JPH02146343A - Supporting structure for clutch in automatic transmission - Google Patents

Abstract

PURPOSE:To surely support a clutch drum by arranging in almost the same position in the axial direction a supporting point provided to be arranged in the internal peripheral part of a cylindrical shaft member and a supporting point supporting the internal peripheral part of an inner cylinder of the clutch drum arranged in the peripheral side. CONSTITUTION:A clutch drum 440 is integrally rotated with an input shaft, internally providing a clutch 12 and its operating piston 450, and an internal peripheral part of an inner cylinder 448 of the clutch drum is supported onto the first intermediate shaft 500 through the second intermediate shaft 550 by a cylindrical shaft member 600. Here a supporting point 551, provided to be arranged in the internal peripheral part of the cylindrical shaft member 600, and a supporting point 601, supporting the internal peripheral part of the inner cylinder 448 of the clutch drum 440, are provided to be arranged in almost the same position in the axial direction. Thus, the clutch drum enables its miniaturization to be contrived, while rigidity in a supporting part is improved enabling generation to be prevented of vibration.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an automatic transmission equipped with a starting device and a planetary gear device.

[Prior Art] In an automatic transmission equipped with a starting device and a planetary gear system, frictional engagement elements such as clutches and brakes are used, and hydraulic pressure is usually used to control these frictional engagement elements. Among frictional engagement elements, the clutch itself rotates, so it has a structure in which the clutch is placed inside a cylindrical clutch drum, and the piston that operates the clutch is inserted into a cylinder formed inside the clutch drum. is taken.

A structure for supporting a clutch drum having such a structure is to rotatably support the inner circumferential side of the inner cylinder of the clutch drum with a fixed member, or to support the inner circumferential side of the inner circumferential side of the inner cylinder of the clutch drum with a shaft that is a rotating member. It has a structure in which it is relatively rotatably supported by members. In either case, it is necessary to supply hydraulic pressure to the clutch drum to operate the piston, and an oil passage for this purpose is often provided in the inner cylinder.

The piston installed in the rotating clutch drum must have a sufficient pressure receiving area to operate the clutch, but in order to eliminate the influence of so-called centrifugal hydraulic pressure that fluctuates due to changes in rotational speed, It is desirable to make the diameter as small as possible.

In order to secure the necessary pressure receiving area while reducing the outer diameter of the piston, the inner diameter of the piston must also be reduced, and the diameter of the inner cylinder of the clutch drum must also be reduced.

Considering the above conditions, a structure in which the clutch drum is directly supported by the rotating shaft is more advantageous in terms of reducing the diameter of the clutch drum's inner cylinder. It will be received by the shaft.

[Problem M to be Solved by the Invention] The present invention directly supports the inner cylinder of a rotating clutch drum by a shaft that is a rotating member, thereby making it possible to reduce the diameter of the inner cylinder of the clutch drum while also providing a clutch. To provide a support structure for a clutch drum that reliably supports the drum.

[Means for Solving the Problems] In order to solve the problems described above, the clutch of the present invention includes a clutch drum (440
) and clutch drum (440).

A cylindrical shaft member (60) that supports the clutch (12) and the piston (450) that operates the clutch, and the inner circumference of the inner cylinder (448) of the clutch drum.
0), the cylindrical shaft member (600) is a cylindrical shaft member having a multilayer structure in which the inner peripheral side of the cylindrical shaft member (600) is further supported by another shaft member (550), the cylindrical shaft member A fulcrum (551) disposed on the inner periphery of the clutch drum and a fulcrum (601) disposed on the outer periphery that supports the inner periphery of the clutch drum's inner cylinder (448) are disposed at approximately the same position in the axial direction. It has a support structure consisting of:

[Function] As described above, the clutch drum inner cylinder (44
The fulcrum (60) of the shaft member (600) supporting the inner circumference of
1) and the fulcrum (551) of another shaft member (550) that supports the inner circumferential portion of the shaft member (600) are overlapped, so the rigidity of the fulcrum is high.

