JP2821016B2 - Carrier device for automatic transmission - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a carrier device in an automatic transmission.

(Prior art) Conventionally, an FF (front engine / front drive) in which an underdrive mechanism is disposed on a counter shaft
The underdrive mechanism has a planetary gear, and the carrier cover of the planetary gear is formed with an oil hole that directly communicates with an oil hole in the shaft, and a lubricating oil is formed on the support surface of the pinion. Is supplied.

FIG. 5 is a sectional view of a carrier device in a conventional automatic transmission (see Japanese Patent Application Laid-Open No. 2-51647).

As shown in the figure, the underdrive mechanism 3 has one planetary gear 1. Further, a counter driven gear 13 is rotatably supported on the counter shaft 2 via a bearing 75.
The reduction gear 35 is fixed above. The counter shaft 2 is rotatably supported at both ends by bearings 86 and 92, and is installed in the transaxle case 40.

On the other hand, the ring gear R3 of the planetary gear 1 is connected to the counter driven gear 13, and the carrier CR3 supporting the pinion gear P3 is formed integrally by bulging the counter shaft 2 in the outer diameter direction.

Further, the sun gear S3 is formed on a hub 17 rotatably supported on the counter shaft 2 by thrust bearings 15, 16 and bushes 83, 85, and a drum 77 fixed to an outer diameter portion of the hub 17 has a sun gear S3. A fourth brake B4 composed of a band brake is engaged with the outer peripheral surface. In addition, a third clutch C3 composed of multiple plates is interposed between the inner peripheral surface of the drum 77 and the hub 78 fixed to the carrier CR3, and further connected to the hub 17 adjacent to the clutch C3. Constitutes a hydraulic actuator 79 for the clutch C3 with the piston member 76 fitted in an oil-tight manner. Further, the piston member 76 is provided with a check valve 88 for eliminating centrifugal oil pressure during rotation. A spring 74 is contracted between the piston member 76 and the ring 82 fixed to the hub 17, and serves as a return spring for the piston member 76.

Also, a boss 40 is provided at the end of the transaxle case 40.
b is formed on the boss portion 40b.
The countershaft 2 is rotatably supported via the. Further, a lubrication hole is provided at the center of the counter shaft 2.
2c are formed, lateral holes 2d, 2f, 2g, 2h, 2i are formed in the radial direction of the countershaft 2, and a plug 18 is attached to the tip of the lubrication hole 2c. The lubricating oil supplied to the hole 2c appropriately lubricates various places.

An extended portion of the hub 17 is fitted on the outer peripheral surface of the boss portion 40b, and the extended portion constitutes an inner race of the third one-way clutch F3. And a transaxle case 40.

Further, an oil passage 17c formed in the hub 17 is connected to the one-way clutch F3, and the one-way clutch F3 is appropriately lubricated with lubricating oil supplied from the lateral hole 2d. A rear cover 42 is fixed to the side surface of the trunk axle case 40 by bolts. Inside the rear cover 42, a pipe 89 for supplying hydraulic pressure from a valve body is installed. The pipe 89 is provided via an oil passage 40c formed in the boss portion 40b, an oil hole 40d, an annular oil groove hole 17a formed in the hub 17, and an oil passage 17b extending obliquely from the oil bottom portion. It is configured to supply oil pressure to the oil chamber of the hydraulic actuator 79.

The carrier CR3 has a carrier cover 6, and the carrier cover 6 is formed integrally with the countershaft 2 by hot forging. The countershaft 2 is configured such that the planetary gear unit 1 has a small-diameter portion 2a and the opposite side has a large-diameter portion 2b with the carrier cover 6 as a boundary, and the planetary gear unit 1 is disposed on the small-diameter portion 2a. Radial dimensions are reduced. Further, a pinion shaft 5 is directly fixed to the carrier cover 6, a lubricating oil hole 5 b is formed in the center of the pinion shaft 5, and an end of the pinion shaft 5 on the side of the carrier cover 6 is provided. Lubricating oil holes 5a are formed in the radial direction.

A plug 5c is attached to the end of the lubricating oil hole 5b to prevent leakage of the lubricating oil. The lubricating oil hole 5a is formed by a lubricating oil formed in the carrier cover 6.
6a, and the lubricating oil hole 6a is
Is directly connected to a lubrication hole 2c formed in the center of the lubrication device.

