JPH10138787A - Differential gear device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To shorten the axial length of a differential gear device even though a pair of friction clutches for controlling the yaw moment of a vehicle body, and actuators for the friction clutches. SOLUTION: A differential gear device comprises a differential gear mechanism 43 for allocating a drive force of an engine which is transmitted to a differential gear casing 5, between wheels through a pair of output members 45, 47, a speed increasing gear set 81, a friction clutch 107, a deceleration gear set 83 and a friction clutch 105 which are located between the differential gear casing 5 and the output member 47, actuators 109, 111 for engaging the friction clutches 105, 107, respectively, and a controller for individually actuating the actuators 109, 111. Further, the friction clutch 105 and the actuator 109 are arranged diametrically outside of the friction clutch 107 and the actuator 111.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a differential device for a vehicle.

[0002]

2. Description of the Related Art A differential device 301 as shown in FIG. 3 is described in Japanese Patent Application Laid-Open No. 8-35528.

The differential device 301 includes a differential mechanism 307 for distributing the driving force of the engine to the drive shafts 303 and 305, a speed increasing gear set 309 and a speed reducing gear set 311, and a differential case 313 of the differential device 301. A transmission gear set 315 connecting the gear sets 309 and 311; a friction clutch 317, 319 connected on one side to the drive shaft 305 and the other side connected to the speed increasing gear set 309 and the reduction gear set 311; , 319 and a pair of hydraulic pistons, and a controller for operating these hydraulic pistons.

The friction clutches 317 and 319 are arranged in the axial direction, and the respective hydraulic pistons are also arranged in the axial direction of the friction clutches 317 and 319.

When the friction clutch 317 is released and the friction clutch 319 is engaged, the rotation of the differential case 313 is reduced by the reduction gear set 311 and the wheels on the drive shaft 305 side are reduced. When the friction clutch 319 is released and the friction clutch 317 is engaged, the rotation of the differential case 313 is increased by the speed increasing gear set 309, and the speed of the wheels on the drive shaft 305 is increased.

The controller transmits and receives a driving force (driving torque) between the drive shafts 303 and 305 by connecting and disconnecting the friction clutches 317 and 319 in this manner, and actively controls the yaw moment of the vehicle to turn. And improve the stability of the attitude of the vehicle.

[0007]

However, as described above, since the friction clutch 317 and its hydraulic piston and the friction clutch 319 and its hydraulic piston are axially arranged with respect to each other, the differential device 301 has a smaller axial dimension. Is long.

In the axial direction of the differential device 301, rubber boots and suspension arms of the drive shafts 303 and 305 are arranged, and there is no room for arrangement, so that interference with these peripheral members is avoided. In addition, the axial dimension of the differential device should be as short as possible.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a differential device which is provided with a pair of friction clutches and respective actuators for reducing the yaw moment of a vehicle body, and which is shortened in the axial direction. I do.

[0010]

According to a first aspect of the present invention, there is provided a differential device for distributing a driving force of an engine input to a differential case to a wheel through a pair of output members.
A speed increasing gear set and a first friction clutch disposed between the differential case and one output member, and a reduction gear set and a second friction clutch disposed between the differential case and the output member. First and second actuators for engaging the first and second friction clutches, respectively, and these actuators
And a controller for operating each of the friction gears separately.
A first friction clutch, an actuator thereof, and a second friction clutch for increasing / decelerating a differential rotation between the motor and the one output member and transmitting / receiving a driving torque between the pair of output members. And its actuators are radially arranged with respect to each other.

