JP2003028271A - Oil passage structure for clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a simple oil passage structure, to improve assembling workability, and to secure axial strength in a clutch device communicated with a multi-systematization oil passage. SOLUTION: This oil passage structure for the clutch device is provided with an input shaft 1 having a hollow hole in the end, a pipe member 30 arranged concentrically in the hollow hole 1a of the input shaft 1 and provided with a hollow part extending in the axial direction of the input shaft 1, and the clutch device 20 arranged in the end of the input shaft 1 and communicated with first, second and third oil passages. The first oil passage includes the hollow part (passage a) in the pipe member 30. The second oil passage includes a clearance (passage b) formed between the outer circumference of the pipe member 30 and the inner circumference part of the input shaft. The third oil passage includes a clearance (passage c) formed between the outer circumference part of the input shaft 1 and the inner circumference part of a stator shaft 27 facing the outer circumference of the input shaft 1.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil passage structure of a clutch device.

[0002]

2. Description of the Related Art Japanese Unexamined Patent Publication No. 7-239026 discloses 2
An oil passage structure of a torque converter with a lockup clutch (clutch device) communicating with an oil passage (for lockup release / for lockup apply) of the system is disclosed (see FIG. 3 of the publication). In this structure, the oil passage for lock-up release includes a hollow hole in the input shaft of the transmission and communicates with the pressure chamber on the front side (facing surface side) of the lock-up clutch. The oil passage for lock-up application includes a gap existing between the outer circumference of the stator shaft of the torque converter and the inner wall of the case of the torque converter, and communicates with the pressure chamber on the back side of the lock-up clutch.

Japanese Patent Laid-Open No. 7-180763 discloses a lubricating structure for an automatic transmission in which a cylindrical oil guide member is inserted into a hollow hole of an output shaft of the transmission. In this transmission, the input shaft, the output shaft, and the drive shaft are coaxially arranged, and the output shaft is located between the input shaft and the drive shaft. The hollow hole of the output shaft is formed to have a large diameter, and an oil guide member having a small diameter is mounted inside the hollow hole. When the shaft rotates, the lubricating oil that has flowed into the hollow hole of the output shaft also flows into the cylindrical oil guide member and flows toward the hollow hole of the front input shaft and the hollow hole of the rear drive shaft. . Since the centrifugal oil pressure is reduced by the diameter of the oil guide member, the lubricating oil can be smoothly supplied to the input shaft side and the drive shaft side even at high speed.

[0004]

By the way, some clutch devices for transmitting power between the engine side and the transmission side require three oil passages. For example, the torque converter with a lock-up clutch disclosed in the above-mentioned Japanese Patent Laid-Open No. 7-230926, to which a hydraulic clutch is added, may be mentioned. For such a clutch device, in addition to the two oil passages for lock-up apply and lock-up release, another oil passage for the hydraulic clutch is required. Further, even in the clutch device in which the pressure chamber for operating the lockup clutch is independent of the torque converter, three systems of oil passages (for lockup apply, lockup release, and lockup clutch operation) are required. If the number of oil passages for the clutch device is increased, the structure of the oil passage becomes complicated, and the workability of assembling and the shaft strength for supporting the clutch device may be insufficient.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a novel oil passage structure for a clutch device, which can simplify the oil passage structure even for a clutch device which needs to communicate with multi-system oil passages. .

Another object of the present invention is to improve the assembling workability of such a clutch device and to secure the shaft strength for supporting the clutch device.

[0007]

In order to solve the above problems, the present invention provides an input shaft having a hollow hole at its end, and concentrically arranged in the hollow hole of the input shaft. And a pipe member having a hollow portion extending in the axial direction of the input shaft, and a pipe member provided at an end of the input shaft, and
There is provided an oil passage structure of a clutch device having a clutch device communicating with the oil passage and the second oil passage. Here, the first oil passage includes the hollow portion of the pipe member. The second oil passage is formed between the outer peripheral portion of the pipe member and the inner peripheral portion of the input shaft, and includes a concentric gap separated from the first oil passage.

In the above structure, the clutch device is the third
It may be connected to the oil passage. In this case, the third oil passage is formed between the outer peripheral portion of the input shaft and the inner peripheral portion of the member facing the outer peripheral portion, and the first oil passage and the second oil passage are separated from each other. It is preferable to include a concentric circular gap.

