JPH02275150A - Clutch device for automatic transmission - Google Patents

Abstract

PURPOSE:To increasingly make a device compact as well as to increasingly secure lubrication by arranging a clutch to be housed in the third clutch drum at the outward side in the radial direction with respect to a clutch to be housed in the second clutch drum, and thereby forming the clutch hub of the third clutch drum into a drum shape. CONSTITUTION:An automatic transmission is equipped with the first clutch drum 410 connected with an input shaft 240, and with the second and third clutch drum 440 and 470 fixed onto the outer circumference of a cylinder member 460. The hub 430 of a clutch 12 to be housed in the second clutch drum 440 is formed integrally with the first drum 410, and a clutch 14 to be housed in the third drum 470 is concurrently arranged at the outward side in the radial direction with respect to the clutch 12 to be housed in the second drum 440. Furthermore, the hub 500 of the clutch 14 to be housed in the third drum 470 is formed into a drum shape which covers the outward side of the first and second drum 410 and 440 in the radial direction so that the inner circumferential surface of the hub in a drum shape thereby forms a feed passage for lubricant to the clutch 14 to be housed in the third drum 470.

Description

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

[Conventional technology]

An automatic transmission is equipped with a starting device and a plurality of rows of planetary gears, and includes a path for transmitting input from the starting device to the elements that make up the planetary gear train, and a path for fixing the elements of the Ti star gear train to receive reaction forces. By selectively switching between the path and the path for extracting output from the elements of the planetary gear train using the frictional engagement element, gears having different gear ratios are configured and the gears are switched.

In an automatic transmission having multiple gears, it is desirable to include many frictional engagement elements in order to smoothly configure and change the gears. Among frictional engagement elements, a clutch in particular generally has a structure in which a clutch plate and a hydraulic piston, which is a servo device, are housed in a freely rotatable drum. Therefore, when a large number of clutches are installed, a problem arises in that space is required in the axial and radial directions, and it is difficult to allocate sufficient space for a supporting device for the rotating clutch drum.

Furthermore, when many clutches are arranged in a limited space, it becomes difficult to supply the necessary lubricating oil to the clutches.

[Problem to be solved by the invention]

The present invention makes effective use of space by collectively arranging three clutches for configuring and switching the gears of an automatic transmission, and also achieves smooth supply of lubricating oil to each clutch. The purpose of the present invention is to provide a clutch device that can perform

[Means to solve the problem]

In order to solve the above problems, the present invention provides a starting device (2
) and the case ('300) that accommodates the planetary gear set. Support part (252)
and an input shaft (
the first clutch drum (410) connected to the first clutch drum (240) and the oil passage member (25
4), and second and third clutch drums (440, 47) fixed to the outer periphery of the cylinder member (460) whose front and rear ends are rotatably supported by the outer periphery of the oil passage member (254).
0), and the hub (430) of the clutch (12) accommodated in the second clutch drum (440) is formed integrally with the first clutch drum (410), and the hub (430) of the clutch (12) is integrally formed with the first clutch drum (410), and the hub (430) of the clutch (12) is integrally formed with the first clutch drum (410). The clutch (14) to be accommodated is housed in the second clutch drum (440) (
12), the basic configuration is that it is disposed radially outward.

Furthermore, the hub (500) of the clutch (14) accommodated in the third clutch drum (470) has a drum shape that covers the radially outer sides of the first and second clutch drums (410, 440). The inner circumferential surface of the hub forms a lubricating oil supply path to the clutch (14) housed in the third clutch drum (470).

[Effect]

By providing the above means, two clutches (12
, 14) are placed one on top of the other in the radial direction, making it possible to utilize space effectively.
500) acts as a lubricating oil supply path to lubricate the outer clutch (14).

Note that the above-mentioned symbols in parentheses are used to contrast with 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. 1 is a sectional view of an automatic transmission implementing the present invention, and FIG.
The figure shows a skeleton, and first, an overview of the whole will be explained with reference to FIG.

The automatic transmission 1 includes a starting device 2 and a transmission 3 having a planetary gear device, but the starting device 2 includes, in addition to the torque converter shown in this embodiment, a fluid coupling, an electromagnetic clutch,
Appropriate means such as a multi-plate clutch, a centrifugal clutch, etc. can be selected.

