JP4908445B2 - Oil passage structure of automatic transmission - Google Patents

Description

  The present invention relates to an oil passage structure in which an oil hole is provided in a cylindrical shaft that surrounds a rotating shaft in an automatic transmission, and oil is supplied to a predetermined portion through the oil hole.

The automatic transmission is configured by combining a planetary gear set and a frictional engagement element, and realizes a plurality of shift stages by a combination of engagement and release of a frictional engagement element that is operated by hydraulic pressure. Accordingly, oil is supplied and discharged in order to fasten and release the frictional engagement element.
For this reason, conventionally, an oil pump is disposed around the input shaft of the automatic transmission, and a clutch oil passage for supplying oil from the oil pump as an adjacent friction engagement element to, for example, a piston chamber of the clutch is provided.
As an example, in Japanese Patent Application Laid-Open No. 11-82644, an oil hole is provided in the stator shaft extending from the torque converter side and surrounding the outer periphery of the input shaft, and an oil hole provided in the stator shaft from the oil pump cover and provided in the input shaft. A configuration is shown in which a clutch oil passage is formed through the oil holes to reach the piston chamber.
JP-A-11-82644

Incidentally, the oil pump cover and the stator shaft are provided with a release hole for forming a release pressure oil passage communicating with the torque converter, in addition to an oil hole of the clutch oil passage communicating with the piston chamber of the clutch.
The release hole is arranged as close to the torque converter as possible so that the axial thickness of the oil pump cover does not increase in the oil pump cover, but the torque converter side thickness of the stator shaft does not decrease in the stator shaft. Therefore, the release hole cannot be inclined so much toward the torque converter.

The opening of the oil hole on the outer peripheral surface of the input shaft of the clutch oil passage is arranged avoiding the opening of the release hole of the stator shaft in the axial direction, but the inclination of the release hole cannot be greatly inclined as described above. The axial position is far from the torque converter side.
Therefore, one end is connected to the oil hole of the oil pump cover to form the clutch oil passage, and the oil hole of the stator shaft whose other end opens to the input shaft side is close to the torque converter side. Since the seal ring is disposed at a position far from the torque converter side, the seal ring is largely inclined from the radial direction perpendicular to the axis of the stator shaft.

As a result, in the conventional oil passage structure in which the input shaft at the connection portion of the oil hole has a constant diameter, the opening of the oil hole forming the clutch oil passage on the inner peripheral surface of the stator shaft is very long in the axial direction of the stator shaft. As a result, the dimension of the stator shaft between the oil pump and the clutch is extended, and the entire automatic transmission is eventually enlarged in the axial direction.
Further, in order to block oil leakage between the input shaft and the stator shaft, when two seal rings are provided across the opening of the oil hole, each seal ring has a predetermined distance from the edge of the opening of the oil hole. Therefore, the increase in the dimension of the stator shaft becomes more remarkable, and the influence of the oil hole opening being elongated in the axial direction of the stator shaft is remarkable.

  Accordingly, in view of the above-described conventional problems, the present invention provides an oil passage structure in which the length of the opening of the oil hole forming the clutch oil passage is suppressed and the entire automatic transmission can be downsized in the axial direction. For the purpose.

  For the above purpose, the present invention provides an oil passage that sequentially communicates from a fixed member of a transmission case to a cylindrical shaft and a rotating shaft, and forms an oil passage that supplies oil to a predetermined portion along the rotating shaft, In an oil passage structure of an automatic transmission in which an oil hole provided in a cylindrical shaft is inclined with respect to an axis, the cylindrical shaft has a large-diameter portion and a small-diameter portion on an inner peripheral surface thereof. The inner peripheral surface side of the provided oil hole opens at a connection portion connecting the large diameter portion and the small diameter portion.

  According to the present invention, the opening in the inner peripheral surface of the cylindrical shaft of the oil hole provided in the cylindrical shaft does not become extremely long in the axial direction of the cylindrical shaft even if the oil hole is inclined, and the stator shaft A simple configuration that suppresses the extension of the dimensions and thus provides only a large diameter portion and a small diameter portion on the inner peripheral surface of the cylindrical shaft, and prevents an increase in the size of the entire automatic transmission in the axial direction while suppressing an increase in cost. The

Hereinafter, embodiments of the present invention will be described in detail.
FIG. 1 is a skeleton diagram showing a gear train of an automatic transmission to which the embodiment is applied.
This automatic transmission includes simple planetary gear sets G1 and G2. The planetary gear set G1 includes a first sun gear S1, a first carrier C1, and a first ring gear R1. The planetary gear set G2 has a second sun gear S2, a second carrier C2, and a second ring gear R2.

