JP2000291687A - Clutch device and differential device using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch device having a compact configuration and improving axial strength and a differential device using the clutch device by arranging an oil pump feeding oil to a slide face of a clutch plate on an inner side from an end face in the axial direction of a casing. SOLUTION: A gear pump 11 as an oil pump is arranged on an inner side in the axial direction on a left end face of a differential carrier 9 which is the right side of its cover 49 and is arranged on an inner side in the radial direction of a hydraulic actuator 7. The oil discharged from the gear pump 11 is fed from a discharge port 77 to an oil passage 65 of an inner rotor 59, a notched teeth part 67 of a countershaft 3, clutch hubs 63, 64, a slide bush 31, and a clutch plate of a multiple disc clutch 5 to lubricate them. Consequently, this clutch device becomes compact in the axial direction to improve vehicle mounting property.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch device and a differential device for controlling the yaw moment of a vehicle body using the clutch device.

[0002]

2. Description of the Related Art Japanese Patent Application Laid-Open No. 1-182127 (26th edition)
No. 41724) discloses a differential device 201 as shown in FIG.

In this differential device 201, the driving force of the engine is transmitted from the input shaft 203 to the bevel gear 2
The differential case 209 is rotated by the engagement of the gears 05 and 207, and the rotation of the differential case 209 is distributed from the differential mechanism 211 to the left and right wheels via the axles 213 and 215.

[0004] The rotation of the differential case 209 is controlled by the gear 21.
7, 219, and a speed change mechanism 221.
The counter-shaft 223 is rotated. The multi-plate clutches 225 and 227 are arranged on the counter shaft 223, and the side gears 229 and 23 of the differential mechanism 211 are arranged.
1 is a gear 23 connected to axles 213 and 215, respectively.
3 and gears 235 connected to the counter-shaft 223 via multi-plate clutches 225 and 227 are connected to the counter-shaft 223 by transmission mechanisms 237 and 239.

[0005] The multi-plate clutches 225, 227 are engaged by respective hydraulic actuators. To these hydraulic actuators, hydraulic pressure is sent from an engine-driven oil pump via a switching valve, and when one of the multiple disc clutches 225, 227 is engaged, the other is released. Thus, the operation is switched between the two hydraulic actuators.

The left multi-plate clutch 225 is disengaged,
When the right multi-plate clutch 227 is engaged, the transmission mechanism 221
And the speed change mechanism 239, and the right axle 215 side is accelerated by the entire speed increasing function, and the left axle 213 side is decelerated via the differential mechanism 211 by the increased speed. -Moment works.

When the right multi-plate clutch 227 is released and the left multi-plate clutch 225 is connected, the transmission mechanism 2
The transmission 21 and the transmission mechanism 237 are connected, and a yaw moment in the right turning direction acts on the vehicle body by the overall speed increasing function.

When the multi-plate clutches 225 and 227 are separately engaged as described above, the transmission mechanism 221 and the multi-plate clutch 22
The drive torque moves left and right through the gears 3 and 227 and the transmission mechanisms 237 and 239, and the yaw moment of the vehicle body is controlled.

If the vehicle is provided with the required direction of yaw moment by the yaw moment control function, the turning performance of the vehicle or the straight running stability is improved.

FIG. 3 shows the structure around the left multi-plate clutch 225.

The multi-plate clutch 225 is disposed between a clutch housing 241 connected to the gear 235 and a clutch hub 243 connected to the counter shaft 223.

The hydraulic actuator 245 of the multi-plate clutch 225 is disposed on a differential carrier 247 that accommodates the differential device 201, and the counter shaft 223 is supported by bearings 249.
It is supported by 47. The bearing 249 is positioned by a nut 250 screwed on the counter shaft 223.

At the left end of the differential carrier 247, an oil pump 251 for lubrication is arranged.

The oil pump 251 has a cover 25 fixed to the left end of the differential carrier 247 by bolts 253.
5. Outer rotor 257 and inner meshing with each other
It comprises a rotor 259 and the like. The outer rotor 257 is rotatably supported between the cover-255 and the differential carrier 247, and the inner rotor 259 is
It is connected to the counter-shaft 223 by 61.

The oil pump 251 is driven by the rotation of the counter shaft 223.

An axial oil passage 263 and oil passages 265 and 265 communicating with the oil passage 263 and opening in the radial direction are provided at the center of the counter shaft 223.