The starting device 2 includes a rear cover 204.
A turbine runner 208, which has a pump impeller 206 formed on the inner circumferential wall surface of the rear cover 204 and is disposed opposite to the pump impeller 206, is held by a turbine shell 210, and the turbine shell 210 has an inner circumferential portion thereof that is connected to a starting device. 2 and is connected to an input shaft 240 that is an input member of the transmission 3. A stator 214 is disposed between the pump impeller 206 and the turbine runner 208, and the inner periphery of the stator 214 is connected to a one-sided clutch 216.
The inner race of the one-way clutch 216 is attached to the outer periphery of a support tube 230, which is a fixed member. 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 planetary gear train of the transmission 3 includes a basic planetary gear train 4a and an auxiliary planetary gear train 4b. The basic planetary gear train 4a is the first
and second simple planetary gear set 110, 12
0, the first simple planetary gear set 110
This is a Simpson-shaped planetary gear train that connects the carrier 113 of the second simple planetary gear set 120 and the ring gear 125 of the second simple planetary gear set 120. The auxiliary planetary gear train 4b includes one row of simple planetary gear sets 130, and includes a sun gear 13.
1 is fixed and the input of the ring gear 135 is connected to the carrier 133.
It has the function of a so-called split-type speed reducer that provides input to the sun gear and ring gear, and outputs to the carrier.

This automatic transmission has five clutches as frictional engagement elements,
Equipped with 3 brakes and 3 one-way clutches,
The coupling relationship between the friction engagement element and each element of the planetary gear train is as follows.

The input shaft 240 of the transmission 3 is connected to the drum of the first clutch 11, and the hub of the first clutch 11 is connected to the first simple planetary gear set 1 via the first intermediate shaft 610.
10 ring gear 115. first clutch 1
The drum of the second clutch 12 also serves as the hub of the second clutch 12, and the drum of the second clutch 12 connects to the sun gear 1 of the first simple planetary gear set 110 via the second intermediate shaft 620.
Connect to 11. The driver t1 of the second clutch 12 is the fourth
It is also connected to the drum of the fourth clutch 14, and the fourth clutch 1
The hub of No. 4 is connected to the carrier 123 of the second simple planetary gear set 120 via the third intermediate shaft 630. The drum of the fourth clutch 14 is the drum of the third clutch 13
It is also connected to the outer race of the first one-way clutch 31. The drum of the third clutch 13 and the inner race of the first one-way clutch 31 are connected to the sun gear 121 of the second simple planetary gear set 120 via a fourth intermediate shaft 640. A second brake 22 is disposed on the outer periphery of the drum of the third clutch 13.

The carrier 113 of the first simple planetary gear set 110 is connected to the ring gear 125 of the second simple planetary gear set 120, and the third simple planetary gear set 130 constitutes the auxiliary planetary gear train 4b via the first connecting member 150. ring gear 135
Become one with.

The carrier 123 of the second simple planetary gear set 120 is connected to the hubs of the second one-way clutch 32 and the fifth clutch 15 via a second connecting member 160. The outer race of the second one-way clutch 32 also serves as the inner race of the third one-way clutch 33 disposed on its outer periphery, and this race is integrated with the drum of the fifth clutch 15 to form the third simple planetary gear. Connected to sun gear 131 of set 130. The first brake 21 is disposed on the outer periphery of the fifth clutch 15, and the outer race of the third one-way clutch 33 is fixed to the inner wall of the transmission case.

The carrier 133 of the third simple planetary gear set 130 is connected to the output shaft 800.

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

The starting device 2 constituting the automatic transmission 1 is a fluid transmission device, and is housed inside a housing 200 that opens toward the engine side (hereinafter, the engine side will be referred to as the "front side"). 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 formed on the inner circumferential wall surface of the rear cover 204, and a turbine runner 208 disposed opposite to the pump impeller 206 is held by a turbine shell 210. The turbine shell 210 is connected to the connecting member 2 at its inner circumference.
11, it is connected 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 impeller 206 and the turbine runner 208, and the inner circumference of the stator 214 is connected to an outer race 215 of a one-way clutch 216, and an inner race 217 of the one-way clutch 216.
is attached to the outer periphery of the front end of the support tube 230. A lock-up clutch 2 having a lock-up piston 222 is disposed between the front cover 202 and the turbine shell 210.
20 will be installed.

A cylindrical case 3.00 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 installed at the joint between the housing 200 and the transmission case 300. Attach the oil pump housing 260 through it. 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 of the oil pump cover 250 forms a cylindrical support portion 252 that protrudes rearward, and this support portion 25
The rear outer circumference of the support tube 230 is press-fitted and fixed to the inner circumference of the support tube 230.

