JPS6152447A - Support mechanism for transmission shaft of automatic speed change gear - Google Patents

Abstract

PURPOSE:To prevent an increase in vibration and to reduce the axial dimensions by supporting the input side end portion of an intermediate transmission shaft by the output side end portion of an input shaft, the output side end portion thereof by the input side end portion of an output shaft, and the intermediate portion by an automatic speed change gear case. CONSTITUTION:The input side end portion 1A of an intermediate transmission shaft 1 is rotatably supported by the output side end portion of an input shaft 11 of a speed change gear. The output side end portion thereof is rotatably supported by the input side end portion of an output shaft 3 of the speed change gear. The intermediate portion is rotatably supported by the automatic speed change gear case. Thus, the whirling amount of the intermediate transmission shaft 1 can be reduced to prevent an increase in vibration, and besides reduce the axial dimensions of the whole transmission shafts.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a support mechanism for a transmission shaft of an automatic transmission having a transmission such as a planetary gear transmission.

[Prior Art] This type of automatic transmission usually has an input shaft as a transmission shaft, an output shaft, and an intermediate transmission shaft located between the input shaft and the output shaft.

The automatic transmission case includes a torque converter housing housing the fluid transmission device, a transmission case housing the above-mentioned lance transmissions, and an extension housing fixed to the output side (rear side) of the transmission case. Each transmission shaft is usually rotatably supported by the automatic transmission case at two fulcrums.

[Problems to be Solved by the Invention] In this type of automatic transmission, conventionally, the intermediate transmission shaft has two parts at the middle part and the two ends (also called the rear part or the rear part) where the output is
The points were supported at the rear end of the transmission case and the input end of the output shaft, respectively, and there was no support at the input side end.

However, this inventor discovered that due to the increase in transmission torque accompanying the tendency for engine output to increase, the intermediate power transmission shaft may be It was discovered that the input side tends to shift around easily, and the increased vibration places a large load on the components of the automatic transmission, causing a decrease in durability.

The purpose of the present invention is to create an intermediate story iI! An object of the present invention is to provide a support mechanism for a transmission shaft of an automatic transmission, which can effectively prevent runout at the input side end of an IJ shaft and reduce the axial dimension of the entire transmission shaft.

[Means for Solving the Problems] The support mechanism for the transmission shaft of the automatic transmission of the present invention rotatably supports the input side end at the output side end of the input shaft of the transmission, and The end portion is rotatably supported by the input end portion of the output shaft of the transmission, and the intermediate portion is rotatably supported by the automatic transmission case.

[Operations and Effects of the Invention] With the above configuration, the automatic transmission transmission shaft support mechanism of the present invention has the following operations and effects.

b) Since the input side end 1A of the intermediate transmission shaft 1 is supported, the amount of whirling of the intermediate transmission shaft 1 can be reduced, which prevents an increase in image pickup and prevents structural elements such as automatic transmission bearings. Durability can be improved.

This makes it possible to increase the transmission torque capacity of the transmission, allowing the use of small automatic transmissions for vehicles even with improved engine output.

c) The input end of the intermediate transmission shaft is rotatably supported by the output end of the input shaft, and the output end of the intermediate transmission is rotatably supported by the input end of the output shaft. By doing so, the axial dimension of the entire transmission shaft can be shortened.

[Example] Next, the present invention will be explained based on embodiments shown in the drawings.

The automatic transmission li 100 includes a torque converter 200 which is a fluid transmission device, a transmission 300 which is a main transmission, a hydraulic control device 400, a four-wheel drive transfer 500 which is a four-wheel drive sub-transmission, and a transfer control. It is composed of a device 600. .

The transmission 300 includes a first planetary gear set p1, one multi-disc clutch C01 operated by a hydraulic servo, one multi-disc brake BO1, and one overdrive FO1. i2 star gear transmission OD, second planetary gear set p2, third planetary gear set p3, two multi-disc clutches C1, C2 operated by hydraulic servo, one belt brake B1, two multi-disc brakes B2. , B3, and two one-way latches Fl, F2, forward three-speed reverse gear 1
It consists of a stage underdrive planetary gear transmission tJD.

The automatic transmission case 110 includes a torque converter 200
The transmission case 130 houses the overdrive planetary gear transmission OD and the underdrive planetary gear transmission UD, and the transfer case 140 is fastened to the rear side of the automatic transmission ioo. Torque converter housing 120 and transmission case 1
30 and transfer case 140 are each fastened with a large number of bolts.