An input shaft IN to which driving force from an engine (not shown) is input via the torque converter 5 is connected to the first sun gear S1 of the planetary gear set G1 via the low clutch L / C and the first member M1. . The input shaft IN is also connected to the second sun gear S2 of the planetary gear set G2 via the reverse clutch REV / C and the second member M2, and to the second carrier via the high clutch H / C and the third member M3. Connected to C2.
The second member M2 can be fixed to and released from the transmission case TC via the band brake B / B.

The second carrier C2 of the planetary gear set G2 is connected to the first ring gear R1 of the planetary gear set G1 via the fourth member M4, and the second ring gear R2 is connected to the first carrier of the planetary gear set G1 via the fifth member M5. It is connected to C1.
The fourth member M4 is supported so as to be capable of rotating in one direction with respect to the transmission case TC via a parallelly arranged low and reverse brake L & R / B and a low one-way clutch L / OWC. The regulation (fixed) and the regulation can be released.
The first carrier C1 is connected to the output gear OUT.

The automatic transmission configured as described above realizes the forward fourth speed (1st to 4th) and the first reverse speed (Rev) by combining the engagement and release of the friction elements shown in FIG. In FIG. 2, a solid line ○ mark indicates fastening, no mark indicates release, and a broken line ○ indicates fastening, but it operates when the engine is braked, and a solid circle indicates that the fastening operation is mechanically (rotation restricted) only when the engine is driven. .
Then, in the D range position, the automatic transmission control for the fourth forward speed is performed according to the shift schedule set based on the vehicle speed and the throttle opening. In addition, the shift control of the first reverse speed is performed by a selection operation from the D range position to the R range position.

Next, with reference to FIGS. 1 and 2, the rotation transmission path of each gear stage will be described.
The first speed (1st) is achieved by engaging the low clutch L / C and engaging the low and reverse brake L & R / B or the low one-way clutch L / OWC.
Engine rotation via the torque converter 5 is decelerated from the input shaft IN via the low clutch L / C, the first member M1, and the planetary gear set G1, and is decelerated by the maximum reduction ratio from the output gear OUT connected to the first carrier C1. Rotation is output. During engine braking, the low and reverse brake L & R / B receives a reaction force in place of the idling low one-way clutch L / OWC.

The second speed (2nd) is achieved by engaging the low clutch L / C and the band brake B / B.
The rotation reduced from the input shaft IN through the first member M1 and the planetary gear set G1 is input from the fifth member M5 to the second ring gear R2. In the planetary gear set G2, the second carrier C2 rotates at a reduced speed while receiving a reaction force from the second sun gear S2 fixed to the transmission case TC by the engagement of the band brake B / B, and the second carrier C2 rotates through the fourth member M4. Since the 1-ring gear R1 is rotated in the same direction as the first sun gear S1, a reduction rotation with a reduction ratio smaller than the first speed is output from the output gear OUT connected to the first carrier C1.

The third speed (3rd) is achieved by engaging the low clutch L / C and the high clutch H / C.
The rotation of the input shaft IN is input to the first sun gear S1 of the planetary gear set G1 via the low clutch L / C and the first member M1. On the other hand, the rotation of the input shaft IN is also input from the high clutch H / C to the first ring gear R1 of the planetary gear set G1 through the third member M3, the second carrier C2 of the planetary gear set G2, and the fourth member M4 in order. The
As a result, the planetary gear set G1 is in a directly connected state, the first carrier C1 rotates with the same rotation as the first sun gear S1, and rotation with a reduction ratio 1 smaller than the second speed is output from the output gear OUT. .

The fourth speed (4th) is achieved by engaging the high clutch H / C and the band brake B / B.
When the band brake B / B is engaged, the second sun gear S2 of the planetary gear set G2 is fixed, while the rotation of the input shaft IN is input to the second carrier C2 via the high clutch H / C and the third member M3. . Therefore, in the planetary gear set G2, the second ring gear R2 rotates higher than the second carrier C2, that is, higher than the rotation of the input shaft IN. As a result, the rotation increased from the input rotation is output from the output gear OUT via the fifth member M5 and the first carrier C1 from the second ring gear R2.

