JPH0127298B2 - - Google Patents

Description

[Detailed description of the invention]

[Industrial Field of Application] The present invention relates to a gear transmission for an automatic transmission. [Prior Art] Conventionally, in a gear transmission device for an automatic transmission, there is no uneven contact with the gears of the planetary gear set.
It is well known that helical gears are used for reasons such as excellent quietness, but thrust loads are generated in helical gears during transmission. Therefore, many thrust bearings have been used in gear transmissions to support the thrust load. Furthermore, in front-engine, front-drive (FF) type automobiles, transmission between the gear transmission and the differential is performed via an output gear provided on the output shaft of the gear transmission. Helical gears were used to ensure smooth transmission. [Problems to be solved by the invention] In this type of gear transmission, the output gear generates a large thrust during transmission, so the tapered roller bearing that supports the output gear requires a large bearing with high thrust resistance. ,
The durability of this bearing has been a problem. By using the inner race of the tapered roller bearing, the present invention can reliably reduce the thrust force acting on the tapered roller bearing, improve the durability of the bearing, and
It is an object of the present invention to provide a gear transmission device for an automatic transmission that allows the use of smaller tapered roller bearings or ball bearings than conventional ones. [Means for Solving the Problems] A gear transmission device for an automatic transmission according to the present invention includes a torque converter 1 and an output shaft 7 of the torque converter.
A gear transmission mechanism 2 consisting of two sets of planetary gear mechanisms 23 and 24 formed of helical gears and a plurality of frictional engagement elements C1, C2, C3, B1, B3 arranged concentrically in and an output shaft 9 of the gear transmission mechanism disposed concentrically with the output shaft of the torque converter, and the output shaft of the torque converter is attached to and detached from the sun gear 231 of the first planetary gear mechanism 23 via the first clutch C1. The ring gear 233 of the first planetary gear mechanism and the carrier 241 of the second planetary gear mechanism 24 are detachably connected via the second clutch C2, and the Sun gear 24 of the 2nd planetary gear mechanism
3, the output shaft of the gear transmission mechanism is connected to the carrier 232 of the first planetary gear mechanism and the ring gear 242 of the second planetary gear mechanism, and the sun gear 243 of the second planetary gear mechanism 1st
The carrier 241 of the second planetary gear mechanism is selectively fixed to the transmission case 6 via a second brake B3,
The output shaft has an output gear 91 formed of a helical gear at the torque converter side end, and a pair of tapered roller bearings 9 at both ends of the output gear.
2 and 93, and is supported by the transmission case 5 via the bearing 9 in the axial direction.
The ring gear 242 of the second planetary gear mechanism is in contact with the inner race 921 of the ring gear flange 2.
The ring gear flange 245 is spline-fitted to the output shaft 9 via the ring gear flange 245, and the torque converter side end of the ring gear flange 245 abuts the inner race 921 of the bearing 92 disposed between the ring gear flange 245 and the output gear 91 in the axial direction. , ring gear 2 of the first planetary gear mechanism
33 is a shaft 26 connected to the carrier 241 of the second planetary gear mechanism via a ring gear flange 235.
The end of the shaft 26 on the torque converter side is fitted with a thrust bearing 264.
axially contacts the opposite end of the ring gear flange 245 from the torque converter, and acts on the ring gears 233, 242 of the first and second planetary gear mechanisms in the forward driving state of the automatic transmission. It is characterized in that the thrust force and the thrust force acting on the output gear 91 are configured to act against the inner race 921 of the bearing 92. [Operation and Effects of the Invention] In the present invention, in the first speed and third speed states of the automatic transmission, the ring gear 2 of the first planetary gear mechanism
The thrust force of 33 is applied to the ring gear flange 235,
The inner race 921 of the tapered roller bearing 92 acts on the inner race 921 of the tapered roller bearing 92 through the shaft 26, the thrust bearing 264, and the ring gear flange 245.
