JP2014101926A - Automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an automatic transmission in which a clutch drum of a second clutch disposed on the radially outer side is hardly deformed.SOLUTION: In an automatic transmission 1, a second clutch C-3 is disposed radially outer side of a first clutch C-4. A clutch drum 20 of the second clutch C-3 forms an oil passage leading to a hydraulic oil chamber 32 of the second clutch C-3 between a piston support part 22 and itself. In a space between an extending part 20b of the clutch drum 20 and a rising part 22a of the piston support part 22 where the oil passage leading to the hydraulic oil chamber 32 is formed, the extending part 20b and the rising part 22a are welded at a plurality of positions in the circumferential direction, whereby close contact parts 62 into which the oil does not enter are formed. A non-close contact part 63 communicating with the hydraulic oil chamber 32 is formed between the close contact parts 62, and the non-close contact part 63 serves as the oil passage leading to the hydraulic oil chamber 32.

Description

  The present invention relates to an automatic transmission that includes first and second clutches, and in which the second clutch is arranged on the outer diameter side of the first clutch so that the axial position of the first clutch overlaps.

  2. Description of the Related Art Conventionally, in an automatic transmission mounted on an automobile or the like, it has been proposed to make the automatic transmission compact in the axial direction by disposing two clutches in the radial direction and overlapping in the axial direction. ing.

  For example, the fourth clutch positioned on the inner diameter side is enclosed by the third clutch positioned on the outer diameter side, and the third and fourth clutches are configured in a two-story shape, thereby shortening in the axial direction. There is an automatic transmission (see Patent Document 1).

  Since the automatic transmission described in Patent Document 1 achieves shortening in the axial direction by making the third and fourth clutches into a two-story structure, the hydraulic oil chamber inevitably also has a configuration. It is formed on the outer diameter side, and oil is supplied to this hydraulic oil chamber through a gap formed between the bottom portion of the clutch drum of the third clutch and the flange portion.

JP 2008-232416 A

  In this way, the third clutch has a hydraulic servo composed of the hydraulic oil chamber and the gap between the bottom portion and the flange portion, which is formed long on the outer diameter side. Is relatively large, and a bending moment corresponding to the centrifugal hydraulic pressure is generated at the bottom of the clutch drum.

  For this reason, it is not desired to apply a force acting in the bending direction as much as possible to the bottom of the clutch drum of the third clutch, but the gap is provided between the bottom and the flange over the entire circumference. ing. If the entire circumference between the bottom portion and the flange portion is an oil passage to the hydraulic oil chamber in this way, the pressure receiving area formed at the bottom portion of the clutch drum is large by forming this oil passage (gap). Thus, there is a problem that the force in the bending direction generated at the bottom of the clutch drum of the third clutch is increased based on the hydraulic pressure of the piston in addition to the centrifugal hydraulic pressure.

  Accordingly, an object of the present invention is to provide an automatic transmission having a configuration in which the clutch drum of the second clutch on the outer diameter side is not easily deformed.

In the present invention, the first clutch (C-4) and the first clutch (C-4) are arranged on the outer diameter side so as to overlap with the first clutch (C-4) in the axial direction. In an automatic transmission (1) having two clutches (C-3),
The first clutch (C-4) includes a clutch drum (41) adjacent to the second clutch (C-3),
The second clutch (C-3)
From the support part (20a) for supporting the first clutch (C-4), the extension part (20b) extending from the support part (20a) toward the outer diameter direction, and the extension part (20b). A clutch drum (20) having a drum portion (20c) extending toward the first clutch side in the axial direction so as to contain the first clutch (C-4);
A hydraulic oil chamber (32) is formed between the second clutch (C-3) and the clutch drum (20), and a cancel oil chamber is provided on the first clutch side in the axial direction of the hydraulic oil chamber (32). A piston (21) forming (33);
From the support part (20a) between the extension part (20b) of the clutch drum (20) of the second clutch (C-3) and the clutch drum (41) of the first clutch (C-4). A rising portion (22a) extending toward the outer diameter direction, a parallel portion (22b) extending parallel to the axial direction on the outer diameter side of the rising portion (22a), and the parallel portion (22b) A piston support member (22) for supporting the piston (21),
The piston support member (22) is in axial contact with the extended portion (20b) of the clutch drum (20) of the second clutch (C-3) at the rising portion (22a). (20a) welded to the extended portion (20b) of the clutch drum (20) of the second clutch (C-3) at a plurality of locations in the circumferential direction,
The piston support member (22) and the clutch drum (20) of the second clutch (C-3) are welded so that oil does not enter between the rising portion (22a) and the extended portion (20b). Non-adhering portions that form an oil passage that extends from the inner diameter side toward the outer diameter side and communicates with the hydraulic oil chamber (32) between the plurality of close contact portions (62). A part (63) is formed.

Further, the clutch drum (20) of the second clutch (C-3) has an abutting surface (65) of the extending portion (20b) against which the rising portion (22a) of the piston support member (22) is abutted. It is preferable that a plurality of groove portions (63 ₁ ) are formed in the _first and second non-contact portions (63) are formed by the plurality of groove portions (63 ₁ ).

  Further, the clutch drum (41) of the first clutch (C-4) rises from the side opposite to the axial direction of the clutch drum (20) of the second clutch (C-2). It is abutted against the portion (20a) and laminated in the axial direction, and projects toward the piston support member (22) at a plurality of locations in the circumferential direction, and the cancel oil chamber ( It is preferable to have a convex part (67) that forms a space part (66) serving as an oil passage communicating with (33).

Further, the clutch drum (C-4) of the first clutch has a rising portion (22a) of the piston support member (22) from the opposite side in the axial direction to the clutch drum (20) of the second clutch (C-3). ) And are laminated in the axial direction,
The rising portion (22a) of the piston support member (22) includes a first convex portion (72) toward the clutch drum side of the axial second clutch and a second convex portion toward the clutch drum side of the axial first clutch. (73) and are bent so that they are alternately formed in the circumferential direction,
The surface of the first convex portion (72) on the clutch drum side of the second clutch in the axial direction comes into contact with the extended portion (20b) of the clutch drum (20) of the second clutch (C-3) and is welded. The contact portion (62) is formed, and a space portion (66) serving as an oil passage to the cancel oil chamber (33) is formed between the first clutch (C-4) and the clutch drum (41). Forming,
The second convex portion (73) has a clutch drum side surface of the first axial clutch in contact with the clutch drum (41) of the first clutch (C-4) and the second clutch (C-3). It is preferable to form the non-contact portion (63) between the extended portion (20b) of the clutch drum (20).

