JP2002213573A - Differential device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a differential device capable of reducing sliding resistance. SOLUTION: This differential device is provided with an outer differential gear case 31 rotated by receiving the driving force of an engine, an inner differential gear case 41 having a differential mechanism 57 differentially distributing the driving force of the engine in it and coaxially rotatably supported in the outer differential gear case 31, a clutch member 43 adjacently arranged in the axial direction of the inner differential gear case 41, movable in the axial direction, and rotated integrally with the outer differential gear case 31, dog clutches 41a and 43a provided on the opposite faces of the inner differential gear case 41 and the clutch member 43 and releasably meshed with each other by the axial movement of the clutch member 43, and an actuator means 65 moving the clutch member 43 in the axial direction to engage or release the dog clutches 41a and 43a. The inner differential gear case 41 is positioned at a portion where it is slid only when the differential mechanism 57 differentially distributes the driving force.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

2. Description of the Related Art FIG. 6 shows a conventional differential device described in Japanese Patent Application Laid-Open No. 9-286254. The differential device 100 is a device in which driving is cut off when switching between two wheels of a part-time four-wheel drive vehicle, and is applied to a front differential of the vehicle.

[0003] The differential device 100 includes an outer differential case 110 that rotates by transmitting the driving force of the engine through a ring gear, and an inner differential case 120 that is rotatably supported inside the outer differential case 110.

[0004] A pinion shaft 121 is integrated with the inner differential case 120 by a spring pin 123 in a direction perpendicular to the rotation axis. Pinion shaft 1
A pair of pinion gears 125 are rotatably arranged on the gear 21 and mesh with output side gears 127 and 129 spline-connected to the front axle of the vehicle. At the time of two-wheel drive, the inner differential case 120, the pinion shaft 1
21, pinion gear 125, side gear 127, 129
Are not connected to the outer differential case 110, but are connected to the outer differential case 110 and rotate together with the outer differential case 110 when the clutch member 130 operates.

[0005] The clutch member 130 is an outer differential case 1.
10 and rotates integrally with the outer differential case 110. Inner differential case 1 of clutch member 130
A dog clutch 131 is formed on the end face (left end face) on the 20 side, while a dog clutch 133 that meshes with the dog clutch 131 is formed on the opposite end face (right end face) of the inner differential case 120. All of the teeth of the dog clutches 131 and 133 are formed so as to be tapered and inclined toward the other party, so that they can be easily meshed.

When the clutch member 130 is moved to the left in the axial direction, the dog clutches 131 and 133 are engaged with each other.
20 and outer differential case 110 are coupled, and inner differential case 120 rotates integrally with outer differential case 110, so that the driving force of the engine is transmitted to the front axle. This results in a four-wheel drive vehicle.

[0007] In order to move the clutch member 130 in the axial direction, the differential device 100 includes:
An actuator 140 driven by fluid pressure such as air pressure or hydraulic pressure is provided.

[0008] Actuator 140 driven by fluid pressure
Has a main body 143 whose bracket 141 is fixed to a differential carrier, and a retainer 145 connecting the main body 143 and the clutch member 130. Body 143
, A pressure chamber 143 a is formed, and this pressure chamber 143 a is connected to an external pressure source via a flow path 149. Also, the retainer 145 and the outer differential case 1
Between the dog clutch 1 and the dog clutch 1.
A return spring 147 is provided to urge in the anti-meshing direction of the members 31 and 133.

[0009] The upper half of FIG.
33 shows a two-wheel-drive state in which the vehicle is disengaged. In this state, the pressure in the pressure chamber 143a is released, and the urging force of the return spring 147 causes the clutch member 130
Has moved to the right and is being demolition joint.

On the other hand, the lower half of FIG. 6 shows four-wheel drive with the dog clutches 131 and 133 engaged. In this state, when the pressurized fluid is supplied to the pressure chamber 143a, the clutch member 130 connected via the retainer 145 moves toward the inner differential case 120, so that the dog clutches 131 and 133 are connected.

[0011]

In the conventional differential device 100, the positioning of the inner differential case 120 is performed by bringing its outer peripheral surface into contact with the inner peripheral surface of the outer differential case 110.

