JPH05172215A - Automatic transmission - Google Patents

Abstract

PURPOSE:To enhance the working efficiency to install a counter-drive gear on a shaft supporting part of a transmission case. CONSTITUTION:An automatic transmission includes a gear consisting of a ring part 66 equipped with cogs on the periphery and an cylindrical hub 15 formed on the inside circumference of the ring part 66 and two sets of tapered roller bearings 18, 19 consisting of two inner raceways 62, 63 fitted by pressure on the hub 15 and one outer raceway 61. One of the inner raceways 62 is fitted by pressure on the hub 15, and thereon the outer raceway 61 is installed and then the other inner raceway 63 is fitted by pressure to erect a sub-assembly. Because a plurality of jig insert holes 75 are formed penetratively in the ring part 66 of the gear in the position mating with the end face of the outer raceway 61, the sub-assembly can be fitted by pressure to the shaft supporting part of the transmission case 16 by inserting jig in the hole 75 and pushing the end face of the outer raceway 61, which enhances the the working efficiency.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic transmission for vehicles.

[0002]

2. Description of the Related Art Conventionally, in automatic transmissions for vehicles,
The torque output from the engine is received via a torque converter, and the torque is changed via an automatic transmission mechanism to drive each drive wheel. Then, in the above automatic transmission mechanism, the respective elements of the plurality of planetary gear units are selectively engaged and disengaged via a clutch, a brake, a one-way clutch and the like.

When the automatic transmission mechanism is mounted on a small vehicle, it is necessary to widen the space in the vehicle compartment or the luggage compartment. Therefore, the engine and the automatic transmission mechanism are arranged so as to extend to the left and right of the vehicle. The engine-front wheel drive) method is often adopted. In the FF type, the transmission unit and the counter shaft are arranged in parallel, and the rotation changed by the transmission unit is transmitted to the counter shaft. In this case, a counter drive gear that outputs the rotation changed by the speed change unit and a counter driven gear that transmits the input rotation to the counter shaft are provided, and they are arranged so as to mesh with each other behind the automatic speed change mechanism. ing.

However, in order to rotatably support the counter drive gear, two sets of bearings are required at positions separated by a predetermined distance in the axial direction, but as described above, the counter drive gear is provided in the transmission case. Since the bearings are arranged rearward, the axial dimension becomes large if two sets of bearings are arranged on both sides of the counter drive gear.

Therefore, there is provided a counter drive gear in which two sets of bearings are provided on one side for cantilever support (Japanese Patent Laid-Open No. 62-15533).
(See Japanese Patent Publication No. 1). In this type of automatic transmission, the hub of the counter drive gear is supported by two sets of tapered roller bearings so that the counter drive gear does not move in the axial direction. In this case, the outer race of the tapered roller bearing is divided into left and right parts, and the left and right outer races are press-fitted into the shaft support portion of the transmission case, and then the inner race and the counter drive gear are assembled.

[0006]

However, in the above conventional automatic transmission, when the counter drive gear is assembled to the shaft support portion of the transmission case,
Many parts such as outer races and inner races of tapered roller bearings must be assembled in a predetermined order, and since subassemblies cannot be formed by these parts and assembled by these subassemblies, work efficiency decreases. Resulting in.

The present invention solves the problems of the conventional automatic transmission described above, and provides an automatic transmission capable of improving work efficiency when the counter drive gear is assembled to the shaft support portion of the transmission case. With the goal.

[0008]

Therefore, in an automatic transmission according to the present invention, a gear comprising an annular portion having teeth cut on the outer periphery and a cylindrical hub formed on the inner peripheral side of the annular portion, Two sets of tapered races consisting of two inner races press-fitted to the outer circumference of the tubular hub and one outer race provided corresponding to the inner races and having an outer circumference press-fitted to the shaft support portion of the transmission case. It has a roller bearing.

A plurality of jig insertion holes are formed through the annular portion of the gear at positions corresponding to the end faces of the outer race.

[0010]

According to the present invention, as described above, a gear having an annular portion whose outer periphery is toothed and a tubular hub formed on the inner peripheral side of the annular portion, and the tubular hub described above. Two inner races that are press-fitted to the outer periphery and two sets of tapered roller bearings that are provided corresponding to the inner races and that have one outer race that is press-fitted to the shaft support portion of the transmission case. Have

Therefore, when forming a sub-assembly for supporting the gear, one inner race is first press-fitted onto the outer periphery of the tubular hub, then the outer race is assembled, and then the other inner race is assembled. Press fit. Further, since a plurality of jig insertion holes are formed through the annular portion of the gear at a position corresponding to the end face of the outer race, after assembling the subassembly as described above, the jig insertion holes are formed. The subassembly can be press-fitted into the shaft support portion of the transmission case by inserting a jig therein and pushing the end surface of the outer race. Therefore, it is possible to assemble the sub-assembly in advance and assemble the sub-assembly together with the transmission case, so that work efficiency is improved.