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 41
Concatenated to 0. The first clutch 11 is housed inside the first clutch drum 410, and the first clutch 11
A piston 420 is provided to operate the .

The rear side of the first clutch drum 410 opens rearward, and the clutch hub 430 is fixed to the front side of the drum 410, and the second clutch 12 is connected between the clutch hub 430 and the second clutch drum 440 disposed opposite to each other. A piston 450 is housed therein. The inner peripheral side of the second clutch drum 440 is a cylinder member 46
This cylinder member 460 is rotatably supported by the support portion 252 of the oil pump cover 250. A fourth clutch drum 470 that accommodates the fourth clutch 14 and a piston 480 is connected to the front end of the cylinder member 460 .

The fourth clutch drum 470 is connected to the outer race 540 of the first one-way clutch 31 via a connecting member 490. The hub 500 of the fourth clutch 14 is connected to the third intermediate shaft 630. The third clutch 13 is provided between the outer race 540 and a third clutch drum 520 disposed on the outer peripheral side thereof, and the piston 530 is housed in the clutch drum 520. A band-type second brake 22 is provided on the outer periphery of the third clutch drum 520, and the inner cylinder side of the clutch drum 520 is integrated with the inner race 510 of the first one-way clutch 31 □.

The inner circumference of the rear end of the input shaft 240 is connected to the first
supports the outer periphery of the distal end of the intermediate shaft 610.

The outer peripheral portion of the rear end of the first intermediate shaft 610 is supported by the inner peripheral portion of the tip end of the output shaft 800 via a bearing. Since the input shaft 240 and the output shaft 800 are firmly supported by the transmission case 300, the support rigidity of the first intermediate shaft 610 supported by these shafts is also increased.

The outer circumference of the first intermediate shaft 610 is a cylindrical second intermediate shaft 6.
20 is supported at two points, and the outer peripheral portion of the second intermediate shaft 620 supports a cylindrical third intermediate shaft 630 at two points. A fourth intermediate shaft 640 arranged concentrically on the outer peripheral side of the third intermediate shaft 630
is supported by the inner periphery of a central support member 310 attached to the center inside the transmission case 300. The center portion of the central support member 310 is formed into a cylindrical portion that protrudes forward and rearward of the case. The inner peripheral portion of the inner cylinder of the third clutch drum 520 is rotatably supported.

1st. The front end of the intermediate shaft 610 is connected to the hub 405 of the first clutch 11, and the front end of the second intermediate shaft '620 is connected to the clutch drum 440 of the second clutch 12. The front end of the third intermediate shaft 630 is connected to the hub 500 of the fourth clutch 14 , and the front end of the fourth intermediate shaft is connected to the drum 520 of the third clutch 13 and the first one-way clutch 31 . Connected to inner race 510. The intermediate shaft having a quadruple structure passes through the central support member 310 and extends to the rear side,
The outer peripheral portion of the rear end of the first intermediate shaft 610 is supported by the inner peripheral portion of the tip end of the output shaft 800 . A rear wall 330 is formed at the rear of the transmission case 300, and a rear support member 350 is inserted into and 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 the cylindrical portion is formed into a plurality of stepped portions whose outer diameters gradually become smaller toward the front. . The front end inner circumferential portion of the cylindrical portion of the support member 350 supports the front outer circumferential portion of the output shaft 800 .

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 fitted concentrically through the rear case 370, supports the rear outer periphery of the output shaft 800 via a bearing. Therefore, the output shaft 800 is reliably supported by the two supporting points, and the first intermediate shaft 610 is reliably supported at its front and rear ends by the input shaft 240 and the output shaft 800, as described above.

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 intermediate shafts 610, 620, 630, 640 and the output shaft 800, which have a quadruple structure. 1st. arranged in the third order.

The ring gear 115 of the first simple planetary gear set 110 is attached to the rear end of the first intermediate shaft 610 via a connecting member 615. A first simple planetary gear set 110 is installed at the rear end of the second intermediate shaft 6゛20.
A sun gear 111 is attached, and a pinion carrier shaft 113 is attached to a second simple planetary gear set 120.
The ring gear 125 is connected to the ring gear 125. One end of the carrier shaft 123 of the second simple planetary gear set 120 is connected to the third intermediate shaft 630, and the other end is connected to the second connecting member 1.
60 to the inner race 700 of the second one-way clutch 32.

