JPH0828654A - Differential gear - Google Patents

Abstract

PURPOSE:To provide a differential gear capable of ensuring differential limiting effect in simple structure. CONSTITUTION:When a gear case 1 is rotated around the shaft center, this torque is transmitted to a gear disk 3 and a side gear 5 through each pinion gear 8. At this moment, when there is a difference in rotation between the gear disk 3 and side gear 5, this difference is permitted by the rotation of each pinion gear 8, achieving the differential motion between the gear disk 3 and side gear 5. When there is a difference in torque between the gear disk 3 and side gear 5, between the gear disk 3 and an output disk 4, one of the two transmits its torque to the other, and since grooves 3a and 4a contact with each ball arranged between the gear disk 3 and the output disk 4 at a specified inclined angle to the direction in which torque works, axial reaction force is produced between the gear disk 3 and the output disk 4 and becomes resistance, limiting the differential motion.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a differential device mainly used in a driving force transmission system of an automobile, and more particularly to a differential device having a differential limiting function.

[0002]

2. Description of the Related Art Conventionally, a differential device used in a driving force transmission system of an automobile is a device which allows a difference in rotation between left and right driving wheels when traveling on a curve or a difference in rotation between front and rear driving wheels in a four-wheel drive vehicle. However, if only one driving wheel rides on a road surface with extremely low friction coefficient such as snow or sand, that wheel will spin and lose the entire driving force, and you will not be able to escape from the place. It was easy. Further, even when the load on the inner wheel is extremely reduced due to centrifugal force when traveling on a curve at a high speed, there is a drawback that the wheel idles and the driving force for traveling at a high speed on the curve is easily lost. .

In order to make up for such drawbacks, there is a conventional differential device having a differential limiting function, which includes a general differential transmission mechanism composed of a pinion gear and a viscous cup. It is known that a rotation speed sensitive type differential limiting mechanism including a ring is added. The viscous coupling is a kind of viscous clutch that transmits the torque by utilizing the shear resistance of viscous fluid (silicon oil etc.), so that a smooth differential limiting effect can be obtained according to the rotation difference. You can

Further, as a differential device having a differential limiting function, a torque-sensitive type device by a combination of worm gears is also known, as described in, for example, Japanese Patent Application Laid-Open No. 4-271926. In this type, a pair of screw-shaped worms that can rotate independently of each other on the same axis are meshed with a plurality of worm wheels that have a rotation axis that is at a right angle to the worm wheels. It uses the unique characteristic of a worm gear that it rotates smoothly, but on the contrary, it is difficult to rotate when trying to rotate it from the worm wheel side. It is characterized by being able to be.

[0005]

However, in a rotational speed sensitive differential device with a differential limiting mechanism represented by a viscous coupling, since the torque transmissibility depends on the viscosity of the fluid, the temperature changes. Then the viscosity of the fluid changes,
There is a drawback that a stable differential limiting effect cannot always be obtained. In addition, in this type, there is a time lag between the occurrence of the rotation difference and the time when the differential limitation is performed, so that there is a problem that it is not possible to instantaneously respond to a change in the running operation. On the other hand, in the differential device using the worm gear, the differential limiting effect is stable because the differential limiting is mechanically performed, but on the other hand, the number of parts is large and the structure is complicated, Extremely high precision is required for assembly. Therefore, there is a problem that the entire device becomes larger than the allowable torque and the manufacturing cost becomes high.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a differential device which can obtain a positive differential limiting effect with a simple structure.

[0007]

In order to achieve the above object, the present invention provides, in claim 1, an input side rotating body which rotates about an axis by a driving force input from the outside, and an input side rotating body. Equipped with a pair of output side rotating bodies arranged on the rotating shaft, and a differential transmission mechanism that transmits the rotational force of the input side rotating body to each output side rotating body while allowing the rotation difference between the output side rotating bodies. In the differential device described above, at least one of the output side rotating bodies is provided with first and second rotating bodies that face each other in the axial direction,
It is composed of a large number of rolling elements interposed between the first and second rotating bodies, and a large number of grooves engaging with the respective rolling elements are provided on the facing surfaces of the first and second rotating bodies. Are provided so as to be in contact with each other at a predetermined inclination angle with respect to the direction of action of.

According to a second aspect of the present invention, in the differential device according to the first aspect, a large number of holes for holding the respective rolling elements are provided in one of the first and second rotating bodies or in the first and second rotating bodies. The same number of other members interposed therebetween are provided at positions different in distance from the rotation axis of the input side rotating body, and the rolling elements are held in holes at arbitrary positions.

According to a third aspect of the present invention, in the differential device according to the first aspect, a plurality of grooves having different inclination angles with respect to the respective rolling elements are alternately provided in the same number, and each rolling element has an arbitrary inclination angle. It is engaged in the groove.

Further, according to a fourth aspect of the present invention, an input side rotating body that rotates about an axis by a driving force input from the outside, and a pair of output side rotating bodies that are arranged on the rotating shaft of the input side rotating body, In a differential device including a differential transmission mechanism that transmits the rotational force of the input side rotating body to each output side rotating body while allowing the rotation difference of each output side rotating body, at least one of the output side rotating bodies is The first and second rotating bodies are axially opposed to each other, and a large number of recesses and protrusions engaging with each other are formed on the opposing surfaces of the first and second rotating bodies with respect to the directions in which the rotational forces act on each other. It is provided so as to contact at a predetermined inclination angle.

According to a fifth aspect of the present invention, in the differential device according to the first, second, third, or fourth aspect, the first and second rotating bodies are provided with an urging means for applying an axial preload.

[0012]

According to the differential device of the first aspect, when the input side rotating body rotates about the axis by the driving force from the outside, this rotating force is transmitted to each output side rotating body through the differential transmission mechanism. To be done. Here, when a rotation difference occurs in each output side rotating body, this rotation difference is allowed by the differential transmission mechanism, and a differential of each output side rotating body is achieved. Further, when torque fluctuation occurs between the output side rotating bodies, the first side forming the output side rotating body
One of the rotating body and the second rotating body tries to transmit the rotating force to the other, and the groove is in contact with each rolling element between the first and second rotating bodies at a predetermined inclination angle with respect to the direction in which the rotating force acts. Therefore, an axial reaction force is generated between the first rotating body and the second rotating body, which acts as resistance and limits the differential.

According to the differential device of the second aspect, in addition to the action of the first aspect, when the distance from the rotation axis of the input side rotating body to each rolling element is different, the reaction force at the time of differential limitation is generated. Since the size is changed, by holding each rolling element in an arbitrary hole, a differential limiting effect having different effects can be selectively obtained.