[0012]

Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 is a state diagram when a counter drive gear support structure is assembled to a transmission case in the automatic transmission of the present invention, FIG. 2 is a schematic diagram of the automatic transmission of the present invention, and FIG. 3 is a main part of the automatic transmission of the present invention. FIG. 4 is a cross-sectional view and FIG. 4 is a diagram showing a state in which the counter drive gear of the automatic transmission according to the present invention is mounted.

In FIG. 2, the automatic transmission includes a fluid coupling 1
00 and a gear train 200. The gear train 200 is coaxially connected to the output shaft 101 of the fluid coupling 100, and is a main transmission unit for performing a shift of three forward gears and one reverse gear, that is, a first underdrive gear shift. Machine 210,
A sub-transmission unit that is connected in parallel to the first underdrive transmission 210 to perform forward two-stage gear shifting, that is, a second underdrive transmission 250 and an output shaft of the second underdrive transmission 250. And a differential gear 270.

The fluid coupling 100 includes a pump impeller 102 connected to the output shaft of the engine, a turbine runner 103 connected to the output shaft 101, and a one-way clutch 1.
A torque converter composed of a stator 105 fixed to the transmission case 16 via 04,
A direct coupling clutch 106 is provided. The first underdrive transmission 210 having the output shaft 101 of the fluid coupling 100 as an input shaft has the input shaft and the left side (the left side in the drawing, the same applies to the left and right directions of the vehicle in the left and right directions in the drawing). The same)) and the output shaft 211 coaxially arranged. The first underdrive transmission 210 has the first
Planetary gear set 220, second planetary gear set 230, and these planetary gear sets 22
Clutches C ₁ and C ₂ , which engage and disengage components 0 and 230, band brake B ₁ , brake B ₂ ,
B _3, formed by disposing the friction engagement device such as a one-way clutch F _1, F _2.

The first planetary gear set 220 includes a ring gear 222 connected to a cylinder 221 connected to the output shaft 101 of the fluid coupling 100 via a clutch C ₁ and a first underdrive transmission 210.
Sun gear 22 formed at the right end of a sun gear shaft 212 that is fitted onto the output shaft 211 of the above and is rotatably supported.
3. A planetary gear 225 that is engaged with the ring gear 222 and the sun gear 223 and is rotatably held by the carrier 224.

A drum 226 is attached to the left end side wall of the sun gear shaft 212, and the first planetary gear set 220 is housed in the drum 226. The open right end of the drum 226 is connected to the cylinder 221 via the clutch C ₂ , and the outer periphery is the band brake B.
It is fixed to the transmission case 16 via ₁ . Further, the sun gear shaft 212, the intermediate portion is fixed to the one-way clutch F ₁ and the one-way clutch F ₁ and the transmission case 16 via the brake B ₂ which are disposed in series.

Further, the second planetary gear set 2
Reference numeral 30 denotes a ring gear 231 connected to the left side portion of the output shaft 211 of the first underdrive transmission 210, a sun gear 232 formed at the left end of the sun gear shaft 212,
One-way clutch F ₂ and the one-way clutch F ₂
And a planetary gear 234 supported by the carrier 233 and meshed between the ring gear 231 and the sun gear 232 via a brake B ₃ arranged in parallel with the carrier 233.

Then, the first underdrive transmission 21
The counter drive gear 21 is provided at the left end of the 0 output shaft 211.
3 is fixed, and the counter drive gear 213 meshes with a counter driven gear 252 fixed to the left end of the input shaft 251 of the second underdrive transmission 250. The second underdrive transmission 250 is the first
An input shaft 251 arranged in parallel with the output shaft 211 of the underdrive transmission 210, and a hollow output externally fitted to the right end of the input shaft 251 and rotatably supported to form an output gear 255 on the outer periphery. a shaft 254, a third planetary gear set 260 disposed between the input shaft 251 and the hollow output shaft 254, the clutch C ₃ to engage or release the components, the brake B _4, the one-way clutch F ₃ Etc. are arranged.