(Problems to be Solved by the Invention) However, in the carrier device of the automatic transmission having the above configuration, the torque transmission capacity cannot be improved.

That is, when transmitting torque from the main transmission mechanism section 11 to the front differential device 29 via the under drive mechanism section 3, the countershaft 2 receives the stress from the main transmission mechanism section 11 and the front differential device.
Deflection occurs due to the reaction force from 29. In order to reduce the deflection, it is necessary to increase the diameter of the countershaft 2. However, as described above, the countershaft 2 is formed with the small-diameter portion 2a for convenience of disposing the planetary gear unit 1.

Therefore, in order to reduce the deflection of the counter shaft 2, it is desirable to make the diameter of the small diameter portion 2a equal to the diameter of the large diameter portion 2b as much as possible without changing the position of the planetary gear unit 1.

However, a thrust bearing 15 is provided between the pinion gear P3 of the planetary gear unit 1 and the small-diameter portion 2a. If the diameter of the small-diameter portion 2a is increased, the thrust bearing 15 and the pinion gear P3 may interfere with each other.

Therefore, if the thickness of the carrier cover 6 is increased and a recess is formed in the carrier cover 6 to accommodate the thrust bearing 15, the interference can be prevented. However, stress concentration occurs in the recess. Counter shaft 2
The strength of the material is reduced. Further, since the lubricating oil holes 6a are formed in the carrier cover 6, the carrier cover 6
For the heat treatment of the part, induction hardening is performed instead of carburizing and quenching. However, if a concave portion is formed in the carrier cover 6, the induction hardening process cannot be performed.

The present invention solves the problems of the carrier device in the conventional automatic transmission, improves the strength of the base portion of the carrier cover without causing interference between the planetary gear unit and the thrust bearing, and improves the torque transmission capacity. It is an object of the present invention to provide a carrier device for an automatic transmission that can increase the power consumption.

(Means for Solving the Problems) For this purpose, in the carrier device of the automatic transmission according to the present invention, an annular carrier cover is integrally formed, and a small-diameter portion is provided on one side of the carrier cover with a large-diameter portion on the other side. A shaft having a diameter portion, a sun gear rotatably supported by the small diameter portion via a support member, a pinion gear meshing with the sun gear, a ring gear meshing with the pinion gear, and fixed to the carrier cover; A pinion shaft that rotatably supports the pinion gear, an annular recess formed in a portion of the carrier cover that comes into contact with the sun gear, and a thrust accommodated in the annular recess and supporting a thrust load between the carrier cover and the sun gear. A bearing, a lubrication hole formed at the center of the shaft, and a radial hole formed in the shaft. A first lateral hole communicating the lubricating hole with the outer peripheral side of the shaft, a lubricating oil hole formed in the pinion shaft for supplying lubricating oil to the planetary gear unit, and supplying the lubricating hole to the outer peripheral side of the shaft. And a reservoir for guiding the lubricating oil into the lubricating oil hole of the pinion shaft.

In the carrier device for another automatic transmission according to the present invention, further, an oil chamber formed between the support member, the shaft and the sun gear, and a second lateral communicating the oil chamber with an outer peripheral side of the sun gear. And a hole.

The first lateral hole communicates between the oil chamber and a lubrication hole in the shaft, and the reservoir supplies the lubricating oil supplied from the oil chamber to an outer peripheral side of a sun gear through the pinion shaft. Guide into the lubricating oil hole.

(Operation and Effect of the Invention) According to the present invention, as described above, in the carrier device of the automatic transmission, the annular carrier cover is integrally formed, and the small diameter portion is formed on one side of the carrier cover with the other small diameter portion on the other side. A shaft having a large-diameter portion formed on the side thereof, a sun gear rotatably supported on the small-diameter portion via a support member,
A pinion gear meshing with the sun gear, a ring gear meshing with the pinion gear, a pinion shaft fixed to the carrier cover and rotatably supporting the pinion gear, and an annular recess formed at a portion of the carrier cover that abuts the sun gear; A thrust bearing housed in the annular recess and supporting a thrust load between the carrier cover and the sun gear; a lubrication hole formed at the center of the shaft; and a lubrication hole formed in a radial direction of the shaft. A first lateral hole communicating with the shaft and an outer peripheral side of the shaft; a lubricating oil hole formed in the pinion shaft for supplying lubricating oil to the planetary gear unit; and a lubricating oil supplied from the lubricating hole to the outer peripheral side of the shaft. And a reservoir for guiding the oil into the lubricating oil hole of the pinion shaft.

