JPH064448U - Pinion gear support structure - Google Patents

Abstract

(57) [Summary] [Purpose] To prevent the pinion gear and pinion shaft from being damaged by the pressing force based on meshing. [Composition] Pinion gears 32, 34 having substantially hemispherical recesses 32a, 34a formed on both end surfaces, and a pinion gear 3
Pinion gears 32, 34 located on either side of 2, 34
The recesses 32a, 34 formed in the pinion gears 32, 34 at the portions facing the recesses 32a, 34a formed in the
a planetary carrier 28, 30 having substantially hemispherical recesses 28a, 30a similar to a, and a pinion gear 3
Recesses 32a, 34a formed in 2, 34 and recesses 28a formed in the planetary carriers 28, 30,
And a substantially spherical rolling element 36 that is rotatably arranged so as to be housed in 30a, and the pinion gears 32 and 34 are attached to the planetary carriers 28 and 30 via the spherical rolling element 36. Positioned freely.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a support structure for a pinion gear, and more particularly to a support structure for a pinion gear used as a planetary gear in a planetary gear mechanism.

[0002]

[Prior art]

 As a conventional pinion gear support structure, for example, there is a pinion gear support structure used in the differential limiting device disclosed in Japanese Patent Laid-Open No. 2-107847.

The differential limiting device disclosed in JP-A-2-107847 uses a planetary gear mechanism as a differential mechanism, and pinion is used as an outer planetary gear and an inner planetary gear of the planetary gear mechanism. -Gear is used.

Each of the outer planetary gear and the inner planetary gear, which is a pinion gear, is rotatably inserted in a pinion shaft provided in a carrier that rotates integrally with one axle. These pinion gears mesh with each other, the pinion gear as the outer planetary gear meshes with the annular gear formed on the inner circumference of the differential case, and the pinion gear as the inner gear meshes with the other axle. It is configured to mesh with the sun gear that rotates integrally.

[0005]

[Problems to be solved by the device]

 In the conventional technology described above, the pinion gears mesh with each other, the pinion gear as the outer planetary gear meshes with the annular gear, and the pinion gear as the inner gear meshes with the sun gear. When rotating on the pinion shaft, the pinion gear may be damaged by the pressing force due to the meshing, or the pressing force due to the meshing may be transmitted to the pinion shaft via the pinion gear. However, there is a problem in that stress may be concentrated on the pinion shaft and the pinion shaft may be damaged.

The present invention has been made in view of the above problems of the prior art, and an object of the present invention is to prevent the pinion gear from being damaged due to the pressing force due to the meshing. The aim is to provide a support structure for the gear.

Further, an object of the present invention is to eliminate the support structure of the pinion gear by the pinion shaft, and to provide a pinion gear support structure without risk of damage to the pinion shaft. It is in.

[0008]

[Means for Solving the Problems]

 In order to achieve the above object, the support structure of the pinion gear in the present invention is a pinion gear having spherical recesses on both end surfaces, and a spherical surface formed on the pinion gear on both sides of the pinion gear. A carrier having a spherical recess formed in a portion facing the recess, a spherical recess formed in the pinion gear and a spherical body rotatably arranged so as to be housed in the spherical recess formed in the carrier, The pinion gear is rotatably supported by the carrier via a sphere.

[0009]

[Action]

 Since the pinion gear is positioned and supported by the carrier via the sphere, the pinion gear is rotatable with respect to the carrier.

Since it is not necessary to form a through hole for penetrating the pinion gear in the pinion gear, the pinion gear can be configured as a solid body, so that the strength of the pinion gear can be improved and Since the pinion gear itself is self-aligning, the meshing condition between the gears is good.

Therefore, since the sphere is arranged in the spherical recesses of the pinion gear and the carrier, stress concentration can be prevented in any of the pinion gear, the carrier and the sphere, so that the pinion gear can be prevented. The durability of the carrier and the sphere is improved, and damage can be prevented.

[0012]

【Example】

 Hereinafter, a support structure for a pinion gear according to the present invention will be described in detail with reference to the drawings.

FIG. 1 is a sectional configuration explanatory view showing a case where an embodiment of a support structure for a pinion gear according to the present invention is used as a planetary gear differential mechanism of a differential limiting device.

The differential limiting device 10 uses a planetary gear differential mechanism 12 as a differential means, and includes a disc-shaped differential case lid portion 14 and a cup-shaped differential case tubular portion 16 with screws. It has a differential case 20 connected by 18.

