JPS6152446A - Support mechanism for transmission shaft of automatic speed change gear - Google Patents

Abstract

PURPOSE:To prevent an increase in vibration by supporting the input side end portions of the first and second intermediate transmission shafts by output side end portions of an input shaft and the first intermediate transmission shaft, and supporting the output side end portions thereof by an automatic speed change gear case and the input side end portion of an output shaft. CONSTITUTION:The input side end portion of the first intermediate transmission shaft 14 of a speed change gear is supported by the output side end portion of an input shaft 11 of the speed change gear. The output side end portion of the first transmission shaft 14 is supported by a case of the automatic speed change gear. The input side end portion of the second transmission shaft 1 of the speed change gear is supported by the output side end portion of the first intermediate transmission shaft 14 of the speed change gear. Further, the output side end portion of the second intermediate transmission shaft 1 is supported by the input side end portion of an output shaft 3. In this arrangement, the whirling amount of the second 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, and particularly to a support mechanism for a transmission shaft of an automatic transmission having a transmission such as a planetary gear transmission. The present invention relates to a support mechanism for a transmission shaft of an automatic transmission in which a device and a third transmission are coaxially arranged in series.

[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 these power saw shafts and the output shaft. 1. The automatic transmission case includes a torque converter housing that houses the fluid transmission device, a transmission case that houses the transmission, and an extension housing that is fixed to the output side (rear side) of the transmission case. The transmission shaft is usually rotatably supported by the automatic transmission case at two supporting points.

[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, the inventor discovered that due to the increase in transmitted torque accompanying the increasing trend of engine output, the input shaft of the output shaft is It has been found that the wheels tend to swing around at the ends of the wheels, and the increased vibration places a heavy load on the components of automatic transmissions, causing a decrease in durability.

SUMMARY OF THE INVENTION An object of the present invention is to provide a support mechanism for a transmission shaft of an automatic transmission for a vehicle, which can effectively prevent vibration at the input side end of an output 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 connects the input side end of the first intermediate transmission shaft of the transmission to the output side end of the input shaft of the transmission. The output side end of the first intermediate transmission shaft is rotatably supported by the automatic transmission case, and the input side end of the second intermediate transmission shaft of the transmission is rotatably supported by the automatic transmission case. The output side end of the first intermediate transmission shaft is rotatably supported, and the output side end of the second intermediate transmission shaft is rotatably supported at the input side end of the output shaft of the transmission. shall be.

[Operations and Effects of the Invention] With the above configuration, the support mechanism for the transmission shaft of the automatic transmission 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 whirling of the intermediate transmission shaft 1 can be reduced, thereby preventing an increase in vibration and increasing the durability of components such as bearings of the automatic transmission. You can improve your sexuality.

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

C) The input side end of the first intermediate transmission shaft is rotatably supported by the output side end of the input shaft, and the input side end of the second intermediate transmission shaft is supported at the output side end of the first intermediate transmission shaft. Rotatably supported at the
By rotatably supporting the output end of the second intermediate transmission shaft by the input end of the output shaft, the axial dimension of the entire transmission shaft can be reduced.

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

As shown in FIG. 1.2.3, the automatic transmission 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, and a 4-wheel drive 01 transmission. It is composed of a four-wheel drive transfer 500 and a transfer control device 600.

The transmission 300 is directly connected to a speed increase stage which is a first transmission including a first planetary gear set p1, one multi-disc clutch C0 operated by a hydraulic servo, one multi-disc brake BO1, and one one-way latch FO. An overdrive planetary gear transmission OD with shiftable gears, a second planetary gear set p2, a third planetary gear set 1-p3, two multi-disc clutches C1, C2 operated by hydraulic servos, and one belt brake. B1
．． It is comprised of an underdrive planetary gear transmission UD with three forward speeds and one reverse speed, which is a second transmission equipped with two multi-disc brakes B2, B3 and two one-way latches Fl, F2.

The four-wheel drive transfer 500 includes a fourth planetary gear set Pf, one multi-disc clutch C3 operated by a hydraulic servo, and one multi-disc brake B4, and a third transmission capable of switching between a direct gear and a reduction gear. A 2-wheel drive/4-wheel drive switching mechanism TF that is equipped with an underdrive planetary gear transmission UD2 that is configured.

