JPH09196145A - Differential gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize the interchangeability of an output shaft by simplifying a connection structure of a side gear to a differential limit device. SOLUTION: A differential gear is provided with a differential mechanism 87, and a differential limit device 39 which comprises a housing 41 and a hub 43, is arranged between a pair of side gears 49, 51, and limits the difference according to the differential rotational speed. The housing 41 is provided with a spline part 65 to be connected to one output shaft on one side, and connected to the side gear 49, the hub 43 is connected to the side gear 51 having a spline part 67 to be connected to an output shaft on the other side through a dog clutch mechanism 93, and the dog clutch mechanism 93 is arranged on the side of larger diameter than that of the spline parts 65, 67.

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 Japanese Unexamined Patent Publication No. 6-33996 discloses a differential device 201 as shown in FIG. This differential device 201 includes a differential case 203.
A helical pinion gear 205, another helical pinion gear meshing with the helical pinion gear 205, output side helical side gears 207 and 209, and a speed-sensitive differential limiting device 21.
1 is provided. The helical pinion gear 205 is slidably rotatably housed in the housing hole 213 of the differential case 203, and the other helical pinion gear is slidably rotatably housed in the other housing hole. Helical side gear 20
7, 209 are connected via respective helical pinion gears, the housing 215 of the differential limiting device 211 is connected to the helical side gear 207, and the hub 217 is connected to the helical side gear 209.

The driving force of the engine rotates the differential case 203 and is transmitted to the wheel side through the helical side gears 207 and 209 from the respective helical pinion gears.

During transmission of torque, frictional resistance is generated between the gears and between the gears and the differential case 203 or the housing 215 due to the meshing reaction force and the meshing thrust force of the gears. It has a torque sensitive differential limiting force. In addition to this, the differential limiting device 211 is provided between the helical side gears 207 and 209.
Causes a speed-sensitive differential limiting force. That is,
Due to the synergistic effect of the torque-sensitive differential limiting force and the speed-sensitive differential limiting force, the driving force to the wheels is accurately transmitted regardless of the road surface condition, and high running stability is maintained.

[0005]

However, in the conventional differential device 201 as described above, the hub 217 of the differential limiting device 211 and the right helical side gear 2 are provided.
09 is connected to the hub 217 by a gap 22 between the left helical side gear 207 and the hub portion 219 of the housing 215.
1 is provided with an extension portion 223 penetrating to the right, an inward bending portion 225 is formed at the right end portion thereof, and a connecting portion 227 extending rightward is formed at the bending portion 225, and the connecting portion 227 is connected to the right helical side gear. 209 is spline-connected to the left end of the hub portion 220.

However, in such a connecting method, an extra space is required to secure the spline portion for connecting, and a bending load is applied to the bent portion 225 during torque transmission. It was necessary to increase the wall thickness, and the axial space X of the connecting portion was large.

For this reason, for example, when the bent portion 225 is moved to the left (housing 215 side), the spline length of the spline portion 229 on the left helical side gear 207 side becomes smaller than the normal length, so that the special length is increased. Becomes an axle and loses compatibility. That is, it is necessary to manufacture an axle different from an ordinary differential device that does not have a differential limiting function, resulting in high cost and complicated parts management.

Further, when the differential device of FIG. 3 is provided with thrust blocks for positioning the left and right axles, the outer diameter of the thrust blocks is the splines 229, 231 on the side of the left and right helical side gears 207, 209.
Since the diameter is smaller than the small diameter, it is difficult to position and easily fall off during parts transfer.

Therefore, an object of the present invention is to provide a differential device which simplifies the connecting structure of the side gear and the differential limiting device and enables the compatibility of the output shafts.

[0010]

In order to solve the above-mentioned problems, a differential device according to a first aspect of the present invention comprises a differential mechanism for distributing the driving force of an engine to each output shaft through a pair of output side gears. A differential limiting device configured to include a side member and another side member and arranged between the pair of side gears to limit a differential according to a differential rotation speed, and one side member of the differential limiting device, An output-side connecting portion that has an output-side connecting portion that is connected to the one-side output shaft and that is connected to one of the pair of side gears, and that the other-side member of the differential limiting device is connected to the other-side output shaft. A differential device connected to the other of the pair of side gears via a differential limiting connecting portion, wherein the differential limiting connecting portion is arranged on a larger diameter side than each of the output side connecting portions. It is characterized by

Therefore, with this arrangement, the restriction from the differential limiting connection portion that affects the axial length setting of each output side connection portion on the small diameter side is greatly alleviated. That is, it is possible to reduce the axial space of the large diameter side limited differential connection portion, and as a result, the selection range of the length of each output side connection portion is expanded.
As a result, each output shaft connected to the output side connecting portion can maintain compatibility with that of another differential device.

