface of the recess 303, and the flange member 85 moves toward the front cover 3 side, that is, the lock-up piston 80 side. It cannot move substantially. The snap ring groove 305 (see FIG. 3) formed in the small diameter cylindrical portion 302 of the center piece 30 is in contact with the flat end surface 851 on the turbine runner 5 side (right side in the drawing) of the base end portion 85a. A snap ring 90 is attached. Thereby, the axial movement of the flange member 85 relative to the front cover 3 is restricted by the snap ring 90, and the flange member 85 is fixed to the center piece 30 so as to rotate integrally with the front cover 3. The flange member 85 fitted to the small diameter cylindrical portion 302 overlaps with the large diameter cylindrical portion 301 when viewed from the radial direction.

  Further, in the starting device 1, an annular flat plate-shaped snap ring movement restricting member 95 is disposed so as to be positioned outside the snap ring 90 attached to the center piece 30. The snap ring movement restricting member 95 has an inner diameter that is slightly larger than the outer diameter of the snap ring 90 mounted in the snap ring groove 305 so as to contact the flat end surface 851 of the base end portion 85a and surround the snap ring 90. Is supported by the flange member 85. That is, as shown in FIGS. 2 and 4, the flange member 85 has a plurality (six in this embodiment) of movement restricting portions 855 for restricting movement of the snap ring movement restricting member 95 in the axial direction. (In this embodiment, it is formed at intervals of 60 °). In the present embodiment, each movement restricting portion 855 is a portion surrounding the snap ring movement restricting member 95 of the base end portion 85a in a state where the snap ring movement restricting member 95 is in contact with the flat end surface 851 of the base end portion 85a. Is formed by pressing (caulking) a part (see the dotted line portion in FIG. 4) to project inward. However, instead of forming the movement restricting portion 855 on the flange member 85, the snap ring movement restricting member 95 may be fixed to the flange member 85 by welding or the like. This corresponds to the restriction unit 855. Furthermore, a second snap ring may be used as the snap ring movement restricting member, and the snap ring movement restricting member may be mounted in an annular groove formed in the flange member 85 so as to surround the snap ring 90.

  The flange member 85 guides the movement of the lockup piston 80 in the axial direction by the outer peripheral portion 85b, and is on the opposite side of the lockup piston 80 from the front cover 3 (side wall portion 34) and the first and second frictions. An engagement side oil chamber 86 is defined inside the engagement plates 83 and 84 together with the lockup piston 80. The engagement side oil chamber 86 is formed in an oil passage (not shown) formed on the input shaft IS of the transmission and a center piece 30 from a hydraulic control device (not shown) connected to an oil pump (not shown) driven by the engine. In order to engage the lock-up clutch 8 via the oil passage 30a and the plurality of oil grooves 306 (see FIG. 2) formed in the bottom surface of the recess 303 of the center piece 30 (in a fully engaged state or a slip state) Hydraulic oil (lock-up pressure) is supplied. Instead of forming the plurality of oil grooves 306 on the bottom surface of the recess 303, a plurality of oil grooves may be formed on the distal end surface 850 of the base end portion 85a of the flange member 85. In the present embodiment, the oil passage 30a formed in the center piece 30 opens in the axial direction with respect to the engagement side oil chamber 86 as shown in FIG.

  Further, the vicinity of the joint portion between the center piece 30 and the cover main body 33 is recessed so as to be separated from the engine so as to avoid interference with members on the engine side, and the vicinity of the joint portion between the center piece 30 and the cover main body 33. A plurality of return springs 87 are disposed between the inner periphery 80a of the lockup piston 80 and the inner periphery 80a. The front cover 3 and the lockup piston 80 are fluid transmissions defined by the front cover 3 and the pump shell 40 of the pump impeller 4 inside the clutch hub 81, that is, the first and second friction engagement plates 83 and 84. An oil passage (oil chamber) 88 for supplying hydraulic oil to the chamber, that is, the first and second friction engagement plates 83 and 84, the pump impeller 4, the turbine hub 7, the damper mechanism 10, and the like is defined. The oil passage 88 is provided with hydraulic oil (for example, a line) from a hydraulic control device (not shown) to a fluid transmission chamber via an oil passage (not shown) formed on the input shaft IS of the transmission and an oil passage 30b formed in the center piece 30. The circulation pressure obtained by reducing the pressure or the like). As shown in FIG. 1, the clutch hub 81 is formed with an opening 81o that allows the oil passage 88 to communicate with the first and second friction engagement plates 83 and 84, that is, the fluid transmission chamber. Is formed with an opening 82o that allows the oil passage 88 side and the fluid transmission chamber to communicate with each other.