A sun gear 121 of the second simple planetary gear set 120 is formed at the rear end of the fourth intermediate shaft 640. Ring gear 125 of the second simple planetary gear set
is integrated with the ring gear 135 of the third simple planetary gear set 13o via the first connecting member 150.

A multi-plate third brake 23 is disposed on the outer periphery of the second coupling member 160 disposed outside the first coupling member 150, and a piston 550 is inserted into the rear wall surface of the central support member 310. to be accommodated.

A sprag and an outer race 710 are arranged on the outer circumferential side of the inner race 700 that is coupled to the second connecting member 160.
A one-way clutch 32 is configured.

Another sprag and an outer race 720 are further disposed on the outer peripheral side of the outer race 710 to constitute the third one-way clutch 33. That is, the race 710 is a member that serves both as an outer race and an inner race, and is interposed between the two one-way clutches 32 and 33, so it is referred to as a middle race 710 in this specification. inner lace 70
0 is integrated with the clutch hub 730, and the middle race 7
10 is connected to the fifth clutch drum 740. The fifth clutch 15 and piston 750 are housed in the fifth clutch drum 740.

The outer periphery of the outer race 720 of the third one-way clutch 33 is spline engaged with the inner periphery of the case 300, and the band-type first brake 21 is disposed on the outer periphery of the fifth clutch drum 740. The shaft member 760, which is integrated with the inner cylinder integrated with the fifth clutch drum 740, has its inner circumference branched at the outer circumference of the rear support member 350, and has a third simple planetary gear cell 1-
Attach 130 Sanghyas 131.

The shaft 133 of the carrier that supports the pinion of the third simple planetary gear set 130 is supported by a connecting portion formed at the front end of the output shaft 800.

The outer periphery of the output shaft 800 inside the rear case 370 includes
A parking gear 810 and a speedometer drive gear 830 are attached, and the parking gear 810
A pawl 820 coupled to the gear 810 is disposed on the outside of the gear 810 .

A connecting member 850 is fixed to the rear end of the output shaft with a nut 855.

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 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, the automatic transmission of the present invention includes five clutches and three brakes as frictional engagement elements.

Three one-way clutches are used to achieve five forward speeds and one reverse speed. Table 1 shows each friction and the engagement state of the engagement elements at each gear stage.

In Table 1, the ○ mark indicates that the frictional engagement element engages,
The (0) mark indicates that it is engaged during engine braking.
Note that the 4A gear has the same gear ratio as the 4th gear, and is a gear that appears immediately before shifting to the 5th gear.

The present invention relates to a clutch device for an automatic transmission having the above-described structure, and the specific structure thereof will be explained below with reference to FIG. 3.

An oil pump cover 250 is firmly attached between the housing of the starting device and the transmission case 300, and the center portion of the oil pump cover 250 forms a cylindrical support portion 252 that projects rearward. The outer circumferential portion of the rear end of the support tube 230 is press-fitted into the inner circumferential portion of the supporting portion 252 .

The rear outer peripheral portion of the input shaft 240 is supported by a radial bearing 241 disposed between the input shaft 240 and the support portion 252, and the rear end portion of the input shaft forms a radially expanding flange portion. The outer peripheral part of the flange part is connected to a first clutch drum 410 that accommodates the first clutch 11, and a piston 420 for operating the first clutch drum 11 is disposed therein.

The hub 405 of the first clutch 11 is connected to the first intermediate shaft 610 via a spline on its inner peripheral side.

The outer peripheral portion of the front end of the first intermediate shaft 610 is supported by the inner peripheral portion of the rear end of the input shaft 240 via a radial bearing 611 . This first intermediate shaft 610 supports the inner peripheral portion of a second intermediate shaft 620 by a radial bearing 612 provided on its outer peripheral portion. Further, the second intermediate shaft 620 supports the inner peripheral part of the third intermediate shaft 630 by a radial bearing 612 provided on its outer peripheral part. Therefore, the three intermediate shafts have a multilayer structure, and the first intermediate shaft The shaft 610 is the second
Supports third intermediate shafts 620, 630.

A lubricating oil supply path 61 is provided at the axial center of the first intermediate shaft 610.
4 is provided, and an oil hole 6 is provided in the radial direction from this supply path 614.
15,616 is the formation.