Note that the above-mentioned symbols in parentheses are in contrast to the drawings, but do not limit the configuration in any way.

[Example] Hereinafter, the present invention will be explained in detail based on the drawings.

FIG. 2 shows a skeleton of an automatic transmission embodying the present invention, and the automatic transmission, designated as a whole by reference numeral 1, includes a starting device 2 and a transmission 3. As shown in FIG.

The starting device 2 is a fluid transmission device, and includes a rear cover 204 connected to the rear part of a front cover 202 that rotates in response to engine rotation, and a pump impeller 206 formed on the inner peripheral wall surface of the rear cover 204. A turbine runner 208 disposed opposite the pump impeller 206 is held by a turbine shell 210 and
0 is connected at its inner peripheral portion to an input shaft 240 which is an output member of the starting device 2 and an input member of the transmission 3.

A stator 214 is disposed between the pump invera 206 and the turbine runner 208, and the inner peripheral portion of the stator 214 is connected to the outer race of the one-way clutch 216, and the inner race of the one-way clutch 216 is connected to a supporting member that is a fixed member. It is attached to the outer periphery of the shaft 230. A lock-up clutch 220 that directly connects the front cover 202 and the turbine shell 210 is disposed between the front cover 202 and the turbine shell 210.

The input shaft 240 of the transmission 3 is connected to a clutch drum, generally designated by the reference numeral 400, and three clutches are disposed inside the clutch drum. In this embodiment, three clutches are connected from the front side of the transmission (hereinafter, the engine side will be referred to as the front, and the side far from the engine will be referred to as the rear), and a fifth clutch 15, which is a coast clutch. A first clutch 11, which is a forward clutch, and a second clutch 12, which is a direct clutch, are arranged in this order. Another drum 470 is arranged at the rear of the clutch drum 400, and the clutch drum 4
A third clutch 13, which is a reverse clutch, is disposed between the hub 445 and the hub 445 connected to the drum 400.

A second brake 22 in the form of a band for controlling the forward gear is provided on the outer periphery of the drum 470.

The hub of the fifth clutch 15 is connected to the front end of a first intermediate shaft 500 disposed at the center of the wheel of the transmission 3, and the hub of the first clutch 11 is connected via the first one-way clutch 31. It is connected to the first intermediate shaft 500 . The front end of the first intermediate shaft 500 is supported by the rear end of the input shaft 240, and the rear end of the first intermediate shaft 500 is supported by the front end of an output shaft 700, which will be described later. The outer periphery of the first intermediate shaft 500 supports the inner periphery of a coaxially arranged second intermediate shaft 550 at two supporting points, and the outer periphery of the second intermediate shaft 550 is coaxially arranged. The inner peripheral portion of the third intermediate shaft 600 is supported by two supporting points. Therefore, the intermediate shaft has a triple shaft structure.

The hub of the second clutch 12 is connected to the front end of the second intermediate shaft 550, and the hub of the second clutch 12 is connected to the front end of the second intermediate shaft 550.
The second drum 470 is connected to the third drum through an inner cylinder 480.
is connected to the front end of the intermediate shaft 600 of.

A planetary gear device is disposed on the outer periphery of the connecting portion between the intermediate shaft and the output shaft. The planetary gear device has a simple planetary gear set with three rows, and from the front side of the transmission 3, the first row, second row,
They are arranged in the order of the third column.

The sun gear 111 of the first row of simple planetary gear sets 110 is connected to the third intermediate shaft 600 and meshes with the pinion 112, and one end of the carrier shaft 113 that supports the pinion 112 is connected to the pinion 112 via the carrier connecting member 114. It is connected to the rear end of the second intermediate shaft 550. The other end of the carrier shaft 113 is connected to the ring gear 125 of the second row simple planetary gear set 120 via a first connection member 150, and further connected to the second one-way clutch 32 via a second connection member 160. outer lace and fourth
The clutch 14 is connected to the hub of the clutch 14. A multi-plate third brake 23 is disposed on the outer periphery of the connecting member 150.

