JP6173814B2 - clutch - Google Patents

Description

  The present invention relates to a clutch that is disposed inside an input member to which hydraulic oil is supplied, and that connects both of the input member and the output member so that power is transmitted from the input member to the output member.

  Conventionally, as this type of clutch, a first friction engagement plate fitted to a clutch hub fixed to a front cover (input member), and a clutch drum connected to a turbine hub (output member) via a damper mechanism A second frictional engagement plate fitted to the piston, a piston that moves in the axial direction and presses the first and second frictional engagement plates, and a turbine hub and a damper mechanism connected to the turbine hub and the piston. There is known a lockup clutch including a flange member (oil chamber defining member) that defines an engagement side oil chamber to which hydraulic oil is supplied together with the piston (see, for example, Patent Document 1). In this lockup clutch, the base portion (inner peripheral portion) of the flange member is inserted into the overlapping portion (concave portion) of the first cylindrical portion and the second cylindrical portion formed in the center piece constituting the front cover, and the snap ring Is fixed in the axial direction with respect to the center piece. In addition, hydraulic oil is supplied to the inside of the front cover through an oil passage defined between the front cover and the piston and inside the first and second friction engagement plates. Is filled with hydraulic fluid.

JP 2013-096558 A

  When releasing the lock-up clutch as described above, there is a difference in rotational speed between the piston or flange member on the front cover side that is the input member and the turbine hub or damper mechanism that is the output member. And the centrifugal hydraulic pressure generated between the flange member and the turbine hub or the like. For this reason, when the lockup clutch is released, particularly on the inner peripheral side of the lockup clutch, there is a difference between the hydraulic pressure between the front cover and the piston (internal pressure) and the hydraulic pressure between the flange member and the turbine hub (internal pressure). As a result of this, an unexpected operation may occur in the lockup clutch.

  Therefore, the main object of the present invention is to keep the clutch in an appropriate state even when there is a difference between the hydraulic pressure between the input member and the piston and the hydraulic pressure between the oil chamber defining member and the output member when the clutch is released. And

The clutch according to the present invention comprises:
In a clutch that is arranged inside an input member to which hydraulic oil is supplied and connects both the input member and the output member so that power is transmitted from the input member to the output member,
A first friction engagement plate fitted to a clutch hub fixed to the input member;
A second friction engagement plate fitted to a clutch drum connected to the output member;
A piston that is supported by the center piece of the input member and moves in the axial direction to press the first and second friction engagement plates toward the side wall portion of the input member extending in the radial direction from the center piece; ,
An oil chamber defining member that is disposed on the side opposite to the side wall portion with respect to the piston and that defines an engagement side oil chamber to which hydraulic oil is supplied together with the piston;
A return spring disposed between the input member and the piston and biasing the piston away from the first and second friction engagement plates;
Between the side wall portion and the piston and between the oil chamber defining member and the output member, hydraulic oil flows,
The center piece has a concave portion recessed in the axial direction and a cylindrical portion surrounding the concave portion,
An inner peripheral portion of the oil chamber defining member is inserted into the concave portion of the center piece and is fitted to the center piece in the concave portion so as to rotate integrally with the input member. The tip surface in the axial direction is in contact with the bottom surface of the recess.

  The clutch is disposed inside an input member to which hydraulic oil is supplied, and is fitted to a first friction engagement plate that is fitted to a clutch hub fixed to the input member, and a clutch drum that is connected to the output member. A second friction engagement plate that is supported by the center piece of the input member and moves in the axial direction to extend the first and second friction engagement plates radially from the center piece to the side wall portion of the input member And a return spring disposed between the side wall portion of the input member and the piston and biasing the piston away from the first and second friction engagement plates. Further, hydraulic oil flows between the side wall portion and the piston and between the oil chamber defining member and the output member.