The clutch drums (41, 20) of the first and second clutches (C-4, C-3) are respectively the first convex portion (72) and the second convex portion of the piston support member (22). Convex portions (75, 76, 67, 70) projecting in the same direction as the first convex portion (72) and the second convex portion (73) are formed in the same phase in the circumferential direction as the portion (73). Is formed by bending alternately in the axial direction as
The clutch drum (41) of the first clutch (C-4), the piston support member (22), and the clutch drum (20) of the second clutch (C-3) It is preferable to be configured to contact.

  Further, the clutch drum (41) of the first clutch (C-4), the piston support member (22), and the clutch drum (20) of the second clutch (C-3) have protrusions having the same protruding direction. It is preferable to penetrate and weld integrally at the contact position (80) in contact.

The rising portion (22a) of the piston support portion (22) is such that the clutch drum (41) of the first clutch (C-4) is different from the clutch drum (20) of the second clutch (C-3). Abutting from the opposite side in the axial direction, the first and second clutches (C-4, C-3) are sandwiched between the clutch drums (41, 20) and stacked in the axial direction. The laminated portion sandwiched between the clutch drums (41, 20) of the second clutch (C-4, C-3) is formed in a flat plate shape,
The clutch drum (20) of the second clutch (C-3) is in contact with the laminated portion of the piston support member (22) to form the contact portion (62), and the piston support member (22) A space (63 ₂ ) is formed between the laminated portions and the non-adhered portion (63) is formed by bending alternately along one side and the other side in the axial direction along the circumferential direction.
The clutch drum (C-4) of the first clutch forms a space (66) between the piston support member (22) and the laminated portion to form an oil passage to the cancel oil chamber (33). At the same time, the circumferential contact position (80) between the clutch drum (20) of the second clutch (C-2) and the laminated portion of the piston support member (22) is the same along the circumferential direction. Formed by bending alternately on one side and the other side in the axial direction,
The clutch drum (41) of the first clutch (C-4), the piston support member (22), and the clutch drum (20) of the second clutch (C-3) are integrated at the contact position (80). It is preferred to be welded.

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for convenience for making an understanding of invention easy, and has no influence on the structure of a claim. It is not a thing.

  According to the first aspect of the present invention, the extended portion of the clutch drum of the second clutch and the rising portion of the piston support portion that constitute the oil passage to the hydraulic oil chamber of the second clutch are welded at a plurality of locations in the circumferential direction. In addition, an intimate part where oil does not enter is formed, and a non-contact part is formed between these intimate parts to provide an oil path to the hydraulic oil chamber. For this reason, even if an oil passage to the hydraulic oil chamber is formed between the extending portion of the clutch drum of the second clutch and the rising portion of the piston support member, the entire circumference in the circumferential direction does not become an oil passage. The pressure receiving area generated in the clutch drum of the second clutch can be reduced by an amount corresponding to the contact portion. Thereby, based on the hydraulic pressure of the piston generated in the clutch drum of the second clutch, the bending moment acting on the clutch drum can be reduced, and the clutch drum of the second clutch can be configured to be difficult to deform.

  According to the second aspect of the present invention, the non-contact portion is constituted by the oil passage formed in the extending portion of the clutch drum of the second clutch, and therefore the piston support portion is provided by the amount of the oil passage recessed toward the extending portion. The first clutch and the second clutch can be configured compactly in the axial direction. Further, since the oil passage to the hydraulic oil chamber is configured by the groove portion, the pipe resistance of the oil passage to the hydraulic oil chamber can be reduced.

  According to the invention which concerns on Claim 3, the convex part is formed in the part laminated | stacked with the standing | starting-up part of the piston support member of the clutch drum of a 1st clutch in an axial direction. For this reason, a space portion communicating with the cancel oil chamber can be formed between the clutch drum of the first clutch and the piston support portion by the convex portion, and the convex portion functions as a rib to be the first. The strength of the clutch drum of the clutch can be improved.

  According to the fourth aspect of the present invention, the rising portion of the piston support member includes the first convex portion toward the clutch drum of the second axial clutch, and the second convex portion toward the clutch drum of the first axial clutch. Are bent so as to be alternately formed in the circumferential direction. For this reason, while the said 1st convex part can form the oil path to a 3rd clutch cancellation oil chamber with the space part between the clutch drums of a 1st clutch, the 2nd convex part is 2nd An oil path to the hydraulic oil chamber of the third clutch can be formed by the space between the clutch drum and the clutch drum. Further, since the space portions as the oil passages to the hydraulic oil chamber and the cancel oil chamber are alternately formed in the circumferential direction, the third and fourth clutches can be arranged compactly in the axial direction. Furthermore, the said 1st and 2nd convex part exhibits the function as a rib, and can improve the intensity | strength of a piston support part.

  According to the invention of claim 5, the clutch drums of the first and second clutches are formed with convex portions protruding in the same direction and in the same circumferential direction as the first convex portion and the second convex portion of the piston support member. In this way, it is bent in the axial direction. For this reason, each said convex part functions also as a rib, and can improve the intensity | strength of the clutch drum of a 1st and 2nd clutch. In addition, the clutch drum of the first clutch, the piston support member, and the clutch drum of the second clutch are stacked in the axial direction so as to come into contact with each other with the same projecting direction, so they are arranged close to the axial direction. The first and second clutches can be configured compactly in the axial direction.

  According to the invention of claim 6, the circumferential phase of the contact position of the clutch drum of the first clutch, the piston support member and the clutch drum of the second clutch is aligned, and these members are welded integrally. The strength as a whole can be improved.

  According to the seventh aspect of the invention, the clutch drums of the first and second clutches are alternately bent in the axial direction, and the oil passage and the cancel oil to the hydraulic oil chamber of the third clutch are formed between the piston support portions. Forms an oil passage to the chamber. For this reason, the strength of the clutch drums of the first and second clutches can be improved by the rib effect. Moreover, since the clutch drum of the first clutch, the piston support member, and the clutch drum of the second clutch are penetrated and integrally welded, the strength of these members as a whole can be improved.

(A) Skeleton diagram of the automatic transmission according to the embodiment of the present invention, (b) Engagement table of the automatic transmission of FIG. 1 (a). (A) Sectional drawing which shows the 3rd and 4th clutch part of the automatic transmission which concerns on the 1st Embodiment of this invention, (b) The oil-path structure to the hydraulic-oil chamber and cancellation oil chamber of a 3rd clutch. FIG. Sectional drawing which shows the 3rd and 4th clutch part of the automatic transmission which concerns on the 2nd Embodiment of this invention. (A) Schematic diagram showing the balancer of the third clutch in FIG. 3, (b) Schematic diagram showing the oil path configuration to the hydraulic oil chamber and cancel oil chamber of the third clutch in FIG. (A) The schematic diagram which shows the oil-path structure to the hydraulic-oil chamber of the 3rd clutch and cancel oil chamber which concern on the 3rd Embodiment of this invention, (b) The 4th Embodiment which concerns on the 4th Embodiment of this invention. Schematic diagram showing the oil path configuration to the hydraulic oil chamber and the cancellation oil chamber of the three clutches, (c) Oil path configuration to the hydraulic oil chamber and the cancellation oil chamber of the third clutch according to the fifth embodiment of the present invention FIG.