The automatic transmission case 110 includes a torque converter 200
A torque converter housing 120 that accommodates the transmission case 1301 that accommodates the bird drive Tt star gear transmission OD and an underdrive planetary gear transmission tJD, and a transfer case 140 that is fastened to the rear side of the automatic transmission lever 100. , these torque converter housing 120, transmission case 130, and lance front case 140 are each fastened with a large number of bolts.

The transfer case 140 has an input shaft chamber 141 from the front.
, a transmission mechanism chamber 142 that stores an underdrive planetary gear transmission bag @U F2, and a two-wheel/four-wheel switching chamber 143 that stores a two-wheel/four-wheel switching mechanism TF. Front transmission mechanism case 146 and rear transmission mechanism case 14 forming mechanism chamber 145
7 and the transfer case 14 forming an output shaft chamber 149.
0, and an extension housing 148 which is the rear cover of the camera.

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 2013. 207, one-way clutch 2
02, a stator 201 supported by a fixed shaft (stator shaft) 203, and the front cover 11.
1 and the turbine shell 207.

An oil pump 150 is accommodated 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. An annular plate-shaped oil pump body 151 having a protruding cylindrical portion 152,
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 159 partitions the overdrive mechanism chamber 133 and the underdrive mechanism chamber 134 and has a cylindrical center support 158 that projects rearward.
is formed separately and fitted. At the rear of the transmission case 130, a rear support wall 151 having a cylindrical rear support 156 projecting forward is provided integrally with the transmission case 130, and between it and the oil pump housing 155 is a transmission device m'.
l=13? is doing.

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 type 141 and the transmission mechanism chamber 142, there is provided a transfer front support 161 having a cylindrical shape coaxial with the center support 156 of the rear support wall 151 and protruding rearward. Front support wall 16
2 is fastened to the extension case 144 with bolts. Further, between the transmission mechanism chamber 142 and the two-wheel/four-wheel switching mechanism chamber 143, a cylinder 164 of the brake 84 has a cylindrical transfer center support 163 that is coaxial with the transfer front support 161 and projects rearward. is formed separately and fitted.

In addition, a two-wheel/four-wheel switching mechanism chamber 143 and a transmission mechanism chamber 145 are provided.
and between the transmission #J mechanism chamber 145 and the output shaft chamber 149, there is a front transmission mechanism case 146 and a rear transmission 114.
It is integrally formed with the M case 147 and has a cylindrical portion 165.1.
A transfer intermediate support wall 167,168 having 66 is provided. Further, a sleeve yoke 10 connected to a propeller shaft (not shown) of the vehicle is inserted through the rear end portion 140A so as to have a coaxial center with the front support 153, and is rotatably supported via a ball bearing b1. .

The input shaft 11 of the transmission, which is the second intermediate transmission shaft of the torque converter 200, is rotatably supported inside the fixed @ 203 inside the front support 153 at two front and rear supporting points via bushes m1 and second. The input shaft 11 has a flange portion 12a at the rear of the front support 153, and a rear end large diameter portion 12 in which a rearwardly facing central hole 13 is formed in the axis. At the rear of the input shaft 11, the tip is inserted into the center hole 13 and rotatably supported via a bush m3, and the middle is rotatably supported by a center support 159 of the intermediate support wall via a roller bearing r1. A first intermediate transmission shaft 14, whose rear end is formed with a rearward-facing central hole 16 in which the tip of the second intermediate transmission lN11 slides and forms a large diameter portion 15, is coaxially and in series with the input shaft 11. It is arranged as follows.

The tip end 1A of the second intermediate power transmission shaft 1, which is the input end, is inserted into the center hole 16 of the intermediate power transmission shaft 14.
In this embodiment, the first intermediate transmission shaft 14 is rotatably supported on the inner peripheral wall of the center sabot 1-1 via the roller bearing r1.
By being rotatably supported by 59, it is rotatably supported by the transmission case 130. In the intermediate portion 1B, in this embodiment, a ring gear is provided that meshes with the ring gear R2 of the third planetary gear set p3 on the outer periphery and has a sleeve-shaped boss portion 2B that is a cylindrical shaft support projecting rearward in the center portion. The sleeve-shaped boss portion 2B is spline-fitted with the flange 2, and is rotatably supported by the transmission case 130 by being rotatably supported by the rear support 156 via the bush m5. The intermediate portion 1B inserted into the case 140 is rotatably supported by the transfer front support via the bush m6, and is rotatably supported by the transfer case 140, and is connected to the sun gear 544 of the planetary gear set Pf on the outer periphery by the spline. They are mated. The tip of the rear end 1C, which is the output end, is inserted into the large diameter part 3B in which the forward center hole 3a of the input end 3A of the first output shaft 3 of the transfer 500, which will be described later, is formed, and the bush m8 is inserted. It is rotatably supported by the transfer case 140 by being rotatably supported by the first output shaft 3 via the first output shaft 3 and rotatably supported by the transfer center support 163 via the first output shaft 3 and the bush m7. Ru. The first output (Ill 3) is arranged in series on the same axis as the second intermediate transmission shaft 1, 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 bush m7, so that the large diameter portion 3b is attached to the transfer case 14G. Rotatably supported.

