JPH1163160A - Differential device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an intermitting means which can separate a block member and a differential case with a simple structure while obtaining large differential restricting force by supporting a pinion gear by block members. SOLUTION: A differential device has a bevel gear type differential mechanism 3 which is arranged in a differential case 15 and is composed of a pinion gear 27 and output side gears 29 and 31, block members 5 and 7 having a support part to slidingly support an addendum of the pinion gear 27 and an intermittent means 9 to intermit the block member 7 and the differential case 15, and differential restricting force is obtained by the cam action generated when torque acts on the support part of the block members 5 and 7.

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 "Automotive Engineering June 1997 9
2, 93 "describes a differential device 203 as shown in FIG. 10 and FIG. 11, and JP-A-9-14394 describes a differential device 205 as shown in FIG. 12 and FIG.

Each of the differential devices 203 and 205 shown in FIGS. 10 and 11 and FIGS.
9, 251 and a pair of block members 253, 253, which are axially movably engaged with the differential cases 249, 251.
255 and 255, and the concave toothed surfaces 261 and 259 provided on the support concave curved surfaces 257 and 259 provided on the respective block members 253 and 255.
63 is supported slidably and rotatably and floatingly supported, and a pinion gear 26
5267, each pair of output side gears 26
9, 271, 273, 275 and each block member 25
3, 255, and the like.

[0004] Each block member 253, 255 is provided with bearing recesses 281, 283 for slidably supporting the tooth tips of the side gears 269, 271, 273, 275. Each of the differential cases 249 and 251 is provided with concave surfaces 289 and 291 for slidably supporting the back portions 285 and 287 of the pinion gears 265 and 267.

[0005] The rotation of the differential cases 249 and 251 is performed by the block members 253 and 255 from the pinion gears 265 and 267.
Are distributed to the side gears 269, 271, 273, and 275 through the differential gears.
Is differentially distributed from the side gears 269, 271, 273, 275 to the respective wheels by the rotation of the pinion gears 265, 267.

Thus, each of the pinion gears 265, 267
When the gears rotate differentially, friction torque is generated between the tooth top surfaces 261 and 263 of the pinion gears 265 and 267 and the concave concave curved surfaces 257 and 259 of each of the block members 253 and 255. Tip surfaces 261 and 263 and concave concave curved surfaces 257 and 259
Is significantly larger than the radius of the normal sliding portion between the pinion shaft and the pinion gear, so that a large differential limiting force can be obtained by these friction torques.

Further, the pinion gears 265 and 267 move on the concave bearing curved surfaces 257 and 259 by the cam action of the concave bearing curved surfaces 257 and 259 having the cam angles 293 and 295, respectively.
The back portions 285 and 287 of the pinion gears 265 and 267 and the concave surfaces 289 and 291 of the differential cases 249 and 251 come into contact with each other to generate friction torque, thereby obtaining a differential limiting force.

Further, the pinion gear 26 receiving the rotational torque
5, 267 are moved to one side of the side gears 269, 271, 273, 275 by the frictional force with the concave bearing curved surfaces 257, 259, and the respective gears have zero or negative backlash due to the wedge action. The differential limiting force is obtained by the meshing and increasing friction torque at each tooth surface.

Further, the urging force of the disc springs 277 and 279 for pressing the side gears 269, 271, 273 and 275 via the respective block members 253 and 255 and the respective side gears 26
9, 271, 273, 275, and the differential cases 249, 251 and each side gear 26
9, 271, 273 and 275 generate a friction torque to obtain a differential limiting force.

As described above, the differential cases 249, 2
51 is transmitted from the block members 253 and 255 to the pinion gears 265 and 267, the pinion gear 2
65, 267 bearing concave surface generated by being pressed by
By the cam action of 59, the bearing recesses 281 and 283 of the block members 253 and 255 are moved to the side gears 269 and 271,
The frictional torque is generated by being pressed by 273 and 275, and a differential limiting force is obtained.

[0011] The large differential limiting force obtained in this way improves the running performance and escape performance of the vehicle on a rough road or the like.

[0012]

In a part-time four-wheel drive vehicle, it is necessary to disconnect the front-wheel or rear-wheel differential device by intermittent means during two-wheel drive.

Each of the above differential devices 203, 2
Since the connecting / disconnecting means 05 does not incorporate the connecting / disconnecting means, the connecting / disconnecting means must be provided outside the differential devices 203 and 205 in the power transmission system.