According to the differential device of the third aspect, in addition to the action of the first aspect, when the inclination angle of the groove contacting each rolling element is different, the magnitude of the reaction force at the time of the differential limitation is changed. By engaging each rolling element with an arbitrary groove, a differential limiting effect having different effects can be selectively obtained.

According to the differential device of the fourth aspect, when the input side rotating body is rotated around the axis by the driving force from the outside, this rotating force is transmitted to each output side rotating body through the differential transmission mechanism. Be transmitted to. Here, when a rotation difference occurs between the output side rotating bodies, this rotation difference is allowed by the differential transmission mechanism,
The differential of each output side rotator is achieved. Further, when a torque fluctuation occurs between the output side rotating bodies, one of the first rotating body and the second rotating body forming the output side rotating body tries to transmit the rotational force to the other, and the first and second rotating bodies Since the concave portions and the convex portions of the rotating body are in contact with each other at a predetermined inclination angle with respect to the direction in which the rotating force acts, an axial reaction force is generated between the first rotating body and the second rotating body, This becomes a resistance and limits the differential.

According to the differential device of the fifth aspect, in addition to the action of the first, second, third or fourth aspect, a preload of a predetermined strength is applied to the first and second rotating bodies in the axial direction. Therefore, the differential limiting effect is increased in addition to the reaction force between the first rotating body and the second rotating body.

[0017]

Embodiment 1 FIGS. 1 to 5 show a first embodiment of the present invention. FIG. 1 is a side sectional view of a differential device, and FIG.
-A line direction arrow sectional view, FIG. 3 is the exploded perspective view.

This differential device includes a gear case 1 forming an input side rotating body, a gear case cover 2 closing one end of the gear case 1, a gear disk 3 forming a first rotating body of one output side rotating body, and one side. The output disc 4 forming the second rotating body of the output side rotating body, the side gear 5 forming the other output side rotating body, the ball holder 6 arranged between the gear disc 3 and the output disk 4, and the ball holder 6 It is composed of a large number of balls 7 that are rolling elements held by and a total of four pinion gears 8 that transmit the rotational force of the gear case 1 to the gear disc 3 and the side gears 5.

The gear case 1 has a cylindrical shape with one end opened, and a bearing 1a for supporting the side gear 5 is provided in the center thereof. A flange 1b is provided around the gear case 1.
And a large number of holes 1c for inserting bolts are formed in the flange 1b. Further, a total of four grooves 1d extending in the axial direction are provided on the inner peripheral surface of the gear case 1, and each groove 1d
The pinion gear 8 is fixed to.

The gear case cover 2 is formed in a disc shape,
A bearing 2a for supporting the output disk 4 is provided in the center thereof. A flange 2b is provided around the gear case cover 2, and a large number of holes 2c for inserting bolts are provided in the flange 2b. That is, the gear case cover 2
Is assembled to the gear case 1 by a bolt 2d that fastens each flange 1b, 2b.

The gear disk 3 has one end surface formed flat, and this surface is opposed to one end surface of the output disk 4. A large number of grooves 3a extending linearly are formed on one end surface of the gear disk 3 at a predetermined angle in the radial direction, that is, at an angle inclined with respect to the direction of the rotational force acting about the axis of the gear case 1.
Are provided at equal intervals in the circumferential direction, and the bevel gear 3 is provided on the other end face.
b is formed. A thrust washer 3c is provided between the other end surface of the gear disc 3 and the step in the gear case 1.
Is interposed.

The output disk 4 is formed with one end surface flat, and this surface is opposed to one end surface of the gear disk 3. Similar to the gear disk 3, a large number of grooves 4a extending linearly at a predetermined angle in the radial direction are provided at one end face of the output disk 4 at equal intervals in the circumferential direction. The grooves 4a and the grooves 3a of the gear disk 3 are provided. And are formed so as to be inclined in opposite directions when they are stacked in the axial direction. The other end of the output disc 4 is connected to the drive shaft 9 on the wheel side by a connecting portion 4
b is provided, and the connecting portion 4b is inserted into the bearing 2a of the gear case cover 2. Further, a thrust washer 4c is interposed between the other end surface of the output disk 4 and the inner surface of the gear case cover 2.

The side gear 5 has one end rotatably supported by the bearing 1a of the gear case 1, and the bevel gear 5a at the other end.
Are formed. Further, the side gear 5 is provided with a connecting portion 5b with the drive shaft 9 on the wheel side. Further, a washer 5 is provided between the side gear 5 and the gear case 1.
c is interposed.

The ball holder 6 is formed in a disk shape, and its both end surfaces are opposed to the gear disk 3 and the output disk 4. The ball holder 6 is provided with a large number of holes 6a, 6b penetrating in the axial direction on two different circles at equal intervals.

Each ball 7 has a hole 6 inside the ball holder 6.
It is held by a, a part of which projects toward the facing surface side of the gear disc 3 and the output disc 4 and is rotatably engaged with the respective grooves 3a, 4a.

The pinion gears 8 are rotatably supported by pinion shafts 8a having support shafts which are orthogonal to each other, and bevel gears 3b of the gear disc 3 and the side gears 5, respectively.
It is meshed with 5a. The pinion shaft 8a is fixed to each groove 1d of the gear case 1 via a washer 8b, and rotates together with the gear case 1.
That is, each pinion gear 8 and the pinion shaft 8a constitute a differential transmission mechanism, and the rotation of each pinion gear 8 causes the gear disc 3 and the side gear 5 to rotate in opposite directions.

In the differential device configured as described above, a ring gear (not shown) for transmitting the driving force from the engine is attached to the flange 1b of the gear case 1, and the entire device rotates about the axis of the gear case 1. It is supposed to do.

Here, the operation of the differential device is carried out in the case where there is no rotation difference between the drive shafts 9 and in the case where there is a rotation difference between the drive shafts 9, and only one drive shaft 9 idles. Each of the cases of falling into an easy state will be described.

First, when there is no rotation difference between the drive shafts 9 such as when the vehicle is traveling straight on a road surface having sufficient frictional force, when the gear case 1 is rotated by the driving force, the pinion shaft is integrated with the gear case 1. 8a rotates, and this rotational force is transmitted to the gear disc 3 and the side gear 5 via each pinion gear 8. In this case, since there is no difference in rotation between the drive shafts 9, the pinion gears 8 do not rotate. Further, the rotational force transmitted to the gear disc 3 is transmitted from each groove 3a to each groove 4a of the output disc 4 via each ball 7.

