JP2892019B2 - Lubricating device in automatic transmission - Google Patents

Description

The present invention is suitable for use in an automatic transmission mounted on an automobile, particularly an automatic transmission equipped with a gear unit having a dual planetary gear. The present invention relates to a lubrication device for a pinion support of a gear unit.

(B) Prior Art Recently, as disclosed in Japanese Patent Application Laid-Open No. 62-93545, for example, the present applicant has disclosed a forward 3-speed or 4-speed automatic transmission comprising a planetary gear unit combining a single planetary gear and a dual planetary gear. An automatic transmission equipped with a.

The automatic transmission mechanism is configured by integrally connecting a sun gear and a carrier of both planetary gears, using the carrier as an output element, transmitting rotation of an input shaft to a ring gear of a single planetary gear (hereinafter, referred to as a small ring gear), and a dual gear. The first gear is obtained by fixing the ring gear of the planetary gear (hereinafter referred to as the large ring gear).
The second gear is obtained by fixing the sun gear in the state of input to the small ring gear, and the planetary gear unit consisting of both gears is rotated integrally to obtain the third gear, thereby constituting an automatic transmission mechanism of the third forward gear. .

Further, a third clutch for connecting / disconnecting the input shaft to / from the large ring gear is provided to transmit the rotation of the input shaft to the large ring gear and fix the sun gear to obtain the fourth speed. Is composed.

Generally, an oil hole is formed in the pinion shaft of the planetary gear unit from the outside toward the pinion support portion, and an oil guide plate is provided in the oil hole opening. The lubricating oil stored in the guide plate is supplied to the pinion support through the oil hole to lubricate the needle bearing in the support.

(C) Problems to be Solved by the Invention However, the lubrication of the pinion support portion only guides the oil scattered by the centrifugal force to the support portion, and is not sufficient to ensure the durability of the bearing. .

In particular, when applied to the four-speed automatic transmission mechanism, the carrier relatively rotates at the time of the forward fourth speed, which has a long use time,
Therefore, since the pinion also rotates at high speed, a sufficient amount of lubricating oil is required.

Accordingly, it is an object of the present invention to provide a lubricating device for an automatic transmission that forcibly lubricates a pinion support portion through an oil hole formed in a carrier, thereby solving the above-described problems.

(D) Means for Solving the Problems The present invention has been made in view of the above circumstances, and for example, as shown in FIG. 1, a planetary gear unit (20) having a carrier (CR1) and a rotating member In the automatic transmission including (5), the carrier (CR1) includes a boss portion (1), a support portion (2) formed to rise from the boss portion, and a pinion ( And a pinion shaft (6, 7) that rotatably supports P1, P2). A bush (9) is interposed in close contact between the boss (1) and the rotating member (5). The boss portion is rotatably supported by the rotating member. The bush (9) is provided between the inner peripheral surface of the boss portion (1) and the outer peripheral surface of the rotating member (5). Oilway (9
a), a second oil passage (from the inner peripheral surface of the boss portion (1), which communicates with the pinion support surface of the shaft through the support portion (2) and the pinion shaft (6, 7). 1a, 2a, 6a, 6b, 7a, 7
b), and a lubricating oil supply oil hole (5) formed in the rotating member (5).
a) and the first oil passage (1a) on the inner peripheral surface of the boss portion are brought into contact with a second oil passage (9) formed by the bush, and the lubricating oil is released to the internal space of the automatic transmission without being released. A lubricating device for an automatic transmission, wherein lubricating oil from a supply oil hole is supplied to the pinion support surface via the first oil passage and the second oil passage.

Further, the planetary gear unit (20) has a dual planetary gear (19), and the planetary gear (1)
9) Supply lubricating oil to both the pinion support portions of the inner pinion (P1) and the outer pinion (P2).

Further, the first oil passage is a hole (9a) formed in the bush, and the second oil passage is the boss portion (1).
From the first oil hole (2a) formed in the support portion (2)
And the first oil hole, and the pinion shaft (6,
7) a second oil hole (6a, 7b) formed in the axial direction, and a second oil hole (6b, 6b, 6b, 7b) communicating with the second oil hole and extending to the outer peripheral surface in the radial direction of the pinion shaft. 7b) and a concave groove (1a) formed on the inner peripheral surface of the boss portion, the first oil hole (2a) being open, and being in contact with the hole (9) of the bush.

