JP2000203294A - Differential device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently lubricate respective lubricating places while reducing agitating resistance, and to enable control by oil pressure by arranging an oil pump being driven by a drive pinion shaft and giving and receiving oil between the oil pump and an oil housing chamber and oil passages for supplying delivery oil to a required place. SOLUTION: An oil housing chamber 157 is formed between a tubular part 5 and a drive pinion shaft 19 by a seal 155 arranged between an intermediate part of the drive pinion shaft 19 and the tubular part 5 and a front side seal 31. An oil pump 158 driven by rotation of the drive pinion shaft 19 is arranged in a rear part of this oil housing chamber 157. An oil passage 179 connected to a delivery outlet of the oil pump 158 branches off into the other oil passage 199. The oil passage 199 is connected to oil passages 210, 203, 205 to thereby supply sufficient oil to respective lubricating places and hydraulic actuators 125, 127.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

2. Description of the Prior Art FIG.
1 is shown.

The differential device 301 includes a differential case 303 which is rotated by the driving force of an engine, and a left and right drive shafts 305 which rotate the differential case 303.
A differential mechanism 309 for distributing to wheels via 307, a drive force control mechanism on the speed increasing side and a driving force reducing side arranged respectively between the differential case 303 and the right drive shaft 307, a controller and the like. Have been.

The driving force control mechanism on the speed increasing side includes a differential case 3
Transmission gear set 313 for connecting the drive shaft 03 and the counter shaft 311, and the speed increasing gear set 31 arranged in series between the counter shaft 311 and the right drive shaft 307.
5 and a multi-plate clutch 317, a hydraulic actuator 319 for fastening the multi-plate clutch 317, and the like.

The driving force control mechanism on the reduction side includes a transmission gear set 313, a reduction gear set 32 arranged in series between the counter shaft 311 and the right drive shaft 307.
1 and a multi-plate clutch 323, a hydraulic actuator 325 for fastening the multi-plate clutch 323, and the like.

The controller operates the hydraulic actuators 319 and 325 individually via control valves, and releases one of the multiple disc clutches 317 and 323 when one of them is engaged.

When the multi-plate clutch 317 is engaged, the rotation of the differential case 303 is accelerated by the speed increasing gear set 315 and transmitted to the right wheel via the speed increasing side driving force control mechanism. The force becomes greater than the driving force of the left wheel, and a counterclockwise yaw moment is generated in the vehicle body. Also, multi-plate clutch 3
When 23 is engaged, the rotation of the differential case 303 is reduced by the reduction gear set 321 and transmitted to the right wheel via the reduction-side driving force control mechanism, so that the driving force of the left wheel is larger than the driving force of the right wheel. The clockwise yaw moment is generated on the vehicle body.

As described above, by controlling the driving forces distributed to the left wheel and the right wheel, for example, when the clockwise yaw moment is applied to the vehicle body, the right turning property is improved, and If the yaw moment is given, the left turning property is improved.

The differential device 301 is accommodated in a differential carrier 327.

The differential carrier 327 is divided into left and right storage chambers 331 and 333 by a partition wall 329. The left housing chamber 331 has a differential case 303 and a transmission gear set 313.
And an oil reservoir for hypoid gear oil is provided. The right accommodation chamber 333 accommodates each driving force control mechanism other than the transmission gear set 313, and is provided with an oil reservoir of an automatic fluid, which is a working oil of the automatic transmission.

The hypoid gear oil in the storage chamber 331 is
The ring gear 335 fixed to the differential case 303, the differential case 303, the transmission gear set 313, etc. are repelled to the surroundings by rotation, and the meshing portion between the ring gear 335 and the drive pinion gear 337, the transmission gear set 313, bearings 339, 341 are provided. , 343, 345 and the like.

The automatic fluid in the storage chamber 333 is repelled to the surroundings by the rotation of the speed increasing gear set 315, the reduction gear set 321 and the like, and each meshing portion of the speed increasing gear set 315 and the reduction gear set 321 is engaged. , Multi-plate clutch 317, 3
23, bearings 347, 349, 351, 353, 3
Lubricate 55 etc.

[0013]

However, in the differential device 301, as described above, the oil in the oil reservoir is repelled by each rotating member for lubrication.
Due to the large resistance caused by the stirring of the oil, a loss of the driving force occurs, and the fuel efficiency of the engine decreases.

In lubrication with repelling oil, like bearings and multi-plate clutches 317 and 323,
It is difficult to supply sufficient oil to lubricating points that are too small to allow oil to enter.

The amount of oil that can be sealed in each of the storage chambers 331 and 333 is insufficient. Even if the amount of oil in the oil reservoir is increased, lubricating efficiency cannot be expected to be improved with the repelling oil. The agitation resistance greatly increased and the condition was poor.

There is also a differential device that incorporates an oil pump that rotates with a drive shaft on the wheel side and is used for a driving force control mechanism as described above or configured to forcibly lubricate each part. In this configuration, since the rotation speed of the oil pump is affected by the differential rotation (differential mechanism) and the discharge amount of the oil fluctuates, the capacity of the oil pump cannot be freely set according to the application. It is difficult to perform accurate driving force movement control and sufficient forced lubrication.

Further, in the configuration in which the oil pump is arranged on the drive shaft, the size of the differential device is increased in the axial direction, so that the vehicle mountability is reduced.