  When the clutch configured as described above is released, a rotational speed difference is generated between the output member and the piston or oil chamber defining member on the input member side. There is a difference between the centrifugal hydraulic pressure that is generated and the centrifugal hydraulic pressure that is generated between the oil chamber defining member and the output member. When the clutch is released and the rotational speed of the input member or the like is higher than the rotational speed of the output member, the centrifugal hydraulic pressure generated between the input member and the piston is increased between the oil chamber defining member and the output member. The hydraulic pressure (internal pressure) between the input member and the piston is increased between the oil chamber defining member and the output member, particularly on the inner peripheral side of the clutch. ). For this reason, when the rotational speed of the input member or the like is higher than the rotational speed of the output member when the clutch is released, the force for moving the oil chamber defining member toward the input member (side wall portion) By acting on the component member, the oil chamber defining member moves to the piston side against the biasing force of the return spring, whereby the first and second friction engagement plates are pressed toward the side wall portion by the piston. There is a risk.

  Based on this, the center piece of the input member is provided with a concave portion that is recessed in the axial direction and a cylindrical portion that surrounds the concave portion, and the inner peripheral portion of the oil chamber defining member is within the concave portion of the input member. The center piece is fitted in the recess so as to be inserted and rotate integrally with the input member. And the front end surface in the axial direction of the inner peripheral part of the oil chamber defining member comes into contact with the bottom surface of the recess. Thus, if the front end surface of the inner peripheral portion of the oil chamber defining member is brought into contact with the bottom surface of the recess of the input member, the oil chamber defining member cannot move toward the input member. Thereby, even if the force which moves the oil chamber defining member to the input member side when the clutch is released acts on the oil chamber defining member, the first and second friction engagement plates are pressed by the piston. Can be suppressed, and the clutch can be kept in an appropriate state.

  Further, in this clutch, the rigidity of the return spring is increased so that the piston does not move when the force to move the oil chamber defining member to the input member side when the clutch is released acts on the oil chamber defining member. Since there is no need, it is possible to suppress an increase in hydraulic pressure for engaging the clutch. Further, the inner peripheral portion of the oil chamber defining member is fitted into the center piece in the recess so as to rotate integrally with the input member, and the tip surface of the inner peripheral portion is brought into contact with the bottom surface of the recess so that the input is performed. Compared to the case where the engaging portion between the member and the oil chamber defining member and the contact portion between the input member and the oil chamber defining member are separated, the clutch is made compact and the structure is simplified. It becomes possible to do.

  Further, at least one rotation restricting recess may be formed in the recess of the center piece, and the inner peripheral portion of the oil chamber defining member is engaged with the rotation restricting recess of the center piece. A rotation restricting convex portion may be formed. Thereby, it becomes possible to rotate both of the oil chamber defining member and the input member satisfactorily while simplifying the configuration for integrally rotating the oil chamber defining member and the input member.

  Further, the return spring may be disposed between the input member and the piston so as to surround the cylindrical portion of the center piece, and the input member is interposed between the input member and the piston. An oil passage may be defined for supplying the hydraulic oil to the inside of the engine. By adopting such a configuration, it is possible to suppress an increase in the dimension of the clutch in the axial direction.

  The first and second friction engagement plates may be disposed so as to surround 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.

  Further, the engagement-side oil chamber communicates between the bottom surface of the recess and the tip surface of the inner peripheral portion and between the inner peripheral surface of the cylindrical portion and the outer peripheral surface of the inner peripheral portion. An oil passage may be defined. As a result, it is possible to supply hydraulic oil to the engagement side oil chamber while reducing the size of the clutch.

  The clutch is supported by the oil chamber defining member so as to be positioned outside the snap ring and a snap ring that restricts movement of the oil chamber defining member in a direction away from the side wall portion. A snap ring movement restricting member that restricts movement of the snap ring in the radial direction may be further included. Thereby, even if the oil chamber defining member cannot move to the input member side (piston side) due to the contact between the bottom surface of the recess and the tip surface of the inner peripheral portion, the oil chamber defining member While the movement in the direction away from the input member is restricted by the snap ring, the snap ring movement restriction member can suppress the expansion of the snap ring in the radial direction.