As described above, when the friction clutch on the reduction gear set side is released and the friction clutch on the speed increasing gear set is engaged, the speed of one of the output member wheels is increased, and the driving torque of the one output member is increased. The driving torque of the other output member is reduced. For example, when one of the output members is connected to the outer wheel side when the vehicle turns, the vehicle generates a yaw moment inward from the turning direction, so that the turning performance is improved and the vehicle posture is stabilized. When the friction clutch on the speed increasing gear group side is released and the friction clutch on the reduction gear group side is engaged, one output member side wheel is decelerated. For example, in this case, the other output member is connected to the outer wheel when the vehicle turns in the opposite direction to the above-described turning direction, and also generates a yaw moment inward from the turning direction of the vehicle. Also in this case, the vehicle can obtain a smoother turning performance and a stable turning posture. Conversely, when the driving torque of the output member on the outer wheel side is applied to the output member on the inner wheel side during turning of the vehicle, a yaw moment in the direction opposite to the turning direction is generated.

Further, as described above, the differential device according to the first aspect includes the first friction clutch and the actuator.
By arranging the second clutch and the second friction clutch and the actuator in the radial direction with respect to each other, the axial dimension is greatly shortened as compared with the conventional example, and the margin on the arrangement space is accordingly increased, and the joint portion and the like are reduced. Interference with peripheral members such as rubber boots and suspension arms can be avoided.

Since there is room in the radial direction of the differential device in the arrangement space, there is no problem even if the radial size is increased by arranging both friction clutches in the radial direction.

According to a second aspect of the present invention, there is provided the differential device according to the first aspect, wherein a common hub is provided between the first and second friction clutches, and an inner friction member of the large-diameter side friction clutch is provided on an outer periphery thereof. And an outer friction member of a small-diameter-side friction clutch is connected to an inner periphery thereof.
The same effect as that of the configuration is obtained.

In addition, the inner friction member of the large diameter friction clutch is connected to the outer periphery of the hub disposed between the first and second friction clutches, and the outer friction member of the small diameter friction clutch is connected to the inner periphery. By connecting, this hub is shared by both friction clutches. As described above, in addition to shortening the axial dimension, the increase in the radial dimension of the portion where both friction clutches are arranged can be small, and the radial This is advantageous also on the arrangement space.

[0016] The invention of claim 3 is claim 1 or claim 2.
A differential device comprising: a parallel shaft disposed in parallel with the one output member; and a transmission means for connecting the differential case and the parallel shaft. First and second friction clutches and actuators are disposed between the output member and the parallel shaft, and the actuators are disposed on the parallel shaft. And a parallel axis is intermittently provided, and an effect equivalent to that of the first or second aspect is obtained.

In addition, a speed increasing gear set and a speed reducing gear set are arranged between the parallel shaft connected to the differential case and the output member, and the first and second friction clutches are mounted on the parallel shaft. The coaxial arrangement is advantageous in that the axial dimension of the differential device is further reduced, and the margin for avoiding interference with peripheral members is increased.

Further, by disposing the two friction clutches on the parallel shaft, the two friction clutches and the actuator can be separated from each other.
For example, it is possible to arrange the members arranged on the drive shaft such that they are overhanged radially outward of the members arranged on the drive shaft, and the effect of preventing interference with peripheral members is further improved.

According to a fourth aspect of the present invention, there is provided the first or second aspect.
A differential device comprising: a parallel shaft disposed in parallel with the one output member; and a transmission means for connecting the differential case and the parallel shaft. First and second friction clutches and respective actuators are disposed on the output member, and are provided between the output member and the parallel shaft. Each output member side gear of the speed increasing gear set and the reduction gear set is disposed on the output member. It is characterized by intermittent connection with the output member,
The same effect as the configuration of claim 1 or 2 is obtained.

When the friction clutches are arranged on the parallel shaft, the gears on the parallel shaft among the gears constituting the speed increasing gear set and the reduction gear set need to have a large diameter in order to avoid interference with the friction clutch. According to the configuration of claim 4, since the friction clutches are arranged on the output member, the friction between the speed increasing gear set and the reduction gear set is increased. Since the gears are released from interference with the clutch and the diameters of the constituent gears can be reduced, the weight of the differential device is reduced accordingly, and the diameter of the portion where the speed increasing gear set and the reduction gear set are arranged is reduced, and the arrangement space is reduced. In terms of advantages.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIG. This embodiment has the features of claims 1, 2, and 3. FIG. 1 shows the differential device 1 of this embodiment, and the left and right directions are the vehicle in which the differential device 1 is used and the left and right directions in FIG.