However, if the intermittent means is provided outside the differential device, the structure of the power transmission device becomes complicated, and the intermittent means may interfere with peripheral members, and the location of the intermittent means is restricted.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a differential device having an intermittent means which can be separated with a simple structure while obtaining a large differential limiting force by a cam action generated on a block member supporting a pinion gear. .

[0016]

According to a first aspect of the present invention, there is provided a differential device comprising: a differential case rotatably driven by a driving force of an engine; a bevel gear type differential mechanism comprising a pinion gear and a pair of output side gears meshed with the pinion gear; A block member rotatably disposed with respect to the differential case and having a concave support portion for slidably supporting the tooth tip of the pinion gear; and a connecting and disconnecting means for connecting and disconnecting the block member and the differential case. It is characterized in that a differential limiting force is obtained by a cam action generated by a torque acting on a bearing portion of the member.

The rotation of the differential case is transmitted from the intermittent means to the pinion gear via the block member, and is distributed from each output side gear to the wheels.

Further, when the pinion gear is differentially rotated, a friction torque is generated between the tip of the pinion gear and the bearing of the block member. This friction torque is strengthened by the cam action generated by the reaction force of the pinion gear in the bearing recess of the block member having the cam angle, and the radius of the sliding portion between the tooth tip of the pinion gear and the bearing recess is large. A large differential limiting force is obtained by the torque.

Further, the pinion gear moves on the support portion by the cam action of the support portion, and the back portion of the pinion gear comes into contact with the differential case side or the block member to generate a friction torque, thereby obtaining a differential limiting force.

The pinion gear which has received the rotational torque moves to one side gear due to friction with the bearing, and the pinion gear and the side gear mesh with zero or negative backlash due to wedge action, and are generated at the respective tooth surfaces. The resulting friction torque provides a differential limiting force.

Further, a friction torque is generated between each side gear and the differential case due to the meshing thrust force, and a differential limiting force is obtained.

The large differential limiting force obtained in this way greatly improves the controllability and stability of the vehicle.

In addition, the connecting / disconnecting means for connecting / disconnecting the driving force is arranged between the block member and the differential case, so that the connecting / disconnecting means is incorporated in the differential case.

Therefore, the structure of the power transmission device is simplified and the problem of the interrupting means interfering with the peripheral members is eliminated as compared with the configuration in which the interrupting means is provided outside the differential device.

Further, since the block member is used as one side member of the interrupting means, the structure of the interrupting means can be simplified accordingly.

In addition, since the block member is used as one side member of the intermittent means and no special differential limiting mechanism is used, the differential device has a simple structure, a small size,
Lightweight and low cost.

Further, if the block member is provided with a friction portion that comes into contact with the back portion of the pinion gear to obtain a differential limiting force, it is not necessary to provide the friction portion in the differential case, and the compatibility of the differential case is improved accordingly.

According to a second aspect of the present invention, in the differential device according to the first aspect, the block member is divided and provided on each side gear side, so that each of the block members is formed by the cam action generated in the support portion. It is characterized in that a differential limiting force is generated by being pressed by the side gear,
An effect equivalent to that of the configuration of claim 1 is obtained.

In addition, since the block member is divided and provided on each side gear side, when the rotation of the differential case is transmitted from each block member to the pinion gear, the support portion of each block member presses the pinion gear and is generated. By the cam action, the block members are pressed against the respective side gears to generate friction torque, and the differential limiting force is strengthened.

According to a third aspect of the present invention, there is provided the differential device according to the first aspect, wherein the block member is formed integrally, and an effect equivalent to that of the first aspect is obtained.

Also, since the block member is formed integrally,
As a result, the number of parts is reduced and the cost is reduced.

According to a fourth aspect of the present invention, there is provided the differential device according to any one of the first to third aspects, wherein the intermittent means is a meshing clutch having meshing teeth formed in the axial direction. As a feature, an effect equivalent to any one of claims 1 to 3 is obtained.

In addition, since the connecting / disconnecting means is a meshing clutch and the meshing teeth are formed in the axial direction, the diameter of the connecting / disconnecting means is reduced, so that the diameter of the differential device can be reduced accordingly.

According to a fifth aspect of the present invention, there is provided the differential device according to any one of the first to fourth aspects, wherein a ring member is rotatably arranged inside the differential case, and the block member is connected to the ring member. In addition to being connected to the member, the intermittent means is arranged between the differential case and the ring member, and the same effect as any one of claims 1 to 4 is obtained.

