JPH08178018A - Differential device - Google Patents

Abstract

PURPOSE: To reduce the number of part items and reduce the cost by equalizing the outer diameters and inner diameters of washers arranged on the side faces of a pair of output side gears separately meshed with a pinion gear. CONSTITUTION: The differential case 21 of a rear differential 7 in the power system of a vehicle is rotatably arranged in a differential carrier, and it is rotatively driven by the driving force of an engine via the meshing between a ring gear fixed to the differential case 21 and a drive pinion gear. A washer 49 supported on the outer periphery of the boss section 55 of an output side pinion gear 39 is provided between output side gears 37, 39 meshed on the outside in the axial direction with a pinion gear 61 in the differential case 21. Washers 51, 53 are supported on the outer peripheries of the boss sections 41, 43 of the output side gears 37, 39. The outer diameters and inner diameters of the washers 49, 51, 53 are made equal respectively, and the number of part items is reduced.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle differential device.

[0002]

2. Description of the Related Art Japanese Unexamined Patent Publication No. 60-175843 discloses a differential device 201 as shown in FIG.
In this differential device 201, the driving force of the engine that rotates the differential case 203 is the pinion gear 2
It is transmitted to the wheel from 05,207 via the side gears 209,211. The pinion gears 205 and 207 mesh with each other while accommodating the storage holes 213 and 21 of the differential case 203.
The side gears 209 and 211 are meshed with the pinion gears 205 and 207, respectively.

Differential case 203 and side gears 209, 2
When differential rotation occurs between the 11 and 11, the inner peripheral wall of the storage holes 213 and 215 of the differential case 203 and the pinion gears 205 and 20.
Friction resistance is generated between the teeth of the pinion 7 and the pinion gear 20.
5, 207 and the side gears 209, 211 are helical gears, the pinion gears 205, 207
Is pressed against the wall surfaces of the housing holes 213, 215 by a reaction force with the side gears 209, 211 to generate frictional resistance, and the gears 205, 207, 209, 211
The meshing thrust force of the helical gear due to the meshing between the pinion gears 205 and 207 and the side gear 20
The respective ends of 9, 211 are pressed by the differential case 203 to further generate frictional resistance, and the torque sensitive differential limiting force is obtained by these frictional resistances.

[0004]

As described above, when the differential case 203 and the side gears 209 and 211 are differentially rotated, the sliding surface between the differential case 203 and the side gears 209 and 211 is worn or the side gears 209 and 211 are worn.
Is constituted by a helical gear, the differential case 20 is so strong that a differential limiting force is generated by the meshing thrust force.
Pressed by 3. Therefore, in order to prevent wear of the sliding surface between the differential case 203 and the side gears 209 and 211 and play in the axial direction, the differential case 203 and the side gear 20 are prevented.
Although it is necessary to heat-treat 9, 211, these are complicated in shape, and especially the differential case 203 is large,
Heat treatment is difficult and costly.

Therefore, washers are arranged on these sliding portions to prevent wear and reduce heat treatment costs.

However, the conventional differential device 20
1, the side gears 209 and 211 are assembled from the outer side in the axial direction, and the side gears 209 and 211 are attached from the outside of the differential case 203.
Since it abuts against 17, the sliding parts 219, 22 at four locations are provided between the side gears 209, 211 and the differential case 203.
There are 1, 223 and 225. Therefore, four washers are required, and conventionally, it is necessary to make a troublesome clearance adjustment at two locations of arrows 221 and 223, which is disadvantageous because of a large number of adjustment man-hours at the time of assembly.

Further, these washers are used not only for preventing abrasion of the sliding portion but also for exchanging those having different thicknesses to adjust the clearance between the respective portions. Therefore, unless the sizes of the washers are the same, it is necessary to prepare different types of washers having different sizes and different thicknesses, resulting in an extremely large number of parts and an increase in cost.

Further, if the size of the washer is different, the sliding area is different, and the differential limiting characteristic becomes unstable. When the washer has a large diameter, interference with the pinion gear causes galling and local wear, which causes a failure of the differential device.

