JP2007046693A - Lubricating device for automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubricating device for an automatic transmission capable of preventing shortage of a lubricant oil volume fed by a pinion shaft to support a long pinion. <P>SOLUTION: The automatic transmission 10 comprises a long pinion LP engaging with a sun gear S2, a short pinion SP, an axial ring gear R2 and a planetary gear PU having a carrier CR2 provided with a pinion shaft PS which supports freely rotatably the long pinion LP. Inside the pinion shaft PS, an axial oil passage a6 communicating with another oil supply passage a5 to supply the lubricating oil from one way of an end part is bored axially and is also bored on a different position in the axial direction and exhaust oil passages a7, a8 which open in the outer peripheral side of the pinion shaft PS from the axial oil passage a6 are bored. The exhaust oil passages a7, a8 are bored in the outer peripheral side than the revolution orbit of the pinion shaft PS. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a lubrication device for an automatic transmission mounted on, for example, a vehicle, and more specifically to a pinion shaft that rotatably supports a long pinion that meshes with a plurality of different gears in the axial direction. The present invention relates to a lubricating device for an automatic transmission having a plurality of discharged oil passages at positions.

  2. Description of the Related Art Conventionally, for example, an automatic transmission mounted on a vehicle or the like has been provided with a transmission gear mechanism having a planetary gear, and by changing a transmission path in the transmission gear mechanism, shifting, forward / reverse switching, and the like are possible. . A planetary gear of such a transmission gear mechanism is generally composed of a sun gear, a ring gear, a carrier that rotatably supports a pinion that meshes with the sun gear or the ring gear, and the like. In order to prevent this and improve the durability, a lubricating oil passage (lubricating device) is provided for performing appropriate lubrication by supplying lubricating oil to these gears.

  By the way, in the planetary gear, a pinion is fitted on the pinion shaft and is rotatably supported, and it is necessary to lubricate a sliding portion (particularly a needle roller) between the pinion and the pinion shaft. Therefore, an axial oil passage and an oil passage that opens to the outer peripheral side from the axial oil passage are drilled inside the pinion shaft, and the lubricating oil is passed between the pinion and the pinion shaft through these oil passages. Have been proposed (Patent Document 1).

  In the pinion or the pinion shaft, the load position (hereinafter referred to as “load point”) and the magnitude of the load change depending on the speed of the shift stage and the drive source (engine or the like). An oil passage that opens to the outer peripheral side from the axial oil passage is opened between the load region and the non-load region of the pinion shaft (that is, aiming at the load point) to prevent the pinion shaft from being worn.

Japanese Patent No. 2792783

  By the way, among the planetary gears of the transmission gear mechanism as described above, for example, a Ravigneaux type has a long pinion that meshes with a plurality of different gears in the axial direction, and a pinion that supports such a long pinion The shaft is longer in the axial direction than a general simple planetary gear. Even if an axial oil passage is provided in such a long pinion shaft and an oil passage that opens to the outer peripheral side is provided, for example, at one location near the center from the axial oil passage, the lubricating oil is supplied in the axial direction. There is a risk that the amount of lubricating oil will be insufficient at the end of this. Therefore, it is conceivable to pierce a plurality of oil passages that open to the outer peripheral side from the axial oil passage in the pinion shaft at different positions in the axial direction.

  However, if an oil passage that opens from the axial oil passage in the pinion shaft to the outer peripheral side is simply formed at a different position in the axial direction, the lubricating oil is supplied to the axial oil passage in the pinion shaft. There is a possibility that the amount of oil discharged from the near oil passage and the far oil passage is different, and eventually there is a portion where the amount of the lubricating oil is insufficient at the axial position on the long pinion shaft.

  In addition, for example, Ravigneaux type planetary gears as described above, for example, two sun gears (for example, one via a short pinion) and one ring gear mesh at different positions in the axial direction of the long pinion. There is a problem that the load point changes greatly according to the rotational speed input to each gear or the input torque (transmitted). For this reason, it is difficult to simply open the oil passage aiming at the load point, and it is required to supply a large amount of lubricating oil to the portion in the axial direction that receives a large load.

  Further, the one that opens the oil passage aiming at the above-mentioned load point is opened on the inner peripheral side of the revolution track of the pinion shaft, so that when the carrier having the pinion shaft is rotated at high speed, it is discharged by centrifugal force. There is a problem that the amount of lubricating oil decreases. In such cases, the load point does not change much, and it may be required to lubricate only in the vicinity of the load point, but if the load point changes significantly as described above, If the amount of lubricating oil becomes insufficient while rotating, there is a possibility that the improvement of durability may be hindered.

  Accordingly, the present invention provides a lubricating device for an automatic transmission in which a plurality of oil discharge passages are drilled from the revolving raceway of the pinion shaft toward the outer peripheral side, thereby preventing an insufficient amount of lubricating oil. This is the first purpose.

  In the present invention, a plurality of drain oil passages are formed by being inclined to the front side or the rear side in the revolution direction with respect to the radial direction from the center of the revolution orbit of the pinion shaft, and thus at different positions in the axial direction. A second object is to provide a lubricating device for an automatic transmission capable of optimizing the amount of lubricating oil discharged from a plurality of discharged oil passages.

The present invention according to claim 1 (see, for example, FIGS. 1 to 14) includes a carrier (CR2) including a pinion (for example, LP) and a pinion shaft (PS) that rotatably supports the pinion (for example, LP). In a lubricating device (1) of an automatic transmission (10) having a planetary gear (PU) having:
An axial oil passage (a6) drilled in the axial direction inside the pinion shaft (PS);
A supply oil passage (a5) for supplying lubricating oil from one end of the axial oil passage (a6);
A plurality of discharge oil passages (a7, a8) opened to the outer peripheral side of the pinion shaft (PS) from the axial oil passage (a6) and drilled at different positions in the axial direction;
The plurality of drain oil passages (a7, a8) are drilled from the revolution orbit (Or) of the center (CT2) of the pinion shaft (PS) toward the outer peripheral side.
The automatic transmission lubrication device (1) is characterized by the above.

According to the second aspect of the present invention (see, for example, FIGS. 1 to 14), the plurality of drain oil passages (a7, a8) are the centers of the revolution orbits (Or) of the center (CT2) of the pinion shaft (PS). With respect to the radial direction from (CT1) (for example, arrow A), the pinion shaft (PS) is drilled to be inclined forward or backward in the revolution rotation direction (ω) of the pinion shaft (PS).
The lubricating device (1) for an automatic transmission according to claim 1, wherein the lubricating device (1) is an automatic transmission.

According to a third aspect of the present invention (see, for example, FIGS. 1 to 14), the plurality of discharge oil passages are a front-side discharge oil passage (a7) close to the supply oil passage (a5) in the axial direction, A rear drain oil passage (a8) farther from the supply oil passage (a5) than the front drain oil passage (a7) in the axial direction,
A lubricating device (1) for an automatic transmission according to claim 2, wherein the lubricating device (1) is provided.