Accordingly, an object of the present invention is to provide a differential device capable of sufficiently lubricating each lubricating portion or controlling by hydraulic pressure while greatly reducing oil stirring resistance.

[0019]

According to a first aspect of the present invention, there is provided a differential device in which a drive pinion shaft which rotates by driving force of an engine, a drive pinion gear which rotates integrally with the drive pinion shaft, and a ring gear which meshes with the drive pinion gear are fixed. It has a differential case, a differential mechanism for distributing the rotation of the differential case to the wheel side via a pair of output members, and a tubular portion and a large-diameter casing, and a drive pinion shaft connects the tubular portion. Penetrate,
A casing provided with a differential carrier for accommodating the differential case, an oil accommodating chamber formed by separating a tubular portion of the differential carrier and the drive pinion shaft with a seal, and driven by the drive pinion shaft; An oil pump for transferring oil to and from the oil storage chamber, and formed on a differential carrier, or provided outside the differential carrier to supply oil to a suction port of the oil pump,
Alternatively, an oil flow path for supplying oil discharged from an oil pump to a required portion is provided.

As described above, in the differential apparatus according to the first aspect, the oil accommodating chamber is formed between the tubular portion of the differential carrier and the drive pinion shaft, and the oil pump that is rotationally driven by the drive pinion shaft is disposed.

If the oil discharged from the oil pump is supplied to, for example, each lubricating point, a lubricating point such as a bearing or a multi-plate clutch, which is narrow and hard to enter oil, is forcibly lubricated and sufficiently lubricated. Wear and seizure are prevented, and durability is greatly improved.

In addition, since the oil can be dry-sprayed by forced lubrication in this manner, it is not necessary to repel the oil with a differential case or the like for lubrication. Loss is prevented, and the fuel efficiency of the engine is greatly improved.

The oil storage chamber provided between the tubular portion of the differential carrier and the drive pinion shaft has a large capacity unlike the oil reservoir formed in the differential carrier in the conventional example, and has a large capacity for rotation of the drive pinion shaft. Since a large resistance is not applied, a sufficient amount of oil can be stored, and sufficient oil can be supplied to necessary parts (such as lubricating parts and a control unit using hydraulic pressure).

The oil pump driven to rotate by the drive pinion shaft on the engine side is different from the oil pump driven to rotate by the drive shaft on the wheel side in that the rotation speed does not fluctuate due to the influence of the differential rotation, and Therefore, the capacity of the oil pump can be set freely according to the application.

Therefore, for example, in a configuration in which the discharge oil is used for the control pressure, accurate control is possible. In a configuration in which lubrication is used, more effective lubrication can be performed.

Also, the configuration in which the oil pump is disposed on the drive pinion shaft is different from the conventional configuration in which the oil pump is disposed on the drive shaft, whereby the differential device is made compact in the axial direction, and the vehicle mountability is improved.

According to a second aspect of the present invention, there is provided a differential device comprising: a drive pinion shaft which is rotated by a driving force of an engine; a drive pinion gear which rotates integrally with the drive pinion shaft; a differential case in which a ring gear meshing with the drive pinion gear is fixed; A differential mechanism for distributing the rotation of the wheel to the wheel side via a pair of output members, a tubular portion and a large-diameter casing, wherein a drive pinion shaft penetrates the tubular portion to form a casing; A differential carrier for accommodating a differential case, and an oil pump for sucking oil accumulated in a casing of the differential carrier; and an oil pump formed on the differential carrier or provided outside the differential carrier and connected to an inlet of the oil pump. Or an oil flow path for supplying discharge oil to the required location And it features.

As described above, in the differential apparatus according to the second aspect, for example, oil that flows down to the casing of the differential carrier after lubricating the respective parts is sucked up by the oil pump, so that the oil reservoir that provides stirring resistance to the differential casing and the like. Are not formed in the casing.

Therefore, loss of driving force is prevented, and the fuel efficiency of the engine is greatly improved.

The third aspect of the present invention provides the first and second aspects.
3. The differential device according to claim 1, wherein an oil pump disposed between the tubular portion of the differential carrier and the drive pinion shaft sucks up oil accumulated in a casing of the differential carrier.
The same effect as that of the configuration is obtained.

In addition, since one set of oil pumps driven by a drive pinion shaft is configured to suck up oil accumulated in the casing of the differential carrier, the structure is simplified and the number of parts is reduced. And
Lightweight, compact, low cost, and easy to mount.

The invention according to claim 4 is the invention according to claims 1 to 3.
The differential device according to any one of the above, between the two output members of the differential mechanism and the differential case, or,
A pair of transmission mechanisms arranged between one of the output members and the differential case to move the driving torque to adjust the torque distribution ratio between the wheels; and a pair of clutches intermittently intermittently transfer the torque by the transmission mechanism. A pair of hydraulic actuators for opening and closing these clutches respectively, wherein the discharge pressure of the oil pump is used for one or both of the operating pressure of the hydraulic actuator and forced lubrication. The same effects as those of the first to third aspects are obtained.

In addition, as described above, the oil pump which is not affected by the rotation speed due to the influence of the differential rotation, the oil discharge amount is stable, and the capacity can be freely set according to the use, is a hydraulic actuator. Since a stable operating pressure is always applied to the motor, precise yaw moment control can be performed.

Further, in a configuration in which the discharge oil is used for forced lubrication, the lubrication can be effectively performed by stabilizing the discharge amount of the oil.