(E) Action Based on the above configuration, the carrier (CR1) has its boss (1) rotatably supported via a bush (9),
For example, the overdrive (4
Speed), the carrier (CR1) is rotated by the rotating member (5)
And the pinions (P1, P2) rotate at high speed.

On the other hand, a lubricating oil supply hole (5
The lubricating oil from a) is supplied to the second oil passage (1a) on the inner peripheral surface of the boss portion through the first oil passage (9a) formed by the bush (9) in contact with the supply hole (5a). The second oil passages (2a, 6a, 6b, 6b, 6a, 6b, 6) are supplied to the internal space of the automatic transmission without opening, and are formed in the support (2) and the pinion shaft (6, 7).
7a, 7b) and is forcibly supplied to a pinion support surface such as a bearing.

(F) Example Hereinafter, an example according to the present invention will be described with reference to the drawings.

First, regarding the automatic transmission A to which the present invention is applied,
The outline of the automatic transmission A will be described with reference to the drawings. The automatic transmission A has three axes of an input shaft 3 aligned with an engine crankshaft 21, a counter shaft 22, and front axle shafts 23a and 23b. A torque converter 26 having a lock-up clutch 25 and a four-speed automatic transmission mechanism 10 are supported, an underdrive mechanism 27 is supported on a counter shaft 22, and a front differential is provided on front axle shafts 23a and 23b. A device 29 is supported.

The four-speed automatic transmission mechanism 10 has a planetary gear unit 20 which is a combination of a single planetary gear 17 and a dual planetary gear 19,
The sun gear S1 of the two planetary gears and the gears CR1 are integrally connected to each other.
Is formed by the long pinion P1. Then, the input shaft 3 and the single planetary gear 17
Ring gear R1 (small ring gear) is connected via a first (forward) clutch C1.
And the sun gear S1 are connected via a second (reverse) clutch C2. Also, sun gear S1 is the first brake
Directly locked by B1 and the second brake B2
Thereby, the one-way rotation is locked via the first one-way clutch F1. In addition, dual planetary gear
19 ring gear R2 (large ring gear) is the third brake B3
And one-way rotation is locked by the second one-way clutch F2. The carrier CR1 is connected to a counter drive gear 31 supported by the case partition 40 ', and the gear 31 is an output member of the four-speed automatic transmission mechanism 10.

The clutches C1 and C2, the brakes B1 and B2, and the one-way clutches F1 and F2 are the same as those of the three-speed automatic transmission mechanism. A third clutch C0 connecting the shaft 3 and the large ring gear R2, an output member of the clutch C0 and a small ring gear R1;
A fourth clutch C3 and a third one-way clutch F0 are interposed between them.

The underdrive mechanism 27 has one single planetary gear 32, and the carrier CR3 and the sun gear S3 of the planetary gear are connected to a fifth (direct) clutch C.
Are linked through four. The sun gear S3 is directly locked by a fourth (under-drive) brake B4, and one-way rotation is locked by a fourth one-way clutch F3. Then, the ring gear R3 meshes with the counter drive gear 31, and this underdrive mechanism
27 is connected to a counter driven gear 33 serving as an input member, and the carrier CR3 is connected to the counter shaft 22. Further, a reduction gear 35 serving as an output member of the underdrive mechanism 27 is fixed to the counter shaft 22.

Further, the front differential device 29 has a differential carrier 36 and left and right side gears 37a and 37b, and a ring gear 39 is provided on the differential carrier 36 serving as a gear mount case.
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 the left and right front axle shafts 23a and 23b, respectively.

Next, the four-speed automatic transmission mechanism 10 of the automatic transmission A is described.
3 will be described with reference to FIG.

The rotation of the engine crankshaft 21 is transmitted to the input shaft 3 via the torque converter 26 or via the lock-up clutch 25. Then, in the first speed state in the D range, the first clutch C1 is in the connected state. In this state, the rotation of the input shaft 3 is transmitted to the small ring gear R1 via the first clutch C1, and in this state, the rotation of the large ring gear R2 is prevented by the second one-way clutch F2. Therefore, while the sun gear S1 is idling in the reverse direction, the common carrier CR1 is greatly reduced in rotation in the forward direction, and the rotation is taken out from the counter drive gear 31.