  The input member may be coupled to a prime mover, and the output member may be coupled to the clutch drum via a damper mechanism and may be coupled to an input shaft of a transmission. It may be configured as a lockup clutch that selectively executes lockup for connecting the input member and the output member and release of the lockup.

It is sectional drawing which shows the starting apparatus provided with the clutch by this invention. It is an expanded sectional view of the starting apparatus shown in FIG. It is explanatory drawing for demonstrating the center piece of the front cover contained in the starting apparatus of FIG. It is explanatory drawing for demonstrating the support structure of the snap ring movement control member in the flange member contained in the starting apparatus of FIG. It is a top view which shows the damper mechanism contained in the starting apparatus of FIG.

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

  FIG. 1 is a sectional view showing a starting device 1 having a clutch according to the present invention, and FIG. 2 is an enlarged sectional view of the starting device 1. A starting device 1 shown in these drawings is mounted on a vehicle including an engine (internal combustion engine) as a prime mover (not shown), 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 multi-plate hydraulic lockup clutch 8 which is a clutch according to the present invention, and a turbine hub 7 And a damper mechanism 10.

  The front cover 3 includes a center piece 30 and a cover main 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 (left side in the figure).

  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 that are recessed in the axial direction and on the engine side (left side in the figure) are equally spaced ( In this embodiment, they are formed at intervals of 60 °. 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 A washer is arranged between the hub 7. Further, the cover main body 33 of the front cover 3 includes a side wall portion 34 extending in the radial direction from the center piece 30 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 lockup is selectively executed. As shown in FIGS. 1 and 2, the lockup clutch 8 is located in the front cover 3, more specifically, between the side wall portion 34 of the front cover 3 and the damper mechanism 10. 4 in the fluid transmission chamber defined by the four pump shells 40.

  As shown in the figure, the lockup clutch 8 is supported by the center piece 30 of the front cover 3 and moves in the axial direction so that the first and second friction engagement plates 83 and 84 are moved to the side wall portion 34 of the front cover 3. A lock-up piston 80 that presses toward the lock-up piston, an annular clutch hub 81 that is fixed to the side wall 34 of the front cover 3 (cover body 33) so as to face the lock-up piston 80, and a speed change via the damper mechanism 10 A clutch drum 82 connected to the input shaft IS of the machine, a plurality of first friction engagement plates 83 (separator plates) fitted to splines formed on the outer periphery of the clutch hub 81, and an inner periphery of the clutch drum 82 A plurality of second friction engagement plates (friction plates having friction materials on both sides) 84 fitted to the splines formed in The center piece 30 of the front cover 3 is located on the side opposite to the side wall portion 34 of the front cover 3 with respect to the close-up piston 80, that is, on the turbine hub 7 and damper mechanism 10 side relative to the lock-up piston 80. And an annular flange member (oil chamber defining member) 85 attached to the.

  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 (tubular 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 that extends in the axial direction on the opposite side of the front cover 3, and a radial direction from each end of the annular portion 82a. And a fastening portion 82b extending inward. Furthermore, in the present embodiment, 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 is also supported by the clutch hub 81. It has an annular abutting portion 34a (see FIG. 1) that abuts with one of the center portions (the center portion of the outer periphery and the inner periphery) of the mating plate 83 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 the cylindrical portion of the lockup piston 80 via a seal member such as an inner peripheral portion 85a fitted to the small diameter cylindrical portion 302 of the center piece 30 and 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 radially outward from the outer edge of the outer peripheral portion 85b on the lockup piston 80 side (perpendicular to the axial direction). And a piston movement restricting portion 85c having an annular surface extending in the direction in which it is made. The inner peripheral portion 85a of the flange member 85 has a rotation restricting convex portion 854 (see FIG. 2) 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. It is formed so as to protrude in the direction.