With such a structure, even if the inner differential case 120 and the outer differential case 110 are disconnected from each other by the clutch member 130 during two-wheel drive, the inner differential case 120 rotates together with the wheels during running of the vehicle. And the outer differential case 110 has a problem that the sliding resistance is increased.

This sliding resistance is measured when the vehicle is running (during two-wheel drive).
Is the running resistance. In other words, there is a problem that when the sliding resistance increases, the running resistance increases, and the fuel consumption increases.

When the sliding resistance is large, the outer differential case 110 and the inner differential case 12
There is a problem in that the temperature of the lubricating oil lubricating between zero increases and the durability of the lubricating oil is also affected.

Accordingly, an object of the present invention is to provide a differential device capable of positioning an inner differential case so that sliding resistance can be reduced.

[0016]

The differential device according to the first aspect of the present invention has an outer differential case in which the driving force of the engine is input and rotates, and a differential mechanism for differentially distributing the driving force of the engine. An inner differential case coaxially rotatably supported in the outer differential case, a clutch member disposed adjacent to the inner differential case in the axial direction, movable in the axial direction, and integrally rotating with the outer differential case, and an inner differential case. And a clutch member provided on a surface facing the clutch member, the clutch member meshing releasably with the axial movement of the clutch member, and actuator means for moving the clutch member in the axial direction such that the meshing clutch disengages. The inner differential case is integrated with the inner differential case when no differential occurs in the differential mechanism. Rotating, it is characterized by being positioned on the sliding portion only when the differential to the differential mechanism has occurred.

According to the present invention, since the inner differential case is positioned only at the portion that slides only when a differential occurs in the differential mechanism, there is no need to position the inner differential case in a structure that contacts the outer differential case. A gap can be provided between the differential case and the outer differential case. Thereby, the sliding resistance between the inner differential case and the outer differential case at the time of two-wheel drive can be significantly reduced, and the running resistance at the time of two-wheel drive can be significantly reduced, thereby suppressing fuel consumption. be able to.

Further, by reducing the sliding resistance between the inner differential case and the outer differential case, it is possible to suppress an increase in the oil temperature of the lubricating oil between the inner differential case and the outer differential case, thereby improving the durability of the lubricating oil. Can be.

According to a second aspect of the present invention, in the differential device according to the first aspect, the inner differential case is positioned via the differential mechanism.

According to the present invention, in addition to the operation and effect of the first aspect of the present invention, since the inner differential case is positioned with respect to the outer differential case via a differential mechanism disposed inside the inner differential case, the number of changed portions is small. It can be implemented with a simple structure.

According to a third aspect of the present invention, in the differential device according to the second aspect, the differential mechanism is rotatably supported on a pinion shaft fixed to an inner differential case at right angles to the inner differential case. A pinion gear, an output side gear that meshes with the pinion gear, and a thrust block provided between the side gears so as to contact the side gear while being connected to the pinion shaft, wherein the inner differential case is a thrust block;
It is characterized in that positioning in the axial direction is performed by a side gear via a pinion shaft.

According to the present invention, in addition to the functions and effects of the second aspect, the thrust block to which the pinion gear is connected is provided between the side gears in a state of contact with the side gear, so that the thrust block and the pinion gear And side gears are positioned relative to each other. The inner differential case is axially positioned by a side gear via a thrust block and a pinion shaft, so that positioning to the outer differential case becomes unnecessary. In such positioning, the inner differential case can be easily positioned in the axial direction, and can be easily assembled.

According to a fourth aspect of the present invention, in the differential device according to the second aspect, the differential mechanism is rotatably supported on a pinion shaft fixed to an inner differential case in a direction perpendicular to the inner differential case. The inner differential case includes a pinion gear and an output side gear that meshes with the pinion gear. The inner differential case is positioned in the radial direction by contacting an inner peripheral side of the inner differential case with an outer peripheral surface of the side gear.

According to the present invention, in addition to having the same operation and effect as the first aspect of the present invention, since the inner peripheral side of the inner differential case is in contact with the outer peripheral surface of the side gear, the radial positioning of the inner differential case can be performed. It can be done and the assembly is easy.

According to a fifth aspect of the present invention, in the differential device according to the second aspect, the differential mechanism is rotatably supported on a pinion shaft fixed to an inner differential case in a direction perpendicular to the inner differential case. A pinion gear and an output side gear that meshes with the pinion gear, and an axial and radial positioning engagement portion is formed on the side gear, and the pinion shaft is engaged with the positioning engagement portion. The inner differential case is characterized in that it is positioned in an axial direction and a radial direction by a side gear via a pinion shaft.