Further, similarly to the conventional example shown in FIG. 5, even with a structure having a good space factor in which a pair of transmission mechanisms and a clutch, a hydraulic actuator and the like are housed in a differential carrier together with a differential case, the speed can be changed by forced lubrication. Narrow lubrication points such as mechanisms and clutches are fully lubricated,
Wear and seizure are prevented, and durability is greatly improved.

According to a fifth aspect of the present invention, in the differential device according to the fourth aspect, the casing of the differential carrier is divided into an accommodation room for accommodating the speed change mechanism and an accommodation room for accommodating the differential case. The oil pump sucks up the oil accumulated in the storage chamber of the transmission mechanism, and has the same effect as that of the fourth aspect.

In this configuration, the casing of the differential carrier is divided into a housing chamber for accommodating the transmission mechanism and a housing chamber for accommodating the differential case, and the oil pump sucks oil from the accommodation chamber of the transmission mechanism.

In this way, since no oil reservoir is formed in the storage chamber of the transmission mechanism, each gear constituting the transmission mechanism is released from the oil stirring resistance, and loss of driving force is prevented.
The fuel efficiency of the engine is greatly improved.

The invention of claim 6 is the first to third aspects of the present invention.
The differential device according to any one of claims 1 to 3, wherein the differential case is provided with an outer case that is rotated by a driving force of an engine, and an inner case rotatably disposed inside the outer case and connected to a differential mechanism. -Case,
A clutch for intermittently connecting the outer case and the inner case, and a hydraulic actuator for opening and closing the clutch are provided. The discharge pressure of the oil pump is controlled by the operating pressure of the hydraulic actuator and the forced lubrication. It is characterized in that it is used for one or both, and the same effects as those of the first to third aspects are obtained.

This differential device is disposed on the wheel side of a four-wheel drive vehicle that is separated during two-wheel drive. When the outer case and the inner case are connected by a clutch, the driving force of the engine is reduced. The power is transmitted from the dynamic mechanism to the wheel side, and the vehicle enters a four-wheel drive state, so that rough road running performance, stability of the vehicle body, hill climbing performance and the like are improved.

When the connection is released and the inner case is disconnected from the wheels, the vehicle enters a two-wheel drive state.
Engine fuel efficiency is improved.

Further, since the discharge amount of the oil pump is stable and a stable operating pressure is constantly applied to the hydraulic actuator, the power is accurately switched on and off at a desired timing, and the performance of the vehicle as described above is greatly improved. Can be improved.

Further, in the configuration in which the discharge oil is used for forced lubrication, the lubrication can be effectively performed by stabilizing the discharge amount of the oil.

In addition to a differential case having a double structure of an outer case and an inner case, a structure having a good space factor for accommodating a clutch and a hydraulic actuator in a differential carrier is also provided by forced lubrication. Since a small lubricating portion such as a clutch is sufficiently lubricated, wear and seizure are prevented, and the durability is greatly improved.

The invention of claim 7 is the first to third aspects of the present invention.
The differential device according to any one of claims 1 to 3, further comprising: a clutch for intermittently connecting any two of the differential rotating members constituting the differential mechanism; and a hydraulic actuator for opening and closing the clutch. 4. The method according to claim 1, wherein the discharge pressure of the oil pump is used for one or both of the operating pressure of the hydraulic actuator and the forced lubrication.
The same effect as that of the configuration is obtained.

In this differential device, when the clutch is engaged, the differential is locked, and the vehicle is improved on a rough road, and when the clutch is released, the differential becomes free and the turning performance is improved.

Further, since the discharge amount of the oil pump is stabilized and a stable operating pressure is constantly applied to the hydraulic actuator, accurate differential locking is performed at a desired timing, and the performance of the vehicle as described above is greatly increased. Can be improved.

Further, in the configuration in which the discharge oil is used for forced lubrication, the lubrication can be effectively performed by stabilizing the discharge amount of the oil.

Further, even in a structure having a good space factor for accommodating the clutch and the hydraulic actuator in the differential carrier together with the differential case, the narrow lubricating portion such as the clutch can be sufficiently lubricated by the forced lubrication, so that wear and seizure can occur. Are prevented, and the durability is greatly improved.

[0050]

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

FIG. 1 shows a differential device 1 according to this embodiment. The differential device 1 has the features of claims 1, 2, 3, and 4. The left and right directions correspond to the vehicle using the differential device 1 and FIG.
Left and right directions.

The differential device 1 is a differential carrier 3
Is housed inside.

As shown in FIG. 1, the differential carrier 3 has a tubular portion 5
And a large-diameter casing 7.

The differential case 9 of the differential device 1 is supported on the casing 7 of the differential carrier 3 by bearings 11 and 13.

Ring gear 15 fixed to differential case 9
Is meshed with the drive pinion gear 17, and the drive pinion gear 17 is formed integrally with the rear end of the drive pinion shaft 19. The drive pinion shaft 19 penetrates the tubular portion 5 of the differential carrier 3 from the front, and is supported by bearings 21, 23, 25.

A flange 27 is spline-connected to the front end of the drive pinion shaft 19, and is fixed with a nut 29. A seal 31 is disposed between the tubular portion 5 and the flange 27 to prevent oil from leaking to the outside.
The drive pinion shaft 19 is connected to the propeller shaft side via a flange 27.

Thus, the driving force of the engine rotates the differential case 9 from the transmission via the propeller shaft.