  As shown in FIG. 2, in the inner peripheral portion 85 a of the flange member 85, each rotation restricting convex portion 854 is fitted into the corresponding rotation restricting concave portion 304 of the center piece 30, and the front end surface 850 in the axial direction is the concave portion 303. It is inserted into the recess 303 so as to abut against the bottom surface 303b. That is, the inner peripheral portion 85 a of the flange member 85 is fitted in the small diameter cylindrical portion 302 so as to overlap with the large diameter cylindrical portion 301 when viewed from the radial direction in the concave portion 303, and is integrated with the center piece 30 in the concave portion 303. The center piece 30 is fitted so as to rotate. And the front end surface 805 of the inner peripheral part 85a contact | abuts the part in which the rotation control recessed part 304 is not formed among the bottom faces 303b of the recessed part 303. FIG. Thereby, the movement of the flange member 85 toward the front cover 3 and the lock-up piston 80 side (left side in the figure) is regulated by the bottom surface 303b of the recess 303, and the flange member 85 is located on the front cover 3 side, ie, the lock-up piston 80 side. Cannot move to.

  Further, as shown in FIG. 3, a snap ring groove 305 is formed in the small diameter cylindrical portion 302 of the center piece 30, and the snap ring groove 305 has an inner peripheral portion 85 a on the turbine runner 5 side (in the drawing). The snap ring 90 is attached so as to contact the flat end surface 851 on the right side). As a result, the movement of the flange member 85 in the direction away from the front cover 3 along the axial direction is restricted by the snap ring 90. The flange member 85 is fixed to the center piece 30 so as to rotate integrally with the front cover 3 by the inner peripheral portion 85a being sandwiched between the bottom surface 303b of the recess 303 and the snap ring 90.

  Furthermore, in the starting device 1, an annular flat plate-shaped snap ring movement restricting member 95 is disposed 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 inner peripheral 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 this embodiment, each movement restricting portion 855 is a portion surrounding the snap ring movement restricting member 95 of the inner peripheral portion 85a in a state where the snap ring movement restricting member 95 is in contact with the flat end surface 851 of the inner peripheral 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 fixed to the center piece 30 so as to rotate integrally with the front cover 3 as described above guides the movement of the lockup piston 80 in the axial direction by the outer peripheral portion 85b, and at the same time, An engagement side oil chamber 86 is defined together with the lockup piston 80 on the opposite side of the front cover 3 (side wall portion 34) and inside the first and second friction engagement plates 83 and 84. The engagement side oil chamber 86 is engaged with the lockup clutch 8 from a hydraulic control device (not shown) connected to an oil pump (not shown) driven by the engine (in order to be in a completely engaged state or a slip state). ) Hydraulic oil (lock-up pressure). The engagement side oil chamber 86 is an oil passage (not shown) formed in the input shaft IS of the transmission, or an oil passage 30a formed in the center piece 30 so as to open in the axial direction with respect to the engagement side oil chamber 86. An oil passage defined between the bottom surface 303b of the recess 303 and the front end surface 850 of the inner peripheral portion 85a of the flange member 85 and between the inner peripheral surface of the large diameter cylindrical portion 301 and the outer peripheral surface of the inner peripheral portion 85a. It connects with a hydraulic control apparatus via 306 (refer FIG. 2).

  In the present embodiment, the bottom surface 303b of the recess 303 is formed such that a portion corresponding to the rotation restricting recess 304 is recessed to the left (engine side) in FIG. A plurality of radial oil passages defined between the bottom surface of 304 and the front end surface 850 of the inner peripheral portion 85a of the flange member 85 are included. However, the bottom surface 303b of the recess 303 is formed flat, and a plurality of oil grooves (recesses) are formed in the front end surface 850 of the inner peripheral portion 85a of the flange member 85, whereby the radial oil passage of the oil passage 306 is configured. May be.

