JP2001153206A - Differential gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily adjust the initial torque of a friction clutch. SOLUTION: This differential gear includes a differential mechanism 7 for distributing the driving power of an engine for rotating a differential case 3 from side gears 41, 43 to the wheel side, a side flange 9 connected to the side gear 41, differential limiting friction clutches 13, 13, and a pre-pressure mechanism 15 for applying initial torque to each clutch 13 by an energizing member 61, and displacing an adjusting member 63 to vary the amount of deflection of the energizing member 61, thereby adjusting the initial torque. In this gear, the adjusting member 63 can be operated to displace through a penetrating hole 99 provided in the flange 9.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a differential device provided with a mechanism for adjusting an initial torque of a friction clutch for limiting a differential.

[0002]

2. Description of the Related Art FIG.
Such a differential device 201 is described.

[0003] The differential device 201 is a differential device having a differential limiting mechanism, and a bevel gear type differential mechanism 20.
3. It is composed of a multi-plate clutch 205, 205, a preload mechanism 207, a preload adjustment mechanism 209, and the like.

[0004] The differential mechanism 203 includes a pinion shaft 213 and a pinion shaft 2 fixed to the differential case 211.
13, the pinion gear 215 and the pinion gear 2
15 and side gears 217 and 219 meshed with each other. The hollow side gears 217 and 219 are spline-connected to shaft portions of side flanges, and the side gears 217 and 219 are connected to the respective wheel sides via the side flanges.

The driving force of the engine for rotating the differential case 211 is controlled by the pinion shaft 213 and the pinion gear 21.
5, distributed from the side gears 217, 219 to each wheel side. Also, if there is a difference in driving resistance between wheels on bad roads,
The rotation of the engine is differentially distributed to each wheel by the revolution of the pinion gear 215.

[0006] The multi-plate clutch 205 includes a differential case 211.
And the side gears 217, 219, respectively, and are fastened by receiving the meshing reaction force of the side gears 217, 219.

Since the meshing reaction force of the side gears 217 and 219 increases in proportion to the transmission torque of the differential device 201, a torque-sensitive differential limiting function can be obtained by the frictional resistance of each multi-plate clutch 205.

The torque-sensitive differential limiting function limits the differential of the differential mechanism 203, thereby improving the maneuverability and stability of the vehicle particularly when starting or accelerating when a large driving force is applied.

The preload mechanism 207 includes a preload cam bolt 2
21, a pair of pressure plates 2 disposed between the side gears 217, 219 and the preload cam bolt 221;
23, 223, a pair of cams 22 formed between the preload cam bolt 221 and each pressure plate 223.
5, 225; a nut 227 screwed to the preload cam bolt 221; a disc spring group 23 disposed between the washer 229 on the nut 227 side and each pressure plate 223;
1 and the like.

Two sets of the preload mechanisms 207 are arranged at regular intervals in the circumferential direction.

The disc spring group 231 is bent between the washer 229 and each pressure plate 223 by the screw thrust force of the nut 227. Disc spring group 23
1 actuates the cams 225 and 225 by pulling the preload cam bolt 221 outward in the radial direction, and the respective cams 225 actuate the respective multi-plate clutches 205 via the pressure plate 223 and the side gears 217 and 219 by the thrust force. To give the initial torque.

Each multi-plate clutch 205 limits the differential of the differential mechanism 203 by the initial torque (a predetermined differential limiting force).

The preload adjusting mechanism 209 is provided with the nut 2
27 and a preload cam bolt 221.

The nut 227 is exposed to the outside through a radial opening 233 provided in the differential case 211. By rotating the nut 227 to change the screw thrust force, the amount of deflection of the disc spring group 231 changes, and As a result, the initial torque of each multi-plate clutch 205 is adjusted.

As described above, a torque-sensitive differential limiting function in which the differential limiting force changes in response to the transmission torque, and a speed-sensitive differential function in which the differential limiting force changes in response to the differential rotation speed. Unlike the dynamic limiting function, the differential torque is always fixed by the initial torque of the multi-plate clutches 205, 205 irrespective of running conditions such as acceleration and deceleration of the vehicle and fluctuations in road surface conditions such as road μ (friction resistance). Power is gained.