Next, when a rotational difference occurs between the drive shafts 9 while the torque is evenly transmitted to the drive wheels, such as when the vehicle is turning on a road surface having sufficient frictional force, the pinion gears 8 are caused to rotate. The rotation of the gear disc 3 and the side gear 5 reversely rotate to achieve a differential.

When torque fluctuations occur between the drive shafts 9 such as when one driving wheel loses friction with the road surface, one of the gear disc 3 and the output disc 4 rotates to the other. In order to transmit the force, a reaction force is generated between each ball 7 and each groove 3a, 4a, whereby the gear disc 3 and the output disc 4 are pressed against each thrust washer 3c, 4c, which causes friction resistance. The differential is limited.

Here, the principle of the differential limiting effect will be described in detail with reference to FIGS. 4 and 5. First, FIG. 4 is a view of the ball 7 and the groove 3a (4a) viewed from the radial direction of the differential device. As shown in the figure, the center of the ball 7 is a gear disk around the main shaft (rotational shaft of the gear case 1). The rotational force A applied from one of 3 and the output disk 4 acts. Here, A≈A ′ (1) At this time, a force C perpendicular to the contact surface with the ball 7 is generated in the groove 3a (4a), and the component force is a rotation about the rotation axis of the gear case 1. A'which is parallel to the force A and B which is perpendicular to A '. Since C is perpendicular to the contact surface with the ball 7, it is located on a line segment passing through the center of the ball 7, and the angle between A'and C is α, the size of C is C = A ' It is represented by × 1 / cosα (2).

Next, as shown in FIG. 5, the balls 7 and the grooves 3 are formed.
When a and 4a are viewed from the direction orthogonal to the rotation axis of the gear case 1, the vertical reaction force actually acting on the contact surface between the grooves 3a and 4a and the ball 7 is D, and the component force thereof is the gear case. A force E parallel to the rotation axis of 1 and a force C perpendicular to E. Since the ball 7 obliquely contacts the grooves 3a and 4a, C
And E act as forces due to rolling friction and sliding friction,
E is called thrust force. Since D is perpendicular to the contact surface with the ball 7, it is located on the line segment passing through the center of the ball 7,
When the angle formed by C and C is β, the magnitude of the surface pressure D is expressed by D = C × 1 / cosβ (3) Further, the magnitude of the thrust force E is expressed by E = C × tan β (4) From the equations (1), (2) and (3), the reaction force D is as follows. D = A × 1 / cosα × 1 / cosβ (5) From the equations (1) and (2), C is C = A × 1 / cosα (6) and the thrust force E is the equation (1). From the equations (2) and (4), E = A × 1 / cosα × tanβ (7)

That is, the reaction force D that the ball 7 receives from each groove 3a, 4a is divided into C and E components, which act as forces due to rolling friction and sliding friction, and particularly thrust force E causes the gear disc 3 and The output disc 4 is pressed against the thrust washers 3c and 4c to obtain a differential limiting effect. At that time, the ball 7 and the grooves 3a,
By setting the contact angles α and β with 4a arbitrarily, it is possible to obtain the differential limiting effect as required.

In the above embodiment, each ball 7 is held in the hole 6a inside the ball holder 6, but
It is also possible to put this into the outer hole 6b and engage with the respective grooves 3a, 4a. That is, the inner hole 6a and the outer hole 6
Since the distance from the rotation axis of the gear case 1 to each ball 7 is different from that of b, the magnitude of the reaction force at the time of differential limitation is changed, and thus, the differential limiting effect having different effects can be selectively obtained. it can.

As described above, according to the differential device of this embodiment, the groove 3 provided in the gear disc 3 and the output disc 4 is provided.
a, 4a and a large number of balls 7 which are rotatably engaged with the balls
When a rotational force is applied from one of the gear disc 3 and the output disc 4 due to the engagement with, the balls 7 generate an axial thrust force by the reaction force received from the contact surface with the grooves 3a, 4a, Since the differential force is limited by the frictional force between the gear disc 3 and the output disc 4 and the thrust washers 3c, 4c, it is not necessary to add a special mechanism for obtaining the differential limiting effect, and the operation is reliable. A torque-sensitive differential limiting effect can be obtained. Further, by setting the contact angle between each ball 7 and each groove 3a, 4a arbitrarily, it is possible to obtain a differential limiting effect as required.

[0037]

[Embodiment 2] FIGS. 6 to 8 show a second embodiment of the present invention. FIG. 6 is a side sectional view of a differential device, and FIG.
-A line direction arrow sectional view, FIG. 8 is the exploded perspective view.

This differential device includes a gear case 10 forming an input side rotating body, a gear case cover 11 closing one end of the gear case 10, a pair of gear disks 12 forming a first rotating body of the output side rotating body, and an output. A pair of output disks 13 forming the second rotating body of the side rotating body, balls 14 forming a large number of rolling elements held by each gear disk 12, and a pair of multi-plates that give resistance to the rotation of each output disk 13. The clutch 15, the inner case 16 accommodated in the gear case 10, and the rotational force of the gear case 10 are transferred to the gear disks 12
And a total of four pinion gears 17 that are transmitted to the.

The gear case 10 has a cylindrical shape with one end open, and a bearing 10a for supporting one output disk 13 is provided in the center thereof. A flange 10b is provided around the gear case 10, and a large number of holes 10c for inserting bolts are provided in the flange 10b. Further, a large number of grooves 10 extending in the axial direction are formed on the inner peripheral surface of the gear case 10.
d is provided, and the inner case 17 is fixed to each groove 10d. Further, on the inner surface of the gear case 10, a large number of grooves 10e for fixing one multi-plate clutch 15 are provided at intervals in the circumferential direction.

The gear case cover 11 is formed in a disk shape, and a bearing 11a for supporting the other output disk 13 is provided in the center thereof. A flange 11b is provided around the gear case cover 11, and a large number of holes 11c for inserting bolts are provided in the flange 11b. That is, the gear case cover 11 includes the flanges 10b and 11b.
It is assembled to the gear case 10 by a bolt 11d that fastens. Further, on the inner surface of the gear case cover 11, a large number of grooves 11e for fixing the other multi-plate clutch are provided at intervals in the circumferential direction.

Each gear disk 12 is formed with one end surface flat, and this surface is opposed to one end surface of each output disk 13. A large number of holes 12 are formed on one end surface of each gear disk 12.
a are provided at equal intervals on the same circumference, and a bevel gear 12b is formed on the other end surface.