The present invention according to claim 4 (see, for example, FIG. 5, FIG. 6, FIG. 13 and FIG. 14) is such that the front drain oil passages (a7 ₁ , a7 ₂ ) are in the rotational direction of rotation of the pinion shaft (PS). (Ω) is inclined and drilled forward,
The lubricating device (1 ₁ , 1 ₂ ) for an automatic transmission according to claim 3, characterized in that:

The present invention according to claim 5 (see, for example, FIG. 5, FIG. 13, and FIG. 14) is such that the back-side drain oil passage (a8 ₁ ) is the front side in the revolution rotation direction (ω) of the pinion shaft (PS). Inclined and drilled,
A lubricating device (1 ₁ ) for an automatic transmission according to claim 4, characterized in that:

According to a sixth aspect of the present invention (see, for example, FIGS. 6, 13, and 14), the back-side drain oil passage (a8 ₂ ) is on the rear side in the revolution rotation direction (ω) of the pinion shaft (PS). Inclined and drilled,
A lubricating device (1 ₂ ) for an automatic transmission according to claim 4, characterized in that:

According to a seventh aspect of the present invention, the automatic transmission (10) is configured such that the pinion shaft (i.e., near the front-side drain oil passages (a7 ₁ , a7 ₂ )) as the rotation of the carrier (CR2) increases. The load (FPr) acting on the outer peripheral side of PSr) is reduced, and the load (FPf) acting on the outer peripheral side of the pinion shaft (ie PSf) in the vicinity of the back side drain oil passages (a8 ₁ , a8 ₂ ) is reduced. Increasing,
A lubricating device (1 ₁ , 1 ₂ ) for an automatic transmission according to any one of claims 4 to 6, characterized in that:

In the present invention according to claim 8 (see, for example, FIG. 7, FIG. 8, FIG. 13, and FIG. 14), the front drain oil passage (a7 ₃ , a7 ₄ ) is the direction of revolution of the pinion shaft (PS). (Ω) is inclined and drilled to the rear side,
A lubricating device (1 ₃ , 1 ₄ ) for an automatic transmission according to claim ₃ , wherein:

According to a ninth aspect of the present invention (see, for example, FIGS. 8, 13, and 14), the back side drain oil passage (a8 ₄ ) is a front side in the revolution rotation direction (ω) of the pinion shaft (PS). Inclined and drilled,
The lubricating device (1 ₄ ) for an automatic transmission according to claim 8, wherein:

According to a tenth aspect of the present invention (see, for example, FIGS. 7, 13, and 14), the back drain oil passage (a 8 ₃ ) is a rear side in the revolution rotation direction (ω) of the pinion shaft (PS). Inclined and drilled,
The lubricating device (1 ₃ ) for an automatic transmission according to claim 8, wherein

The present invention according to claim 11 (see, for example, FIGS. 1 to 14), the planetary gear (PU) is a Ravigneaux type planetary gear,
The plurality of different gears mesh with the first sun gear (S2) meshed with the long pinion (LP) and the second sun gear (S3) at different positions in the axial direction of the first sun gear (S2). A short pinion (SP) meshing with the long pinion (LP), and a ring gear (R2) meshing with the long pinion (LP) on the outer peripheral side of the second sun gear (S3),
The pinion shaft (PS) is configured to rotatably support the long pinion (LP).
The automatic transmission lubrication device (1) according to any one of claims 1 to 10, wherein the lubricating device (1) is an automatic transmission.

According to a twelfth aspect of the present invention, in the automatic transmission (10), a central shaft (12, 13) disposed from the front to the rear and a front portion of the central shaft (12, 13) are freely rotatable. A case (11) having a partition member (11b, 11c) to be supported on an oil pump, and an oil pump (15) disposed in the partition member (11b),
The partition member (11c) has an oil passage in the partition wall (a0) that communicates with the discharge portion of the oil pump (15) and opens to the outer periphery of the central shaft (12).
The central shaft (12) communicates with the oil passage in the partition wall (a0) and communicates axially rearward in the central shaft (12, 13) with the central shaft oil passages (a1, a2, a3). , A4)
The planetary gear (PU) is disposed on the outer peripheral side of the rear portion of the central shaft (12, 13),
The supply oil passage (a5) is provided in a side plate (CRr) on the rear side of the carrier (CR2) and communicates with the oil passage in the central shaft (a4).
Based on the hydraulic pressure generated in the oil pump (15), the oil passage in the partition wall (a0), the oil passages in the central shaft (a1, a2, a3, a4), the supply oil passage from the oil pump (15). Lubricating oil is supplied to the axial oil passage (a6) via (a5).
The lubricating device (1) for an automatic transmission according to any one of claims 1 to 11, characterized in that:

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for convenience for making an understanding of invention easy, and has no influence on the structure of a claim. It is not a thing.

  According to the first aspect of the present invention, since the plurality of drain oil passages are drilled from the revolving track at the center of the pinion shaft toward the outer peripheral side, the centrifugal force is increased even when the carrier having the pinion shaft is at a high speed. Therefore, it is possible to prevent the amount of lubricating oil discharged from being reduced, and to always ensure the amount of lubricating oil. As a result, it is possible to prevent wear or seizure between the pinion and the pinion shaft, thereby improving durability.

  According to the second aspect of the present invention, the plurality of drain oil passages are perforated by being inclined forward or rearward in the revolution rotation direction of the pinion shaft with respect to the radial direction from the center of the revolution orbit at the center of the pinion shaft. Therefore, the lubricating oil supplied from the supply oil passage to the axial oil passage can be appropriately distributed.

  According to the third aspect of the present invention, the plurality of discharge oil passages are closer to the supply oil passage in the axial direction and closer to the supply oil passage in the axial direction than the front discharge oil passage in the axial direction. Since it comprises the back side discharge oil passage, the lubricating oil can be appropriately distributed at different positions in the axial direction between the pinion and the pinion shaft.

  According to the fourth aspect of the present invention, the front side discharge oil passage is inclined and drilled forward in the revolution rotation direction of the pinion shaft. The amount of lubricating oil to be discharged can be reduced as appropriate, and the amount of lubricating oil supplied to the back-side discharged oil passage can be increased appropriately.

  According to the fifth aspect of the present invention, the back side discharge oil passage is inclined and drilled forward in the revolving rotation direction of the pinion shaft. The amount of lubricating oil to be discharged can be appropriately reduced.

  According to the sixth aspect of the present invention, the back side discharge oil passage is inclined and drilled to the rear side in the revolution rotation direction of the pinion shaft. The amount of lubricating oil discharged can be increased appropriately.

  According to the seventh aspect of the present invention, in the automatic transmission, as the rotation of the carrier increases, the load acting on the outer peripheral side of the pinion shaft in the vicinity of the front side discharge oil passage decreases and the vicinity of the back side discharge oil passage. Although the load acting on the outer peripheral side of the pinion shaft in the shaft increases, the amount of lubricating oil discharged from the front side discharge oil passage can be appropriately reduced and supplied to the back side discharge oil passage as the carrier speed increases. Since the amount of lubricating oil to be increased can be appropriately increased, lubrication can be optimized by using the lubricating device of the automatic transmission.

  According to the eighth aspect of the present invention, the front-side drain oil passage is inclined and drilled to the rear side in the revolution rotation direction of the pinion shaft. The amount of lubricating oil to be discharged can be increased as appropriate, and the amount of lubricating oil supplied to the back-side discharged oil passage can be reduced as appropriate.

  According to the ninth aspect of the present invention, the back side discharge oil passage is inclined and drilled forward in the revolving rotation direction of the pinion shaft. The amount of lubricating oil to be discharged can be appropriately reduced.

  According to the tenth aspect of the present invention, the back-side drain oil passage is inclined and drilled to the rear side in the revolution rotation direction of the pinion shaft. The amount of lubricating oil to be discharged can be increased as appropriate, and in combination with the increase in the amount of lubricating oil discharged from the front side discharge oil passage, the front side discharge oil passage and the back side discharge oil passage are relatively The amount of lubricating oil discharged from the engine can be equalized.

  According to the eleventh aspect of the present invention, the planetary gear is a Ravigneaux type planetary gear, and a plurality of different gears mesh with the second sun gear at a position different in the axial direction from the first sun gear and the first sun gear. In addition, a short pinion that meshes with the long pinion and a ring gear that meshes with the long pinion on the outer peripheral side of the second sun gear, and the pinion shaft rotatably supports the long pinion, so the rotational speed of the gear stage and the drive source The load point and its load vary greatly depending on the torque input from the drive source, but the amount of lubricating oil can be constantly reduced by drilling the drain oil passage from the revolution track of the pinion shaft toward the outer periphery. This prevents wear and seizure between the long pinion and the pinion shaft. Things can be, it is possible to improve the durability. Further, in particular, the front side drain oil passage and the back side drain oil passage are appropriately inclined to the front side or the rear side in the revolving rotation direction of the pinion shaft with respect to the radial direction, so that at different positions in the axial direction. Lubricating oil can be dispensed as appropriate and can respond to significant changes in load points and loads.

