阅读说明：本技术 行星齿轮差速器 (Planetary gear differential mechanism ) 是由 叶权 章娇凤 于 2019-12-11 设计创作，主要内容包括：本发明所述的行星齿轮差速器,通过将行星轮设置成轮轴与外齿圈相组合的形式,在轮轴外圆周面和外齿圈内圆周面之间通过设置滚针的方式实现转动配合,使得行星轮的外齿圈相对于行星架能够转动,通过使滚针的直径等于外齿圈内径与轮轴外径的差值,消除了径向间隙,降低了使用时的噪声；在行星轮的尺寸发生变化时,可以人工调整使外齿圈内径与轮轴外径的差值不变,提高滚针的通用性；滚针单价低,使用成本低；安装滚针能够减小行星齿轮差速器的径向尺寸,并且径向承载能力高,抗磨损能力强。(According to the planetary gear differential mechanism, the planetary gear is arranged in a mode that the wheel shaft is combined with the outer gear ring, and the outer gear ring of the planetary gear can rotate relative to the planet carrier by realizing the rotating fit between the outer circumferential surface of the wheel shaft and the inner circumferential surface of the outer gear ring in a mode of arranging the roller needles, so that the radial clearance is eliminated and the noise in use is reduced by enabling the diameter of the roller needles to be equal to the difference value between the inner diameter of the outer gear ring and the outer diameter of the wheel shaft; when the size of the planet wheel changes, the difference between the inner diameter of the outer gear ring and the outer diameter of the wheel shaft can be adjusted manually, so that the universality of the roller pin is improved; the unit price of the roller pins is low, and the use cost is low; the radial dimension of the planetary gear differential can be reduced by installing the rolling needles, and the radial bearing capacity and the abrasion resistance are high.)

1. A planetary gear differential comprising:

a body;

the planetary transmission mechanisms are arranged in the machine body and comprise planetary carriers, planetary wheels and auxiliary planetary carriers, and the auxiliary planetary carriers and the planetary carriers are respectively arranged on two sides of the planetary wheels;

the method is characterized in that:

the planet wheel comprises a wheel shaft and an outer gear ring, the wheel shaft is erected between the auxiliary planet carrier and the planet carrier, the outer gear ring is rotatably sleeved on the wheel shaft, a plurality of roller pins are arranged between the outer circumferential surface of the wheel shaft and the inner circumferential surface of the outer gear ring, and the diameter of each roller pin is equal to the difference value between the inner diameter of the outer gear ring and the outer diameter of the wheel shaft.

2. A planetary gear differential as claimed in claim 1, wherein: and a retainer ring used for limiting the limit position of the needle roller when the needle roller moves left and right is arranged between the auxiliary planet carrier/the planet carrier and the planet wheel.

3. A planetary gear differential as claimed in claim 2, wherein: and a gap of 0.3-0.8mm is formed between the inner side surface of the retainer ring and the end surface of the roller pin.

4. A planetary gear differential as claimed in claim 2, wherein: the retainer ring is fixed on the wheel shaft or the outer gear ring through screws.

5. A planetary gear differential as claimed in claim 1, wherein: and lubricating oil is filled in a gap between the needle roller and the outer gear ring and between the needle roller and the wheel shaft.

6. A planetary gear differential as claimed in claim 1, wherein: two end faces of the roller pin are convex hemispherical faces.

7. A planetary gear differential as claimed in claim 1, wherein: the surface roughness of the roller pins is less than 0.2 mu m.

8. A planetary gear differential as claimed in claim 1, wherein: the hardness of the outer circumferential surface of the needle roller is HRC 58-63.

9. A planetary gear differential as claimed in claim 1, wherein: the diameter of the roller pin is 5-10 mm.

10. A planetary gear differential according to any one of claims 1-9, wherein: the rolling needle is made of a plug gauge.

Technical Field

The invention relates to the field of planetary gear differentials.

Background

In a planetary gear differential, a planetary gear and a planet carrier are in running fit usually in a mode of arranging a bearing or a bearing bush, and the bearing or the bearing bush needs to be provided with a radial gap during the matching, so that the planetary gear differential has higher noise during the running; when the size of the planet wheel changes, the types of the bearing and the bearing bush need to be changed, and the universality is poor; the unit price of the bearing and the bearing bush is high, and the bearing bush are used as easily-damaged parts, so that the use cost is high; the radial dimension of the planetary gear differential mechanism is increased by mounting the bearing, the requirement of miniaturization is not met, and the radial bearing capacity is low and the planetary gear differential mechanism is easy to wear although the mounting bearing bush meets the requirement of miniaturization.

Disclosure of Invention

The invention aims to overcome the defects of the prior art and provides a planetary gear differential mechanism which realizes running fit between a planetary gear and a planetary carrier in a mode of arranging a roller pin.

In order to achieve the above object, the present invention adopts a technical solution in which a planetary gear differential comprises:

a body;

the planetary transmission mechanisms are arranged in the machine body and comprise planetary carriers, planetary wheels and auxiliary planetary carriers, and the auxiliary planetary carriers and the planetary carriers are respectively arranged on two sides of the planetary wheels;

the planet wheel comprises a wheel shaft and an outer gear ring, the wheel shaft is erected between the auxiliary planet carrier and the planet carrier, the outer gear ring is rotatably sleeved on the wheel shaft, a plurality of roller pins are arranged between the outer circumferential surface of the wheel shaft and the inner circumferential surface of the outer gear ring, and the diameter of each roller pin is equal to the difference value between the inner diameter of the outer gear ring and the outer diameter of the wheel shaft.