The rear end of the first intermediate shaft 500 is connected to the sun gear 121 of the second row of simple planetary gear sets, and the second row sun gear 121 has a larger outer diameter than the first row sun gear 111. The front end of the shaft 123 of the carrier that supports the pinion 122 that meshes with the sun gear 121 and ring gear 125 of the second row is connected to the ring gear 115 of the first row via the carrier connecting member 116, and the rear end of the shaft 123 is connected to the ring gear 115 of the first row. It is connected to a third row ring gear 135 via a connecting member 126 of another carrier.

Inner cylinder 800 integrated with third row sun gear 131
is connected to the inner race of the second one-way clutch 32 and the third one-way clutch 33, and is also connected to the clutch drum 830 of the fourth clutch 14. This clutch drum 830 also serves as a brake drum for the band-type first brake 21.

Carrier shaft 133 supporting the third row of binions 132
is coupled to the output shaft 700 via the carrier coupling portion 136.

FIG. 1 is a sectional view showing a specific structure of the automatic transmission having the skeleton explained in FIG.

The starting bag M2 constituting the automatic transmission 1 is a fluid transmission device, and includes a housing 200 that opens on the engine side (front side).
is housed inside. A carrier cover 204 is integrally attached to the rear of the front cover 202, which rotates under the drive of the engine.

A pump impeller 206 is mounted on the inner peripheral wall of the rear cover 204.
A turbine runner 208 is formed and disposed opposite the pump impeller 206 and is held by a turbine shell 210. The turbine shell 210 is connected at its inner peripheral portion to an input shaft 240 which is an output member of the starting device 2 and an input member of the transmission 3 via a connecting member 211 . A stator 214 is disposed between the pump impeller 206 and the turbine runner 208, and the inner peripheral portion of the stator 214 is connected to the outer race 215 of the one-way clutch 216, and the inner race 21 of the one-way clutch 216.
7 is attached to the outer periphery of the front end of the support tube 230. A lockup clutch 220 having a lockup piston 222 is disposed between the front cover 202 and the turbine shell 210.

A cylindrical case 300 that houses the components of the transmission 3 is connected to the rear of the housing 200, and an oil pump cover 250 and a partition plate 270 are connected to the joint between the housing 200 and the transmission case 300. Attach the oil pump housing 260. An internal gear pump consisting of an external gear 262 and an internal gear 264 is accommodated within the oil pump housing 260, and the inner peripheral portion of the external gear 262 is connected to a shaft 266 that is integral with the carrier cover 204. The center portion of the oil pump cover 250 forms a cylindrical support portion 252 that protrudes rearward, and the rear outer circumference of the support tube 230 is press-fitted and fixed into the inner circumference of the support portion 252.

The support tube 230 supports the input shaft at two fulcrums on its inner circumference, and the rear end of the input shaft forms a radially expanding flange. The outer peripheral part of the flange part is the first clutch drum 40
The inner cylinder 410 is connected to the inner periphery of the rear end of the inner cylinder 410, which is integral with the inner cylinder 410. The first clutch 11 and the fifth clutch 15 are housed inside the first clutch drum 400, and a piston 420 for operating the first clutch 11 and a piston 430 for operating the fifth clutch 15 are arranged as a double piston. placed in the structure.

The rear end of the first clutch drum 400 opens rearward, and the second clutch drum 440 is connected via a spline formed on the inner circumference of this opening. Inside the second clutch drum 440, the second clutch 12 and the second clutch 12 are disposed.
A piston 450 for operating the clutch 12 is provided.

The inner circumference of the rear end of the human power shaft 240 is connected to the first
supports the outer periphery of the distal end of the intermediate shaft 500.