Therefore, an object of the present invention is to provide a differential device which is capable of obtaining stable differential limiting characteristics, has a small number of gap adjusting points and types of washers, is low in cost, and does not cause galling between the washer and the pinion gear. And

[0010]

According to another aspect of the present invention, there is provided a differential device having a differential case which is rotationally driven by a driving force of an engine and a pair of meshing members which are slidably and rotatably housed in a housing hole formed in the differential case. A pinion gear, a pair of output side gears respectively meshing with the pinion gears, and a washer arranged on a side surface of each side gear are provided, and each washer has an outer diameter and an inner diameter that are equal to each other.

A differential device according to a second aspect of the present invention is the differential device according to the first aspect, wherein the pair of pinion gears mesh with each other axially outside of the side gears, and the pair of side gears slide through the washers. It is characterized by

A differential device according to a third aspect of the present invention is the differential device according to the first or second aspect, wherein among the washers disposed on the side surfaces of the side gears, the differential device is disposed between the side gears and the differential case. The washer is supported on the outer periphery of the boss portion of each of the side gears, and the washer disposed between the side gears is supported on the inner periphery of a convex portion provided on the side surface of one of the side gears.

A differential device according to a fourth aspect is the differential device according to the first or second aspect, wherein among the washers disposed on the side surfaces of the side gears, the differential device is disposed between the side gears and the differential case. The washer is disposed between the end surface of the boss portion of each side gear and the differential case, and the washer disposed between the side gears has its outer periphery supported by a recess provided on the side surface of one side gear.

According to another aspect of the present invention, there is provided a differential device, which is slidably and rotatably housed in a differential case which is rotationally driven by a driving force of an engine and a housing hole formed in the differential case.
A pair of pinion gears that mesh with each other, a pair of output side gears that mesh with each of these pinion gears, a block arranged over the inner circumference of each side gear, a boss end surface of each side gear, and the differential case. A washer arranged between the blocks, and a washer supported on the outer periphery of the block, wherein each of the washers has an outer diameter and an inner diameter equal to each other, and the pair of pinion gears mesh with each other axially outside of the side gear. Characterize.

A differential device according to a sixth aspect of the present invention is slidably and rotatably housed in a differential case which is rotationally driven by a driving force of an engine and a housing hole formed in the differential case.
A pair of pinion gears that mesh with each other, a pair of output side gears that mesh with each of these pinion gears, a block arranged across a recess provided in the inner circumference of each side gear, and a side surface of each side gear. The washer is provided between the differential case and the outer circumference of the boss portion of each side gear, and the washer is supported on the outer circumference of the block.The outer diameter of the block and the outer diameter of the boss portion of the side gear are provided. And are set to have substantially the same diameter.

A differential device according to claim 7 is the differential device according to any one of claims 1 to 6, characterized in that the pair of pinion gears have a tooth height smaller than that of a standard gear. To do.

[0017]

In the differential device of the first aspect, the outer diameter and the inner diameter of the washers arranged on the side surfaces of the side gears are made equal to each other.

As described above, unlike the conventional example, it is not necessary to prepare different types of washers with different thicknesses for the gap adjustment, so that the number of parts can be reduced and the cost can be reduced.

Further, the use of the washer eliminates the need for heat treatment of the side gear and the differential case, and the post-heat treatment does not have to be performed, resulting in a lower cost.

Further, since the washers have the same dimensions and the washers are commonly used, the sliding areas of the washers are equalized, and when the side gears are helical gears, even if the direction of the mesh thrust force changes, the washer portion is changed. The magnitude of the differential limiting force does not change, and thus the differential limiting characteristic is stable.

The differential device according to a second aspect of the present invention is configured such that each pinion gear meshes with an outer side of a side gear in the axial direction, and both side gears slide through a washer.

By thus meshing the pinion gears on the axially outer side of the side gears, a space for the meshing portion of the pinion gears is not required between the both side gears, so that both side gears are arranged close to each other and slid through the washers. It is possible to let Therefore, in addition to the effect according to the invention described in claim 1,
The number of washers is reduced by one instead of two as in the conventional example, the gap adjustment cost and the number of parts at the time of assembly are reduced, and the cost is reduced.

A differential device according to a third aspect of the present invention is the differential device according to the first or second aspect, in which a washer between each side gear and a differential case is supported by an outer periphery of a boss portion of each side gear, and a washer between the side gears is provided on one side gear side surface. Since the inner periphery is supported by the provided convex portion, the sliding area of the washer can be increased and the surface pressure of the sliding surface of the side gear can be reduced.