The transfer case 140 has an input shaft chamber 141 from the front.
, transmission mechanism chamber 142 and two-wheel/four-wheel switching mechanism chamber 143
a front transmission mechanism case 146 and a rear transmission case 147 that form a transmission filter chamber 145; an extension housing 148 that forms an output shaft chamber 149 and is a rear cover of the transfer case 140; Consisting of

The torque converter 200 is housed in a torque converter chamber 121, which is located at the front (engine side) of the torque converter housing 120, and includes a front cover 111 connected to the engine output shaft, and a circular ring welded to the front cover 111 at the outer periphery. A plate-shaped rear cover 112, a pump impeller 205 disposed around the inner peripheral wall of the rear cover 112, a turbine runner 206 disposed opposite to the pump impeller 205, and a turbine shell holding the turbine runner 20G. 207, one-way clutch 20
2, a stator 201 supported by a fixed shaft (stator shaft) 203, and the front cover 111
A direct coupling clutch (lock-up clutch) 113 is provided to directly connect the turbine shell 207 and the turbine shell 207.

An oil pump 150 is housed in a recess formed on the rear surface between the torque converter chamber 121 and a cylindrical transmission chamber 132 provided in the transmission case and continuous to the rear thereof. A thin plate-shaped oil pump body 151 having a cylindrical portion 152 protruding from
The front end of the transmission case 130 is fitted into the center of the transmission case 130 and fastened with bolts.
An oil pump cover 154 having a cylindrical front support 153 that is coaxial with 52 and projects rearward is fastened. The oil pump body 151 and the oil pump cover 154 constitute an oil pump housing 155, which serves as a partition between the torque converter chamber 121 and the transmission chamber 132, and also serves as a partition between the transmission case 130 and the transmission case 130.
It forms the front supporting wall of. Further, in the middle of the transmission chamber 132, an intermediate support wall 15 that separates the overdrive mechanism chamber 133 and the underdrive structure 134 and has a cylindrical center support 158 that protrudes rearward is provided.
9 is formed separately and fitted. At the rear of the transmission case 130, a rear support wall 157 having a cylindrical rear support 156 projecting forward is provided integrally with the transmission case 130, and a space between the rear support wall 157 and the partition wall 155 forms a transmission chamber 132. There is.

The extension case 14 is fitted and fastened to the outer surface of the rear support wall 157 of the transmission case.
4, between the input shaft chamber 141 and the transmission horizontal type 142, there is provided a transfer front support 161 having a cylindrical shape coaxial with the center support 156 of the rear support wall 157 and protruding rearward. Front support wall 16
2 is fastened to the extension case 144 with bolts. Also, between the horizontal transmission 142 and the two-wheel/four-wheel switching mechanism chamber 143, there is a cylinder of a brake B4 having a coaxial center with the transfer front support 161 and overlooking a cylindrical transfer center support 163 that projects rearward. 164 is formed separately and fitted.

. In addition, there is a 2-wheel/4-wheel switching compartment 143 and a transmission mechanism compartment 145.
and between the transmission mechanism chamber 145 and the output shaft chamber 149, there is a transfer intermediate case formed integrally with the front transmission mechanism case 146 and the rear transmission mechanism case 141, and having cylindrical parts 165 and 166. A support wall 167.16B is provided. Further, the rear end portion 140A is provided with a vehicle propeller shaft (
A sleeve yoke 10 (not shown) connected to the sleeve yoke 10 is inserted through the sleeve yoke 10 and rotatably supported via a ball bearing b1.

The input shaft 11 of the transmission, which is the output shaft of the torque converter 200, is mounted on the inside of the fixed shaft 203 inside the front support 153 at two supporting points in the front and rear.
1 and m2, it is rotatably supported by the oil pump housing 155. The input shaft 11 has a flange portion 12a at the rear of the front support 153, and a large diameter portion 1 at the rear end in which a rearward-facing center hole 13 is formed in the axial center.
It has 2. At the rear of the input shaft 11, the tip is inserted into the center hole 13, and the input shaft 1 is inserted through the bushing m4.
1 is rotatably supported, with a roller bearing r in the middle.
1, the rear end is rotatably supported by the center support 159 of the intermediate support wall via
: Overdrive "fl star gear transmission OD" which has a large diameter part with a rearward facing center hole 16 in sliding contact.
The output shaft of the underdrive planetary gear transmission UD
The first intermediate transmission shaft 14 is the input shaft of the input shaft 11.
are arranged coaxially in series.