  According to the twelfth aspect of the present invention, lubricating oil is supplied from the oil pump to the axial oil passage through the oil passage in the partition wall, the oil passage in the central shaft, and the supply oil passage based on the hydraulic pressure generated by the oil pump. Therefore, although the amount of lubricating oil supplied to the axial oil passage is small, it is possible to prevent the amount of lubricating oil discharged by centrifugal force from decreasing even when the carrier rotates at high speed. Can be ensured.

  Hereinafter, embodiments according to the present invention will be described with reference to the drawings. First, a schematic configuration and operation of an automatic transmission to which the present invention can be applied will be described with reference to FIGS.

  As shown in FIG. 1, for example, an automatic transmission 10 that is optimal for use in an FR type vehicle includes a torque converter 5 and a transmission mechanism 2 in a case 11, and an output from an engine (drive source) is The signal is input to the input shaft 3 of the automatic transmission 10 and input to the input shaft (center shaft) 12 of the transmission mechanism 2 via the torque converter 5. The torque converter 5 is provided with a lock-up clutch 4.

  The speed change mechanism 2 is provided with a simple planetary gear PR and a Ravigneaux type planetary gear unit (planetary gear) PU that is configured to connect two planetary gears. The simple planetary gear SP includes a sun gear S1, a carrier CR1 that meshes with the sun gear S1 via a pinion P1, and a ring gear R1 that meshes with the carrier CR1, and the input to the ring gear R1 of the simple planetary SP. The shaft 12 is connected. In addition, the sun gear S1 is fixedly supported by a boss member 11c and a sleeve-like member 11e fixed to the case 11, which will be described in detail later, and the carrier CR is connected to the clutch C-3 and the clutch C-1. Has been.

  On the other hand, the planetary gear unit PU has two sun gears S2 (a plurality of different gears) and a sun gear S3, and a carrier CR2 that has a long pinion LP and a short pinion SP (a plurality of different gears) and meshes with the sun gears S2 and S3. , And a ring gear R2 (a plurality of different gears) meshing with the carrier CR2. The sun gear S2 is connected to the clutch C-3 and is connected to the brake B-1. When the clutch C-3 is engaged, the sun gear S2 is connected to the carrier CR1 and is connected to the case 11 by the brake B-1. When locked against it, it is fixed so that it cannot rotate. The sun gear S3 is connected to the clutch C-1, and is connected to the carrier CR1 when the clutch C-1 is engaged.

  One end of the carrier CR2 is connected to the clutch C-2, and when the clutch C-2 is engaged, the carrier CR2 is connected to the input shaft 12 via the intermediate shaft (center shaft) 13, and the other end is connected to the one-way clutch. It is connected to F-1 and connected to the brake B-2. The one-way clutch F-1 restricts rotation in one direction and is locked to the case 11 by the brake B-1. It is fixed so that it cannot rotate. The ring gear R3 is connected to the output shaft 14 of the speed change mechanism 2, and the forward sixth speed is determined by the engagement states of the clutches C-1, C-2, C-3 and the brakes B-1, B-2. The rotation of the first gear and the reverse first gear is transmitted to the output shaft 14 and output to a drive wheel (not shown).

  Next, the operation of the automatic transmission 10 will be described. As shown in FIG. 2, when the shift ranges are the P (parking) range and the N (neutral) range, the clutches C-1, C-2, C-3 and the brakes B-1, B-2 are all released. In particular, since the clutches C-1, C-2, and C-3 are disengaged, the power transmission between the input shaft 12 and the output shaft 14 is disconnected.

  In the first forward speed (1st) state, as shown in FIG. 2, the clutch C-1 is engaged and the one-way clutch F-1 is engaged by a hydraulic control device (not shown). Then, as shown in FIG. 1, the rotation of the input shaft 12 is input to the ring gear R1, the decelerated rotation is output from the carrier CR1 by the fixed sun gear S1, and the decelerated rotation is output to the sun gear S3 via the clutch C-1. Rotation is input. The decelerated rotation of the sun gear S3 is further decelerated via the carrier CR2 whose rotation in one direction is restricted by the one-way clutch F-1, and is input to the ring gear R3. Communicated. During engine braking, the brake B-2 is engaged instead of the one-way clutch F-1, and the rotation of the carrier CR2 is fixed.

  In the second forward speed (2nd), as shown in FIG. 2, the clutch C-1 and the brake B-1 are engaged by a hydraulic control device (not shown). Then, as shown in FIG. 1, the rotation of the input shaft 12 is input to the ring gear R1, the decelerated rotation is output from the carrier CR1 by the fixed sun gear S1, and the decelerated rotation is output to the sun gear S3 via the clutch C-1. Rotation is input. On the other hand, the rotation of the sun gear S2 is fixed to the case 11 by the brake B-1. The carrier CR2 is decelerated and rotated by the decelerated rotation of the fixed sun gear S2 and sun gear S3, and the decelerated rotation of the sun gear S3 is output to the ring gear R3 via the carrier CR2, and the output shaft 14 is decelerated and rotated as the second gear. Is transmitted to.

  In the state of the third forward speed (3rd), as shown in FIG. 2, the clutch C-1 and the clutch C-3 are engaged by a hydraulic control device (not shown). Then, as shown in FIG. 1, the rotation of the input shaft 12 is input to the ring gear R1, the decelerated rotation is output from the carrier CR1 by the fixed sun gear S1, and the decelerated rotation is output to the sun gear S3 via the clutch C-1. The rotation is input, and the same reduced rotation is input to the sun gear S2 via the clutch C-3. Then, the carrier CR2 and the ring gear R3 become the same reduced speed rotation by the reduced speed rotation of the sun gear S2 and the sun gear S3, and are output from the ring gear R3, and transmitted to the output shaft 14 as the 3rd speed reduced speed rotation.

  In the fourth forward speed (4th), the clutch C-1 and the clutch C-2 are engaged by a hydraulic control device (not shown) as shown in FIG. Then, as shown in FIG. 1, the rotation of the input shaft 12 is input to the ring gear R1, the decelerated rotation is output from the carrier CR1 by the fixed sun gear S1, and the decelerated rotation is output to the sun gear S3 via the clutch C-1. Rotation is input. On the other hand, the rotation of the input shaft 12 is also input to the carrier CR2 via the clutch C-2. Then, the decelerated rotation of the sun gear S3 and the rotation of the input shaft 12 of the carrier CR2 are output to the ring gear R3 as decelerated rotation that is slightly decelerated, and are transmitted to the output shaft 14 as decelerated rotation of the fourth speed stage.

  In the fifth forward speed (5th), as shown in FIG. 2, the clutch C-2 and the clutch C-3 are engaged by a hydraulic control device (not shown). Then, as shown in FIG. 1, the rotation of the input shaft 12 is input to the ring gear R1, the decelerated rotation is output from the carrier CR1 by the fixed sun gear S1, and the decelerated rotation is output to the sun gear S2 via the clutch C-3. Rotation is input. On the other hand, the rotation of the input shaft 12 is also input to the carrier CR2 via the clutch C-2. Then, the reduced rotation of the sun gear S2 and the rotation of the input shaft 12 of the carrier CR2 are output to the ring gear R3 as an increased rotation that is slightly increased, and transmitted to the output shaft 14 as an increased rotation of the fifth gear. .

  In the sixth forward speed (6th), as shown in FIG. 2, the clutch C-2 and the brake B-1 are engaged by a hydraulic control device (not shown). Then, as shown in FIG. 1, the rotation of the input shaft 12 is input to the carrier CR2 via the clutch C-2. On the other hand, the rotation of the sun gear S2 is fixed to the case 11 by the brake B-1. Then, the fixed sun gear S2 and the rotation of the input shaft 12 of the carrier CR2 are output to the ring gear R3 as a speed-up rotation, and are transmitted to the output shaft 14 as a speed-up rotation of the sixth gear.