As a result, wear of the washer can be prevented and durability can be improved. Further, when the side gear is formed of a helical gear, the sliding area of the washer is large, so the differential limiting force can be strengthened.

According to a fourth aspect of the present invention, in the differential device, the washers between the side gears and the differential case are arranged between the end faces of the boss portions of the side gears and the differential case, and the washers between the side gears are provided in the recesses provided on the side surfaces of one side gear. Since the outer periphery of the washer is supported, the washer has no risk of interfering with the pinion gear in addition to the effect of the differential device of the first or second aspect.

According to another aspect of the differential device of the present invention, a washer between each side gear and the differential case is arranged between the end surface of the boss portion of each side gear and the differential case, and the outer periphery of the block arranged across the inner circumference of each side gear. Since the washers between the side gears are supported by the side gears, it is not necessary to center the washers between the side gears by the side gears, in addition to the operation of the differential device according to claims 1 and 2, and the shape of the side gears is simplified, thereby reducing the manufacturing cost. It can be reduced.

According to a sixth aspect of the present invention, in the differential device, the washers between the side gears and the differential case are arranged between the side surfaces of the side gears and the differential case, and the washers between the side gears are arranged so as to extend over the recesses on the inner circumference of the side gears. Since the outer diameter of the block is supported and the outer diameter of the block and the outer diameter of the boss of each side gear are set to be approximately the same diameter, each washer can be formed to have a large diameter and the side gear has a washer on its side surface. The side gear has a simple shape because it has no bearing.

Further, an oil sump is formed between the concave portion of the inner circumference of the side gear and the notch portion of the block, and the oil lubricates the washer sliding portion by the centrifugal force, so that the lubricity of the washer is improved.

In addition to the operation of the differential device according to any one of claims 1 to 6, the differential gear of claim 7 has a tooth height of the pinion gear smaller than that of the standard gear. Therefore, there is no risk of interference between the washer and the pinion gear. Disappear. Therefore, the washer diameter can be increased correspondingly, and the differential limiting force can be further strengthened.

Further, since the surface pressure can be reduced, it is possible to avoid the failure of the differential gear between the side gears and the differential case or between the side gears due to galling of the sliding portion or local wear.

[0031]

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 claims 1, 2, 3, and 7. 1 and 2 are sectional views of this embodiment. The left and right directions are the left and right directions in FIGS.

As shown in FIGS. 1 and 2, the differential case 21 of the differential device 7 includes a casing body 31 and a cover 3.
3 and 3 are fixed by bolts 35. Inside the differential case 21, left and right side gears 37, 39 (output side gears) formed of helical gears are arranged. The side gears 37, 39 are assembled to the casing body 31 from the left.

Hollow boss portion 4 of each side gear 37, 39
1, 43 are rotatably supported by bearings 45, 47 of the differential case 21, and the bosses 41, 43 are spline-coupled to the output shaft, respectively.

A thrust washer 49 (washer) is arranged between the side gears 37, 39,
Thrust washers 51 and 53 (washers) are arranged between the 39 and the differential case 21, respectively. The thrust washer 49 is supported on the outer periphery of the convex portion 55 formed on the right side gear 39, and the thrust washers 51, 53 are supported on the outer periphery of the boss portions 41, 43. The thrust washers 49, 51, 53 have the same outer diameter and inner diameter, and are commonly used.

The differential case 21 has a plurality of sets of storage holes 57,
59 are formed at equal intervals in the circumferential direction. Pinion gears 61 and 63 formed of long and short helical gears are slidably and rotatably housed in these housing holes 57 and 59, respectively.

The long pinion gear 61 is composed of first and second gear portions 65 and 67 and a small-diameter shaft portion 69 connecting them, and the first gear portion 65 meshes with the right side gear 39. The short pinion gear 63 (FIG. 2) is composed of first and second gear parts 71 and 73, the first gear part 71 meshes with the left side gear 37, and the second gear part 73 is the second gear part of the pinion gear 61. It is in mesh with 67.

The tooth height of each pinion gear 61, 63 is lower than the standard tooth height, and each thrust washer 49, 51,
53 has an outer diameter larger than the root diameter of the side gears 37, 39.