Further, the clutch device may include a torque converter with a lockup clutch, and a hydraulic clutch having a pressure chamber independent of the torque converter. It is preferable that the clutch device communicates with at least three oil passages including an oil passage for lock-up release, an oil passage for lock-up apply, and an oil passage for operating the hydraulic clutch.

The clutch device may include a torque converter and a lockup clutch having a pressure chamber independent of the torque converter. The clutch device preferably communicates with at least three oil passages including a lockup release oil passage, a lockup apply oil passage, and a lockup clutch operating oil passage.

On the other hand, the concentric gaps formed between the outer peripheral portion of the pipe member and the inner peripheral portion of the input shaft are preferably sealed by seal members at both ends of the pipe member. As a result, the first oil passage and the second oil passage can be separated. The pipe member may have a tubular core made of metal and a seal member provided on the outer peripheral portion of the tubular core. It is preferable that both ends of the pipe member are provided with enlarged diameter portions by forming a thick sealing member. Further, it is desirable that a step or a groove is provided in a portion of the inner peripheral portion of the input shaft that abuts the enlarged diameter portion on the pipe member side.

Further, the pipe member may be fixed by being press-fitted into the hollow hole through an opening provided at the end of the input shaft.

[0013]

1 is a sectional view of an automatic transmission for a four-wheel drive vehicle to which a clutch device according to this embodiment is applied. This automatic transmission (AMT) has five forward gears and shift gears are switched by automatic operation of a synchro mechanism. The input shaft 1 (main shaft) and the output shaft 2 (drive pinion shaft) are arranged in parallel with each other. The power of the crankshaft 16 on the engine side is transmitted to the input shaft 1 on the transmission side via a torque converter type clutch device 20 with a lockup clutch. This clutch device 20 is used for the crankshaft 1 of the engine.
Although the power of 6 is transmitted to the input shaft 1 of the transmission, the clutch torque is released (that is, the power transmission is cut off) at the time of gear shifting in order to suppress the shift shock. Although a specific structure will be described later, the clutch device 20 according to the present embodiment is provided with a torque release hydraulic clutch in addition to the torque converter with the lockup clutch.

A power transmission mechanism including a speed change gear and a switching mechanism for defining each speed ratio from the first speed to the fifth speed is arranged between the two rotary shafts 1 and 2 which are parallel to each other. These speed change gears are arranged from the front side (clutch device 20 side) to the rear side (sub clutch 14 side) from the first speed gears 3 and 2.
High speed gear 4, third speed gear 5, fourth speed gear 6, and fifth speed gear 7 are arranged in this order. During forward movement except during gear shifting, the power of the input shaft 1 is transmitted to the output shaft 2 after being gear-shifted by one gear shift gear selected by operating the three synchronizing mechanisms 8-10. The synchronizing mechanisms 8 to 10 are well-known ones including a synchronizing hub, a synchronizing sleeve, a synchronizing ring, etc., but are automatically controlled by hydraulic pressure. The power of the output shaft 2 is transmitted to the front drive wheels via the differential device 11 and to the rear drive wheels via the gear train 12 and the transfer clutch 13.

The synchro mechanisms 8-10 are controlled in cooperation with the transmission torque control of the sub-clutch 14, but the synchro mechanisms 8-10 themselves generally operate as follows. For example, when the shift speed is set to the 1st speed, the synchronizing mechanisms 9 and 10 are set to the neutral state, and the synchronizing mechanism 8 is hydraulically operated to the 1st speed gear 3 side. As the operation amount of the synchro mechanism 8 (shift amount of the synchro sleeve) increases, the rotation of this synchro sleeve and the driven gear constituting the first speed gear 3 are synchronized. When both members are synchronized, the outer spline integrally formed with the driven gear spline-fits with the inner spline of the synchronizing sleeve at that timing. Since the synchro sleeve is constantly spline-fitted with the synchro hub that rotates integrally with the output shaft 2, the power of the input shaft 1 is transmitted to the output shaft 2 via the first speed gear 3 and the synchro mechanism 8. It On the other hand, when setting the shift speed to the second speed, the synchro mechanisms 9 and 10 are set to the neutral state, and the synchro sleeve of the synchro mechanism 8 is hydraulically operated to the second gear 4 side. Further, when the speed is set to the third speed or the fourth speed, the synchro mechanism 9 is operated, and when the fifth speed is set, the synchro mechanism 10 is operated (the synchro mechanisms other than the operation target are in the neutral state). Set).