In this case, since the planetary gear unit is disposed in the small diameter portion, the outer diameter of the planetary gear unit can be reduced, and the size of the carrier device in the automatic transmission can be reduced.

Further, an annular concave portion is formed in a portion of the carrier cover that comes into contact with the sun gear, and a thrust bearing is housed in the annular concave portion. The bearing and the pinion gear do not interfere, and the capacity of the torque transmitted via the shaft can be increased.

Therefore, lubricating oil for lubricating the planetary gear unit is supplied from the lubrication hole of the shaft to the planetary gear unit through the lubricating oil hole of the shaft and the pinion shaft. It is not necessary to form an oil passage for use.

As a result, the strength of the shaft can be increased by carburizing and quenching. That is, since no oil passage for lubrication is formed in the carrier cover, it is not necessary to perform drilling after carburizing and quenching the shaft, so that drill breakage and the like do not occur.

In the carrier device for another automatic transmission according to the present invention, further, an oil chamber formed between the support member, the shaft and the sun gear, and a second lateral communicating the oil chamber with an outer peripheral side of the sun gear. And a hole.

The first lateral hole communicates between the oil chamber and a lubrication hole in the shaft, and the reservoir supplies the lubricating oil supplied from the oil chamber to an outer peripheral side of a sun gear through the pinion shaft. Guide into the lubricating oil hole.

In this case, lubricating oil for lubricating the planetary gear unit is supplied from the lubrication hole of the shaft to the planetary gear unit through the oil chamber, the second lateral hole, the outer peripheral side of the sun gear, and the lubrication oil hole of the pinion shaft. Therefore, there is no need to form an oil passage for lubrication in the carrier cover.

(Example) Hereinafter, an example of the present invention will be described in detail with reference to the drawings.

First, an automatic transmission to which the carrier device in the automatic transmission according to the present invention is applied will be described with reference to FIG.

FIG. 2 is a schematic view of an automatic transmission to which the carrier device in the automatic transmission according to the present invention is applied.

In the figure, the automatic transmission A has an input shaft 10, a counter shaft 2, and front axle shafts 23a and 23b aligned with an engine crankshaft 7, and a lock-up clutch 25 is provided on the input shaft 10. The torque converter 26 and the main transmission mechanism 11 are supported.
The underdrive mechanism 3 is supported on the upper side, and a front differential device 29 is supported on the front axle shafts 23a and 23b.

The main transmission mechanism section 11 has a planetary gear unit 32 formed by combining a single planetary gear 30 and a dual planetary gear 31, and the planetary gear unit 32 is composed of the sun gear S1 and the carrier of the two planetary gears.
CR1 is integrally connected, and sun gear S1 is arranged so as to mesh with long pinion P1.

The input shaft 10 and the ring gear R1 of the single planetary gear 30 are connected via a first clutch C1, and the input shaft 10 and the sun gear S1 are connected via a second clutch C2. Also, sun gear S1 is the first brake
While being directly locked by B1, rotation in one direction is prevented by the second brake B2 via the first one-way clutch F1.

Further, the ring gear R2 of the dual planetary gear 31 is directly locked by the third brake B3, and the rotation in one direction is prevented by the second one-way clutch F2. The carrier CR1 is connected to a counter drive gear 33 supported by a partition of the case, and the counter drive gear 33 is an output member of the main transmission mechanism 11.

The underdrive mechanism 3 has one single planetary gear 1, and the carrier CR3 of the planetary gear 1 and the sun gear S3 are connected via a third clutch C3. Further, the sun gear S3 is directly locked by the fourth brake B4, and rotation in one direction is prevented by the third one-way clutch F3.

And, the ring gear R3 is the counter drive gear 33
And is connected to a counter driven gear 13 serving as an input member of the under drive mechanism 3.
CR3 is connected to the counter shaft 2. further,
A reduction gear 35 serving as an output member of the underdrive mechanism 3 is fixed to the counter shaft 2.