In addition, by providing the intermittent means between the differential case and the ring member, the meshing teeth of the intermittent means are formed in the axial direction. It becomes easy to do.

Further, since a friction portion for obtaining a differential limiting force by contacting the back portion of the pinion gear can be formed on the ring member, there is no need to provide the friction portion in the differential case, and the compatibility of the differential case is improved.

[0037]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIGS. This embodiment has the features of the first and second aspects. FIG. 1 shows a differential device 1 of this embodiment, and the left and right directions are the left and right directions in FIGS. 1 and 2. In addition, members that are not given reference numerals are not shown.

In a four-wheel drive vehicle, the differential device 1 is disposed on a wheel side that is separated from an engine side during two-wheel drive travel.

The differential device 1 comprises a bevel gear type differential mechanism 3, a pair of block members 5, 7, a meshing clutch 9 (intermittent means), an actuator 11 of the meshing clutch 9, a coil spring 13, and the like.

The differential device 1 is arranged inside a differential carrier provided with an oil reservoir, and a differential case 15 is formed by fixing a casing body 17 and a cover 19 with bolts 21. Casing body 1
Bosses 23 and 25 are provided on the cover 7 and the cover 19, and the differential case 15 is rotatably supported on the differential carrier by bearings at the bosses 23 and 25. The differential case 15 is driven to rotate by the driving force of the engine.

The bevel gear type differential mechanism 3 includes a plurality of pinion gears 27 and a pair of output side gears 29 and 31 meshing with the respective pinion gears 27 from the left and right.

The side gears 29, 31 are supported by the support portions 37, 39 of the differential case 15 via the respective boss portions 33, 35.
It is supported rotatably. The boss 33 of the left side gear 29 is splined to the axle of the left wheel, and the boss 35 of the right side gear 31 is splined to the axle of the right wheel.

Each of the side gears 29 and 31 and the differential case 15
A thrust washer 41 is disposed between the two. A radial oil groove 43 is provided on the thrust washer 41 side of the differential case 15 to lubricate the sliding surface of the thrust washer 41 with oil.

Each of the block members 5, 7 is rotatably arranged on the inner periphery of the differential case 15. As shown in FIGS. 2 and 3, bearing recesses 47, 47 having cam angles 45, 45 are formed on each of the block members 5, 7 by lathe processing. It is slidably and rotatably supported, and is floating supported inside each bearing recess 47.

The block members 5 and 7 are provided with a sliding portion 53 which comes into contact with the back 51 of the pinion gear 27.

Further, the block members 5 and 7 are provided with sliding portions 55 which come into contact with the side gears 29 and 31, respectively.

The side gears 29 and 31 are pinion gears 27.
It is supported from the outside by meshing with. The pinion gear 27 is supported from the inside by meshing with the side gears 29 and 31, and the back portion 51 is supported from the outside by the sliding portion 53 of the block members 5 and 7.

The dog clutch 9 is provided between the right block member 7 and the operation member 57.

As shown in FIG. 3, the block member 7 is provided with radial meshing teeth 59, and the operating member 57 is provided with meshing teeth 61 which can be disengaged therefrom. The operation member 57 includes a ring 63 provided with the meshing teeth 61, and an arm 67 integrally formed with the ring 63 and penetrating from an opening 65 of the differential case 15.

Actuator 11 of dog clutch 9
Is formed in a ring shape, is disposed on the outer periphery of the boss portion 25 of the differential case 15, and is fixed to the vehicle body side. Air pressure is sent to the actuator 11 from an air pump via an air hose 69.

The coil spring 13 is disposed between the retainers 71 and 73, and the retainer 73 is
Is fixed to the operation member 57. The relative rotation between the differential case 15 and the actuator 11 is controlled by the retainer 73.
And the pressing member 75 of the actuator 11 slides.

When the air pressure is sent to the actuator 11, the operating member 57 is moved to the left while the coil spring 13 is flexed, the meshing teeth 59 and 61 mesh, and the meshing clutch 9 is connected. When the supply of air pressure is stopped, the operating member 5 is actuated by the urging force of the coil spring 13.
7 returns to the right, and the connection of the dog clutch 9 is released.

When the dog clutch 9 is engaged, the driving torque of the engine for rotating the differential case 15 is as shown in FIG.
As shown by white arrows in FIG. 2, each pinion gear 2 is moved from the dog clutch 9 via the block members 5 and 7.
7 to revolve each pinion gear 27. The revolution of each pinion gear 27 is distributed to the left and right wheels via side gears 29 and 31.