This cancels out the thrust force of the output gear 91 acting on the output gear 91. In the second speed state of the automatic transmission, the thrust force of the ring gear 233 of the first planetary gear mechanism is applied to the ring gear flange 235, the shaft 26, and the thrust bearing 2.
64, inner race 921 of tapered roller bearing 92 via ring gear flange 245
At the same time, the thrust force of the ring gear 242 of the second planetary gear mechanism is applied to the tapered roller bearing 92 via the ring gear flange 245.
The thrust force of the output gear 91 acts on the inner race 921 of the tapered roller bearing 92 and cancels it out. In the fourth speed state of the automatic transmission, the thrust force of the ring gear 242 of the second planetary gear mechanism acts on the inner race 921 of the tapered roller bearing 92 via the ring gear flange 245. 92
This cancels out the thrust force of the output gear 91 acting on the output gear 1. In this way, in the forward driving state of the automatic transmission, the ring gears 233 of the first and second planetary gear mechanisms,
242 is configured so that the thrust force generated in the output gear 91 and the inner race 921 of the bearing 92 cancel each other out, so that the thrust force acting on the bearing 92 supporting the output gear is always equal to Since the thrust force acting on the ring gears 233 and 242 of the second planetary gear mechanism can be reduced by the amount corresponding to the thrust force, the durability of the bearing 92 is improved and it is possible to use a smaller tapered roller bearing or ball bearing than before. It has the effect of being able to. [Example] The present invention will be explained based on an example shown in the drawings. FIG. 1 shows a front engine, front drive automatic transmission equipped with a gear transmission 2 having four forward speeds and one reverse speed according to the present invention. The torque converter 1 is installed in a torque converter case 5 whose front side (engine side) is open, and the gear transmission 2 is housed in a transmission case 6 connected to the rear end 5A of the torque converter case 5. . At the rear of the torque converter case 5, an output gear room 51 that holds the output gear 91 of the gear transmission 2 is provided in the center, and a governor room 53 that houses the governor hydraulic pressure generating mechanism 11 is formed outside of the output gear room 51, and the torque converter A differential gear room 54 is formed on the side of the case 5. A deceleration mechanism room 52 is formed between the output gear room 51 and the differential device room 54 and holds the deceleration mechanism 4 that connects the output gear 91 and the differential device 3. The rear end of the transmission case 6 is closed with a rear cover 60, and an oil pump cover 61 housing an oil pump 12 is fastened to the outer surface of the rear cover 60. The transmission case 6 has an intermediate support wall 63 provided with a cylindrical center support 62 at its center, and a rear center support 64 having a coaxial center with the center support 62 is formed at the center of the rear cover 60. ing. At the center of the torque converter case 5 and transmission case 6 is a front cover 1 at the front.
3, a drive shaft 8 that is supported by a rear center support 64 at the rear, projects rearward, and is connected to the oil pump 12.
is provided, and a hollow cylindrical input shaft of the gear transmission 2 and an output shaft 7 of the torque converter is provided coaxially therewith. Furthermore, an output shaft 9 of the gear transmission 2 is provided outside the gear transmission 2, which is hollow and has an output gear 91 formed at its tip, a first intermediate shaft 26 is provided outside the output shaft 9, and a second intermediate shaft 27 is provided outside the output shaft 9. ing. The hydraulic torque converter 1 with a direct coupling clutch has a known configuration, and includes a pump impeller 14 connected to an engine output shaft via a front cover 13;
A turbine runner 1 connected to the output shaft 7 of the hollow torque converter via a turbine hub 15
6. The stator 18 is engaged with a fixed part via a one-way brake 17, and the direct coupling clutch 19 is connected to the turbine hub. The gear transmission 2 of the automatic transmission of this embodiment includes a first planetary gear set 23 disposed at the rear of the intermediate support wall 63, and a second planetary gear set 23 disposed at the front of the intermediate support wall 63. set 24 and three multi-disc clutches C1, C2, C3 operated by hydraulic servos to connect and engage or disengage the elements of each planetary gear set, three multi-disc brakes B1,
B2, B3, one one-way clutch F0, and two one-way brakes F1, F2. The output shaft 7 of the torque converter, which is the input shaft of the gear transmission 2, is pivotally supported by a rear center support 64 at its rear end, and rotatably fitted onto the rear center support 64 near its rear end. Annular hydraulic servo rear drum 25
is fitted with a spline. The rear drum 25 for hydraulic servo is open at the front and has an intermediate cylinder wall 25.