Therefore, unlike a torque-sensitive differential limiting function in which the differential limiting force is reduced when one of the wheels rotates idle, for example, one wheel is large when the vehicle starts or accelerates or when the vehicle is on a rough road. Even if you try to spin, the multi-plate clutch 205,
Since the driving force of the engine is sent to the other wheel by the initial torque of 205, the torque is prevented from escaping from the wheel on the idling side, and the startability and acceleration of the vehicle and the running and egress of rough roads are improved. Kept high.

[0017]

However, in the conventional differential device 201, the operation of the nut 227 is performed through a radial opening 233 provided in the differential case 211, and other locations and directions are different. For example,
The preload cannot be adjusted from the axial direction.

In order to adjust the preload from the opening 233,
In a casing that houses the differential device 201,
It is necessary to provide an opening for that, and with this,
Casing incompatibility is lost and the casing becomes costly.

If the casing has no opening,
Each time the preload is adjusted, the vehicle must be returned to a well-equipped factory for disassembly, resulting in high costs.

Japanese Patent Application No. 10-272057 discloses a differential device capable of adjusting the preload in the axial direction.

However, in this case, the preload cannot be adjusted unless the axle is removed from the differential device.

The axle and the side gear may be connected by a retaining ring. In such a case, a special tool is required to remove the axle, which is difficult for a general user.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a differential device which can easily adjust the initial torque of a friction clutch for limiting a differential at low cost.

[0024]

According to a first aspect of the present invention, there is provided a differential device comprising: a differential case rotatably driven by an engine driving force; a differential gear rotatably disposed on the differential case; and a pair of gears meshing with the differential gear. A differential mechanism having an output side gear, a shaft flange connected to each side gear and a side flange connected to the wheel side, a friction clutch for limiting the differential of the differential mechanism, and a friction clutch by an urging member. Preload and give initial torque,
A preload mechanism capable of adjusting the amount of deflection of the biasing member by the adjusting member and adjusting the initial torque is provided, a through hole is provided in the side flange, and the adjusting member can be operated from the outside through the through hole. It is characterized by:

Since the biasing member of the preload mechanism applies an initial torque to the friction clutch for limiting the differential, even under conditions where one wheel is large and easily slips, such as when starting, accelerating, or traveling on a rough road. , This initial torque prevents the torque from escaping to the idling wheels,
It is possible to keep the startability and acceleration of the vehicle, and the traveling and escape of rough roads high.

In the differential device according to the first aspect of the present invention, the through-hole is provided in the side flange connected to the side gear of the differential mechanism, so that, for example, a tool is inserted through the through-hole without removing the side flange. Thus, the adjusting member of the preload mechanism can be operated from the outside.

Therefore, a special tool for removing the side flange is not required, and even a general user can easily adjust the initial torque.

A differential device according to a second aspect is the differential device according to the first aspect, wherein an adjustment shaft is disposed in a through hole of a side flange, and an adjustment member of a preload mechanism is provided at an inner end of the adjustment shaft. The connecting portion is provided, and the operating portion formed at the outer end is exposed to the outside, so that the same effect as the configuration of claim 1 can be obtained.

In addition, an adjusting shaft is disposed in the through hole of the side flange so that an inner end thereof can be connected to an adjusting member of the preload mechanism, and an operating part formed at the outer end is exposed to the outside. As a result, the initial torque can be adjusted from outside the side flange via the adjustment shaft, and the adjustment of the initial torque is further facilitated by such a simple structure.

A differential device according to a third aspect is the differential device according to the second aspect, wherein a connecting portion between the adjustment shaft and the adjustment member is made detachable. An equivalent effect can be obtained.

In addition, since the adjusting shaft and the adjusting member can be disengaged, if the adjusting shaft is separated from the adjusting member except when adjusting the initial torque, the urging member of the preload mechanism can be used. For example, since the influence of the side flange and the adjustment shaft (for example, thrust force) is released, the fluctuation of the initial torque is prevented, and the starting property, acceleration property, running ability on rough roads, escape property, etc. of the vehicle are kept high. Can be.