Reverse (Rev) is achieved by engaging the reverse clutch REV / C and the low and reverse brake L & R / B.
The rotation of the input shaft IN is input to the second sun gear S2 of the planetary gear set G2 via the reverse clutch REV / C and the second member M2.
The second ring gear R2 reversely receives the reaction force by the second carrier C2 fixed to the transmission case TC via the fourth member M4 by engaging the low and reverse brake L & R / B, and the fifth member M5, the planetary gear Reduced reverse rotation is output from the output gear OUT via the first carrier C1 of the set G1.

FIG. 3 is a longitudinal sectional view showing a specific structure from the torque converter to the oil pump and the low clutch part.
An oil pump 10 is attached to the transmission case, and a sleeve 8 extending from the converter case 6 of the torque converter 5 is connected to an inner race 13 a of the oil pump 10. The converter case 6 supports the impeller 5a of the torque converter.
A cylindrical stator shaft 15 is press-fitted into an oil pump cover 12 of the oil pump 10 in a central hole 14 having the same diameter as the outer diameter of the sleeve 8, and the stator shaft 15 extends into the torque converter 5 from the inside of the sleeve 8. 5c is supported. The portion of the stator shaft 15 located in the sleeve 8 has a smaller diameter than the central hole 14 press-fitted portion of the oil pump cover 12.

A main shaft 30 (input shaft IN in FIG. 1) is rotatably supported in the stator shaft 15. The main shaft 30 is connected to the turbine 5b of the torque converter at the tip.
The low clutch L / C, the first output gear OUT, the planetary gear set G1, and the planetary gear set G2 are sequentially arranged along the main shaft 30 on the opposite side of the oil pump 10 from the torque converter 5, and surround the planetary gear set G1. A low and reverse brake L & R / B and a low one-way clutch L / OWC are provided on the outer peripheral side.

  The low clutch L / C includes a clutch drum 40 having a spline in the outer peripheral cylindrical portion and coupled to the main shaft 30 by a disk portion 42, a clutch hub 44 having a spline disposed inside the clutch drum 40, and the clutch drum 40 and the clutch hub. 44 is accommodated in a clutch plate 46 which is alternately overlapped in the axial direction with a friction plate which is provided between 44 and meshes with one of the respective splines, and is slidable in the axial direction in a piston chamber 60 formed in the clutch drum 40. And a piston 47. When oil is supplied to the piston chamber 60, the piston 47 presses the clutch plate 46, and the low clutch L / C is engaged.

The clutch hub 44 is connected to the sun gear S1 of the planetary gear set G1 via a first member M1 having a cylindrical portion coaxial with the main shaft 30.
The first carrier C1 of the planetary gear set G1 is connected to the output gear OUT on the outer periphery of the first member M1. The output gear OUT meshes with the counter gear 49 of the intermediate shaft and outputs rotation to a final reduction gear (not shown).
The first ring gear R1 of the planetary gear set G1 is coupled with a clutch hub 49 having a spline at the outer peripheral cylinder portion, and the outer peripheral cylinder portion constitutes a part of the low and reverse brake L & R / B and the tip of the outer peripheral cylinder portion. Is connected to the low one-way clutch L / OWC. The clutch hub 49 also serves as the fourth member M4.

Hereinafter, the details around the oil passage will be described with reference to the enlarged view of FIG.
The oil pump includes a main body portion 11 that houses the inner race 13a and the outer race 13b and is attached to an end face of the transmission case, and an oil pump cover 12 that is attached to the main body portion 11 inside the transmission case.
The stator shaft 15 has a thick part 16 having a large outer diameter and press-fitted into the central hole 14 of the oil pump cover 12, and an extension part 17 having an outer diameter smaller than that of the thick part and extending inside the main body 11 and the sleeve 8 part. The tip of the thick wall portion 16 is connected to the oil pump cover 12 and the serration 19. A stepped portion 18 having an end surface perpendicular to the axial direction is formed between the thick portion 16 and the elongated portion 17.

The inner diameter of the elongated portion 17 of the stator shaft 15 is slightly larger than the inner peripheral surface of the thick portion 16. The inner peripheral surface of the thick portion 16 has a relatively small diameter portion 20, but the inner peripheral surface of the tip portion corresponding to the serration coupling portion is widened to the extent corresponding to the outer peripheral diameter of the elongated portion 17. It is a diameter portion 21.
In other words, the inner peripheral surface of the thick portion 16 is divided into a large diameter portion 21 corresponding to the serration coupling portion and a small diameter portion 20 corresponding to the actual press-fitting section excluding the serration coupling portion.
A connecting portion between the small diameter portion 20 and the large diameter portion 21 is an inclined surface 22 that is inclined with respect to a surface perpendicular to the axial direction of the stator shaft 15.