The rear side of the first clutch drum 410 opens rearward, and a clutch hub 430 is fixed to the front surface of the front wall of the clutch drum 410. A second clutch drum 4 that accommodates the second clutch 12 is disposed on the outer peripheral side of the clutch hub 430.
40 and insert a piston 450 that operates the second clutch 12. An inner peripheral portion of the front wall of the clutch drum 440 is fixed to a central portion of the cylinder member 460. A rear end portion of the clutch drum 440 is engaged with a drum-like coupling member 443 via a spline 442.

The inner circumference of the rear radial wall 444 of the connecting member 443 is fixed to the outer circumference of the tip of the second intermediate shaft 620 . A radial opening 445 is provided in the cylindrical portion of the connecting member 443. The cylinder member 460 has a stepped cylindrical shape and has approximately the same length as the support portion 252 of the oil pump cover 250.

A cylindrical oil passage member 254 is press-fitted and fixed to the outer periphery of the support portion 252 of the oil pump cover 250.

The oil pump cover 250 is generally made of a material such as an aluminum alloy, but this oil passage member is made of, for example, iron. Then, precision can be improved by cutting. The oil passage member 254 rotatably supports the front and rear ends of the inner circumference of the cylinder member 460 by radial bearings 255a and 255b disposed at the front and rear ends of the outer circumference. That is, the cylinder member 460 is connected to the oil passage member 254 which is a fixed member.
It is definitely supported at two points. This cylinder member 46
0 is also a machined part to ensure high accuracy. The small diameter portion formed in the latter half of the outer peripheral side of the cylinder member 460 is
It becomes the inner cylinder of the piston 450 that operates the second clutch 12. A clutch drum accommodating the fourth clutch 14, generally designated by the reference numeral 470, is attached to the first half of the outer peripheral side of the cylinder member 460. The clutch drum 470 has a structure in which two drums, a drum 472 disposed on the inside and a drum 474 disposed on the outside, are integrally overlapped, and the inner part of the inner drum 472 is connected to the cylinder member 460.
The spline 463 engages the two with each other.

A piston 480 is inserted into the inner drum 472, and the fourth clutch 14 is disposed on the inner peripheral side of the outer drum 474. The inner circumferential portion of a suppressing member 482 is fixed to the outer circumferential portion of the piston 480, and the fourth clutch 14 is operated to suppress by the outer circumferential portion of the suppressing member 482.

The rear end of the clutch drum 470 of the fourth clutch 14 is connected to a drum-shaped connecting member 490 via a spline, and the inner circumference of the rear end of the connecting member is connected to the outer race 540 of the first one-way clutch 31. .

The hub 500 of the fourth clutch 14 has a drum shape,
A disk of the fourth clutch 14 is spline supported at its front end outer periphery, the disk support having a radial opening 508 and a rear radial wall 508 of the hub 500.
02 is fixed to the front end outer circumference of the third intermediate shaft 630.

As described above, the present invention has a configuration in which three clutches are arranged together, and among these, the clutch drum 440 that accommodates the second clutch 12 and the clutch drum 470 that accommodates the fourth clutch 14 are attached to a common cylinder member 460 and rotate together.

This is because the clutch drum 440 of the second clutch 12 and the clutch drum 470 of the fourth clutch 14 are connected to form a power transmission path, so the above-described configuration can be adopted.

As shown in Table 1, the fourth clutch 14 is engaged during the first to second forward speeds to receive the reaction force, and transmits power in the third and higher speeds, and the torque capacity is It is relatively small. However, it is desirable to increase the heat capacity.

Therefore, by utilizing this characteristic, the fourth clutch 14 is
The clutches 12 are stacked in a stepped manner in the outer diameter direction of the clutches 12.

In addition, since the piston 480 that operates the clutch 14 with a small torque capacity requires a relatively small effective area, it is a small diameter piston and is inserted into the clutch drum 472 disposed inside the double structure clutch drum. do. Since the clutch drum 470 rotates at a high speed of 3rd speed or higher, it is easily affected by centrifugal oil pressure generated by centrifugal force, but by forming the piston 480 with a small diameter, the influence of centrifugal oil pressure is eliminated as much as possible. be able to.

On the other hand, the first clutch 11 is engaged from the first forward speed to the fourth forward speed, and the power from the input shaft 240 is transferred to the first intermediate shaft 6.
10. Since the power of the first intermediate shaft 610 is transmitted to the ring gear of the first simple planetary gear set, which has a large diameter, it is possible to reduce the diameter of the first intermediate shaft 610, making the intermediate shaft with a multiple structure compact. It can be configured as follows.