The differential device 1 includes a differential carrier 3
The differential case 5 is supported on the differential carrier 3 by bearings 7 and 9.

Ring gear 11 fixed to differential case 5
Are engaged with the drive pinion gear 13. The drive pinion gear 13 is formed integrally with the rear end of the drive pinion shaft 15 and has bearings 17, 19,
1 supports the differential carrier 3.

A flange 23 is spline-connected to the front end of the drive pinion shaft 15 and is fixed with a nut 25. A seal 27 is disposed between the differential carrier 3 and the flange 23 to prevent oil leakage to the outside. doing. The drive pinion shaft 15 is connected to the propeller shaft via a flange 23.

Thus, the driving force of the engine rotates the differential case 5 from the transmission via the propeller shaft.

A plurality of pinion shafts 31 are arranged radially around the boss 29 inside the differential case 5. A pair of pressure rings 33 are connected to the inner periphery of the differential case 5 so as to be movable in the axial direction. Cams 35 are formed between the outer end of each pinion shaft 31 and each pressure ring 33.

A pinion gear 37 is rotatably supported on the pinion shaft 31. The pinion gear 37 meshes with the left and right side gears 39 and 41 to form a bevel gear type differential mechanism 43. Side gear 39, 4
1 is supported from the radial outside by meshing with the pinion gear 37.

The respective side gears 39, 41 are spline-connected to left and right drive shafts 45, 47 (output members), and the respective drive shafts 45, 47 are connected via joints 49, 51 and the other drive shafts, respectively. Connected to wheels. A seal 53 is arranged between the differential carrier 3 and each of the drive shafts 45 and 47 to prevent oil leakage to the outside.

The differential case 5 and the side gears 39, 4
The multi-plate clutch 55 is disposed between the clutches 1 and 2.

The driving force of the engine for rotating the differential case 5 is transmitted from the pressure rings 33, 33 to the cams 35, 35.
Is transmitted to the pinion shaft 31 via the pinion shaft 31, and further distributed from the pinion shaft 31 to the side gears 39 and 41 via the pinion gear 37, and transmitted to each wheel side. or,
When a difference in driving resistance occurs between wheels on a bad road or the like, the driving force of the engine is differentially distributed to each wheel side by the rotation of the pinion gear 37.

Further, the torque for rotating the differential case 5 operates the cams 35, 35 to press the multiple disc clutch 55 via the pressure rings 33, 33 to be engaged. The torque-sensitive differential limiting force is obtained by the friction torque of each multi-plate clutch 55, and the differential rotation of the differential mechanism 43 is limited.

The straight running stability of the vehicle is improved by the torque-sensitive differential limiting force.

At the right end of the differential case 5, a large-diameter boss portion 5 is provided.
The bearing 9 supports the inner periphery of the boss 57 between the boss 57 and the partition 59 of the differential carrier 3. Seals 61, 61 are arranged between the partition wall 59 and the drive shaft 47 on the right side to prevent oil leakage from the side where the differential case 5 is arranged. Partition part 5
9 is provided with an air hole 62 for communicating between the seals 61, 61 and the atmosphere side, and the pressure between the seals 61, 61 is set to the atmospheric pressure.

A parallel shaft 6 is provided in front of the drive shaft 47.
3 are arranged. A flange member 65 is spline-connected to the right end of the parallel shaft 63. The parallel shaft 63 is supported by the differential carrier 3 at the left end by a bearing 67 and at the right end by a bearing 69 via a flange member 65. Partition 59 of differential carrier 3
Seals 71, 71 are arranged between the shaft and the parallel shaft 63 to prevent oil leakage between the seal 71 and the parallel shaft 63. The partition wall 59 is provided with an air hole 72 for communicating between the seals 71, 71 and the atmosphere side.
Is between the atmosphere.