A radially expanding flange portion 510 is formed at the front portion of the first intermediate shaft 500, and constitutes an inner race of the one-way clutch. This flange portion 510 and the first clutch 11
A first one-sided clutch 31 is disposed between the hub 520 and the hub 520. The front end of this flange portion 510 has a fifth
The hub 435 of the clutch 15 is fixed.

A hub 455 of the second clutch 12 housed within the second clutch drum 440 is connected to the front end of the second intermediate shaft 550. The second intermediate shaft 550 has a cylindrical shape, and the outer peripheral portion of the first intermediate shaft 500 supports two fulcrums at the front and rear of its inner peripheral portion. A clutch hub 445 is provided at the rear of the second clutch drum 440, and the third clutch 13 is provided between the third clutch drum 470 and the inner cylinder of the drum 470. A piston 490 is housed between the piston 480 and the piston 480 . The drum 470 also serves as a brake drum for the band-type second brake 22. A front end portion of the inner cylinder 480 is connected to the third intermediate shaft 600 via a connecting member 610.

The third intermediate shaft 600 has a cylindrical shape, and two supporting points at the front and rear of its inner circumference are supported by the outer circumference of the second intermediate shaft 550.

A central support member 3 is installed in the center of the transmission case 300.
Get 10. The central support member 310 has an outer circumferential portion joined to an inner circumferential portion of the transmission case, and a central portion formed into a cylindrical portion that protrudes forward. The ring member 310 is press-fitted into the outer peripheral part of the cylindrical part that protrudes forward, and the ring member 31
The inner circumferential portion of the inner cylinder 480 of the third clutch drum 470 is rotatably supported by the outer circumferential portion of the third clutch drum 470 .

The intermediate shaft having a triple structure extends rearward through the inner circumference of the central support member 310, and the outer circumference of the rear end of the first intermediate shaft 500 is supported by the inner circumference of the tip of the output shaft 700. A rear wall 330 is formed at the rear of the transmission case 300, and a rear support member 350 is fixed to the inner circumference of the rear wall 330.

The rear support member 350 includes a cylindrical portion that protrudes toward the front inside the transmission case 300, and the outer diameter of one cylindrical portion is formed into a plurality of stepped portions whose outer diameters gradually become smaller toward the front. . The inner peripheral portion of the front end of the cylindrical portion of the support member 350 is connected to the output shaft 7.
Supports the front outer circumference of 00.

A spigot engagement portion 360 is provided at the rear end of the transmission case 300.
The inner periphery of the rear end of the rear case 370, which is concentrically fitted through the rear case 370, supports the rear outer periphery of the output shaft 700 via a bearing. Therefore, the output shaft 700 is reliably supported by the two supporting points, and the first intermediate shaft 500 is reliably supported by the input shaft 240 and the output shaft 700 at its front and rear ends.

As explained in the skeleton of FIG. 2, three rows of simple planetary gear sets are arranged on the outer periphery of the connecting portion between the triple-structured intermediate shafts 500, 550, 600 and the output shaft 700. A first row of sun gear 111 is formed at the rear end of the third intermediate shaft 600 supported on the outermost side, and a pinion 112
meshes with Carrier shaft 11 supporting pinion 112
The inner circumferential portion of the carrier connecting member 114 supporting one end of the second intermediate shaft 550 is attached to the outer circumferential portion of the rear end of the second intermediate shaft 550 via a spline. The carrier connecting member 117 supporting the other end of the carrier shaft 113 is connected to the first connecting member 15.
The second row ring gear 125 is further connected to the second row ring gear 125 via a second connection member 160 to the outer race 810 of the second one-way clutch 32 via a second connection member 160.
connected to. A multi-plate third brake 23 is disposed on the outer periphery of the first connecting member 150, and the central support member 310
A piston 650 for operating the brake 23 is disposed on the rear wall.6 A second row of sun gears 121 is connected to the rear outer peripheral portion of the first intermediate shaft 500. This second row of sun gear 121 is
It has a larger outer diameter than the sun gear 111 in the row. The front end of the shaft 123 of the carrier that supports the pinion 122 that meshes with the sun gear 121 and ring gear 125 of the second row is connected to the ring gear 115 of the first row through a connecting member 116 of the carrier.
The rear end of the shaft 123 is connected to a third row ring gear 135 via a connecting member 126 of another carrier.