A plurality of pinion shafts 35 are arranged radially around the boss 33 inside the differential case 9. A pair of pressure rings 37 are connected to the inner periphery of the differential case 9 so as to be movable in the axial direction. A cam 39 is provided between the outer end of each pinion shaft 35 and each pressure ring 33. 39 are formed.

A pinion gear 41 is rotatably supported on the pinion shaft 35. The pinion gear 41 meshes with the left and right side gears 43 and 45 to form a bevel gear type differential mechanism 47. Side gear 43, 4
5 is supported from the radial outside by meshing with the pinion gear 41.

The side gears 43 and 45 are spline-connected to left and right drive shafts 49 and 51 (output members), and the respective drive shafts 49 and 51 are connected to the left and right drive shafts via joints 53 and 55 and other drive shafts, respectively. Connected to wheels.

The differential carrier 3 and each drive shaft 4
A seal 57 is disposed between the seals 9 and 51 to prevent oil leakage to the outside.

Further, the differential case 9 and the respective side gears 43, 4
5, a multi-plate clutch 59 is disposed.

The driving force of the engine for rotating the differential case 9 is transmitted from the pressure rings 37, 37 to the cams 39, 39.
To the pinion shaft 35, and further distributed from the pinion shaft 35 to the side gears 43, 45 via the pinion gear 41, and the drive shafts 49, 51
And is transmitted to the left and right wheels via the.

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 41.

Further, the cams 39, 39 operate by receiving the torque, and press the multiple disc clutches 59, 59 via the pressure rings 37, 37 to be engaged. Each multi-plate clutch 59
A torque-sensitive type differential limiting force is obtained by the friction torque of, and the differential rotation of the differential mechanism 47 is limited.

The torque-sensitive differential limiting force improves, for example, the stability and maneuverability of the vehicle during straight-ahead acceleration.

The casing 7 of the differential carrier 3 comprises a partition 6
1 divides into left and right accommodation chambers 63 and 65.
Hypoid gear oil,
Alternatively, an automatic fluid is enclosed.

The differential case 9 is housed in the left housing chamber 63, and a large-diameter boss 67 is formed on the right end side. The above bearing 13 for supporting the differential case 9
Supports the boss 67 on the partition wall 61.

The drive shaft 51 on the right side is
1, a pair of seals 69, 69 are disposed between the drive shaft 51 and the partition wall 61. These seals 69, 69 prevent the movement of oil between the storage chamber 63 and the storage chamber 65, and prevent ingress and egress of the respective abrasion powder.

A space 71 is formed between the seals 69, 69, and the partition wall 61 is provided with a pressure release hole 73 communicating the space 71 with the atmosphere, so that the space 71 is always large. Maintained at atmospheric pressure.

A counter shaft 75 is arranged in front of the drive shaft 51, and a flange member 77 is spline-connected to the right end of the counter shaft 75. The counter shaft 75 is supported on the differential carrier 3 by a bearing 79 at the left end and by a bearing 81 via a flange member 77 at the right end.

The counter shaft 75 penetrates the partition wall 61, and a pair of seals 83 are arranged between the counter shaft 75 and the partition wall 61. These seals 83, 83 prevent movement of oil between the storage chamber 63 and the storage chamber 65, and prevent ingress and egress of respective abrasion powder and the like.

A space 85 is formed between the seals 83, 83, and a pressure release hole 87 is provided in the partition wall 61 for communicating the space 85 with the atmosphere, so that the space 85 is always large. Maintained at atmospheric pressure.

A transmission gear 89 is spline-connected to the outer periphery of the boss portion 67 of the differential case 9.
9 is supported on the partition wall 61 by bearings 91. The counter shaft 75 has another transmission gear 93.
Are formed integrally, and between the drive shaft 51 and the counter-shaft 75 which mesh with the transmission gear 89 to form the transmission gear set 95, a speed increasing gear set 97 (transmission mechanism) and a reduction gear set 99. (Transmission mechanism). The speed-increasing gear set 97 includes large-diameter and small-diameter gears 101 and 103 that mesh with each other, and the reduction gear set 99 includes small-diameter and large-diameter gears 105 and 107 that mesh with each other.

The gears 101 and 105 are connected to the drive shaft 5
1 and are supported on the casing 7 by bearings 109 and 111, respectively, and are supported on each other by a support 113.

The gear 103 has a bearing 11 at the left end.
5 is mounted on the partition wall 61, and the right end is a bearing 1
17 is mounted on the counter shaft 75. The gear 107 is supported on the outer periphery of the gear 103 by two bearings 119.

On the right side of the speed increasing gear set 97 and the speed reducing gear set 99, large-diameter and small-diameter multi-plate clutches 121, 123 (clutches) and large-diameter and small-diameter hydraulic actuators 125, 127 for engaging these clutches, respectively. Is arranged. Small-diameter multi-plate clutch 119 and its hydraulic actuator 123
Are disposed radially inward of the large-diameter multi-plate clutch 117 and its hydraulic actuator 121, respectively.

The multi-plate clutches 121 and 123 are connected to the hub 12
9 are shared. In addition, the large-diameter multi-plate clutch 121 includes an outer hub 131 and a shared hub 129 disposed inside the outer hub 131.
And the outer and inner clutch plates are engaged with each other. The small-diameter multi-plate clutch 119 is provided between the shared hub 129 and the inner hub 133 disposed on the outer side. It is configured by engaging a clutch plate.