  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. And a plurality of return springs 87 are disposed between the inner peripheral portion 80a of the lock-up piston 80 so as to surround the large-diameter cylindrical portion 301. The front cover 3 and the lockup piston 80 define an oil passage (oil chamber) 88 inside the clutch hub 81, that is, the first and second friction engagement plates 83 and 84. The oil passage 88 is connected to the inside of the front cover 3, that is, the 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 from a hydraulic control device (not shown). Hydraulic fluid (for example, a circulating pressure obtained by adjusting the drain pressure accompanying the generation of the line pressure) is supplied.

  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. An opening 82o that connects the oil passage 88 side and the fluid transmission chamber is formed. Further, the second friction engagement plate 84 is formed so as to extend in the radial direction, for example, by arranging a plurality of friction materials at intervals in the circumferential direction, and hydraulic fluid (not shown) that allows the hydraulic fluid to flow therethrough. Has a passage. As a result, when the first and second friction engagement plates 83 and 84 are frictionally engaged with each other, the inner peripheral side and the outer periphery of the first and second friction engagement plates 83 and 84 via the hydraulic oil passage. Flow of hydraulic oil between the sides is allowed. Thus, the hydraulic oil supplied to the oil passage 88 is supplied to the fluid transmission chamber defined by the front cover 3 and the pump shell 40, that is, the first and second friction engagement plates 83 and 84, the pump impeller 4, and the turbine runner 5. The damper mechanism 10 and the like can be supplied, and the periphery of the lockup clutch 8 is filled with hydraulic oil.

  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.

  In the starting device 1 configured as described above, when the lock-up clutch 8 is released, the lock-up piston 80 and the flange member 85 on the front cover 3 side, the turbine hub 7 and the damper mechanism 10 coupled thereto are provided. Between the front cover 3 (side wall portion 34) and the lockup piston 80, the centrifugal hydraulic pressure generated in the oil passage 88, the flange member 85, the turbine hub 7 and the damper mechanism 10 There is a difference between the centrifugal oil pressure generated in the hydraulic oil inflow region 89. When the lockup clutch 8 is released and the rotational speed of the front cover 3 or the like is higher than the rotational speed of the turbine hub 7, the oil is generated in an oil path 88 between the front cover 3 and the lockup piston 80. Since the centrifugal oil pressure becomes larger than the centrifugal oil pressure generated in the hydraulic oil inflow region 89 between the flange member 85 and the turbine hub 7, the oil pressure (internal pressure) in the oil passage 88, particularly on the inner peripheral side of the lockup clutch 8. Becomes lower than the hydraulic pressure (internal pressure) in the hydraulic oil inflow region 89.

  For this reason, if the rotational speed of the front cover 3 or the like is higher than the rotational speed of the turbine hub 7 when the lockup clutch 8 is released, the force for moving the flange member 85 toward the front cover 3 is affected by the flange member 85. As a result, the flange member 85 moves the lock-up piston 80 toward the front cover 3 against the urging force of the return spring 87, whereby the first and second friction engagement plates 83 and 84 are locked. The up piston 80 may be pressed toward the side wall part 34 (contact part 34a). Based on this, the center piece 30 that constitutes the front cover 3 of the starting device 1 is formed with the concave portion 303 that is recessed in the axial direction and the large-diameter cylindrical portion 301 that surrounds the concave portion 303 as described above. An inner peripheral portion 85 a of the flange member 85 is inserted into the recess 303 of the front cover 3 and is fitted to the center piece 30 in the recess 303 so as to rotate integrally with the front cover 3. Then, the front end surface 850 in the axial direction of the inner peripheral portion 85 a of the flange member 85 comes into contact with the bottom surface 303 b of the recess 303.