  Hereinafter, an automatic transmission according to an embodiment of the present invention will be described with reference to the drawings. The automatic transmission according to the embodiment of the present invention is an automatic transmission that is suitable for being mounted on an FF (front engine / front drive) type engine (drive source) horizontally mounted vehicle, as shown in FIG. 2) The left and right directions in FIGS. 2 (a) and 3 correspond to the left and right directions in the actual vehicle mounting state. For convenience of explanation, the right side in the drawing, which is the engine side, is “front side”, The side is called “rear side”.

<First Embodiment>
<Schematic configuration of automatic transmission>
As shown in FIG. 1A, an FF type automatic transmission 1 includes a case 6 including a housing case and a transmission case, and an automatic that can be connected to an engine (not shown) on the front side of the case 6. An input member (front cover and center piece) 10 as the transmission 1 is provided. Further, the automatic transmission 1 is provided with a torque converter 2 having a lock-up clutch 2 a, and a transmission mechanism 3, a counter shaft part 4, and a differential part 5 are arranged in a transmission case 6.

  The torque converter 2 is disposed on an axis centering on the input shaft 7 of the transmission mechanism 3 that is coaxial with the output shaft of the engine. Further, the counter shaft portion 4 is disposed on a counter shaft 12 that is on an axis parallel to the input shaft 7, and the differential portion 5 has a left and right axle 15 on an axis parallel to the counter shaft 12. Is arranged.

  The transmission mechanism 3 includes a reduction planetary gear (hereinafter simply referred to as “planetary gear”) DP that decelerates the rotation of the input shaft 7 on the input shaft 7, and a planetary gear unit PU on the rear side thereof. .

  As shown in FIG. 1 (a), the planetary gear DP includes a first sun gear S1, a first carrier CR1, and a first ring gear R1, and the first carrier CR1 includes a first sun gear. This is a so-called double pinion planetary gear having a pinion P2 meshing with S1 and a pinion P1 meshing with the first ring gear R1 in mesh with each other.

  On the other hand, the planetary gear unit PU has a second sun gear S2, a third sun gear S3, a second carrier CR2, and a second ring gear R2 as four rotating elements, and the second carrier CR2 A so-called Ravigneaux type planetary gear having a long pinion P3 meshing with the third sun gear S3 and the second ring gear R2 and a short pinion P4 meshing with the second sun gear S2 and the long pinion P3. is there.

  The rotation of the first sun gear S1 of the planetary gear DP is fixed with respect to the case (mission case) 6. The carrier CR1 is connected to the input shaft 7 and is rotated in the same rotation as the rotation of the input shaft 7 (hereinafter referred to as “input rotation”), and the fourth clutch C-4 (the fourth clutch C-4). 1 clutch). Further, the first ring gear R1 is decelerated by the input rotation being decelerated by the fixed first sun gear S1 and the input first carrier CR1, and the first clutch C-1 And the third clutch C-3 (second clutch).

  The third sun gear S3 of the planetary gear unit PU is connected to the first brake B-1 and can be fixed to the case 6, and the fourth clutch C-4 and the third clutch. Connected to C-3, the input rotation of the first carrier CR1 via the fourth clutch C-4, the reduced rotation of the first ring gear R1 via the third clutch C-3, Each can be entered freely. Further, the second sun gear S2 is connected to the first clutch C-1, and the reduced rotation of the first ring gear R1 can be input.

  Further, the second carrier CR2 is connected to the second clutch C-2 to which the rotation of the input shaft 7 is input, and the input rotation can be input via the second clutch C-2. In addition, it is connected to the one-way clutch F-1 and the second brake B-2, and rotation in one direction with respect to the case 6 is restricted via the one-way clutch F-1, and the second The rotation can be fixed via the brake B-2. The second ring gear R2 is connected to a counter gear 8 that is rotatably supported by a center support member fixed to the mission case 6.

  The counter gear 8 meshes with a large-diameter gear 11 fixed on the counter shaft 12 of the counter shaft portion 4, and the counter shaft 12 has a small diameter formed on the outer peripheral surface. The gear 14 of the differential portion 5 is engaged with the gear 12a. The gear 14 is fixed to a differential gear 13 and is connected to the left and right axles 15 and 15 via the differential gear 13.

  The speed change mechanism 3 configured as described above includes the clutches C-1 to C-4, the brakes B-1 and B-2, and the one-way clutch F-1 shown in the skeleton of FIG. By engaging and disengaging as shown in the table, the first forward speed (1ST) to the eighth forward speed (8TH) and the first reverse speed (Rev1) to the second reverse speed (Rev2) are achieved and input. The rotation input to the shaft 7 is shifted at each shift speed and output to the drive wheels via the left and right axles 15 and 15.

<Configuration of third and fourth clutches>
Next, the configuration of the third clutch C-3 and the fourth clutch C-4 described above will be described with reference to FIG. As shown in FIG. 2 (a), the third and fourth clutches C-3 and C-4 are disposed in the front portion of the speed change mechanism 3, and the third clutch (second clutch) C- 3 is arranged on the outer diameter side of the fourth clutch (first clutch) C-4 so as to overlap the fourth clutch C-4 in the axial direction, and is configured in a two-story structure.

  More specifically, the third and fourth clutches C-3 and C-4 are configured such that the third clutch C-3 on the outer diameter side includes the fourth clutch C-4 on the inner diameter side. The third clutch C-3 includes a clutch drum 20, a piston 21, a balancer 22, a return spring 23, a clutch hub 25, and the like as components.

  The clutch drum 20 of the third clutch C-3 is rotatably arranged via a bearing 26 on a boss portion 6a that extends from the body of an oil pump (not shown) and is formed integrally with the case 6. It is a cylindrical member having a sleeve-like support portion 20a at the center. Specifically, the clutch drum 20 extends in the axial direction, is disposed on the boss portion 6a, and supports the fourth clutch C-4. The support drum 20 extends outward from the support portion 20a. An extending portion 20b extending toward the end, and a drum portion 20c extending from the extending portion 20b toward the fourth clutch in the axial direction so as to include the fourth clutch C-4. ing. Further, the clutch drum 20 of the third clutch C-3 is divided into two members in the middle portion of the extending portion 20b, and these two members are welded.