A small-diameter transmission gear 73 is spline-connected to the outer periphery of the boss portion 57 of the differential case 5, and the transmission gear 73 is supported on a partition wall 59 of the differential carrier 3 by a bearing 75. A large-diameter transmission gear 77 is formed integrally with the parallel shaft 63, and meshes with the transmission gear 73 to form a transmission gear set 79 (transmission means).

A speed increasing gear set 81 and a speed reducing gear set 83 are arranged between the drive shaft 47 and the parallel shaft 63. The speed-increasing gear set 81 includes large-diameter and small-diameter gears 85 and 87 that mesh with each other, and the reduction gear set 83 includes small-diameter and large-diameter gears 89 and 91 that mesh with each other.

The gears 85 and 89 are spline-connected to the drive shaft 47, are supported on the differential carrier 3 by bearings 93 and 95, respectively, and are supported on each other by a support portion 97.

The gear 87 has a left end supported by the partition wall 59 by a bearing 99 and a right end supported by the bearing 10.
1 is mounted on the parallel shaft 63. Also, the gear 91
Is supported on the outer periphery of the gear 87 by two bearings 103, 103.

On the right side of the speed increasing gear set 81 and the speed reducing gear set 83, large-diameter and small-diameter multi-plate clutches 105 and 107 and large-diameter and small-diameter hydraulic actuators 10 for fastening these clutches.
9, 111 (actuators) are arranged. Small-diameter multi-plate clutch 107 and its hydraulic actuator 111
Are disposed radially inward of the large-diameter multi-plate clutch 105 and its hydraulic actuator 109, respectively.

Each of the multi-plate clutches 105 and 107 is connected to the hub 11.
3, the large-diameter multi-plate clutch 105 is configured by engaging the outer and inner clutch plates (friction members) between the outer hub 115 and the shared hub 113 disposed inside thereof. The small-diameter multi-plate clutch 107 is configured by engaging outer and inner clutch plates (friction members) between a shared hub 113 and an inner hub 117 disposed outside.

The common hub 113 is fixed to the flange member 65 of the parallel shaft 63, and the hub 115 outside the multi-plate clutch 105 is integrated with the gear 91, and the multi-plate clutch 1
The hub 117 inside 07 is formed integrally with the gear 87.

The pistons 119 and 121 of the hydraulic actuators 109 and 111 are engaged with cylinders 123 and 125 provided on the differential carrier 3 via seals, respectively, and are stopped by detent pins 127 and 129. Have been.

The pressing members 131 and 133 are the flange members 6
5 and needle bearings 135 and 137 are disposed between the pressing members 131 and 133 and the pistons 119 and 121, respectively.

The hydraulic pressure is sent to the cylinders 123 and 125 of the hydraulic actuators 109 and 111 from an oil pump driven by the engine through a hydraulic circuit and oil plugs 139 and 141. When the hydraulic pressure is sent, the pistons 119 and 123 press the multi-plate clutches 105 and 107 via the needle bearings 135 and 137 and the pressing members 131 and 133, respectively, to fasten them.

A hydraulic switching valve is disposed in the hydraulic circuit of each of the hydraulic actuators 109 and 111. The controller operates the hydraulic switching valve to switch the hydraulic switching valve so as to send hydraulic pressure to the hydraulic actuator 109. -Ta 11
When the hydraulic pressure on the first side is cut off and the hydraulic pressure is sent to the hydraulic actuator 111, the hydraulic pressure on the hydraulic actuator 109 side is cut off.

As described above, the differential case 5 is connected to the hub 1 via the transmission gear set 79, the parallel shaft 63 and the flange member 65.
13, the hydraulic actuator 109
When the multi-plate clutch 105 is engaged and the multi-plate clutch 105 is engaged, the differential case 5 and the drive shaft 47 on the right side are connected via a reduction gear set 83, and the hydraulic pressure is sent to the hydraulic actuator 111 so that the multi-plate clutch 107 is Is fastened, the differential case 5 and the right drive shaft 47 are connected to the speed increasing gear set 81.
Are connected via.