Then, the third planetary gear set 26
0 is the input shaft 25 of the second underdrive transmission 250
1, a ring gear 261 connected to the right end of the input shaft 25, the input shaft 25
1 is rotatably fitted on the outside and the left side is the brake B.
₄ and the sun gear shaft 253 fixed to the transmission case 16 via a one-way clutch F ₃ arranged in parallel with the brake B ₄ , a sun gear 262 formed at the right end of the sun gear shaft 253, and the third gear. The planetary gear set 260 is housed, the right end is connected to the hollow output shaft 254, the left end is connected to the left end of the sun gear shaft 253 via the clutch C ₃ , and the governor drive gear 256 and the parking gear 257 are formed on the outer periphery. And the carrier 263 connected to the drum 258 and the ring gear 261 and the sun gear 262 are meshed with each other and the carrier 26 is
3 and a planetary gear 264 rotatably supported by

Further, the differential gear 270
Is composed of a drive large gear 271, which meshes with the output gear 255 of the second underdrive transmission 250, a differential gear box 272, a differential gear 273, and output shafts 274, 275 connected to the drive wheels. In FIG. 3, the fluid coupling 1 is provided inside the front center support 11.
00 (see FIG. 2), the fixed shaft 12 of the one-way clutch 104 that supports the stator 105 is fitted into the fixed shaft 1.
The output shaft 101 of the fluid coupling 100 and the input shaft of the gear train 200 are rotatably supported on the inner side of 2. The rear end of the input shaft has a large diameter, and the output shaft 211 of the first underdrive transmission 210 is rotatably mounted behind it.

The counter drive gear 213 is provided at the rear end 14 of the output shaft 211, and the rotation of the counter drive gear 213 is transmitted to the counter driven gear 252. Therefore, the rear end 14 of the output shaft 211 has the counter drive gear 21
The tubular hub 15 of No. 3 is spline-fitted. The cylindrical hub 15 extends forward, and the transmission case 1
Inside the center support 17 formed integrally with 6,
They are supported via tapered roller bearings 18 and 19, respectively. A sun gear shaft 212 is rotatably fitted on the outer side of the output shaft 211 on the distal end side via bearings 21 and 22.

In the counter driven gear 252 of the second underdrive transmission 250 that meshes with the counter drive gear 213, the cylindrical hub 23 at the center thereof is supported by the center support 17 via the roller bearing 24, and the second underdrive gear 252 is supported. The rear end 25 of the input shaft 251 of the drive transmission 250 is spline-fitted into the cylindrical hub 23. On the other hand, a flange-shaped protrusion 26 is formed at the tip of the input shaft 251 of the second underdrive transmission 250, and is supported by the transmission case 16 via a roller bearing (not shown). Between the roller bearing of the input shaft 251 and the flange-shaped projection 26, a pair of tapered roller bearings 27 are provided to connect the output gear 2 to each other.
55 is supported, and the output gear 255 meshes with the drive gear 271 of the differential gear 270 (see FIG. 2).

A cylindrical sun gear shaft 253 is rotatably supported between the flange-shaped projection 26 of the input shaft 251 and the center support 17 via bearings 31 and 32, and is provided outside the center support 17. The cylindrical inner race shaft 33 is rotatably supported via bearings 34 and 35, and the outer rear end of the sun gear shaft 253 and the inner front end of the inner race shaft 33 are spline-fitted.

In the automatic transmission having the above structure,
The drum 226 that opens to the rear is the front center support.
It is rotatably fitted to the seat 11 and has an annular shape between its inner and outer peripheral walls.
Piston 36 is fitted and clutch C₂Hydraulic servo
And the return spring 3 on the inner wall side.
7. Clutch C inside the outer wall₂Is installed. That
Therefore, inside the drum 226, there is a rear opening.
Hydraulic servo drum 39 having an annular projection 38 on the front of the peach
Is fixed to the rear end 40 of the output shaft 101, and the rear end 40
The annular piston 41 is fitted at the ends of the
Touch C₁Hydraulic servo of the
Turn spring 9, clutch C inside the outer wall₁Is dressed
Be worn. A clutch is provided on the outer circumference of the annular protrusion 38.
C ₂Is attached to the clutch C₂Through the drum 226
And a hydraulic servo drum 39 are connected.

A first planetary gear set 220 is provided on the rear side of the hydraulic servo drum 39, a ring gear 222 thereof is connected to the hydraulic servo drum 39 via a clutch C ₁ , and a carrier 224 of the output shaft 211. The sun gear 223 is integrated with the sun gear shaft 212 by spline fitting at the tip. Also, the drum 226
The rear end is connected to the sun gear shaft 212 on the rear side of the first planetary gear set 220, and the band brake B ₁ is provided on the outer peripheral side.