When a difference in driving resistance occurs between the wheels, the pinion gear 27 rotates and the engine driving torque is differentially distributed to the left and right sides.

At this time, when the pinion gear 27 is differentially rotated (rotated), a friction torque is generated between the tooth tip 49 and the bearing concave portions 47 of the block members 5 and 7. This friction torque is applied to the bearing recess 47 receiving the reaction force of the pinion gear 27.
Is enhanced by the cam angle 45. Further, since the radius of the sliding portion between the tooth tip 49 and the bearing recess 47 is large, a large differential limiting force can be obtained by this friction torque.

As described above, when the bearing recesses 47 of the block members 5 and 7 press the pinion gear 27 during torque transmission, the pinion gear 27 moves radially outward due to the cam action of the cam angle 45 of the bearing recess 47. Its back 51
Contacts the sliding portion 53 of the block members 5 and 7. Furthermore,
A centrifugal force of the pinion gear 27 and a counter reaction force act on the sliding portion 53. Thus, the differential limiting force is obtained by the large friction torque generated in the sliding portion 53.

Further, the pinion gear 27 receiving the rotation torque
Is moved to one side of the side gears 29, 31 by friction with the bearing recesses 47 of the block members 5, 7, and these gears mesh with zero or negative backlash due to wedge action, and the friction generated on each tooth surface The torque provides the differential limiting force.

Further, the side gears 29, 31 and the differential case 1 are connected by the meshing thrust force of the side gears 29, 31.
5, a friction torque is generated, and a differential limiting force is obtained.

The block members 5 and 7 are connected to each side gear 2.
9 and 31, the drive torque is transmitted from the block members 5 and 7 to the pinion gear 27.
By the cam angle 75 of each bearing recess 47, the block member 5,
7 presses the side gears 29 and 31, respectively, to generate a friction torque, and a differential limiting force is obtained.

The large differential limiting force thus obtained greatly improves the controllability and stability of the vehicle.

When the connection of the dog clutch 9 is released, the torque is cut off between the differential case 15 and the block members 5, 7, the differential device 1 is disconnected from the engine side, and the vehicle is brought into a two-wheel drive running state. Become.

Openings 65 and 76 are provided in the differential case 15, and spiral oil grooves are provided on the inner periphery of each of the bosses 23 and 25. The oil in the oil sump flows into and out of the differential case 15 through these openings 65 and 76 and the oil groove, and sufficiently lubricates the above-mentioned sliding portions to enhance durability. Thus, the differential device 1 is configured.

In the differential device 1, the tooth tips 49 of the pinion gear 27 are formed by the support recesses 47 of the block members 5 and 7.
Is slidably supported, and the rotation of the differential case 15 is transmitted to the differential mechanism 3 through these block members 5 and 7, so that the torque is generated at each part of the torque transmission path as described above. By the friction torque, a large differential limiting force can be obtained without using a special differential limiting mechanism, thereby greatly improving the controllability and stability of the vehicle.

In addition, the meshing clutch 9 for separating the differential device 1 is disposed between the block member 7 and the operation member 57 on the side of the differential case 15 so as to be built in the differential case 15.

Therefore, as compared with a configuration in which the connecting / disconnecting means is provided outside the differential device, the structure of the power transmission device is simplified, and the problem of the connecting / disconnecting means interfering with peripheral members is eliminated.

Further, the pinion gear 2 is attached to the block members 5 and 7.
Since the friction portion 53 that comes into contact with the back portion 51 is provided, it is not necessary to provide such a friction portion in the differential case 15, and the compatibility of the differential case 15 is improved accordingly.

Further, the block member 7 is engaged with the
The structure of the dog clutch 9 is simpler.

As described above, no special differential limiting mechanism is used, and the block member 7 is engaged with the clutch 9
Used for one side member of the differential device 1
Has a simple structure, small size, light weight and low cost.

Next, a second embodiment of the present invention will be described with reference to FIG. This embodiment has the features of the first and second aspects. FIG. 4 shows a main part of the differential device of this embodiment. In addition, members that are not given reference numerals are not shown.

In the description of FIG. 4 and the second embodiment, members having the same functions as those of the differential device 1 of the first embodiment will be given the same reference numerals and will be omitted, and redundant description of these same members will be omitted.

In the differential device of the second embodiment, notches 77, 77 are formed on the opposing portions of the block members 5, 7, respectively.