  Thus, if the front end surface 850 of the inner peripheral portion 85a of the flange member 85 is brought into contact with the bottom surface 303b of the recess 303 of the front cover 3, the flange member 85 cannot move toward the front cover 3. . Thus, even when a force that moves the flange member 85 toward the front cover 3 when the lockup clutch 8 is released acts on the flange member 85, the flange member 85 and the lockup piston 80 are directed toward the front cover 3. Thus, it is possible to prevent the first and second friction engagement plates 83 and 84 from being pressed and to keep the lockup clutch 8 in an appropriate state. Further, in the lockup clutch 8, the return spring 87 is arranged so that the lockup piston 80 does not move when a force that moves the flange member 85 toward the front cover 3 acts on the flange member 85 when the lockup clutch 8 is released. There is no need to increase rigidity. Thereby, it is possible to suppress an increase in hydraulic pressure to be supplied to the engagement side oil chamber 86 when the lockup clutch 8 is engaged.

  Further, the rotation restricting recess 304 of the center piece 30 and the rotation restricting protrusion 854 of the inner peripheral portion 85a are engaged so that the flange member 85 rotates integrally with the front cover 3 in the recess 303 of the front cover 3. By bringing the front end surface 850 of the inner peripheral portion 85a into contact with the bottom surface 303b of the recess 303, the engagement portion between the front cover 3 and the flange member 85 and the contact portion between the front cover 3 and the flange member 85 are separated. Compared to the case, the lock-up clutch 8 can be made compact while simplifying its structure. A plurality of rotation restricting recesses 304 are formed in the recess 303 of the center piece 30, and a plurality of rotation restricting protrusions 854 that engage with the rotation restricting recesses 304 are formed in the inner peripheral portion 85 a of the flange member 85. It is possible to reliably rotate both the member 85 and the front cover 3 while simplifying the configuration for rotating the member 85 and the front cover 3 integrally.

  Further, the lock-up piston 80 of the lock-up clutch 8 is supported by the large-diameter cylindrical portion 301 of the center piece 30 so as to be movable in the axial direction, and near the joint between the center piece 30 and the cover main body 33 and the lock-up piston 80. A plurality of return springs 87 are disposed between the inner peripheral portion 80a and the large-diameter cylindrical portion 301 so as to surround it. 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 lockup clutch 8, since the inner peripheral portion 85 a of the flange member 85 is located on the inner side of the lockup piston 80, the inertia at the time of rotation of the flange member 85 is increased compared to the lockup piston 80. Become. However, since the flange member 85 rotates integrally with the front cover 3, even if the inertia during rotation of the flange member 85 increases, the contact portion between the flange member 85 and the large-diameter cylindrical portion 301 of the center piece 30 or both There is no adverse effect on the sealing member (O-ring) disposed between them.

  Further, in the lock-up clutch 8, the first and second friction engagement plates 83 and 84 are disposed so as to surround the engagement-side oil chamber 86, so that the increase in the dimension of the lock-up clutch 8 in the axial direction is improved. Can be suppressed. In addition, in the lockup clutch 8, the gap between the bottom surface 303b of the recess 303 and the front end surface 850 of the inner peripheral portion 85a of the flange member 85, and the inner peripheral surface of the large-diameter cylindrical portion 301 and the outer peripheral surface of the inner peripheral portion 85a. An oil passage 306 communicating with the engagement side oil chamber 86 is defined therebetween. As a result, the hydraulic oil can be supplied to the engagement side oil chamber 86 while downsizing the lockup clutch 8.

  In the lockup clutch 8, the movement of the flange member 85 in the direction away from the front cover 3 is restricted by the snap ring 90, and the snap ring movement that restricts the movement of the snap ring 90 in the radial direction is restricted to the flange member 85. The restriction member 95 is mounted so as to be positioned outside the snap ring 90. Thus, the flange member 85 cannot move to the front cover 3 side (lock-up piston 80 side) due to the contact between the bottom surface 303b of the concave portion 303 of the front cover 3 and the front end surface 850 of the inner peripheral portion 85a. However, while the movement of the flange member 85 in the direction away from the front cover 3 is restricted by the snap ring 90, the snap ring movement restriction member 95 can suppress the radial expansion of the snap ring 90. Become.