The differential case 21 is provided with openings 75, 76, 77 which communicate with the storage holes 57, 59.
A spiral oil groove 83 is formed on the inner circumference of the boss portions 79 and 81 of the first embodiment.
Is provided. As the differential case 21 rotates, oil flows into and out of the differential case 21 from the oil reservoir of the differential carrier through the openings 75, 76, 77 and the oil groove 83, and lubricates the meshing parts and sliding parts of each gear. .

The driving force of the engine for rotating the differential case 21 is from the pinion gears 61, 63 to the side gears 37, 3.
9 is distributed to the left and right output shafts, and when a drive resistance difference occurs between the output shafts on a bad road or the like, the driving force of the engine is differentially distributed to the left and right sides by the rotation of the pinion gears 61 and 63.

While the torque is being transmitted, the tooth tips of the pinion gears 61 and 63 are pressed against the wall surfaces of the storage holes 57 and 59 by the reaction force of engagement with the side gears 37 and 39, so that frictional resistance is generated. Further, due to the meshing thrust force of the helical gears, frictional resistance is generated between the end faces of the pinion gears 61 and 63 and the differential case 21, and the thrust washers 51 and 53 are provided between the side gears 37 and 39 via the thrust washers 49. Through side gears 37, 3
Friction resistance occurs between the 9 and the differential case 21. These frictional resistances provide a torque sensitive differential limiting function.

One of the thrust washers 49, 51, 53 is used for adjusting the clearance, and the other two 1.4-
The thickness of the differential device 7 is adjusted by preparing one having a thickness 1.7 times as large as that of the required thickness.

For example, when the thrust washer 53 is used for adjusting the clearance, the distance from the sliding surface 85 between the cover 33 and the pinion gear 61 to the right end surface 87 of the right side gear 39 is set to A as shown in FIG. The distance from the moving surface 85 to the sliding surface 89 between the casing body 31 and the washer 53 is B
Then, prepared thrust washers 53 of various thicknesses are prepared.
Among them, the one having a thickness of BA is selected and used.
If the gap cannot be adjusted with this, the space is adjusted by using one of the other thrust washers 49, 51 for adjusting the gap.

Thus, the differential device 7 is constructed.

When the differential device 7 of FIG. 1 is applied to a vehicle, the behavior of the vehicle body when a large torque is applied such as when starting or accelerating is stabilized by the torque sensitive differential limiting function of the differential device 7. The maneuverability is improved.

In the differential device 7, as described above, since the thrust washers 49, 51, 53 have the same size and the sliding areas are uniform, the direction of the meshing thrust force changes to the left or right. However, regardless of which thrust washer 49, 51, 53 slides, the magnitude of the differential limiting force generated does not change, and the differential limiting characteristic is stable.

Further, the thrust washer 49 is attached to the side gear 3
9 is arranged on the outer periphery of the convex portion 55 of the thrust washer 51,
53 is arranged on the outer periphery of the boss portions 41, 43 of the side gears 37, 39, and the tooth heights of the pinion gears 61, 63 are made lower than the standard tooth height.
The outer diameters of 51 and 53 can be increased by that much, the sliding area is widened, and a large differential limiting force is obtained, and galling and local wear due to interference with the pinion gears 61 and 63 are prevented. The failure of the differential device 7 can be avoided.

In the differential device 7, since the inner and outer diameters of the thrust washers 49, 51, 53 are made common, different types of washers are provided with different thicknesses for gap adjustment, unlike the conventional example. There is no need, and the number of parts is reduced and the cost is reduced.

Further, by engaging the pinion gears 61 and 63 on the outer sides of the side gears 37 and 39 in the axial direction,
Both side gears 37 and 39 are arranged close to each other and can be slid through the thrust washer 49. Therefore,
The sliding position between the side gears 37, 39 is not one as in the conventional example but one, and the number of thrust washers is reduced by one, reducing the number of parts and the clearance adjustment cost during assembly. And low cost.

Further, by using the thrust washers 49, 51, 53, the heat treatment of the side gears 37, 39 and the differential case 21 becomes unnecessary, and the heat treatment cost and the processing cost after the heat treatment are reduced accordingly.

Next, the second embodiment will be described with reference to FIG. This embodiment has the features of claims 1, 2, 6, and 7. FIG. 3 is a sectional view of the embodiment, and the left and right directions are as shown in FIG.
The left and right directions. In addition, in this embodiment, FIG.
The members having the same function as the member having the same function are indicated by the same reference numerals, and the description of these members having the same function is omitted.