  The boss portion 6a is provided with a cylindrical portion 27 extending from the body of the oil pump and a stator shaft 29 disposed through the interior of the oil pump so as to support a stator (not shown) of the torque converter 2. And the input shaft 7 with respect to the boss portion 6a via the bush 30 on the inner peripheral side of the boss portion 6a (stator shaft 29). It is supported rotatably.

  The balancer 22 of the third clutch C-3 is provided between the extended portion 20b of the clutch drum 20 of the third clutch C-3 and the clutch drum 41 of the fourth clutch C-4. Has a rising portion 22a extending toward the outer diameter side, and a parallel portion 22b extending parallel to the axial direction on the outer diameter side of the rising portion 22a, and the parallel portion 22b supports the piston 21. It is a piston support member.

  The balancer 22 has a cancel plate portion 22c that extends further from the parallel portion 22b to the outer diameter side. The piston 21 supported by the parallel portion 22b forms the hydraulic oil chamber 32 of the third clutch C-3 with the clutch drum 20 of the third clutch C-3, and the hydraulic oil chamber 32. A cancel oil chamber 33 is formed with the cancel plate portion 22c of the balancer 22 on the first clutch side in the axial direction. For this reason, even if the centrifugal hydraulic pressure acts on the piston 21 from the hydraulic oil chamber 32, the centrifugal hydraulic pressure from the hydraulic oil chamber side is canceled by the centrifugal hydraulic pressure generated in the cancel oil chamber 33.

  Further, a return spring 23 that urges the piston 21 toward the hydraulic oil chamber of the third clutch C-3 is provided between the cancel plate portion 22c of the balancer 22 and the piston 21 of the third clutch C-3. The piston 21 is moved in the axial direction by the force relationship between the urging force of the return spring 23 and the hydraulic pressure supplied to the hydraulic oil chamber 32.

  The above-described third clutch C-3 is supplied with oil to the hydraulic oil chamber 32 and has a plurality of outer friction plates 36 that are spline-engaged with the drum portion 20c of the clutch drum 20, and a spline-engagement with the clutch hub 25. At the same time, the friction plate 39 composed of the outer friction plate 36 and the inner friction plates 37 arranged alternately in the axial direction is engaged by being pressed by the piston 21.

  On the other hand, the fourth clutch C-4 disposed on the inner diameter side includes a clutch drum 41, a piston 42, a cancel plate 43, a return spring 45, a clutch hub 46, and the like as its components.

  The clutch drum 41 of the fourth clutch C-4 is disposed inside the clutch drum 20 of the third clutch C-3, extends in the axial direction, and the clutch drum 20 of the third clutch C-3. A sleeve portion 41a fixed to the support portion 20a, an extension portion 41b extending from the sleeve portion 41a to the outer diameter side, and an axial direction extending from the extension portion 41b on the outer diameter side of the sleeve portion 41a. And a drum portion 41c.

  The piston 42 forms a hydraulic oil chamber 47 with the clutch drum 41, and forms a cancel oil chamber 49 with the cancel plate 43 on the opposite side of the hydraulic oil chamber 47 in the axial direction. ing. A return spring 45 is disposed between the piston 42 and the cancel plate 43 so as to urge the piston 42 toward the hydraulic oil chamber side of the fourth clutch C-4. In order to receive the urging force from the return spring 45, the snap ring 50 is prevented from coming off in the axial direction with respect to the support portion 20a of the clutch drum 20 of the third clutch C-3.

  Oil is supplied to the hydraulic oil chamber 47 of the fourth clutch C-4 via the support portion 20a of the clutch drum 20 of the third clutch C-3 and the oil passage 51 formed in the sleeve portion 41a. . The above-described fourth clutch C-4 is supplied with oil to the hydraulic oil chamber 47 and is spline-engaged with the plurality of outer friction plates 52 that are spline-engaged with the drum portion 41c of the clutch drum 41 and the clutch hub 46. At the same time, a friction plate 55 comprising the outer friction plate 52 and inner friction plates 53 arranged alternately in the axial direction is engaged by being pressed by the piston 42.

<Support structure of clutch drum>
Next, the above-described clutch drum support structure will be described in detail with reference to FIG. As shown in FIG. 2A, the clutch drum 20 of the third clutch C-3 includes an oil passage 35 formed in the support portion 20a, a space between the clutch drum 20 and the balancer 22, a hydraulic oil chamber. The hydraulic servo 56 of the third clutch C-3 configured by 32 and the like is formed together with the balancer 22 and the piston 21.

  For this reason, when centrifugal hydraulic pressure is generated in the hydraulic servo 56, the clutch drum 20 of the third clutch C-3 receives force from the piston 21 side toward the opposite side of the axial piston 21 by this centrifugal hydraulic pressure, A bending moment is generated in the clutch drum 20 with a connection portion 57 (hereinafter referred to as a root portion) 57 of the extended portion 20b with the support portion 20a as a fulcrum.

  In particular, the third and fourth clutches C-3 and C-4 have a two-story structure, and the hydraulic oil chamber 32 of the third clutch C-3 located on the outer diameter side is provided on the inner diameter side. The hydraulic servo 56 is also longer in the radial direction than the hydraulic oil chamber 47 of the fourth clutch C-4. Since the centrifugal hydraulic pressure increases according to the centrifugal force, naturally, the centrifugal hydraulic pressure acting on the clutch drum 20 increases as it extends to the outer diameter side, and the higher the rotational speed, the larger the clutch drum 20 of the third clutch C-3. Bending moment may occur.

  Therefore, in the present embodiment, in order to suppress the deformation of the clutch drum 20 as much as possible even if a large bending moment is generated in the clutch drum 20 of the third clutch C-3 as described above, Of the components of the fourth and third clutches arranged on the inner side of the clutch drum 20 of the clutch C-3, the member fixed to the support portion 20a and the outer diameter side of the support portion 20a. Connected by welding.

  Specifically, as shown in FIG. 2A, the balancer (piston support member) 22 has a base portion of a rising portion 22a with respect to the support portion 20a of the clutch drum 20 of the third clutch C-3. In addition to being fixed by welding, the rising portion 22a is abutted (contacted) with the extended portion 20b of the clutch drum 20 of the third clutch C-3 and stacked in the axial direction.

  In the balance drum 22 and the clutch drum 20 of the third clutch C-3, the rising portion 22a and the extending portion 20b stacked in the axial direction are welded by laser welding at a plurality of locations in the circumferential direction from the clutch drum 20 side. Yes. For this reason, the clutch drum 20 of the third clutch C-3 has a balancer positioned not only at the root portion 57 on the inner diameter side but also at the outer diameter side from the root portion 57 even if a bending moment is generated by centrifugal hydraulic pressure. The bending moment can be received by the welded portion 59 with the rising portion 22a of 22.