The cam angle 75 formed in the bearing recess 47 of the block members 5 and 7 corresponds to the reaction force direction 79 of the pinion gear 27.
On the other hand, it becomes smaller on the side of the facing portion.

As described above, since the notch 77 is provided at the opposing portion of the block members 5 and 7 having the small cam angle 75, the pinion gear 27 is pressed by the large portion of the bearing recess 47 where the cam angle 75 is large. .

Accordingly, with the differential rotation of the pinion gear 27, the friction torque generated between the tooth tip 49 and each bearing recess 47 and strengthened by the cam angle 75 further increases, and the differential limiting force is increased. You.

Next, a third embodiment of the present invention will be described with reference to FIGS.
An embodiment will be described. This embodiment has the features of claims 1 and 3. FIG. 5 shows a differential device 81 of this embodiment. The left and right directions are the left and right directions in FIGS. In addition, members that are not given reference numerals are not shown.

In FIGS. 5 to 7 and the description of the third embodiment, the same reference numerals are given to members having the same functions as those of the differential devices of the first and second embodiments, and the same functional members are described again. Description is omitted.

The differential device 81 includes a bevel gear type differential mechanism 3, an integral block member 83, a meshing clutch 9, an actuator 11, a coil spring 13, and the like.

The block member 83 is rotatably arranged on the inner periphery of the differential case 15. As shown in FIG. 7, a support recess 85 having cam angles 45 and 45 is formed on the block member 83 by lathing, and the pinion gear 27 has a tooth tip 49 thereof.
Is slidably and rotatably supported by the bearing recess 85, and the bearing recess 8 is provided.
5 is floating supported inside.

A spherical washer 87 is disposed between the pinion gear 27 and the differential case 15, and the spherical washer 87 is provided with a sliding portion 89 that comes into contact with the back 51 of the pinion gear 27.

The sliding portion 89 may be provided on the inner periphery of the differential case 15 without using the spherical washer 87.

The pinion gear 27 has side gears 29 and 31.
And the back portion 51 is supported from the outside by the sliding portion 89 of the spherical washer 87.

The dog clutch 9 is provided between the block member 83 and the operation member 57. As shown in FIG.
The block member 83 is provided with radial meshing teeth 91, and the operating member 57 is provided with meshing teeth 61 that can mesh with this.

The arrow 93 in FIG. 6 indicates the direction of rotation of the differential case 15 (block member 83) when the vehicle travels forward (drives).
5, a notch 95 is formed at a central portion in the axial direction at a position where the pinion gear 27 contacts the pinion gear 27 when traveling forward.

Since the cam angle 75 formed in the support recess 85 becomes smaller toward the center in the axial direction, the notch 95 is provided at the center where the cam angle 75 is smaller, so that the pinion gear 27 The large portion of the corner 75 is pressed.

The arrow 97 in FIG. 6 indicates the differential case 15 (the block member 8) when the vehicle travels backward (coast).
Although the rotation direction of 3) is shown, a notch is not formed at a position where it contacts the pinion gear 27 when the vehicle travels backward.

Thus, the differential device 81 is configured.

In the differential device 81, similar to the differential devices of the first and second embodiments,
Due to the differential rotation of the pinion gear 27, a friction torque is generated between the tooth tip 49 and the bearing recess 85 of the block member 83. This friction torque is strengthened by the cam angle 75 of the bearing recess 85, and Since the radius of the sliding portion between the bearing and the bearing recess 85 is large, a large differential limiting force can be obtained by this friction torque.

Further, the back portion 51 of the pinion gear 27 is moved by the spherical washer 8 by the cam action of the cam angle 45 of the support recess 85.
7 comes into contact with the sliding portion 89. Further, the centrifugal force of the pinion gear 27 and the meshing reaction force act on the sliding portion 89. Thus, a differential limiting force is obtained by the friction torque generated in the sliding portion 89.

Further, the pinion gear 27 receiving the rotational torque
Is moved to one side of the side gears 29 and 31 by friction with the bearing recess 85 of the block member 83, and these gears mesh with zero or negative backlash due to wedge action, and the friction torque generated on each tooth surface causes A differential limiting force is obtained.

The side gears 29 and 31 and the differential case 1 are connected to each other by the engagement thrust force of the side gears 29 and 31.
5, a friction torque is generated, and a differential limiting force is obtained.

[0091] The large differential limiting force thus obtained greatly improves the controllability and stability of the vehicle.