The common hub 129 is a counter-shaft 7
5 is fixed to the flange member 77. The hub 131 outside the multi-plate clutch 121 is integrated with the gear 107, and the hub 133 inside the multi-plate clutch 123 is formed integrally with the gear 103.

The pistons 135 and 137 of the hydraulic actuators 125 and 127 are engaged with cylinders 139 and 141 provided on the differential carrier 3 via seals, respectively, and are stopped by detent pins 143 and 145. Have been.

The pressing members 147 and 149 are the flange members 7
7. Needle bearings 151 and 153 are disposed between the pressing members 147 and 149 and the pistons 135 and 137, respectively.
149 is blocked from the pistons 135 and 137.

As shown in FIG. 1, a seal 155 is disposed between the intermediate portion of the drive pinion shaft 19 and the tubular portion 5 of the differential carrier 3, and the seal 155 and the front seal are provided. An oil storage chamber 157 is formed between the tubular portion 5 and the drive pinion shaft 19 by the screw 31.

Further, at the rear of the oil storage chamber 157,
The oil pump 158 shown in FIG. 1 or the oil pump 159 shown in FIG. 2 is arranged between the tubular portion 5 and the drive pinion shaft 19.

The oil pump 158 has an outer gear connected to the tubular portion 5 and an inner gear connected to the drive pinion shaft 19.
Gear pump connected to the oil pump 1
59, the cam ring 160 is connected to the tubular portion 5 and the rotor 161 is connected to the drive pinion shaft 19 as shown in FIG.
Is a vane pump connected to the pump.

Each of the oil pumps 158 and 159 is driven by the rotation of the drive pinion shaft 19.

As shown in the example of the oil pump 159 of FIG. 2, the oil pumps 158 and 159 have two suction ports 16.
2, 163 and two discharge ports 165, 167 are provided.

One of the suction ports 162 is provided in the oil storage chamber 157.
To inhale oil. Also, the other suction port 163
Are oil passages 16 provided outside the differential carrier 3.
9 communicates with the bottom of the storage chamber 63, and sucks up oil from this bottom.

Further, although not shown, this inlet 1
Similarly, 63 sucks up oil from the bottom of the storage chamber 65 through another oil flow path.

As shown in FIG. 3, four control valves 171, 173 and 17 are provided in the hydraulic circuit of the differential device 1.
5, 177 are used. These are solenoid valves.

The control valves 171 and 173 constitute directional change valves, and as shown in FIG. 1, discharge ports 165 and 167 of oil pumps 158 and 159 through an oil flow path 179 provided outside the differential carrier 3. It is connected to.

The control valves 171 and 173
One is opened and the other is closed by a direction change valve signal 183 given from a controller 181 to switch the supply destination of the discharge oil between the hydraulic actuators 125 and 127.

By this switching, when the hydraulic actuator 121 is operated by sending the hydraulic pressure, the hydraulic pressure on the hydraulic actuator 123 side is cut off, and when the hydraulic pressure is sent to the hydraulic actuator 123 to be operated, the hydraulic pressure is reduced. The hydraulic pressure on the actuator 121 side is shut off.

The control valves 175 and 177 are respectively connected to the control valves 171 and 173 and the hydraulic actuator 12.
5 and 127 are connected on an oil line, and an ON-OFF signal 18 from a controller 181 is provided.
5 and 187, the hydraulic actuator 12 in operation.
5 and 127, the oil is returned to the oil storage chamber 157, and the flow rate of the returned oil is adjusted.
The hydraulic pressure (pressing force) of the hydraulic actuators 125 and 127 is adjusted.

When hydraulic pressure is sent to each of the cylinders 139 and 141 of the hydraulic actuators 125 and 127, each of the pistons 135 and 137 is connected to the multi-plate clutch via the needle bearings 151 and 153 and the pressing members 147 and 149, respectively. 121 and 123 are pressed and fastened.

As shown in FIG. 4, the controller 181 includes:
Throttle sensor 189, steering sensor 191,
Vehicle speed sensor 193, front and rear G sensor 195, lateral G sensor 1
The signal from 97 enters. Based on these signals, the controller 181 determines the direction change valve signal 1 based on these signals, as described above.
83, ON-OFF signals 185 and 187 are controlled by control valve 1
Send to 71,173,175,177.

Speed increasing gear set 97 and small-diameter multi-plate clutch 12
3 and the hydraulic actuator 127 constitute a driving force control mechanism on the speed increasing side, and the reduction gear set 99, the large-diameter multi-plate clutch 121 and the hydraulic actuator 125 constitute a driving force control mechanism on the reduction side. I have.

As described above, since the differential case 9 is connected to the hub 133 via the transmission gear set 95, the counter shaft 75, and the flange member 77, the hydraulic actuator of the reduction-side driving force control mechanism is provided. When the hydraulic pressure is sent to 125 and the multi-plate clutch 121 is engaged, the differential case 9 and the drive shaft 51 are connected via a reduction-side driving force control mechanism (reduction gear set 99).

When hydraulic pressure is sent to the hydraulic actuator 127 of the speed increasing side driving force control mechanism and the multi-plate clutch 123 is engaged, the differential case 9 and the drive shaft 51 are connected to the speed increasing side driving force control mechanism ( The gears are connected via a speed increasing gear set 97).