The second intermediate transmission shaft 1, which is a transmission shaft to which the transmission shaft support mechanism of the present invention is applied, has a tip end 1A, which is the input end, inserted into the center hole 16 of the first intermediate transmission J-shaft 14. and is rotatably supported on the inner circumferential wall of the hole 16 via a bush m4, and in this embodiment, the first intermediate transmission shaft 14 is rotatably supported by the center support 159 via the roller bearing r1. As a result, it is rotatably supported by the transmission case 130. In this embodiment, the intermediate portion 1B has a sleeve-shaped boss portion 2B which is a cylindrical shaft support projecting rearward, which is engaged with the ring gear R2 of the third planetary gear set p3 on the outer periphery, and at the center portion. The ring gear flange 2 is spline-fitted, and the sleeve-shaped boss portion 2B is a bush...5
The transformer 77 is rotatably supported by the transmission case 130 by being rotatably supported by the rear support 156 via the transformer 77 case 140.
The intermediate portion 1B inserted therein is rotatably supported by the transfer front support 161 via the bushing m6, thereby being rotatably supported by the transfer case 140, and is spline-fitted with the sun gear 544 of the planetary gear set Pf on the outer periphery. It matches. The tip of the rear end 1C, which is the output side, is a transfer 500, which will be described later.
The forward center hole 3 of the input side end 3A of the first output shaft 3 of
a is inserted into the large diameter portion 3B formed with the bushing m8, and is rotatably supported by the first output shaft 3 via the bushing m8, and rotatably supported by the transfer center support 163 via the first output shaft 3 and the bushing m7. As a result, it is rotatably supported by the transfer case 140.

The first output shaft 3 is arranged in series with the second intermediate transmission shaft 1 on the circumferential axis, and forms a center hole 3a that slides into the rear end 1C of the second intermediate transmission shaft 1 at the input side end 3A. The large diameter portion 3b is connected to the carrier 547 of the planetary gear set Pf by welding, and is rotatably supported by the transfer center support 163 via the bushing m7, so that the transfer case 140 is rotatably supported. In this embodiment, the intermediate portion 3C is spline-fitted on the outer periphery with the cylinder 543 of the clutch C4, and the output end portion 3B is spline-fitted with the sleeve yoke 10, and the sleeve yoke 10 is connected to the ball bearing b1.
The extension housing 148 is rotatably supported at the rear end of the extension housing 148 via the extension housing 148 . In this way, by inserting the tip OiIA of the second intermediate transmission shaft 1 into the center hole 16 of the first intermediate transmission shaft 14 and supporting it on the transmission case 130 via the intermediate support wall 158, the second intermediate transmission shaft 1 It is possible to reliably prevent vibration caused by the rotation of the distal end portion 1A.

Underdrive planetary gear transmission UD as in this embodiment
Center hole 16 at the rear end of the first intermediate transmission @14 which is the input shaft of
By providing a center hole 3a at the tip of the first output shaft 3 and inserting the rear end 1C of the second intermediate transmission shaft 1 thereinto, the second intermediate power transmission shaft 1 is inserted and supported. , the axial dimension of the entire transmission shaft can be shortened.

At each support portion of the tip portion 1Δ, the intermediate portion 1B, and the rear end portion 1C of the second intermediate transmission shaft 1, the tip portion 1A and the rear end portion 1
Center support 159 and transfer center support 16 of the transmission case at C
3 and play opening S3 are both set to the same extent, and the middle part 1
The play DS3 between B and the rear support 156 is set to be more than twice and less than four times the values of S1 and s2. As a result, the second intermediate power transmission shaft 1 is rotatably supported at its front end 1A and rear end 1C by two supporting points during transmission during steady running. For example, when the rotational balance becomes uneven, such as when the frictional force of a multi-disc brake is partially strong or weak in the circumferential direction, the intermediate portion 1B of the second intermediate power transmission shaft 1 bends and whirls around. When this vibration reaches a predetermined level, the intermediate portion 1B is moved to the rear support 156 via the boss portion 2B of the ring gear flange 2.
This prevents foot swing from increasing. In addition, the play S3 between the intermediate portion 1B of the second intermediate power transmission shaft 1 and the rear support 156 is increased, and the spline fitting between the outer periphery of the second intermediate power transmission shaft 1 and the sleeve-shaped boss portion 2B is increased. The amount of play S5 between the sleeve-shaped boss portion 2B and the rear support 156 via the bush m5
The following effects can be achieved by distributing it almost evenly.