The rear end of the input shaft 1 (clutch device 20
A sub-clutch 14 which is a hydraulically controlled multi-plate clutch is provided at the end (opposite to the). The sub-clutch 14 is composed of a pair of rotating members including a clutch drum and a clutch hub. At the time of gear shift, the clutch device 20 cuts off power transmission between the engine side and the transmission side, and the engagement control of the sub-clutch 14 is performed in this state. As a result, a transmission path of torque via the sub-clutch 14 and the gear train 15 is formed between the input / output shafts 1 and 2, and the transmission torque is variably controlled. Regarding specific control of the sub-clutch 14, Japanese Patent Application No. 2000-34878, which is a prior application of the present applicant.
No. 2000-35066 or 2000-
An example thereof is disclosed in No. 13099, and if necessary, refer to it.

FIG. 2 is a sectional view of the clutch device 20. The clutch device 20 includes a torque converter 21,
The lockup clutch 22 and the hydraulic clutch 23 are mainly configured. Here, the hydraulic clutch 23 is a release clutch that cuts off power transmission between the crankshaft 16 and the input shaft 1 during gear shifting.

The torque converter 21 comprises a pump impeller 21a, a turbine runner 21b and a stator 21c. The pump impeller 21a rotates together with the converter cover 24 and the drive plate 25 together with the crankshaft 16 on the engine side. A turbine runner 21b facing the pump impeller 21a is connected to a turbine hub 21d rotatably attached to the input shaft 1. In the present clutch device 20, the power transmission from the turbine runner 21b to the rotary shaft 1 is performed by the turbine hub 2
It is not performed via 1d but via a hydraulic clutch 23 described later. The stator 21c is provided on the outer race side of the one-way clutch 21e,
ATF (automatic transmission oil) flowing out from the turbine runner 21b is turned. This one-way clutch 21
The inner race side of e is spline-fitted with a stator shaft 27 integrated with the oil pump body 26.

The lockup clutch 22 is composed of a lockup piston 22a and a damper 22b which are rotatably mounted on a hub 28. On the facing surface side (front side) of the lock-up piston 22a, the facing surface 2 is provided at a portion facing the converter cover 24.
2c is provided, and a damper 22b is integrally attached to the back side thereof. The damper 22b is engaged with a clutch drum 29 integrated with the turbine runner 21b.

FIG. 3 is an illustration of engagement of the clutch drum 29. A plurality of cutouts 29a are provided on the entire outer peripheral end of the clutch drum 29. The engaging projections A formed on the outer peripheral portion of the damper 22b are engaged with the respective cutouts 29a. As a result, the lockup piston 22a is rotatable with respect to the hub 28, and the turbine runner 2 is rotated via the damper 22b.
It rotates integrally with 1b.

The hydraulic clutch 23 is the clutch disc 2
3a, a clutch piston 23b, and a retainer plate 23c. As shown in FIG. 4, engaging recesses are formed at predetermined intervals on the inner peripheral portion of the hollow disc-shaped clutch disc 23a, and the hub 2 is formed in each recess.
The claw portion formed on the outer peripheral portion of 8 is engaged. As a result, the clutch disc 23a rotates integrally with the hub 28. On the other hand, as shown in FIG. 3, the clutch piston 2
An engagement protrusion B formed on the outer peripheral portion of 3b engages with the notch 29a on the clutch drum 29 side. As a result, the clutch piston 23b rotates integrally with the turbine runner 21b via the clutch drum 29.

Here, the pressure of the pressure chamber S1 formed on the facing surface side of the lock-up piston 22a is P1. This pressure P1 causes the piston 22a to act on the release side in relation to the pressure P2. In addition, the pressure of the pressure chamber S2 formed on the back side of the lockup piston 22a is set to P
Set to 2. This pressure P2 causes the piston 22a to act on the engagement side in relation to the pressure P1. The engagement / release of the lockup clutch 22 is determined by the magnitude relationship between the pressures P1 and P2. If P1> P2, the lockup clutch 22 is released (torque converter state), and if P1 <P2, it is engaged (lockup state).