The oil discharged from the oil pump 251 is sent from these oil passages 263 and 265 to a bearing 249, a sliding bush 267 between the clutch housing 241 and the clutch hub 243, a multi-plate clutch 225, and the like to lubricate them. I do.

The periphery of the multi-plate clutch 227 on the right side is similarly constructed, and an oil pump 251 for lubrication is arranged at the right end of the differential carrier 247.

[0019]

Since the differential device 201 has the lubricating oil pumps 251 disposed at the left end and the right end of the differential carrier 247 as described above, the differential device 201 is large in the axial direction. Is declining.

Further, the strength of the counter shaft 223 is greatly reduced due to machining of the oil passage 263 in the axial direction and the oil passage 265 in the radial direction. May be impaired.

Also, by providing a hole 269 through which a pin 261 for connecting the inner rotor 259 is provided,
The strength of the shaft 223 further decreases.

Accordingly, an object of the present invention is to provide a clutch device which is compact and has high shaft strength and a differential device using the same.

[0023]

According to a first aspect of the present invention, there is provided a clutch device which is housed in a casing and is driven by receiving rotation of a torque transmitting member and a friction clutch in which a clutch plate is connected to a pair of torque transmitting members. And an oil pump for feeding oil to the sliding surface of the clutch plate, wherein the oil pump is disposed inside the axial end surface of the casing.

Thus, the clutch device of claim 1 is
Since the oil pump is disposed axially inward from the end face of the casing, the oil pump is compact in the axial direction and has high in-vehicle mountability.

According to a second aspect of the present invention, there is provided the clutch device according to the first aspect, wherein the oil pump is arranged in a radial direction of the actuator that presses the friction clutch. An effect equivalent to the configuration is obtained.

In addition, by disposing the oil pump in the radial direction of the actuator that presses the friction clutch, the device becomes more compact in the axial direction, and the vehicle mountability is improved.

The oil pump may be arranged radially inside or outside the actuator.

The invention of claim 3 provides claim 1 or claim 2.
2. The clutch device according to claim 1, wherein a toothless portion is provided on a spline portion of the torque transmission shaft, and discharge oil of an oil pump is guided to the friction clutch via the toothless portion. Alternatively, an effect equivalent to that of the configuration of claim 2 is obtained.

In addition to this, the spline portion of the torque transmission shaft is provided with a toothless portion to provide an oil passage for guiding the oil discharged from the oil pump to the friction clutch.
3 and the radial oil passage 265 make the counter-shaft 2
Unlike the conventional example in which the strength of the shaft 23 greatly decreases, the shaft strength is prevented from lowering.

Therefore, bending of the shaft is prevented, and the normal function is maintained.

The center oil passage 263 and the radial oil passage 2
In comparison with the machining of No. 65, machining of the toothless portion on the spline portion on the outer periphery of the shaft is extremely easy, and can be performed at low cost.

Further, the spline portion is provided on the outer periphery of the torque transmitting shaft, and the centrifugal force of the torque transmitting shaft is applied to the toothless portion provided on the spline portion, so that the oil flow is promoted by the centrifugal force. The lubrication efficiency of peripheral members such as friction clutches and bearings is greatly improved.

The invention according to claim 4 is the invention according to claims 1 to 3.
The clutch device according to any one of claims 1 to 3, wherein one rotation member of the oil pump is fixed to the torque transmission shaft by a nut, and is equivalent to any one of claims 1 to 3. Get the effect.

In addition, in this configuration in which the one-side rotating member is fixed to the torque transmitting shaft by the nut, the nut can be used for positioning a bearing that supports the torque transmitting shaft, and thus the nut can be used. For example, since one nut performs both functions of the conventional connecting pin 261 and the bearing positioning nut 250, the number of parts is reduced and the cost is reduced.

Further, since no connecting pin is used for fixing the one-side rotating member, unlike the conventional example, it is not necessary to form a hole for passing the pin in the torque transmitting shaft, and the shaft strength is improved accordingly. .

The invention of claim 5 is the invention of claims 1 to 4
The clutch device according to any one of the above, wherein the oil pump is an internal gear pump,
An effect equivalent to any one of claims 1 to 4 is obtained.

In addition to this, the gear pump can be formed to be thin in the axial direction, which is optimal for the present invention which makes the apparatus compact in the axial direction.

Further, an inscribed gear pump in which the outer rotor and the inner rotor are coaxially arranged makes the device compact in the radial direction, so that the in-vehicle mountability is further improved.