  As shown in FIGS. 1 and 2, the damper mechanism 10 includes a drive member 11 as an input element and a first intermediate engaged with the drive member 11 via a plurality of first outer peripheral springs (first elastic bodies) SP11. A second intermediate member 14 that engages with the first intermediate member 12 via a member (annular member) 12 and a plurality of second outer peripheral springs (first elastic bodies) SP12 and constitutes an intermediate element together with the first intermediate member 12. And a driven member (output element) 15 that engages with the second intermediate member 14 via a plurality of inner peripheral springs (second elastic bodies) SP2. In the damper mechanism 10, the first and second outer peripheral springs SP <b> 11 and SP <b> 12 are compressed by the relative rotation of the drive member 11 and the first and second intermediate members 12 and 14, respectively. The member 14 and the driven member 15 are compressed by relative rotation.

  In the present embodiment, the first outer peripheral spring SP11 and the second outer peripheral spring SP12 are coil springs made of a metal material spirally wound so as to have an axis that extends straight when no load is applied, The first outer peripheral spring SP11 has higher rigidity (spring constant) than the second outer peripheral spring SP12. However, the first and second outer peripheral springs SP11 and SP12 may have the same rigidity (same specifications). Further, in the present embodiment, the inner peripheral spring SP2 includes an outer coil and an inner coil made of metal materials wound in opposite directions so as to have an axial center extending in an arc shape when no load is applied. Heavy arc spring. However, the inner peripheral spring SP2 may be an arc spring made of a single coil or a coil spring.

  The drive member 11 is a clutch drum of the lockup clutch 8 with the second intermediate member 14 as an intermediate element sandwiched between the outer peripheral side region of the fluid transmission chamber defined by the front cover 3 and the pump shell 40 of the pump impeller 4. It arrange | positions on the opposite side to 82, and is fixed to the some fastening part 82b of the clutch drum 82 via a rivet. As shown in FIGS. 1 and 5, the drive member 11 corresponds to a plurality of spring contact portions 11 a that extend toward the lockup clutch 8 and abut against one end of the corresponding first outer peripheral spring SP <b> 11. And a plurality of spring support portions (elastic body support portions) 11b that support the outer periphery of the first or second outer periphery springs SP11, SP12.

  The first intermediate member 12 surrounds the first and second outer peripheral springs SP11 and SP12 from the outside, and the first and second outer peripheral springs SP11 and SP12 together with the plurality of spring support portions 11b of the drive member 11 on the same circumference. It is comprised as an annular member which can be supported next to each other (alternately). As shown in FIGS. 1 and 2, the first intermediate member 12 is fitted to an annular portion 82a of the clutch drum 82 constituting the lockup clutch 8 so as to be rotatable around the axis of the starting device 1, It is supported in the radial direction by the outer peripheral surface of the annular portion 82a and disposed in the outer peripheral side region in the fluid transmission chamber. Further, as shown in FIGS. 1 and 5, the first intermediate member 12 includes a corresponding other end of the first outer peripheral spring SP11 and one end of the second outer peripheral spring SP12 adjacent to the first outer peripheral spring SP11. A plurality of spring abutting portions 12a (abutting portions) disposed between and abutting both are provided.