According to the present invention, in addition to having the same action and effect as the second aspect of the present invention, the pinion shaft is engaged with the positioning engagement portion of the side gear, whereby the inner differential case is connected via the pinion shaft. Indirectly in the axial and radial directions. With this structure, the inner differential case can be reliably positioned both in the axial direction and the radial direction only by forming the positioning engagement portion on the side gear.

[0027]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows a power transmission system of a part-time four-wheel drive vehicle based on a rear-wheel drive vehicle, and the differential device of the present embodiment is applied to a front differential of the vehicle. FIG. 2 is an overall sectional view of the front differential 13 of the present embodiment. The front differential 13 of this embodiment has the features of claims 1, 2, 3, and 4.

As shown in FIG. 1, the driving force of the engine 1 is distributed to the rear wheels 7 and the front wheels 9 via the transmission 3 and the power switching device 5. The driving force to the front wheel 9 is input to a front differential (differential device of the present embodiment) 13 via a propeller shaft 11.
Furthermore, the front wheels 9, 9 are distributed to the left and right front axles 15, 15, respectively.
Drive. On the other hand, the driving force to the rear wheel 7 is input to the rear differential 19 via the propeller shaft 17 and further distributed to the left and right rear axles 21 and 21 to drive the rear wheels 7 and 7.
As shown in FIG. 2, the outer differential case 31 of the front differential 13 is configured by fixing a case main body 31 a and a cover 31 b with bolts 33. A ring gear 35 (see FIG. 1) is fixed to the outer differential case 31,
The driving force of the engine 1 is input to the ring gear 35 via a drive pinion 37 (see FIG. 1) and driven.

The outer differential case 31 has boss portions 31 at both ends.
It is rotatably supported in the fixed differential carrier 39 (see FIG. 1) by c and 31d.

A substantially short cylindrical inner differential case 41 is coaxially rotatably supported on the inner periphery of the case body 31a. A substantially short cylindrical clutch member 43 is similarly disposed on the right side of the inner differential case 41.

The inner differential case 41 and the clutch member 43
Radial dog clutches (mesh clutches) 41a and 43a which can be disengaged from each other are formed on the surfaces facing each other. The meshing projections of the dog clutches 41a and 43a are each formed to have a predetermined tapered slope to facilitate meshing.

A pinion shaft 45 is integrated with the inner differential case 41 by a spring pin 47 perpendicular to the rotation axis. On the pinion shaft 45,
Three pinion gears 49 composed of bevel gears (two of which are not shown) are rotatably arranged, and mesh with the side gears 51 and 53 composed of a pair of opposed bevel gears.

A thrust block 59 is arranged between the pair of side gears 51 and 53. The thrust block 59 connects the plurality of pinion shafts 45 by partially inserting the plurality of pinion shafts 45. Further, the thrust block 59 rotates integrally with the pinion shaft 45 and the pinion gear 49.

The inner peripheral surface 41 b of the inner differential case 41 receives the thrust of the pinion gear 49. Washers 55 and 55 are disposed between the side gears 51 and 53 and the outer differential case 31, respectively.
Has received the thrust of. And the side gears 51 and 5
Numerals 3 are respectively spline-connected to the front axles 15, 15 in FIG. Thus, the bevel-type differential mechanism 57 including the inner differential case 41, the pinion gear 49, and the side gears 51 and 53 is not directly connected to the outer differential case 31 that houses the differential mechanism 57.

The thrust block 59 includes a side gear 51,
It is disposed between the side gears 51 and 53 so as to be in contact with the side gear 53. That is, the thrust block 59
A large diameter portion 59a is formed on the outer surface in the axial direction of the thrust block 5 between the side gears 51 and 53 so that the large diameter portion 59a contacts the side surfaces of the side gears 51 and 53.
9 is to be inserted. Thus, the thrust block 59 is axially positioned by the side gears 51 and 53.

As described above, the inner differential case 41 and the pinion shaft 45 are connected by the spring pin 47, and the pinion shaft 45 is connected to the thrust block 59. When the thrust block 59 contacts the side gears 51 and 53, the side gear The inner differential case 41 has a structure in which the inner differential case 41 is axially positioned by the side gears 51 and 53 via the pinion shaft 45 and the thrust block 59 by being provided between the inner gear 51 and the inner gear 51.