According to a sixth aspect of the present invention, there is provided a differential device, wherein the differential case is rotatably driven by the driving force of the engine, the differential mechanism outputs the rotation of the differential case from a pair of side gears to the axle side, the differential case and the axle. A speed increasing mechanism and a speed reducing mechanism respectively disposed between the clutch device and the clutch device according to any one of claims 1 to 5 disposed in a power transmission system of the speed increasing mechanism, and a power transmission system of the speed reducing mechanism. Claim 1
A clutch device according to any one of claims 1 to 5, wherein the clutch device releases one of the speed-up mechanism and the speed-reduction mechanism when the other is connected.

When the speed increasing mechanism is connected and the speed reducing mechanism is disconnected, for example, when the driving force moves from one axle to the other axle and the speed of the other wheel is increased, the other wheel is shifted to the outer wheel side. Is generated on the vehicle body.

When the deceleration mechanism is connected and the speed increasing mechanism is disconnected, the driving force moves from the other axle to the one axle to increase the speed of the one wheel, and the one wheel becomes the outer wheel. -Moment occurs on the vehicle body.

By providing such a yaw moment control function, the yaw moment in the required direction is given to the vehicle body, whereby the behavior of the vehicle body can be controlled and the maneuverability and stability can be greatly improved. .

For example, when turning at medium to low speeds, if the torque on the outer wheel side is increased to provide a yaw moment for encouraging turning, the turning performance of the vehicle is greatly improved. If the torque on the inner ring side is increased, high-speed stability is improved.

When the vehicle body is meandering on a rough road or the like, if the vehicle body is given a yaw moment in a direction opposite to the meandering, the meandering is converged, and the stability and the straight traveling property are improved.

In addition, in the configuration using the clutch device according to the first aspect, wherein the oil pump is disposed inside the axial end surface of the casing (for example, the differential carrier), the differential device and the differential carrier are made compact in the axial direction. In addition, the vehicle mountability is greatly improved.

Also, an actuator for pressing the friction clutch
In the configuration using the clutch device according to the second aspect in which the oil pump is disposed in the radial direction of the rotor, the engine is further compact in the axial direction, and the on-board performance is improved.

Further, in the configuration using the clutch device according to the third aspect, the toothless portion provided in the spline portion of the torque transmission shaft is used as an oil passage of the oil pump. It is prevented and the normal function is maintained, and the machining of the toothless part is easy and low cost.

Further, the flow of oil is promoted by the centrifugal force applied to the toothless portion, and the lubrication efficiency of peripheral members is greatly improved.

Further, in the configuration using the clutch device according to the fourth aspect, wherein one rotating member of the oil pump is fixed to the torque transmitting shaft with a nut, a connecting pin is not required, and the hole through which the pin is passed is formed on the shaft. Since the need for processing is eliminated, the strength of the shaft is improved accordingly.

In the configuration using the clutch device according to claim 5, wherein the oil pump is an internal gear pump, the oil pump can be made thin in the axial direction and the device can be made compact in the radial direction. It is suitable for the present invention, and the in-vehicle property is further improved.

[0051]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIG.

FIG. 1 shows a clutch device 1 of this embodiment. This clutch device 1 is claimed in claims 1, 2, 3,
The present invention has the features of the fourth and fifth aspects and is used for a differential device having the features of the sixth aspect.

The left and right directions are the vehicle using the differential device and the left and right directions in FIG. 1, and the members and the like without reference numerals are not shown.

This differential device, like the differential device 201 of FIG. 2, is a differential case that rotates by the driving force of the engine, a differential mechanism that distributes the rotation of the differential case to left and right wheels via an axle, and a counter. A pair of transmission gear mechanisms disposed between the differential case and each axle via the shaft 3 (torque transmission shaft), and a pair of multi-plate clutches 5 disposed between the counter shaft 3 and each transmission gear mechanism. (Friction clutch of the clutch device 1), a pair of hydraulic actuators 7, 7 for pressing these multi-plate clutches 5, 5, respectively, a controller for operating these hydraulic actuators 7, and the like. .

The differential device is arranged inside a differential carrier 9 provided with an oil reservoir.

The driving force of the engine for rotating the differential case is distributed from the differential mechanism to the respective wheels via the left and right axles, and the speed is changed by the transmission gear mechanism.
Each multi-plate clutch 5 arranged on the shaft 3 connects and disconnects the respective transmission gear mechanism and the counter-shaft 3 as described below.