  In the state of the first reverse speed (R), as shown in FIG. 2, the clutch C-3 and the brake B-2 are engaged by a hydraulic control device (not shown). Then, as shown in FIG. 1, the rotation of the input shaft 12 is input to the ring gear R1, the decelerated rotation is output from the carrier CR1 by the fixed sun gear S1, and the decelerated rotation is output to the sun gear S2 via the clutch C-3. Rotation is input. On the other hand, the rotation of the carrier CR2 is fixed to the case 11 by the brake B-2. The decelerated rotation of the sun gear S2 is output as a reverse rotation to the ring gear R3 by the fixed carrier CR2, and is transmitted to the output shaft 14 as a reverse rotation of the first reverse speed.

  Next, the lubricating device 1 for an automatic transmission will be described with reference to FIG.

  As shown in FIG. 3, the automatic transmission 10 includes a transmission case 11 a that encloses the transmission mechanism 2, and the transmission mechanism 2 and the torque converter are disposed on the front side (left side in the figure) of the transmission case 11 a. A partition wall member 11b that separates from the wall 5 is provided. An oil pump 15 interlocking with the input shaft 3 as the automatic transmission 10 is disposed in the partition member 11b, and a boss member fixed to the partition member 11b so as to close the oil pump 15. 11c is provided. Further, a sleeve-like member 11e for fixing the stator of the torque converter 5 is fixed to the inner peripheral side of the boss member 11c, and the sun gear S1 is attached to the outer peripheral portion of the rear end of the sleeve-like member 11e. The tooth surface is formed. On the other hand, on the rear side (right side in the figure) of the mission case 11a, a partition member 11d that separates from an extension case (not shown) is integrally fixed. The mission case 11a, the partition member 11b, the boss member 11c, and the partition member 11d are integrally configured to form a case 11 of the automatic transmission 10.

  An input shaft 12 is fitted on the sleeve-shaped member 11e and is rotatably supported on the inner peripheral side of the sleeve-shaped member 11e. A rear end of the input shaft 12 is connected to the input shaft 12 with respect to the input shaft 12. And an intermediate shaft 13 that is rotatably supported. An output shaft 14 is fitted on the further rear end side of the intermediate shaft 13, and the output shaft 14 is rotatably supported by the partition member 11d. Thereby, the input shaft 12, the intermediate shaft 13, and the output shaft 14 are rotatably supported with respect to the case 11 on the same axis.

  A planetary gear unit PU, which is a main part of the present invention, is disposed on the outer peripheral side of the intermediate shaft 13. As described above, the planetary gear unit PU includes the sun gear S2, the sun gear S3, the carrier CR2 having the long pinion LP and the short pinion SP, and the ring gear R2.

  More specifically, a sleeve 16 that is rotatably fitted to the outer peripheral side of the intermediate shaft 13 is provided, and a tooth surface is formed as a sun gear S3 on the outer peripheral portion of the rear end of the sleeve 16. Further, a sleeve 17 that is rotatably fitted to the outer peripheral side of the sleeve 16 is provided, and a tooth surface is formed as a sun gear S2 on the outer peripheral portion of the rear end of the sleeve 17. Further, on the outer peripheral side of the sleeve 17, a front carrier plate CRf which is a side plate on the front side of the carrier CR2 is fitted and provided.

  On the other hand, on the outer peripheral side of the intermediate shaft 13 and on the rear side of the sun gear S3 of the sleeve 16, a rear carrier plate CRr which is a side plate on the rear side of the carrier CR2 is fitted and provided. The front carrier plate CRf and the rear carrier plate CRr are provided with a cylindrical pinion shaft PS fixed in the axial direction. A long pinion LP is provided on the outer peripheral side of the pinion shaft PS and a needle on the front side. A bearing bf and a needle bearing br on the rear side are rotatably supported and provided. The front half of the long pinion LP is engaged with the sun gear S2, and the rear half of the long pinion LP is engaged with the short pinion SP and the ring gear R2 (not shown).

  Next, the lubricating oil path that constitutes the lubricating device 1 of the automatic transmission will be described. An oil passage a0 is formed on the outer peripheral side of the sleeve member 11e by being closed by a boss member 11c, and the oil passage a0 communicates with the discharge port of the oil pump 15, Lubricating oil with the generated pressure as the original pressure is supplied. The oil passage a0 is sealed between the sleeve-like member 11e and the input shaft 12 by seal rings c1 and c2, and communicates with the oil passage a1 in the input shaft 12. The oil passage a1 is connected to the input shaft 12 communicates with an oil passage a2 drilled in the axial direction.

  The rear end side in the axial direction of the oil passage a2 opens toward the intermediate shaft 13, and the space between the input shaft 12 and the intermediate shaft 13 is sealed by a seal ring c3, so that the oil passage a2 and the intermediate shaft 13 are sealed. An oil passage a3 drilled in the axial direction is in communication therewith. The oil passage a3 communicates with an oil passage a4 formed in a radial direction at a position corresponding to the rear carrier plate CRr. The oil passage a4 is formed in the rear carrier plate CRr. And communicated with a supply oil passage a5 connected to one end (one end portion) of an axial oil passage a6 described later.

  From the axial oil passage a3 in the intermediate shaft 13, an oil passage a10 that opens toward the output shaft 14 and oil passages a11, a12, a13, a14, a15, a16 that open to the outer peripheral portion, respectively. a17, a18, a19, etc. are perforated, and oil passages a20, a21, a22, a23, a25, a26, etc. are perforated in the sleeve 16 and the sleeve 17, and slide with the output shaft 14. Lubricating oil is supplied to the parts and sliding parts of the planetary gear unit PU and the like can be lubricated.

  Further, oil passages a34, a35, a36 and the like opening in the outer peripheral portion are bored from the axial oil passage a2 in the input shaft 12, and each slide of the planetary gear PR not shown in FIG. Lubricating oil can be supplied to the moving part and the like to be lubricated. Further, oil passages a31, a332, a33 and the like opening in the outer peripheral portion are formed from the oil passage a0 formed in the sleeve-like member 11e, and each slide of the planetary gear PR not shown in FIG. Lubricating oil can be supplied to the parts and the like for lubrication.

  The oil path for supplying the lubricating oil to the supply oil path a5 is not limited to the above-described oil path, but is, for example, an oil path that is supplied from the output shaft side via a hydraulic controller (not shown). As long as the lubricating oil is supplied up to the supply oil passage a5, any type may be used.

  As shown in FIGS. 4A and 4B, the pinion shaft PS includes an axial oil passage a6 that is formed in the axial direction at the center CT2 of the pinion shaft PS. The opening at the rear end of the oil passage a6 communicates with the supply oil passage a5, and the lubricating oil supplied to the supply oil passage a5 is supplied to the axial oil passage a6. From the axial oil passage a6, the outer side of the revolving trajectory Or of the center CT2 of the pinion shaft PS that revolves on the center CT1 of the intermediate shaft 13 (that is, the central axis) as the carrier CR2 revolves. Two discharge oil passages a7 and a8 opened toward the front are formed.

  The two drain oil passages are an oil passage a7 formed in the pinion shaft rear portion PSr corresponding in the axial direction to a position where the long pinion LP meshes with the ring gear R2 and the short pinion SP, and the long pinion LP is a sun gear S2. And an oil passage a8 formed in the pinion shaft front side portion PSf corresponding in the axial direction to the position meshing with each other. The oil passage a7 is close to the supply oil passage a5 in the axial direction, and the supplied lubricating oil is discharged on the front side, and the oil passage a8 is supplied in the axial direction more than the oil passage a7. The supplied lubricating oil is discharged far from the path a5 on the front side. For this reason, in this specification, the oil passage a7 is referred to as a “front side discharge oil passage”, and the oil passage a8 is referred to as a “back side discharge oil passage”.