Further, since the differential limiting connecting portion is arranged on the larger diameter side than the output side connecting portions, the thrust block is arranged so as not to drop in the space radially inward of the differential limiting connecting portion. It is also possible to do.

A differential device according to a second aspect of the present invention is the differential device according to the first aspect, characterized in that the differential limiting coupling portion is formed of a dog clutch mechanism.

Therefore, an operation equivalent to that of the differential device according to claim 1 can be obtained, and the dog clutch mechanism, which has a simple structure and is in butt mesh with each other, simply applies the transmission torque load to the other member of the differential limiting device. Therefore, it becomes easy to secure the wall thickness strength of the other side member.

Further, since the lubricating oil is supplied radially outward through the meshing clearance of the dog clutch mechanism, the lubricity of each meshing portion and sliding portion inside the differential device is improved.

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION A first embodiment of the present invention will be described with reference to FIG. FIG. 1 is a cross-sectional view of the differential device according to the first embodiment. The left and right directions are the left and right directions in FIG.

As shown in FIG. 1, the differential case 21 has a casing body 31, a cover 33, and a ring 35. The cover 33 is fixed to the casing body 31 with bolts, and the ring 35 is fixed to the casing body 31 with bolts 37. Has been done. The differential case 21 is rotatably arranged in a differential carrier (not shown), and an oil reservoir is formed in the differential carrier.

A differential rotation speed sensitive differential limiting device 39 is disposed inside the differential case 21. The differential limiting device 39 includes a housing 41 (one side member) and a hub 43 (the other side member), and a pressure chamber 45 is formed between them. The pressure chamber 45 has a differential rotation speed sensitive mechanism such as a generally used vane pump type or plunger pump type oil discharge resistance or a member shear resistance against viscous fluid. It is provided. A washer 47 is arranged between the housing 41 and the differential case 21 so as not to come into direct contact therewith.

A pair of left and right helical side gears 49, 51 are arranged inside the differential case 21. The left side gear 49 is a housing 41 of the differential limiting device 39.
It is integrated by welding. Inner peripheral portion 5 of housing 41
3 is provided with a spline portion (output side connecting portion) 65,
An unillustrated left (one side) output shaft is connected to this portion. On the other hand, an inner peripheral portion 55 of the right side gear 51 is provided with a spline portion 67 having the same size as the spline portion 65, and a right (other side) output shaft (not shown) is connected to this portion.

A plurality of sets of short storage holes 69 and long storage holes 71 are formed in the differential case 21 in the circumferential direction. A short helical pinion gear 73 is slidably and rotatably stored in the short storage hole 69, and a long helical pinion gear 75 is slidably and rotatably stored in the long storage hole 71. The short pinion gear 73 is axially positioned by the wall surface of the short storage hole 69 formed in the casing body 31 and the ring 35, and the long pinion gear 75 is axially positioned by the housing 41 and the ring 35.

The short pinion gear 73 is composed of first and second gear portions 77 and 79, and the first gear portion 77 meshes with the right side gear 51. Also, the long pinion gear 75
Is composed of first and second gear portions 81 and 83 and a small-diameter shaft portion 85 that connects them, the first gear portion 81 meshes with the left side gear 49, and the second gear portion 83 has a short pinion gear 73. Meshes with the second gear portion 79. In this way, the differential mechanism 87 is configured.

The hub 43 of the differential limiting device 39 is formed with an extension 89 passing between the inner peripheral portion 53 of the housing 41 and the left side gear 49. The right end of the extension 89 and the right side gear are formed. A dog clutch mechanism (differential limited coupling portion) 93 that meshes with each other is formed at the left end portion of 51. As shown in FIG. 1, the dog clutch mechanism 93 is provided radially outward (larger diameter side) than the root diameters b of the splines 65 and 67 of the housing 41 and the right side gear 51. Thus, the hub 43 of the differential limiting device 39 is connected to the right side gear 51, and the axial space occupied by the dog clutch mechanism 93 is in the range X in FIG.

A thrust block 95 is arranged in a space radially inward of the dog clutch mechanism 93, and both ends of the block 95 are opposed to the left and right output shafts. In addition,
Since the outer diameter a of the block 95 is larger than the inner diameters of the spline portions 65 and 67, there is no risk that the block 95 will fall out of the differential device. On the other hand, a thrust washer 91 is arranged radially outward of the dog clutch mechanism 93 between the side gears 49 and 51. A thrust washer 97 is arranged between the right side gear 51 and the differential case 21.