Each multi-plate clutch 5 is pressed and engaged by the corresponding hydraulic actuator 7. Oil pressure is sent to these hydraulic actuators 7 from an engine-driven oil pump via a switching valve.

The controller operates this switching valve to switch and operate the hydraulic actuators 7,7.

When the engagement of the left-wheel multi-plate clutch 5 is released and the right-wheel multi-plate clutch 5 is engaged, the right-wheel multi-plate clutch 5 side transmission gear mechanism increases the speed of the right wheel, for example. Then, the left wheel side is decelerated by the speed increase via the differential mechanism, and the left turning yaw momentum acts on the vehicle body.

When the multi-plate clutch 5 on the right wheel is released and the multi-plate clutch 5 on the left wheel is engaged, the speed of the left wheel is increased by the transmission gear mechanism on the multi-plate clutch 5 of the left wheel. At the same time, the right wheel side is decelerated by the speed increase via the differential mechanism, and the right-handed yaw moment is applied to the vehicle body.

When the left and right multi-plate clutches 5 are separately engaged as described above, the driving torque moves left and right via the transmission gear mechanism, the multi-plate clutch 5 and the differential mechanism, and the yaw rate of the vehicle body is increased.
You can control the

By giving the vehicle the necessary direction of yaw moment by such a yaw moment control function, the behavior of the vehicle body can be controlled to greatly improve the maneuverability and stability. .

For example, when turning at a medium to low speed, the turning performance of the vehicle can be greatly improved by increasing the torque on the outer wheel side and providing a yaw moment for encouraging the turning. If the torque on the inner ring side is increased, high-speed stability is improved.

When the vehicle body is meandering on a rough road or the like, if the vehicle is provided with the yaw moment in the direction opposite to the meandering, the meandering is converged, and the stability and the straightness can be improved.

If the engagement force of the multi-plate clutches 5, 5 is controlled and they are slid appropriately, the yaw moment can be adjusted. It is possible to precisely control turning property, straight running property, stability, and the like.

When the two multi-plate clutches 5, 5 are released, the yaw moment control function is stopped.

As described above, the clutch device 1 is disposed on the left and right sides of the counter shaft 3, the left clutch device 1 connects and disconnects the left wheel side transmission gear mechanism, and the right clutch device 1 connects and disconnects the right wheel gear device. The transmission gear mechanism of each side is interrupted.

FIG. 1 shows the clutch device 1 on the left wheel side. Hereinafter, the clutch device 1 on the left wheel side will be described as an example.

The clutch device 1 comprises a multi-plate clutch 5, a hydraulic actuator 7, an internal gear pump 11 (oil pump) and the like.

The gears 12 and 13 meshing with each other form a part of a left-wheel-side transmission gear mechanism.

The gear 12 is supported on the differential carrier 9 by a bearing 15 and is spline-connected to the left axle. The bearing 15 is positioned by a bearing cap 17 screwed to the differential carrier 9. An O-ring 19 and an oil seal 21 are arranged between the left axle, the gear 12 and the bearing cap 17, respectively.
The O-ring 23 is disposed between the two to prevent oil leakage and foreign matter intrusion.

The gear 13 is spline-connected to the clutch housing 25, and a pressure receiving plate 27 receiving the pressing force of the multi-plate clutch 5 is fixed to the counter shaft 3.

The multi-plate clutch 5 includes the counter-shaft 3
It is arranged coaxially above and is arranged between the clutch housing 25 and the clutch hub 29. The clutch hub 29 is spline-connected to the counter-shaft 3, and a sliding bush 31 is disposed between the clutch housing 25 and the clutch hub 29.

As described above, the counter shaft 3, the gears 12, 13 and the left axle are connected via the multi-plate clutch 5.

The cylinder 33 of the hydraulic actuator 7 is provided on the differential carrier 9. The piston 35 is X
It is engaged with the cylinder 33 via the rings 37 and 39 and is prevented from rotating by the differential carrier 9 by a pin.

The hydraulic pressure is sent from the engine driven oil pump to the cylinder 33 via the switching valve. As described above, the controller operates the switching valve by the switching valve.
The hydraulic pressure is switched between the cylinder 33 of the left wheel side clutch device 1 and the cylinder 33 of the right wheel side clutch device 1.