1, and an annular piston 254 is fitted between the intermediate cylinder wall 251 and an inner circumferential wall 252 externally fitted on the rear center support 64 to form an annular hydraulic servo c1 of the clutch C1. wall 251
An annular piston 255 is fitted between the clutch C2 and the outer peripheral wall 253 to form a hydraulic servo c2 of the clutch C2. The first planetary gear set 23 includes a sun gear 231 connected to the rear drum 25 via a multi-plate clutch C1 formed in the intermediate cylinder wall of the drum, and a sun gear 231 disposed coaxially outside the input shaft 7. A carrier 232 spline-fitted to the output shaft 9 of the gear transmission 2 is connected to the rear drum 25 via a multi-plate clutch C2 formed in the outer peripheral wall of the drum 25, and is coaxially connected to the outside of the output shaft 9. A link gear 233 is spline-fitted to a hollow first intermediate shaft 26 of a gear transmission arranged in a shape, and a planetary gear 234 is rotatably supported by a carrier 232 and meshed with a sun gear 231 and a ring gear 233. It consists of. An annular cylinder 631 is formed on the front surface of the intermediate support wall 63, and an annular piston 632 is fitted into the hydraulic cylinder 631 to form a hydraulic servo b3 for operating the brake B3.
An annular protrusion 633 is formed on the rear surface of 3, and an annular cylinder 634 is provided outside the annular protrusion 633, and an annular piston 635 is fitted thereinto to form a hydraulic servo b1 for operating the brake B1. An annular cylinder 6 is provided inside the protrusion.
36 is formed, and an annular piston 637 is fitted therein to form a hydraulic servo b2 for operating the brake B2. The second planetary gear set 24 includes the first planetary gear set 24.
A carrier 241 is fixed to the outer race of the one-way brake F2, which is connected to the intermediate shaft 26 of the engine and engages the transmission case 6 via the brake B3, a ring gear 242 spline-fitted to the output shaft 9, and a first A sun gear 243 is formed integrally with the second intermediate shaft 27 which is rotatably supported between the intermediate shaft 26 and the center support 62, and is rotatably supported by the carrier 241 and between the sun gear 243 and the ring gear 242. It consists of a planetary gear 244 in mesh with each other. The one-way brake F2 has an inner race spline-fitted and fixed to the outer periphery of the center support 62, and is disposed inside the brake B3. An inner race f1 of a one-way clutch F0 is spline-fitted to the rear end of the second intermediate shaft 27, and an inner race f2 of a one-way brake F1 is rotatably fitted to the rear end of the center support 62.
A common inner race 29 is formed integrally with the common inner race 29. A rotating front drum 28 consisting of a front small diameter section 281 and a rear large diameter section 282 extending from the small diameter section 281 is welded to the common inner race 29 at the tip side wall of the small diameter section 281 . The stepped annular cylinder 223 formed by the front drum 28 and the common inner race 29 has a small diameter portion 284 and a large diameter portion 2 corresponding to the shape of the annular cylinder 223.
A piston 283 consisting of 85 is fitted to constitute a hydraulic servo c3, and is connected to a hub 80 integrally formed with the outer race of the one-way clutch F0 via a multi-plate clutch C3 formed within the front drum 28. The front drum 28 is engaged. The outer race of the one-way clutch F0 is connected to the hub 8.
0 and is spline fitted to the rear drum 25.