When the differential case 5 and the drive shaft 47 are connected via the reduction gear set 83, the drive force of the drive shaft 47 decreases by the reduction torque, and the drive torque of the left drive shaft 45 increases by that amount. I do. Also, when the differential case 5 and the drive shaft 47 are connected via the speed increasing gear set 81, the driving torque of the drive shaft 47 increases by the speed increasing torque, and the driving force of the left drive shaft 45 increases accordingly. Decrease.

Each of the gears 91 and 91 is proportional to the amount of drive torque transmitted to the large-diameter gear 91 and the small-diameter gear 87.
87 is connected to the large-diameter multi-plate clutch 105 and the small-diameter multi-plate clutch 107.

In addition to the torque-sensitive differential limiting force by the multi-plate clutch 55, the driving torque is transmitted and received between the left and right drive shafts 45 and 47 by operating the multi-plate clutches 105 and 107, and the yaw of the vehicle is controlled. Actively control the moment to improve the turning performance and posture stability of the vehicle.

Thus, the differential device 1 is configured.

As described above, in the differential device 1, the multi-plate clutch 105 and its hydraulic actuator 10
9, the multi-plate clutch 107 and its hydraulic actuator 1
11 are arranged in the radial direction with respect to each other, the axial dimension is greatly reduced as compared with the conventional example in which they are arranged in the axial direction, and the margin on the arrangement space of the differential device 1 is increased accordingly, and the drive Interference with peripheral members such as rubber boots and suspension arms on the shaft 47 side can be avoided.

Further, since the hub 113 is shared by both the multi-plate clutches 105 and 107, in addition to shortening the axial dimension,
The increase in the radial dimension of the portion where the multiple disc clutches 105 and 107 are arranged is small, which is advantageous also in the radial space.

In addition, the multi-plate clutches 105, 10
7 and the hydraulic actuators 109 and 111 are connected to a parallel shaft 63.
With the arrangement above, the axial dimension of the differential device 1 is further shortened, and the margin for avoiding interference with peripheral members is advantageously increased.

Also, by arranging the multi-plate clutches 105 and 107 and the hydraulic actuators 109 and 111 on the parallel shaft 63, as shown in FIG. It is possible to dispose it in a bar-hanging manner, thereby further improving the effect of preventing interference with peripheral members.

Next, a second embodiment of the present invention will be described with reference to FIG. This embodiment has the features of claims 1, 2, and 4. FIG. 2 shows the differential device 143 of this embodiment, and the left and right directions are the vehicle using the differential device 143 and the left and right directions in FIG.

In FIG. 2 and the following description, members having the same functions as those of the differential device 1 are given the same reference numerals and quoted.

The differential device 143 is housed inside the differential carrier 3. The differential case 145 is supported on the differential carrier 3 by bearings 147 and 149, and is rotated by the driving force of the engine.

A plurality of pinion shafts 151 are radially arranged inside the differential case 145, and a pinion gear 153 is rotatably supported on each of the pinion shafts 151. Each pinion gear 153 meshes with left and right side gears 155, 157 to form a bevel gear type differential mechanism 159. Side gear 155, 1
57 is supported from the radial outside by meshing with the pinion gear 153.

The boss portion 16 of each side gear 155, 157
1, 163 are spline-connected to left and right drive shafts 45, 47, respectively.
Are respectively connected to the left and right wheels via a joint and another drive shaft.

A multi-plate clutch 165 is arranged between each of the bosses 161 and 163 and the differential case 145. Each multi-plate clutch 165 has a disc spring 167
Initial torque.

The ends of the bosses 161 and 163 abut against the differential case 145 to form the torque limiters 169 and 171 of the multi-plate clutch 165.

The driving force of the engine for rotating the differential case 145 is transmitted from the pinion shaft 151 to the pinion gear 15.
3 and is distributed to the side gears 155 and 157 and transmitted to each wheel side. When a difference in driving resistance occurs between the wheels on a bad road or the like, the driving force of the engine is differentially distributed to each wheel by the rotation of the pinion gear 153.