In the oil pump cover 12, a first release hole 23 is provided along the vicinity of the end surface facing the main body 11, and opens to the stator shaft press-fitting surface of the central hole 14.
The stator shaft 15 is provided with a second release hole 24 penetrating in the radial direction in the thick portion 16. The outer opening of the second release hole 24 is aligned with the first release hole 23. The second release hole 24 is inclined in a direction in which the inner opening approaches the torque converter side, leaving a predetermined minimum thickness on the stepped portion 18 side.

A portion of the main shaft 30 inserted into the elongated portion 17 of the stator shaft 15 is a small-diameter portion, and a gap 25 is formed between the outer peripheral surface of the main shaft 30 and the inner peripheral surface of the stator shaft 15. Yes. The main shaft 30 is provided with a third release hole 26 in the radial direction that opens into the air gap 25 in the vicinity of the axial torque converter, and a fourth release hole 27 that communicates with the third release hole 26 and extends in the distal direction. Although not particularly illustrated, the fourth release hole 27 opens at the tip of the main shaft 30 and communicates with the torque converter 5.
Of the gap 25 portion, a predetermined area including a portion facing the inner opening of the second release hole 24 is further narrowed, and the radial direction size of the gap 25 is made larger than the other areas.
A release pressure oil passage from the first release hole 23 to the torque converter 5 is formed by the second release hole 24, the gap 25, the third release hole 26, and the fourth release hole 27.

The main shaft 30 includes a small-diameter portion 31 and a large-diameter portion 32 that respectively match the small-diameter portion 20 and the large-diameter portion 21 on the inner peripheral surface of the stator shaft 15, and an inclined surface 33 is formed between the small-diameter portion 31 and the large-diameter portion 32. ing.
In addition, the main shaft 30 has a maximum diameter portion 34 having a larger outer diameter than the large diameter portion 32 on the side opposite to the small diameter portion 31 of the large diameter portion 32, and further a narrow diameter portion 35.
The clutch drum 40 has its disk portion 42 coupled to the corner of the maximum diameter portion 34. The outer peripheral surface of the maximum diameter portion 34 forms a part of the sliding surface of the piston 47 in the clutch drum 40.
A gap 29 is formed between the inclined surface 33 of the main shaft 30 and the inclined surface 22 of the stator shaft 15.

A lubricating oil hole 36 is provided in the center of the shaft from the small diameter portion 35 to the maximum diameter portion 34 of the main shaft 30. For example, to the thrust bearing 60 provided between the oil pump cover 12 and the disk portion 42 of the clutch drum 40, etc. Oil is ejected through a radial hole 37 communicating with the lubricating oil hole 36.
The small-diameter portion 31 of the main shaft 30 is located on the side away from the torque converter adjacent to the edge of the inner opening of the second release hole 24 in the stator shaft 15, and has a seal holding groove at the substantially axial center. The ring 63 is held.
The large-diameter portion 32 of the main shaft 30 also has a seal holding groove at substantially the center in the axial direction, and holds the seal ring 65.

In the oil pump cover 12, the first oil hole 50 is provided at a position avoiding interference with the first release hole 23 along the vicinity of the end surface facing the main body portion 11 in the same manner as the first release hole. The 14 stator shafts 15 open to the press-fitting surface.
The stator shaft 15 is provided with second oil holes 51 in the thick portion 16 in the radial direction. The second oil hole 51 has an outer opening that communicates with the first oil hole 50, and the inner opening is inclined so as to move away from the torque converter, and is opened on the inclined surface 22 from the small diameter portion 20 to the large diameter portion 21.
That is, when the inner opening of the second oil hole 51 is taken as a reference, the inner peripheral surface of the stator shaft 15 has a small diameter portion 20 on the side where the second oil hole 51 extends and a large diameter portion 21 on the opposite side.

