JPS60263728A - Transmission shaft - Google Patents

Abstract

PURPOSE:To enable transfer of sufficient torque through a compact structure, by a method wherein an input part and an output part are spline-engaged with each other, and the spline-engaged part is welded. CONSTITUTION:A transmission shaft 9 is coupled at an outer spline 96 of a forward end 93 of the transmission shaft 9 with a coupling cylinder 111 through an inner spline 111H formed in an inner surface 111G of the coupling cylinder 111. An engaging part 94 of the inner spline 111H of the coupling cylinder 111 with the outer spline 96 of the transmission shaft 9 is formed in size about equal to the root size of an output gear 92 and simultaneously with formation of the output gear being a helical gear having grooves 97a and 97b machined in a large part 97, and the large part is spline-engaged with the coupling cylinder 111, and a spline-engaged part 95 is welded by means of electronic beams.

Description

[Detailed description of the invention] Field F] The present invention relates to a power transmission structure for a vehicle transmission.

[Prior Art] A conventional power transmission 4M''lA related to the present invention will be explained with reference to FIG. 71 and its main parts in FIG. 8. The J two-shaft automatic transmission shown in FIG. and the first axis 50
1 and connected to the first shaft 501 via a pair of gears 501A and 502A.
2, and the second shaft 502 has an input shaft 5.3 and an input shaft 5.
03 freely rotatable tapered roller bearing 510A
, the output shaft supported by 510B! A planetary tooth Φ transmission m505 is disposed between the planetary tooth Φ transmission mechanism 505, and the output of the planetary tooth Φ transmission mechanism 505 is connected to a cylindrical output drum 506 and a flange 507 having a parking gear on its outer periphery and to which a gobap drive VA 508 is fixed. The signal is transmitted to the output shaft 504 via the Since gears are used, not only radial force but also thrust force acts on the output shaft 504. Therefore, the above-mentioned no-bird roller bearing 510 is used as a bearing that supports the output shaft 504.
Δ、! i 10 Unless a large diameter bearing is used like F3, the use of the inner diameter of the output shaft 504 is limited.
``)j・Range Vruj) The reduction ratio between 11 and ``j'' is also limited by the outer diameter of the output shaft (the diameter of the tooth bottom of the output gear 509).

With such dimensionally limited conditions, the flange:
) 07 and the output shaft 504. Conventionally, the flange 507 and the output shaft 504 were connected by welding at the cylindrical surface 509B formed at one end of the output shaft 504 as shown in FIG. However, the diameter of the cylindrical surface 509B must be smaller than the diameter of the tooth bottom 509A of the output gear 509 in order to avoid being affected by the tooth profile modification of the output tooth 1)09. Mill limit and combined 1
! The thickness J'JAh becomes thinner, and the diameter of the welded part is small, which is disadvantageous in terms of strength when it is transferred to silk.1. :oAlso, since both parts are joined only by welding,
Deep weld depth is required.

[Object of the Invention] An object of the present invention is to provide a power transmission shaft having a connection structure that is sufficient to transmit torque in members having severe dimensional restrictions at the joint portion.

[Configuration of the Invention] The power transmission shaft of the present invention has a configuration in which an input portion and an output portion are spline-fitted, and the spline-fitting portion is welded.

Effect of invention 1 With the above configuration, the power transmission shaft of the present invention has the following effects.

b) When the input part and the output part are spline-fitted, since the outer periphery of the spline-fitting part is welded, the large diameter part of the outer spline of the output part receives torque, resulting in a thick wall. You can increase your strength to become stronger.

(b) When the manpower part and the protruding horn part are spline-fitted, the outer periphery of the spline-fitting part is welded, so even if a large-diameter bearing that can withstand the force acting on the transmission shaft is installed, the wall thickness will be reduced. It is advantageous for strength experts because it is thick.

c) Since the manpower section and the output section are spline-fitted and the spline-fitting section is welded, the welding depth can be made shallow as only welding is required to prevent removal.

Embodiment 1 Next, a transmission shaft of the present invention is shown in the drawings and will be explained based on an embodiment where m=m.

First, regarding the present invention 3! 7.8 is a sectional view of a conventional transmission shaft, FIG. 1 is a sectional view of a two-shaft automatic transmission incorporating an embodiment of the transmission shaft of the present invention, and FIG. L/
FIG. 6 shows its main cross-sectional view -'tJ.

The two-shaft automatic transmission 100 shown in FIG. 1 is comprised of a hydraulic i-silk converter 200, a one-heran transmission 300, a denono-rural 90, and a hydraulic control device u (not shown).