The hydraulic clutch 23 is in the engaged state except when shifting, but is disengaged when shifting. The clutch piston 23b is constantly pressed toward the engagement side by the pressure in the pressure chamber S2. Also, the clutch piston 23
b and the turbine runner 21b, pressure chambers S1 and S
A pressure chamber S3 independent of 2 is formed. When the pressure P3 of the pressure chamber S3 is lower than the pressure P2 of the pressure chamber S2 (P2> P3), the clutch piston 23b presses the clutch disc 23a via the retainer plate 23c, so that the hydraulic clutch 23 is engaged. It becomes a state. On the other hand, when hydraulic oil is supplied into the pressure chamber S3 and the pressure P3 becomes high (P2 <P3), the clutch piston 23b is displaced against the pressure P2, so that the hydraulic clutch 23 is released. become.

In order for the clutch device 20 to take the above-mentioned three states (torque converter state, lock-up state, hydraulic clutch released state), it is necessary to supply at least three systems of oil passages. That is, one is an oil passage for lock-up release that communicates with the pressure chamber S1 on the facing surface side of the lock-up piston 22a. The second is the pressure chamber S2 on the back side of the lockup piston 22a.
It is an oil passage for lock-up application that communicates with. The third is an oil passage for releasing the hydraulic clutch 23 that supplies hydraulic oil to the pressure chamber P3.

These three oil passages can be realized by using the input shaft 1 having the hollow hole 1a having a concentric double separation structure. FIG. 5 is an explanatory view of a plurality of concentric circular passages formed in the input shaft 1. A hollow hole 1a is provided at the front end of the input shaft 1, and a pipe member 30 having a hollow portion extending in the axial direction is arranged in the hollow hole 1a. The pipe member 30 has an outer diameter smaller than the hole diameter of the hollow hole 1a, and both ends thereof are sealed. Therefore, concentric passages a and b separated from each other are formed in the hollow hole 1a. The concentric gap between the outer peripheral portion of the input shaft 1 and the wall portion (inner peripheral portion of the stator shaft 27) of another member facing the outer peripheral portion is a passage c separated from the passages a and b. Used as.

The oil passage for lock-up release includes a passage hole 31 formed in the oil pump body 26 and a hollow hole 1
It includes a passage hole 1b communicating with a and being bored in the radial direction, and a passage a which is a hollow portion of the pipe member 30. The front end of the passage a is open, and the opening communicates with the pressure chamber S1 on the facing surface side of the lockup piston 22a. The pressure chamber S1 can communicate with the pressure chamber S2 via the lockup piston 22a, and the pressure chamber S2 communicates with the oil filling space of the torque converter 21. In addition, the oil passage for lock-up application is the passage hole 3 formed in the oil pump body 26.
2, a passage c formed in the outer peripheral portion of the input shaft 1, and a passage hole 33 formed in the oil pump body 26. The passage 33 hole communicates with the oil filling space of the torque converter 21. Further, the oil passage for release of the hydraulic clutch 23 has an oil passage hole 34 formed in the oil pump body 26.
And a passage hole 1c formed in the input shaft 1 in the radial direction,
1d and a passage b formed between the outer peripheral portion of the pipe member 30 and the inner peripheral portion of the input shaft 1. The passage hole 1d communicates with the hydraulic chamber S3 of the hydraulic clutch 23.

FIG. 6 shows a case where the input shaft 1 is press-fitted into the hollow hole 1a.
It is sectional drawing of the pipe member 30 fixed. The pipe member 30 is composed of a metallic cylindrical core member 30a (for example, an iron core bar) and a seal member 30b (for example, elastic seal rubber). Seal member 30b
Is baked on the entire outer periphery of the tubular core material 30a, but is thickly baked on both ends of the tubular core material 30a to form the stepped expanded portions 30c and 30d. These expanded parts 30
c and 30d have a sealing function of preventing oil leakage, and by providing a step, the pipe member 30 can be made into the hollow hole 1
It also has a positioning function when press-fitting into a.

