JP2010065741A - Lubricating structure for vehicular automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enable reliable supply of lubricating oil into a pinion shaft when the planetary carrier of a planetary gear mechanism for a vehicular automatic transmission is stopped. <P>SOLUTION: An oil reservoir 47b opened toward the oil hole 44a of the pinion shaft 44 is recessed in a ring gear hub 47 for supplying the lubricating oil into the oil hole 44a of the pinion shaft 44 on the planetary carrier 19. Thus, even when the rotation of the planetary carrier 19 is stopped to disable oil supply through a centrifugal force, the lubricating oil supplied from rotating shafts 13, 36 to the oil reservoir 47c through the centrifugal force is sprayed toward the oil hole 44a of the pinion shaft 44 with a rib 47c of the oil reservoir 47b. This eliminates the need for forming an oil path for the lubricating oil in the planetary carrier 19 itself and for supplying the pressure lubricating oil to the oil path, and enables reliable supply of the lubricating oil into the oil path 44a of the pinion shaft 44 on the planetary carrier 19 whose rotation is stopped, in a simple construction. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention includes a planetary gear mechanism in which a sun gear, a planetary carrier, and a ring gear are coaxially arranged around a rotation shaft, and a pinion supported on the planetary carrier via a pinion shaft is engaged with the sun gear and the ring gear. The present invention relates to a lubricating structure of an automatic transmission for lubricating a sliding surface between the pinion shaft and the pinion with lubricating oil supplied to an oil hole formed inside the shaft.

  When lubricating a needle bearing disposed between a pinion shaft and a pinion through an oil passage formed in a pinion shaft of a planetary carrier of a planetary gear mechanism of an automatic transmission for a vehicle, the planetary carrier is rotating. Sometimes, lubricating oil can be supplied to the pinion shaft by centrifugal force from an oil passage inside the rotating shaft that supports the planetary carrier. However, when the planetary carrier stops rotating at a specific gear stage of the automatic transmission, it becomes difficult to supply the lubricating oil by the centrifugal force described above. It is necessary to enlarge the diameter of the oil passage of the planetary carrier.

Therefore, what is described in Patent Document 1 below forms an oil passage 280b extending radially in the output shaft 280 that rotates in the vicinity of the planetary carrier C201 when the planetary carrier C201 is stopped. Lubricating oil is supplied to the inside of the pinion shaft of the planetary carrier C201 by having the end face the radially inner end of the lubricating oil passage C201a formed in the planetary carrier C201 in the radial direction.
JP-A-7-208586

  However, in the above-mentioned conventional one, it is necessary to form a lubricating oil passage C201a that extends from the radially inner end side to the pinion shaft inside the planetary carrier C201, which increases the size of the planetary carrier C201 and increases the weight. In addition, there is a problem that causes an increase in cost due to an increase in the number of processing steps for forming the lubricating oil passage C201a and an increase in the number of parts due to the plug closing the downstream end of the lubricating oil passage C201a.

  The present invention has been made in view of the above-described circumstances, and makes it possible to reliably supply lubricating oil to the inside of a pinion shaft when the planetary carrier of the planetary gear mechanism of the automatic transmission for a vehicle is stopped. For the purpose.

  In order to achieve the above object, according to the first aspect of the present invention, a sun gear, a planetary carrier and a ring gear are arranged coaxially around a rotation axis, and the pinion supported by the planetary carrier via a pinion shaft is Lubricating a vehicle automatic transmission that includes a planetary gear mechanism that meshes with a sun gear and the ring gear, and that lubricates a sliding surface between the pinion shaft and the pinion with lubricating oil supplied to an oil hole formed inside the pinion shaft. In the structure, an oil reservoir that opens at least toward the oil hole of the pinion shaft is recessed in the rotating member that rotates around the rotating shaft while the planetary carrier is stopped, and is supplied from the rotating shaft to the oil reservoir. The vehicular automatic characterized in that the lubricated oil is scattered toward the oil hole of the pinion shaft Lubrication structure of the speed machine is proposed.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the oil reservoir is formed in an annular shape so as to surround the rotating shaft, and the oil of the pinion shaft is provided at a plurality of locations in the circumferential direction. A lubricating structure for an automatic transmission for a vehicle is proposed in which a rib protruding toward the hole is formed.