Then, as described above, the side gears 51,
Since the washer 55 arranged between the outer differential case 53 and the outer differential case 31 receives the thrust in the axial direction of the side gears 51 and 53, even if the dog clutches 41a and 43a are engaged and engaged, the side end surface of the inner differential case 41 and the outer A gap G1 can be secured between the differential case 31 and the differential case 31.

In this embodiment, the inner differential case 41
Of the side gears 51 and 53
c, 53c. With this contact, the inner differential case 41 is positioned in the radial direction. In addition, the side gears 51 and 53 have ring portions 51a and 53a extending outward in the axial direction.
53a is the boss portion 31c, 31d of the outer differential case 31
Of the side gear 5 due to this contact.
1, 53 are restricted from moving in the radial direction. Therefore,
The inner differential case 41, which is positioned in the radial direction by the side gears 51 and 53, is also restricted from moving in the radial direction. Thereby, a gap G2 can be provided between the outer peripheral surface of the inner differential case 41 and the inner peripheral surface of the outer differential case 31.

A diaphragm-type actuator body 65, which is one of the members constituting the actuator means, is disposed on the right side of the clutch member 43 (outer right side in FIG. 2).
7, it is fixed to the differential carrier 39 (see FIG. 1) side. The pressure chamber 65a is connected to an external pressure source via a flow path 69. In addition, a return spring 63, which is the other member constituting the actuator means, is disposed between the case main body 31 a and the clutch member 43.

In addition, on the tip end surfaces of the legs of the clutch member,
A retainer 61 formed by molding a thin cylindrical spring material is disposed integrally with the clutch member 43, and the tip end side of the leg portion of the clutch member 43 in the retainer 61 is a flange portion 6.
1a, the return spring 63 is disposed between the flange portion 61a and the case body 31a.

On the other hand, the other end of the thin cylinder of the retainer 61 is
The clutch member 43 is also pushed into the inner periphery of the retainer 61 and locked by utilizing the resiliency of the projecting portion 61c. In this way, since the clutch member 43 and the retainer 61 are integrated, the return spring 63 urges the case body 31a to separate the clutch member 43 outward (to the right) in the axial direction. .

Thus, the dog clutches 41a, 41
3a, hole 3 of clutch member 43 and outer differential case 31
1e, the actuator main body 65, the return spring 63, and the receiving portion on the half-clutch side end surface of the inner differential case 41 are arranged on substantially the same diameter, so that the transmission of force when the dog clutches 41a, 43a are disengaged is performed. It is made smoothly on the same diameter, and the engagement and disengagement are performed smoothly.

Next, the operation of the front differential 13 will be described. In a state where a predetermined pressure is supplied to the pressure chamber 65a of the actuator body 65 (four-wheel drive state), the diaphragm opposes the urging force of the return spring 63. Since the dog clutches 41a and 43a of the inner differential case 41 and the clutch member 43 are engaged by displacing the left differential 65b to the left, the outer differential case 31 is connected via the clutch member 43.
And the inner differential case 41 therein rotate integrally.
When the dog clutches 41a and 43a are engaged, the thrust of the inner differential case 41 is received by the wall of the outer differential case 31 that is in contact with the thrust.

On the other hand, when the pressure in the pressure chamber 65a is released, the diaphragm 65b returns to the right by the urging force of the return spring 63, so that the dog clutches 41a, 43
Since a is removed, the outer differential case 31 and the inner differential case 41 inside the outer differential case 31 can rotate independently (two-wheel drive state).

The supply and discharge of the pressure to and from the pressure chamber 65a are performed in conjunction with the operation of the 4WD / 2WD switching device 5a (FIG. 1) of the transfer 5.

In the case of this vehicle, when the four-wheel drive state is switched to two-wheel drive, the driving force from the engine to the front wheels is cut off by the power switching device 5. The driving force of the engine 1 drives only the rear wheels 7, 7 via the propeller shaft 17 and the rear differential 19.