FIG. 7 is a sectional view of the input shaft 1. When the input shaft 1 is drilled to form the hollow hole 1a, first, a hole having a depth L1 is drilled from the front end of the input shaft 1 with a drill having a drill diameter φ1. Next, drill diameter φ2
With the drill of (φ2> φ1), the bored hole is widened by a depth L2 (L2 <L1) which is shallower than the initial depth L1. In addition, the widened hole has a drill diameter of φ3 (φ3> φ
Use the drill in 2) to widen the depth by L3 (L3 <L2). As a result, a step for positioning that is engageable with the expanded diameter portion 30d on the pipe member 30 side is formed in the bottom shape of the hollow hole 1a. Further, the inner periphery of the hollow hole 1a near the front end is cut into a ring shape to form the engagement groove 1e. The engagement groove 1e is provided on the side of the pipe member 30 with the enlarged diameter portion 30.
It is engageable with c and effectively prevents the pipe member 30 press-fitted into the hollow hole 1a from coming off. Further, three holes in the radial direction of the input shaft 1 are drilled to form the above-mentioned passage holes 1b to 1d.

With such an oil passage structure, in the torque converter state, oil is supplied from the above-mentioned oil passage for lock-up release. Then, the supplied oil flows in the order of the facing surface side of the lockup clutch 22, the rear surface side thereof, and the torque converter 21, and is discharged from the lockup apply oil passage. When the oil flows in this way, the lockup clutch 22 is released. Since the hydraulic clutch 23 is engaged except when shifting, the power transmission path in the clutch device 20 includes the crankshaft 16, the converter cover 24, and the pump impeller 21.
a, the turbine runner 21b, the clutch drum 29, the clutch disc 23a, the hub 28, and the input shaft 1 in that order.

On the other hand, in the lockup state (clutch direct connection state), oil is supplied from the oil passage for lockup application. The supplied oil is the torque converter 2
1 to the back side of the lockup clutch 22. As a result, the pressure P2 on the back surface side of the lockup clutch 22 becomes higher than the pressure P1 on the facing surface side. As a result, the facing surface 22c of the lockup clutch 22 is pressed against the inner wall of the converter cover 24, and the lockup clutch 22 is engaged. Since the hydraulic clutch 23 is engaged except when shifting, the power transmission path in the clutch device 20 includes the crankshaft 16, the converter cover 24, the lockup piston 22a, the damper 22b, the clutch drum 29, and the clutch disc 2.
3a, hub 28, input shaft 1 in this order.

Further, at the time of gear shift, hydraulic oil is supplied to the hydraulic chamber S3 through the oil passage for releasing the hydraulic clutch to increase the pressure P3 in the hydraulic chamber S3. As a result, the hydraulic clutch 23 is released, and the power transmission between the clutch drum 29 and the clutch disc 23a is cut off.

In this embodiment, the hollow hole 1a provided at the end of the input shaft 1 has a double separation structure, and concentric circular passages a and b are formed in the hollow hole 1a.
As a result, an oil passage structure having a simple structure can be realized even if the oil passages are multi-systemized, and good assembling performance can be obtained. Further, the pipe member 30 is provided in the hollow hole 1a of the input shaft 1.
The two passages a and b are concentrically formed in the hollow hole 1a by arranging. Clutch device 20
The input shaft 1 that supports the end portion has a smaller diameter than the other rotating shafts in the transmission, but with the above configuration, the thickness of the input shaft 1 can be sufficiently secured. Moreover, in particular, the structure of the concentric hollow passages a and b as in the present embodiment has higher torsional rigidity as compared with the input shaft in which two hollow passages that are point-symmetric with respect to the shaft center are provided. It is advantageous in terms of shaft strength.
At the same time, by configuring the passages a and b concentrically,
It becomes easy to secure the required oil passage area.

Further, the expanded diameter portions 30c, 3 having a sealing function are provided at both ends of the pipe member 30 press-fitted into the hollow hole 1a.
0d is provided. As a result, even if the input shaft 1 is not subjected to such high processing precision, the expanded diameter portions 30c and 30d having elasticity can ensure airtightness and integrity after press fitting. In particular, it is difficult to perform precision machining of the inner diameter of the hollow hole 1a formed in the input shaft 1, and it is advantageous in terms of cost if this point is unnecessary. Furthermore, by using the metal tubular core member 30a for the pipe member 30, both the assembling property and the pressure resistance at the time of press-fitting the pipe member 30 can be achieved.