  According to a third aspect of the present invention, in addition to the configuration of the first or second aspect, a guide member that guides the lubricating oil scattered from the oil reservoir to the oil hole of the pinion shaft is provided. A lubricating structure for an automatic transmission for a vehicle is proposed.

  The input shaft 13 and the center shaft 36 of the embodiment correspond to the rotation shaft of the present invention, the first planetary gear mechanism 16 of the embodiment corresponds to the planetary gear mechanism of the present invention, and the ring gear hub of the embodiment. 47 corresponds to the rotating member of the present invention.

  According to the first aspect of the present invention, the lubricating oil is supplied to the oil holes formed in the pinion shaft provided in the planetary carrier of the planetary gear mechanism of the automatic transmission of the vehicle so that the pinion shaft and the pinion supported on the outer periphery thereof are provided. In order to lubricate the sliding surface, the oil reservoir that opens toward the oil hole of the pinion shaft is recessed in the rotating member that rotates around the rotation axis even when the planetary carrier is stopped, so that the planetary carrier rotates. Even when oil supply by centrifugal force is stopped, lubrication oil supplied by centrifugal force from the rotating shaft to the oil reservoir of the rotating member is scattered toward the oil hole of the pinion shaft, so that the outer periphery of the pinion shaft slides. The moving surface can be effectively lubricated. In this way, it is not necessary to form an oil passage for lubrication in the planetary carrier itself, or to supply pressurized oil to the oil passage, and the rotation of the planetary carrier pinion shaft that has stopped rotating is simple. The lubricating oil can be reliably supplied with a simple structure.

  According to the second aspect of the present invention, the ribs extending toward the oil holes of the pinion shaft are formed at a plurality of circumferential positions of the oil sump formed in an annular shape so as to surround the rotation shaft. Lubricating oil can be effectively scattered by the ribs and supplied to the oil holes.

  According to the third aspect of the present invention, since the guide member that guides the lubricating oil scattered from the oil reservoir to the oil hole of the pinion shaft is provided, the lubricating oil can be efficiently supplied from the oil reservoir to the oil hole of the pinion shaft. Can do.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  1 to 4 show a first embodiment of the present invention. FIG. 1 is a skeleton diagram of an automatic transmission for a vehicle, FIG. 2 is a velocity diagram of the automatic transmission for a vehicle, and FIG. The principal part expanded sectional view of an automatic transmission, FIG. 4 is a perspective view of a ring gear hub.

  As shown in FIG. 1, an automatic transmission T having eight forward speeds and one reverse speed for a front engine / rear drive vehicle has an input shaft 13 connected to a crankshaft 11 of an engine E via a torque converter 12, A center shaft 36 fitted to the outer periphery of the rear portion (left side in the figure) of the input shaft 13 so as to be relatively rotatable, an output shaft 14 disposed coaxially with the input shaft 13, and a counter shaft 15 disposed parallel to the input shaft 13. The first planetary gear mechanism 16 and the second planetary gear mechanism 17 are disposed on the outer periphery of the input shaft 13 and the center shaft 36.

  The first planetary gear mechanism 16 includes a sun gear 18 fixed to the center shaft 36, a planetary carrier 19 supported on the outer periphery of the center shaft 36 so as to be relatively rotatable, a ring gear 21 fixed to the ring gear carrier 20, A plurality of pinions 22 supported rotatably on the planetary carrier 19, and the pinions 22 mesh with both the sun gear 18 and the ring gear 21.

  The second planetary gear mechanism 17 rotates to the sun gear 23 fixed to the center shaft 36, the planetary carrier 24 fixed to the output shaft 14, the ring gear 26 fixed to the ring gear carrier 25, and the planetary carrier 24. A plurality of pinions 27 that are freely supported are provided, and the pinions 27 mesh with both the sun gear 23 and the ring gear 26.

  The ring gear carrier 20 of the first planetary gear mechanism 16 can be constrained to the casing 28 via the first brake B 1, and the ring gear carrier 25 of the second planetary gear mechanism 17 is connected via the second brake B 2 and the one-way clutch 29. The casing 28 can be restrained. The input shaft 13 can be coupled to the center shaft 36 via the first clutch C1, and the input shaft 13 can be coupled to the planetary carrier 19 of the first planetary gear mechanism 16 via the second clutch C2.