Differential case 2 of the differential device 91
Left and right side gears 93 and 95 (output side gears) formed of helical gears are arranged inside the unit 1.
The side gears 93 and 95 are arranged from the left side of the casing main body 31.
Assembled to.

Hollow boss portion 9 of each side gear 93, 95
7, 99 are rotatably supported by bearings 45, 47 of the differential case 21, and the bosses 97, 99 are spline-coupled to the output shaft, respectively.

A thrust washer 49 (washer) is arranged between the side gears 93 and 95,
Thrust washers 51 and 53 (washers) are arranged between the 95 and the differential case 21, respectively.

The side gears 93 and 95 are formed with a cylindrical recess 101 extending over the inner circumference thereof. A thrust block (block) 103 having a two-face width shape provided with a notch for abutting the output shaft is arranged in the recess 101, and the thrust washer 49 is supported on the outer periphery of the thrust block 103. The thrust washers 51, 53 are supported on the outer circumferences of the bosses 97, 99. As described above, each thrust washer 49, 5
The outer diameters and the inner diameters 1 and 53 are the same and common.

The first gear portion 65 of the pinion gear 61 meshes with the right side gear 95, and the first gear portion 71 of the pinion gear 63 meshes with the left side gear 93. or,
The tooth height of each pinion gear 61, 63 is lower than the standard tooth height, and the outer diameter of each thrust washer 49, 51, 53 is made larger than the root diameter of the side gear 93, 95.

The driving force of the engine is the pinion gears 61, 6
3 is distributed to the left and right output shafts via the side gears 93 and 95, and when a drive resistance difference occurs between the output shafts on a bad road or the like, the driving force of the engine is differentially distributed to the left and right sides by the rotation of the pinion gears 61 and 63. To be done.

While transmitting the torque, the tooth tips of the pinion gears 61 and 63 are pressed against the wall surfaces of the housing holes 57 and 59 by the reaction force of meshing with the side gears 93 and 95 to generate frictional resistance. Further, due to the meshing thrust force of the helical gear, frictional resistance is generated between the end faces of the pinion gears 61 and 63 and the differential case 21, and the thrust washers 51 and 53 are also separated between the side gears 93 and 95 via the thrust washer 49. Through side gears 93, 9
Frictional resistance occurs between the 5 and the differential case 21. These frictional resistances provide a torque sensitive differential limiting function.

In this way, the differential device 91 is constructed.

When the differential device 91 of FIG. 3 is applied to a vehicle, the behavior of the vehicle body when a large torque is applied such as when starting or accelerating is stabilized by the torque sensitive differential limiting function of the differential device 91. The maneuverability is improved.

In the differential device 91, since the thrust washers 49, 51 and 53 have the same sliding area, the magnitude of the differential limiting force generated even when the direction of the meshing thrust force changes to the left or right. Does not change,
The differential limiting characteristic is stable.

The thrust washers 51, 53 are arranged on the outer circumferences of the bosses 97, 99 of the side gears 93, 95, and the outer diameter of the thrust washers 49, 51, 53 is larger than the root diameter of the side gears 93, 95. Since the diameter is set, the sliding area is widened accordingly and a large differential limiting force can be obtained.

Further, the oil collected between the notch of the thrust block 103 and the recess 101 of the side gears 93, 95 pushes the thrust washer 49 into the sliding portion between the thrust washer 49 and the side gears 93, 95 by centrifugal force. The lubricity is improved.

Since the sliding area is large, the side gear 93,
The thrust surface pressure of 95 can be lowered, and galling and local wear due to the interference between the thrust washers 49, 51, 53 and the pinion gears 61, 63 can be prevented, and the failure of the differential device 91 can be avoided.

Similar to the differential device 7, the thrust washer 49, 51, 53 adjusts the space of the differential device 91 by using any one of them for adjusting the clearance.

Further, since the thrust washers 49, 51, 53 are made common, it is not necessary to prepare different types of washers having different thicknesses for the clearance adjustment, and the number of parts is reduced and the cost is reduced. Become.

Furthermore, since the side gears 93, 95 slide through the thrust washer 49, the side gears 93, 9
The number of sliding points between the five is reduced to one and the number of thrust washers is reduced by one, so that the number of parts and the clearance adjustment cost at the time of assembly are reduced.