In the second speed state in the D range, the second brake B2 operates in addition to the connection of the first clutch C1. Then, the rotation of the sun gear S1 is stopped by the operation of the first one-way clutch F1 based on the brake B2. Therefore, the rotation of the small ring gear R1 from the input shaft 3 rotates the carrier CR1 while idling the large ring gear R2 in the forward direction. The rotation is reduced in the forward direction, and the rotation is taken out to the counter drive gear 10 as the second speed. At the time of 1 → 2 shift, the second one-way clutch F2 is switched from the locked state to the overrun state,
Shifts smoothly without causing a shift shock due to gripping.

In the third speed state in the D range, the third clutch C3 and the fourth clutch C4 are connected from the second speed state. Then, the power is transmitted from the input shaft 3 to the small ring gear R1 via the first clutch C1 and to the large ring gear R2 via the third clutch C0, the planetary gear unit 19 rotates integrally, and the direct connection rotation is counted by the counter. The power is transmitted to the drive gear 31. At the time of 2 → 3 shift, the first one-way clutch F1
Is switched from the locked state to the overrun state, and the shift is smoothly performed without causing a shift shock due to gripping. In the third speed state, the fourth clutch C3 is connected together with the third clutch C0, and the rotation of the input shaft 3 is controlled by the third clutch C0, the fourth clutch C3, and the third one-way clutch. Small ring gear even on the path through F0
Transmitted to R1.

Then, during an upshift from the third speed to the fourth speed in the D range, first, the first clutch C1 is released. In this state, only the third clutch C0 and the fourth clutch C0
The rotation is transmitted to the small ring gear R1 through a path via C3 and the third one-way clutch F0, and in this state, the first brake B1 operates. Then, sun gear S1
The rotation of the large ring gear R2 transmitted from the input shaft 3 via the third clutch C0 causes the carrier CR1 to rotate while the small ring gear R1 idles at high speed by overrunning the one-way clutch F0. Extracted as overdrive rotation. At this time, since the first clutch C1 is in the disengaged state and the speed is changed under the action of the third one-way clutch F0, the shift is smoothly performed without causing a shift shock due to the re-gripping.

Further, in an engine brake operating state such as three range, two range or one range, at the first speed, the third brake B3 is operated to stop the large ring gear R2 against the reverse rotation. At the time of speed, the first brake B1 is operated to stop the sun gear S1 against reverse rotation.

And in the reverse range, the second clutch
With the connection of C2, the third brake B3 operates. In this state. The rotation of the input shaft 3 is controlled by the second clutch C2.
Is transmitted to the sun gear S1, and in this state, the large ring gear R2 is fixed by the operation of the third brake B3.
1 also reverses, and the reverse rotation of the carrier causes the counter drive gear 3
Taken out by one.

On the other hand, the underdrive mechanism 27
And / or when the sun gear S3 is stopped by the fourth one-way clutch F3, the rotation from the counter driven gear 33 is taken out from the ring gear R3 to the carrier CR3 as deceleration (under drive) rotation. When the fourth brake B4 is released and the fifth clutch C4 is engaged, the carrier CR3 and the sun gear S3 are integrated, and the directly connected rotation is taken out to the counter shaft 22.

In the automatic transmission A, a predetermined shift stage is obtained by appropriately combining the forward four-speed shift of the four-speed automatic transmission mechanism 10 and the deceleration and direct connection of the underdrive mechanism 27, and the rotation is reduced to the reduction gear 35 and the ring gear. It is transmitted to the front differential device 29 via 39, and furthermore, the left and right front axle shafts 23
a, 23b. For example, the four-speed automatic transmission mechanism 10
And the underdrive mechanism 27, the underdrive mechanism 27 is decelerated, the 4-speed automatic transmission mechanism 10 is operated to set the power mode, and the underdrive mechanism 27 is directly connected to the 4-speed automatic transmission mechanism 10 to operate the economy. A mode switching means for setting a mode, or a means for operating the special case by setting the underdrive mechanism 27 to extra low or high, or a four-speed automatic transmission mechanism for the underdrive mechanism 27. 10 second gear and 3
It is conceivable that the forward speed is set to the fifth speed by inserting it between the speeds.