  Further, the clutch drum 41 of the fourth clutch C-4 is abutted against the balancer 22 from the side opposite to the clutch drum 20 of the third clutch in the axial direction. Specifically, the extended portion 41b of the clutch drum 41 of the fourth clutch C-4 is formed to be bent in accordance with the shape of the balancer 22, and the first portion facing the rising portion 22a of the balancer 22. The balancer 22 is in axial contact with the balancer 22 at two locations: the extension 41b1 and the second extension 41b2 that faces the cancel plate 22c of the balancer 22 in the axial direction.

  In the clutch drum 41 of the fourth clutch C-4, a sleeve portion (base portion) 41a is fixed to the support portion of the clutch drum of the second clutch by welding, and the outer diameter side of the sleeve portion 41a. The second extending portion 41b2 is connected to the balancer 22 by welding.

  That is, the clutch drum 41 of the fourth clutch C-4 is connected to the clutch drum 20 of the third clutch C-3 via the balancer 22 by welding on the outer diameter side from the support portion 20a. The strength of the third clutch C-3 against bending of the clutch drum 20 is increased. Further, since the clutch drum 41 of the fourth clutch C-4 is connected to the balancer 22 to increase its strength against bending, the deformation of the clutch drum 41 due to the centrifugal hydraulic pressure acting on the hydraulic oil chamber 47 can also be suppressed. .

  The welded portion 59 between the clutch drum 20 and the balancer 22 of the third clutch C-3 is positioned with the balancer 22 applied to the clutch drum 20 and welded to the support portion 20a by the welded portion 58. After being welded, it is desirable to be welded. Similarly, the welded portion 61 between the balancer 22 and the clutch drum 41 of the fourth clutch C-4 is positioned by the clutch drum 41 being abutted against the balancer 22 and welded to the support portion 20a by the welded portion 60. It is desirable to weld after being welded.

  Further, the welded portion 61 between the balancer 22 and the clutch drum 41 of the fourth clutch C-4 is welded from the clutch drum 41 side toward the balancer 22 side, and a third clutch C-3, which will be described later, is welded. In order to form an oil passage to the cancel oil chamber 33, the entire circumference is welded.

<Oil channel configuration>
Next, the configuration of the oil path to the hydraulic oil chamber and the cancel oil chamber of the third clutch will be described based on FIGS. 2 (a) and 2 (b). The hydraulic oil chamber 32 of the third clutch C-3 is filled with oil through the oil passage 35, the extended portion 20b of the clutch drum 20 of the third clutch C-3, and the rising portion 22a of the balancer 22. The extended portion 20b of the clutch drum 20 and the rising portion 22a of the balancer 22 are arranged at a plurality of locations in the circumferential direction in order to improve the strength of the clutch drum 20 as described above. Welded.

  Therefore, in the present embodiment, an oil passage that communicates with the hydraulic oil chamber 32 is formed between the circumferential directions of the welded portion 59 that is a welded portion between the extending portion 20b and the rising portion 22a. Specifically, the welded portion 59 is formed in an enclosure shape (a rectangular shape in the present embodiment) in which the welded portion surrounds a predetermined area, and is welded as shown in FIG. A close contact portion 62 where oil does not enter is formed between the rising portion 22a and the extending portion 20b.

  Further, unlike the above-described welded portion 61 between the balancer 22 and the clutch drum 41 of the fourth clutch C-4, a plurality of welded portions 59 are provided at intervals in the circumferential direction instead of the entire circumferential direction. . Therefore, a plurality of the close contact portions 62 are formed at intervals in the circumferential direction, and the clutch drum 20 and the balancer 22 are located between the plurality of close contact portions (welded portions) 62 from the inner diameter side to the outer diameter side. A non-contact portion that extends and communicates with the hydraulic oil chamber 32 is formed as an oil passage to the hydraulic oil chamber 32.

In particular, the non-adhesion portion is, in this embodiment, is formed by a plurality of grooves 63 ₁ formed in the abutment surface 65 of the extending portion 20b against which marked with the rising portion 22a of the balancer 22 , oil supplied through the oil passage 35, and is supplied to the hydraulic oil chamber 32 through the groove 63 ₁ provided in the circumferential direction a plurality of locations.

  On the other hand, the oil is supplied to the cancel oil chamber 33 of the third clutch C-3 through the space between the balancer 22 and the first extending portion 41b1 of the clutch drum 41 of the fourth clutch C-4. The balancer 22 and the first extending portion 41b1 of the clutch drum 41 are also laminated in the axial direction as described above.

  Therefore, the clutch drum 41 of the fourth clutch (first clutch) C-4 protrudes toward the balancer (piston support member) 22 at a plurality of locations in the circumferential direction of the first extending portion 41b, and the balancer 22 rises. A convex portion 67 that forms a space portion 66 communicating with the cancel oil chamber 33 is provided between the portion 22a and the portion 22a.

  More specifically, between the balancer 22 serving as an oil passage to the cancel oil chamber 33 and the clutch drum 41 of the fourth clutch C-4, a welded portion 61 whose radial position overlaps with the cancel oil chamber 33 is provided. It is welded over the entire circumference so as to be oil-tight, and communicates with the cancel oil chamber 33 by an oil passage 69 that is formed in the cancel plate portion 22c of the balancer 22 obliquely toward the outer diameter side in the axial direction. doing.

  The clutch drum 41 is bent at the first extending portion 41b so that convex portions 67 toward the balancer 22 and convex portions 70 toward the opposite side of the balancer are alternately formed. The convex portion 67 contacts the rising portion 22 a of the balancer 22, and the space portion 66 is formed between the convex portion 70. Furthermore, the balancer 22, the clutch drum 41 of the fourth clutch C-4, and the welded portion 61 are welded on the outer diameter side of the oil passage 69. Therefore, the oil supplied from the inner diameter side proceeds to the outer diameter side through the space portion 66 and is supplied from the side surface side to the cancel oil chamber 33 through the oil passage 69.

  By configuring the automatic transmission 1 as described above, the clutch drum 20 of the third clutch C-3 is configured of the third and fourth clutches C-3 and C-4 disposed inside thereof. Of the parts, the parts fixed to the support portion 20a of the clutch drum 20 of the third clutch C-3 are connected by welding, and the strength of the clutch drum 20 against bending moment can be improved.

  That is, in the present embodiment, since the clutch drum 20 of the third clutch C-3 is welded and connected to the balancer 22 by the welded portion 59, only the root portion 57 of the clutch drum 20 located on the inner diameter side. In addition, the clutch drum 20 can be supported by the welded portion 59 on the outer diameter side, and deformation of the clutch drum 20 due to a bending moment can be reduced. Further, the clutch drum 20 also improves the strength against the bending moment by forming the root portion 57 and the joint portion 31 thick.