Next, the lubricating oil supply mechanism in this device will be explained.

When the first intermediate shaft 610 rotates, the lubricating oil in the supply path 614 is sent out from one oil hole 615 in the radial direction by centrifugal force, and lubricates the surrounding bearings as well as the hole 243 of the constantly rotating input shaft 240. through the first clutch 1
Lubricate 1. The oil lubricating the first clutch 11 is transferred to the drum-shaped connecting member 4 by the centrifugal force of the clutch drum 410.
43 and reaches the inner circumferential surface of the cylindrical hub 500 of the fourth clutch 14 via the opening 445.

The oil coming out of the other oil hole 616 passes through the hole 622 formed in the second intermediate shaft 620, lubricates the surrounding bearings, and connects the drum 440 of the second clutch 12 and the second intermediate shaft 620. It reaches the gap 503 between the wall 444 of the connecting member 443 and the wall 502 of the hub 500 of the fourth clutch 14, and is sent to the inner peripheral surface of the hub 500.

Oil is also sent to the second clutch 12 via an oil passage (not shown) through the opening of the spline 442 and the like to the hub 50.
It is sent to the inner peripheral surface of 0.

These lubricating oils flow along the inner peripheral surface of hub 500 and are sent to fourth clutch 14 through opening 508 to participate in lubrication.

Therefore, the fourth clutch 14 disposed on the radially outer side of the clutch drum 440 of the second clutch 12 can also be sufficiently lubricated from the axial direction.

〔Effect of the invention〕

As described above, the present invention is a clutch device installed in an automatic transmission, in which three clutches can be arranged in a concentrated manner at the front of a case of the automatic transmission. A support portion formed in the center of the oil pump cover, which is firmly fixed to the transmission case, reliably supports the input shaft at its inner periphery, and the first clutch drum is attached to the input shaft. An oil passage member is press-fitted into the outer periphery of the support portion, and second and third clutch drums are fixed to the outer periphery of the cylinder member supported by the outer periphery of the oil passage member.

With this configuration, three clutches can be reliably supported by the fixed member.

By arranging the clutch housed in the third clutch drum radially outside of the clutch housed in the second clutch drum, space can be used effectively to achieve compactness.

By arranging the clutch housed in the third clutch drum radially outward from the clutch housed in the second clutch drum, lubrication of the clutch housed in the third clutch drum becomes a problem. In the invention, the hub of the clutch housed in the third clutch drum is shaped like a drum, and the inner peripheral surface of the hub is used as a lubricating oil passage, so lubricating oil can be reliably supplied from the shaft center. .

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of an automatic transmission embodying the present invention, FIG. 2 is an explanatory diagram showing an overview of the automatic transmission embodying the present invention, and FIG. 3 is a partial cross-sectional view of essential parts. 1... Automatic transmission, 2... Starting device. 12... Second clutch, 14... Fourth clutch, 200... Housing, 240... Input shaft, 250... Oil pump cover 252...
... Support part, 254 ... Oil passage member, 300 ... Case, 410 ... First clutch drum, 430 ...
...Second clutch hub, 440...Second clutch drum, 470...Third clutch drum, 500...Fourth clutch hub .

Claims (2)

[Claims] (1) In an automatic transmission equipped with a starting device and a planetary gear device, an oil pump cover that is clamped and fixed between a housing that accommodates the starting device and a case that accommodates the planetary gear device, and a center portion of the oil pump cover on the case side. a first clutch drum connected to an input shaft supported by an inner periphery of the support part; an oil passage member press-fitted into the outer periphery of the support part; and an outer periphery of the oil passage member. The hub of the clutch housed in the second clutch drum is fixed to the outer periphery of a cylinder member that rotatably supports the front and rear ends of the cylinder member.
An automatic transmission characterized in that the clutch is formed integrally with a clutch drum, and the clutch accommodated in the third clutch drum is disposed radially outward from the clutch accommodated in the second clutch drum. clutch device. (2) In the clutch device according to claim 1, the hubs of the clutches housed in the third clutch drum are connected to the first and second clutches.
An automatic transmission having a drum shape that covers the outside in the radial direction of a third clutch drum, the inner peripheral surface of the drum-shaped hub forming a supply path for lubricating oil to a clutch housed in a third clutch drum. clutch device.