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

The automatic transmission A has an integrated case including a transaxle case 40, a transaxle housing 41, and a rear cover 42. The case includes an input shaft 3, a counter shaft
A ring gear mount case 36 serving as a differential carrier of the front differential device 22 and the front differential device 29 is rotatably supported. A torque converter 26 having a lock-up clutch 25 and a four-speed automatic transmission mechanism 10 are provided on the input shaft 3, and an underdrive mechanism 27 is provided on the counter shaft 22. The transaxle case 40 is provided with a valve body 44 covered by a side cover 48.

The four-speed automatic transmission mechanism 10 includes a brake unit 43, an output unit 45, a planetary gear unit 20 and a clutch unit 47 arranged in this order axially rearward from the engine crankshaft 21, and further includes a brake unit 43 and a torque converter. An oil pump 49 is disposed in a portion between the shaft 26 and the shaft 26. The hollow shaft 5 is rotatably supported by being fitted to the input shaft 3.

The planetary gear unit 20 includes a single planetary gear 17 and a dual planetary gear 19 (see FIG. 2). The single planetary gear 17 supports a sun gear S1, a ring gear R1 formed on the hollow shaft 5, and a pinion P1 meshing with these gears. Carrier CR1
The dual planetary gear 19 is formed of a carrier CR1 that supports a sun gear S1, a ring gear R2 formed on the hollow shaft 5, and a first pinion P1 meshing with the sun gear S1 and a second pinion P2 meshing with the ring gear R2 so as to mesh with each other. Become. The two planetary gears 17, 19 are formed by a single gear having the same number of teeth formed on the hollow shaft 5 in the sun gear S1, the carrier CR1 is integrally formed, and the pinion P1 is formed into an integrated long pinion. It is configured.

Then, the carrier CR1 is, as shown in detail in FIG.
A boss 1 is provided, and the boss 1 is provided with a support 2 which stands up from the end in the radial direction and is integrally formed. Bushes 9, 45 are arranged between the inner peripheral surface of the boss 1 and the outer peripheral surface of the hollow shaft 5, and the boss 31a of the counter drive gear 31 is spline-coupled to the outer peripheral surface of the boss 1. In addition, the ring gear R2 and the outer race support member 50 of the one-way clutch F2 arranged in parallel on the outer periphery of the carrier CR1 are in contact with the counter gear boss 31a via a thrust bearing 60. On the other hand, the shafts 6 and 7 of the pinions P1 and P2
The shafts 6 and 7 are fixed to pinions P1 and P2 via needle bearings 11a, 11b, 13a and 13b, respectively.
Support. A thrust bearing 61 is in contact with the support portion 2 on the opposite side of the pinion shafts 6 and 7, and together with the thrust bearing 60, a support member is provided.
50 is rotatably carried.

The bush 9 is provided with a hole 9a at the center thereof, and the hole 9a is in contact with a horizontal hole 5a formed in the hollow shaft 5. Further, a groove 1a is formed in the inner peripheral surface of the boss portion 1 facing the bush 9, and the groove 1a is formed in the hole 9 of the bush.
Is facing. In addition, a large number of oil passages
2a is formed radially, and the base end of the oil passage 2a is
It communicates with 1a. And a part of many oil passages 2a is the first
Oil passage formed in the shaft 6 supporting the pinion
6a, and the tip is closed with a stopper. The other oil passage 2a communicates with an oil passage 7a formed in the shaft 7 supporting the second pinion, and the tip thereof is connected to a plug 2b.
Is closed. Further, the oil passages 6a, 7a formed in the shafts 6, 7 are closed at their ends with plugs 6d, 7d, and at the intermediate portion, the lateral holes 6b, formed in the shafts 6, 7 are formed. 7b, and these lateral holes 6b, 7b are provided with bearings 11a, 11b, 13a, 13b and thrust washers 12a, 12b, 1b.
Opened to lubricate 5a, 15b. Thus, an oil passage for forcibly lubricating the bearing and the thrust washer is formed from the lateral hole 5a. Since the lubricating oil supplied from the lateral hole 5a is guided to the groove 1a through the oil hole 9a, the lubricating oil does not leak between the boss 1 and the intermediate shaft 5.