  Further, the balancer 22 and the clutch drum 41 of the fourth clutch C-4 are welded by the welding portion 61, whereby the clutch drum 20 of the third clutch C-3 is connected to the fourth clutch via the balancer 22. It can also be supported by the C-4 clutch drum 41.

  Further, by welding the clutch drum 20 and the balancer 22 of the third clutch C-3 at a plurality of locations in the circumferential direction, between the rising portion 22a of the balancer 22 and the extending portion 20b of the clutch drum 20. A close contact portion 62 that does not allow oil to enter can be formed. Further, the non-contact portion 63 is formed between the plurality of close contact portions 62 to form an oil passage to the hydraulic oil chamber 32, thereby reducing the pressure receiving area of the clutch drum 20 generated by forming this oil passage. The bending moment acting on the clutch drum 20 can be reduced by the oil pressure in the oil passage.

  Furthermore, by forming the welded portion between the clutch drum 20 and the balancer 22 of the third clutch C-3 in a surrounding shape (bag shape) surrounding a predetermined area, the reduced pressure receiving area can be made larger.

Further, by providing the groove section 63 ₁ to the third clutch C-3 of the clutch drum 20, by forming the non-adhesion portion 63 of the oil passage that communicates with the hydraulic oil chamber 32, a plate-shaped clutch drum 20 Compared to the case where a clearance is provided between the balancer 22 and the oil passage, the clutch C-3 can be configured compactly in the axial direction, and the pipe resistance can be reduced. That is, like the automatic transmission described in Patent Document 1, the balance between the clutch drum 20 and the balancer of the third clutch C-3 is formed in order to form an oil passage to the hydraulic oil chamber 32 of the third clutch C-3. If the clutch 22 is disposed apart from the clutch drum 20 by a predetermined amount in the axial direction, the clutch drum 20 and the balancer 22 cannot be brought into contact with each other in the axial direction as in the automatic transmission according to the present embodiment. And the balancer 22 are elongated in the axial direction by the gap. Furthermore, since a gap is formed over the entire circumference in the circumferential direction between the clutch drum 20 and the balancer 22, the resistance to oil when passing between the clutch drum 20 and the balancer 22 is as in the present application. It becomes large with respect to what formed the groove | channel. In the present embodiment, the clutch drum 20 of the third clutch C-3 includes the clutch drum 20, the balancer 22, and the clutch drum 41 of the fourth clutch that are stacked in the axial direction. among the most thickness is formed thick, it is possible to form the groove 63 ₁ without reducing the rigidity of the clutch drum 20.

  Further, the first extending portions 41b1 of the clutch drum 41 of the fourth clutch C-4 are alternately bent in the axial direction, and the convex portions 67, 70 are used to configure the space portion 66, so that these convex portions 67, 70 becomes a rib and the strength of the clutch drum 41 can be improved.

  In addition, since the cancel plate portion 22c that forms the cancel oil chamber 33 of the third clutch C-3 is formed integrally with the balancer 22, assembly of the clutch can be facilitated. Further, since the balancer 22 is welded to the support portion 20a of the clutch drum 20 of the third clutch C-3, the urging force of the return springs 23 and 45 of the third and fourth clutches C-3 and C-4. In the configuration in which the third and fourth clutches C-3 and C-4 are disposed adjacent to each other, the spring force of each return spring 23 and 45 can be freely set.

  Further, by forming an oil passage 69 drilled in the axial direction in the cancel plate portion 22c of the balancer 22, the space between the balancer 22 and the clutch drum 41 of the fourth clutch C-4 and the third Since the cancel oil chamber 33 of the clutch C-3 is communicated, it is not necessary to form an oil passage for supplying oil to the cancel oil chamber 33 in the parallel portion 22b that supports the piston 21, and the movement range of the piston 21 is reduced. It can be secured widely, and the oil passage to the cancel oil chamber does not hinder the movement of the piston 21.

<Second Embodiment>
Next, a second embodiment according to the present invention will be described. The automatic transmission according to the second embodiment is different from the automatic transmission according to the first embodiment only in the oil path configuration to the hydraulic oil chamber and the cancel oil chamber of the third clutch. Therefore, in the following description, only parts different from the first embodiment will be described, and descriptions of other parts will be omitted.

  As shown in FIGS. 3 and 4, in the automatic transmission 1, the rising portion 22 a of the balancer 22 includes a first convex portion 72 toward the clutch drum of the third axial clutch (second clutch) C-3. The second convex portions 73 to the clutch drum side of the fourth clutch (first clutch) C-4 in the axial direction are bent so as to be alternately formed in the circumferential direction.

  Further, the extension portion 20b of the clutch drum 20 of the third clutch C-3 and the extension portion 41b of the clutch drum 41 of the fourth clutch C-4 that are stacked in the axial direction together with the rising portion 22a of the balancer 22 are provided. The laminated portions are each formed in a flat plate shape. For this reason, the first convex portion 72 of the balancer 22 is in contact with the extending portion 20b of the clutch drum 20 of the third clutch C-3 at the surface on the clutch drum side of the third clutch C-3 in the axial direction. A welded portion 62 is formed by welding, and a space 66 is formed between the extended portion 41b of the clutch drum 41 of the fourth clutch C-4 and an oil passage to the cancel oil chamber 33 is formed. Yes.

On the other hand, the second convex portion 73 of the balancer 22 is such that the surface on the clutch drum side of the fourth clutch C-4 in the axial direction is in contact with the first extending portion 41b1 of the clutch drum 41 of the fourth clutch C-4. , to form a non-adhesion portion 63 to form a space (non-contact portion) 63 ₂ between the extending portion 20b of the third clutch C-3 of the clutch drum 20.