(a) In order to prevent the ring gear flange 2 from twisting during assembly, the plays JiS4 and S5 can be largely removed, improving the ease of assembling the ring gear flange. .

(b) By providing play between the second intermediate transmission shaft 1 and the boss portion 2B of the ring gear flange 2, the flange 2 floats with respect to the second intermediate transmission shaft 1, and thrust Bearing life is increased.

In addition, the intermediate part 1B and the transfer front support 161
The play ms6 with the bushing m5 is set larger than the play ff1s3 between the intermediate portion 1B and the rear support 156.
Or, only when the bush m8 is worn out, the second intermediate transmission shaft 1
The intermediate portion 1B of is supported by a transfer front support 161 via a bush m6.

In the overdrive mechanism chamber 133, the input shaft 1
A first planetary gear set p1 is provided on the rear side of the
The ring gear RO is connected to the first intermediate transmission shaft 14 via a flange plate 22, the planetary carrier PO is connected to the flange portion 12a of the input shaft 11, and the sun gear SO is formed on the inner race shaft 23. On the front side of the first planetary gear set p1, a first hydraulic servo drum 24 that opens to the rear gear is fixed to an inner race shaft 23, and an annular piston 25 is fitted between its outer peripheral wall and the inner race shaft 23, and the clutch CO A hydraulic servo C-0 is formed, and a return spring 2 is installed on the inner race shaft 23 side.
6. A clutch Co is attached to the inside of the outer peripheral wall, and is connected to the carrier PO via the clutch CO. , 1st
Inner race 1rll1 on the inner circumference of the hydraulic servo drum 24
A one-way latch FO with 23 as an inner race is provided, a clutch CO and a brake Bo are provided on the outer periphery between the outer race 27 and the transmission case 130, and a piston 29 is fitted into the front side of the center support 159 on the rear side. Hydraulic servo B of brake BO
−0, and the tip inner circumferential portion 3 of the center support 159
A return spring 32 installed at 1 is fitted.

In the underdrive mechanism chamber 134, at the front,
A second hydraulic servo drum 41 that opens rearward is rotatably fitted onto the center support 159, and an annular piston 42 is fitted between its inner and outer circumferential walls to form a hydraulic servo C-2 of the clutch C2, while returning to the inner circumferential wall side. A clutch C2 is mounted inside the spring 44 and the outer peripheral wall. On the rear side of the second hydraulic servo drum 41, a third hydraulic servo drum 46 is fixed to the rear end portion 15 of the first intermediate transmission shaft 14 and is open to the rear and has an annular protrusion 35 at the front. An annular piston 4 is provided between the portion 15 and the outer peripheral wall.
7 is fitted to form the hydraulic servo C-1 of the clutch C1, a return spring 49 is attached to the inner circumferential side, and a clutch C2 is attached to the outer circumference of the roughly annular projection 35, and the second and third hydraulic servo drums are connected via the clutch C2. 41.46 are connected. A second planetary gear set p2 is provided on the rear side of the third hydraulic servo drum 46, and its ring gear R1 is connected to the third hydraulic servo drum 46 via an annular projection 48 and a clutch C1.
is spline-fitted to the tip portion 1A of the second intermediate transmission shaft 1, and the sun gear S1 is integrally formed with the sun gear shaft 45. Further, a connecting drum 60, which is molded to cover the second and third hydraulic servo drums 41, 46 and the second planetary gear set p2 in a minimum space, is fixed to the outer periphery of the second hydraulic servo drum 41 at its tip, and The end is attached to the sun gear shaft 45 on the rear side of the second planetary gear set p2.
They are connected and a belt brake B1 is provided on the outer circumferential side.