The transmission 300 includes two multi-disc clutches C1, C2, 1 operated by hydraulic servos, such as a first planetary gear set 40 and a second planetary gear set 50.
Two band brakes B1. Two multi-disc brakes B2, B
3, one one-way latch F1 and one -h direction play 4=F2.
, a third planetary r-asset 80, and an underdrive device 60 comprising one multi-disc clutch C3, one multi-disc brake B4, and one one-way latch F3 operated by a hydraulic servo. be done.

The automatic transmission housing 110 includes a torque converter 2
00 and a front housing 1201 in which each chamber housing the differential 90 is integrally formed.
The main housing 130 is formed by integrally forming each chamber housing the underdrive device 60 and the rear cover 131 of the transmission 11 90, and houses the output center 6 of the transmission and the input center 7 of the underdrive device 60. Along with
It consists of a rear cover 140 that heats the rear side of the automatic transmission, a front housing 120, and a main housing 13.
0. The main housing 130 and the rear cover 140 are each strongly and firmly fastened with bolts.

The torque converter 200 is housed in a torque converter chamber 121 that is open at the front (engine side). Between the cylindrical transmission chamber 132 continuous to the rear of the torque converter chamber 121 and the torque converter chamber 121, there is provided an annular body (a cylindrical portion protruding forward into the interior) which accommodates the oil pump 150 therein. 152 is firmly fastened to the main housing 130, and on the rear side of the oil pump front cover 151 there is provided an oil pump front cover 151 that is coaxial with the cylindrical portion 1!]2 and protrudes rearward. The oil pump cover 154 on the right side of the cylindrical front support 153 is tightened, and 1) the oil pump front 1~
A cover 151 and an oil pump cover 154 form a partition wall 15 between both chambers. Further, at the rear of the transmission chamber 132, there is a cylindrical center revolver h 15G that protrudes forward.
An intermediate support wall 151 is provided. A transmission chamber 132 is formed between the partition wall 15j) and the intermediate support wall 157, and a gear chamber 141 of the transmission is formed between the intermediate support wall 151 and the rear cover 140.
40 has a cylindrical rear port 142 coaxial with the front support 153 that projects forward.

A cylindrical underdrive device chamber 133 is provided descending to the side of the cylindrical transmission chamber 132, and a hole-shaped blade control support is provided in the wall 123 of the front housing 120 in the center of the front of the front housing 120. 158 is provided, and at its rear,
An intermediate support wall 160 is provided to which a cylindrical center support 159 that protrudes long forward is fastened with bolts, and the space between the rear cover 140 and the intermediate support wall 160 forms the input tooth Φ chamber 142A of the underdrive device 60. The space between the intermediate support wall 160 and the wall 123 forms an under-dry solution installation chamber 133.

, A fixed shaft 203 of a one-way latch 202 supporting the data 201 of the Rukuni 1 inverter 200 is fitted inside the Freon 1-Sabo h 153, and the fixed shaft 20
The input shaft 1 of the transmission 31, which is the output shaft of the torque-1 inverter 200, is rotatably supported inside the shaft 11. has a large diameter, and a rearward-facing hole 3 is formed in the center of the rear end portion 2.

A first intermediate transmission 'I'll' 4 arranged in series with the input shaft 1 is rotatably attached to the rear of the input shaft 1, and the first intermediate transmission shaft 4 has its tip formed in the hole 3. The rear end is spline-fitted into the inner hole 613 of the central cylindrical portion 6△ of the output gear 6, and the cylindrical portion 6A of the output gear 6 is connected to the inside of the center support 156 and the rear support 142. are supported through bearings 101 and 102, respectively, and the 8F
! 1. A sun gear shaft 1) is rotatably fitted on the outside of the front end side of the intermediate transmission shaft 4 via a bearing.

an underdrive device 60 meshing with the output gear 6;
The cylindrical portion IA at the center of the manual tooth width 7 is supported by the pintary bow i 159 via the roller bearing 103, and the second intermediate transmission shaft 8 passing through the center of the underdrive device chamber 133 is inserted into the inner hole 7B. The rear end is spline fitted. The second intermediate power transmission shaft 8 has a rod shape with a flange-like protrusion 81 provided at the intermediate portion on the tip side and an oil passage 8Δ formed inside, and the tip portion is connected to the hole-shaped flon 1 through the roller bearing 104. -Support 1j〕
Supported by 8.

Between the flange-shaped protrusion 81 such as 1] and the rubber bearing 104 on the second intermediate transmission shaft 8, a spring holder 105 is sandwiched in the middle, and the spring 105 is fixed to the tip of the flange-shaped projection 81. An output section forming an output center 92 of a two-shaft automatic transmission (a multi-stage transmission F/ consisting of a transmission 10 and an underdrive device 60) through the attached pair of tapers 1 to roller bearings 106. A transmission shaft 9 is supported, and an output 6FI of the transmission 11To9 92 is meshed with a large driving gear 91 of a differential range 1 full 90.