During transmission of torque, each side gear 15
5, 157 are moved left and right by the reaction force of the engagement with the pinion gear 153, and press and engage the multi-plate clutch 165. A torque-sensitive differential limiting force is obtained by the friction torque of each multi-plate clutch 165, thereby limiting the differential rotation of the differential mechanism 159.

The straight running stability of the vehicle is improved by the torque-sensitive differential limiting force. When a large torque is applied to the differential mechanism 159 due to sudden acceleration or the like, and the pressing force of each multi-plate clutch 165 exceeds a certain value, the torque limiter 16
9 and 171 operate to protect the multi-plate clutch 165 and prevent interference with the drive torque transfer control between the drive shafts 45 and 47.

A hollow parallel shaft 173 is disposed on one drive shaft 47 side. The parallel shaft 173 is a support shaft 177 fixed to the partition 175 of the differential carrier 3.
It is rotatably supported above.

The transmission gear 1 is provided at the right end of the differential case 145.
79 is spline-connected. A transmission gear 181 is integrally connected to the parallel shaft 173.
A speed increasing gear set 185 and a speed reducing gear set 187 are arranged between the drive shaft 47 and the parallel shaft 173 which mesh with the drive gear 79 and constitute a transmission gear set 183 (transmission means). The speed increasing gear set 185 is composed of a large-diameter and a small-diameter gear 1 meshed with each other.
The reduction gear set 187 is composed of small-diameter and large-diameter gears 193 and 195 meshing with each other.

The gears 189 and 193 are integrally connected to the transmission gear 181 of the transmission gear set 183 via the parallel shaft 173. The gear 191 is integrated with the hub 197,
The hub 197 is supported on the outer periphery of the drive shaft 47 by bearings 199 and 201. Gear 19
5 is integrated with the hub 203, and the hub 203 is supported on the outer periphery of the hub 197 by a bearing 205.

On the right side of the speed increasing gear set 185 and the speed reducing gear set 187, large-diameter and small-diameter multi-plate clutches 207 and 209 and large-diameter and small-diameter hydraulic actuators 211 and 213 (actuator) for engaging these clutches Are coaxially arranged on the drive shaft 47. Small-diameter multi-plate clutch 20
9 and its hydraulic actuator 213 are disposed radially inside the large-diameter multi-plate clutch 207 and its hydraulic actuator 211, respectively.

Each multi-plate clutch 207, 209 is connected to the hub 21.
5 is shared, and this hub 215 is
Through the drive shaft 47.

The large-diameter multi-plate clutch 207 is connected to the outer hub 2.
03 and a shared hub 215 disposed on the inner side thereof, the outer and inner clutch plates 219 and 221 (friction members) are engaged with each other.
09 is a shared hub 215 arranged outside and a hub 1 arranged inside.
97, the outer and inner clutch plates 223, respectively.
225 (friction member).

The pressure receiving member 227 of the multi-plate clutch 207 is fixed to the hub 215, and the pressure receiving member 229 of the multi-plate clutch 209 is fixed to the hub 197.

The hydraulic actuator 211 is disposed on the left side of the multiple disc clutch 207, and the hydraulic actuator 213 is disposed on the right side of the multiple disc clutch 209. Pistons 231 and 233 of hydraulic actuators 211 and 213
Are cylinders 235, 237 provided on the differential carrier 3.
Respectively.

The pressing member 239 penetrates the hub 203, and the pressing member 241 penetrates the flange 217 of the hub 215. Pressing members 239, 241 and pistons 231, 2
33 and needle bearings 243 and 2 respectively.
45 are arranged.

The hydraulic pressure is sent to the cylinders 235 and 237 of the hydraulic actuators 211 and 213 from an oil pump driven by the engine through a hydraulic circuit and oil plugs 247 and 249. When the hydraulic pressure is sent, the pistons 231 and 233 press and fasten the multi-plate clutches 207 and 209 via the needle bearings 243 and 245 and the pressing members 239 and 241 respectively.