When the differential case 9 and the drive shaft 51 are connected via the deceleration-side driving force control mechanism, the differential case
The rotation of the gear 9 is reduced by the reduction gear set 99, the right wheel on the drive shaft 51 side is reduced, and the clockwise
Moment occurs.

Also, the differential case 9 and the drive shaft 51
Are connected via a speed increasing side driving force control mechanism, the rotation of the differential case 9 is speeded up by the speed increasing gear set 97, the right wheel is speeded up, and the yaw motor rotates counterclockwise to the vehicle body. -Ment occurs.

The controller 181 has the multi-plate clutches 121 and 12 of the driving force control mechanisms on the speed increasing side and the speed reducing side.
By controlling the driving force of the right wheel by switching the number 3, the yaw moment of the vehicle body is controlled.

For example, if the vehicle body is provided with clockwise yaw moment, the right turning property is improved, and if the counterclockwise yaw moment is provided, the left turning property is improved.

Further, if the yaw moment is controlled in such a direction as to cancel the turning of the vehicle body in addition to the torque-sensitive differential limiting force by the multi-plate clutch 59, the straight running stability of the vehicle body is improved.

Also, as shown in FIG.
The oil flow path 179 connected to the discharge ports 165 and 167 of the 159 branches to another oil flow path 199. The oil passage 199 is provided in the casing 7 of the differential carrier 3.
And an oil passage 201 in the axial direction provided through the oil passage 201 and the counter shaft 75.
1 includes a radial oil flow path 20 opening into the accommodation chamber 65.
3, 205 are provided.

The oil discharged from the oil passages 203 and 205 is supplied to the speed increasing gear set 97, the reduction gear set 99, the multi-plate clutches 121 and 123, the bearings 81, 109 and 11
1, 115, 117, 119, needle bearing 15
Lubricate 1, 153 and the like and flow down to the bottom of the storage chamber 65.

The oil that has flowed down to the bottom of the storage chamber 65 is
As described above, since the oil is sucked up by the oil pumps 158 and 159 and returned to the oil storage chamber 157, no oil reservoir is formed in the storage chamber 65.

Similarly, the interior of the storage chamber 63 is forcibly lubricated by the oil from the oil pumps 158 and 159, and the oil that has flowed to the bottom of the storage chamber 63 is
8, 159, the oil storage chamber 157
Therefore, no oil reservoir is formed in the storage chamber 63.

Thus, the differential device 1 is configured.

As described above, in the differential device 1, the oil storage chamber 157 is formed between the tubular portion 5 of the differential carrier 3 and the drive pinion shaft 19, and
The drive pinion shaft 1 is
Oil pumps 158 and 159 driven to rotate by
Was placed.

Each lubricated portion is forcibly lubricated by the oil pumps 158 and 159, and each bearing and the multi-plate clutch 1 are lubricated.
Since lubricating portions such as 21 and 123 which are small and hard to enter oil are sufficiently lubricated, abrasion, seizure and the like are prevented, and durability is greatly improved.

As described above, since the lubrication is performed by the dry spraying method of the oil, the oil does not need to be repelled by a differential case or the like for lubrication. Loss is prevented, and the fuel efficiency of the engine is greatly improved.

The oil storage chamber 157 provided between the tubular portion 5 of the differential carrier 3 and the drive pinion shaft 19
Unlike the oil reservoir provided in the differential carrier as in the conventional example, the oil reservoir has a large capacity and does not give a large resistance to the rotation of the drive pinion shaft 19, so that it is possible to store a sufficient amount of oil. Sufficient oil can be supplied to each lubrication point and the hydraulic actuators 125 and 127.

Oil pumps 158 and 159 which are driven to rotate by a drive pinion shaft 19 on the engine side.
Is different from an oil pump driven by the drive shafts 49 and 51 on the wheel side in that the rotation speed does not fluctuate due to the influence of the differential rotation and the oil discharge amount is stabilized. The capacity of the pump can be freely set.

Accordingly, accurate yaw moment control can be performed, and each part can be effectively lubricated.

Further, the configuration in which the oil pumps 158 and 159 are arranged on the drive pinion shaft 19 is different from the conventional configuration in which the oil pump is arranged on the drive shaft 19 in that the differential device 1 is more compact in the axial direction. The on-board performance is improved.

Further, oil that flows down to the casing 7 (housing chambers 63 and 65) of the differential carrier 3 after lubricating each part is sucked up by the oil pumps 158 and 159, so that the oil that gives a resistance to stirring to the differential case 9 and the like is provided. No pool is formed.

Accordingly, loss of driving force is prevented, and engine fuel efficiency is greatly improved.

Further, since one set of oil pump 158 or one set of oil pump 159 controls the momentum and performs forced lubrication,
Simple structure, reduced number of parts, lightweight, compact,
The cost is reduced and the in-vehicle performance is improved.

Further, as described above, the oil pumps 158 and 159 capable of releasing the influence of the differential rotation, stabilizing the oil discharge amount and freely setting the capacity are always stable to the hydraulic actuators 125 and 127. Since the operating pressure is adjusted, precise yaw moment control can be performed.

Further, by stabilizing the oil discharge amount, forced lubrication can be performed more effectively.