Thereafter, as long as the two-wheel drive state is maintained, the differential mechanism 57 in the front differential 13 follows the drive path reverse to that of the previous four-wheel drive and is caused to idle by the front wheels 9, In conjunction with switching to two-wheel drive, the electromagnet 6
1, the dog clutches 41a and 43a are disengaged, so that the clutch member 43, the outer differential case 31, the ring gear 35 and the like are not idled. Therefore, it is possible to reduce the generation of energy loss and noise due to the running resistance of these idling members.

According to this embodiment, the inner differential case 41 is axially positioned by the output side gears 51 and 53 via the thrust block 59 and the pinion shaft 45 constituting the differential mechanism 57. When the engagement between the dog clutch 53a of the clutch member 43 and the dog clutch 41a of the inner differential case 41 is released (two-wheel drive state), a gap G1 is secured between the side end surface of the inner differential case 41 and the outer differential case 31. The sliding resistance between the side surface of the inner differential case 41 and the outer differential case 31 can be greatly reduced.

The inner peripheral surface 41 of the inner differential case 41
Since the inner differential case 41 is positioned in the radial direction by contacting the outer peripheral surfaces 51c and 53c of the side gears 51 and 53, the inner differential case 41 is positioned between the outer peripheral surface of the inner differential case 41 and the inner peripheral surface of the outer differential case 31. Gap G
2 can be provided.

Therefore, the outer differential case 31 and the inner differential case 41 do not need to be in contact with each other on the entire peripheral surface, and the sliding resistance between the outer differential case 31 and the inner differential case 41 can be greatly reduced. By reducing the sliding resistance in this way, the running resistance during two-wheel drive is reduced, and the fuel consumption during two-wheel drive can be reduced.

Further, by reducing the sliding resistance in this way, it is possible to suppress an increase in the oil temperature of the lubricating oil and improve the durability of the lubricating oil.

Further, according to the above structure, since the inner differential case 41 is positioned with respect to the outer differential case via the differential mechanism 57 disposed therein, the inner differential case 41, the thrust block 59, the side gear 51, Because it is possible only by changing 53,
It can be easily performed, and the assembly is easy.

[Second Embodiment] FIG. 3 shows a second embodiment of the present invention. The front differential 13 of this embodiment has the features of claims 1, 2, and 4.

In the front differential 13 of this embodiment, the large-diameter portion 59a is not formed in the thrust block 59, and the side gears 51, 5 via the thrust block 59 are provided.
3, the axial positioning of the inner differential case 41 is not performed. Therefore, the thrust block 59
Molding is easy.

On the other hand, the inner peripheral surface 41 of the inner differential case 41
c is in contact with the outer peripheral surfaces of the side gears 51 and 53,
With this contact, the inner differential case 41 is positioned in the radial direction. Even in such a structure, the gap G2 can be secured between the outer peripheral surface of the inner differential case 41 and the inner peripheral surface of the outer differential case 31, and the sliding resistance at this portion can be reduced.

By reducing the sliding resistance in this manner, the running resistance during two-wheel drive is reduced, the fuel consumption during two-wheel drive can be reduced, and the increase in the lubricating oil temperature is suppressed. As a result, the durability of the lubricating oil can be improved.

[Third Embodiment] FIG. 4 shows a third embodiment of the present invention. The front differential 13 of this embodiment has the features of claims 1, 2, 3, and 4.

Also in this embodiment, the inner differential case 4
1 and the pinion shaft 45 are connected by a spring pin 47.

On the other hand, both the side gears 51 and 53 extend in the radial direction, and the extending portions 71 and 73 are in contact with the outer portion of the inner differential case 41. More specifically, the extending portions 71 and 73 have right-angled end surfaces, and each of the orthogonal end surface portions is the inner differential case 4.
1 is in contact with the outer part.

In such a contact structure, the side gear 5
Reference numerals 1 and 53 support the inner differential case 41 in the radial direction and the axial direction, and perform positioning of the inner differential case 41 in the radial direction and the axial direction. Also, the side gear 51,
In contrast to 53, a washer 55 provided between the side gears 51, 53 and the outer differential case 31 receives thrust in the axial direction, and the ring portion 5 of the side gears 51, 53 is provided.
1a and 53a are boss portions 31d of the outer differential case 31,
31c and restricts movement in the radial direction.