An annular hydraulic servo drum 42, which opens rearward, is fixed to an extra space outside the first planetary gear set 220 and the drum 226, and a piston 43 is fitted therein to form a hydraulic servo of the brake B ₂ . The spline 44 formed inside the transmission case 16 on the rear side of the hydraulic servo includes a brake B from the front.
_{The second} brake disc 45, the one-way clutch F ₂ outer race 46, and the brake B ₃ brake disc 47 are spline-fitted. Also, the rear side of the center support 17 and the transmission case 16
The piston 48 is fitted in the annular hole between the brake B
A hydraulic servo ₃ is formed, and a return spring 49 of the hydraulic servo is supported by a flange plate attached to the tip of the center support 17.

A one-way clutch F ₁ having an inner race on the sun gear shaft 212 is provided inside the brake B ₂ , an outer race 50 is connected to the brake B _2, and a _second clutch is provided on the rear side of the _one- way clutch F ₁ . A planetary gear set 230 is attached. In the second planetary gear set 230, the sun gear 232 is formed integrally with the sun gear shaft 212, the carrier 233 is connected to the inner race 51 of the outer one-way clutch F _{2 and} the brake B _3, and the ring gear 231 is connected to the ring gear 231. It is connected to the output shaft 211 via the flange 52.

In addition, the second underdrive transmission 250
At the rear end of the output gear 255, a large-diameter flange plate-shaped parking gear 257 is fixed. A third planetary gear set 260 is provided behind the output gear 255, and the ring gear 261 of the third planetary gear set 260 is connected to the input shaft 25.
1 is coupled to the protrusion 26 of the first gear via the ring gear flange 53, the carrier 263 is coupled to the parking gear 257 via the drum 258, and the sun gear 262 is coupled to the sun gear shaft 2.
53 is formed.

Then, the third planetary gear set 26
On the rear side of 0, a hydraulic servo drum 54 opening to the front is fixed to the inner race shaft 33, and an annular piston 55 is fitted between the outer peripheral shaft and the inner race shaft 33 to form a hydraulic servo of the clutch C _3. At the same time, a return spring 8 is mounted on the inner race shaft 33 side, and a clutch C ₃ is mounted inside the outer peripheral wall, and is connected to the carrier 263 via the clutch C ₃ .

A one-way clutch F ₃ having an inner race shaft 33 as an inner race is provided behind the hydraulic servo drum 54, and a brake B ₄ is provided behind the one-way clutch F ₃ between the inner race shaft 33 and the transmission case 16. piston 56 forms a hydraulic servo of the brake B ₄ is fitted in an annular hole between the outer peripheral side and the transmission case 16 side of the center support 17, a return spring in a groove provided at equal intervals on the outer peripheral side of the brake B ₄ 57 is fitted.

Next, the support state of the counter drive gear 213 will be described. In FIG. 4, the counter drive gear 213 is a counter driven gear 252 (see FIG.
(Refer to FIG. 3), the output shaft 211 is a rotating shaft of the counter drive gear 213 because it is meshed in a helical shape.
Thrust force is applied to. Therefore, the tubular hub 15 that is spline-fitted to the output shaft 211 has two sets of tapered roller bearings 1 for the center support 17.
It is supported via 8 and 19.

The two sets of tapered roller bearings 18 and 19 have a common outer race 61 and two inner races 62 and 63. The outer race 61 is positioned on the center support 17 by a snap ring 64 and a tapered snap ring 65 arranged on the outer circumference. The rear end surface of the inner race 62 contacts the annular portion 66 of the counter drive gear 213, and the front end surface of the inner race 63 contacts the ring gear flange 52 for positioning.

The output shaft 2 is provided on the inner peripheral side of the cylindrical hub 15.
The rear end 14 of 11 is spline-fitted by the spline fitting portions 67 and 68. Further, on the rear end 14 of the output shaft 211, a projection 69 having a thread formed on the outer periphery is formed, and a nut 70 is arranged so as to mesh with the screw of the projection 69, and the nut 70 is rotated. As a result, the preload can be adjusted by increasing or decreasing the distance between the ring gear flange 52 and the annular portion 66.

Next, a method and apparatus for mounting the counter drive gear support structure having the above-mentioned structure on the center support 17 of the transmission case 16 will be described. In FIG. 1, reference numeral 71 is a counter drive gear subassembly, which comprises a counter drive gear 213 and tapered roller bearings 18 and 19. In the counter drive gear subassembly 71, first, the inner race 62 is press-fitted into the tubular hub 15 of the counter drive gear 213, the outer race 61 is attached via the roller portion, and then the inner race 63 is attached to the tubular hub 15. It is formed by press fitting into.