This differential case 20 includes a hub (14a) located at the outer end of the differential case lid portion (14), and a bearing (not shown) through a bearing (not shown) on the left side support wall of a differential carrier (not shown). The hub 16a is rotatably supported on the right side support wall of the differential carrier via a bearing (not shown) and is rotatably supported on the hub 16a at the outer end of the differential case cylinder 16. By being supported, it is disposed in the differential carrier. A left axle 22 and a right axle 24 are inserted through the hub 14a and the hub 16a, respectively.

A sun gear 26 is axially movable in the left-hand side axle 22 and is spline-coupled to the left-hand side axle 24 while being prevented from rotating in the rotation direction, while a planetary carrier 28 is axially attached to the right-side axle 24. It is free to move and is fixed in the direction of rotation and is splined.

Further, an outer planetary gear 32 and an inner planetary gear 34 are arranged between the planetary carrier 28 and the planetary carrier 30 fixed to the planetary carrier 28. The outer planetary gear 32 and the inner planetary gear 34 are solid, and substantially hemispherical recesses (spherical recesses) 32a, 34a are formed on both end faces thereof, respectively. On the other hand, the side surfaces of the planetary carriers 28 and 30 facing the substantially hemispherical recesses 32a and 34a are also substantially hemispherical recesses (spherical recesses) 28a similar to the substantially hemispherical recesses 32a and 34a. , 30a are formed.

Then, between the substantially hemispherical recess 32a and the substantially hemispherical recesses 28a and 30a, and between the substantially hemispherical recess 34a and the substantially hemispherical recesses 28a and 30a. A rolling element (sphere) 36 having a substantially spherical shape is rotatably arranged. Therefore, the outer planetary gear 32 and the inner planetary gear 34 are rotatably supported between the planetary carriers 28 and 30 via the rolling elements 36.

The outer planetary gear 32 is formed with a gear portion 32b that meshes with the gear portion 16b formed on the outer diameter side inner wall surface of the differential case tubular portion 16, and the inner planetary gear 34 is formed with a sun gear. A gear portion 34b that meshes with the gear portion 26a of the reference numeral 26 is formed. Further, the gear portion 32b of the outer planetary gear 32 and the gear portion 34b of the inner planetary gear 34 mesh with each other to form a differential means by a planetary gear mechanism.

Outer clutch plates 38 and inner clutch plates 40 are alternately arranged on the planetary carrier 30 and the sun gear 26, respectively, to form a multi-plate friction clutch mechanism.

The coupling relationship between the carrier 30 and the outer clutch plate 38 is such that the lug portion 38 a located on the outer diameter side of the outer clutch plate 38 is fitted in the groove portion 30 b of the planetary carrier 30 and rotates in the rotational direction. The sun gear 26 and the inner clutch plate 40 are connected to each other by engaging the lug portion 40a located on the inner diameter side of the inner clutch plate 40 with the gear portion 26a of the sun gear 26. It is locked by stopping rotation in the rotation direction.

An intermediate plate 42 is arranged between the inner side wall surface of the differential case lid portion 14 and the multi-plate friction clutch mechanism. An outer diameter side end portion 42a of the intermediate plate 42 is bent and engages with the groove portion 14b of the differential case lid portion 14 to rotate integrally with the differential case 20.

Further, the differential limiting device 10 is composed of an electromagnetic clutch mechanism having a multi-plate friction clutch device 44 and an armature 46 arranged between the differential case cylinder portion 16 and the planetary carrier 28. A pilot clutch device 48 is provided. In the pilot clutch device 48, a field 54 having an electromagnetic coil 52 built in a yoke 50 is mounted on the hub 16a via a bearing 56 fitted and positioned in the hub portion 16a. A cam ring 58 is arranged on the planetary carrier 28, and between the grooved cam portion 58 a of the cam ring 58 and the grooved cam portion 28 b formed on the wall surface of the planetary carrier 28. A ball 60 is arranged in the.

The multi-plate friction clutch device 44 of the pilot clutch device 48 includes an outer plate 62 that is locked by inserting a lug portion into a groove portion 16c of an outer diameter side inner wall surface of the differential case tubular portion 16. And an inner plate 64 having a lug portion fitted into the outer diameter side groove portion 58b of the cam ring 58 to prevent rotation of the cam ring 58.

In the above configuration, the outer planetary gear 32 and the inner planetary gear 34 are rotatably supported between the planetary carrier 28 and the planetary carrier 30 via the substantially spherical rolling element 36. , The outer planetary gear 32 meshes with the gear portion 16b of the differential case cylinder portion 16, and the inner planetary gear 34 meshes with the sun gear 26 gear portion 26a to form a planetary gear differential mechanism. Therefore, differential rotation between the left axle 22 and the right axle 24 is allowed.