A hydraulic switching valve is disposed in the hydraulic circuit of the hydraulic actuators 211 and 213. The controller switches this hydraulic switching valve to send hydraulic pressure to the hydraulic actuator 211. -Ta 21
When the hydraulic pressure at the hydraulic actuator 211 is shut off and the hydraulic pressure is sent to the hydraulic actuator 213, the hydraulic pressure at the hydraulic actuator 211 is interrupted.

The differential case 145 is connected to a speed increasing gear set 185 and a speed reducing gear set 187 via a transmission gear set 183.
Since the shared hub 215 of the multi-plate clutches 207 and 209 is connected to the drive shaft 47, when hydraulic pressure is sent to the hydraulic actuator 211 and the multi-plate clutch 207 is fastened, the differential case 145 and the right drive shaft 4
7 are connected via a reduction gear set 187, and when the hydraulic pressure is sent to the hydraulic actuator 213 and the multiple disc clutch 209 is engaged, the differential case 145 and the right drive shaft 47 are connected via the speed increasing gear set 185. Connected.

The differential case 145 and the drive shaft 47
Are connected via the reduction gear set 187, the driving force of the drive shaft 47 decreases by the reduction torque, and the driving torque of the left drive shaft 45 increases by that amount. or,
When the differential case 145 and the drive shaft 47 are connected via the speed increasing gear set 185, the drive shaft 47
Is increased by the speed increasing torque, and the driving force of the left drive shaft 45 is reduced accordingly.

Each gear 1 is set to be proportional to the amount of drive torque transmitted to the large-diameter gear 195 and the small-diameter gear 191.
Reference numerals 95 and 191 are connected to a large-diameter multi-plate clutch 207 and a small-diameter multi-plate clutch 209.

In addition to the torque-sensitive differential limiting force by the above-described multi-plate clutch 165, the multi-plate clutches 207, 209
By the operation, the drive torque is transmitted and received between the left and right drive shafts 45 and 47, the yaw moment of the vehicle is positively controlled, and the turning performance and the posture stability of the vehicle are improved.

Thus, the differential device 143 is configured.

As described above, the differential device 14
3, the multi-plate clutch 207 and its hydraulic actuator 211, the multi-plate clutch 209 and its hydraulic actuator
By arranging the motors 213 and 213 in the radial direction with respect to each other, the dimension in the axial direction is greatly reduced as compared with the conventional example in which these are arranged in the axial direction.
Interference with peripheral members such as rubber boots and suspension arms on the drive shaft 47 side can be avoided.

Further, since the hub 215 is shared by the two-plate clutches 207 and 209, in addition to the reduction of the axial dimension,
The increase in the dimension in the radial direction is small, which is advantageous in terms of the arrangement space in the radial direction.

In addition to this, each friction clutch 207, 2
09 is arranged on the drive shaft 47, the speed increasing gear set 185 and the speed reducing gear set 187 are released from interference with the friction clutches 207 and 209, and each gear 18
9, 191, 193 and 195 can be made smaller in diameter, so that the differential device 143 becomes lighter and the arrangement portion of each gear set 185 and 187 is made smaller in diameter, which is more advantageous in terms of arrangement space. .

The differential device of the present invention
Front differential (differential device that distributes engine driving power to left and right front wheels), rear differential (differential device that distributes engine driving force to left and right rear wheels), and center differential (engine driving force distributed to front and rear wheels) (A differential device for distributing).

The friction clutch is not limited to the multi-plate clutch, but may be a cone clutch, for example.

The transmission means may be a chain transmission or a belt transmission in addition to the gear transmission.

[0087]

According to the first aspect of the present invention, as described above, the speed increasing gear set and the speed reducing gear set provided between the differential case and one of the drive shafts are the first.
And the second friction clutch to transfer drive torque between one of the drive shafts and the other drive shaft to generate a yaw moment, thereby positively improving the turning performance and posture stability of the vehicle, By arranging the actuators in the radial direction with respect to each other, the dimension in the axial direction is shorter than that of the conventional example, so that the allowance on the arrangement space is correspondingly increased, and the joint parts, rubber boots, suspension arms, etc. Interference with unnecessary peripheral members can be avoided.