Further, the differential case 9, the ring gear 15, the drive pinion gear 17, the drive pinion shaft 19
In addition, the transmission gear set 95, the speed increasing gear set 97, the reduction gear set 99, the multi-plate clutches 121 and 123, the hydraulic actuators 125 and 127, and the like are accommodated in the casing 7 of the differential carrier 3. Even with a good structure, as described above, the narrow lubricated portion is sufficiently lubricated by the forced lubrication, so that abrasion, seizure and the like are prevented, and the durability is greatly improved.

Further, the differential device 1 includes two drive force control mechanisms on the speed increasing side and the decelerating side.
Since the driving force control mechanism is arranged on one side, the driving force control mechanism can be accommodated in one accommodation room 65 as compared with a configuration in which the driving force control mechanism is arranged on both output members. Is improved.

In the present invention, unlike the embodiment,
The oil flow path of the oil pump may be formed in a differential carrier.

Further, in the structure of the fourth aspect, different from the above-described embodiment, both the speed change mechanism for controlling the yaw moment of the vehicle body is a speed increasing mechanism or a speed reducing mechanism, and these are used as both output members. It may be arranged between the case and the differential case.

Further, the structure of claim 4 is a structure in which the yaw moment of the vehicle body is controlled by the transmission mechanism.
According to the fifth aspect of the present invention, the oil is sucked up from the storage chamber provided for the transmission mechanism to prevent the formation of an oil reservoir, and each gear is released from the oil stirring resistance, thereby reducing the loss of driving force.

In the structure in which the casing of the differential carrier is divided into a housing for the transmission mechanism and a housing for the differential case, the housing for the transmission mechanism is provided by an oil pump. Alternatively, the oil may be sucked up from the storage chamber of the differential case.

As described above, in the configuration in which the casing is divided into two chambers and the oil is sucked up from one of the two chambers, different types of oil, for example, the differential oil is supplied to the respective storage chambers of the differential case. In this case, an automatic fluid can be used in the accommodation room of the transmission mechanism.

Further, the invention of claim 6 is a differential device having an intermittent power function, and the invention of claim 7 is a differential device having a differential lock function.

As in the case of the embodiment, in each case, the narrow lubricated portion is sufficiently lubricated by the forced lubrication, so that a predetermined function is obtained, and abrasion and seizure are prevented.
The durability is greatly improved.

The oil pump is not limited to a gear pump or a vane pump, but may be another type of oil pump.

The differential device according to the fourth, fifth and sixth aspects of the present invention includes a front differential (a differential device for distributing the driving force of the engine to the left and right front wheels) and a rear differential (a differential for distributing the driving force of the engine to the left and right rear wheels). Device).

The differential device according to claim 7 is
The present invention can be used for any of a front differential, a rear differential, and a center differential (a differential device for distributing the driving force of an engine to front wheels and rear wheels).

[0133]

According to the first aspect of the present invention, as described above, the oil storage chamber is formed between the tubular portion of the differential carrier and the drive pinion shaft, and the oil pump driven by the drive pinion shaft is provided. As a result, due to the forced lubrication of the oil pump, lubricating points where oil does not easily enter are sufficiently lubricated, wear and seizure are prevented, and durability is greatly improved.

Further, since the oil can be dry-sprayed, it is free from the stirring resistance due to the splashing of the oil.
Engine fuel efficiency is greatly improved.

Further, since the oil storage chamber provided between the tubular portion of the differential carrier and the drive pinion shaft has a large capacity, a sufficient amount of oil can be obtained, and sufficient oil can be obtained at a necessary portion (a lubricating portion, a hydraulic control unit, etc.). Oil can be supplied.

The oil pump, which is driven to rotate by the drive pinion shaft on the engine side, is not affected by the differential rotation and the oil discharge amount is stable. Therefore, the capacity of the oil pump can be freely set according to the application. It is possible to

Therefore, in the configuration in which the discharge oil is used for the control pressure, accurate control is possible, and in the configuration in which the forced oil is used, lubrication can be performed effectively.

Further, in the configuration in which the oil pump is arranged on the drive pinion shaft, the differential device is made compact in the axial direction, and the vehicle mountability is improved.

In the differential device according to the second aspect, an oil sump which gives agitating resistance to the differential case or the like is not formed in the differential carrier, and the loss of driving force is reduced, so that the fuel efficiency of the engine is greatly improved.

The third aspect of the present invention provides the first and second aspects.
In addition to obtaining the same effect as the configuration described above, a set of oil pumps that are driven to rotate by the drive pinion shaft sucks up the oil that accumulates in the differential carrier. Therefore, the structure is simple, the number of parts is small, lightweight, compact, and low. It is a cost and the in-vehicle property is improved.

The invention of claim 4 is the invention of claims 1 to 3
The same effect as that of the configuration is obtained.

Further, an oil pump that stabilizes the oil discharge amount and can freely set the capacity according to the application can perform precise yaw moment control, and can sufficiently lubricate a narrow lubricated portion by forced lubrication. , Abrasion, seizure, etc. are prevented, and the durability is greatly improved.

According to the fifth aspect of the present invention, the same effects as those of the fourth aspect are obtained, and each gear of the transmission mechanism is released from the oil stirring resistance, loss of driving force is prevented, and fuel consumption of the engine is increased. improves.

The invention of claim 6 is the invention of claims 1 to 3
The same effect as that of the configuration is obtained.

Further, the power is interrupted at a desired timing by an oil pump that stabilizes the oil discharge amount and can freely set the capacity according to the intended use, so that the vehicle can travel on rough roads, maneuverability and stability. Is greatly improved, and the forced lubrication sufficiently lubricates a narrow lubricated portion, thereby preventing abrasion, seizure and the like, and greatly improving the durability.