The main shaft 30 is provided with a third oil hole 52 penetrating on the diameter line of the main shaft so as to open to a portion adjacent to the inclined surface 33 of the small diameter portion 31.
Further, the main shaft 30 further avoids the lubricating oil hole 36 and is connected to the third oil hole 52 in the axial direction. The fourth oil hole 53 is connected to the fourth oil hole 53 and opened on the outer peripheral surface of the maximum diameter portion 34. And a fifth oil hole 54 is provided. The opening of the fifth oil hole 54 faces the piston chamber 60 of the low clutch.
The fourth oil hole 53 is formed by piercing from the end surface of the maximum diameter portion 34 on the side far from the torque converter, and 55 is a sealing ball.
From the first oil hole 50 to the second oil hole 51, and through the gap 29 between the inclined surfaces 22 and 33 of the stator shaft 15 and the main shaft 30, the third oil hole 52 to the fifth oil hole 54 leads to the low clutch. A clutch oil passage is formed.

In the present embodiment, the oil pump cover 12 corresponds to a fixing member in the invention, the stator shaft 15 corresponds to a cylindrical shaft, and the main shaft 30 corresponds to a rotating shaft. The low clutch L / C corresponds to a predetermined portion along the rotation axis, and is formed by the first oil hole 50, the second oil hole 51, the gap 29 between the inclined surfaces, and the third oil hole 52 to the fifth oil hole 54. The clutch oil passage corresponds to an oil passage for supplying oil to a predetermined portion, and in particular, the second oil hole 51 corresponds to an oil hole provided in the cylindrical shaft.
The inclined surface 22 connecting the small diameter portion 20 and the large diameter portion 21 of the stator shaft 15 corresponds to a connecting portion in the cylindrical shaft, and the inclined surface 33 connecting the small diameter portion 31 and the large diameter portion 32 of the main shaft 30 is connected in the rotating shaft. Corresponds to the part.

  The present embodiment is configured as described above, and the main shaft 30 is provided with oil holes (50 to 54) sequentially communicating from the oil pump cover 12 fixed to the transmission case side to the stator shaft 15 and the main shaft 30. In the oil passage structure of the automatic transmission, a clutch oil passage for supplying oil to the low clutch L / C is formed, and the second oil hole 51 provided in the stator shaft 15 is inclined with respect to the axis. The stator shaft 15 has a small-diameter portion 20 and a large-diameter portion 21 on its inner peripheral surface, and the inner peripheral surface side of the second oil hole 51 opens to a connection portion connecting the small-diameter portion 20 and the large-diameter portion 21. Therefore, the opening in the inner peripheral surface of the stator shaft of the second oil hole 51 provided in the stator shaft 15 does not become extremely long in the axial direction of the stator shaft even if the oil hole is inclined.

In the comparative diagram of FIG. 5, in the comparative example (indicated by phantom lines) that does not have the large diameter portion 21 on the inner peripheral surface of the stator shaft 15, the oil hole is removed from the reference surface S of the oil pump cover 12. Whereas the distance Lz is required from the torque converter side to the far edge Ez of the opening, in the embodiment, the second oil hole 51 opens on the inclined surface 22 from the small diameter portion 20 to the large diameter portion 21 even at the same inclination angle. This is because the edge Eo is positioned at a distance Lo in front of the reference plane S with respect to Ez.
As a result, the extension of the axial dimension of the stator shaft 15 is suppressed, and accordingly, the axial dimension of the oil pump cover 12 is also shortened. That is, since only the large diameter portion 21 and the small diameter portion 20 are provided on the inner peripheral surface of the stator shaft 15, the entire automatic transmission can be enlarged in the axial direction with a simple configuration while suppressing an increase in cost. The effect that can be prevented.

The main shaft 30 has, on its outer peripheral surface, a small diameter portion 31 and a large diameter portion 32 that match the small diameter portion 20 and the large diameter portion 21 of the inner peripheral surface of the stator shaft 15, respectively. Between the large diameter portion 21 of the stator shaft 15 and the large diameter portion 32 of the main shaft 30, with the communication portion of the second oil hole 51 and the third oil hole 52 interposed therebetween. , 65 can be arranged.
Since the length of the opening of the first oil hole 51 in the stator shaft 15 is suppressed, the distance between the two seal rings 63 and 65 is also small.

A gap 29 is provided between the connecting portion connecting the small diameter portion 20 and the large diameter portion 21 on the inner peripheral surface of the stator shaft 15 and the connecting portion connecting the small diameter portion 31 and the large diameter portion 32 on the outer peripheral surface of the main shaft 30, and Oil communication is ensured between the second oil hole 51 of the rotating stator shaft 15 and the third oil hole 52 of the main shaft 30.
Since the connecting portion of the stator shaft 15 and the connecting portion of the main shaft 30 are inclined surfaces 22 and 33, the cross-sectional change is gentle and stress concentration does not occur, and a flow path (gap 29) formed between the inclined surfaces 22 and 33. ) There is no extreme change in cross-sectional area, so the oil flow is smooth.