  A first gear 30 fixed to the input shaft 13 meshes with a second gear 31 that is freely supported by the counter shaft 15 via a third clutch C3. The third gear 32 that is detachably supported by the input shaft 13 via the fourth clutch C4 meshes with the fourth gear 33 that is fixed to the counter shaft 15. The fifth gear 34 fixed to the counter shaft 15 meshes with the sixth gear 35 fixed to the ring gear carrier 20 of the first planetary gear mechanism 16.

  Next, the establishment of each gear stage will be described with reference to the speed diagram of the automatic transmission T shown in FIG. 2 and the clutch and brake engagement table shown in Table 1.

  First, establishment of the first forward speed to the fifth forward speed will be described. When the first forward speed to the fifth forward speed are established, the input shaft 13 is coupled to the center shaft 36 by the engagement of the first clutch C1, and the center shaft 36 rotates at the same speed as the input shaft 13.

  When the second brake B2 is engaged and the ring gear carrier 25 and the ring gear 26 of the second planetary gear mechanism 17 are non-rotatably constrained to the casing 28 in order to establish the first forward speed, the sun gear fixed to the center shaft 36 is secured. The rotation of the motor 23 is decelerated and transmitted to the planetary carrier 24, and the output shaft 14 integrated with the planetary carrier 24 rotates to establish the first forward speed.

  At this time, the ring gear carrier 25 of the second planetary gear mechanism 17 and the planetary carrier 19 of the first planetary gear mechanism 16 integral with the ring gear 26 are stopped, but the rotation of the sun gear 18 of the first planetary gear mechanism 16 is stopped by the pinion 22. Is transmitted to the ring gear 21, via which the ring gear 21 rotates.

  Further, in order to establish the forward second speed gear stage, when the first brake B1 is engaged and the ring gear carrier 20 and the ring gear 21 of the first planetary gear mechanism 16 are non-rotatably constrained to the casing 28, they are fixed to the center shaft 36. The rotation of the sun gear 18 is decelerated and transmitted from the planetary carrier 19 to the ring gear carrier 25 and the ring gear 26 of the second planetary gear mechanism 17. Then, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward second speed gear.

  When the fourth clutch C4 is engaged to establish the third forward speed, the rotation of the input shaft 13 causes the fourth clutch C4, the third gear 32, the fourth gear 33, the counter shaft 15, the fifth gear 34, It is transmitted to the ring gear 21 via the ring gear carrier 20 of the sixth gear 35 and the first planetary gear mechanism 16. Then, the planetary carrier 19 is rotated by the differential rotation of the ring gear 21 and the sun gear 18 of the first planetary gear mechanism 16, and the rotation of the planetary carrier 19 is transmitted to the ring gear carrier 25 and the ring gear 26 of the second planetary gear mechanism 17. Then, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward third gear.

  When the third clutch C3 is engaged to establish the forward fourth speed, the rotation of the input shaft 13 causes the first gear 30, the second gear 31, the third clutch C3, the counter shaft 15, the fifth gear 34, It is transmitted to the ring gear 21 via the ring gear carrier 20 of the sixth gear 35 and the first planetary gear mechanism 16. Then, the planetary carrier 19 is rotated by the differential rotation of the ring gear 21 and the sun gear 18 of the first planetary gear mechanism 16, and the rotation of the planetary carrier 19 is transmitted to the ring gear carrier 25 and the ring gear 26 of the second planetary gear mechanism 17. Then, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward fourth speed gear.

  When the second clutch C2 is engaged to establish the forward fifth gear, the rotation of the input shaft 13 is directly performed through the second clutch C2 and the planetary carrier 19 of the first planetary gear mechanism 16 as it is. 17 ring gears 26. As a result, the sun gear 23 and the ring gear 26 of the second planetary gear mechanism 17 rotate at the same speed as the input shaft 13, so that the second planetary gear mechanism 17 is locked, and the planetary carrier 24 and the output shaft 14 are input. The fifth forward speed is established by rotating at the same speed as the shaft 13.