The third row sun gear 131 has its rear end connected to the inner race 870 of the second one-way clutch and also connected to the inner race 820 of the third one-way clutch 33 via the inner cylinder 800 .

A drum 830 formed opposite to the inner cylinder 800
The fourth clutch 14 and a piston 880 for operating the fourth clutch 14 are accommodated inside the fourth clutch 14 , and a clutch hub 815 is connected to an outer race 810 of the second one-way clutch 32 . A band-type first brake 21 is disposed on the outer periphery of the clutch drum 830, and the clutch drum 830 is connected to the brake 21.
Also serves as the brake drum. Third one-way clutch 33
The outer periphery of the outer race 840 is the transmission case 300.
is fixed to the inner wall of the

A carrier shaft 133 supporting the third row of pinions 132
is supported by a connecting portion 136 formed at the front end of the output shaft 700. A parking gear 710 and a speedometer drive gear 730 are attached to the outer periphery of the output shaft 700 inside the rear case 370, and a claw 720 that connects to the gear 710 is provided on the outside of the parking gear 710. . A connecting member 750 is attached to the rear end of the output shaft using a nut 7.
Fixed at 55.

Rotation sensors 305 and 3 for detecting the rotation speed of rotating members are installed in the main parts inside the transmission case 300 and rear case 370.
06, 307 to obtain information for controlling the frictional engagement elements.

A hydraulic control device (not shown) is attached to the bottom of the transmission case 300 and covered with a cover 309 that also serves as an oil pan.

As described above, this automatic transmission is equipped with a 3-row simple planetary gear set as a planetary gear device, and uses 5 clutches, 3 brakes, and 3 one-way clutches to achieve 5 forward speeds and 1 reverse speed. The operation of each friction engagement element is shown below.

Note that in the above table, the O mark indicates that the friction engagement element is engaged, and the (○) mark indicates that it is engaged during engine braking.

The present invention relates to a support structure for a clutch for gear position control in an automatic transmission as described above, and its cross-sectional structure is shown in FIG. It is.

Inside the transmission case 300 is a first clutch drum 400 connected to the input shaft.
The first clutch 11 which is a forward clutch in 00
to be placed. The first clutch 11 is always engaged when the vehicle is moving forward.

The clutch hub 520 also serves as the outer race of the first one-way clutch 31, and the inner race 510 is connected to the first intermediate shaft 500. At the rear of the first intermediate shaft 500 is a sun gear 121 of a second simple planetary gear set.
Attach. The rear end of the first clutch drum 400 opens rearward, and is connected to the second clutch drum 440, which opens forward, via a spline formed on the inner periphery of this opening.

Inside the second clutch drum 440, a second clutch 12, which is a direct clutch, and a piston 450 for operating the second clutch 12 are disposed. second clutch 1
The inner periphery of the second hub 455 is connected to the front end of the second intermediate shaft 550, and the connecting member 116 constituting the carrier of the first row of simple planetary gear sets is connected to the rear end of the second intermediate shaft 550. stick.

The rear wall connecting the rear end of the outer cylinder 441 and the rear end of the inner cylinder 448 of the second clutch drum 440 has a rear wall 443 of the outer diameter part that projects rearward, and a rear wall 443 of the outer diameter part that projects rearward, and the rear wall of the inner diameter part that is provided forward by a step. A stepped rear wall is formed by the wall 447. Outer cylinder 441 and inner cylinder 4
The piston 450 inserted between the stepped rear wall 443 and 447 also has a shape corresponding to the stepped rear wall 443 and 447, and the piston 450
There is a return spring 45 between the and inner cylinder 448.
4 is stretched, and a check ball 452 is installed inside the piston 450 to quickly release the pressure in the hydraulic chamber when the piston returns.