In this embodiment, the intermediate portion 3C is spline-fitted to the cylinder 543 of the clutch C4 on the outer periphery, and the output end portion 3B is spline-fitted to the sleeve yoke 10, and the sleeve yoke 10 is connected to the cylinder 543 of the clutch C4 through a roller bearing b1. The extension housing 148 is rotatably supported at the rear end portion of the extension housing 148. In this way, the tip 1A of the second intermediate transmission shaft 1
By inserting it 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, it is possible to reliably prevent the deflection caused by the rotation of the tip end 1A of the second intermediate transmission shaft 1. .

As in this embodiment, a center hole 13 is provided at the rear end of the input shaft 11, and the tip of the first intermediate transmission shaft 14 is inserted and supported, and the first intermediate transmission shaft 14 is inserted and supported. A center hole 16 is provided at the rear end of the IJ shaft 14 to insert and support the tip 1A of the second intermediate power transmission shaft 1, and a center hole 3a is provided at the end of the first output shaft 3 to support the second intermediate power transmission shaft 1. By inserting and supporting the rear end 1C of the transmission shaft, the axial dimension of the entire transmission shaft can be shortened.

In each of the support parts of the tip part IA, the intermediate part 1B, and the rear end part 1C of the second intermediate transmission shaft 1, the tip part 1A and the rear end part 1
Center support 159 and transfer center support 163 of the transmission case at C
The play ωS3 with the intermediate part 1B is set to the same extent.
The play 933 between the rear support 156 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 transmission shaft 1 is rotatably supported at the leading end 1A and rear end 1C at 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 deflection reaches a predetermined level, the intermediate portion 1B is supported by the rear support 156 via the boss portion 2B of the ring flange, thereby preventing an increase in the amount of blur. The same effect also occurs when the rotational balance becomes uneven due to other causes, such as when the frictional force of a multi-disc brake is locally strong or weak in the circumferential direction.

In addition, the rear support 1 with the intermediate portion 1B of the second intermediate transmission shaft 1
56, and the play ff1s4 due to the spline fitting between the outer periphery of the second intermediate transmission shaft 1 and the sleeve-shaped boss portion 2B, and the bush m5.
through the sleeve-shaped boss portion 2B and the rear support 15.
If the play with 6 and 1fis5 is distributed almost evenly, the following effect will be obtained.

(a) Plays ff1s4 and S5 can be increased to prevent ring gear flange 2 from twisting during assembly, improving ease of assembly of the parking gear flange.

Mouth) By providing backlash due to play mS4 between the second intermediate transmission shaft 1 and the boss portion 2B of the ring gear flange 2,
The ring gear flange 2 floats relative to the second intermediate transmission shaft 1, increasing the life of the thrust bearing.