Further, since the notch 95 is provided in the supporting recess 85 which contacts the pinion gear 27 during forward running to increase the cam angle 75, as described above, there is generated between the tooth tip 49 of the pinion gear 27 and each supporting recess 85. The friction torque strengthened by the cam angle 75 is further increased, and the differential limiting force is increased.

Therefore, when the vehicle is traveling forward, the enhanced differential limiting force greatly improves the running performance and the escape performance on rough roads and the like.

Further, since there is no notch provided at the position where the pinion gear 27 contacts the reverse traveling, the braking force in which the torque direction is the same as that of the reverse traveling becomes small, so that the differential limiting force becomes small. B. Interference with S (anti-lock brake system) is prevented.

In order to change the differential limiting force between forward traveling and reverse traveling, the pinion pin 225 and the differential case 20 are used.
Unlike the conventional examples of FIGS. 10 to 13 which require the pin receiving hole 227 of FIG. 7, this is not performed, and only the notch 95 is provided in the block member 83 to perform forward traveling and reverse traveling. The differential device 81 capable of changing the differential limiting force has a small number of components, a simple structure, and low cost.

Since the block member 83 is integrated,
As a result, the number of parts is reduced and the cost is reduced.

In addition to this, the differential device 81
Is formed between the block member 83 and the operation member 57 on the differential case 15 side so as to be incorporated in the differential case 15, so that the power transmission can be performed as compared with the configuration in which the intermittent means is provided outside the differential device. The structure of the device is simplified, and the problem that the interrupting means interferes with the peripheral member is relieved.

Also, the pinion gear 27 is attached to the spherical washer 87.
Since the friction portion 89 that comes into contact with the back portion 51 is provided, it is not necessary to provide such a friction portion in the differential case 15,
The compatibility of the differential case 15 is improved accordingly.

Further, since the block member 83 is used as one side member of the dog clutch 9, the structure of the dog clutch 9 is simplified accordingly.

In addition, since the block member 83 is used as one side member of the dog clutch 9 and no special differential limiting mechanism is used, the differential device 81
Has a simple structure, small size, light weight and low cost.

Next, a fourth embodiment of the present invention will be described with reference to FIGS. This embodiment has the features of the first and second aspects. FIG. 8 shows a differential device 99 of this embodiment. The left and right directions are the left and right directions in FIG. In addition, members that are not given reference numerals are not shown.

In FIGS. 8 and 9 and the description of the fourth embodiment, members having the same functions as those of the differential devices of the first, second and third embodiments are given the same reference numerals and are quoted. Duplicate explanations are omitted.

The differential device 99 includes the bevel gear type differential mechanism 3, a ring member 101, a pair of block members 103 and 105, a meshing clutch 107 and the like.

The ring member 101 is rotatably arranged on the inner periphery of the differential case 15.

As shown in FIG. 9, each block member 103, 1
Reference numeral 05 is connected to the ring member 101 via a connecting portion 109 in the rotational direction, and is movable in the axial direction.

The block members 103 and 105 have a cam angle of 4
Each of the bearing recesses 111 having five and 45 is lathe-processed, and the pinion gear 27 has its tip 49 slidably and rotatably supported in each bearing recess 111.
Floating inside is supported.

The block members 103 and 105 are provided with sliding portions 113 that come into contact with the side gears 29 and 31, respectively.

A sliding portion 115 is provided on the inner periphery of the ring member 101 to be in contact with the back portion 51 of the pinion gear 27.

The pinion gear 27 has side gears 29 and 31.
, And the back portion 51 is supported from the outside by the sliding portion 115 of the ring member 101.

The meshing clutch 107 is connected to the ring member 10.
1 and an operation member 117.

As shown in FIG. 8, the ring member 101 is provided with a small-diameter portion 119 protruding to the right, and the outer periphery of the small-diameter portion 119 is formed with an axial meshing tooth 121. The operation member 117 includes a ring 123 arranged on the outer periphery of the differential case 15 so as to be movable in the axial direction, and an arm 127 protruding inward from the ring 123 and penetrating through the opening 125 of the differential case 15. The arm 127 is provided with a meshing tooth 129 that can be disengaged from the meshing tooth 121.

The operating member 117 is provided on the peripheral groove 13 of the ring 123.
8 is connected to the ring member 101 by the meshing clutch 107 as shown in the upper half of FIG. 8, and is connected to the ring member 101 as shown in the lower half of FIG. The connection is released.