A clutch hub 445 is integrally formed on the rear side of the rear wall 443 of the second clutch drum 440.
45 and a third clutch drum 470 disposed behind the second clutch drum 440, a third clutch 13, which is a reverse clutch, is provided. The third clutch drum 470 also serves as a brake drum for the band-type second brake 22 disposed on the outer circumferential side, and inside the clutch drum 470 is a piston 490 that operates the third clutch 13.
to accommodate.

The inner cylinder 448 of the second clutch drum 440 is rotatable at its inner circumference via a bearing 601 at the outer circumference of the front end of the third intermediate shaft 600, and at the rear end of the third intermediate shaft 600. The sun gear 111 of the first row of simple planetary gear sets is integrally formed.

As explained in FIGS. 1 and 2, the first intermediate shaft 50
0 has its leading end supported by an input shaft supported by the case 300 of the transmission, and its rear end supported by an output shaft similarly supported by the case 300. Therefore, the first intermediate shaft 500 is supported at its front and rear ends via members that are reliably supported by the transmission, resulting in a highly rigid support structure.

The outer periphery of the first intermediate shaft 500 is connected to the inner periphery of the cylindrical second intermediate shaft 500 using two supporting points at the front and rear ends of the bearing 50.
1,502. Similarly, the second intermediate shaft 5
The outer peripheral portion of the shaft 50 supports the inner peripheral portion of the cylindrical third intermediate shaft 600 at two supporting points at the front and rear ends via bearings 551 and 552. Therefore, the three intermediate shafts have a triple structure, but each shaft can be reliably supported at two points at the front and rear ends, and the bearing 601 that supports the inner cylinder 448 of the second clutch drum 440 The second clutch drum 440
The support rigidity can be increased.

A central support member 3 is installed in the center of the transmission case 300.
Get 10. This central support member 310 is joined to the inner circumference of the transmission case at its outer circumference, and the inner circumference is formed into a cylindrical portion that protrudes forward. A ring member 320 is press-fitted into the outer circumferential portion of the cylindrical portion that protrudes forward, and the inner circumferential portion of the inner cylinder 480 of the third clutch drum 470 is rotatably supported by the outer circumferential portion of the ring member 320. The front end of the inner cylinder 480 is connected to the third
is connected to an intermediate shaft 600 of. Third clutch drum 4
A thrust plate 313 is inserted between the rear wall 475 of the third clutch drum 4 and the central support member 310.
70 is positioned in the axial direction and receives a reaction force. Similarly, a thrust plate 620 is inserted between the connecting member 605 and the rear wall 443 of the second clutch drum 440 to position the second clutch drum 440 in the axial direction and to receive the reaction force. The forward position of 440 is regulated by a flange 615 fixed to the front end of the third intermediate shaft 600.

A sleeve 315 is press-fitted into the inner peripheral portion of the central support member 310 to form an oil passage 310a, which communicates with the hydraulic control device via an oil passage (not shown) provided within the central support member 310.

A plurality of oil passages in addition to the oil passage 310a are provided between the inner peripheral part of the central support member 310 and the sleeve 315, and the third clutch 13 is operated, for example, via the oil passage 320a provided in the ring member 320. The hydraulic oil is sent to the hydraulic chamber of the piston 490.

A sleeve 610 is fixed to the inner peripheral portion of the third intermediate shaft 600, and an oil passage 600a is formed between the sleeve 610 and the third intermediate shaft 600. A radial oil passage 6 provided at one end of this oil passage 600a
Sleeve 31 with 00b attached to central support member 310
5 and communicates with the oil passage 310a. Similarly.