The oil passage structure in which the two oil passages are concentrically provided in the hollow hole 1a of the input shaft 1 and the other oil passage is provided on the outer peripheral portion of the input shaft 1 as shown in FIG. It can be widely applied to other than the clutch device 20 shown in FIG.
For example, the present invention can be applied to a clutch device in which the hydraulic chamber that operates the lockup clutch is independent of the torque converter. In this case, it is necessary to provide two oil passages for lock-up apply / lock-up release of the torque converter and another oil passage for supplying hydraulic oil for operating the multi-plate lock-up clutch. . By applying the oil passage structure according to the present invention to the clutch device that requires such multi-system oil passages, the above-described excellent effects can be obtained.

[0035]

As described above, according to the present invention, it is possible to simplify the oil passage structure for the clutch device which needs to communicate with the oil passages of multiple systems. At the same time, the assembling workability can be improved and the shaft strength for supporting the clutch device can be ensured.

[Brief description of drawings]

FIG. 1 is a sectional view of an automatic transmission to which a clutch device according to this embodiment is applied.

FIG. 2 is a sectional view of a clutch device.

FIG. 3 is an explanatory diagram of engagement of a clutch drum.

FIG. 4 is an explanatory diagram of engagement of a clutch disc.

FIG. 5 is an explanatory view of a plurality of concentric circular passages.

FIG. 6 is a sectional view of a pipe member.

FIG. 7 is a sectional view of the input shaft.

[Explanation of symbols]

16 crankshafts, 20 clutch device, 21 torque converter, 21a Pump impeller, 21b Turbine runner, 21c stator, 21d turbine hub, 21e One-way clutch, 22 Lockup clutch, 22a Lock-up piston, 22b damper, 22c facing surface, 23 hydraulic clutch, 23a clutch disc, 23b clutch piston, 23c retainer plate, 24 converter cover, 25 drive plate, 26 oil pump body, 27 Stator shaft, 28 hubs, 29 Clutch drum, 39 pipe members, 31-34 Passage hole

Claims (8)

[Claims] 1. In an oil passage structure of a clutch device, an input shaft having a hollow hole at an end thereof, concentrically arranged in the hollow hole of the input shaft, and A pipe member having a hollow portion extending in the axial direction; and a clutch device provided at an end of the input shaft and communicating with the first oil passage and the second oil passage. The first oil passage includes the hollow portion of the pipe member, and the second oil passage is formed between an outer peripheral portion of the pipe member and an inner peripheral portion of the input shaft. An oil passage structure of a clutch device, which includes a concentric circular gap separated from the first oil passage. 2. The clutch device is further communicated with a third oil passage, and the third oil passage has an outer peripheral portion of the input shaft and an inner peripheral portion of a member facing the outer peripheral portion. The oil passage structure of the clutch device according to claim 1, further comprising: a concentric gap that is formed between the first oil passage and the second oil passage and is separated from each other. 3. The clutch device includes a torque converter with a lock-up clutch, a hydraulic clutch having a pressure chamber independent of the torque converter, an oil passage for lock-up release, and a lock-up apply. 3. The oil passage structure of the clutch device according to claim 2, wherein the oil passage structure communicates with at least three oil passages including the oil passage of FIG. 3 and the oil passage for operating the hydraulic clutch. 4. The clutch device includes a torque converter and a lockup clutch having a pressure chamber independent of the torque converter, and an oil passage for lockup release and an oil passage for lockup apply. Including an oil passage for operating the lockup clutch,
The oil passage structure of the clutch device according to claim 2, wherein the oil passage structure communicates with at least three oil passages. 5. A concentric gap formed between an outer peripheral portion of the pipe member and an inner peripheral portion of the input shaft is sealed by seal members at both ends of the pipe member. The oil passage structure of the clutch device according to any one of claims 1 to 4. 6. The pipe member includes a metal tubular core member,
A sealing member provided on an outer peripheral portion of the tubular core member, wherein the pipe member is provided with an enlarged diameter portion at both ends thereof by forming the sealing member thick. Item 6. The oil passage structure of the clutch device according to item 5. 7. The step according to claim 6, wherein a step or a groove is provided in a portion of the inner peripheral portion of the input shaft that abuts the enlarged diameter portion on the pipe member side. Clutch device oil passage structure. 8. The pipe member is fixed by being press-fitted into the hollow hole through an opening provided at an end portion of the input shaft. The oil passage structure of the clutch device described in.