  As described above, the lockup clutch 8 included in the starting device 1 includes the first friction engagement plate 83 fitted to the clutch hub 81 fixed to the front cover 3 and the turbine hub via the damper mechanism 10. The first friction engagement plate 83 is supported by the center piece 30 of the front cover 3 and moves in the axial direction and is moved in the axial direction. , 84 are pressed toward the side wall portion 34 of the front cover 3, and the hydraulic oil is disposed with the lockup piston 80 on the opposite side of the side wall portion 34 of the front cover 3 with respect to the lockup piston 80. The flange member (oil chamber defining member) 85 that defines the engagement side oil chamber 86 to which the oil is supplied, the front cover 3 and the lock-up It is disposed between the piston 80 and a return spring 87 for biasing so as to separate the lockup piston 80 from the first and second frictional engaging plates 83, 84. The lockup clutch 8 is disposed inside the front cover 3 to which hydraulic oil is supplied, and includes an oil passage 88 between the front cover 3 (side wall portion 34) and the piston, a flange member 85, the turbine hub 7, and the like. The hydraulic oil flows into the hydraulic oil inflow region 89 between the two. Further, the center piece 30 constituting the front cover 3 is provided with a concave portion 303 that is recessed in the axial direction and a large-diameter cylindrical portion (tubular portion) 301 that surrounds the concave portion 303, and an inner peripheral portion of the flange member 85. The (inner peripheral portion) 85a is inserted into the recess 303 of the center piece 30 and is fitted to the center piece 30 in the recess 303 so as to rotate integrally with the front cover 3. The tip end surface 850 in the axial direction of the inner peripheral portion 85 a of the flange member 85 abuts on the bottom surface 303 b of the recess 303. Thus, even when a force that moves the flange member 85 toward the front cover 3 when the lockup clutch 8 is released acts on the flange member 85, the flange member 85 and the lockup piston 80 are directed toward the front cover 3. Thus, it is possible to prevent the first and second friction engagement plates 83 and 84 from being pressed and to keep the lockup clutch 8 in an appropriate state.

  In the lockup clutch 8, the flange member 85 defines an engagement side oil chamber 86 to which hydraulic oil is supplied together with the lockup piston 80, the clutch hub 81 is fixed to the front cover 3, and the lockup piston 80. Moves toward the front cover 3 and presses the first and second friction engagement plates 83, 84, and a return spring 87 is disposed between the front cover 3 and the lockup piston 80 so that the lockup piston 80 is moved. The clutch is urged away from the front cover 3, but the clutch according to the present invention is not limited to such a configuration. That is, the clutch according to the present invention includes a clutch hub fixed to an annular flange member, a piston that moves toward the flange member and presses the first and second friction engagement plates, and between the piston and the flange member. A return spring that biases the piston away from the flange member, and an engagement side oil chamber (operating oil inflow region) defined between the front cover as the input member and the piston. It may be included.

  In the above embodiment, the front cover 3 connected to the engine and the turbine hub 7 connected to the clutch drum 82 via the damper mechanism 10 and connected to the input shaft IS of the transmission are locked up. Although the present invention has been described as being applied to the lockup clutch 8 that selectively executes the release of the lockup, the application target of the present invention is not limited to this. That is, the present invention may be applied to a multi-plate hydraulic clutch that connects the rotating elements that constitute the transmission, and a multi-plate hydraulic brake that fixes the rotating elements that constitute the transmission to be non-rotatable.

  And this invention is not limited to the said embodiment at all, and it cannot be overemphasized that a various change can be made within the range of the extension of this invention. Furthermore, the mode for carrying out the invention described above is merely a specific embodiment of the invention described in the column for solving the problem, and is described in the column for means for solving the problem. It is not intended to limit the elements of the invention.