Further, by using the thrust washers 49, 51, 53, the heat treatment of the side gears 93, 95 and the differential case 21 becomes unnecessary, and the heat treatment cost and the processing cost after the heat treatment are reduced accordingly.

Next, the third embodiment will be described with reference to FIG. This embodiment has the features of claims 1, 2, and 4. FIG. 4 is a sectional view of the embodiment, and the left and right directions are the left and right directions in FIG. It should be noted that members and the like to which reference numerals are not given are not shown.

As shown in FIG. 4, the differential device 10
The differential case 107 of No. 5 has a cover 111 on the left end and a ring plate 113 on the right end of the casing body 109.
Each is configured with bolts. Inside the differential case 107, left and right side gears 115 and 117 (output side gears) formed of helical gears are arranged. The side gears 115 and 117 are attached to the casing body 109 from the left.

The hollow boss portions 119 and 121 of the side gears 115 and 117 are the support portions 123 of the differential case 107, respectively.
It is rotatably supported by 125, and each boss 1
19, 121 are respectively spline-connected to the output shaft.

Thrust washers 127 (washers) are arranged between the side gears 115 and 117, and thrust washers 129 and 131 (washers) are arranged between the side gears 115 and 117 and the differential case 107, respectively. Thrust washer 127 is right side gear 1
The thrust washers 129, 131 are supported on the inner circumference of the recess 133 formed in the groove 17, and are disposed between the end faces of the bosses 119, 121 and the differential case 107. The thrust washers 127, 129, and 131 have the same outer diameter and inner diameter, and are commonly used.

The differential case 107 has a plurality of sets of storage holes 13
5 and 137 are formed at equal intervals in the circumferential direction, and long and short pinion gears 139 and 141 formed of helical gears, respectively.
Is stored so that it can slide and rotate.

The long pinion gear 139 comprises the first and second gear parts 143, 145 and the small-diameter shaft part 1 connecting them.
47 and the first gear portion 143 is the left side gear 1
It meshes with 15. The short pinion gear 141 is composed of first and second gear portions 149 and 151, the first gear portion 149 meshes with the right side gear 117, and the second gear portion 151 meshes with the second gear portion 145 of the pinion gear 139. There is. Also, the pinion gear 139 and the differential case 1
A washer 153 is provided between the washer 157 and the driver.

Storage holes 135, 13 are provided in the differential case 107.
7 are provided with openings 155, 157, and spiral oil grooves are provided on the inner periphery of the boss portions 159, 161 of the differential case 107. With the rotation of the differential case 107, the oil flows from the oil reservoir of the differential carrier through the openings 155, 157 and the oil groove to the differential case 10.
7, and lubricates the meshing parts and sliding parts of each gear.

The driving force of the engine for rotating the differential case 107 is from the pinion gears 139 and 141 to the side gear 1.
When the driving resistance is distributed to the left and right output shafts via 15, 117, and a drive resistance difference occurs between the output shafts on a bad road, etc.
Due to the rotation of 9,141, the driving force of the engine is differentially distributed to the left and right sides.

While the torque is being transmitted, the tooth tips of the pinion gears 139 and 141 are pressed against the wall surfaces of the storage holes 135 and 137 by the meshing reaction force with the side gears 115 and 117 to generate frictional resistance. Further, the meshing thrust force of the helical gear causes frictional resistance between the end surface of the pinion gear 139 and the differential case 21 (washer 153) and between the end surface of the pinion gear 141 and the differential case 21, and through the thrust washer 127. Between the side gears 115 and 117, the thrust washer 1
Friction resistance is generated between the side gears 115 and 117 and the differential case 21 via 29 and 131. These frictional resistances provide a torque sensitive differential limiting function.

Thrust washers 127, 129, 131
Prepare various thicknesses with one of them being used for gap adjustment, and select the thickness of the required thickness from these to adjust the space of the differential device 105.

In this way, the differential device 105 is constructed.

When the differential device 105 of FIG. 4 is applied to a vehicle, the behavior of the vehicle body when a large torque is applied, such as when starting or accelerating, is the behavior of the differential device 10.
The torque sensitive differential limiting function of 5 stabilizes and improves maneuverability.

In the differential device 105, since the thrust washers 127, 129, 131 have the same sliding area as described above, the difference generated even when the direction of the meshing thrust force changes to the left or right direction. The magnitude of the dynamic limiting force does not change, and the differential limiting characteristic is stable.