Next, the operation of this differential device will be described.

The driving force of the engine for rotating the differential case 21 is from the pinion gears 73 and 75 to the side gear 49.
It is distributed to the left and right output shafts via 51. Further, for example, when a driving resistance difference occurs between the left and right output shafts while traveling on a rough road, the driving force of the engine is differentially distributed to the left and right sides by the rotation of the pinion gears 73 and 75.

At this time, the tooth tips of the pinion gears 73 and 75 are pressed against the wall surfaces of the receiving holes 69 and 71 by the reaction force of engagement with the side gears 49 and 51 to generate frictional resistance, and the meshing thrust force of the helical gears causes the frictional resistance. Friction resistance is generated between the end faces of the pinion gears 73 and 75 and the differential case 21, the ring 35, the housing 41 of the differential limiting device 39, and the like, and a torque-sensitive differential limiting force is obtained by these frictional resistances. At the same time, the housing 41 and the hub 43 of the differential limiting device 39 rotate integrally with the left and right side gears 49 and 51, respectively, so that a rotational speed sensitive differential limiting force can be obtained.

Therefore, if this differential device is applied to the drive axle, the behavior of the vehicle body is stable and the maneuverability is improved due to the torque-sensitive differential limiting force when a large torque is applied such as when starting or accelerating. In addition, the speed-sensitive differential limiting force prevents one-wheel idling even under the condition that one of the drive axles spins on a bad road or the like, and sufficient escapeability and running performance are obtained.

In this way, according to the present embodiment, since the dog clutch mechanism 93 is a butt mesh with a simple structure, the axial space X occupied by the dog clutch mechanism 93 can be reduced, and the dog clutch mechanism 93 is arranged on the larger diameter side than the spline portions 65 and 67. Since the spline portions 65 and 67 can be selected in a wider range of lengths, the output shaft to be connected can be made common to that of other differential devices, and compatibility can be maintained.

Unlike the multi-stage bending structure of the conventional example, the butt joint structure simplifies how to apply a transmission torque load, so that it is easy to secure the wall thickness strength of the extension portion 89 of the hub 43.

Further, since the dog clutch mechanism 93 is arranged on the larger diameter side than the spline portions 65 and 67, the thrust block 95 can be easily arranged, and the arranged thrust block 95 does not fall off during transportation. .

Furthermore, since the lubricating oil is supplied radially outward through the meshing clearance of the dog clutch mechanism 93, the lubricity of each meshing portion and sliding portion inside the differential case 21 is improved.

Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 2 is a sectional view of this differential device.

Inside the differential case 101, a rotational speed-sensitive differential limiting device 103 and a multi-plate clutch 104 are arranged. The differential limiting device 103 includes a housing 105 (one side member) and a hub 107 (the other side member), and a pressure chamber 109 is formed between them. The pressure chamber 109 is provided with a speed-sensitive mechanism. Multi-plate clutch 104
Is the inner peripheral portion 111 of the housing 105 and the differential case 101.
It is provided between and. This provides a torque sensitive differential limiting force.

A pinion shaft 113 is arranged inside the differential case 101 in a direction perpendicular to the rotation axis of the differential case 101, and an end portion of the pinion shaft 113 is supported in a groove 116 of the differential case 101 so as to be movable in the axial direction. ing. A pinion gear 117 is rotatably supported on the pinion shaft 113. Pinion gear 1
A pair of left and right output side gears 119 and 121 are arranged at 17. The left side gear 119 is the housing 1
05, and the inner peripheral portion 1 of the housing 105.
A spline portion (output side connecting portion) 131 is provided at 11, and the left side (one side) output shaft 9 is connected to this portion. On the other hand, the inner peripheral portion 123 of the right side gear 121 is provided with a spline portion (output side connecting portion) 133, and the right side (other side) output shaft 11 is connected to this portion.

Thus, the bevel gear type differential mechanism 135
Is configured. The pinion shaft 113, the pinion gear 117, and the side gears 119 and 12 of the differential mechanism 135.
1 is capable of moving appropriately in the axial direction.

On the hub 107 of the differential limiting device 103, an extension portion 137 passing between the inner peripheral portion 111 of the housing 105 and the left side gear 119 is formed. In addition, an extension 139 that penetrates the center of the pinion shaft 113 to the left is provided on the inner peripheral portion 123 of the right side gear 121.
Are formed. A dog clutch mechanism 141 that meshes with each other is formed at opposite ends of the extension portions 137 and 139. As shown in FIG. 2, the dog clutch mechanism 141 is provided radially outward (larger diameter side) than the root diameter of each spline portion 131, 133 (a> b). Thus, the hub 137 of the differential limiting device 103 is connected to the right side gear 121.