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 rearward is UIA-mounted to the inner race shaft 23.
An annular piston 2 between its outer peripheral wall and the inner race shaft 23
5 is fitted to form the hydraulic servo C-O of the clutch Co, and a return spring 26 is attached to the inner race shaft 23 side, and the clutch CO is attached to the inside of the outer peripheral wall, and is connected to the carrier PO via the clutch Go. There is. A one-way latch FO with the inner race shaft 23 as an inner race is provided on the inner periphery of the first hydraulic servo drum 24, and a clutch CO and a brake Bo are provided on the outer periphery between the outer race 27 and the transmission case 130. A piston 29 is fitted into the front side of the center support 159 on the side to form a hydraulic servo Bo of the brake Bo, and a return spring 32 provided on the inner circumference 31 of the tip of the center support 159 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 peripheral walls to form a hydraulic servo C-2 of the clutch C2. A clutch C2 is installed inside the return 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 projection 35 at the front. An annular piston 4 is located between the end 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 annular protrusion 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 4G 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 connected to the sun gear shaft 45 on the rear side of the second planetary gear set p2, 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 an annular hole between the two to form a hydraulic servo 3-3 of the brake B3, and a return spring 79 of the hydraulic servo 8-3 is supported by a retainer 82 attached to the tip of the rear support 156. . 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 one-sided clutch F2 spline-fitted on the outer inner diameter is attached. 3rd planetary gear set p3
The sun gear S2 is formed integrally with the sun gear shaft 45,
The carrier P2 is connected to the outer race 86 of the front one-sided 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.
The engagement of each clutch and brake is controlled by hydraulic pressure selectively output to the hydraulic servo of each friction engagement device from a hydraulic control device 400 in a valve body 403 built in an oil pan 401 fastened to the lower part of the valve 30 by a bolt 402. The gears are engaged or released, resulting in four forward speeds or one reverse speed change. The operation of each clutch, brake, and one-way clutch and the gear position (RANGE) achieved
- Examples are shown in Table 1.

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

(L) indicates that the corresponding one-sided clutch is engaged only in the engine drive state and is not engaged in the engine brake state. Roughly L is engaged in the corresponding one-way ludge engine drive state,
This indicates that the engagement is not necessarily required (lock) since power transmission is guaranteed by a clutch or brake installed in parallel. Zarani t
indicates that the corresponding one-sided clutch is free.

A rough X indicates that the corresponding clutch and brake are released.

A transfer 500 in FIG. 3 includes a clutch C3, a brake B4, a clutch C4, which are frictional engagement elements, and a second intermediate transmission shaft 1 of a planetary gear set 'p2, p3.
as an input shaft, a first output shaft 3 of the transfer arranged in series with the input shaft (1), a planetary gear set Pf arranged between the input shaft (1) and the first output shaft 3, A four-wheel drive sleeve 551 is rotatably fitted around the first output shaft 3, and a second output is arranged in parallel with the input shaft (1) and installed in the opposite direction to the first output shaft 3. a transmission mechanism 53 between the shaft 4, the sleeve 551 and the second output shaft 4;
has. The planetary gear set Pf includes a sun gear 544 spline-fitted to the end of the input shaft (1), a planetary binion 545 that meshes with the sun gear 544, a ring gear 546 that meshes with the planetary binion 545, and a planetary gear 546 that meshes with the planetary binion 545. It consists of a carrier 547 that rotatably holds the binion 545 and is connected to the tip of the first output shaft 3 of the lance snor 500 described above. In this embodiment, as shown in FIG. 4, the brake B4 is a multi-disc friction brake for engaging the ring gear 546 with the transfer case 140, and is attached to a cylinder 164 formed within the transfer case 140. It is operated by a hydraulic servo 3-4 composed of a piston 164P and a piston 164P. Clutch C3 is gear set 1 to Pf
The sun gear 5 is placed on the transmission 300 side of the
44 and the carrier 547, and is operated by a hydraulic servo C-3 composed of a cylinder 550 connected to the carrier 547 and a piston 550P mounted in the cylinder 550. .

The clutch C4 is a multi-disc type for connecting and connecting the first output shaft 3 connected to the rear gear 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. It is a friction clutch and is operated by a hydraulic servo C-4, which is composed of a cylinder 558 rotatably supported by the transfer case 140 and a piston 558P mounted within the cylinder 558. Transmission engine (Omu 553 is sleeve 551
It consists of subblocks 1 to 556 spline-fitted to the subrockets 1 to 556, a sprocket 555 formed on the second output shaft 4, and a chain 557 stretched between these subblocks.

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 position 559 and fixes 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 3-4 are provided with a hydraulic control device for supplying and discharging hydraulic pressure; 1 to 3-4 are provided with a hydraulic control device; 561 is an oil pan thereof; Clutches C3, C4 and brake B4
The pressure oil supplied to the hydraulic servos C-3, C-4 and 13-4 is transferred via an oil passage 364 provided in the transmission case 130 and an oil passage 564 provided in the transmission case 140. It leads to a transfer valve body 560 in which a control device 600 is provided.