The input shaft 7 is also connected to the input shaft 7 via a connecting ring 20 that is spline-fitted to the input shaft 7. front drum 28
is engaged with the transmission case 6 via the brake B1, and the outer race of the one-way brake F1 is engaged with the transmission case 6 via the brake B2. One-way clutch F
0 is formed inside the clutch C3, and the one-way brake F1 is formed inside the brake B2. The drive shaft 8 is inserted into the output shaft 7 of the torque converter 1 and is spline-fitted into an inner hole 102 in a protrusion 101 formed at the center of the torque converter front cover 13. The section is pivotally supported by a rear center support 64, and a gear 110 is spline-fitted to the rear end.
The gear drives the oil pump 12 inside the oil pump cover 61. The output gear 91 is formed integrally with the output shaft 9 at the tip of the output shaft 9 of the gear transmission, and is connected to the output gear loom 5 by a pair of tapered roller bearings 92 and 93.
It is rotatably supported within 1. The speed reduction mechanism 4 includes a support shaft 41 mounted in a reduction gear room 52 in parallel with the output shaft 9 of the gear transmission, and a pair of tapered roller bearings 42, 4.
The output gear 91 includes a reduction gear 44 supported by the support shaft 41 via the support shaft 3 and meshing with the output gear 91. The reduction gear 44 meshes with the large drive gear 31, where deceleration is achieved and the wheel axle 3 is
4,35 is driven. The governor oil pressure generating mechanism 11, which has the governor valve 50 as its main part, has a cylindrical portion 246 that projects forward from the ring gear 242 of the second planetary gear set.
A gear 247 is formed on the outer periphery of the vehicle, the gear and the drive gear 501 mesh with each other, and a rotating part 502 connected to the drive gear rotates to supply governor pressure according to the vehicle speed to the hydraulic control device 10. . The operation of the clutch, brake, one-way clutch, and one-way brake of this gear transmission 2 and the gears and reduction ratios achieved are shown in the table.

[Table] In the table, ○ indicates engagement, × indicates disengagement, and △ indicates that engine braking action can be obtained by engagement. FIG. 2 particularly shows a gear transmission constructed to cancel the thrust force generated by the planetary gear set and the thrust force generated by the output gear, which is the gist of the present invention. Ring gear 2 of second planetary gear set 24
42 is a hub portion 248 having a spline formed on its inner periphery via a flange portion 245, and is spline-fitted to the output shaft 9. The right end surface of the hub portion 248 of the ring gear 242 in the drawing is in direct contact with one end surface of the inner race 921 of the tapered roller bearing 92. The other end surface of the inner race 921 of the tapered roller bearing 92 is placed in contact with one end surface of the output gear 91. Ring gear 2 of first planetary gear set 23
33 is a hub portion 236 having a spline formed on the inner circumference via a flange portion 235, and a hub portion 236 is connected to the first intermediate shaft 2 through a flange portion 235.
It is spline fitted to one end 260 of 6. The right end surface of the hub portion 236 of the ring gear 233 is the first
It is disposed in contact with a snap ring 262 fitted into a circumferential groove 261 formed in the intermediate shaft 26 of. The other end 263 of the first intermediate shaft 26 rotatably contacts the hub portion 248 of the ring gear 242 of the second planetary gear set 24 via a thrust bearing 264. The twisting direction and twisting angle of the teeth of the output gear 91 are set so as to generate a thrust to the left in the figure as indicated by an arrow F in the case of an engine drive. Next, the operation of this embodiment will be explained. In the case of engine drive, in the first gear, the torque transmitted from the turbine 16 of the torque converter 1 via the output shaft 7 of the torque converter (input shaft of the gear transmission) is transmitted from the sun gear 231 of the first planetary gear set 23. is input. In this case, transmission is provided by the first planetary gearset 23. At this time, the first planetary gear set 2
The twist direction and twist angle of the teeth of each gear 3 are set so that the ring gear 233 applies a thrust force to the right in the figure as indicated by arrow B. Thrust force B is applied to the snap spring 262, the first
The output gear 91 acts on the inner race 921 of the tapered roller bearing 92 in the right direction in the figure through the intermediate shaft 26, the thrust bearing 264, and the hub portion 248 of the ring gear 242, and the output gear 91 acts on the inner race 921 of the tapered roller bearing 92 in the left direction in the figure. It cancels out the thrust force acting on the In the case of the second speed, transmission is performed through both the first and second planetary gear sets 23 and 24. At this time, the twist direction and twist angle of the teeth of each gear of the second planetary gear set 24 are determined by the ring gear 2.