Therefore, to form a space portion 63 ₂ which is a oil passage to the third clutch C-3 of the hydraulic oil chamber 32, and a space 66 serving as the oil passage to the cancel oil chamber 33, alternately in the circumferential direction The clutch drum 20 of the third clutch C-3, the balancer 22, and the clutch drum 41 of the fourth clutch C-4 can be compactly stacked in the axial direction. In particular, as in the automatic transmission described in Patent Document 1, the oil path to the hydraulic oil chamber 32 and the cancel oil chamber 33 of the third clutch C-3 is connected to the clutch drum 20 and the balancer of the third clutch C-3. The axial length can be shortened more effectively than that formed by disposing the clutch drum 41 of the 22nd and the fourth clutch C-4 apart from each other by a predetermined amount in the axial direction. That is, in the automatic transmission described in Patent Document 1, a gap between the clutch drum 20 and the balancer 22 is used as an oil passage to the hydraulic oil chamber 32, and a gap between the balancer 22 and the clutch drum 41 is set as a cancel oil chamber. As an oil route to. For this reason, in the automatic transmission described in Patent Document 1, a gap between members communicating with the hydraulic oil chamber 32 and the cancel oil chamber 33 is simply arranged in parallel in the axial direction with the balancer 22 interposed therebetween. This is a configuration that is longer in the axial direction. On the other hand, the automatic transmission 1 according to the present embodiment, the space portion 63 ₂ which is a oil passage balancer 22 axially bent alternately to the third clutch C-3 of the hydraulic oil chamber 32, cancel Space portions 66 serving as oil passages to the oil chamber 33 are alternately arranged in the circumferential direction, and these space portions 63 ₂ and 66 are arranged close to the axial direction. Accordingly, constitute close the space 66 of the oil passage to the space portion 63 ₂ and the cancel oil chamber 33 of the oil path to these working oil chamber 32 in the axial direction, the configuration of the clutch C-3, C-4 Can be shortened in the axial direction.

  Furthermore, by bending the balancer 22 alternately, the first and second convex portions 72 and 73 become ribs, and the rigidity of the balancer 22 can be improved.

<Third Embodiment>
Next, a third embodiment according to the present invention will be described. The automatic transmission according to the third embodiment is different from the automatic transmission according to the second embodiment in the configurations of the clutch drum and the balancer of the fourth clutch. Therefore, in the following description, only the part different from the second embodiment will be described, and the description of the other part will be omitted.

  As shown in FIG. 5A, the automatic transmission 1 is similar to the balancer 22 in that the extended portion 20b of the clutch drum 20 of the third clutch C-3 and the clutch drum 41 of the fourth clutch C-4. The first extending portion 41b1 is also bent and formed.

  Specifically, the clutch drums 20 and 41 of the third and fourth clutches C-3 and C-4 are respectively provided with an extending portion 20b and a first extending portion 41b1 that are stacked together with the balancer 22. It is formed by being alternately bent along the circumferential direction in the protruding direction of the first convex portion 72 and the protruding direction of the second convex portion 73. That is, the clutch drums 20 and 41 of the third and fourth clutches C-3 and C-4 are in the same phase in the circumferential direction as the first convex portion 72 and the second convex portion 73 of the balancer 22, respectively. It is formed by bending alternately in the axial direction so as to form protrusions 75, 76, 67, 70 protruding in the same direction as the protrusion direction of the protrusion 72 and the second protrusion 73.

  Then, the clutch drum 20 of the third clutch C-3, the balancer 22 and the clutch drum 41 of the fourth clutch C-4 have the projections 76, 72, 67, 72, 75, 73 having the same protruding direction. , 73 and 70 are laminated in the axial direction so as to contact each other.

  Thus, the convex portions 76, 72, 67, 75 are formed on all of the clutch drum 20, the balancer 22, and the clutch drum 41 of the fourth clutch C-4 that constitute the oil passages 63, 66. , 73 and 70 are alternately formed, so that these convex portions become ribs and the strength of each member can be improved.

  Further, the clutch drum 20 of the third clutch C-3, the balancer 22 and the clutch drum 41 of the fourth clutch C-4 have projections 76, 72, 67, 72, 75, 73, 73 having the same protruding direction. , 70. For this reason, the protruding side of the other convex portion overlaps the concave side of the one convex portion to be laminated, and the clutch drum 20, the balancer 22 and the fourth clutch C-4 of the third clutch C-3. The clutch drum 41 can be stacked compactly in the axial direction.

<Fourth embodiment>
Next, a fourth embodiment according to the present invention will be described. The automatic transmission according to the fourth embodiment is different from the automatic transmission according to the third embodiment in the welding configuration between members. Therefore, in the following description, only parts different from the third embodiment will be described, and description of other parts will be omitted.

  As shown in FIG. 5B, the contact position 80 in the circumferential direction of the clutch drum 20 of the third clutch C-3, the balancer 22, and the clutch drum 41 of the fourth clutch C-4 are in the same phase. The clutch drum 20 of the third clutch C-3, the balancer 22 and the clutch drum 41 of the fourth clutch C-4 penetrate at the contact position 80 and are integrally welded. . That is, the abutting position 80 is constituted by abutting portions of protrusions having the same protruding direction. At the abutting position 80, the clutch drum 20, the balancer 22 and the fourth clutch of the third clutch C-3. The clutch drum 41 of C-4 is welded through.

  In this way, convex portions are formed on all of the clutch drum 20, the balancer 22 of the third clutch C-3, and the clutch drum 41 of the fourth clutch C-4, and these members are integrally connected by through welding. By doing so, the rigidity of the entire welded member can be improved.

<Fifth embodiment>
Next, a third embodiment according to the present invention will be described. The automatic transmission according to the third embodiment is different from the automatic transmission according to the fourth embodiment in the configuration of the balancer. Therefore, in the following description, only parts different from the fourth embodiment will be described, and description of other parts will be omitted.

  As shown in FIG. 5C, the rising portion 22a of the balancer 22 is stacked in the axial direction so as to be sandwiched between the clutch drums 20 and 41 of the third and fourth clutches C-3 and C-4. The laminated portion sandwiched between the clutch drums 20 and 41 of the third and fourth clutches C-3 and C-4 is formed in a flat plate shape.

The extended portion 20b of the third clutch C-3 of the clutch drum 20, to form a contact portion 62 laminated portion and abuts against the balancer 22, the space portion 63 ₂ between the laminated portion of the balancer 22 In order to form the non-contact portion 63, it is formed by being alternately bent along the circumferential direction on one side and the other side in the axial direction.

  Further, the clutch drum 41 of the fourth clutch C-4 forms a space 66 with the laminated portion of the balancer 22 to form an oil passage to the cancel oil chamber 33, and the third clutch C- The three clutch drums 20 and the laminated portion of the balancer 22 are alternately bent along the circumferential direction so that the contact positions 80 in the circumferential direction are the same. The clutch drum 20 of the third clutch C-3, the balancer 22, and the clutch drum 41 of the fourth clutch C-4 are integrally welded at the contact position 80.

  Thus, among the clutch drum 20, the balancer 22 of the third clutch C-3, and the clutch drum 41 of the fourth clutch C-4, the balancer 22 having the thinnest plate thickness is not bent and is laminated. Is also welded by integrally connecting the balancer 22 and the clutch drums 20 and 41 of the third and fourth clutches C-3 and C-4, which are bent alternately, by through welding. Further, the rigidity of the entire member can be improved.