During normal driving, the line pressure supplied to the hydraulic control device of the automatic transmission is supplied to the hydraulic servo C-3 to engage the clutch C3, and the pressure is discharged from the hydraulic servos 3-4 and C-4 to control the brake B4 and the clutch. Release C4. As a result, the sun gear 544 and the 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 with only the rear wheels is increased by 1q. At this time, the power from the input shaft (1) is
The carrier 54 is connected to the carrier 54 through the clutch C3 without going through the sun gear 544, planetary binion 545, or ring gear 546.
7 to the first output shaft 3, no load is applied to the tooth surfaces of each gear, increasing the life of the gears. When 4-wheel drive is required during this 2-wheel drive driving, manually shift the shift lever installed on the driver's seat etc. to 1 to gradually supply line pressure to the hydraulic servo C-4 of the transfer control device 600. When the clutch C4 is smoothly engaged, the first output shaft 3
and the sleeve 551 are connected, power is also transmitted to the front wheels via the transmission mechanism 553, the second output shaft 4 and the propeller shaft, and a reduction ratio of 1 is generated from the input shaft (1) to the first output shaft 3 and the second output shaft 4. Power is transmitted through the 4-wheel drive system (high-speed 11-wheel drive state).

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 hydraulic servo C-3 is activated at an appropriate timing. The hydraulic pressure is discharged, brake B4 is gradually engaged, and clutch C3 is smoothly released. 1 As a result, sun gear 544 and carrier 547 are released, ring gear 546 is fixed, and power is input! Sun gear 544 from Tl1l (1)
, is decelerated and transmitted to the first output shaft 3 and the second output shaft 4 via the planetary pinion 545 and the carrier 547,
A four-wheel drive deceleration driving state (low-speed four-wheel drive state) with large torque is obtained. Table 2 shows the manual shift setting range of Transfer 500, brake B4, clutch C3 and C.
4 shows the engagement and release of No. 4 and the running state of the vehicle.

Table 2 In Table 3, ◯ indicates the engaged state of the friction engagement element, and × indicates the released state. The reduction ratio (3.0 in the example) is the reduction ratio when the tooth ratio of the sun gear 544 and ring gear 546 of the planetary gear mechanism is λ, and the tooth ratio λ is 0.5 = (1 + λ)
/λ=3.0.

[Brief explanation of the drawing]

Fig. 1 is a skeletal diagram of an automatic transmission for four-wheel drive that adopts the transmission shaft support mechanism of the automatic transmission of the present invention, and Fig. 2 shows a skeletal diagram of a four-wheel drive automatic transmission adopting the transmission shaft support mechanism of the automatic transmission of the present invention. Fig. 3 is a cross-sectional view of a sub-transmission of a four-wheel drive automatic transmission employing the transmission shaft support structure of the automatic transmission 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)

[Claims] 1) An input end of a first intermediate transmission shaft of a transmission is rotatably supported by an output end of the input shaft of the transmission, and the output of the first intermediate transmission shaft is The input side end of the second intermediate transmission shaft of the transmission is rotatably supported on the automatic transmission case by the output side end of the first intermediate transmission shaft of the transmission. A support mechanism for a transmission shaft of an automatic transmission that supports an output side end of a second intermediate transmission shaft and rotatably supports an output side end of a second intermediate transmission shaft at an input side end of an output shaft of a transmission. 2) The transmission includes a first transmission, a second transmission, and a third transmission, and the input shaft is an input shaft of the first transmission, and the first intermediate transmission The shaft is an output shaft of the first transmission and an input shaft of the second transmission, and the second intermediate transmission shaft is an output shaft of the second transmission and an input shaft of the third transmission. A support mechanism for a power transmission shaft of an automatic transmission according to claim 1, wherein the output shaft is an output shaft of a third transmission. 3) The input shaft has a center hole at the output end. An input end of the first intermediate power transmission shaft is inserted into the center hole and is rotatably supported within the center hole, and an output end of the first intermediate power transmission shaft is provided with a center hole. The input side end of the second intermediate transmission shaft is inserted into the center hole and is rotatably supported within the center hole, the output shaft has a center hole provided at the input side end, and the second intermediate transmission shaft has a center hole provided at the input side end. 2. The support mechanism for a transmission shaft of an automatic transmission according to claim 1, wherein the output end of the transmission shaft is inserted into the center hole and rotatably supported within the center hole.