  The second intermediate member 14 sandwiches the annular first plate member 141 sandwiched between the clutch drum 82 of the lockup clutch 8 and the drive member 11, and the inner peripheral spring SP <b> 2 and the driven member 15 together with the first plate member 141. And an annular second plate member 142 connected (fixed) to the first plate member 141 via a rivet 145. The first plate member 141 of the second intermediate member 14 has a plurality of spring contact portions (second contact portions) 141a that contact the other end of the corresponding second outer peripheral spring SP12 on the outer peripheral portion, and an inner peripheral portion. A plurality of spring support portions for supporting the spring SP2 are provided on the inner peripheral portion. In addition, the second plate member 142 of the second intermediate member 14 has a plurality of spring support portions that support the inner peripheral spring SP2 so as to face the spring support portions of the first plate member 141, respectively. The first plate member 141 is formed with a plurality of spring abutting portions 141b (see FIG. 5) that abut against one end of the corresponding inner circumferential spring SP2. The second plate member 142 is also formed with a plurality of spring abutting portions (not shown) that abut against one end of the corresponding inner circumferential spring SP2.

  Thus, the plurality of first outer peripheral springs SP11 are arranged on the outer peripheral portion of the damper mechanism 10 so as to be positioned between the spring contact portion 11a of the drive member 11 and the spring contact portion 12a of the first intermediate member 12, respectively. The plurality of second outer peripheral springs SP12 are respectively disposed between the spring contact portion 12a of the first intermediate member 12 and the second intermediate member 14, that is, the spring contact portion 141a of the first plate member 141. It will be arranged on the outer periphery of the mechanism 10. Further, the plurality of inner peripheral springs SP2 are respectively spaced apart from the first and second outer peripheral springs SP11 and SP12 in the radial direction of the starting device 1, and are located on the inner side of the first and second outer peripheral springs SP11 and SP12. Will do.

  As shown in FIG. 2, the second plate member 142 that constitutes the second intermediate member 14 is rotatably fitted to the small-diameter aligning portion 72 of the turbine hub 7, and is radially arranged by the outer peripheral surface of the small-diameter aligning portion 72. Supported by Accordingly, the second intermediate member 14 including the first and second plate members 141 and 142 is centered by the small diameter aligning portion 72, that is, the turbine hub 7. Further, as shown in FIG. 2, the second plate member 142 is rotatably fitted in an annular portion 82 a of the clutch drum 82 constituting the lockup clutch 8. Thus, the clutch drum 82 is supported in the radial direction by the outer peripheral surface of the second plate member 142. Accordingly, the first intermediate member 12 fitted to the annular portion 82a of the clutch drum 82 is centered by the second intermediate member 14 (second plate member 142) via the annular portion 82a. Further, as described above, the drive member 11 that is an input element of the damper mechanism 10 is fixed to the plurality of fastening portions 82 b of the clutch drum 82. Accordingly, the drive member 11 is also centered by the second intermediate member 14 (second plate member 142) via the clutch drum 82.

  The driven member 15 is formed in an annular shape, and has a plurality of spring contact portions 15a that contact the other end of the corresponding inner peripheral spring SP2, as shown in FIGS. Further, as shown in FIGS. 2 and 5, the driven member 15 engages with any of the plurality of openings 142 b formed in the second plate member 142, and the second intermediate member 14 rotates with respect to the driven member 15. A plurality of protrusions 15b that regulate the above are formed.

  The driven member 15 is disposed between the first plate member 141 and the second plate member 142 of the second intermediate member 14 and is fitted to the large-diameter aligning portion 71 of the turbine hub 7, so that the turbine shell 50 is fixed to the turbine hub 7 through a rivet common to 50. Thus, the driven member 15 is centered by the large diameter aligning portion 71, that is, the turbine hub 7 together with the turbine runner 5. Here, in the present embodiment, the radius of curvature of the large-diameter aligning portion 71 is larger than the radius of curvature of the small-diameter aligning portion 72 as described above. Therefore, the inner diameter (the inner diameter of the center hole) of the inner peripheral side end of the second intermediate member 14, that is, the second plate member 142 fitted to the small diameter aligning portion 72 is fitted to the large diameter aligning portion 71. The inner diameter of the driven member 15 is smaller than the inner diameter (the inner diameter of the center hole). In the present embodiment, the rivets 145 for fastening the first and second plate members 141 and 142 constituting the second intermediate member 14 are arranged outside the driven member 15 as shown in FIGS. It is disposed inside the annular portion 82 a of the clutch drum 82.