Transmission case 1 on the rear side of the brake B2
The brake disc b2 of the brake B2 and the brake disc b3 of the brake B3 are spline-fitted from the front to the spline 75 formed on the inside of the transmission case 30. A piston 77 is fitted into the annular hole between them to form a hydraulic servo 3-3 of the brake B3, and a return spring 79 of the hydraulic servo 13-3.
is attached to the tip of rear ribs 1 to 156 or supported by tape. A one-way latch F1 having the sun gear shaft 45 as an inner race is provided inside the brake B2, an outer race 39 is connected to the brake B2, and a return biasing means 9 is provided on the rear side of the one-way clutch F1.
0 and the inner race 83 to the fourth hydraulic servo drum 72
A spline-fitted one-way latch F2 is attached to the outer inner diameter. 3rd planetary gear set p3
, the sun gear S2 is integrally formed with the sun gear shaft 45,
The carrier P2 is connected to the outer race 86 of the front one-way clutch F2 and also to the brake B3, and the ring gear R2 is connected to the intermediate portion 1B of the second intermediate transmission shaft 1.

The transmission 300 changes the transmission case 1 according to vehicle driving conditions such as vehicle speed and throttle opening.
Each clutch and brake is controlled by hydraulic pressure selectively output from a hydraulic control device 400 in a valve body 403 built in an oil pan 401 fastened to the lower part of a valve 30 by a bolt 402 to a hydraulic servo of each friction engagement device. The engagement or disengagement is performed to perform four forward gears or 3181 rear gears. The gear position (RAN,
Examples of GE) are shown in Table 1.

Table 1 In Table 1, E indicates that the corresponding clutch, brake, or one-way clutch is engaged.

(b) indicates that the corresponding one-way clutch is engaged only in the engine drive state and is not engaged in the engine brake state. Furthermore, the corresponding one-way clutch is engaged in the engine drive state,
This indicates that this engagement is not necessarily required (lock) because power transmission is guaranteed by a clutch or brake built in parallel. Roughly r indicates that the corresponding one-way clutch is free. A rough cross indicates that the corresponding clutch and brake are released.

The transfer 500 in FIG. 3 has a clutch C3, a brake B4, and a clutch C4, which are frictional engagement elements, and a second intermediate transmission shaft 1, which is an output shaft of a planetary gear set p1, p2, as input shafts. ), the first output shaft 3 of the transfer is arranged in series with the input shaft (1).
and the first output shaft 3, a four-wheel drive sleeve 551 rotatably fitted around the first output shaft 3, and a four-wheel drive sleeve 551 arranged parallel to the input shaft (1). The second output shaft 4 is installed in the opposite direction to the first output shaft 3, and has a transmission mechanism 53 between the sleeve 551 and the second output shaft 4. The planetary gear set Pf includes a sun gear 544 spline-fitted to the end of the input shaft (1).
, a planetary binion 54 meshing with the sun gear 544
5, a ring gear 546 that meshes with the planetary binion 545, and a carrier 547 that rotatably holds the planetary binion 545 and is connected to the tip of the first output shaft 3 of the transfer 500.

The brake B4 is a multi-plate friction brake for engaging the ring gear 546 with the transfer case 140, and is a cylinder 164 formed inside the transfer case 140.
and a piston 164P mounted within the cylinder 164. Clutch C3 is arranged on the transmission 300 side of planetary gear set Pf, and is connected to sun gear 544 and carrier 5.
Hydraulic servo C-3 is configured with a cylinder 550 connected to a carrier 547 and a piston 550P mounted in the cylinder 550.
activated by Clutch C4 is a multi-disc friction clutch that connects and connects the first output shaft 3 connected to the carrier 547 and the sleeve 551 connected to one sprocket 556 of the transmission mechanism 553 for driving the second output shaft 4 of the transfer 500. and transfer case 140
A cylinder 558 rotatably supported by the cylinder 5
It is actuated by a hydraulic servo C-4 composed of a piston 558P mounted in a cylinder 58. The transmission number mechanism 553 is
Sprocket 5 spline-fitted to sleeve 551
56, a sprocket 555 formed on the second output shaft 4 and a chain 557 stretched between these sprockets
Consisting of

A parking gear 559 is provided around the outer circumferential side of the cylinder 550 of the hydraulic servo C-3, and when the shift lever of the transmission 300 is selected to the parking position, the pawl engages with the parking gear 559 to fix the first output shaft 3. do.

560 is the clutch C3 of the 4-wheel drive transfer 500
, C4 and brake B4 hydraulic servo C-3, C-4
and B-4 are provided with a hydraulic control device for supplying and discharging hydraulic pressure, 1 to 1 to 1-transfer valve bodies, and 61 is an oil pan thereof. Pressure oil supplied to hydraulic servos C-3, C-4, and B-4 of clutches C3, C4, and brake B4 is supplied to transfer control device 600 via oil passages 564 provided in transmission case 130 and transfer case 140. is guided to a transfer valve body 560 where a is provided.