Further, a first one-way clutch F1, a first brake B1 composed of a multi-plate brake, and a second brake composed of a multi-plate brake are sequentially provided from the inner diameter side to the outer diameter direction.
Brake B2 is provided. In the first one-way clutch F1, the tip of the hollow shaft 5 is spline-engaged with the inner race, and a second brake hub extending outwardly is fixed to the outer race. Further, a first brake hub is fixed to the front side (engine side) of the one-way clutch F1 in the inner race. On the other hand, the oil pump 49 is composed of an oil pump assembly in which a pump cover made of aluminum die-cast is integrally fixed to a pump body with bolts sandwiching a pump plate. The first hydraulic actuator 52 for brakes and the second hydraulic actuator 51 for brakes are arranged on the rear side of the oil pump cover in order from the inner side of the oil pump cover.
Are arranged.

On the other hand, the output unit 45 has the counter drive gear 31 located substantially at the center of the four-speed automatic transmission mechanism 10,
The counter drive gear 31 is rotatably supported by a partition wall 40 'formed in the axle case 40 via a double tapered bearing 53, and its boss is connected to the carrier CR1 of the planetary gear unit 20.
Further, the outer race of the bearing 53 is a case partition wall.
40 'is fitted on the inner peripheral surface by spline engagement, and a second one-way clutch is fitted on the outer peripheral surface of the race extension.
F2 is installed.

The outer race of the second one-way clutch F2 is fixed to the ring gear R2 of the dual planetary gear 19, and the ring gear R2 is sandwiched between the counter gear boss portion and the carrier CR1 via a thrust bearing. Supported by a supporting plate. Further, a third brake B3 is interposed between the outer periphery of the ring gear R2 and the axle case 40, and a cylinder is formed on one side wall surface of the partition wall 40 ', and a hydraulic pressure comprising a piston is provided on the cylinder. The actuator 65 is provided so as to be sandwiched between the second one-way clutch F2.

The clutch unit 47 includes a first (forward) clutch C1 and a second (reverse) clutch C2, and is located at the rear end of the four-speed automatic transmission mechanism 10 and housed in the transaxle cover 42. ing. Also, input shaft 3
A sleeve 3a is fixed to the rear end so as to fit the central boss 42a of the cover 42, and a clutch drum 67 is integrally connected to the sleeve 3a. Further, a movable member 69 is fitted to the clutch drum 67 slidably only in the axial direction by a spline, and a piston member 70 is fitted to the movable member 69 in an oil-tight manner. Further, the movable member 69 constitutes an oil chamber between itself and a cylinder having an inner peripheral surface of the clutch drum 67 to constitute a hydraulic actuator 71 for the first clutch C1. On the other hand, the piston member 70 constitutes an oil chamber between itself and the cylinder having the inner peripheral surface of the movable member 69, and constitutes a hydraulic actuator 72 for the second clutch C2. Further, a spring 73 is contracted between the piston member 70 and a spring receiving member 71 fixed to the sleeve portion 3a by a snap ring, and the spring 73 is attached to the piston member 69 of both hydraulic actuators 71 and 72. , 70 constitute a return spring. 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 axially extending portion 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 outer peripheral surface of the hub 5a fixed to the hollow shaft 5.

The four-speed automatic transmission mechanism 10 has the following devices in addition to the components common to the three-speed automatic transmission mechanism described above. That is, the sleeve member 75 is fitted into the annular boss portion 42b of the rear cover 42, and the flange member 79 is fixed to the sleeve member 75, thereby forming a cylinder of the third clutch C0 hydraulic actuator 80. . A piston 77 is fitted in the cylinder in an oil-tight manner, and a flange member is provided.
The outer peripheral portion of 79 has a comb-like slit formed therein, and a separator plate and a backing plate that constitute an external friction plate for the third clutch C0 are disposed through the slit. Further, a hub is fixed to a step portion of the clutch drum 67, and a clutch plate which is engaged with the hub and forms an inner friction plate is disposed. The clutch plate and the separator plate allow the hydraulic actuator 80 to be fixed. An adjacent third clutch C0 is configured.