  The lockup clutch 8 of the starting device 1 configured as described above restricts the movement of the flange member 85 that defines the engagement side oil chamber 86 together with the lockup piston 80 by the snap ring 90. And a snap ring movement restricting member 95 that is supported by the flange member 85 so as to be positioned outside the 90 and restricts the movement of the snap ring 90 in the radial direction. Thereby, the movement of the flange member 85 to the front cover 3 side, that is, the lock-up piston 80 side (left side in the figure) is restricted by the bottom surface of the recess 303 of the center piece 30, and the snap ring 90 is Even in the configuration in contact with the flat end surface 851 of 85a, it is possible to suppress the expansion of the snap ring 90 in the radial direction while restricting the movement of the flange member 85 by the snap ring 90.

  In the starting device 1, the center piece 30 of the front cover 3 includes a concave portion 303 that is recessed in the axial direction and a cylindrical large-diameter cylindrical portion 301 that surrounds the concave portion 303, and a proximal end portion of the flange member 85. 85 a is inserted into the recess 303 so that the tip surface 850 contacts the bottom surface of the recess 303 of the center piece 30, and the lockup piston 80 is supported by the large-diameter cylindrical portion 301 so as to be movable in the axial direction. As a result, it is possible to suppress an increase in the dimension in the axial direction of the lock-up clutch 8, particularly in the axial direction around the place where the return spring 87 is disposed. In the lock-up clutch 8, the base end portion 85 a of the flange member 85 is located on the inner side of the lock-up piston 80, so that the dimension in the radial direction of the flange member 85 increases, and the rotation of the flange member 85 is correspondingly increased. Although the inertia at the time also increases, since the flange member 85 rotates integrally with the front cover 3, even if the inertia at the time of rotation of the flange member 85 increases, the flange member 85 and the center piece 30 have a large diameter. There is no adverse effect on the contact portion with the cylindrical portion 301 or the seal member (O-ring) disposed between the two.

  Further, a plurality of rotation restricting recesses 304 are formed in the recess 303 of the center piece 30, and a rotation restricting projection 854 that engages with the rotation restricting recess 304 is formed in the base end portion 85 a of the flange member 85, thereby providing a flange member. While simplifying the configuration for integrally rotating 85 and the front cover 3, both can be reliably rotated integrally. Further, in the lockup clutch 8, the first and second friction engagement plates 83 and 84 are disposed outside the engagement side oil chamber 86, so that the dimension of the lockup clutch 8 in the axial direction is further improved. Can be suppressed.

  In the above-described embodiment, the lockup for selectively executing the lockup and the release of the lockup for connecting the front cover 3 connected to the engine and the turbine hub 7 connected to the input shaft IS of the transmission. Although the present invention has been described as being applied to the clutch 8, the application target of the present invention is not limited to this. That is, the present invention may be applied to a hydraulic multi-plate clutch that connects rotating elements that constitute a transmission, and a hydraulic multi-plate brake that fixes a rotating element that constitutes a transmission to be non-rotatable.

  As described above, in the lockup clutch 8 included in the starting device 1 of the above embodiment, the snap ring 90 regulates the movement of the flange member 85 that defines the engagement side oil chamber 86 together with the lockup piston 80. Thus, the radial expansion of the snap ring 90 can be satisfactorily suppressed. The correspondence between the main elements of the above embodiment and the main elements of the invention described in the column of means for solving the problem is described in the column of means for solving the problem by the embodiment. Since it is an example for concretely explaining the form for carrying out the invention, the element of the invention indicated in the column of the means for solving a subject is not limited. That is, the embodiment is merely a specific example of the invention described in the means for solving the problem, and the interpretation of the invention described in the means for solving the problem is It should be done based on the description.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and it goes without saying that various modifications can be made without departing from the scope of the present invention. Absent.