Further, a flange-shaped protrusion 81 on the second intermediate transmission shaft 8
A cylindrical one-number gear shaft 61 is rotatably supported between the range report 159 and the center amount nabot 159 via a cylindrical shaft.
is rotatably supported via a bushing, and the outer rear end of the sun gear shaft 61 and the inner end of the inner race shaft 62 are spline-fitted.

In the transmission chamber 132, at the front, a first hydraulic servo drum 11, which is connected to the rear, is rotatably fitted onto the front ports 1 to 153 of the engine E1. 12 is fitted to form a hydraulic servo C-2 of the clutch C2, a return spring 14 is mounted on the inner circumferential wall side, and the clutch C2 is mounted on the inside of the outer circumferential wall. On the rear side of the first hydraulic nervo drum 11, there is a second hydraulic nervo drum 11 which is open to the rear and has an annular protrusion 15 at the front.
A hydraulic nervo drum 16 is fixed to the rear end 2 of the human power shaft 1, and an annular piston 17 is fitted between the rear end 2 and the outer peripheral wall to form the hydraulic servo C-1 of the clutch C1. A return spring 19 is attached to the side, a clutch C1 is attached to the inside of the outer peripheral wall, and an annular projection 15 is attached.
A clutch C2 is attached to the outer periphery of the engine, and the first and second hydraulic cylinders are connected to the bottom drum 11.16 via the clutch C2. On the rear side of the second oil E ribbon drum 1G, a first
A planetary gear set 40 is provided, the ring gear 71 (1 of which is connected to the second hydraulic servo drum 16 via the clutch C1, and the rear gear P1 of the gear 1r is spline-fitted to the tip of the first intermediate transmission shaft 4). , the ring gear 81 is integrated with the ring gear shaft 5.

Further, a connecting drum 20, which is molded so as to cover the first and second hydraulic servo drums 11.16a3 and the first planetary gear set 40 in a minimum space, is fixed to the outside of the first hydraulic servo drum 11 at its tip, and the rear The end is connected to the sun gear shaft 5 on the rear side of the first planetary gear set 40,
A band brake B1 is provided c) on the outer circumferential side.

In the surplus space 21 outside the connecting drum outside the first planetary gear set 40, an annular third hydraulic revo drum 22 that opens at the rear is fixed, and a piston 23 is fitted into it (hydraulic pressure υ"- of the play 4-82). Form B-2. Main housing 13 on the rear side of the oil aQ-bol 13-2.
0 The spline groove 25 formed on the inside has the brake B2 from the front, the one-way play-IF2) rear race 2
G, multi-plate brake B3 are installed in this order, and the outer peripheral side of the register support 156 of the intermediate support wall 157 on the rear side
~ The screw 27 is inserted into the annular hole between the housing 120.
■Inset multi-plate rule--183 hydraulic 4 novo [3-3
The return spring 29 of the hydraulic servo B-3 is supported by a flange plate 30 attached to the tip of the center support 156. 1 Said multi-disc brake B
A one-way latch F1 is provided on the inside of the latch F1, and an outer race 31 is connected to the multi-plate play 4 [32]. 2 Bane Regiarets 1 to b01fi The a pigeon 21st Rane gear set 50 installed is ring gear S.
2 is formed integrally with the sun gear shaft 5, the gear 1r rear P2 is connected to the outer one-way brake 1:2 inner race 32 and to the multi-plate play 4=83, and the ring gear R2 is connected to the first intermediate brake. It is connected to the transmission shaft 4.

In the underdrive device chamber 133, the transmission is performed as shown in FIGS. 2 to 6, respectively. 1119 and the transmission shaft 9
The inner spline 111H formed on the inner circumference 1110 connects to the outer spline 96 of the tip 93 of It has a groove 1111 that is engaged with 64Δ, and the outer periphery 111
11) includes a connecting cylinder 111 in which a purging gear 111F is formed, and a side surface 111 of a side wall 111A of the connecting cylinder 111.
A transmission shaft 113 consisting of a governor drive gear 112 etc. which is electron beam welded to F is provided, and the transmission shaft 91,
+1f J connection tube 111 inner support line 1111-
1 and the fitting part 94 of the transmission shaft 9 and the outer spline 96 are machined with grooves 97a and 97b in the large diameter part 97, and the shape is almost the same as the root diameter of the output tooth width 92, which is a J-shaped tooth Φ. Il! , =j are spline-fitted to the connecting cylinder 111, and the eleven spline fitting portions 95 are welded with electronic beer. In this embodiment, the protruding tooth width 9 of the transmission shaft 9
2. Because the tooth width is used, the engagement ratio is tight and the engagement is smooth, making it suitable for high-load, high-speed transmission.