One end face of each output disc 13 is formed flat, and this face is opposed to one end face of each gear disc 12. A large number of grooves 13a, 13b extending linearly are formed on one end surface of each output disk 13 at different angles in the radial direction, that is, at angles inclined with respect to the direction of the rotational force acting about the axis of the gear case 10. Are provided alternately in the circumferential direction, and these grooves 13a and 13b are formed in the respective output disks 13
When they are stacked in the axial direction, they are formed so as to incline in mutually opposite directions. Further, a connecting portion 13c with the drive shaft 9 on the wheel side is provided at the other end of each output disk 13, and each connecting portion 13c is inserted into the bearings 10a, 11a of the gear case 10 and the gear case cover 11, respectively. Further, on the other end surface of each output disk 13, a large number of grooves 13d for fixing the multi-plate clutch 15 are provided at intervals in the circumferential direction.

Each ball 14 has a hole 1 in each gear disk 12.
2a, a part of which is projected to the side of each output disk 13 and is rotatably engaged with one groove 13a.

Each multi-plate clutch 15 is composed of first and second clutch plates 15a and 15b formed in an annular shape, and two clutch plates 15a and 15b are alternately stacked. The first clutch plate 15a has a large number of protrusions 15c on its outer periphery.
The projection 15c of one multi-plate clutch 15 is engaged with the groove 10e of the gear case 10, and the projection 15c of the other multi-plate clutch 15 is engaged with the groove 11e of the gear case cover 11. The second clutch plate 15b has a large number of protrusions 15d on its inner circumference, and the protrusions 15d are engaged with the grooves 13d of each output disk 13. That is, in each multi-plate clutch 15, the first clutch plate 15a is fixed to the gear case 10 or the gear case cover 11, and the second clutch plate 15b rotates together with the output discs 13, so that the clutch plates 15a and 15b are connected to each other. Friction resistance is generated.

The inner case 16 is formed in a tubular shape, and a large number of ridges 16a provided on the outer peripheral surface thereof are provided in the gear case 10.
It is fixed to the gear case 10 by engaging with the respective grooves 10d. Further, a large number of grooves 16b for holding each pinion gear 16 are provided on the inner peripheral surface of the inner case 16 at intervals in the circumferential direction.

Each pinion gear 17 is rotatably supported by a pinion shaft 17a having support shafts orthogonal to each other, and is meshed with a bevel gear 12b of each gear disk 12. The pinion shaft 17a is a washer 1
It is fixed to each groove 16b of the inner case 16 via the inner case 7b so as to rotate integrally with the gear case 10 via the inner case 16. That is, each pinion gear 1
7 and the pinion shaft 17a constitute a differential transmission mechanism, and the rotation of each pinion gear 17 causes the respective gear disks 12 to rotate in mutually opposite directions.

In the differential device configured as described above, the ring gear (not shown) for transmitting the driving force from the engine is attached to the flange 10b of the gear case 10, and the entire device rotates about the axis of the gear case 10. It is supposed to do.

Here, the operation of the above-mentioned differential device is carried out when no rotation difference occurs in each drive shaft 9, when there is a rotation difference in each drive shaft 9, and only one drive shaft 9 idles. Each of the cases of falling into an easy state will be described. The principle of the differential limiting effect is the same as that of the first embodiment, and the description thereof is omitted.

First, when there is no difference in rotation between the drive shafts 9 such as when the vehicle is traveling straight on a road surface having sufficient frictional force, when the gear case 10 is rotated by the driving force, the pinion is integrated with the gear case 10. Shaft 17
a rotates, and this rotational force is transmitted to each gear disk 12 via each pinion gear 17. In this case, since there is no rotation difference between the drive shafts 9, the pinion gears 17 do not rotate. Further, the rotational force transmitted to each gear disc 12 is transmitted to the groove 13 a of each output disc 13 via each ball 14.

Next, when there is a rotation difference between the drive shafts 9 while the torque is evenly transmitted to the drive wheels, such as when the vehicle is turning on a road surface having sufficient frictional force, the pinion gears 17 are caused to rotate. The rotation of the gear discs 12 causes the gear discs 12 to rotate in the reverse direction to achieve the differential.

Further, when torque fluctuations occur between the drive shafts 9 such as when one of the drive wheels loses frictional force with the road surface, one of the gear disks 12 transmits the rotational force to the other. Each ball 14 and groove 13
A reaction force is generated between the gear disc 12a and
And each output disk 13 presses each other plate clutch 15, and the friction resistance of each clutch plate 15a, 15b increases, and the differential is limited. In this case, each output disk 13 is given a preload of a predetermined strength by each other plate clutch 15 to increase the differential limiting effect.

In the above embodiment, each ball 14 is engaged with one groove 13a of each output disk 13, but it is also possible to engage each ball 14 with the other groove 13b having a different angle. is there. That is, each ball 14 is attached to each groove 13
If the angles of contact with a and 13b are different, each other plate clutch 1
Since the magnitude of the force that presses 5, that is, the thrust force, changes, a differential limiting effect having different effects can be selectively obtained.

[0053]

[Third Embodiment] FIGS. 9 to 11 show a third embodiment of the present invention. FIG. 9 is a side sectional view of a differential gear, and FIG. 10 is a sectional view taken along the line AA of FIG. 11 is an exploded perspective view thereof.

This differential device includes a gear case 20 forming an input side rotating body, a gear case cover 21 closing one end of the gear case 20, a gear disk 22 forming a first rotating body of one output side rotating body, and one side. Of the output side rotating body, the output disk 23 forming the second rotating body, the other output side rotating body forming the side gear 24, the roller holder 25 arranged between the gear disk 22 and the output disk 23, and the roller holder 25. Roller 26, which is formed by a number of rolling elements
And a large number of springs 27 for preloading the gear disc 22 and the output disc 23 in the axial direction, and the gear case 2
It is composed of a total of four pinion gears 28 that transmit a rotational force of 0 to the gear disc 22 and the side gear 24.

The gear case 20 has a cylindrical shape with one end open, and the bearing 20 supporting the side gear 24 is provided in the center thereof.
a is provided. A flange 20b is provided around the gear case 20, and a large number of holes 20c for inserting bolts are provided in the flange 20b. Further, a total of four grooves 20d extending in the axial direction are provided on the inner peripheral surface of the gear case 20, and the pinion gear 28 is fixed to each groove 20d.

The gear case cover 21 is formed in a disk shape, and the bearing 2 for supporting the output disk 23 is provided in the center thereof.
1a is provided. A flange 21b is provided around the gear case cover 21, and a large number of holes 21c for inserting bolts are provided in the flange 21b. That is, the gear case cover 21 is attached to the gear case 20 by the bolts 21d that fasten the flanges 20b and 21b.