A groove 72 for attaching the snap ring 64 is formed on the outer race 61 side on the inner race 62 side, and a groove 73 for attaching the tapered snap ring 65 (see FIG. 4) is formed on the inner race 63 side. However, when the counter drive gear sub-assembly 71 is assembled, only the snap ring 64 is attached. A plurality of jig insertion holes 75 are formed in the annular portion 66 of the counter drive gear 213.

The jig insertion hole 75 is formed in the outer race 61 in the radial direction of the counter drive gear 213.
Of the counter drive gear 213 at a position facing the end face of the counter drive gear 213 at equal intervals in the circumferential direction. The jig insertion hole 75 has a diameter larger than the radial dimension of the end surface of the outer race 61.

By the way, the counter drive gear 21
3 is to form a mold by forging the material,
After that, the mold is drilled to form the jig insertion hole 75, and the gear cutting process is performed to form the helical teeth. Then, after that, heat treatment is performed by carburizing and quenching, but strain occurs during this heat treatment. However, since the jig insertion hole 75 is formed in the vicinity of the center of the annular portion 66, it is not affected by the strain due to the heat treatment.

Reference numeral 76 is a jig for press-fitting the counter drive gear subassembly 71 into the transmission case 16. The jig 76 is the jig insertion hole 7
The same number of rods 77 are provided at the positions corresponding to 5. The rod 77 penetrates the jig insertion hole 75 and is brought into contact with the end surface of the outer race 61 when the counter drive gear subassembly 71 is press-fitted. And
When the rod 77 is pushed downward in the figure, the outer race 61 is press-fitted along the inner peripheral surface 78 of the center support 17 of the transmission case 16.

When the end surface of the center support 17 comes into contact with the snap ring 64, the rod 77 is pressed.
The work is completed by stopping the pushing down of the tape and mounting the tapered snap ring 65 (see FIG. 4) in the groove 73. Reference numeral 79 is a jig for fixing the lower end surface of the center support 17, and 80 is a support member for supporting the end surface of the tubular hub 15 of the counter drive gear 213.

The present invention is not limited to the above embodiments, but various modifications can be made based on the spirit of the present invention, and they are not excluded from the scope of the present invention.

[Brief description of drawings]

FIG. 1 is a state diagram when a counter drive gear support structure is assembled to a transmission case in an automatic transmission according to the present invention.

FIG. 2 is a schematic diagram of an automatic transmission according to the present invention.

FIG. 3 is a sectional view of an essential part of the automatic transmission according to the present invention.

FIG. 4 is a diagram showing a counter drive gear mounting state of the automatic transmission according to the present invention.

[Explanation of symbols]

 15 Cylindrical hub 16 Transmission case 17 Center support 18, 19 Tapered roller bearing 61 Outer race 62, 63 Inner race 64 Snap ring 66 Annular portion 71 Counter drive gear subassembly 72, 73 Groove 75 Jig insertion hole 76, 79 Jig 77 Rod 78 Inner peripheral surface 80 Support member 213 Counter drive gear

 ─────────────────────────────────────────────────── --- Continuation of the front page (72) Inventor Takehito Kano 10 Takane, Fujii-cho, Anjo City, Aichi Prefecture Aisin AW Co., Ltd. (72) Fumitomo Yokoyama 10 Takane, Fujii-cho, Anjo City, Aichi Prefecture Aisin AW Co., Ltd. (72) Inventor Atsushi Honda Atsushi Toyota, Aichi Prefecture 1 Toyota Town, Toyota Motor Co., Ltd. (72) Inventor Tatsuo Kushima 1 Toyota Town, Aichi Prefecture Toyota Motor Corporation Stock Company (72) Inventor Takeji Koide 1 Toyota-cho, Toyota-shi, Aichi Toyota Motor Co., Ltd.

Claims (1)

[Claims] 1. A gear comprising an annular portion having teeth cut off on its outer periphery and a cylindrical hub formed on the inner peripheral side of the annular portion, and two inner races press-fitted to the outer periphery of the cylindrical hub. And two sets of tapered roller bearings, which are provided corresponding to the inner races and whose outer circumferences are press-fitted into the shaft supporting portion of the transmission case, and which are formed by one outer race, and the annular portion of the gear has an annular portion. An automatic transmission characterized in that a plurality of jig insertion holes are penetratingly formed at positions corresponding to the end faces of the outer race.