A thrust block 143 is arranged in a space inside the dog clutch mechanism 141, and both ends of the block 143 face the left and right output shafts. In addition,
The outer diameter of the block 143 is equal to that of the spline portions 131 and 133.
Since the root diameter of the block 143 substantially coincides with the root diameter of the block, there is no risk that the block 143 will fall out of the differential device. Further, a thrust washer 145 is arranged between the right side gear 121 and the differential case 101.

With such a structure, the differential case 101
The drive power of the engine that rotates the pinion shaft 1
13 through the pinion gear 117 to the side gear 11
9, 121, that is, the left and right output shafts 9, 11. When a drive resistance difference occurs between the output shafts 9 and 11, the drive force of the engine is differentially distributed to the left and right sides by the rotation of the pinion gear 117. At this time, the multi-plate clutch 104 is pressed to the left by the left side gear 119 via the housing 105, whereby a torque-sensitive differential limiting force is obtained and a speed-sensitive differential is provided by the differential limiting device 103. Limited power is obtained.

In this way, according to the present embodiment, since the dog clutch mechanism 141 is a butt mesh with a simple structure, the axial space occupied by the dog clutch mechanism 141 can be reduced, and the dog clutch mechanism 141 is arranged on the larger diameter side than the spline portions 131, 133. Therefore, the selection range of the lengths of the spline portions 131 and 133 is widened, and the output shafts 9 and 11 to be connected can be shared with those of other differential devices, and compatibility can be maintained.

Since the butt meshing is simple, the method of applying the transmission torque load is simple.
It becomes easy to secure the wall thickness strength of 37,139.

Further, since the dog clutch mechanism 141 is arranged on the larger diameter side than the spline portions 131, 133, the thrust block 143 can be easily arranged, and the arranged thrust block 143 does not fall off during transportation. .

Further, since the lubricating oil is supplied radially outward through the meshing clearance of the dog clutch mechanism 141, the lubricity of each meshing portion and sliding portion inside the differential case 101 is improved.

[0043]

As is apparent from the above description, according to the invention described in claim 1, since the axial space of the differential limiting connecting portion can be reduced, the selection width of the length of each output side connecting portion can be reduced. Spreads. As a result, each output shaft connected to the output side connecting portion can maintain compatibility with that of another differential device.

Further, since the differential limiting connecting portions are arranged on the larger diameter side than the respective output side connecting portions, the thrust block is not dropped by utilizing the radially inner space portion of the differential limiting connecting portions. It is also possible to arrange as.

According to the invention described in claim 2, since the differential limiting connecting portion is formed by the dog clutch mechanism, an effect equivalent to that of the invention described in claim 1 is obtained, and the dog clutch mechanism enables the differential limiting device to operate. Since the method of applying the transfer torque load to the other member is simplified, it is easy to secure the wall thickness strength of the other member.

Further, since the lubricating oil is supplied radially outward through the meshing clearance of the dog clutch mechanism, the lubricity of each meshing portion and sliding portion inside the differential device is improved.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a differential device according to a first embodiment.

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

FIG. 3 is a cross-sectional view of a differential device according to a conventional example.

[Explanation of symbols]

9, 11 Output shaft 21, 101 Differential case 39, 103 Differential limiting device 41, 105 Housing (one side member) 43, 107 Hub (other side member) 49, 51, 119, 121 Side gear 65, 67, 131, 133 Spline Part (output side connecting part) 69,71 Storage hole 73,75,117 Pinion gear 87,135 Differential mechanism 89,137,139 Extension part 93,141 Dog clutch mechanism (differential limiting connecting part) 95,143 Thrust block 104 Multi Plate clutch a Thrust block outer diameter b Spline root diameter

Claims (2)

[Claims] 1. A differential mechanism for distributing the driving force of an engine to each output shaft via a pair of output side gears, and a differential mechanism which is arranged between the one side member and the other side member and is arranged between the pair of side gears. A differential limiting device that limits the differential according to the rotational speed of rotation, and one side member of the differential limiting device has an output side connecting portion connected to an output shaft on one side and the pair of side gears. The other side member of the differential limiting device is coupled to the other of the pair of side gears having an output side coupling part coupled to the output shaft of the other side via the differential limiting coupling part. A differential device, wherein the differential limiting connection part is arranged on a larger diameter side than the output side connection parts. 2. The differential device according to claim 1, wherein the differential limiting coupling portion includes a dog clutch mechanism.