One end face of the gear disc 22 is formed flat, and this face is opposed to one end face of the output disc 23. On one end surface of the gear disk 22, a total of three linear grooves 22a which are orthogonal to the radial direction, that is, which are inclined with respect to the direction of the rotational force acting around the axis of the gear case 20, form triangular shapes. And a bevel gear 22b is formed on the other end surface. A thrust washer 22c is interposed between the other end surface of the gear disc 22 and the step inside the gear case 20.

The output disk 23 is formed with one end surface flat, and this surface is opposed to one end surface of the gear disk 22. Similar to the gear disc 22, a total of three linear grooves 23a orthogonal to the radial direction are provided on one end surface of the output disc 23 so as to form mutually triangular shapes. Further, a connecting portion 23b with the drive shaft 9 on the wheel side is provided at the other end of the output disk 23, and the connecting portion 23b is inserted into the bearing 21a of the gear case cover 21. Further, a thrust washer 23c is interposed between the other end surface of the output disk 23 and the inner surface of the gear case cover 21.

One end of the side gear 24 is rotatably supported by the bearing 20a of the gear case 20, and a bevel gear 24a is formed at the other end. Further, the side gear 24 is provided with a connecting portion 24b with the drive shaft 9 on the wheel side. Further, a washer 24c is interposed between the side gear 24 and the gear case 20.

The roller holder 25 is formed in a disk shape, and its both end surfaces are opposed to the gear disk 22 and the output disk 23. The roller holder 25 is provided with a large number of elliptical holes 25a and a large number of circular holes 25b penetrating in the axial direction.

Each roller 26 is held in an elliptical hole 25a of the roller holder 25, and a part of the roller 26 is projected toward the facing surface side of the gear disk 22 and the output disk 23 to form each groove 22.
Two in total are engaged with a and 23a.

Each spring 27 is held in the circular hole 25b of the roller holder 25, and is interposed between the gear disk 22 and the output disk 23 in a compressed state.

Each pinion gear 28 is rotatably supported by a pinion shaft 28a having support shafts orthogonal to each other, and meshed with bevel gears 22b and 24a of a gear disk 22 and a side gear 24, respectively. The pinion shaft 28a is attached to the gear case 20 via the washer 28b.
It is fixed in each groove 20d and rotates integrally with the gear case 20. That is, each pinion gear 28 and the pinion shaft 28a constitute a differential transmission mechanism, and the rotation of each pinion gear 28 causes the gear disc 22 to rotate.
The side gear 24 and the side gear 24 rotate in opposite directions.

In the differential device configured as described above, the ring gear (not shown) for transmitting the driving force from the engine is attached to the flange 20b of the gear case 20, and the entire device rotates about the axis of the gear case 20. It is supposed to do.

Here, the operation of the above-mentioned differential device is performed when no rotation difference occurs in each drive shaft 9, when there is a rotation difference in each drive shaft 9, and only one drive shaft 9 idles. Each of the cases of falling into an easy state will be described. The principle of the differential limiting effect is the same as that of the first embodiment, and the description thereof is omitted.

First, when there is no rotation difference between the drive shafts 9 such as when the vehicle is traveling straight on a road surface having sufficient frictional force, when the gear case 20 is rotated by the driving force, the pinion shaft 28a is integrated with the gear case 20. Rotates, and this rotational force is transmitted to the gear disc 22 and the side gear 24 via each pinion gear 28. In this case, since there is no rotational difference between the drive shafts 9, the pinion gears 28 do not rotate. Further, the rotational force transmitted to the gear disc 22 is transmitted from the groove 22a to each roller 2
It is transmitted to the groove 23 a of the output disk 23 via 6.

Next, when a rotation difference occurs in each drive shaft 9 while the torque is evenly transmitted to each drive wheel, such as when the vehicle is turning on a road surface having sufficient frictional force, each pinion gear 28 is caused to rotate. The rotation of the gear disk 22 and the side gear 24 reversely rotate to achieve the differential.

Further, when torque fluctuation occurs between the drive shafts 9 such as when one driving wheel loses friction with the road surface, the gear disc 22 and the output disc 2
In FIG. 3, one tries to transmit the rotational force to the other, so that a reaction force is generated between each roller 26 and each groove 22a, 23a, which causes the gear disc 22 and the output disc 23 to the thrust washers 22c, 23c. It is pressed, and this becomes frictional resistance, limiting the differential. In this case, each spring 27 is attached to the gear disc 22 and the output disc 23.
Due to this, a preload of a predetermined strength is applied in the direction of pressing the thrust washers 22c, 23c, and the differential limiting effect is increased.

[0069]

Fourth Embodiment FIGS. 12 to 16 show a fourth embodiment of the present invention. FIG. 12 is a side sectional view of a differential gear, and FIG.
16 is a partially enlarged cross-sectional view thereof, FIG. 14 is a cross-sectional view taken along the line AA, and FIG. 15 is a cross-sectional view taken along the line BB.
FIG. 4 is an exploded perspective view thereof.

This differential device includes a gear case 30 forming an input side rotating body, a gear case cover 31 closing one end of the gear case 30, a gear disk 32 forming a first rotating body of one output side rotating body, and one side. An output disc 33 forming a second rotating body of the output side rotating body, a side gear 34 forming the other output side rotating body, and a total of four pinion gears 35 for transmitting the rotational force of the gear case 30 to the gear disc 32 and the side gear 34. It consists of

The gear case 30 has a cylindrical shape with one end open, and the bearing 30 for supporting the side gear 34 is provided in the center thereof.
a is provided. A flange 30b is provided around the gear case 30, and a large number of holes 30c for inserting bolts are provided in the flange 30b. Further, a total of four grooves 30d extending in the axial direction are provided on the inner peripheral surface of the gear case 30, and the pinion gear 35 is fixed to each groove 30d.

The gear case cover 31 is formed in a disk shape, and the bearing 3 for supporting the output disk 33 is provided in the center thereof.
1a is provided. A flange 31b is provided around the gear case cover 31, and a large number of holes 31c for inserting bolts are provided in the flange 31b. That is, the gear case cover 31 is assembled to the gear case 30 by the bolt 31d that fastens the flanges 30b and 31b.

One end face of the gear disc 32 is opposed to one end face of the output disc 33, and a large number of recesses 32a extending in the radial direction are provided on this face at equal intervals in the circumferential direction. As shown in FIG. 13, each recess 32a is formed of a flat bottom surface and slopes on both sides inclined at a predetermined angle. Further, a bevel gear 32b is provided on the other end surface of the gear disc 32.
Is formed, and a thrust washer 32c is interposed between this surface and the step in the gear case 30.