When the electromagnetic coil 52 is excited, a magnetic path shown by an arrow A in FIG. 1 connecting the yoke 50, the hub 16 a, the outer plate 62, the inner plate 64 and the armature 46 is formed. Then, the outer plate 62 and the inner plate 64 are pressed against each other by the armature 46, the rotation of the cam ring 58 is restrained, and the relative displacement with the planetary carrier 28 occurs. Due to this relative displacement, a thrust force is generated between the grooved cam portion 58a and the grooved cam portion 28b via the ball 60, and the planetary carrier 28 is pressed to the left side in the axial direction in FIG. By pressing the planetary carrier 28, the planetary carrier 30 integrated with the planetary carrier 28 is pressed to the left side in the axial direction in FIG.

At this time, since the outer clutch plate 38 and the inner clutch plate 40 are restricted from moving to the left in the axial direction by the intermediate plate 42 locked to the differential case lid portion 14, the outer clutch plate 38 and the inner clutch plate 40 are prevented from moving. The clutch plate 38 and the inner clutch plate 40 are pressed against each other, and the differential rotation between the left axle 32 and the right axle 34 is limited.

[0028]

[Effect of device]

 Since the present invention is configured as described above, it has the following effects.

[0029] Pinion gears having spherical recesses formed on both end faces, carriers arranged on both sides of the pinion gear and having spherical recesses formed at positions facing the spherical recesses formed on the pinion gear, and a pinion gear. A spherical recess formed in the gear and a spherical body rotatably arranged so as to be accommodated in the spherical recess formed in the carrier, and the pinion gear is rotatable with respect to the carrier through the spherical body. Since the pinion gear is positioned, the pinion gear can be configured as a solid body, so that the strength of the pinion gear can be improved.

That is, since the pinion shaft does not support the pinion gear, it is not necessary to form a through hole for penetrating the pinion shaft in the pinion gear. Since it can be configured, it is possible to improve the strength of the pinion gear.

Therefore, since the sphere is arranged in the spherical concave portion of the pinion gear and the carrier, stress concentration can be prevented in any of the pinion gear, the carrier and the sphere, so that the pinion gear can be prevented. The durability of the carrier and the sphere is improved, and damage can be prevented.

Further, when the pinion gear is positioned, it is only necessary to dispose the spherical body in the spherical concave portion, which simplifies the assembling, improves the assembling property, and enables self-centering.

Further, when the pinion gear is supported by the spherical body instead of the pinion shaft, a bending moment is not generated, which is advantageous in strength.

Further, since there is no need to form a through hole for inserting the pinion shaft in the pinion gear, the shaft diameter of the pinion gear can be made small, so that there is no space such as in a small device. Can be used for.

[Brief description of drawings]

FIG. 1 is a sectional view showing a differential limiting device using an embodiment of a support structure for a pinion gear according to the present invention.

[Explanation of symbols]

 10 Differential Limiting Device 12 Planetary Gear Differential Mechanism 14 Lid 14a Hub 14b Groove 16 Cylindrical 16a Hub 16b Gear 16c Groove 18 Screw 20 Differential Case 22 Left Axle 24 Right Axle 26 Sun Gear 26a Gear 28 28 Planetary Carrier 28a recess (spherical recess) 28b grooved cam portion 30 planetary carrier 30a recess (spherical recess) 30b groove 32 outer planetary gear 32a recess (spherical recess) 32b gear portion 34 inner planetary gear 34a recess (spherical recess) ) 34b Gear part 36 Rolling body (sphere) 38 Outer clutch plate 38a Lug part 40 Inner clutch plate 40a Lug part 42 Intermediate plate 42a Outer diameter side end part 44 Multi-plate friction clutch device 46 Armature 48 Pilot clutch device 50 Yoke 52 Electromagnetic carp 54 field 56 bearing 58 cam ring 58a groove-like cam portion 58b groove 60 ball 62 outer plate 64 inner plate

Claims (1)

[Scope of utility model registration request] 1. A pinion having spherical recesses formed on both end surfaces.
A gear and both sides of the pinion gear, the pinion
A carrier having a spherical recess formed in a portion facing the spherical recess formed in the gear, and a spherical recess formed in the pinion gear and the carrier arranged to be housed in the spherical recess formed in the carrier. A support structure for a pinion gear, wherein the pinion gear is rotatably supported with respect to the carrier via the sphere.