According to a fourth aspect of the present invention, there is provided the differential device according to the third aspect, further comprising a return spring for urging the adjustment shaft in a direction of releasing the connection with the adjustment member. The same effect as that of the third configuration can be obtained.

In addition, after the adjustment of the initial torque, the adjusting shaft is automatically separated from the adjusting member by the return spring (returns to the uncoupling position), so that the operation for separating the adjusting shaft is unnecessary. Therefore, the workability of the initial torque adjustment is further improved.

[0034]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment (differential device 1) of the present invention will be described with reference to FIGS.

This differential device 1 has the following features.
4 and FIG. 1 and FIG. 2 show the differential device 1 in different states. FIG. 3 is an exploded perspective view of the components, and the left and right directions are drawn in opposite directions to FIGS. The left and right directions are the vehicle using the differential device 1 and the left and right directions in FIGS. 1 and 2, and the members and the like without reference numerals are not shown.

The differential device 1 includes a differential case 3, pressure rings 5, 5, a bevel gear type differential mechanism 7, side flanges 9, cams 11, 11, multiple disc clutches 13, 13 (friction clutches), a preload mechanism 15, and switching. Shaft 17 (adjustment shaft), return spring 1
9 and the like.

The differential device 1 is disposed inside a differential carrier, and a predetermined amount of oil is injected into the differential carrier to form an oil reservoir.

The differential case 3 is formed by fixing the casing body 21 and the cover 23 with bolts 25. The left and right bosses 27, 29 are supported by differential carriers by bearings, and are driven to rotate by the driving force of the engine.

Each pressure ring 5 is connected so that it can move in the axial direction while rotating integrally with the differential case 3 by engaging a convex portion 31 provided on the outer periphery with an axial groove 33 provided in the differential case 3. Have been.

The differential mechanism 7 includes a pinion shaft 37 radially disposed around the hollow boss 35, a pinion gear 39 (differential gear) rotatably disposed on each of the pinion shafts 37, and a pinion gear. 39 and a pair of output side gears 41 and 43 engaged with each other.

Each boss 45, 4 of the side gears 41, 43
Reference numeral 7 is supported on the inner periphery of a support portion provided on the differential case 3.

The side flange 9 is spline-connected to the boss 45 of the left side gear 41. The side flange 9 is connected to the flange on the joint side, and is connected to the left wheel side via an axle. Right side gear 4
The other boss portion 47 is spline-connected to another side flange, and this side flange is connected to the right wheel via an axle.

A spherical washer portion 49 is formed on the inner periphery of each pressure ring 5, and these spherical washer portions 49 support the rear surface of the pinion gear 39 and receive the centrifugal force and the meshing reaction force. I have.

The cams 11, 11 are provided between the distal end of the pinion shaft 37 and the two pressure rings 5, and have the same cam angle in both rotation directions of the differential case 3.

Each multi-plate clutch 13 has an inner periphery of the differential case 3 and bosses 45 and 47 (side gears 41 and 43).
And the outer circumference of the.

The driving force of the engine for rotating the differential case 3 is input to the differential mechanism 7 via the pressure rings 5 and 5, the cams 11 and 11 and the pinion shaft 37, and from the pinion gear 39 via the side gears 41 and 43. Distributed to the left and right wheels.

Further, for example, when a difference in driving resistance occurs between the wheels at the time of starting, accelerating, or traveling on a rough road, the driving force of the engine is differentially distributed to the left and right wheels by the rotation of the pinion gear 39.

At this time, the cam 1 receives the transmission torque between the pressure rings 5 and 5 and the pinion shaft 37 and receives the torque.
The multi-plate clutches 13, 13 are pressed via the pressure rings 5 by the cam thrust force,
Will be concluded.

Further, the multi-plate clutches 13, 13 are connected to a side gear 4 generated by meshing with a pinion gear 39.
Each pressure ring 5
Is pressed through.