When the dog clutch 107 is engaged,
The driving torque of the engine that rotates the differential case 15 is
As shown by arrows in FIG. 8, the transmission is transmitted from the dog clutch 107 to the differential mechanism 3 via the ring member 101 and the block members 103 and 105, and is distributed to the left and right wheels. When a difference in drive resistance occurs between the wheels, the pinion gear 27 rotates, and the drive torque of the engine is differentially distributed to the left and right sides.

When the pinion gear 27 rotates, a friction torque is generated between the tooth tip 49 and the bearing recesses 111 of the block members 103 and 105, and the friction torque is strengthened by the cam angle 45 of the bearing recess 111. Tooth tip 4
Since the sliding portion radius between the bearing 9 and the bearing recess 111 is large, a large differential limiting force can be obtained by this friction torque.

Also, the back portion 51 of the pinion gear 27 is moved by the cam action of the cam angle 45 of the
No. 01 comes into contact with the sliding portion 115, and further, the sliding portion 115 is engaged with the centrifugal force of the pinion gear 27 and acts as a reaction force. Thus, a differential limiting force is obtained by the friction torque generated in the sliding portion 115.

Further, the pinion gear 27 receiving the rotational torque
Are side gears 29, 3 due to friction with the bearing recess 111.
1 and these gears mesh with zero or negative backlash due to wedge action, and a differential limiting force is obtained by friction torque generated on each tooth surface.

Further, the side gears 29 and 31 are connected to the differential case 1 by the meshing thrust force of the side gears 29 and 31.
5, a friction torque is generated, and a differential limiting force is obtained.

In addition to this, the block members 103, 10
5 is provided on the side gears 29 and 31 side,
The block members 103 and 105 respectively press the side gears 29 and 31 by the cam action of the cam angle 75 of each bearing recess 111 to generate friction torque, thereby obtaining a differential limiting force.

[0119] The large differential limiting force obtained in this way greatly improves the maneuverability and stability of the vehicle.

When the connection of the dog clutch 107 is released, the torque is cut off between the differential case 15 and the ring member 101, the differential device 99 is disconnected from the engine side, and the vehicle enters a two-wheel drive running state.

The openings 76 and 125 are provided in the differential case 15.
Also, the oil in the oil pool flows out and in from the oil grooves on the inner periphery of the bosses 23 and 25, and the above sliding portions are sufficiently lubricated to enhance the durability.

Thus, the differential device 99 is configured.

In the differential device 99, the pinion gear 2 is formed by the support recesses 111 of the block members 103 and 105.
7 is slidably supported, and the rotation of the differential case 15 is transmitted to the differential mechanism 3 through these block members 103 and 105. As a result, the friction torque generated in each part as described above allows A large differential limiting force can be obtained without using a special differential limiting mechanism, thereby greatly improving the controllability and stability of the vehicle.

In addition to this, the differential device 99
The engagement clutch 107 for disconnecting the
1 and the operation member 117 on the differential case 15 side, so that it was built in the differential case 15.

Therefore, the structure of the power transmission device is simplified and the problem of the intermittent means interfering with the peripheral members is eliminated as compared with the configuration in which the intermittent means is provided outside the differential device.

Since the meshing clutch 107 is reduced in diameter by forming the meshing teeth 121 and 129 of the meshing clutch 107 in the axial direction, the diameter of the differential device 99 can be reduced accordingly.

Further, by disposing the meshing clutch 107 between the differential case 15 and the ring member 101, the meshing teeth 121 and 129 are formed in the axial direction as described above, so that the diameter of the differential device 99 can be easily reduced. become.

Also, the pinion gear 27 is attached to the ring member 101.
Since the friction portion 115 that comes into contact with the back portion 51 is provided, it is not necessary to provide such a friction portion in the differential case 15, and the compatibility of the differential case 15 is improved accordingly.

Also, since the ring member 101 is used as one side member of the meshing clutch 107, the meshing clutch 1
07 becomes simpler.

In addition, since the ring member 101 is used as one side member of the dog clutch 107 and no special differential limiting mechanism is used, the differential device 9 can be used.
9 is simple in structure, small in size, light in weight, and low in cost.

[0131]

According to the present invention, the pinion gear is slidably supported by the support recess of the block member, and the rotation of the differential case is transmitted to the differential mechanism via the block member. By the friction torque generated in each part, a large differential limiting force can be obtained without using a special differential limiting mechanism, thereby greatly improving the controllability and stability of the vehicle.