  In the above-described embodiment, the description has been given by taking the FF type automatic transmission of the eighth forward speed and the second reverse speed as an example. However, the present invention is not limited to this, and the automatic transmission in which two clutches are arranged adjacent to each other. The present invention can be applied to any automatic transmission. In addition, the automatic transmission is not limited to an engine using a drive source, but a transmission mechanism using an engine and a motor as a drive source, a transmission mechanism using a motor as a drive source, and the like are also part of the automatic transmission of the present invention. is there.

  Further, in the above-described embodiment, the clutch drum 20 of the third clutch C-3 is divided into two at the extending portion 20b. However, this division position may be anywhere, and the clutch drum 20 as an integral part. May be formed. In addition, if possible, the moment force applied to the joint portion between the members can be reduced by disposing the dividing position on the outer diameter side as much as possible as in the present embodiment.

  Further, the shape of the welded portion 59 described above is not necessarily a rectangular shape as long as it is a surrounding shape surrounding a predetermined area, and may be a polygonal shape of a triangle or more or a circular shape. Further, since oil does not enter the portion surrounded by the welded portion 59 as the close contact portion, the surrounding portion of the clutch drum 20 may be thinned and lightened. The automatic transmission 1 supports the piston 21 of the third clutch C-3 by the clutch drum 41 of the fourth clutch C-4, does not provide the balancer 22, and The clutch drum 41 and the clutch drum 20 of the third clutch C-3 may be directly connected by welding at the extended portion. Furthermore, the inventions described in the above embodiments may be combined in any way.

DESCRIPTION OF SYMBOLS 1: Automatic transmission, 20: Clutch drum, 20a: Support part, 20b: Extension part, 21: Piston, 22: Piston support member (balancer), 22a: Stand-up part, 22b: Parallel part, 22c: Cancel plate part 32: Hydraulic oil chamber, 33: Cancel oil chamber, 41: Clutch drum, 41a: Base, 42: Piston, 47: Hydraulic oil chamber, 62: Close contact portion, 63: Non-contact portion, 63 ₁ : Groove portion, 63 ₂ : Space part, 67: convex part, 72: first convex part, 73: second convex part, 80: contact position, C-3: second clutch (third clutch), C-4: first clutch (4th clutch)

Claims (7)

In an automatic transmission comprising a first clutch and a second clutch arranged so that an axial position thereof overlaps with the first clutch on the outer diameter side of the first clutch,
The first clutch includes a clutch drum adjacent to the second clutch,
The second clutch is
A support portion that supports the first clutch, an extension portion that extends from the support portion toward an outer diameter direction, and toward the first clutch side in the axial direction so as to include the first clutch from the extension portion. A clutch drum having a drum portion extended in an extended manner;
A piston that forms a hydraulic oil chamber with the clutch drum of the second clutch, and that forms a cancel oil chamber on the first clutch side in the axial direction of the hydraulic oil chamber;
A rising portion extending in an outer diameter direction from the support portion between the extending portion of the clutch drum of the second clutch and the clutch drum of the first clutch, on the outer diameter side of the rising portion A piston support member having a parallel portion extending parallel to the axial direction and supporting the piston at the parallel portion;
The piston support member is in axial contact with the extending portion of the clutch drum of the second clutch at the rising portion, and the extending portion of the clutch drum of the second clutch at a plurality of circumferential positions of the rising portion. And welded with
The piston support member and the clutch drum of the second clutch are welded to form a plurality of contact portions where oil does not enter between the rising portion and the extending portion, and an inner diameter between the plurality of contact portions. Forming a non-contact portion that extends from the side toward the outer diameter side and serves as an oil passage communicating with the hydraulic oil chamber;
An automatic transmission characterized by that. The clutch drum of the second clutch has a plurality of groove portions formed on the abutting surface of the extending portion against which the rising portion of the piston support member is abutted, and the non-contact portion is formed by the plurality of groove portions.
The automatic transmission according to claim 1. The clutch drum of the first clutch is abutted against the rising portion of the piston support portion from the opposite side in the axial direction to the clutch drum of the second clutch, and is laminated in the axial direction. Projecting toward the support member, and having a convex portion that forms a space portion serving as an oil passage communicating with the cancellation oil chamber between the piston support member,
The automatic transmission according to claim 1 or 2. The clutch drum of the first clutch is abutted against the rising portion of the piston support member from the axially opposite side to the clutch drum of the second clutch, and is laminated in the axial direction.
The rising portions of the piston support member are alternately formed in the circumferential direction with first convex portions toward the clutch drum of the second axial clutch and second convex portions toward the clutch drum of the first axial clutch. Bent so that
The first convex portion is welded so that the clutch drum side surface of the second clutch in the axial direction is in contact with the extended portion of the clutch drum of the second clutch to form the contact portion, and the first clutch Forming a space portion between the clutch drum and the oil passage to the cancel oil chamber;
The second convex portion has a non-contact portion between the clutch drum side surface of the first clutch in the axial direction and the clutch drum extension portion of the second clutch. Forming,
The automatic transmission according to claim 1. The clutch drums of the first and second clutches are the same as the first convex portion and the second convex portion, respectively, in the same phase in the circumferential direction as the first convex portion and the second convex portion of the piston support member. It is formed by bending alternately in the axial direction so that convex portions protruding in the direction are formed,
The clutch drum of the first clutch, the piston support member, and the clutch drum of the second clutch are configured such that the protruding directions are in contact with each other with the same protrusions.
The automatic transmission according to claim 4. The clutch drum of the first clutch, the piston support member, and the clutch drum of the second clutch are welded integrally through a contact position where the protrusions having the same protruding direction contact each other.
The automatic transmission according to claim 5. The rising portion of the piston support portion is such that the clutch drum of the first clutch is in contact with the clutch drum of the second clutch from the opposite side in the axial direction and is sandwiched between the clutch drums of the first and second clutches. A laminated portion sandwiched between the clutch drums of the first and second clutches is formed in a flat plate shape while being laminated in the axial direction.
The clutch drum of the second clutch is in contact with the laminated portion of the piston support member to form the contact portion, and a space is formed between the piston support member and the non-contact portion. It is formed by bending alternately in the axial direction one side and the other side along the circumferential direction so as to form,
The clutch drum of the first clutch forms a space portion with the laminated portion of the piston support member to form an oil passage to the cancel oil chamber, and the clutch drum of the second clutch and the piston support It is formed by bending alternately in the axial direction one side and the other side along the circumferential direction so that the contact position in the circumferential direction with the laminated portion of the member is the same,
The clutch drum of the first clutch, the piston support member, and the clutch drum of the second clutch are integrally welded at the contact position,
The automatic transmission according to claim 1.

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