The oil 8600d provided at the other end of the oil passage 600a is opposed to the hole 448a of the second clutch drum 448, and the piston 450 and the rear wall 443 of the second clutch drum 440 are
It communicates with the hydraulic chamber formed between the

In the present invention, the second clutch drum 440 is
When supporting at the outer circumference of the tip of the intermediate shaft 600,
In order to support the intermediate shaft 600 of the third intermediate shaft 600 by the second intermediate shaft 550, a bearing 601 is disposed on the outer circumference of the front end directly above the bearing 551 disposed on the inner circumference of the front end of the third intermediate shaft 600. Inner cylinder 4 of clutch drum 440
It has a structure that supports the inner circumference of the front end of 48. Furthermore, the second
The bearing 501 disposed between the intermediate shaft 550 and the first intermediate shaft 5000 also includes the bearing 551 and the bearing 60.
It is arranged at the same axial position as 1. This structure allows the third intermediate shaft 600 to support the second clutch drum 440.
The rigidity of the fulcrum is high, and vibrations and the like that occur when the clutch drum 440 rotates can be reliably suppressed.

Further, the second clutch drum 440 is disposed between the first clutch drum 400 and the third clutch drum, and its axial position is similar to that of a flange whose front side is fixed to the front end of the third intermediate shaft 600. At 615, the rear side is regulated by the thrust plate 620 inserted between the connecting member 605 that connects the third intermediate shaft 600 and the third clutch drum 470, so that axial positioning is also ensured.

[Effects of the Invention] As described above, the present invention has a structure in which the clutch drum of an automatic transmission is directly supported by a shaft member, so the diameter of the inner cylinder of the clutch drum can be reduced compared to a case where the clutch drum is supported by a fixed member. It can be made small. Therefore, the inner diameter of the piston disposed within the clutch drum can also be made small, and the outer diameter can also be made small while ensuring the necessary pressure receiving area. Therefore, the check ball can be installed closer to the center axis of rotation, making it less susceptible to centrifugal force and allowing the check ball to operate smoothly to discharge pressure. By smoothing the exhaust pressure, problems such as clutch dragging due to residual pressure are prevented. By downsizing the clutch drum.

The dynamic unbalance caused by the unbalance of the rotating mass can also be reduced.

Furthermore, the shaft part that supports the inner cylinder of the clutch drum has a multilayer structure in which the inner periphery is supported by other shaft members, thereby reducing the axial dimension of the automatic transmission. By overlapping the fulcrum of the shaft and the fulcrum supporting the inner cylinder of the clutch drum in the axial direction, the rigidity of the support portion can be kept high and vibrations can be prevented from occurring. By aligning the positions of these fulcrums, it is also possible to improve the concentricity of each rotating member.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of an automatic transmission embodying the present invention, FIG. 2 is an explanatory diagram showing a skeleton, and FIG. 3 is a sectional view of a main part above the center line showing an embodiment of the present invention. 1... Automatic transmission, 2... Starting device, 3... Transmission, 12... Second clutch, 400... First clutch drum. 440...Second clutch drum, 448...
...Inner cylinder, 470...Third clutch drum, 500...
...First intermediate shaft, 550... Second intermediate shaft, 600... Third intermediate shaft.

Claims (1)

[Claims] (1) In the clutch of an automatic transmission equipped with a starting device and a planetary gear device, there is a clutch drum that rotates together with the input shaft, a clutch disposed inside the clutch drum, a piston that operates the clutch, and an inner part of the clutch drum. A cylindrical shaft member that supports the inner peripheral part of the cylinder, and the cylindrical shaft member has a multilayer structure in which the inner peripheral side of the cylindrical shaft member is further supported by another shaft member, The fulcrum located on the inner periphery of the cylindrical shaft member and the fulcrum supporting the inner periphery of the inner cylinder of the clutch drum disposed on the outer periphery are arranged at approximately the same position in the axial direction. Characteristic automatic transmission clutch support structure.