Thus, the multi-plate clutches 13, 13
A torque-sensitive differential limiting function is established by the cam thrust force of the cams 11 and 11 and the meshing reaction force of the side gears 41 and 43, which are increased in proportion to the transmission torque, and the frictional resistance of the engaged multi-plate clutches 13 and 13. Is obtained.

The differential of the differential mechanism 7 is limited by the torque-sensitive differential limiting function, and the maneuverability and stability of the vehicle are improved.

In particular, when starting or accelerating when a large driving force is applied, a large differential limiting force can be obtained by the torque-sensitive differential limiting function, so that the maneuverability and stability are further improved.

The preload mechanism 15 includes a switching shaft 17,
It comprises left and right pressure plates 51, shims 53, setting plates 55, cam plates 57, cam mechanisms 59, disc spring groups 61 (biasing members), thrust blocks 63 (adjusting members), connecting portions 65, and the like.

Each pressure plate 51 has a side gear 4
1 and 43 are arranged to face each other. Sim 5
3, the setting plate 55, the cam plate 57, the cam mechanism 59, and the disc spring group 61 include the pressure plate 51,
51, they are arranged in this order from the left, and they are arranged inside the boss 35 of the pinion shaft 37. Each of these members is hollow, and the thrust block 63 penetrates them.

As shown in FIG. 3, the setting plate 55
Are provided with two concave portions 67 having a semicircular cross section penetrating in the axial direction at equal intervals in the circumferential direction. Further, a flange portion protruding from the entire circumference in the circumferential direction is provided on the inner periphery of the boss portion 35, and a semicircular cross-section penetrating in the axial direction is provided on the inner periphery of the flange portion at a position facing the recess 67. Are provided.

The setting plate 55 and the boss 35 are connected by inserting a detent pin 69 into these recesses.
5 is prevented from rotating toward the pinion shaft 37 (differential case 3), and is movable in the axial direction.

The rotation of the setting plate 55 with respect to the boss portion 35 is performed by a spline or serration, for example, in addition to using a connecting member such as a pin or a key, if the setting plate 55 is movable in the axial direction. You may.

The cam mechanism 59 has, as shown in FIG. 3, a convex portion 71 formed on the setting plate 55 and, as shown in FIGS.
77.

As shown in FIG. 3, two protrusions 71 are formed at equal intervals in the circumferential direction, and two sets of grooves 73, 75, 77 are provided at equal intervals in the circumferential direction. In addition, these grooves 73,
75 and 77 are deeper in this order as shown in FIG.

The disc spring group 61 is pressed between the cam plate 57 and the right pressure plate 51, and the cam plate 57, the cam mechanism 59, and the setting plate 5
5, the left multi-plate clutch 13 is pre-pressed via the shim 53 and the left pressure plate 51, and the right multi-plate clutch 13 is pre-pressed via the right pressure plate 51, and an initial torque is given to each. I have.

When the thickness of the shim 53 is adjusted, the amount of deflection of the disc spring group 61 changes, and the initial torque of the multi-plate clutch 13 changes.

When the vehicle is starting or accelerating, or when traveling on a rough road, one of the wheels is likely to idle easily, and the torque escapes from the idle wheel to reduce the torque-sensitive differential limiting function. Under such conditions, the initial torque of the multi-plate clutches 13 prevents the torque from escaping from the idle wheels.

In this way, the startability and acceleration of the vehicle, the running ability on rough roads and the escapement of the rough road are prevented from being reduced, and the behavior of the vehicle body at the time of starting, accelerating, on rough roads is stabilized, and the maneuverability is greatly improved. I do.

As shown in FIG. 4, the groove 7 of the cam plate 57
3, 75 and 77 have inclined walls on both sides in the circumferential direction, and rotate the setting plate 55 (displacement operation).
Then, the two convex portions 71 are respectively provided with the grooves 73, 75,
77 in order.

The distance between the setting plate 55 and the rear surface of the cam plate 57 becomes wider as the groove in which the projection 71 engages becomes shallower, and the amount of deflection of the disc spring group 61 becomes larger, as shown in FIG. The initial torque (cam thrust force of the cam mechanism 59) applied to the multi-plate clutches 13, 13 is strongest in the shallow groove 73, weakest in the deep groove 77, and intermediate in the middle groove 75.