Further, the front differential device 29 has a differential carrier 36 and left and right side gears 37a, 37b, and the differential carrier 36 serving as a gear mount case has a ring gear.
39 has been fixed. The ring gear 39 meshes with the reduction gear 35 to form a final reduction mechanism, and left and right side gears 37a and 37b are connected to left and right front axle shafts 23a and 23b, respectively.

Next, the operation of the automatic transmission will be described with reference to FIG.

FIG. 3 is a view showing the operation of the automatic transmission to which the carrier device in the automatic transmission according to the present invention is applied.

The rotation of the engine crankshaft 7 is transmitted to the input shaft 10 via the torque converter 26 or via the lock-up clutch 25. In the first speed state in the D range, the first clutch C1 is in the connected state, and the fourth brake B4 is in the engaged state. In this state, the rotation of the input shaft 10 is transmitted to the ring gear R1 of the single planetary gear 30 via the first clutch C1, and in this state, the ring gear R2 of the dual planetary gear 31 is connected to the second one-way clutch. Since the rotation is prevented by F2, the common carrier CR1 is largely decelerated and rotated in the forward direction while the sun gear S1 is idled in the reverse direction, and the rotation is taken out from the counter drive gear 33.

On the other hand, in the under drive mechanism 3, the sun gear S3 is locked by the fourth brake B4 and the third one-way clutch F3, and the rotation from the counter driven gear 13 is taken out from the ring gear R3 to the carrier CR3 as decelerated rotation.

Therefore, the first-speed rotation of the main transmission mechanism 11 and the reduced rotation of the underdrive mechanism 3 are combined, and the resulting rotation is transmitted to the front differential device 29 via the reduction gear 35 and the ring gear 39, and is further To the front axle shafts 23a and 23b.

In the second speed state in the D range, the second brake B2 operates in addition to the connection of the first clutch C1 and the operation of the fourth brake B4. At this time, the rotation of the sun gear S1 is stopped by the operation of the first one-way clutch F1 based on the brake B2, and the rotation transmitted from the input shaft 10 to the ring gear R1 via the first clutch C1 is applied to the dual planetary gear 31. The carrier CR1 is decelerated and rotated in the forward direction while the ring gear R2 idles in the forward direction, and the rotation is taken out by the counter drive gear 33 as the second speed. At this time, the underdrive mechanism 3 remains in the decelerated state, and the combined rotation of the second speed of the main transmission mechanism 11 and the reduced rotation of the underdrive mechanism 3 is transmitted to the front axle shafts 23a and 23b. .

In the third speed state in the D range, the main transmission mechanism section 11 maintains the second speed state as it is, releases the fourth brake B4 in the underdrive mechanism section 3, and engages the third clutch C3. At this time, the carrier CR3 and the sun gear S3 are integrated, the planetary gear 1 rotates integrally, and the directly connected rotation is taken out to the counter shaft 2.

At this time, since the fourth brake B4 is released before the third clutch C3 is engaged, the third one-way clutch F3
The transmission is prevented from being disabled.

Then, the second speed rotation of the main transmission mechanism 11 and the direct connection rotation of the underdrive mechanism 3 are combined to obtain the third speed of the automatic transmission A as a whole.

During the downshift to the 2nd and 3rd speeds in the D range, that is, during the coast, the first brake B1
Are also engaged to operate the engine brake.

In the fourth speed state in the D range, the second clutch C2 is engaged from the third speed state. Then, the rotation of the input shaft 10 is the first
Is transmitted to the ring gear R1 via the clutch C1, and to the sun gear S1 via the second clutch C2,
The planetary gear unit 32 rotates integrally, and the direct rotation is transmitted to the counter drive gear 33. The direct rotation of the main transmission mechanism 3 and the direct rotation of the underdrive mechanism 3 are combined, and the counter drive gear 33 and the counter driven gear 13 have a predetermined speed increase relationship. , An overdrive rotation is obtained.

At this time, when the first brake B1 is operating in the third speed, the first brake B1 is released earlier when upshifting to the fourth speed, and the first one-way clutch
The second clutch C2 is connected while the sun gear S1 is locked by F1, thereby preventing the occurrence of a shift shock due to a change in the clutch.