Next, the inclination directions of the front side discharge oil passage a7 and the back side discharge oil passage a8 will be described with reference to FIGS. Incidentally, the lubricating device 1 _1, 1 2, _{1 3,} 1 ₄ of the automatic transmission shown in FIGS. 5 to 8 is an embodiment of the present invention, a lubricating device for an automatic transmission shown in FIGS. 9 and 10 Reference numerals 101 ₅ and 101 ₆ are reference examples for comparing the effects of the present invention.

As shown in FIG. 5 (a), in the lubricating device 1 ₁ of the automatic transmission, the pinion shaft PS is roughly pinion shaft front portion PSf, pinion shaft central portion PSc, is constituted by the pinion shaft rear portion PSr , back side oil discharging passage a8 ₁ and is bored in the front side oil discharge passage a7 ₁ and the pinion shaft front portion PSf the pinion shaft rear portion PSr.該手front discharge oil passage a7 ₁ is opened in a substantially center of the needle bearing br above the rear side, also該奥side oil discharging passage a8 ₁ is substantially the center of the needle bearing bf of the front side of the above Is open.

As shown in FIG. 5 (b), the pinion shaft front portion PSf, rear side oil discharging passage a8 ₁ is emitted from the center of the intermediate shaft 13, i.e., the center of the orbit Or of the pinion shaft PS CT1 (see FIG. 4) With respect to the direction (the direction of arrow A in FIG. 4B), the pinion shaft PS is formed so as to be inclined forward in the revolution rotation direction ω. Moreover, as shown in FIG.5 (c), the drain oil path is not provided in the pinion shaft center part PSc. Then, as shown in FIG. 5 (d), the pinion shaft rear portion PSr, as well the front side oil discharge passage a7 _1, center CT2 (figure orbit Or the center of the intermediate shaft 13, i.e. pinion shafts PS 4) and is inclined to the front side of the revolution rotation direction ω of the pinion shaft PS with respect to the radial direction (the direction of arrow A in FIG. 4B).

Further, in the lubricating device _{1 2} of the automatic transmission shown in FIG. 6 (a), as shown in FIG. 6 (b), the rear-side oil discharge passage a8 _2, from the center CT1 of the orbit Or of the pinion shaft PS It is perforated so as to incline to the rear side in the revolution rotation direction ω of the pinion shaft PS with respect to the radial direction (the direction of arrow A) (see FIG. 4), and as shown in FIG. side discharge oil passage a7 ₂ is (see FIG. 4) relative to the pinion shaft PS of orbit radial direction from the center CT1 of Or (arrow a direction), inclined to the front side of the revolution direction ω of the pinion shaft PS It has been drilled. In addition, as shown in FIG.6 (c), the drain oil path is not similarly provided in the pinion shaft center part PSc.

Further, in the lubricating device _{1 3} of the automatic transmission shown in FIG. 7 (a), as shown in FIG. 7 (b), the rear-side oil discharge passage a8 ₃ is from the center CT1 of the orbit Or of the pinion shaft PS With respect to the radial direction (the direction of arrow A) (see FIG. 4), the pinion shaft PS is formed to be inclined to the rear side in the revolution rotation direction ω, and as shown in FIG. side discharge oil passage a7 ₃ is (see Fig. 4) relative to the pinion shaft PS of orbit radial direction from the center CT1 of Or (arrow a direction), inclined to the rear side of the revolution direction ω of the pinion shaft PS It has been drilled. In addition, as shown in FIG.7 (c), the drain oil path is not similarly provided in the pinion shaft center part PSc.

Then, in the lubricating device _{1 4} of the automatic transmission shown in FIG. 8 (a), as shown in FIG. 8 (b), the rear-side oil discharge passage a8 _4, from center CT1 of the orbit Or of the pinion shaft PS With respect to the radial direction (the direction of arrow A) (see FIG. 4), the pinion shaft PS is formed so as to incline forward in the revolution rotation direction ω of the pinion shaft PS, and as shown in FIG. side discharge oil passage a7 ₄ is (see FIG. 4) relative to the pinion shaft PS of orbit radial direction from the center CT1 of Or (arrow a direction), inclined to the rear side of the revolution direction ω of the pinion shaft PS It has been drilled. In addition, as shown in FIG.8 (c), the drain oil path is not similarly provided in the pinion shaft center part PSc.

In the lubricating device 101 ₅ of the automatic transmission as a reference example shown in FIG. 9 (a), as shown in FIG. 9 (b), the back-side discharge oil passage a8 _5, the pinion shaft PS orbit Or with respect to the radial direction from the center CT1 of have been drilled inclined rearward in the revolution direction ω of the pinion shaft PS, as shown in FIG. 9 (d), the front side oil discharge passage a7 ₅ is The pinion shaft PS is drilled toward the inner peripheral side from the revolution track Or, and in particular, is tilted from the rearmost position of the revolution track Or to the rear side in the revolution rotation direction ω. In addition, as shown in FIG.9 (c), the drain oil path is not similarly provided in the pinion shaft center part PSc.

Further, in the lubricating device 101 ₆ of the automatic transmission as a reference example shown in FIG. 10 (a), as shown in FIG. 10 (b), the rear-side oil discharge passage a8 ₆ is orbit of the pinion shaft PS Or with respect to the radial direction from the center of, but are bored inclined to the front side of the revolution direction ω of the pinion shaft PS, as shown in FIG. 10 (d), the front side oil discharge passage a7 ₆ is The pinion shaft PS is drilled toward the inner peripheral side from the revolution track Or, and is similarly tilted from the rearmost position of the revolution track to the rear side in the revolution rotation direction ω. In addition, as shown in FIG.10 (c), the drain oil passage is not similarly provided in the pinion shaft center part PSc.

  Incidentally, as shown in FIG. 5 to FIG. 8B, on the outer peripheral side of the pinion shaft front portion PSf, there is a shift speed, a rotational speed, and torque input from the engine (hereinafter simply referred to as “input torque”). Accordingly, a load FPf indicated by a plurality of arrows in the figure acts in such a manner that a load point (acting position) changes. Further, as shown in FIG. 5 to FIG. 8D, the load FPr indicated by a plurality of arrows in the drawings is also provided on the outer peripheral side of the pinion shaft rear portion PSr in accordance with the shift speed, the rotational speed, and the input torque. Acts in such a way that the load point (the position where it acts) changes.

  Here, the load FP and its load points will be briefly described with reference to FIGS. 11 and 12.

  As shown in FIG. 12A, a load FP acting on the needle bearings bf and br from the long pinion LP acts on the outer peripheral side of the pinion shaft PS via the needle bearings bf and br. This load FP includes a tangential force F generated based on the input torque, a thrust force T generated based on the helical pinion of the long pinion LP and the gear meshing with the long pinion LP, a separate force S generated based on the transmission path in each gear stage, It is generated by the centrifugal force V ′ of the long pinion LP itself.

That is, as shown in FIG. 12B, the load FPf acting on the outer peripheral side of the pinion shaft front portion PSf is tangential force F ₁ acting on the front portion of the long pinion LP by the sun gear S2, thrust force T ₁ , and The separating force S ₁ and the centrifugal force V ′ of the long pinion LP itself are synthesized and act. The load FPr acting on the outer peripheral side of the pinion shaft rear portion PSr includes the tangential force F ₂ , thrust force T ₂ , and separation force S ₂ acting on the rear portion of the long pinion LP by the ring gear R2, and the long The centrifugal force V ′ of the pinion LP itself is synthesized and acts.

  As shown in FIG. 11, when the engine speed Ne1 at the first forward speed, at the engine speed Ne2, at the engine speed Ne1 at the fifth forward speed, at the engine speed Ne2 (however, Ne1 In each of <Ne2), the load FPf acting on the outer peripheral side of the pinion shaft front portion PSf and the load FPr acting on the outer peripheral side of the pinion shaft rear portion PSr are considered.