Between the piston 35 and the multi-plate clutch 5,
A thrust bearing 41 and a pressing member 43 are arranged, and when hydraulic pressure is sent to the cylinder 33, the piston 35 presses and engages the multi-plate clutch 5 via these.

The pressing member 43 includes a snap ring 45.
A return spring 47 is disposed between the snap ring 45 and the clutch hub 29. When the hydraulic pressure is switched to the clutch device 1 on the other side, the return spring 47 pushes back the piston 35 and releases the multi-plate clutch 5.

A plate-like cover is provided on the left end surface of the differential carrier 9.
49 is fixed by bolts 51, and 0
A ring 53 is arranged to prevent oil leakage.

The gear pump 11 is disposed on the right side of the cover 49 (axially inside the left end face of the differential carrier 9), and further on the radially inner side of the hydraulic actuator 7.

The outer rotor 55 (torque transmitting member) of the gear pump 11 is rotatably supported by a cylindrical support portion 57 provided on the differential carrier 9.
Nut 59 (torque transmitting member: one side rotating member)
And is fixed to the left end of the counter-shaft 3.

The left end of the counter shaft 3 is supported on the differential carrier 9 by bearings 63 and 64, and the nut 61 presses and positions the bearings 63 and 64 via the inner rotor 59.

The inner rotor 59 is provided with an oil passage 65 in the radial direction, and the spline portion of the counter shaft 3 connecting the inner rotor 59 is provided with an oil passage 6.
5 is provided with a missing tooth portion 67 (oil passage) communicating with the fifth tooth.

Further, at the left and right ends of the clutch hub 29, radial oil passages 69 and 71 communicating with the toothless portion 67 are provided.
Are provided.

The suction port 75 provided in the pump chamber of the cover 49 sucks oil from the oil reservoir of the differential carrier 9 into the pump chamber, and the oil discharged from the gear pump 11 flows through the discharge port 77 to the inner rotor 59. From the oil passage 65, the missing tooth portion 67 of the counter shaft 3 and the oil passages 69 and 71 of the clutch hub 29 to the bearings 63 and 64, the sliding bush 31, the clutch plate of the multi-plate clutch 5, and the like. Lubricate.

The oil lubricating the multi-plate clutch 5 is supplied to the oil passage 7
It is discharged from 3 and returns to the oil sump.

The flow of the oil is promoted by the centrifugal force of the counter shaft 3, the clutch hub 29, and the clutch housing 25 to circulate through the respective parts, thereby improving the lubrication efficiency.

The toothless portion 67 provided on the spline portion on the outer periphery of the counter shaft 3 has a counter
Unlike the central oil passage 263 provided in the shaft 223, the centrifugal force of the counter shaft 3 is applied, so that the oil flow is further promoted by this centrifugal force and the lubrication efficiency is greatly improved.

Thus, a differential device using the clutch device 1 is configured.

As described above, the differential device (clutch device 1) differs from the prior art in that the gear pump 11
Are arranged inside the axial end face of the differential carrier 9 and further radially inside the hydraulic actuator 7, so that the differential device and the differential carrier 9 are compact in the axial direction, and the vehicle mountability is greatly improved.

Further, since the spline portion of the counter shaft 3 is provided with a toothless portion 67 to form an oil passage and no oil passage is formed at the center, unlike the conventional counter shaft 223, the counter shaft 3 The strength is not reduced, bending is prevented, and normal functions are maintained.

Further, it is extremely easy to machine the toothless portion 67 in the spline portion, rather than machining the oil passage 263 at the center and the oil passage 265 in the radial direction as in the conventional example. It can be implemented at low cost.

Further, as described above, the counter shaft 3
A large centrifugal force is applied to the toothless portion 67 provided on the outer periphery of the, and the oil flow is promoted by the centrifugal force, and the lubrication efficiency is greatly improved.

The inner rotor 59 of the gear pump 11
Is fixed to the counter-shaft 3 with a nut 61.
Since the nut 61 is used for positioning the bearings 63 and 64, the function of both the connecting pin 261 and the bearing positioning nut 250 of the conventional example is performed by one nut 61, so that the number of parts is reduced and the number of parts is reduced. Cost.

Further, since it is not necessary to form a hole for passing the connecting pin 261 in the counter-shaft 3,
The strength of the counter-shaft 3 is further improved.

Since the gear pump 11 can be made thin in the axial direction, it is suitable for the present invention in which the differential device (clutch device 1) is made compact in the axial direction.