As described above, the convex portion 71 and the grooves 73, 75,
77 are arranged at equal intervals in the circumferential direction, so that the cam thrust force of the cam mechanism 59 uniformly presses the entire circumference of the disc spring group 61 to prevent uneven wear.

The thrust block 63 has a two-divided configuration with half blocks 79 and 81.

As shown in FIG. 3, the half block 79 includes a hexagonal column-shaped head 83 and a cylindrical shaft 85, and the half block 81 includes a hexagonal column-shaped head 87 and a cylindrical shaft 89. .

These half blocks 79, 81 are provided with key grooves 90, 91 formed on the tip side of the respective shaft portions 85, 89.
After the key 93 is engaged with the
5 to form an integral thrust block 63.

Further, the key 93 is engaged with a key groove 97 provided through the setting plate 55 in the axial direction, and the thrust block 63 is connected to the setting plate 55 by the key 93 in the rotation direction. Thus, it can be freely moved in the axial direction.

When the thrust block 63 is rotated, the setting plate 55 is rotated, and the initial torque can be adjusted by switching the strength of the cam thrust of the cam mechanism 59 as described above.

The thrust block 63 restricts the side flanges on the side gears 41 and 43 from moving inward.

As shown in FIGS. 1 and 2, the switching shaft 17
Are housed in the through holes 99 of the side flange 9. The head 101 of the switching shaft 17 is exposed to the outside through the through hole 99, and the head 101 has a hexagon wrench
A square hole 103 (operation unit) is formed. Head 1
O-rings, X-rings, D-rings, etc. 105 are arranged between 01 and the through hole 99 to prevent oil leakage.

A hexagonal engaging portion 109 is formed at the tip of the small diameter portion 107 formed on the switching shaft 17, and a hexagonal hole which can be disengaged from the engaging portion 109 is formed on the head 83 of the half block 79. 111 are formed to form the connecting portion 65.

Retaining rings 113 and 115 are fixed to the through holes 99 of the side flange 9, and the return spring 19 connects the switching shaft 17 between the retaining ring 115 and the connecting portion 65 (the engaging portion 109 and the hexagonal hole). 111).

As described above, since the head 101 of the switching shaft 17 is exposed outside the side flange 9 (through hole 99), the switching can be performed simply by removing the flange on the axle side connected to the side flange 9. The hexagonal hole 103 of the shaft 17 becomes accessible from outside.

Then, a wrench is inserted into the hexagonal hole 103 and the switching shaft 17 is pushed rightward as it is, as shown in FIG.
9 can be engaged with the hexagonal hole 111 of the thrust block 63. At this time, the engaging portion 109 and the hexagonal hole 111
If the phases do not match, the switching shaft 17 may be turned with a wrench until the phases match.

When the engaging portion 109 is engaged with the hexagonal hole 111, the switching shaft 17 is turned with a wrench to
Setting plate 5 via thrust block 63
Since the rotation of the cam mechanism 5 can be performed, the switching of the cam mechanism 59 as described above can be performed from outside the side flange 9.

After the switching of the cam mechanism 59 is completed,
When the switching shaft 17 is released and the pressing to the right is stopped, the switching shaft 17 is automatically returned to the uncoupling position in FIG.
Is disconnected and separated from the thrust block 63. In this disconnected state, the switching shaft 17 is pressed by the retaining ring 113 and the retaining ring 113 prevents the switching shaft 17 from falling off.

The openings 117, 119, and 1 are provided in the differential case 3.
21 and 123 are provided, and spiral oil grooves 125 and 127 are provided on the inner periphery of the boss portions 27 and 29. These openings 117, 119, and 1 are provided in the differential case 3.
The oil in the oil reservoir flows out and in through the oil grooves 21 and 123 and the oil grooves 125 and 127.