  Next, the establishment of the sixth forward speed to the eighth forward speed will be described. At the time of establishment of the sixth forward speed to the eighth forward speed, the second clutch C2 is engaged so that the rotation of the input shaft 13 is performed via the second clutch C2 and the planetary carrier 19 of the first planetary gear mechanism 16. The planetary carrier 19 of the first planetary gear mechanism 16 and the ring gear 26 of the second planetary gear mechanism 17 rotate at the same speed as the input shaft 13.

  When the third clutch C3 is engaged to establish the sixth forward speed, the rotation of the input shaft 13 causes the first gear 30, the second gear 31, the third clutch C3, the counter shaft 15, the fifth gear 34, 6 is transmitted to the ring gear 21 through the ring gear carrier 20 of the first planetary gear mechanism 16. Then, the sun gear 18 is rotated by the differential rotation of the ring gear 21 of the first planetary gear mechanism 16 and the planetary carrier 19, and the center shaft 36 and the sun gear 23 of the second planetary gear mechanism 17 are integrated with the sun gear 18 of the first planetary gear mechanism 16. Rotate. As a result, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated, thereby establishing a forward sixth speed.

  When the fourth clutch C4 is engaged to establish the forward seventh speed, the rotation of the input shaft 13 causes the fourth clutch C4, the third gear 32, the fourth gear 33, the counter shaft 15, the fifth gear 34, 6 is transmitted to the ring gear 21 through the ring gear carrier 20 of the first planetary gear mechanism 16. Then, the sun gear 18 is rotated by the differential rotation of the ring gear 21 of the first planetary gear mechanism 16 and the planetary carrier 19, and the center shaft 36 and the sun gear 23 of the second planetary gear mechanism 17 are integrated with the sun gear 18 of the first planetary gear mechanism 16. Rotate. As a result, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward seventh speed gear stage.

  When the first brake B1 is engaged to establish the forward eighth speed, the ring gear carrier 20 and the ring gear 21 of the first planetary gear mechanism 16 are restrained to the casing 28 so as not to rotate. Then, the sun gear 18 is rotated by the differential rotation of the ring gear 21 of the first planetary gear mechanism 16 and the planetary carrier 19, and the center shaft 36 and the sun gear 23 of the second planetary gear mechanism 17 are integrated with the sun gear 18 of the first planetary gear mechanism 16. Rotate. As a result, the planetary carrier 24 is rotated by the differential rotation of the ring gear 26 and the sun gear 23 of the second planetary gear mechanism 17, and the output shaft 14 integrated with the planetary carrier 24 is rotated to establish the forward 8-speed gear stage.

  Next, the establishment of the reverse gear will be described.

  When the fourth clutch C4 is engaged to establish the reverse gear, the rotation of the input shaft 13 causes the fourth clutch C4, the third gear 32, the fourth gear 33, the counter shaft 15, the fifth gear 34, and the sixth gear. 35 and the ring gear carrier 20 of the first planetary gear mechanism 16 is transmitted to the ring gear 21. At the same time, when the second brake B2 is engaged, the ring gear carrier 25 of the second planetary gear mechanism 17 and the planetary carrier 19 of the first planetary gear mechanism 16 are restrained by the casing 28 so as not to rotate. As a result, the sun gear 18 of the first planetary gear mechanism 16 rotates, and the sun gear 23 of the second planetary gear mechanism 17 integral with the sun gear 18 rotates, so that the second planetary gear is rotated by the differential rotation with the stopped ring gear 26. The planetary carrier 24 of the mechanism 17 rotates in the reverse direction, and the output shaft 14 integrated with the planetary carrier 24 rotates in the reverse direction, thereby establishing the reverse gear.

  At this time, the planetary carrier 19 of the first planetary gear mechanism 16 is stopped by the engagement of the second brake B2, but the ring gear 21 of the first planetary gear mechanism 16 is rotated by the engagement of the fourth clutch C4.

  Next, the structure of the first planetary gear mechanism 16 will be described in detail based on FIG. 3 and FIG.