In addition, the 1st speed state of the 3 range is the 1st speed state of the D range,
The 2nd and 3rd speed states are the same as the 2nd and 3rd speed states of the D range with the first brake B1 engaged.

In addition, the 1st and 2nd gear states in the 2nd range are 1st gear in the 3rd range.
It is the same as the second speed state.

Further, in the first range, in the first speed state, the third brake B3 is engaged in addition to the connection of the first clutch C1 and the engagement of the fourth brake B4. In this state, in addition to the engagement by the second one-way clutch F2, the third brake B3 is engaged with the ring gear R2 irrespective of the rotational direction, and the ring gear R2 operates the engine brake. The second speed state is the same as the second speed in the two ranges.

And, in the reverse range, the second clutch C2
And the third brake B3 and the fourth brake B4 are engaged. In this state, the rotation of the input shaft 10 is the second
Is transmitted to the sun gear S1 via the clutch C2, and the ring gear R2 of the dual planetary gear 31
B3, the carrier CR1 is rotated while the ring gear R1 of the single planetary gear 30 is rotated in the reverse direction.
Also reverses, and the reverse rotation of the carrier causes the counter drive gear 33 to rotate.
Is taken out. Further, the reverse rotation of the counter drive gear 33 is reduced by the under drive mechanism 3 and transmitted to the front axle shafts 23a and 23b.

Next, an embodiment in which the above-described automatic transmission A is embodied will be described with reference to FIG.

FIG. 4 is an overall sectional view of an automatic transmission on which the carrier device in the automatic transmission according to the present invention is mounted.

In the figure, the automatic transmission A is a transaxle case
40, a torque converter housing 41, and an integral case composed of a rear cover 42.
Counter shaft 2 and front differential device
A ring gear mount case serving as 29 differential carrier 36 is rotatably supported. A torque converter 26 having a lock-up clutch 25 and a main transmission mechanism 11 are provided on the input shaft 10.
An underdrive mechanism 3 is provided above. Further, a bubble body 44 is provided in the transaxle case 40.

The main transmission mechanism 11 includes a brake unit 43, an output unit 45, a planetary gear unit 32, and a clutch unit 47 arranged in this order axially rearward from the engine crankshaft 7, and further includes a brake unit 43 and a torque converter 26. An oil pump 49 is provided in the intervening portion, and a hollow shaft 50 fitted on the input shaft 10 is rotatably supported.

The planetary gear unit 32 includes a single planetary gear 30 and a dual planetary gear 31 (see FIG. 2).
And a carrier CR1 supporting a pinion P1 meshing with these gears, and a dual planetary gear 31 meshes with a sun gear S1, a ring gear R2 and a sun gear S1 formed on a hollow shaft 50. A carrier CR1 supports the second pinion P2 meshing with the pinion P1 and the ring gear R2 so as to mesh with each other. The planetary gears 30 and 31 are composed of a single gear with the same number of teeth formed on the hollow shaft 50, and the carrier CR1 is integrally formed, and the pinion P1 is formed of an integrated long pinion. Have been.

The brake part 43 is provided with a first one-way clutch F1, a first brake B1 composed of multiple disc brakes, and a second brake B2 composed of multiple disc brakes in this order from the inner diameter side to the outer diameter direction. And the second brake B2
The hydraulic actuator 51 is fixed to a position adjacent to the second brake B2, and the hydraulic actuator 52 is fixed to the cover of the oil pump 49 in a position adjacent to the second brake B2. Further, the first brake B1 is provided with the hollow shaft
The inner race of the first one-way clutch F1 is connected to the hollow shaft 50, and the outer race is connected to the second brake B2.

On the other hand, the output section 45 includes a counter drive gear 33 located substantially at the center of the main transmission mechanism 11. The counter drive gear 33 is rotatably supported by a partition 40c formed in the axle case 40 via a double tapered bearing 45a, and its boss is connected to the carrier CR1 of the planetary gear unit 32. Further, the outer race of the double tapered bearing 45a is spline-engaged with the inner peripheral surface of the partition wall 40a of the case and fitted therein, and a second one-way clutch F2 is mounted on the outer peripheral surface of the race extension.