On the other hand, the underdrive mechanism 27 has one single planetary gear 32 as shown in FIG. Further, a counter driven gear 33 is rotatably supported on the counter shaft 22 via a bearing 103, and
A reduction gear 35 is fixed on 22. The ring gear R3 of the planetary gear 32 is connected to the counter driven gear 33, and the carrier CR3 that supports the pinion P3 is formed integrally with the counter shaft 22 by bulging the counter shaft 22 in the outer diameter direction. Further, the sun gear S3 is formed on a hub 105 rotatably supported on the shaft 22, and a drum 106 fixed to the outer diameter portion of the hub has a fourth brake B4 formed of a band brake on the outer peripheral surface thereof. Is engaged. The drum 106
A fifth clutch C4 is interposed between the inner peripheral surface of the clutch C4 and the hub fixed to the carrier CR3, and a piston is fitted to the hub 105 adjacent to the clutch C4 so that a clutch C4 is provided. The hydraulic actuator 107 is configured. Also hub 1
A fourth one-way clutch F3 is interposed between the extension of 05 and the case 40.

The front differential device 29 has a ring gear mount case 36 serving as a differential carrier,
The case 36 is rotatably supported by the housing 41 and the case 40 via bearings. Further, a large-diameter ring gear 39 meshing with the reduction gear 35 is fixed on the count case 36, and a pinion shaft 11 is
The pinion gear 111 is rotatably supported by 0, and the left and right side gears 37a, 37b meshing with the gear 111 are rotatably supported. Then, the side gears 37a, 37
b is fitted with left and right front axle shafts 23a and 23b, respectively.
Be linked.

Since the present embodiment is configured as described above, when the automatic transmission A is driven, the rotation appropriately shifted by the 4-speed automatic transmission mechanism 10 is taken out from the carrier CR1, and the counter driven gear 33 is moved from the counter drive gear 31 to the counter driven gear 33. The power is transmitted to the underdrive mechanism 27 via the control unit.

At this time, the carrier CR1 rotates according to each shift speed, and accordingly, the pinions P1 and P2 also rotate. And input shaft 3
The lubricating oil supplied from the oil passage 3a is supplied to the input shaft 3 through the lateral holes 3b.
The air is supplied to a number of lateral holes of the hollow shaft 5 through the space between the hollow shaft 5 and the hollow shaft 5.

The lubricating oil supplied to the lateral hole 5a is supplied to the carrier CR1.
Is supplied to the oil passages 6a and 7a of the pinion shaft via the holes 9a and the grooves 1a of the bush 9 and the oil passage 2a of the carrier support 2 due to the centrifugal force caused by the rotation of. Further, the lubricating oil is supplied to the oil passages 6a and 7a.
Are supplied to the bearings 11a, 11b, 13a, 13b and thrust washers 12a, 12b, 15a, 15b through the lateral holes 6b, 7b, and after lubricating the bearings 11a, 11b, 13a, 13b, the thrust washers 12a, 1b.
Lubricate 2b, 15a, 15b.

In particular, at the 4th speed in the 4-speed automatic transmission mechanism 10, the ring gear R1 of the single planetary gear 17 idles at high speed, and the input rotation is transmitted to the ring gear R2 of the dual planetary gear 19, so that the first pinion P1 and the second Although the pinion P2 rotates at high speed, the horizontal hole 5b of the hollow shaft 5 is used.
The lubricating oil supplied to the bearings 11a, 11b, 13a, 13b and the thrust bearings 12a, 12b without leaking to the outside when passing through the hole 9a by the bush 9 arranged between the carrier boss 1 and the hollow shaft 5. , 15a and 15b are lubricated in a sufficient amount and forcibly without loss of lubricating oil.

(G) Advantageous Effects of the Invention As described above, according to the present invention, the pinion (P1, P1) supported by the carrier (CR1) rotating relative to the rotating member (5) and capable of rotating at high speed. P
2) The lubricating oil supply hole (5a) of the rotating member
Therefore, the lubricating oil is forcibly supplied without releasing the lubricating oil into the internal space of the automatic transmission, and the pinion supporting portion can be reliably lubricated with a sufficient amount of lubricating oil.

In particular, when the carrier (CR1) rotates at a high speed (for example, at the time of overdrive), the pinions (P1) and (P2) also rotate at a high speed, and a more sufficient amount of lubricating oil is required for the support portion. Inner pinion of dual planetary gear (P
1) By forcibly lubricating the outer pinion (P2), the lubrication of the bearing can be reliably prevented.