One end surface of the output disk 33 is opposed to one end surface of the gear disk 32, and a large number of radially extending projections 33a are provided on this surface at equal intervals in the circumferential direction. As shown in FIG. 13, each of the convex portions 33a is formed of a flat top portion and inclined surfaces on both sides inclined at a predetermined angle, and each inclined surface is slightly bulged outward. That is, the output disk 3
The respective convex portions 33a of No. 3 and the respective concave portions 32a of the gear disc 32 are engaged with each other, and the slopes thereof are in contact with each other. Further, the other end of the output disc 33 is provided with a connecting portion 33b with the drive shaft 9 on the wheel side.
3b is inserted in the bearing 31a of the gear case cover 31. Further, a thrust washer 33c is interposed between the other end surface of the output disk 33 and the inner surface of the gear case cover 31.

One end of the side gear 34 is rotatably supported by the bearing 30a of the gear case 30, and a bevel gear 34a is formed at the other end. Further, the side gear 34 is provided with a connecting portion 34b with the drive shaft 9 on the wheel side. Further, a washer 34c is interposed between the side gear 34 and the gear case 30.

Each of the pinion gears 35 is rotatably supported by a pinion shaft 35a having support shafts orthogonal to each other, and meshed with bevel gears 32b and 34a of a gear disc 32 and a side gear 34, respectively. The pinion shaft 35a is attached to the gear case 30 via the washer 35b.
It is fixed in each groove 30d and rotates together with the gear case 30. That is, each pinion gear 35 and the pinion shaft 35a constitute a differential transmission mechanism, and the rotation of each pinion gear 35 causes the gear disc 32 to rotate.
The side gear 34 and the side gear 34 rotate in opposite directions.

In the differential device configured as described above, the ring gear (not shown) for transmitting the driving force from the engine is attached to the flange 30b of the gear case 30, and the entire device rotates about the axis of the gear case 30. It is supposed to do.

Here, the operation of the above-mentioned differential device is carried out in the case where there is no rotation difference between the drive shafts 9 and in the case where there is a rotation difference between the drive shafts 9, and only one drive shaft 9 is idling. Each of the cases of falling into an easy state will be described. The principle of the differential limiting effect is the same as that of the first embodiment, and the description thereof is omitted.

First, when there is no rotational difference between the drive shafts 9 such as when the vehicle is traveling straight on a road surface having sufficient frictional force, when the gear case 30 is rotated by the driving force, the pinion shaft 35a is integrated with the gear case 30. Rotates, and this rotational force is transmitted to the gear disc 32 and the side gear 34 via each pinion gear 35. In this case, since there is no rotation difference between the drive shafts 9, the pinion gears 35 do not rotate. Further, the rotational force transmitted to the gear disc 32 is transmitted from each concave portion 32a to each convex portion 33a of the output disc 33.

Next, when the vehicle makes a turn on a road surface having sufficient frictional force, and when a difference in rotation occurs between the drive shafts 9 while the torque is evenly transmitted to the drive wheels, the pinion gears 35 are caused to rotate. The rotation is performed and the gear disc 32 and the side gear 34 are rotated in the reverse direction to achieve the differential.

Further, when torque fluctuation occurs between the drive shafts 9 such as when one driving wheel loses friction with the road surface, the gear disc 32 and the output disc 3
In 3, the one tries to transmit the rotational force to the other, so that a reaction force is generated between each concave portion 32a and each convex portion 33a, whereby the gear disc 32 and the output disc 33 are pressed against the thrust washers 32c, 33c. This causes frictional resistance and limits the differential. In this case, each recess 32a
Also, the gentler the slope of each convex portion 33a, the greater the differential limiting effect.

[0082]

[Fifth Embodiment] FIGS. 17 to 20 show a fifth embodiment of the present invention. FIG. 17 is a side sectional view of a differential gear device, and FIG.
Is a sectional view taken along the line AA of the arrow, FIG. 19 is a sectional view taken along the line BB of the arrow, and FIG. 20 is an exploded perspective view thereof.

This differential device includes a gear case 40 forming an input side rotating body, a gear case cover 41 closing one end of the gear case 40, a pair of gear disks 42 forming a first rotating body of the output side rotating body, and an output. A pair of output disks 43 forming the second rotating body of the side rotating body, each gear disk 42 and a pair of springs 44 for applying an axial preload to each output disk 43, and the rotational force of the gear case 40 is applied to each gear disk 42. And a total of four pinion gears 45 that are transmitted to the.

The gear case 40 has a cylindrical shape with one end opened, and a bearing 40a for supporting one output disk 43 is provided in the center thereof. A flange 40b is provided around the gear case 40, and a large number of bolt insertion holes 40c are provided in the flange 40b. Further, a large number of grooves 40 extending in the axial direction are formed on the inner peripheral surface of the gear case 40.
d is provided, and each pinion gear 45 is held in each groove 40d.

The gear case cover 41 is formed in a disk shape, and a bearing 41a for supporting the other output disk 43 is provided in the center thereof. A flange 41b is provided around the gear case cover 41, and a large number of holes 41c for inserting bolts are provided in the flange 41b. That is, the gear case cover 41 includes the flanges 40b and 41b.
It is assembled to the gear case 40 by a bolt 41d that fastens.

One end face of each gear disc 42 is opposed to one end face of each output disc 43, and a large number of recesses 42a extending in the radial direction are provided on this face at equal intervals in the circumferential direction. Similar to the fourth embodiment, each recess 42a is formed of a flat bottom surface and slopes on both sides inclined at a predetermined angle. A bevel gear 42b is formed on the other end surface of each gear disc 42.

One end face of each output disc 43 is opposed to one end face of each gear disc 42, and a large number of convex portions 43a extending in the radial direction are provided on this face at equal intervals in the circumferential direction. Similar to the fourth embodiment, each convex portion 43a is formed of a flat top portion and slopes on both sides inclined at a predetermined angle. That is, each convex portion 43a of each output disk 43
And the recesses 42a of the gear discs 42 are engaged with each other, and the slopes are in contact with each other. Further, a connecting portion 43b with the drive shaft 9 on the wheel side is provided at the other end of each output disk 43, and the connecting portion 43b is inserted into the bearing 41a of the gear case cover 41. Further, the other end surface of the output disk 43 and the gear case cover 41
A thrust washer 43c is interposed between the inner surface and the inner surface of the.

Each spring 44 is wound around the central portion of each gear disc 42, and is interposed between each gear disc 42 and each output disc 43 in a compressed state.