In addition, the intermittent means for separating the differential device is disposed between the block member and the differential case, so that the intermittent means is built in the differential case.
Compared to a configuration in which the interrupting means is provided outside the differential device, the structure of the power transmission device is simplified, and the problem that the interrupting means interferes with peripheral members is eliminated.

Further, since the block member is used as one side member of the interrupting means, the structure of the interrupting means can be simplified accordingly.

In addition, since the block member is used as one side member of the intermittent means and no special differential limiting mechanism is used, the differential device has a simple structure, a small size,
Lightweight and low cost.

If the block member is provided with a friction portion for obtaining a differential limiting force by contacting the back of the pinion gear, it is not necessary to provide the friction portion in the differential case, and the compatibility of the differential case is improved accordingly.

According to the second aspect of the invention, the same effect as that of the first aspect is obtained, and since the block member is divided and provided on each side gear side, the bearing of each block member presses the pinion gear. The resulting cam action
The block members are pressed against the respective side gears to generate friction torque, and the differential limiting force is strengthened.

According to the third aspect of the present invention, the same effect as that of the first aspect is obtained, and since the block member is formed integrally, the number of parts is reduced and the cost is reduced.

According to the fourth aspect of the present invention, the same effect as any one of the first to third aspects is obtained, and the connecting / disconnecting means has a small diameter by forming the engaging teeth of the engaging clutch which is the connecting / disconnecting means in the axial direction. Therefore, the diameter of the differential device can be reduced accordingly.

According to the fifth aspect of the present invention, the same effect as any of the first to fourth aspects is obtained, and the intermittent means is arranged between the differential case and the ring member. Since the meshing teeth of the intermittent means are formed in the axial direction, it is easy to reduce the diameter of the differential device.

Further, since a friction portion for obtaining a differential limiting force by contacting the back of the pinion gear can be formed on the ring member, it is not necessary to provide the friction portion in the differential case, and the compatibility of the differential case is improved accordingly.

[Brief description of the drawings]

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

FIG. 2 is a view taken in the direction of arrow A in FIG. 1;

FIG. 3 is a view taken in the direction of arrow B in FIG. 1;

FIG. 4 is a view showing a main part of a second embodiment.

FIG. 5 is a sectional view showing a third embodiment.

FIG. 6 is a view showing a main part of a third embodiment.

FIG. 7 is a view showing another main part of the third embodiment.

FIG. 8 is a sectional view showing a fourth embodiment.

FIG. 9 is a view showing a main part of a fourth embodiment.

FIG. 10 is a longitudinal sectional view of a first conventional example.

FIG. 11 is a sectional view of a main part of a first conventional example.

FIG. 12 is a longitudinal sectional view of a second conventional example.

FIG. 13 is a transverse sectional view of a second conventional example.

[Explanation of symbols]

1, 81, 99 differential device 3 bevel gear type differential mechanism 5, 7, 103, 105 divided block member 9 meshing clutch (intermittent means) 15 differential case 27 pinion gear 29, 31 output side gear 45, 75 cam angle 47, 85 , 111 Support recess (support portion) of the block member that supports the pinion gear 49 Tip of the pinion gear 77, 95 Notch of the block member 83 Integrated block member 101 Ring member 107 Mesh clutch (meshing means) with meshing teeth formed in the axial direction )

Claims (5)

[Claims] 1. A differential case, which is rotatably driven by the driving force of an engine, a bevel gear type differential mechanism including a pinion gear and a pair of output side gears meshed with the pinion gear, and is rotatably disposed with respect to the differential case. A cam member having a block member having a concave bearing portion for slidably supporting the tooth tip of the pinion gear; and a connecting / disconnecting means for connecting and disconnecting the block member and the differential case; A differential device wherein a differential limiting force is obtained by using 2. The invention according to claim 1, wherein the block member is divided and provided on each side gear side, so that each block member is pressed by the respective side gear by the cam action generated in the support portion, and the differential is provided. A differential device wherein a limiting force is generated. 3. The differential device according to claim 1, wherein the block member is formed integrally. 4. The differential device according to claim 1, wherein the connecting / disconnecting means is a meshing clutch having meshing teeth formed in an axial direction. 5. The invention according to claim 1, wherein a ring member is rotatably arranged inside the differential case, the block member is connected to the ring member, and the ring member is intermittently connected. The differential device, wherein the means is disposed between the differential case and the ring member.