The inflowing oil flows into the meshing portions of the gears of the differential mechanism 7, the convex portions 31 of the pressure rings 5 and 5 and the grooves 33 of the differential case 3, the cams 11 and 11, the spherical washer portions 49, and the multi-plate clutch 13. , 13, pressure plate 5
1. Shim 53, Setting plate 55, Cam plate 57, Grooves 73, 75, 77 of the cam mechanism 59, and the projection 7
1. Disc spring group 61, key 93 and key groove 97, engaging portion 109 of switching shaft 17 and thrust block 63
Sliding parts and lubricating parts such as the square hole 111 and the return spring 19 are sufficiently lubricated to operate normally and to improve durability.

Thus, the differential device 1 is configured.

The differential device 1 has the following advantages due to the above-described features.

(1) By providing the through-hole 99 in the side flange 9 and providing the switching shaft 17 passing through the through-hole 99, the switching can be performed simply by removing the flange on the axle side connected to the side flange 9. By operating the preload mechanism 15 via the shaft 17, the multi-plate clutches 13, 13
Can be adjusted.

Accordingly, the side flange 9 is connected to the side gear 4
This eliminates the need for a special tool for extracting the initial torque, and allows a general user to easily adjust the initial torque.

(2) Since the initial torque can be directly adjusted via the switching shaft 17 without using a tool inserted through the through hole 99 of the side flange 9, the initial torque can be extremely adjusted by such a simple structure. It can be done easily.

(3) Since the switching shaft 17 and the thrust block 63 can be disengaged by the connecting portion 65, except when adjusting the initial torque, if the switching shaft 17 is separated from the thrust block 63, the preload mechanism can be used. 15 (disc spring group 61) is, for example, a side flange 9
And the effect of fluctuation due to the thrust force of the switching shaft 17 is prevented, the fluctuation of the initial torque is prevented, and the startability, acceleration, running ability on rough roads, escapeability, etc. of the vehicle can be kept high. it can.

(4) After the adjustment of the initial torque, the switching shaft 17 is automatically separated from the thrust block 63 by the return spring 19 and returns to the original uncoupling position, so that an operation for disconnecting the switching shaft 17 is unnecessary. The workability of the initial torque adjustment is further improved.

(5) According to the present invention, it is easy to adjust the initial torque to compensate for the decrease in the torque-sensitive differential limiting function.
The present invention is particularly suitable for the differential device 1 in which a torque-sensitive differential limiting function is obtained by the thrust forces 1 and 11 and the meshing reaction force between the side gears 41 and 43.

The following configuration is also possible in the differential device of the present invention.

(1) The through hole of the side flange is not limited to the hollow hole (concentric through hole) as in the embodiment.

For example, a notch may be formed through a spline portion with the side gear, and the notch may be formed at a plurality of positions in the circumferential direction.

(2) The side flanges connected to both side gears may be hollow, so that the initial torque can be adjusted from both sides in the axial direction.

(3) When the initial torque adjustment is performed only from one side in the axial direction as in the present embodiment, it is not necessary to provide a through hole in the side flange on which the initial torque adjustment operation is not performed. Can be configured.

(4) The preload mechanism may be arranged at a place other than between the side gears (side flanges), unlike the embodiment, as long as the operation section can be operated from the through hole of the side flange.

(5) Further, unlike the embodiment, the preload mechanism is not limited to the configuration in which the initial torque is adjusted stepwise by the groove cam.

For example, the initial torque may be jointly adjusted by a tilt cam, or the initial torque may be adjusted by operating a tilt cam by rotating a screw.

(6) The displacement operation of the adjustment member is not limited to the rotation operation.

For example, if the preload mechanism is configured to convert a thrust operation force into a rotational force by a cam,
The adjusting shaft used in the configurations of claims 2 and 3 may be configured to perform a thrust (push-in) operation instead of the rotating operation as in the embodiment.

(7) The friction clutch is disposed between the side gear (shaft: S) and the differential case (housing: H) as in the embodiment, and the SS is disposed between the side gear and the side gear. May be.

(8) As described above, the initial torque of the friction clutch compensates for the torque-sensitive differential limiting function in a situation where the differential limiting function is reduced. Therefore, the differential device of the present invention which can easily adjust the initial torque is provided. Any type of differential device having a torque-sensitive differential limiting function can be implemented with any type of differential device, and is extremely effective.

For example, there are the following differential devices.