A third planetary gear slot 80 is provided on the rear side of the transmission shaft 9, and its ring gear R3 is connected to the protrusion 81 of the second intermediate transmission shaft 8 via a flange plate 63. 11] 3 is the side E164a which is the front stage of the annular protrusion 69 that connects with the clutch C3, and one end of the side wall 64a.
4b, line side g! The sun gear S3 is connected to a connecting cylinder 111 which is a human power section through an output drum 64 consisting of a cylindrical part 64c extending from an R-shaped part 64b of 64a. Third planetary t!
Noah t! On the rear side of the tube 1-80, there is a fourth opening that opens forward.
A hydraulic servo drum G5 is fixed to the inner race shaft 62, and an annular piston 6G is fitted between its outer circumference and the in-place shaft 62 to form a hydraulic servo C-3 of the clutch C3. A clutch 03 is installed inside the return spring 68 and the outer peripheral wall.
It is connected to the cylindrical goose P3 via the clap C3. The rear inner race shaft 62 of the fourth hydraulic servo dome 65 is an inner race. An H-direction ridge 3 is provided, and an I rake B4 is provided between the inner race shaft 62 and the main housing 130 on the rear side. The piston 70 is attached to the annular protrusion 69 between the outer peripheral side of the intermediate support wall 160 on the rear side and the main housing 130.
are fitted to form the hydraulic servo 3-4 of the brake B4, and return springs 72 are fitted into grooves provided at equal intervals on the outer circumferential side of the brake B4.

A differential gear chamber 12 is located on the side of the torque converter chamber 121.
A differential gear 90 is supported by a bird roller bearing 101, and a large driving gear 91 provided at the rear end rests on the output gear 92.

1-The transmission transmission 300 selectively outputs hydraulic pressure to the hydraulic servo of each friction engagement control depending on the vehicle speed and speed to engage or disengage each clutch and brake.
When [ is released, the gears are changed to 4 front YL gears or 1 reverse gear. Table 1 shows an example of the gear position (RANGE) achieved by the operation of each latch, brake, one-way clutch, and one-way brake V. .

■, Stomach Table 1 In Table 1, O indicates that the corresponding clutch, brake, one-way clutch, or one-way brake is engaged. However, Δ indicates that the corresponding one-h direction clutch or one-way □ brake engages only in engine drive state at J3, and does not engage in engine brake state at a3. Furthermore, ◎ indicates that the corresponding one-way latch or one-way brake is engaged in the -L engine drive' state, but this engagement is caused by the transmission of power by the clutch or play-1 built in parallel with this. Since it is guaranteed, it is not necessarily necessary.0 The above describes an example in which a gear is installed in the output section. It is clear that the effects of the present invention are similarly affected when one tooth is shifted to the right.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view of the transmission shaft of the present invention incorporating the transmission shaft, Fig. 2 is a cross-sectional view of the main part of the transmission shaft of the present invention, and Fig. 3.4 is the i[plane] of the connecting cylinder connected to the transmission shaft of the present invention. Figures and sectional views, FIG. 5 is a sectional view of the governor drive gear connected to the transmission shaft of the present invention,
FIG. 6 is a sectional view of the transmission shaft of the present invention, and FIG.
The figure is a cross-sectional view of a conventional power transmission shaft, and Figure 8 is a cross-sectional view of a two-wheel automatic transmission machine incorporating a conventional power transmission shaft. Intermediate transmission shaft 6.
...Output southeast of the transmission 7.Manual power south center of underdrive equipment 8..Second intermediate transmission shaft 9.Transmission shaft 1°...Transmission device 60..Underdrive device 64. ...Output drum 81...Norange-shaped projection
82...]-Tsu l"9!i...Spline fitting part 103, 104...[]-La bearing 10G,
107... Tapered roller bearing 111...
Output part (connection fl) 111E...Parking gear
112...Governor drive gear charge (1 Kurokano-2 Fig. 3-163- Fig. 4 Fig. 5 Fig. 6

Claims (1)

[Scope of Claims] 1) A power transmission shaft in which an input part and an output part are spline-fitted and the spline-fitting part is welded. 2) The power transmission shaft according to claim 1, wherein the welding is performed on the outer peripheral portion of the spline fitting portion. 3) The output part has a gear, and the output part has a l
2. The power transmission shaft according to claim 1, wherein the spline portion that fits into the yJ entry horn portion has a tooth profile that differs from the gear only in a larger diameter. 4) The transmission shaft according to claim 3, wherein the gear is a helical gear. 5) The input section includes an input shaft, an M star gear mechanism connected to the input shaft and having at least two gear stages, and the planetary 6
i! a transmission mechanism output part that is connected to an output member on the side of the I vehicle m and has a spline on an inner periphery that fits with the output part, and the output part is rotatable on the input shaft via a bearing. Claim 4 characterized in that it is supported by
Transmission shaft as described in section.