Each pinion gear 45 is rotatably supported by a pinion shaft 45a having support shafts orthogonal to each other, and is meshed with a bevel gear 42b of each gear disc 42. The pinion shaft 45a has a washer 4
It is fixed to each groove 40d of the gear case 40 via 5b,
It is adapted to rotate integrally with the gear case 40. That is, the pinion gears 45 and the pinion shafts 45a constitute a differential transmission mechanism, and the rotations of the pinion gears 45 cause the gear disks 42 to rotate in opposite directions. Also, the pinion shaft 45a
A thrust washer 45c is interposed between the gear disc 42 and each gear disc 42.

In the differential device configured as described above, the ring gear (not shown) for transmitting the driving force from the engine is attached to the flange 40b of the gear case 40, and the entire device rotates about the axis of the gear case 40. It is supposed to do.

Here, the operation of the above-mentioned differential device is carried out in the case where there is no rotation difference between the drive shafts 9 and in the case where there is a rotation difference between the drive shafts 9, and only one drive shaft 9 is idling. Each of the cases of falling into an easy state will be described. Since the principle of the differential limiting effect is the same as that of the first embodiment, its explanation is omitted.

First, when there is no rotation difference between the drive shafts 9 such as when the vehicle is traveling straight on a road surface having sufficient frictional force, when the gear case 40 is rotated by the driving force, the pinion is integrated with the gear case 40. Shaft 45
a rotates, and this rotational force is transmitted to each gear disc 42 via each pinion gear 45. In this case, since there is no rotation difference between the drive shafts 9, the pinion gears 45 do not rotate. Further, the rotational force transmitted to each gear disc 42 is transmitted from each recess 42a to each output disc 4
3 is transmitted to each convex portion 43a.

Next, when the vehicle makes a turn on a road surface having sufficient frictional force, and when a difference in rotation occurs between the drive shafts 9 while the torque is evenly transmitted to the drive wheels, the pinion gears 45 are caused to rotate. A rotation is performed, and a differential is achieved by the reverse rotation of each gear disk 42.

Further, when torque fluctuation occurs between the drive shafts 9 such as when one of the drive wheels loses frictional force with the road surface, one of the gear disks 42 transmits the rotational force to the other. Therefore, a reaction force is generated between each concave portion 42a and each convex portion 43a, each gear disk 42 is pressed against each thrust washer 45c, each output disk 43 is pressed against each thrust washer 43c, and this causes friction resistance. Therefore, the differential is limited. In this case, each spring 4 is attached to each gear disc 42 and each output disc 43.
4, the preload of a predetermined strength is applied in the direction of pressing each thrust washer 45c, 43c, and the differential limiting effect is increased.

[0095]

[Sixth Embodiment] FIGS. 21 to 24 show a sixth embodiment of the present invention. FIG. 21 is a side sectional view of a differential gear device, and FIG.
Is a sectional view taken along the line A-A, and FIG. 23 is a sectional view taken along the line B-B, and FIG. 24 is an exploded perspective view thereof.

This differential device includes a gear case 50 forming an input side rotating body, a pair of gear disks 51 forming a first rotating body of an output side rotating body, and a pair of second rotating bodies forming an output side rotating body. The output discs 52, the gear discs 51, a pair of springs 53 for applying an axial preload to the output discs 52, and a total of two pinion gears 54 for transmitting the rotational force of the gear case 50 to the gear discs 51. ing.

The gear case 50 is an integrally molded product whose side faces are open, and bearings 50a for supporting the output disks 52 are provided at both ends thereof. A flange 50b is provided around the gear case 50, and a large number of holes 50c for inserting bolts are provided in the flange 50b. Further, holes 50d are provided at two positions on the side surface of the gear case 50, and the pinion gears 54 are held in the holes 50d.

One end face of each gear disc 51 is opposed to one end face of each output disc 52, and on this face, a large number of recesses 51a extending in the radial direction are provided at equal intervals in the circumferential direction. Similar to the fourth embodiment, each recess 51a is formed of a flat bottom surface and slopes on both sides inclined at a predetermined angle. A bevel gear 51b is formed on the other end surface of each gear disc 51.

One end surface of each output disk 52 is opposed to one end surface of each gear disk 51, and a large number of radially extending projections 52a are provided on this surface at equal intervals in the circumferential direction. Similar to the fourth embodiment, each convex portion 52a is formed by a flat top portion and slopes on both sides inclined at a predetermined angle. That is, the convex portions 52a of the output discs 52 and the concave portions 51a of the gear discs 51 are engaged with each other, and the slopes are in contact with each other. Further, a connecting portion 52b with the wheel-side drive shaft 9 is provided at the other end of each output disk 52, and the connecting portion 52b is inserted into one bearing 50a of the gear case 50. Further, a thrust washer 52c is interposed between the other end surface of each output disk 52 and the inner surface of the gear case 50.

Each spring 53 is wound around the central portion of each output disk 52, and is interposed between each gear disk 51 and each output disk 52 in a compressed state.

Each pinion gear 54 is the pinion shaft 5
4a is rotatably supported, and each gear disc 5
It is meshed with the first bevel gear 51b. The pinion block 54b interposed between the pinion gears 54 is inserted into the pinion shaft 54a.
b is fixed to the pinion shaft 54a by a pin 54c. Further, the pinion shaft 54a is fixed to each hole 50d of the gear case 50 via a washer 54d so as to rotate integrally with the gear case 50. That is, each pinion gear 54 and pinion shaft 5
A differential transmission mechanism is configured by 4a, and each gear disk 51 rotates in the opposite direction by the rotation of each pinion gear 54. A thrust washer 54e is interposed between the pinion shaft 54b and each gear disc 51.

In the differential device configured as described above, the ring gear (not shown) for transmitting the driving force from the engine is attached to the flange 50b of the gear case 50, and the entire device rotates about the axis of the gear case 50. It is supposed to do.

Here, the operation of the above-mentioned differential device is carried out when the drive shafts 9 do not have a rotation difference, when the drive shafts 9 have a rotation difference, and only one drive shaft 9 idles. Each of the cases of falling into an easy state will be described. Since the principle of the differential limiting effect is the same as that of the first embodiment, its explanation is omitted.

First, when there is no rotation difference between the drive shafts 9 such as when the vehicle is traveling straight on a road surface having sufficient frictional force, when the gear case 50 rotates due to the driving force, the pinion is integrated with the gear case 50. Shaft 54
a rotates, and this rotational force is transmitted to each gear disk 51 via each pinion gear 54. In this case, since there is no rotation difference between the drive shafts 9, the pinion gears 54 do not rotate. Further, the rotational force transmitted to each gear disc 51 is transmitted from each recess 51a to each output disc 5
2 is transmitted to each convex portion 52a.