Further, the inscribed type gear pump 11 in which the outer rotor 55 and the inner rotor 59 are coaxially arranged can make each device compact in the radial direction, so that the in-vehicle mountability is further improved.

[0098]

According to the first aspect of the present invention, since the oil pump is arranged inside the axial end surface of the casing, the clutch device is compact in the axial direction and has high vehicle mountability.

According to the second aspect of the present invention, the same effect as that of the first aspect is obtained, and the oil pump is arranged in the radial direction of the actuator, so that it is more compact in the axial direction and has high mountability. .

The invention of claim 3 is the invention of claim 1 or claim 2.
In addition to obtaining the same effect as the configuration described above, the missing tooth portion is used as the oil passage of the oil pump, and the oil passage is not provided in the center portion or in the radial direction of the torque transmission shaft. Function is preserved.

Further, it is very easy to process the missing tooth portion on the spline portion, and it can be implemented at low cost.

Further, the flow of oil is promoted by the centrifugal force applied to the toothless portion on the outer periphery of the torque transmission shaft, and the lubrication efficiency of peripheral members such as friction clutches and bearings is greatly improved.

The invention of claim 4 is the first to third aspects of the present invention.
By obtaining the same effect as any one of the above, by fixing the rotating member on one side of the oil pump and positioning the bearing of the torque transmission shaft with the same nut, the number of parts is reduced as compared with the conventional example, Lower cost.

Further, since a hole for passing the connecting pin of the one-side rotating member is not formed in the torque transmitting member, the shaft strength is improved accordingly.

The invention of claim 5 is the invention of claims 1 to 4
In addition to obtaining the same effect as any of the above, the device is thin in the axial direction and is compact in both the axial direction and the radial direction by an inscribed gear pump in which the outer rotor and the inner rotor are coaxially arranged. , And the on-board performance is further improved.

According to a sixth aspect of the present invention, there is provided the differential device, wherein the clutch device according to any one of the first to fifth aspects is used for a clutch for intermittently connecting a speed increasing mechanism and a speed reducing mechanism for controlling the yaw moment of the vehicle body. As a result, the same effects as those described above are obtained.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is a skeleton mechanism diagram of a differential device using a conventional example.

FIG. 3 is a sectional view of a conventional example.

[Description of Signs] 1 Clutch device 3 Counter shaft (torque transmission shaft) 5 Multi-plate clutch (friction clutch) 7 Hydraulic actuator (actuator pressing friction clutch) 9 Differential carrier (casing) 11 Internal connection Type gear pump (oil pump) 55 Outer rotor of gear pump 11 59 Inner rotor of gear pump 11 Nut 63, 64 for fixing inner rotor 59 to shaft 3 and positioning bearings 63, 64 Bearing 67 that supports the counter shaft 3 Missing tooth portion (oil passage) provided in the spline portion of the counter shaft 3

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3D042 AA06 AA07 CA12 CB02 CB03 CC00 3J057 AA04 BB04 CA13 EE05 EE10 GA11 GA71

Claims (6)

[Claims] 1. A friction clutch which is housed in a casing and has a clutch plate connected to a pair of torque transmitting members, and is driven by the rotation of the torque transmitting member to send oil to a sliding surface of the clutch plate. A clutch device, comprising: an oil pump, wherein the oil pump is disposed inside an axial end surface of the casing. 2. The clutch device according to claim 1, wherein the oil pump is disposed in a radial direction of the actuator that presses the friction clutch. 3. The torque transmission shaft according to claim 1, wherein a spline portion of the torque transmission shaft is provided with a toothless portion, and oil discharged from an oil pump is supplied to the friction clutch via the toothless portion. A clutch device characterized by being guided to a clutch. 4. The invention according to claim 1, wherein the one side rotating member of the oil pump is
A clutch device fixed to a torque transmission shaft by a nut. 5. The clutch device according to claim 1, wherein the oil pump is an internal gear pump. 6. A differential case which is rotationally driven by a driving force of an engine, a differential mechanism which outputs rotation of the differential case from a pair of side gears to an axle side, and is arranged between the differential case and the axle. 6. A speed increasing mechanism and a speed reducing mechanism, and a power transmission system of the speed increasing mechanism.
And a clutch device according to any one of claims 1 to 5 disposed in a power transmission system of the speed reduction mechanism, and these clutch devices connect one of the speed increasing mechanism and the speed reduction mechanism. A differential device for releasing the other connection when connecting.