  Then, in the state of the first forward speed and the engine speed Ne1, the pinion shaft front portion PSf has a load point slightly on the left side in the figure, for example, a load FPf of X1 [Nm] is acting. The pinion shaft rear portion PSr has a load point slightly below the right side in the figure, for example, a load FPr of X2 [Nm] (where X1 <X2) is acting.

  Further, in the state of the first forward speed and the engine speed Ne2, the pinion shaft front portion PSf has a load point slightly on the left side in the figure, for example, a similar load FPf of X1 [Nm] is provided. In the pinion shaft rear portion PSr, there is a load point slightly below the right side in the figure, for example, a similar load FPr of X2 [Nm] (where X1 <X2) is acting. In the automatic transmission 10 according to the present embodiment, at the first forward speed, the rotation of the carrier CR2 is stopped by the one-way clutch F-1 or the brake B-2.

  On the other hand, in the state of the fifth forward speed and the engine speed Ne1, the pinion shaft front portion PSf has a load point on the lower left side in the drawing, for example, a load FPf of X3 [Nm] is applied, and the pinion The shaft rear side portion PSr has a load point on the lower right side in the figure, and a load FPr of, for example, X4 [Nm] (X3> X4) is acting.

  Then, in the state of the fifth forward speed and the engine speed Ne2, the pinion shaft front portion PSf has a load point on the slightly lower side on the left side in the drawing, for example, a load FPf of X5 [Nm] larger than X3. The pinion shaft rear portion PSr has a load point slightly on the left side in the figure, for example, a load FPr of X6 [Nm] (X5> X6) smaller than X4 is applied. Yes.

  As described above, in the planetary gear unit PU in the automatic transmission 10, the load point changes according to the shift speed and the engine speed, and the higher the high speed speed, that is, the rotation speed of the pinion shaft PS. It can be seen that as the rotation speed increases, the magnitude of the load FPf at the load point of the pinion shaft front portion PSf increases, whereas the magnitude of the load FPr at the load point of the pinion shaft rear portion PSr decreases.

  Subsequently, the difference in the discharge flow rate caused by the difference in the perforating direction of the front side discharge oil passage a7 and the back side discharge oil passage a8 will be described with reference to FIGS.

As shown in FIG. 13, in the automatic transmission lubrication devices 101 ₅ , 10 ₁₆ which are reference examples, as described above, the front side drain oil passages a7 ₅ , a7 ₆ are arranged on the inner periphery of the revolution track Or of the pinion shaft PS. As the pinion shaft rotation speed increases, it is affected by the centrifugal force, and the flow rate of the lubricating oil discharged from the near-side discharge oil passages a7 ₅ and a7 ₆ increases as the rotation speed increases. Will soon decrease significantly. Further, as the flow rate of the lubricating oil discharged from the front side discharged oil passages a7 ₅ and a7 ₆ decreases, the flow rate of the lubricating oil discharged from the back side discharged oil passages a8 ₅ and a8 ₆ As the number rises, it will increase significantly.

However, in the lubricating device _{1 1,} 1 _2, 1 3, _{1 4} of the automatic transmission according to the present invention, the front side discharge oil passage _a7 1 as described _above, a7 _2, a7 3, a7 ₄ pinion shaft PS Since the opening is directed toward the outer peripheral side from the revolution orbit, the centrifugal force is not affected even if the rotation speed of the pinion shaft is increased. Thereby, it is possible to prevent the flow rate of the lubricating oil discharged from the front side discharge oil passages a7 ₁ , a7 ₂ , a7 ₃ , a7 ₄ from being significantly reduced as the rotational speed increases, and after the pinion shaft An appropriate amount of lubricating oil can be secured between the side portion PSr and the long pinion LP (that is, the needle bearing br portion).

Further, since the flow rate of the lubricating oil discharged from the front side discharge oil passages a7 ₁ , a7 ₂ , a7 ₃ , a7 ₄ does not decrease significantly as the pinion shaft speed increases, the back side discharge It is possible to prevent the flow rate of the lubricating oil discharged from the oil passages a8 ₁ , a8 ₂ , a8 ₃ , a8 ₄ from significantly increasing as the pinion shaft speed increases, and the pinion shaft front portion PSf and the long pinion An appropriate amount of lubricating oil can be ensured between LP and the needle bearing bf.

  As described above, in the automatic transmission 10, for example, the rotation of the carrier CR2 is stopped at the first forward speed, and a large load FPr is generated with respect to the pinion shaft rear portion PSr. On the other hand, in the automatic transmission 10, for example, when the rotation of the carrier CR2 increases with the engine speed at the fifth forward speed, the load FPr generated on the pinion shaft rear portion PSr decreases and the pinion The load FPf generated with respect to the shaft front portion PSf increases.

  That is, in this automatic transmission 10, it is sufficient that the flow rate of the lubricating oil slightly decreases between the pinion shaft rear portion PSr and the long pinion LP in a state where the rotation speed of the pinion shaft is increased, and the pinion shaft It is preferable that the flow rate of the lubricating oil slightly increases between the front portion PSf and the long pinion LP.

Therefore, (see FIG. 5) in the lubricating device 1 ₁ of an automatic transmission according to the present invention, the revolution direction of the front side oil discharge passage a7 ₁ and the rear-side oil discharge passage a8 ₁ as described above pinion shafts PS inclined to the front side of the ω is opened, with the increase of the pinion shaft rotational speed, the inertial force of slightly revolution in the lubricating oil of該手front discharge oil passage a7 ₁ and the rear-side oil discharge passage a8 ₁ It is comprised so that it may arise in the reverse direction to the direction discharged | emitted.

Thus, as shown in FIG. 14, slightly decreasing the flow rate of the lubricating oil discharged from the front side oil discharging passage a7 ₁ is with an increase in rotational speed, the discharge along with it from the rear side oil discharging passage a8 ₁ The flow rate of the lubricating oil is slightly increased as the rotational speed is increased. That lubricating device 1 ₁ of the automatic transmission, as in this automatic transmission 10, for example a load FPr of the pinion shaft rear portion PSr as pinion shaft rotational speed is higher is reduced, and the pinion shaft rotational speed is higher Accordingly, it is optimal for use in such a case that the load FPf of the front portion PSf of the pinion shaft increases.

Further, (see FIG. 6) in the lubricating device 1 ₂ of the automatic transmission according to the present invention, the opening front side oil discharge passage a7 ₂ as described above is inclined to the front side of the revolution direction ω of the pinion shaft PS and, and the rear-side oil discharge passage a8 ₂ has opened rearwardly inclined side of the revolution direction ω of the pinion shaft PS, with increasing of the pinion shaft rotational speed, in particular the front side oil discharge passage a7 ₁ The lubricating oil is configured to generate in a direction opposite to the direction in which a slightly rotating inertial force is discharged.

Thus, as shown in FIG. 14, slightly decreasing the flow rate of the lubricating oil discharged from the front side oil discharging passage a7 ₂ is with an increase in rotational speed, the discharge along with it from the rear side oil discharging passage a8 ₂ The flow rate of the lubricating oil is slightly increased as the rotational speed is increased. That even in the lubricating device 1 ₂ of the automatic transmission, as in this automatic transmission 10, for example a load FPr of the pinion shaft rear portion PSr as pinion shaft rotational speed is higher is reduced, and the pinion shaft rotational speed It is suitable for use in such a case that the load FPf of the pinion shaft front side portion PSf increases as the height increases.

On the other hand, (see FIG. 7) in the lubricating device 1 ₃ of the automatic transmission according to the present invention, the revolution direction of the pinion shaft PS Forward side oil discharging passage a7 ₃ and the rear side discharge oil passage a8 ₃ as described above ω the inclined rear side is open and, with the increase of the pinion shaft rotational speed, the inertial force of slightly revolution in the lubricating oil of該手front discharge oil passage a7 ₃ and the rear side discharge oil passage a8 within ₃ It is configured to occur in the discharge direction.