Further, the thrust washers 129 and 131 are arranged between the end faces of the boss portions 119 and 121 of the side gears 115 and 117 and the differential case 107. Since the thrust washers 127, 129, 131 have a small diameter in this manner, there is no risk of the thrust washers 127, 129, 131 interfering with the pinion gears 139, 141, and galling, local wear, and failure of the differential device 105 due to interference do not occur.

Further, thrust washers 127, 129, 1
By making 31 common, there is no need to prepare different types of washers with different thicknesses,
As a result, the number of parts is reduced and the cost is reduced.

Further, since the side gears 115 and 117 slide through the thrust washer 127, the side gear 1
The number of sliding points between 15, 117 is one instead of two as in the conventional example, and the number of thrust washers is also reduced by one, which reduces the number of parts and the clearance adjustment cost during assembly.

Further, the thrust washers 127, 129, 1
By using 31, the side gears 115, 117
Therefore, the heat treatment of the differential case 107 becomes unnecessary, and the heat treatment cost and the processing cost after the heat treatment can be reduced.

The thrust washer 127 disposed between the side gears 115 and 117 is the side gear 11
A thrust block may be arranged on the inner circumference of the 5, 117 and arranged on the outer circumference of the thrust block. In that case, it is not necessary to form the recess 133 in the side gear 117, and the structure is simplified.

As described above, the differential devices 7, 91, 1
05 has been described as an example, but the differential device of the present invention is a rear differential or a front differential (axle differential on the front wheel side).
Alternatively, it can be used for a center differential (a differential device that distributes a driving force to front wheels and rear wheels).

[0087]

According to the differential device of the first aspect, since the outer diameter and the inner diameter of the washers arranged on the side surfaces of the side gears are equal to each other, different from the conventional example, the gap adjustment is performed for each of various types of washers. Since it is not necessary to prepare different thicknesses, the number of parts can be reduced and the cost can be reduced.

Further, by using the washers, the heat treatment of the side gear and the differential case becomes unnecessary, and the processing after the heat treatment does not have to be performed, so that the cost is reduced accordingly.

Further, since the washers have the same size and the washers are commonly used, the sliding areas of the washers are equalized, and when the side gear is composed of the helical gear, even if the direction of the meshing thrust force changes, the washer portion is changed. The magnitude of the differential limiting force does not change, and thus the differential limiting characteristic is stable.

According to the differential device of the second aspect, in addition to the effect of the differential device of the first aspect, the pinion gears are meshed with each other on the outer side in the axial direction of the side gears so that the both side gears slide through the washers. Since there is no space for the meshing portion of the pinion gear between both side gears, both side gears can be arranged close to each other and can be slid through washers. Therefore, the number of sliding points between both side gears is one instead of two as in the conventional example, and the number of washers is reduced by one, which reduces the clearance adjustment cost and the number of parts during assembly. , Low cost.

According to the differential device of claim 3, in addition to the effect of the differential device of claim 1 or 2, the washer between each side gear and the differential case is supported by the outer periphery of the boss portion of each side gear, and the washer between the side gears is supported. Since the inner periphery is supported by the convex portion provided on the side surface of one of the side gears, the sliding area of the washer can be increased and the surface pressure of the sliding surface of the side gear can be reduced.

As a result, the washer can be prevented from being worn and the durability can be improved. Further, when the side gear is formed of a helical gear, the sliding area of the washer is large, so the differential limiting force can be strengthened.

According to the differential device of the fourth aspect, the washer between each side gear and the differential case is arranged between the boss end surface of each side gear and the differential case, and the washer between each side gear is provided on one side gear side surface. Since the outer periphery is supported by the concave portion, in addition to the effect of the differential device according to the first or second aspect, there is no fear that the washer interferes with the pinion gear.

According to the differential device of the fifth aspect, the washer between each side gear and the differential case is arranged between the end face of the boss portion of each side gear and the differential case, and the block of the block arranged across the inner circumference of each side gear is arranged. Since the washers between the side gears are supported on the outer periphery, in addition to the effect of the differential device according to claims 1 and 2, it is not necessary to center the washers between the side gears by the side gears, and the shape of the side gears is simplified. Cost can be reduced.