(A) A differential device in which a friction clutch is engaged only by a meshing reaction force of a side gear of a bevel gear type differential mechanism to obtain a torque-sensitive differential limiting function.

(B) A pair of output side gears are connected via a pinion gear slidably housed in a housing hole of the differential case, and these gears are constituted by helical gears. A differential device that obtains a torque-sensitive differential limiting function by frictional resistance generated between the helical gears and frictional resistance generated by the meshing thrust force of the helical gear.

(9) The biasing member of the preload mechanism is not limited to a disc spring, but may be, for example, a coil spring.

(10) The friction clutch is not limited to the multi-plate clutch, but may be another type of friction clutch such as a conical clutch.

(11) The differential device of the present invention includes a front differential (a differential device that distributes the driving force of the engine to the left and right front wheels) and a rear differential (a differential device that distributes the driving force of the engine to the right and left rear wheels). And a center differential (a differential device that distributes the driving force of the engine to the front wheels and the rear wheels).

[0108]

According to the first aspect of the present invention, since the through-hole is provided in the side flange connected to the side gear, the initial torque can be adjusted by operating the preload mechanism from the outside.

Therefore, a special tool for extracting the side flange is not required, and a general user can easily adjust the initial torque.

According to the differential device of the second aspect, the same effect as that of the configuration of the first aspect is obtained, and the initial torque can be adjusted from outside the side flange through the adjustment shaft disposed in the through hole of the side flange. It is possible and adjustment of the initial torque is easier.

According to the differential device of the third aspect, the same effect as that of the configuration of the second aspect can be obtained, and the adjustment shaft and the adjustment member can be disengaged. If it is separated, the biasing member of the preload mechanism is released from the influence of the thrust force of the side flange and the like, and the fluctuation of the initial torque is prevented.

According to the differential device of the fourth aspect, the same effect as the configuration of the third aspect is obtained, and the adjusting shaft is automatically separated from the adjusting member by the return spring, so that the operation of separating the adjusting shaft becomes unnecessary. The workability is further improved.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing one embodiment of the present invention, and shows a state in which initial torque is being adjusted.

FIG. 2 is a cross-sectional view of one embodiment, showing a state in which initial torque is not adjusted.

FIG. 3 is an exploded perspective view of various members used in one embodiment.

FIG. 4 is a view taken in the direction of arrows AA in FIG. 3;

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

[Explanation of symbols]

REFERENCE SIGNS LIST 1 differential device 3 differential case 7 bevel gear type differential mechanism 9 side flange 13, 13 multi-plate clutch (friction clutch) 15 preload mechanism 17 switching shaft (adjustment shaft) 19 return spring 39 pinion gear (differential gear) 41, 43 output side Side gear 61 Disc spring group (biasing member) 63 Thrust block (adjusting member) 65 Connecting portion provided between switching shaft 17 and thrust block 63 99 Through hole in side flange 9 103 6 provided on switching shaft 17 Square hole (operation part)

Claims (4)

[Claims] A differential case having a differential case rotatably driven by a driving force of an engine, a differential gear rotatably disposed on the differential case, and a pair of output side gears meshed with the differential gear; A shaft portion is connected to each side gear, a side flange connected to the wheel side, a friction clutch for limiting the differential of the differential mechanism, a friction member is preloaded by an urging member, and an initial torque is given, and an adjusting member is provided. A preload mechanism that can adjust the amount of deflection of the biasing member by adjusting the initial torque, adjust the initial torque, provide a through hole in the side flange, and enable the adjusting member to be operated from the outside through the through hole. Characteristic differential device. 2. The differential device according to claim 1, wherein an adjusting shaft is disposed in a through hole of the side flange, and a connecting portion with an adjusting member of a preload mechanism is provided at an inner end of the adjusting shaft. A differential device wherein an operation unit formed at an outer end is exposed to the outside. 3. The differential device according to claim 2, wherein a connecting portion between the adjusting shaft and the adjusting member is detachable. 4. The differential device according to claim 3, further comprising a return spring for urging the adjustment shaft in a direction of releasing the connection with the adjustment member.