The clutch unit 47 includes a first clutch C1 and a second clutch C2, and is housed in the rear cover 42 at the rear end of the main transmission mechanism 11. The rear end of the input shaft 10 forms a sleeve 10a so as to cover the boss 42a of the cover 42, and the clutch drum 67 is integrally connected to the sleeve 10a.

Further, a movable member 69 is fitted to the clutch drum 67 by a spline so as to be slidable only in the axial direction, and a piston member 70 is fitted to the movable member 69. The movable member 69 forms an oil chamber between itself and a cylinder formed on the inner peripheral surface of the clutch drum 67, and forms a hydraulic actuator 71 for the first clutch C1.

On the other hand, the piston member 70 forms an oil chamber between the movable member 69 and a cylinder formed on the inner peripheral surface thereof, thereby forming a hydraulic actuator 72 for the second clutch C2. Further, a spring 73 is contracted between the piston member 70 and a ring fixed to the sleeve portion 10a.
Constitutes a return spring common to the piston members 69, 70 of both hydraulic actuators 71, 72.

The first clutch C1 is interposed between a spline formed on the inner peripheral surface of the outer diameter portion of the clutch drum 67 and a spline formed on the outer peripheral surface of the ring gear R1.
The clutch C2 is interposed between a spline formed on the inner peripheral surface of the outer diameter portion of the movable member 69 and a spline formed on the hub 50a fixed to the hollow shaft 50.

Next, the underdrive mechanism 3 will be described with reference to FIG.

FIG. 1 is a view showing a carrier device in an automatic transmission according to the present invention.

As shown in the figure, the underdrive mechanism 3 has one planetary gear 1. Further, a counter driven gear 13 composed of a helical gear is rotatably supported on the counter shaft 2 via a bearing 75, and a reduction gear 35 is fixed on the counter shaft 2. The counter shaft 2 is rotatably supported at both ends by bearings 86 and 92, and is installed in the transaxle case 40.

On the other hand, the ring gear R3 of the planetary gear 1 is connected to the counter driven gear 13, and the carrier device CR3 supporting the pinion P3 is formed integrally by bulging the counter shaft 2 in the outer diameter direction.

Further, the sun gear S3 is formed on a hub 17 rotatably supported on the counter shaft 2 by thrust bearings 15, 16 and bushes 83, 85, and a drum 77 fixed to an outer diameter portion of the hub 17 has a sun gear S3. A fourth brake B4 composed of a band brake is engaged with the outer peripheral surface. Further, a third clutch C3 composed of multiple plates is interposed between the inner peripheral surface of the drum 77 and the hub 78 fixed to the carrier CR3, and the third clutch C3 adjacent to the third clutch C3 is further provided. A piston member 76 is fitted to the hub 17 in an oil-tight manner to constitute a hydraulic actuator 79 for the third clutch C3. Further, the piston member 76 is provided with a check valve 88 for eliminating centrifugal oil pressure during rotation. A spring 74 is contracted between the piston member 76 and the ring 82 fixed to the hub 17, and serves as a return spring for the piston member 76.

A boss 40b is provided at the end of the transaxle case 40.
The bearing 86 is provided on the boss 40b.
The countershaft 2 is rotatably supported via the. Further, a lubrication hole is provided at the center of the counter shaft 2.
2c, a horizontal hole 2d, 2g, 2h, 2i, 2j as a first horizontal hole is formed in the radial direction of the counter shaft 2, and a plug 18 is provided at the tip of the lubrication hole 2c. Are mounted, and the lubricating oil supplied to the lubrication holes 2c lubricates various portions as appropriate. Here, the above-mentioned lateral hole 2j is
The diameter is larger than d, 2g, 2h, 2i, and the bush 83, 85
Thereby, it communicates with an oil chamber 85 formed between the hub 17 and the counter shaft 2.

An extended portion of the hub 17 is fitted on the outer peripheral surface of the boss portion 40b, and the extended portion constitutes an inner race of the third one-way clutch F3. And a transaxle case 40.