Thus, as shown in FIG. 14, the flow rate of the lubricating oil discharged from the front side oil discharging passage a7 ₃ and the rear side discharge oil passage a8 ₃ is increased or decreased in a trace amount with increasing rotational speed, substantially constant Flow rate. That lubricating device 1 ₃ of the automatic transmission, for example, by the pinion shaft rotational speed, the pinion shaft rear portion load PSr FPR, and with the automatic transmission magnitude of the load FPf of the pinion shaft front portion PSf does not change much Is preferred.

Then, in the lubricating device 1 ₄ of the automatic transmission according to the present invention (see FIG. 8), the front side discharge oil passage a7 ₄ as described above is inclined to the rear side of the revolution direction ω of the pinion shaft PS opening and, and the rear-side oil discharge passage a8 ₄ are opened inclined to the front side of the revolution direction ω of the pinion shaft PS, with increasing of the pinion shaft rotational speed, in particular the front side oil discharge passage a7 ₄ occurs in the direction in which the inertial force of slightly revolution in the lubricating oil is discharged, the inertial force of slightly revolution in the lubricating oil of the rear side oil discharging passage a8 ₄ is configured to generate a direction opposite to the direction to discharge Yes.

Thus, as shown in FIG. 14, the flow rate of the lubricating oil discharged from the front side oil discharging passage a7 ₄ is slightly increased with an increase in rotational speed, the discharge along with it from the rear side oil discharging passage a8 ₄ The flow rate of the lubricating oil is slightly reduced as the rotational speed is increased. That In the lubricating device 1 ₄ of the automatic transmission, for example, pinion shaft load FPr of the pinion shaft rear portion PSr as rotational speed increases increases, and the pinion shaft front portion as pinion shaft rotational speed is higher PSf This is suitable for use in an automatic transmission in which the magnitude of the load FPf is small.

  As described above, according to the lubricating device 1 for an automatic transmission according to the present invention, the front-side drain oil passage a7 and the back-side drain oil passage a8 are drilled from the revolution track OR of the center CT2 of the pinion shaft PS toward the outer peripheral side. Therefore, even if the carrier CR2 having the pinion shaft PS is rotated at a high speed, it is possible to prevent the amount of lubricating oil discharged by the centrifugal force from being reduced, and to always ensure the amount of lubricating oil. As a result, it is possible to prevent wear and seizure between the long pinion LP and the pinion shaft PS, thereby improving durability.

  Further, the front side discharge oil passage a7 and the back side discharge oil passage a8 are in a rotational rotation direction ω of the pinion shaft PS with respect to a radial direction (arrow A direction) from the center CT1 of the revolution orbit Or of the center CT2 of the pinion shaft PS. Therefore, the lubricating oil supplied from the supply oil passage a5 to the axial oil passage a6 can be appropriately distributed.

  In particular, it is composed of a front side discharge oil passage a7 close to the supply oil passage a5 in the axial direction and a back side discharge oil passage a8 farther from the supply oil passage a5 than the front discharge oil passage a7 in the axial direction. The lubricating oil can be appropriately distributed at different positions in the axial direction between the long pinion LP and the pinion shaft PS.

Further, the front side oil discharge passage a7 _1, a7 _2, since it is drilled is inclined to the front side in the revolution direction ω of the pinion shaft PS, the front side oil discharge passage as the carrier CR2 rotating at the high speed a7 _1, a7 appropriately can be reduced by the inertial force of the revolution amount of lubricating oil to be discharged from _2, also to increase the back side oil discharging passage a8 _1, a8 ₂ amount of lubricating oil supplied to the appropriate Can be possible. Especially the far side oil discharging passage a8 _1, since it is drilled is inclined to the front side in the revolution direction ω of the pinion shaft PS, discharged from the rear side oil discharging passage a8 ₁ as the carrier CR2 rotating at the high speed The amount of lubricating oil can be appropriately reduced. In particular, the back side oil discharging passage a8 _2, since the inclined rear side is bored in the revolution direction of the pinion shaft PS, discharged from the rear side oil discharging passage a8 ₂ as carrier CR2 rotating at the high speed The amount of lubricating oil to be increased can be increased appropriately.

As a result, in the automatic transmission 10, as the rotation of the carrier CR2 increases, the load FPr acting on the outer peripheral side of the pinion shaft PS in the vicinity of the front side discharge oil passage a7 decreases, and in the vicinity of the back side discharge oil passage a8. Although the load FPf acting on the outer peripheral side of the pinion shaft PS increases, the amount of lubricating oil discharged from the front-side discharged oil passage a7 can be appropriately reduced as the carrier CR2 becomes higher in rotation, and the back-side discharged oil it is possible to increase the amount of lubricating oil to properly supply the road a8, it is possible to optimize the lubrication with the lubricating device 1 _1, or 1 ₂ of the automatic transmission.

Further, since the front side discharge oil passages a7 ₃ and a7 ₄ are inclined and drilled rearward in the revolution rotation direction ω of the pinion shaft PS, the front side discharge oil passages a7 as the carrier CR2 becomes higher in rotation. ₃ , the amount of lubricating oil discharged from a7 ₄ can be increased appropriately, and the amount of lubricating oil supplied to the back side discharged oil passages a8 ₃ , a8 ₄ can be reduced appropriately. . In particular, the back side oil discharging passage a8 _4, since is drilled is inclined to the front side in the revolution direction of the pinion shaft PS, discharged from the rear side oil discharging passage a8 ₄ as the carrier CR2 rotating at the high speed The amount of lubricating oil can be appropriately reduced. Rear side oil discharging passage a8 ₃ in particular also because is inclined rearward is bored in the revolution direction of the pinion shaft PS, discharged from the rear side oil discharging passage a8 ₃ as the carrier CR2 rotating at the high speed the amount of lubricating oil can also be increased accordingly, it is possible to equalize the amount of lubricating oil to be discharged from a relatively front side discharge oil passage a7 ₃ and the rear side discharge oil passage a8 _3.

  The Ravigneaux-type planetary gear unit PU includes a sun gear S2 meshing with the long pinion LP, a short pinion SP meshing with the sun gear S3 at a position different from the sun gear S2 in the axial direction, and meshing with the long pinion LP, and a sun gear S3. Since the ring gear R2 meshes with the long pinion LP on the outer peripheral side of the gear, the load point and its load FP vary greatly depending on the gear position, the rotational speed of the drive source, and the input torque. By drilling the drain oil path a7 and the back side drain oil path a8 from the revolution orbit of the pinion shaft PS toward the outer peripheral side, the amount of lubricating oil can always be secured, and the long pinion LP and the pinion shaft PS can be secured. It is possible to prevent wear and seizure from occurring, and to improve durability. Then, as described above, the front-side drain oil passage a7 and the back-side drain oil passage a8 are formed by being appropriately inclined forward or rearward in the revolution rotation direction ω of the pinion shaft PS with respect to the radial direction. , Different positions in the axial direction, ie, the pinion shaft front portion PSf and the pinion shaft rear portion PSr and the long pinion LP can be appropriately distributed, and the load points and the significant changes in the loads FPf and FPr It can correspond to.

  In particular, based on the hydraulic pressure generated by the oil pump 15, from the oil pump 15, the oil passage a0 in the partition walls 11c and 11e, the oil passages a1, a2, a3 and a4 in the central shafts 12 and 13 and the supply oil passage a5 are provided. The amount of lubricating oil supplied to the axial oil passage a6 is small, but the amount of lubricating oil discharged by the centrifugal force even when the carrier CR2 is rotated at high speed. Therefore, it is possible to ensure the amount of lubricating oil.