According to the differential device of the sixth aspect, the washers between the side gears and the differential case are arranged between the side surfaces of the side gears and the differential case, and the washers between the side gears straddle the recesses on the inner circumference of the side gears. The outer diameter of the block and the outer diameter of the block and the outer diameter of the boss of each side gear are set to be approximately the same diameter, so each washer can be formed with a large diameter and the side gears have The side gear side surface is simple because it has no washer support.

Further, an oil sump is formed between the concave portion of the inner circumference of the side gear and the cutout portion of the block, and the oil lubricates the washer sliding portion by the centrifugal force, so that the lubricity of the washer is improved.

According to the differential device of claim 7, in addition to the effect of the differential device of any one of claims 1 to 6, since the tooth height of the pinion gear is smaller than the tooth height of the standard gear, interference between the washer and the pinion gear is prevented. Fear disappears. Therefore, the washer diameter can be increased correspondingly, and the differential limiting force can be further strengthened.

Further, since the surface pressure can be reduced, it is possible to avoid the failure of the differential gear between the side gears and the differential case or between the side gears due to galling of the sliding portion or local wear.

[Brief description of drawings]

FIG. 1 is a sectional view of a first embodiment taken along a plane passing through a long pinion gear.

FIG. 2 is a sectional view of the first embodiment cut along a plane passing through a short pinion gear.

FIG. 3 is a sectional view of a second embodiment.

FIG. 4 is a sectional view of a third embodiment.

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

[Explanation of symbols]

7, 91, 105 Differential device 21, 107 Differential case 37, 39, 93, 95, 115, 117 Side gear (output side gear) 41, 43, 55, 97, 99, 119, 121 Boss portion 49, 51, 53, 127 , 129, 131 Thrust washer (washer) 57, 59, 135, 137 Storage hole 61, 63, 139, 141 Pinion gear 103 Thrust block 133 Recess

Claims (7)

[Claims] 1. A differential case which is rotationally driven by a driving force of an engine, a pair of pinion gears which are slidably and rotatably accommodated in an accommodation hole formed in the differential case, and which are meshed with each other, and a pair which is meshed with each of these pinion gears. Of the output side side gears and washers arranged on the side surfaces of the side gears, wherein each of the washers has an outer diameter and an inner diameter that are equal to each other. 2. The differential device according to claim 1, wherein the pair of pinion gears mesh with each other on an axially outer side of the side gear, and the pair of side gears slide through the washer. apparatus. 3. The differential device according to claim 1, wherein among the washers arranged on a side surface of each of the side gears,
A washer arranged between each side gear and the differential case is supported on the outer periphery of the boss portion of each side gear,
A differential device characterized in that the washer disposed between the side gears is supported at its inner circumference by a convex portion provided on the side surface of one side gear. 4. The differential device according to claim 1, wherein among the washers arranged on a side surface of each of the side gears,
The washers arranged between the side gears and the differential case are arranged between the boss end surfaces of the side gears and the differential case, and the washers arranged between the side gears are recesses provided on one side gear side surface. A differential device characterized in that its outer periphery is supported by the. 5. A differential case which is rotationally driven by a driving force of an engine, a pair of pinion gears which are slidably and rotatably accommodated in an accommodation hole formed in the differential case, and which are meshed with each other, and a pair of these pinion gears which are respectively meshed with each other. Output side gears, blocks arranged over the inner circumference of each side gear, washers arranged between the boss end surface of each side gear and the differential case, and side gears supported on the outer circumference of the block. And a pair of washers, the outer diameter and the inner diameter of each of the washers being equal to each other, and the pair of pinion gears mesh with each other axially outside of the side gears. 6. A differential case which is rotationally driven by a driving force of an engine, a pair of pinion gears which are slidably and rotatably housed in a housing hole formed in the differential case, and which are meshed with each other, and a pair of which are respectively meshed with these pinion gears. Of the output side gears, a block having a cutout portion extending across a recess provided in the inner circumference of each side gear, and a side gear arranged between the side surface of each side gear and a differential case. A washer supported on the outer periphery of the boss portion and a washer supported on the outer periphery of the block, and the outer diameter of the block and the outer diameter of the boss portion of each of the side gears are set to be substantially the same. Differential device. 7. The differential device according to claim 1, wherein the pair of pinion gears have a tooth height smaller than a tooth height of a standard gear.