According to the differential device of the second aspect, the same effect as the configuration of the first aspect is obtained, and the hub is shared between the two friction clutches. The increase in the radial dimension of the portion that has been made is small, which is advantageous also in the radial arrangement space.

According to the differential device of the third aspect, the same effect as the configuration of the first or second aspect is obtained, and the first and second friction clutches and the respective actuators are arranged on the parallel shaft. As a result, the axial dimension of the differential device is further reduced, so that the margin of the arrangement space is increased, and interference with peripheral members is avoided.

Further, the two friction clutches and the actuator can be arranged so as to be overhanged radially outside of the member arranged on the drive shaft, thereby preventing interference with peripheral members. Is further improved.

According to the fourth aspect of the present invention, the differential device has the same effect as that of the first or second aspect, and the speed increasing gear set and the speed reducing gear set reduce the diameter of each gear without interfering with the friction clutch. Therefore, the weight of the differential device can be reduced accordingly, and the diameter of the portion where the speed increasing gear set and the speed reducing gear set are arranged is reduced, which is advantageous in terms of arrangement space.

[Brief description of the drawings]

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

FIG. 2 is a skeleton diagram showing a second embodiment of the present invention.

FIG. 3 is a skeleton diagram of a conventional example.

[Explanation of symbols]

1,143 differential device 5,145 differential case 43,159 differential mechanism 47 drive shaft (one output member) 63,173 parallel shaft 79,183 transmission gear set (transmission means) 81,185 speed increasing gear set 83, 187 Reduction gear set 105, 207 Multi-plate clutch (large-diameter side friction clutch) 107, 209 Multi-plate clutch (small-diameter side friction clutch) 109, 211 Hydraulic actuator (large-diameter side actuator) 111, 213 Hydraulic actuator (Small diameter actuator) 113, 215 Shared hub 221 Clutch plate (inner friction member of large diameter friction clutch) 223 Clutch plate (outer friction member of small diameter friction clutch)

Claims (4)

[Claims] 1. A differential mechanism for distributing a driving force of an engine input to a differential case to a wheel side via a pair of output members, and a speed increasing mechanism disposed between the differential case and one of the output members. A gear set and a first friction clutch, a reduction gear set and a second friction clutch disposed between the differential case and the output member, and first and second clutches for engaging the first and second friction clutches, respectively. A second actuator and a controller for operating each of the actuators separately, and a differential case and one of the outputs of the differential clutch via a friction clutch, a speed increasing gear set and a speed reducing gear set. What is claimed is: 1. A differential device for increasing / decelerating a differential rotation between members and transmitting / receiving a driving torque between a pair of output members, comprising: a first friction clutch and an actuator thereof; a second friction clutch and an actuator thereof; Are arranged radially to each other. A differential device characterized by being placed. 2. The invention according to claim 1, wherein the first
A common hub is provided between the first and second friction clutches, the inner friction member of the large-diameter friction clutch is connected to the outer periphery thereof, and the outer friction member of the small-diameter friction clutch is connected to the inner periphery thereof. Differential device. 3. The invention according to claim 1, wherein a parallel shaft arranged in parallel with said one output member;
A differential gear and a transmission means for connecting the parallel shaft; a speed increasing gear set and a reduction gear set are provided between the output member and the parallel shaft; A differential device, wherein each actuator is disposed on the parallel shaft, and each parallel shaft side gear of the speed increasing gear set and the speed reducing gear set is interrupted and connected to the parallel shaft. 4. The invention according to claim 1, wherein a parallel shaft arranged in parallel with said one output member;
A differential gear and a transmission means for connecting the parallel shaft; a speed increasing gear set and a speed reducing gear set are provided between the output member and the parallel shaft; A differential device, wherein each actuator is disposed on an output member, and each output member side gear and output member of a speed increasing gear set and a reduction gear set are intermittently connected.