  As shown in FIG. 3, the sun gear 18 of the first planetary gear mechanism 16 is splined to the outer periphery of the center shaft 36 supported on the outer periphery of the input shaft 13 via the needle bearing 41. A clutch inner 43 of the second clutch C <b> 2 is supported on the outer periphery of the center shaft 36 via needle bearings 42, 42 so as to be relatively rotatable, and the planetary carrier 19 is spline-coupled to the clutch inner 43. Accordingly, the planetary carrier 19 can rotate relative to the center shaft 36. A pinion shaft 44 is fitted to the planetary carrier 19, and the pinion 22 is rotatably supported on the outer periphery of the pinion shaft 44 via needle bearings 45 and 45. A ring gear hub 47 is supported on the outer periphery of a portion where the planetary carrier 19 is splined to the clutch inner 43 via a needle bearing 46 so as to be relatively rotatable.

  As apparent from FIG. 4, the substantially disc-shaped ring gear hub 47 has a shaft hole 47a into which the needle bearing 46 is fitted at the center, and an annular oil reservoir 47b on the outer periphery of the shaft hole 47a on one side surface thereof. Is recessed. In the oil reservoir 47b, a plurality of (six in the embodiment) ribs 47c. Further, the ring gear hub 47 includes a plurality of (in the embodiment, twelve) engaging holes 47d... On the outer side in the radial direction of the oil reservoir 47b, and a large number of uneven portions 47e.

  3, the ring gear 21 meshing with the pinions 22 is provided with a plurality of engaging projections 21a projecting on one end side in the axial direction, and the engaging projections 21a are engaged with the engaging holes 47d. The ring gear 21 is coupled to the ring gear hub 47 by combining and fixing with the circlip 48. The ring gear 21 is coupled to the ring gear carrier 20 by engaging the uneven portions 47 e formed on the outer peripheral surface of the ring gear hub 47 with the uneven portions 20 a formed on the end portion of the ring gear carrier 20. Further, by engaging a large number of concave and convex portions 19a protruding from the radial outer end of the planetary carrier 19 with a large number of concave and convex portions 25a formed on the inner peripheral surface of the ring gear carrier 25 of the second planetary gear mechanism 17, Planetary carrier 19 is coupled to ring gear carrier 25.

  One end of an oil hole 44 a is opened at the end face of the pinion shaft 44 on the ring gear hub 47 side, and this oil hole 44 a faces the oil reservoir 47 b of the ring gear hub 47. An oil hole 13b, 13c extending in the radial direction from an oil passage 13a formed in the axial direction inside the input shaft 13 penetrates to the outer peripheral surface and is fitted to the outer side in the radial direction via needle bearings 42, 42. Oil holes 36a and 36b extending in the radial direction through the shaft 36 penetrate to the outer peripheral surface. Oil holes 43 a and 19 b extending in the radial direction pass through the clutch inner 43 and the planetary carrier 19 positioned on the radially outer side of the center shaft 36. Further, a plurality (four in the embodiment) of oil holes 44b through the oil holes 44a of the pinion shaft 44 penetrate in the radial direction.

  Now, since the planetary carrier 19 of the first planetary gear mechanism 16 stops rotating when the first forward speed and the reverse speed described above are established, the lubricating oil adhering to the planetary carrier 19 moves radially outward by centrifugal force. Then, it hardly flows into the oil hole 44a of the pinion shaft 44 and lubricates the sliding surface with the pinions 22. However, since the ring gear hub 47 that supports the ring gear 21 rotates when the first forward speed and the reverse speed in which the planetary carrier 19 of the first planetary gear mechanism 16 stops rotating, the ring gear hub 47 rotates the pinion shaft. Lubricating oil can be supplied to the 44 oil holes 44a to effectively lubricate the pinion 22.

  That is, the lubricating oil supplied from the oil passage 13a of the input shaft 13 through the oil hole 13b lubricates the needle bearing 41, then lubricates the needle bearings 42 and 42 through the oil hole 36a of the center shaft 36, and further the clutch inner. After the needle bearing 46 is lubricated through the oil hole 43 a of 43 and the gap between the planetary carrier 19 and the clutch inner 43, the oil is supplied to the oil reservoir 47 b of the ring gear hub 47. The lubricating oil supplied from the oil passage 13 a of the input shaft 13 through the oil hole 13 c is supplied to the oil reservoir 47 b of the ring gear hub 47 through the oil hole 19 b of the planetary carrier 19.