The invention of claim 7 is the first to third aspects of the present invention.
The same effect as that of the configuration is obtained.

Further, the differential lock is performed at a desired timing by an oil pump that stabilizes the oil discharge amount and can freely set the capacity according to the application, thereby greatly improving the maneuverability and stability of the vehicle. In addition, the forced lubrication sufficiently lubricates a narrow lubricated portion, prevents abrasion, seizure, etc., and greatly improves durability.

[Brief description of the drawings]

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

FIG. 2 is a sectional view of an oil pump used in the embodiment of FIG.

FIG. 3 is a hydraulic circuit diagram illustrating a configuration of a hydraulic system according to the embodiment of FIG. 1;

FIG. 4 is a block diagram illustrating a configuration of a control system according to the embodiment of FIG. 1;

FIG. 5 is a sectional view of a conventional example.

[Explanation of symbols]

Reference Signs List 1 Differential device 3 Differential carrier 5 Differential carrier tubular portion 7 Differential carrier casing 9 Differential case 15 Ring gear 17 Drive pinion gear 19 Drive pinion shaft 31, 155 Seal 47 that partitions oil storage chamber 157 47 Differential mechanisms 49, 51 Drive shaft (output member) 63 Housing for differential case 9 65 Housing for speed increasing gear set 97 and reduction gear set 99, etc. 97 Speed increasing gear set (speed increasing mechanism) 99 Reduction gear set (speed reducing mechanism) 121, 123 Multi-plate clutch (clutch) 125, 127 Hydraulic actuator 157 Oil storage chamber 158 Oil pump (gear pump) 159 Oil pump (vane pump) 169, 179, 199 Oil flow passages 201, 203, provided outside differential carrier 205 Inside of differential carrier Oil flow path provided in

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3D036 EB14 3D042 AA06 AA07 AB01 CA03 CC02 3J027 FA36 FA37 FB01 GB05 GB10 HA01 HB07 3J063 AA02 AB04 AB53 AC11 BA11 CA05 XD03 XD23 XD32 XD43 XD56 XD72 XE15 XF15

Claims (7)

[Claims] A drive pinion shaft which is rotated by the driving force of an engine, a drive pinion gear which rotates integrally with the drive pinion shaft, a differential case in which a ring gear meshing with the drive pinion gear is fixed, and rotation of the differential case is paired. A differential mechanism for distributing to the wheel side via the output member of the above, and a tubular portion and a large-diameter casing, wherein a drive pinion shaft penetrates the tubular portion and the casing has a differential casing.
A differential carrier for accommodating the oil, and an oil storage chamber formed by partitioning the tubular portion of the differential carrier and the drive pinion shaft with a seal, and an oil storage chamber driven by the drive pinion shaft and connected to the oil storage chamber. An oil pump for supplying and receiving oil, and an oil passage formed in the differential carrier or provided outside the differential carrier to supply oil to a suction port of the oil pump or supply discharge oil of the oil pump to a required portion. A differential device comprising: 2. A drive pinion shaft which is rotated by a driving force of an engine, a drive pinion gear which rotates integrally with the drive pinion shaft, a differential case in which a ring gear meshing with the drive pinion gear is fixed, and rotation of the differential case is paired. A differential mechanism for distributing to the wheel side via the output member of the above, and a tubular portion and a large-diameter casing, wherein a drive pinion shaft penetrates the tubular portion and the casing has a differential casing.
A differential carrier for accommodating the oil, and an oil pump for sucking up the oil accumulated in the casing of the differential carrier. A differential device provided with an oil flow path for supplying oil to a required portion. 3. The invention according to claim 1, wherein the oil pump disposed between the tubular portion of the differential carrier and the drive pinion shaft sucks up the oil accumulated in the casing of the differential carrier. Differential device. 4. The invention according to claim 1, wherein the two output members of the differential mechanism and the differential
And a pair of transmission mechanisms arranged between the output member and one of the output members and the differential case to adjust the torque distribution ratio between the wheels by moving the driving torque. A pair of intermittent clutches and a pair of hydraulic actuators for opening and closing these clutches separately are used, and the discharge pressure of the oil pump is used for one or both of the operating pressure of the hydraulic actuator and forced lubrication. A differential device, characterized in that: 5. The invention according to claim 4, wherein the casing of the differential carrier is divided into a housing chamber for accommodating the transmission mechanism and a housing chamber for accommodating the differential case. A differential device characterized by sucking up oil accumulated in a storage chamber of a mechanism. 6. The invention according to claim 1, wherein the differential case includes an outer case that is rotated by a driving force of the engine, and an inner case that is rotatable inside the outer case. An inner case connected to the differential mechanism and arranged to connect and disconnect the outer case and the inner case, and a hydraulic actuator for opening and closing the clutch. A differential device characterized in that a discharge pressure of an oil pump is used for one or both of an operating pressure of a hydraulic actuator and forced lubrication. 7. A clutch according to any one of claims 1 to 3, wherein the clutch connects and disconnects any two of the differential rotating members constituting the differential mechanism. And a hydraulic actuator for opening and closing the hydraulic pump, and utilizing a discharge pressure of an oil pump for one or both of an operating pressure of the hydraulic actuator and forced lubrication.