Accordingly, also in this embodiment, a gap G1 can be secured between the side end surface of the inner differential case 41 and the outer differential case 31, and the outer peripheral surface of the inner differential case 41 and the inner peripheral surface of the outer differential case 31 can be secured. A gap G2 can be secured therebetween. This allows
The sliding resistance at this portion can be reduced.

By reducing the sliding resistance in this manner, the running resistance during two-wheel drive is reduced, the fuel consumption during two-wheel drive can be reduced, and an increase in lubricating oil temperature is suppressed. As a result, the durability of the lubricating oil can be improved.

In this embodiment, the side gear 5
Since the radial direction and the axial direction of the inner differential case 41 are determined only by the parts 1 and 53, the structure is simple, and the working and the assembly are easy.

[Fourth Embodiment] FIG. 5 shows a fourth embodiment of the present invention. The front differential 13 of this embodiment has the features of claims 1, 2, and 5.

In this embodiment, the side gears 51, 53
And the pinion shaft 45 is changed. That is, the positioning engagement portion 7 is
5, 77 are respectively formed. Positioning engagement part 7
5 and 77 are pinion shafts 4 of side gears 51 and 53.
5, the bottom portions 75a, 77a cut along the axial direction and the side portions 75b, 7 cut along the radial direction so as to be orthogonal to the bottom portions 75a, 77a.
7b.

On the other hand, a flange portion 79 is formed at an end of the pinion shaft 45 opposite to the spring shaft 47 in an enlarged state. The flange portion 79 includes a bottom portion 79a extending in the axial direction and a side portion 79b extending in the radial direction so as to be orthogonal to the bottom portion 79a.

Then, the bottom surface portion 79a of the flange portion 79 contacts the bottom surface portions 75a, 77a of the positioning engagement portions 75, 77, and the side surface portion 79b of the flange portion 79 contacts the side surface portions of the positioning engagement portions 75, 77. The pinion shaft 45 is assembled to the side gears 51 and 53 so as to come into contact with 75b and 77b. Also in this case, the inner differential case 41
The pinion shaft 45 is fixed by a spring pin 47.

The side gears 51 and 53 are provided with washers 5.
The axial thrust is received by 5 and
The radial movement is restricted by the ring portions 51a and 53a coming into contact with the boss portions 31d and 31c of the outer differential case 31.

In such a structure, the bottom surface portion 79a of the flange portion 79 comes into contact with the bottom surface portions 75a, 77a of the positioning engagement portions 75, 77 of the side gears 51, 53, so that the inner differential case 41 separates the side gears 51, 53.
The positioning in the radial direction is thereby performed. Further, when the side surface portion 79b of the flange portion 79 comes into contact with the side surface portions 75b, 77b of the side gears 51, 53, the inner differential case 41 is axially positioned by the side gears 51, 53.

Accordingly, also in this embodiment, a gap G1 can be secured between the side end surface of the inner differential case 41 and the outer differential case 31, and the outer peripheral surface of the inner differential case 41 and the inner peripheral surface of the outer differential case 31 can be secured. A gap G2 can be secured therebetween. As a result, the sliding resistance at this portion is reduced, so that the running resistance at the time of two-wheel drive is reduced, the fuel consumption at the time of two-wheel drive can be reduced, and the rise in lubricating oil temperature is suppressed. As a result, the durability of the lubricating oil can be improved.

In the above-described first to fourth embodiments, the example in which the inner differential case 31 is positioned by the thrust block 59 and the side gear 53 has been described. However, the inner differential case 31 slides only when a differential occurs in the differential mechanism 57. Inner differential case 3
What is necessary is just a thing which positions 1. For example, when the inner differential case 31 is positioned by a drive shaft or the like connected to the side gear 53, it goes without saying that the same effect as in the above embodiment can be obtained.

[0072]

According to the first aspect of the present invention, since the inner differential case is positioned at a portion which slides only when a differential occurs in the differential mechanism, a gap is provided between the inner differential case and the outer differential case. Can be provided, whereby the sliding resistance between the inner differential case and the outer differential case can be significantly reduced, and the fuel consumption can be suppressed.

According to the second aspect of the present invention, in addition to the same effects as those of the first aspect of the present invention, the inner differential case is connected to the outer differential case via a differential mechanism disposed inside the inner differential case. Since the positioning is performed, the number of changed portions is small, and the operation can be performed with a simple structure.