  In addition, although embodiment described the example which applied this invention to the clutch oil path from the oil pump cover 12 to the adjacent low clutch L / C, this invention is not limited to this, A fixed member to a cylindrical shaft, The oil is supplied to a predetermined portion along the rotation shaft by the oil holes sequentially provided in the rotation shaft, and can be similarly applied to an oil passage in which the oil hole of the cylindrical shaft is inclined.

It is a skeleton figure which shows the gear train of the automatic transmission with which embodiment is applied. It is a figure which shows the combination of the fastening of the friction element for implement | achieving a gear stage, and releasing | release. It is a longitudinal cross-sectional view which shows the specific structure of embodiment. It is an enlarged view which shows the detail around an oil path. It is a comparison figure which shows the comparison with a prior art example.

Explanation of symbols

5 Torque converter 6 Converter case 8 Sleeve 10 Oil pump 11 Body 12 Oil pump cover (fixing member)
14 Center hole 15 Stator shaft (cylindrical shaft)
16 Thick part 17 Elongation part 18 Step part 19 Serration 20 Small diameter part 21 Large diameter part 22 and 33 Inclined surface 23 First release hole 24 Second release hole 25 Gap 26 Third release hole 27 Fourth release hole 29 Gap 30 Spindle (Axis of rotation)
31 Small diameter portion 32 Large diameter portion 34 Maximum diameter portion 35 Small diameter portion 36 Lubricating oil hole 37 Radial hole 40 Clutch drum 42 Disk portion 44, 49 Clutch hub 46 Clutch plate 47 Piston 50 First oil hole 51 Second oil hole 52 Third oil hole 53 Fourth oil hole 54 Fifth oil hole 60 Piston chamber 63, 65 Seal ring B / B Band brake C1 First carrier C2 Second carrier G1, G2 Planetary gear set H / C High clutch IN Input shaft L / C Low clutch L / OWC Low one-way clutch L & R / B Low and reverse brake OUT Output gear R1 First ring gear R2 Second ring gear REV / C Reverse clutch S1 First sun gear S2 Second sun gear TC Transmission case

Claims (7)

An oil hole that sequentially communicates with a fixed member fixed to the transmission case, a cylindrical shaft coupled to the fixed member, and a rotating shaft disposed in the cylindrical shaft is provided, and a predetermined portion along the rotating shaft is provided. In an oil passage structure of an automatic transmission that forms an oil passage for supplying oil and is arranged so that an oil hole provided in a cylindrical shaft is inclined with respect to the axis,
The cylindrical shaft has a large-diameter portion and a small-diameter portion on an inner peripheral surface, and an inner peripheral surface side of an oil hole provided in the cylindrical shaft opens to a connection portion connecting the large-diameter portion and the small-diameter portion. The oil passage structure of the automatic transmission. 2. The automatic transmission according to claim 1, wherein the rotating shaft has, on an outer peripheral surface thereof, a large diameter portion corresponding to the large diameter portion of the cylindrical shaft and a small diameter portion corresponding to the small diameter portion of the cylindrical shaft. Oil passage structure. The oil passage structure for an automatic transmission according to claim 2, wherein a gap is provided between the connecting portion of the cylindrical shaft and the connecting portion of the large-diameter portion and the small-diameter portion of the rotating shaft. 4. The oil passage structure for an automatic transmission according to claim 3, wherein the connecting portion of the cylindrical shaft is inclined with respect to a plane perpendicular to the axial direction of the cylindrical shaft. The oil passage structure for an automatic transmission according to claim 4, wherein the connecting portion of the rotating shaft is inclined with respect to a surface perpendicular to the axial direction of the cylindrical shaft. Between the oil hole provided in the cylindrical shaft and the communicating portion of the oil hole provided in the rotary shaft, between the large diameter portion of the cylindrical shaft and the large diameter portion of the rotary shaft, and the small diameter of the cylindrical shaft The oil passage structure for an automatic transmission according to any one of claims 2 to 5, wherein a seal ring is provided between each portion and the small diameter portion of the rotary shaft. The fixing member is an oil pump cover, the cylindrical shaft is a stator shaft that supports a stator of a torque converter, the rotating shaft is a main shaft, and the predetermined portion along the rotating shaft is a friction fastening element. An oil passage structure for an automatic transmission according to any one of claims 1 to 6.

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