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

  DESCRIPTION OF SYMBOLS 1 Start apparatus, 3 Front cover, 30 Centerpiece, 30a Oil path, 30b Oil path, 301 Large diameter cylindrical part, 302 Small diameter cylindrical part, 303 Recessed part, 303b Bottom face, 304 Rotation restriction recessed part, 305 Snap ring groove, 306 Oil path 33 Cover 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 aligning part, 72 Small diameter aligning part, 73 Recessed part, 8 Lock-up clutch, 80 Lock-up piston, 80a Inner peripheral part, 80b cylindrical part, 80 Pressing portion, 81 clutch hub, 81o opening, 82 clutch drum, 82a annular portion, 82b fastening portion, 82o opening, 83 first friction engagement plate, 84 second friction engagement plate, 85 flange member, 85a inner peripheral portion, 85b Outer peripheral part, 85c Piston movement restricting part, 850 Tip end face, 851 End face, 854 Rotation restricting convex part, 855 Movement restricting part, 86 Engagement side oil chamber, 87 Return spring, 88 Oil path, 89 Hydraulic oil inflow area, 10 Damper mechanism, 11 drive member, 11a spring 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 rivets, 15 drills Bun member, 15a spring contact portion, 15b protrusion, 90 snap ring, 95 snap ring movement restricting member, SP11 first outer peripheral spring, SP12 second outer peripheral spring, SP2 inner peripheral spring.

Claims (6)

In a clutch that is arranged inside an input member to which hydraulic oil is supplied and connects both the input member and the output member so that power is transmitted from the input member to the output member,
A first friction engagement plate fitted to a clutch hub fixed to the input member;
A second friction engagement plate fitted to a clutch drum connected to the output member;
A piston that is supported by the center piece of the input member and moves in the axial direction to press the first and second friction engagement plates toward the side wall portion of the input member extending in the radial direction from the center piece; ,
An oil chamber defining member that is disposed on the side opposite to the side wall portion with respect to the piston and that defines an engagement side oil chamber to which hydraulic oil is supplied together with the piston;
A return spring disposed between the input member and the piston and biasing the piston away from the first and second friction engagement plates;
Between the side wall portion and the piston and between the oil chamber defining member and the output member, hydraulic oil flows,
The center piece has a concave portion recessed in the axial direction and a cylindrical portion surrounding the concave portion,
An inner peripheral portion of the oil chamber defining member is inserted into the concave portion of the center piece and is fitted to the center piece in the concave portion so as to rotate integrally with the input member. the distal end surface in the axial direction, and contact with the bottom surface of the recess,
At least one rotation restricting recess is formed in the recess of the center piece, and a rotation restricting protrusion that engages with the rotation restricting recess of the center piece is formed on the inner peripheral portion of the oil chamber defining member. clutch, wherein Rukoto part has been formed. The clutch according to claim 1 , wherein
The return spring is disposed between the input member and the piston so as to surround the cylindrical portion of the center piece,
A clutch characterized in that an oil passage for supplying the hydraulic oil into the input member is defined between the input member and the piston. The clutch according to claim 2 ,
The clutch, wherein the first and second friction engagement plates are disposed so as to surround the engagement side oil chamber. In the clutch according to any one of claims 1 to 3 ,
An oil passage that communicates with the engagement-side oil chamber between the bottom surface of the recess and the tip surface of the inner peripheral portion and between the inner peripheral surface of the cylindrical portion and the outer peripheral surface of the inner peripheral portion. A clutch characterized in that is defined. In the clutch according to any one of claims 1 to 4 ,
A snap ring for restricting movement of the oil chamber defining member in a direction away from the side wall portion;
A clutch further comprising a snap ring movement restricting member that is supported by the oil chamber defining member so as to be positioned outside the snap ring and restricts movement of the snap ring in a radial direction. In the clutch according to any one of claims 1 to 5 ,
The input member is connected to a prime mover, and the output member is connected to the clutch drum via a damper mechanism and to an input shaft of a transmission,
A clutch that is configured as a lockup clutch that selectively executes lockup for connecting the input member and the output member and release of the lockup.