According to the third aspect of the invention, in addition to the same effect as that of the second aspect of the invention, the inner differential case is axially positioned by the side gear via the thrust block and the pinion shaft. Positioning with respect to the outer differential case is not required, so that sliding resistance can be reduced, and the inner differential case can be easily positioned in the axial direction, and can be easily assembled.

According to the fourth aspect of the invention, the same effect as that of the second aspect of the invention can be obtained. In addition, since the inner peripheral side of the inner differential case is in contact with the outer peripheral surface of the side gear, the radial direction of the inner differential case can be improved. Can be positioned,
Assembly becomes easy.

According to the fifth aspect of the present invention, in addition to the same effect as that of the second aspect of the invention, the inner differential case is indirectly pivoted by engaging the pinion shaft with the positioning engagement portion of the side gear. Since the positioning is performed in the direction and the radial direction, the sliding resistance of the inner differential case is reduced, and the inner differential case can be reliably positioned both in the axial direction and the radial direction simply by forming the positioning engagement portion on the side gear.

[Brief description of the drawings]

FIG. 1 is a plan view showing a power transmission system of a vehicle to which a first embodiment is applied.

FIG. 2 is a cross-sectional view of the differential device according to the first embodiment.

FIG. 3 is a sectional view of a differential device according to a second embodiment.

FIG. 4 is a sectional view of a differential device according to a third embodiment.

FIG. 5 is a cross-sectional view of a differential device according to a fourth embodiment.

FIG. 6 is a sectional view of a conventional differential device.

[Explanation of symbols]

 13 front differential 31 outer differential case 41 inner differential case 43 clutch member 45 pinion shaft 49 pinion gear 51, 53 side gear 57 differential groove 65 actuator means

Continued on the front page (72) Inventor Takeshi Shimanuki 2388 Omiyacho, Tochigi City, Tochigi Prefecture Tochigi Fuji Industrial Co., Ltd. F-term (reference) 3D036 GA14 GA38 GB05 GB07 GD02 GD04 GF04 GF10 GH06 GH26 GJ01 3J027 FA34 FB04 HB07 HC21 HD01 HF02 HG07 HH20

Claims (5)

[Claims] 1. An inner case having an outer differential case that receives and rotates an engine driving force and a differential mechanism that differentially distributes the driving force of the engine and is rotatably supported coaxially in the outer differential case. The differential case and the inner differential case are arranged adjacent to each other in the axial direction, and are movable in the axial direction.
A clutch member that rotates integrally with the outer differential case, a meshing clutch that is provided on a surface facing the inner differential case and the clutch member, and that meshes releasably with the axial movement of the clutch member, and the meshing clutch disengages. Actuator means for moving the clutch member in the axial direction, the inner differential case rotates integrally with the inner differential case when the differential mechanism is not differentially driven, and the differential mechanism transmits the differential to the differential mechanism. A differential device characterized in that the differential device is positioned at a portion that slides only when the condition occurs. 2. The differential device according to claim 1, wherein the inner differential case is positioned via the differential mechanism. 3. The differential device according to claim 2, wherein the differential mechanism includes: a pinion shaft fixed in a direction perpendicular to an inner differential case; a pinion gear rotatably supported on the pinion shaft; An output side gear that meshes with a pinion gear, and a thrust block provided between the side gears so as to contact the side gear while being connected to the pinion shaft, and the inner differential case is axially driven by the side gear through a thrust block and a pinion shaft. A differential device characterized in that a direction is determined. 4. The differential device according to claim 2, wherein the differential mechanism includes: a pinion shaft fixed in a direction perpendicular to an inner differential case; a pinion gear rotatably supported on the pinion shaft; A differential device comprising a pinion gear and an output side gear meshing with the inner differential case, wherein the inner differential case is positioned in a radial direction by an inner peripheral side of the inner differential case being in contact with an outer peripheral surface of the side gear. 5. The differential device according to claim 2, wherein the differential mechanism includes a pinion shaft fixed to an inner differential case in a direction perpendicular to the inner differential case, a pinion gear rotatably supported on the pinion shaft, and a pinion. An output side gear that meshes with a gear. An axial and radial positioning engagement portion is formed on the side gear, and the pinion shaft is engaged with the positioning engagement portion. A differential device characterized in that it is positioned in an axial direction and a radial direction by a side gear via a first gear.