Further, the third one-way clutch F3 has a hub 17
Is connected to the lubricating oil supplied from the lateral hole 2d. A rear cover 42 is fixed to a side surface of the transaxle case 40 with bolts. Inside the rear cover 42 is a valve body
A pipe 89 for supplying oil pressure from 44 (see FIG. 4) is provided. The pipe 89 is provided via an oil passage 40c formed in the boss portion 40b, an oil hole 40d, an annular oil groove hole 17a formed in the hub 17, and an oil passage 17b obliquely extending from the bottom of the oil groove. It is configured to supply oil pressure to the oil chamber of the hydraulic actuator 79.

The hub 17 is formed with a horizontal hole 17d as a second horizontal hole, and lubricating oil supplied to the oil chamber 84 between the bushes 83 and 85 through the horizontal hole 2j of the counter shaft 2 is supplied to the horizontal hole 17d. Hole 1
It is supplied to the planetary gear 1 via 7d. As described above, since the diameter of the lateral hole 2j is large, it is possible to supply a sufficient amount of lubricating oil.

The lubricating oil supplied to the outer peripheral side of the hub 17 is
The pinion shaft 5 and the pinion gear are formed via an oil hole 78a formed in the hub 78 of the third clutch C3, a lubricating oil hole 5d formed in the center of the pinion shaft 5, and a horizontal hole 5e extending radially from the oil hole 5d. Supplied between P3.

The hub 78 of the third clutch C3 has the oil hole
A reservoir 78b is formed to guide the supply of lubricating oil to 78a.

The carrier device CR3 has a carrier cover 6, and the carrier cover 6 is formed integrally with the countershaft 2 by hot forging.

Here, the counter shaft 2 is provided with a carrier cover 6.
The small diameter portion 2a is on the planetary gear 1 side and the large diameter portion 2b is on the opposite side. The diameter of the small-diameter portion 2a is reduced for the sake of arranging the planetary gear 1, but is increased to be substantially equal to the diameter of the large-diameter portion 2b in order to suppress the bending of the count shaft 2.
In order to accommodate the thrust bearing 15 disposed between the pinion gear P3 and the count shaft 2, the carrier cover 6 has an axial dimension, that is, a thick wall, and a recess 2k.

Therefore, the torsional strength of the carrier cover 6 can be maintained, and the interference between the pinion gear P3 and the thrust bearing 15 does not occur.
Can be increased in diameter.

In addition, since the concave portion 2k is formed in the count shaft 2, heat treatment by induction hardening cannot be performed. Therefore, the count shaft 2 is carburized and quenched, and the strength of the carrier cover 6 is increased. As described above, the lubrication of the planetary gear unit 1 is performed by the horizontal hole 2j and the oil hole.
Since the oil is supplied via 78a, it is not necessary to form an oil passage for supplying lubricating oil to the carrier cover 6. Therefore, when forming a hole for attaching a pinion shaft after carburizing and quenching, it is possible to prevent the occurrence of drill breakage and the like in a portion of the lubricating oil passage hardened by carburizing and quenching.

The front differential 29 (see FIG. 4) is a ring gear mount case 36 serving as a differential carrier.
The ring gear gear mount case 36 is rotatably supported by the torque converter housing 41 and the transaxle case 40 via bearings. Further, a large-diameter ring gear 39 meshing with the reduction gear 35 is fixed on the ring gear mount case 36,
Further, a pinion gear 81 is rotatably supported inside thereof, and left and right side gears 37a, 37b meshing with the pinion gear 81 are rotatably supported. The left and right front axle shafts 23a and 23b are fitted and connected to the side gears 37a and 37b, respectively.

In the automatic transmission configured as described above, the rotation appropriately shifted in the main transmission mechanism 11 is transmitted from the counter driven gear 13 to the underdrive mechanism 3. Then, at the 1st speed and 2nd speed in the D range, 1 range, 2 range and 3 range, the sun gear S3 is stopped by the fourth brake B4 and the third one-way clutch F3, and the underdrive mechanism 3 The vehicle enters the reduced rotation state, and the reduced rotation is taken out to the carrier CR3. Further, the deceleration rotation is
The rotation is transmitted to the front differential device 29 in combination with the rotation appropriately reduced in the main transmission mechanism 11.