  The present invention can be used in the clutch manufacturing field and the like.

  DESCRIPTION OF SYMBOLS 1 Start device, 3 Front cover, 30 Centerpiece, 30a Oil path, 30b Oil path, 301 Large diameter cylindrical part, 302 Small diameter cylindrical part, 303 Recessed part, 304 Rotation restriction recessed part, 305 Snap ring groove, 306 Oil groove, 33 Cover Main body, 34 Side wall part, 34a Contact part, 35 Outer cylinder part, 36 Set block, 4 Pump impeller, 40 Pump shell, 41 Pump blade, 5 Turbine runner, 50 Turbine shell, 51 Turbine blade, 55 Rivet, 6 Stator, 60 Stator blade, 61 One-way clutch, 65 Thrust bearing, 7 Turbine hub, 71 Large-diameter alignment part, 72 Small-diameter alignment part, 73 Recessed part, 8 Lock-up clutch, 80 Lock-up piston, 80a Inner peripheral part, 80b Cylindrical part 80c pressing part, 81 Clutch hub, 81o opening, 82 clutch drum, 82a annular part, 82b fastening part, 82o opening, 83 first friction engagement plate, 84 second friction engagement plate, 85 flange member, 85a base end part, 85b outer peripheral part, 85c Piston movement restricting part, 850 Tip face, 851 End face, 854 Rotation restricting convex part, 855 Movement restricting part, 86 Engagement side oil chamber, 87 Return spring, 88 Oil path, 10 Damper mechanism, 11 Drive member, 11a Spring contact Contact portion, 11b Spring support portion, 12 First intermediate member, 12a Spring contact portion, 14 Second intermediate member, 141 First plate member, 141a, 141b Spring contact portion, 142 Second plate member, 142b Opening, 145 Rivet, 15 driven member, 15a spring contact part, 5b projections 90 snap ring 95 snap ring movement restricting member, SP11 first outer circumference spring, SP 12 second outer peripheral spring, SP2 inner peripheral springs.

Claims (7)

In the clutch that connects the two so that power is transmitted from the input member to the output member, and releases the connection between the input member and the output member,
A first friction engagement plate fitted to a clutch hub provided on the input member;
A second friction engagement plate fitted to a clutch drum provided on the output member;
A piston that moves in an axial direction and presses the first and second friction engagement plates;
An oil chamber defining member that is attached to the input member so as to rotate integrally with the input member and that defines an engagement side oil chamber to which hydraulic oil is supplied together with the piston;
A snap ring for restricting movement in the axial direction of the oil chamber defining member relative to the input member;
A snap ring movement restricting member that is supported by the oil chamber defining member so as to be located outside the snap ring and restricts movement of the snap ring in a radial direction;
A clutch comprising: The clutch according to claim 1, wherein
The input member has a concave portion that is recessed in the axial direction, and a cylindrical portion that surrounds the concave portion,
The base end portion of the oil chamber defining member is inserted into the concave portion of the input member,
The clutch, wherein the piston is supported by the cylindrical portion so as to be movable in the axial direction. The clutch according to claim 2,
The clutch, wherein the base end portion of the oil chamber defining member is inserted into the recess so that at least a part of a front end surface is in contact with the bottom surface of the recess. The clutch according to claim 2 or 3,
At least one rotation restricting recess is formed in the recess of the input member,
A clutch, wherein a rotation restricting convex portion that engages with the rotation restricting concave portion of the input member is formed at the base end portion of the oil chamber defining member. In the clutch according to any one of claims 1 to 4,
The oil chamber defining member has a movement restricting portion that restricts movement of the snap ring movement restricting member in the axial direction. In the clutch according to any one of claims 1 to 5,
The clutch, wherein the first and second friction engagement plates are disposed outside the engagement side oil chamber. The clutch according to any one of claims 1 to 6,
The input member is connected to a prime mover, the output member is connected to an input shaft of a transmission, and a lock that selectively executes lockup and release of the lockup for connecting the input member and the output member. A clutch configured as an up clutch.