During normal driving, the hydraulic servo C-3 is supplied with the line pressure supplied to the hydraulic control device for automatic transmission to engage the clutch C3, and the hydraulic servos B-4 and C-4 are discharged to release the brake B4 and the clutch. Release C4. As a result, the sun gear 544 and carrier 547 of the planetary gear set Pf are connected, power is transmitted from the input shaft (1) to the first output shaft 3 at a reduction ratio of 1, and two-wheel drive driving using only the rear wheels is obtained. At this time, the power from the input shaft (1) is transmitted to the carrier 547 via the clutch C3 without passing through the sun gear 544, planetary pinion 545, or ring gear 546.
Since the power is transmitted to the first output shaft 3, no load is applied to the tooth surfaces of each gear, increasing the life of the gears. When four-wheel drive driving becomes necessary during this two-wheel drive driving, the shift lever installed on the driver's seat etc. is manually shifted, and line pressure is gradually supplied to hydraulic servo C-4 of transfer control device 600 to clutch C-4. When they are smoothly engaged, the first output shaft 3 and the sleeve 551 are connected, and power is transmitted to the front wheels via the transmission mechanism 553, the second output shaft 4, and the propeller shaft, and the power is transmitted from the input shaft (1) to the first Output shaft 3 and second output shaft 4
Power is transmitted at a reduction ratio of 1, and a four-wheel drive directly coupled driving state (high-speed four-wheel drive state) is obtained.

During this four-wheel drive driving, when the shift lever is manually shifted when an increase in output torque is required, such as on a steep slope, line pressure is gradually supplied to hydraulic servo B-4, and at the same time, hydraulic servo C- 3, and gradually engages the brake B4 and smoothly releases the clutch C3. As a result, the sun gear 544 and the carrier 547 are released, the ring gear 546 is fixed, and the power is transferred to the input shaft ( 1) is decelerated and transmitted to the first output shaft 3 and second output shaft 4 via the sun gear 544, planetary pinion 545, and carrier 547, and a four-wheel drive deceleration driving state (low-speed four-wheel drive state) with a large torque is achieved. can get. Table 2 shows the setting range of the manual shift of the transfer 500, the engagement and disengagement of the brake B4, the clutches C3 and C4, and the running state of the vehicle.

Table 2 In Table 3, is yAl? 31 indicates the engaged state of the engagement element, and x indicates the released state. The reduction ratio (3.0 in the example) is N
The gear ratio of the sun gear 544 and the ring gear 546 of the 1-gear mechanism is λ, and the reduction ratio when the gear ratio λ is 0.5 = (
1+λ)/λ=3.0.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view of the main transmission of a four-wheel drive automatic transmission employing the transmission shaft support mechanism of the automatic transmission of the present invention, and Fig. 2 is a support structure of the transmission shaft of the automatic transmission of the present invention. 4 which adopted the mechanism
FIG. 3 is a sectional view of a sub-transmission of a four-wheel drive automatic transmission employing the automatic transmission transmission shaft support mechanism of the present invention. In the figure 1... Second intermediate power transmission shaft 3... First output shaft 11... Input shaft 14... First intermediate power transmission shaft 100
... Automatic transmission 200 ... Torque converter 30
0...Transmission 400...Hydraulic control device 500...Transfer

Claims (1)

[Scope of Claims] 1) The input side end is rotatably supported at the output side end of the input shaft of the transmission, and the output side end is supported at the input side end of the output shaft of the transmission. A support mechanism for the transmission shaft of an automatic transmission, which is rotatably supported and whose intermediate portion is rotatably supported by the automatic transmission case. 2) the transmission includes a first transmission and a second transmission, and the input shaft is an input shaft of the first transmission;
Claim 1, wherein the output shaft is an output shaft of a second transmission, and the transmission shaft is both an output shaft of the first transmission and an input shaft of the second transmission. A support mechanism for a power transmission shaft of an automatic transmission according to item 1. 3) The input shaft has a center hole at the output end,
The input end of the transmission shaft is inserted into the center hole and is rotatably supported, the output shaft has a center hole at the input end, and the output end of the transmission shaft is inserted into the center hole. 3. A support mechanism for a power transmission shaft of an automatic transmission according to claim 2, wherein the support mechanism is inserted into a center hole and rotatably supported.