42 is set so that a thrust force acts in the right direction in the figure as indicated by arrow A in the figure. ring gear 2
Thrust force B acting on 33 and ring gear 24
The thrust force A that acts on the inner race 921 of the tapered roller bearing 92 is applied to the inner race 921 of the tapered roller bearing 92 in the right direction in the drawing, and the output gear 91 cancels out the thrust force that acts on the inner race 921 of the tapered roller bearing 92 in the left direction in the drawing. In the case of the third speed, the same effect as in the case of the first speed is performed. In the case of the fourth speed, transmission is performed by the second planetary gear set 24. The thrust force A acting on the ring gear 242 acts on the inner race 921 of the tapered roller bearing 92 in the right direction in the drawing, and cancels out the thrust force that the output gear 91 acts on the inner race 921 of the tapered roller bearing 92 in the left direction in the drawing. . In this way, in the case of engine drive, the ring gears 233, 242 are
The thrust force acting on the output gear 91 and the thrust force acting on the inner race 921 of the tapered roller bearing 92 cancel each other out. In addition, in the case of engine braking for reverse and forward travel, the thrust force acting on the ring gears 233 and 242 is in the opposite direction, and the thrust force acting on the tapered roller bearing 92 is not reduced, but in the case of reverse travel, the usage time is extremely long. Because it is short, and because the input torque for forward engine braking is smaller than for engine drive, its influence is small and does not pose a problem.

[Brief explanation of drawings]

FIG. 1 is a sectional view of an automatic transmission equipped with a gear transmission according to the present invention, and FIG. 2 is a sectional view of the main parts thereof. In the figure 2...Gear transmission, 7...Input shaft of gear transmission, 9...Output shaft of gear transmission, 23...First
Planetary gear set, 24... Second planetary gear set, 26... First intermediate shaft, 91... Output gear,
92...Taper roller bearing, 921...Inner race, 264...Thrust bearing, 23
3,242...Ring gear.

Claims (1)

[Claims] 1. A torque converter, a gear transmission mechanism consisting of two sets of planetary gear mechanisms formed of helical gears arranged concentrically on the output shaft of the torque converter, and a plurality of frictional engagement elements, and an output of the torque converter. an output shaft of the gear transmission mechanism disposed concentrically with the shaft, the output shaft of the torque converter is removably connected to the sun gear of the first planetary gear mechanism via a first clutch; The ring gear is detachably connected to the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism via the second clutch, and is detachably connected to the sun gear of the second planetary gear mechanism via the third clutch. connected, the output shaft of the gear transmission mechanism is connected to a carrier of a first planetary gear mechanism and a ring gear of a second planetary gear mechanism,
The sun gear of the second planetary gear set is selectively secured to the transmission case via the first brake, and the carrier of the second planetary gear set is selectively secured to the transmission case via the second brake. The output shaft has an output gear formed of a helical gear on the side end of the torque converter, and is supported by the transmission case via a pair of tapered roller bearings at both ends of the output gear. The ring gear of the second planetary gear mechanism is spline-fitted to the output shaft via the ring gear flange, and the torque converter side end of the ring gear flange is in contact with the output gear. The ring gear of the first planetary gear mechanism is spline-fitted to a shaft connected to the carrier of the second planetary gear mechanism via a ring gear flange, and is in axial contact with the inner race of the bearing disposed between the ring gear and the ring gear of the first planetary gear mechanism. At the same time, the end of the shaft on the torque converter side contacts the end of the ring gear flange opposite to the torque converter in the axial direction via a thrust bearing, and when the automatic transmission is in the forward driving state,
A gear transmission device for an automatic transmission, characterized in that a thrust force acting on a ring gear of a planetary gear mechanism and a thrust force acting on an output gear are configured to act against an inner race of a bearing.