  At this time, since the ring gear hub 47 is in a rotating state, the lubricating oil held in the oil reservoir 47b is repelled in the axial direction by the plurality of ribs 47c of the oil reservoir 47b, and the oil of each pinion shaft 44 opposed thereto. It is supplied to the hole 44a. The lubricating oil supplied to the oil holes 44a passes through the oil holes 44b extending in the radial direction from the oil holes 44a, and can lubricate the needle bearings 45, 45 between the pinion 22 and the oil holes 44a.

  As described above, when the planetary carrier 19 is stopped and it is difficult to supply the lubricating oil to the oil hole 44a of the pinion shaft 44 by centrifugal force, the centrifugal force of the ring gear hub 47 rotating in the vicinity of the planetary carrier 19 is used. Since the lubricating oil can be supplied to the oil hole 44a of the pinion shaft 44, a special lubricating oil passage is formed inside the planetary carrier 19, or the lubricating oil is supplied at a high pressure. This eliminates the need for a means, prevents an increase in the size of the planetary carrier 19 and contributes to cost reduction.

  Next, a second embodiment of the present invention will be described with reference to FIG.

  In the second embodiment, an annular guide member 49 facing the radially outer end of the oil reservoir 47b of the ring gear hub 47 is provided on the side surface of the planetary carrier 19 of the first planetary gear mechanism 16 on the ring gear hub 47 side. It is. Since the guide member 49 extends from the radially outer end of the oil reservoir 47b to the radially outer end of the oil hole 44a of the pinion shaft 44, the lubricating oil in the oil reservoir 47b is not wasted into the oil hole 44a of the pinion shaft 44 without waste. I can guide you.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. Is possible.

  For example, in the embodiment, the oil sump 47 b is formed in the ring gear hub 47, but the member that forms the oil sump 47 b is not limited to the ring gear hub 47.

Skeleton diagram of automatic transmission for vehicle according to first embodiment Speed diagram of automatic transmission for vehicles Expanded cross-sectional view of the main parts of an automatic transmission for vehicles Perspective view of ring gear hub The figure corresponding to the said FIG. 3 based on 2nd Embodiment.

Explanation of symbols

13 Input shaft (rotating shaft)
16 First planetary gear mechanism (planetary gear mechanism)
18 Sun gear 19 Planetary carrier 21 Ring gear 22 Pinion 36 Center shaft (rotating shaft)
44 Pinion shaft 44a Oil hole 47 Ring gear hub (rotating member)
47b Oil reservoir 47c Rib 49 Guide member

Claims (3)

A sun gear (18), a planetary carrier (19) and a ring gear (21) are arranged coaxially around the rotation shafts (13, 36), and are supported on the planetary carrier (19) via a pinion shaft (44). ) Is meshed with the sun gear (18) and the ring gear (21), and the pinion is supplied with lubricating oil supplied to an oil hole (44a) formed in the pinion shaft (44). In the lubricating structure of the automatic vehicle transmission that lubricates the sliding surface between the shaft (44) and the pinion (22),
An oil sump that opens at least toward the oil hole (44a) of the pinion shaft (44) is provided in the rotating member (47) rotating around the rotating shaft (13, 36) while the planetary carrier (19) is stopped. (47b) is recessed, and the lubricating oil supplied from the rotating shaft (13, 36) to the oil sump (47b) is scattered toward the oil hole (44a) of the pinion shaft (44). Lubricating structure for automatic transmission for vehicles.   The oil sump (47b) is formed in an annular shape so as to surround the rotating shaft (13, 36), and ribs projecting toward the oil hole (44a) of the pinion shaft (44) at a plurality of locations in the circumferential direction. 47. The lubricating structure for an automatic transmission for a vehicle according to claim 1, wherein 47c) is formed.   The vehicle according to claim 1 or 2, further comprising a guide member (49) for guiding lubricating oil scattered from the oil reservoir (47b) to an oil hole (44a) of the pinion shaft (44). Lubrication structure for automatic transmissions.

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