  In the present embodiment described above, the long pinion LP of the Ravigneaux type planetary gear unit PU in the automatic transmission 10 that achieves the sixth forward speed and the first reverse speed optimal for use in, for example, an FR type vehicle, for example. The present invention has been applied to the pinion shaft PS portion, but of course, any automatic transmission can be used as long as the pinion shaft has a plurality of oil discharge passages. The present invention can be applied to any pinion shaft.

  In addition, the exhaust oil passage described in the present embodiment is only the two oil passages of the front side discharge oil passage a7 and the back side discharge oil passage a8, but includes three or more discharge oil passages. It may be. In particular, even those having three or more drain oil passages are discharged from each drain oil passage by appropriately inclining the drain oil passages to the front side or the rear side in the revolution rotation direction of the pinion shaft. Needless to say, the flow rate of the lubricating oil can be adjusted.

  Further, the oil discharge passage described in the present embodiment is simply inclined forward or backward in the revolution rotation direction of the pinion shaft, but is opened toward the outer peripheral side of the revolution track of the pinion shaft. It is needless to say that the flow rate of the lubricating oil discharged from each discharged oil passage can be adjusted by setting the angle freely within the range. In particular, a plurality of discharged oil passages are not inclined to the front side or the rear side in the revolution rotation direction of the pinion shaft, that is, even if the discharge oil passage is opened in a radial direction from the center of the revolution track of the pinion shaft. It is within the scope of the claims of the present invention if the road opens toward the outer peripheral side from the revolution track of the pinion shaft.

The skeleton figure of the automatic transmission which can apply this invention. Automatic transmission engagement table. 1 is a partially omitted cross-sectional view of an automatic transmission to which the present invention can be applied. It is a figure which shows the part of a pinion shaft in detail, (a) is sectional drawing of a carrier, (b) is a figure which shows the relationship between a pinion shaft and a revolution track. In view showing a lubricating device 1 ₁ according to the present invention, (a) shows the sectional view of the carrier, (b) is sectional view of the pinion shaft front portion, (c) is sectional view of the pinion shaft center portion, (d) is Sectional drawing of the pinion shaft rear side part. In view showing a lubricating device 1 ₂ according to the present invention, (a) shows the sectional view of the carrier, (b) is sectional view of the pinion shaft front portion, (c) is sectional view of the pinion shaft center portion, (d) is Sectional drawing of the pinion shaft rear side part. A view showing a lubricating device 1 ₃ according to the present invention, (a) is a cross-sectional view of the carrier, (b) is a sectional view of the pinion shaft front portion, (c) is a sectional view of the pinion shaft center portion, (d) is Sectional drawing of the pinion shaft rear side part. A view showing a lubricating device 1 ₄ according to the present invention, (a) is a cross-sectional view of the carrier, (b) is a sectional view of the pinion shaft front portion, (c) is a sectional view of the pinion shaft center portion, (d) is Sectional drawing of the pinion shaft rear side part. A view showing a lubricating device 101 ₅ is a reference example, (a) shows the cross sectional view of the carrier, (b) is a sectional view of the pinion shaft front portion, (c) is a sectional view of the pinion shaft center portion, (d) is Sectional drawing of the pinion shaft rear side part. A view showing a lubricating device 101 ₆ is a reference example, (a) shows the cross sectional view of the carrier, (b) is a sectional view of the pinion shaft front portion, (c) is a sectional view of the pinion shaft center portion, (d) is Sectional drawing of the pinion shaft rear side part. Explanatory drawing which shows the load point based on the relationship between a gear stage and rotation speed, and its load. Explanatory drawing which shows the force relationship which acts as a load of a load point. The figure which shows the relationship between the rotation speed of a pinion shaft, and the flow volume discharged | emitted from a discharge oil path. The figure which expanded the scale of the flow volume in FIG.

Explanation of symbols

1 Automatic transmission lubrication device 10 Automatic transmission CR2 Carrier LP Long pinion PS Pinion shaft PU Planetary gear (planetary gear unit)
S2 A plurality of different gears, a first sun gear S3, a second sun gear SP, a plurality of different gears, a short pinion R2, a plurality of different gears, a ring gear a6, an axial oil passage a5, a supply oil passage a7, a discharge oil passage, and a front discharge oil passage a8. Road, back side oil discharge path ω Revolution rotation direction

Claims (12)

In a lubricating device for an automatic transmission having a planetary gear having a carrier having a pinion and a pinion shaft that rotatably supports the pinion,
An axial oil passage drilled in the axial direction inside the pinion shaft;
A supply oil passage for supplying lubricating oil from one end of the axial oil passage;
A plurality of discharge oil passages that are opened from the axial oil passage to the outer peripheral side of the pinion shaft, and are drilled at different positions in the axial direction;
Drilling the plurality of drain oil passages toward the outer peripheral side from the revolving track of the center of the pinion shaft,
A lubricating device for an automatic transmission. The plurality of drain oil passages are formed by being inclined to the front side or the rear side in the revolution rotation direction of the pinion shaft with respect to the radial direction from the center of the revolution orbit of the center of the pinion shaft.
The lubricating device for an automatic transmission according to claim 1. The plurality of drain oil passages are a front-side drain oil passage that is close to the supply oil passage in the axial direction, and a back-side drain oil passage that is farther from the supply oil passage than the near-side drain oil passage in the axial direction. And consist of,
The lubricating device for an automatic transmission according to claim 2. The front-side drain oil passage is formed by being inclined to the front side in the revolution rotation direction of the pinion shaft.
The lubricating device for an automatic transmission according to claim 3. The back side drain oil passage is formed by being inclined to the front side in the revolution rotation direction of the pinion shaft,
The lubricating device for an automatic transmission according to claim 4. The back-side drain oil passage is formed by being inclined to the rear side in the revolution rotation direction of the pinion shaft.
The lubricating device for an automatic transmission according to claim 4. In the automatic transmission, as the rotation of the carrier increases, the load acting on the outer peripheral side of the pinion shaft in the vicinity of the front-side discharge oil passage decreases, and the pinion shaft in the vicinity of the back-side discharge oil passage decreases. The load acting on the outer peripheral side increases.
The lubricating device for an automatic transmission according to any one of claims 4 to 6. The front-side drain oil passage is formed by being inclined to the rear side in the revolution rotation direction of the pinion shaft.
The lubricating device for an automatic transmission according to claim 3. The back side drain oil passage is formed by being inclined to the front side in the revolution rotation direction of the pinion shaft,
The lubricating device for an automatic transmission according to claim 8. The back-side drain oil passage is formed by being inclined to the rear side in the revolution rotation direction of the pinion shaft.
The lubricating device for an automatic transmission according to claim 8. The planetary gear is a Ravigneaux type planetary gear,
The plurality of different gears include a first sun gear that meshes with the long pinion, a short pinion that meshes with the second sun gear and meshes with the long pinion at positions different from the first sun gear in the axial direction, A ring gear meshing with the long pinion on the outer peripheral side of the two sun gears;
The pinion shaft is configured to rotatably support the long pinion.
The lubricating device for an automatic transmission according to any one of claims 1 to 10, wherein: The automatic transmission includes a central shaft disposed from the front to the rear, a case having a partition member that rotatably supports a front portion of the central shaft, and an oil pump disposed in the partition member. With
The partition member has an oil passage in the partition wall that communicates with a discharge portion of the oil pump and opens to an outer peripheral portion of the central shaft,
The central shaft communicates with the oil passage in the partition wall, and has a central shaft oil passage communicated axially rearward in the central shaft,
The planetary gear is disposed on the outer peripheral side of the rear portion of the central shaft,
The supply oil passage is provided in a side plate on the rear side of the carrier and communicates with the oil passage in the central shaft.
Based on the hydraulic pressure generated by the oil pump, lubricating oil is supplied from the oil pump to the axial oil passage through the oil passage in the partition wall, the oil passage in the central shaft, and the supply oil passage.
12. The lubricating device for an automatic transmission according to claim 1, wherein the lubricating device is an automatic transmission.

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