In the third and fourth speeds, the third clutch C3 is engaged. That is, the hydraulic pressure for engagement of the third clutch C3 is supplied from the valve body 44 to the oil passage 40c through the pipe 89. Further, the hydraulic pressure for engagement of the third clutch C3 is
c through an oil hole 40d, an annular oil groove hole 17a, and an oil passage 17b.
C3 is engaged. In this state, the carrier CR3 and the sun gear S3 rotate integrally and rotate directly. The direct connection rotation is combined with the rotation appropriately shifted in the main transmission mechanism section 11 to form a front differential device.
It is transmitted to 29.

Also, a counter driven gear 13 consisting of a helical gear
Generates an axial force due to the rotation, and the axial force acts on the hub 17 and the thrust bearings 15 and 16 so that the transaxle case 40
Boss portion 40b. On the other hand, the reaction force of the axial force is backed up on the large-diameter side 2b of the counter shaft, and the underdrive mechanism 3 is always kept in an appropriate stress state.

It should be noted that the present invention is not limited to the above embodiment, and various modifications are possible based on the gist of the present invention.
They are not excluded from the scope of the present invention.

[Brief description of the drawings]

FIG. 1 is a view showing a carrier device in an automatic transmission of the present invention, FIG. 2 is a schematic diagram of an automatic transmission to which the carrier device in the automatic transmission of the present invention is applied, and FIG. 3 is an automatic transmission of the present invention. FIG. 4 is a view showing the operation of the automatic transmission to which the carrier device is applied in FIG. 4; FIG.
FIG. 1 is a sectional view of a carrier device in a conventional automatic transmission. 2 ... counter shaft, 2c ... lubrication hole, 2k ... recess,
5. Pinion shaft, 5a, 5b, 5d, 6a ... Lubricating oil hole, 6 ...
Carrier cover, 15 ... thrust bearing, 17 ... hub, 2d, 2f, 2g, 2h, 2i, 2j, 5e, 17d ... side hole, 78b ... reservoir, 84 ... oil chamber, S3 ... sun gear, P3: Pinion gear, R1, R2, R3: Ring gear.

Continuation of the front page (56) References JP-A-61-41043 (JP, A) JP-A-51-42861 (JP, A) JP-A-61-24857 (JP, A) JP-A-2-110747 (JP) , U) Japanese Utility Model 1-115057 (JP, U) Japanese Utility Model 2-107865 (JP, U) Japanese Utility Model Showa 60-116458 (JP, U) Japanese Utility Model Utility Model Showa 55-18699 (JP, U) Japanese Utility Model Utility 52-127175 (JP, U) Japanese Utility Model Showa 50-10980 (JP, U) Japanese Utility Model Showa 50-9670 (JP, U) (58) Fields investigated (Int. Cl. ⁶ , DB name) F16H 57/00 -57/10 F16H 3/44-3/78

Claims (2)

(57) [Claims] An annular carrier cover is integrally formed,
A shaft having a small-diameter portion formed on one side and a large-diameter portion formed on the other side with the carrier cover interposed therebetween; a sun gear rotatably supported on the small-diameter portion via a support member; and a pinion gear meshing with the sun gear. A ring gear meshing with the pinion gear, a pinion shaft fixed to the carrier cover and rotatably supporting the pinion gear, an annular recess formed in a portion of the carrier cover that comes into contact with the sun gear, and accommodated in the annular recess. A thrust bearing for supporting a thrust load between the carrier cover and the sun gear, a lubrication hole formed at the center of the shaft, and a lubrication hole formed in the shaft in a radial direction, and the lubrication hole and the outer peripheral side of the shaft. Lubricating oil formed in the first lateral hole communicating with the pinion shaft and supplying lubricating oil to the planetary gear unit When the carrier device in the automatic transmission, characterized in that it comprises a reservoir for guiding the lubricating oil supplied from the lubricating hole on the outer peripheral side of the shaft in the lubricating oil hole of the pinion shaft. 2. An oil chamber formed between the support member, a shaft and a sun gear, and a second horizontal hole communicating the oil chamber with an outer peripheral side of the sun gear; The hole communicates between the oil chamber and a lubricating hole in the shaft, and the reservoir guides lubricating oil supplied from the oil chamber to an outer peripheral side of a sun gear into a lubricating oil hole of the pinion shaft. A carrier device for the automatic transmission according to claim 1.