Next, when the vehicle makes a turn on a road surface having sufficient frictional force, and when a difference in rotation occurs between the drive shafts 9 while torque is being evenly transmitted to the drive wheels, the pinion gears 54 are not moved. The rotation of the gear discs 51 causes the gear discs 51 to rotate in the reverse direction to achieve the differential.

Further, when torque fluctuation occurs between the drive shafts 9 such as when one driving wheel loses frictional force with the road surface, one of the gear discs 51 transmits the rotational force to the other. Therefore, a reaction force is generated between each concave portion 51a and each convex portion 52a, each gear disk 51 is pressed against each thrust washer 54e, each output disk 52 is pressed against each thrust washer 52c, and this causes friction resistance and The differential is limited. In this case, each gear disc 5
The spring 53 applies a preload of a predetermined strength to the first and the output disks 52 in a direction of pressing the thrust washers 54e and 52c, so that the differential limiting effect is increased.

[0107]

As described above, according to the differential device of the first aspect, the differential limiting function can be added only by adding a simple structure to the conventional differential device having only the differential transmission mechanism. Therefore, a small and inexpensive differential device can be realized.
In addition, since a torque sensitive type extremely stable differential limiting effect can be obtained, there is an advantage that it is excellent in practicality.

Further, according to the differential device of the second and third aspects, in addition to the effect of the first aspect, the differential limiting effect having different effects can be selectively obtained according to the application, so that it is versatile. Has the advantage of being excellent.

According to the differential device of the fourth aspect, the same effect as that of the first aspect can be obtained, and the structure can be simplified.

According to the differential device of the fifth aspect, in addition to the effect of the first, second, third, or fourth aspect, the differential limiting effect can be increased, so that the practicality can be further enhanced. it can.

[Brief description of drawings]

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

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is an exploded perspective view of a differential device.

FIG. 4 is an explanatory view of the action of the force applied from the ball to the groove.

FIG. 5 is an explanatory view of the action of the force applied from the ball to the groove.

FIG. 6 is a side sectional view of a differential gear device according to a second embodiment of the present invention.

7 is a sectional view taken along the line AA of FIG.

FIG. 8 is an exploded perspective view of a differential device.

FIG. 9 is a side sectional view of a differential gear device showing a third embodiment of the present invention.

FIG. 10 is a sectional view taken along the line AA of FIG.

FIG. 11 is an exploded perspective view of the differential device.

FIG. 12 is a side sectional view of a differential gear device according to a fourth embodiment of the present invention.

FIG. 13 is a partially enlarged sectional view of a differential device.

14 is a sectional view taken along the line AA of FIG.

FIG. 15 is a sectional view taken along line BB of FIG.

FIG. 16 is an exploded perspective view of a differential device.

FIG. 17 is a side sectional view of a differential gear device according to a fifth embodiment of the present invention.

FIG. 18 is a sectional view taken along line AA of FIG.

FIG. 19 is a sectional view taken along the line BB of FIG.

FIG. 20 is an exploded perspective view of the differential device.

FIG. 21 is a side sectional view of a differential gear device showing a sixth embodiment of the present invention.

22 is a sectional view taken along line AA of FIG.

23 is a sectional view taken along the line BB of FIG.

FIG. 24 is an exploded perspective view of the differential device.

[Explanation of symbols]

1 ... Gear case, 3 ... Gear disc, 3a ... Groove, 4 ... Output disc, 4a ... Groove, 5 ... Side gear, 6 ... Ball holder, 6a, 6b ... Hole, 7 ... Ball, 8 ... Pinion gear, 10 ... Gear case, 12 ... gear disk, 12a,
12b ... Groove, 13 ... Output disk, 14 ... Ball, 15
... Multi-disc clutch, 17 ... Pinion gear, 20 ... Gear case, 22 ... Gear disc, 22a ... Groove, 23 ... Output disc, 23a ... Groove, 24 ... Side gear, 25 ... Roller holder, 26 ... Roller, 27 ... Spring, 28 ... Pinion gear, 30 ... Gear case, 32 ... Gear disc, 32
a ... concave part, 33 ... output disk, 33a ... convex part, 34 ...
Side gear, 35 ... Pinion gear, 40 ... Gear case,
42 ... Gear disc, 42a ... Recessed portion, 43 ... Output disc, 43a ... Convex portion, 44 ... Spring, 45 ... Pinion gear, 50 ... Gear case, 51 ... Gear disc, 51a
... concave portion, 52 ... output disk, 52a ... convex portion, 53 ... spring, 54 ... pinion gear.

Claims (5)

[Claims] 1. An input side rotating body that rotates around an axis by a driving force input from the outside, a pair of output side rotating bodies arranged on the rotation axis of the input side rotating body, and each output side rotating body. A differential transmission mechanism that transmits the rotational force of the input-side rotating body to each output-side rotating body while allowing the rotation difference of the output-side rotating body, at least one of the output-side rotating bodies The first and second rotating bodies are opposed to each other, and a large number of rolling elements are interposed between the first and second rotating bodies. The opposing surfaces of the first and second rotating bodies are engaged with the respective rolling elements. A differential device characterized in that a large number of grooves are provided so as to contact each rolling element at a predetermined inclination angle with respect to the direction in which the rotational force acts. 2. The rotation of the input side rotating body to one of the first and second rotating bodies or another member having the plurality of holes for holding each rolling body interposed between the first and second rotating bodies. The differential device according to claim 1, wherein the rolling elements are provided in the same number at positions different in distance from the shaft, and the rolling elements are held in holes at arbitrary positions. 3. A plurality of grooves having different inclination angles with respect to the respective rolling elements are provided alternately in the same number, and the respective rolling elements are engaged with the grooves having an arbitrary inclination angle. Differential. 4. An input side rotating body which rotates about an axis by a driving force input from the outside, a pair of output side rotating bodies arranged on the rotation axis of the input side rotating body, and each output side rotating body. A differential transmission mechanism that transmits the rotational force of the input-side rotating body to each output-side rotating body while allowing the rotation difference between the output-side rotating bodies, at least one of the output-side rotating bodies facing each other in the axial direction. The first and second rotating bodies are provided with a plurality of concave and convex portions that engage with each other on the facing surfaces of the first and second rotating bodies at a predetermined inclination angle with respect to the direction in which the rotational force acts. A differential device which is provided so as to be in contact with each other. 5. The differential device according to claim 1, further comprising an urging means for applying an axial preload to the first and second rotating bodies.