In addition, since the leakage of the lubricating oil is prevented by the bush (9) interposed between the boss (1) and the rotating member shaft (5), the sealing performance of the oil passage for pinion lubrication is improved and sufficient. An amount of lubricating oil can be reliably supplied to the pinion support.

Further, the bush (9) has a hole (9a) penetrating from the inner peripheral surface to the outer peripheral surface thereof, and furthermore, the bush (9) is provided between the outer peripheral surface of the bush and the inner peripheral surface of the boss portion through the hole (9a). By forming a groove (1a) communicating with the oil hole (2a) of the part (2), the oil hole (5a) formed in the hollow shaft (5) is connected to the oil passage (2a) of the support part (2). Lubricating oil can be supplied smoothly.

Further, oil passages (1a), (2) are provided inside the carrier (CR1).
a), the lubricating oil supply hole (for example, the lateral hole 5a)
, Etc.), it is not necessary to newly provide an oil passage communicating with the apparatus, and it is possible to prevent the apparatus from becoming complicated, to achieve weight reduction and cost reduction.

[Brief description of the drawings]

1 is a sectional view showing a lubricating device according to the present invention, FIG. 2 is a schematic diagram showing an automatic transmission to which the present invention is applied, and FIG. 3 is a diagram showing the operation thereof. FIG. 4 is a sectional view showing the entire automatic transmission. DESCRIPTION OF SYMBOLS 1 ... Carrier boss part, 1a ... (concave) groove, 2 ... Carrier support part, 2a ... Oil passage (first oil hole), 5 ... Rotating member (hollow shaft), 6 ... Inner pinion shaft , 6a, 6b ……
Oil passage (second oil hole), 7 ... Outer pinion shaft, 7
a, 7b ... oil passage (second oil hole), 9 ... bush, 9a ...
First oil passage (hole), A: Automatic transmission, CR1: Carrier, P1: Inside (first) pinion, P2: Outside (second)
Pinion.

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Haruki Takemoto 10 Takane, Fujii-machi, Anjo, Aichi Prefecture Inside Aisin AW Co., Ltd. (72) Mamoru Niimi 10 Takane, Fujii-cho, Anjo, Aichi Prefecture Aishi (56) References JP-A-62-93545 (JP, A) JP-A-58-196367 (JP, A) JP-A-2-51647 (JP, A) Japanese Utility Model Showa 63 -49053 (JP, U) Fully open 1977-127175 (JP, U) Fully open 1962-183160 (JP, U) Fully open 1960-116458 (JP, U) (58) Fields surveyed (Int.Cl) . ^6, DB name) F16H 57/00 - 57/04 F16H 3/44 - 3/78

Claims (3)

(57) [Claims] 1. An automatic transmission comprising a planetary gear unit having a carrier and a rotating member, wherein the carrier has a boss portion, a support portion formed upright from the boss portion, and a pinion provided on the support portion. A pinion shaft that rotatably supports the boss portion, wherein a bush is interposed in close contact between the boss portion and the rotating member, and the boss portion is rotatably supported by the rotating member; Forming a first oil passage between an inner peripheral surface of the boss portion and an outer peripheral surface of the rotating member, and passing the shaft from the inner peripheral surface of the boss portion through the support portion and the pinion shaft. Forming a second oil passage communicating with the pinion support surface of the second member, and connecting the lubricating oil supply oil hole formed in the rotating member and the first oil passage on the inner peripheral surface of the boss portion to a second oil formed by the bush. Facing the road, Supplying the lubricating oil from the lubricating oil supply oil hole to the pinion support surface via the first oil passage and the second oil passage without releasing the oil to the internal space of the transmission. Lubrication device for automatic transmission. 2. The lubricating device for an automatic transmission according to claim 1, wherein said planetary gear unit has a dual planetary gear, and supplies lubricating oil to both pinion support surfaces of an inner pinion and an outer pinion of said dual planetary gear. . 3. The first oil passage is a hole formed in the bush, and the second oil passage is provided with a first oil hole formed in the support portion from the boss portion. A second oil hole communicating with the first oil hole and formed in the axial direction of the pinion shaft;
A second oil hole communicating with the oil hole of the pinion shaft and extending to an outer peripheral surface in a radial direction of the pinion shaft; and a second oil hole formed in the inner peripheral surface of the boss portion. The lubricating device for an automatic transmission according to claim 1, further comprising: a contacting groove.