Preferably, a retainer ring for limiting the limit position of the needle roller in left-right movement is arranged between the auxiliary planet carrier/the planet carrier and the planet wheel.

Further preferably, a gap of 0.3-0.8mm is formed between the inner side surface of the retainer ring and the end surface of the needle roller.

Further preferably, the retainer ring is fixed to the wheel axle or the outer gear ring by a screw.

Preferably, a gap between the needle roller and the outer ring gear and the wheel axle is filled with lubricating oil.

Preferably, two end faces of the roller pin are convex hemispheroids.

Preferably, the surface roughness of the needle roller is less than 0.2 μm.

Preferably, the hardness of the outer circumferential surface of the needle roller is HRC 58-63.

Preferably, the diameter of the roller pin is 5-10 mm.

Further preferably, the needle roller is made of a plug gauge.

Due to the application of the technical scheme, compared with the prior art, the invention has the following advantages:

according to the planetary gear differential mechanism, the planetary gear is arranged in a mode that the wheel shaft is combined with the outer gear ring, and the outer gear ring of the planetary gear can rotate relative to the planet carrier by realizing the rotating fit between the outer circumferential surface of the wheel shaft and the inner circumferential surface of the outer gear ring in a mode of arranging the roller needles, so that the radial clearance is eliminated and the noise in use is reduced by enabling the diameter of the roller needles to be equal to the difference value between the inner diameter of the outer gear ring and the outer diameter of the wheel shaft; when the size of the planet wheel changes, the difference between the inner diameter of the outer gear ring and the outer diameter of the wheel shaft can be adjusted manually, so that the universality of the roller pin is improved; the unit price of the roller pins is low, and the use cost is low; the radial dimension of the planetary gear differential can be reduced by installing the rolling needles, and the radial bearing capacity and the abrasion resistance are high.

Drawings

FIG. 1 is a schematic cross-sectional view of the present invention.

Fig. 2 is a schematic cross-sectional view of one embodiment of the needle roller of the present invention.

Wherein: 101, a body; 102. an end cap; 103. a shaft sleeve; 200. a belt pulley; 201. a connector; 300. an input shaft; 401. a primary planet carrier; 402. a primary planet wheel; 4021. a primary planet wheel axle; 4022. rolling needles; 4023. a primary planet gear outer gear ring; 4024. a primary axial oil hole; 4025. a first-stage radial oil hole; 403. a primary planet auxiliary frame; 404. a primary sun gear; 405. a primary annular gear; 406. a first-stage retainer ring; 501. a secondary planet carrier; 502. a secondary planet wheel; 5021. a secondary planet wheel axle; 5022a. a first roller pin; 5022b. a second roller pin; 5023. a secondary planet gear outer gear ring; 5024. a secondary axial oil hole; 5025. a secondary radial oil hole; 503. a secondary planet auxiliary frame; 504. a secondary sun gear; 505. a secondary annular gear; 506. and a secondary retainer ring.

Detailed Description

The invention will be further described with reference to examples of embodiments shown in the drawings to which:

the left and right directions in the present invention refer to the left and right directions in fig. 1.

As shown in fig. 1, the present invention provides a planetary gear differential comprising: the main body comprises a main body 101, end covers 102 and a shaft sleeve 103, the main body 101 is cylindrical, the number of the end covers 102 is two, the two end covers 102 are fixedly connected to the left end face and the right end face of the main body 101 through bolts, the shaft sleeve 103 is fixedly arranged on the end cover 102 positioned on the left end face of the main body 101 through bolts, and the shaft sleeve 103 is used for supporting the input shaft 300; the input shaft 300 is rotatably arranged on the shaft sleeve 103 in a penetrating way, the right end part of the input shaft 300 extends into the main body 101, and external power is transmitted from left to right along the input shaft 300; the belt pulley 200 is rotatably sleeved on the shaft sleeve 103 through a bearing, the outer ring of the connector 201 is connected with the belt pulley 200 through a bolt, and the inner ring of the connector 201 is in pin connection with the input shaft 300;

the primary planetary transmission mechanism is arranged in the main body 101 and comprises a primary planet carrier 401, a primary planet wheel 402, a primary planet auxiliary frame 403, a primary central gear 404, a primary annular gear 405 and a primary retainer ring 406, wherein the primary planet auxiliary frame 403 and the primary planet carrier 401 are respectively positioned at the left side and the right side of the primary planet wheel 402, the primary planet auxiliary frame 403 is rotatably connected to the end cover 102 positioned at the left end face of the main body 101 through a bearing, the right end part of the input shaft 300 penetrates through the middle part of the primary planet auxiliary frame 403 rightwards, the right end part of the input shaft 300 is integrally formed with the primary central gear 404, the primary central gear 404 is positioned between the primary planet auxiliary frame 403 and the primary planet carrier 401, and the primary annular gear 405 is fixedly arranged on the inner wall; the primary planet wheel 402 comprises a primary planet wheel shaft 4021, roller pins 4022 and a primary planet gear outer gear ring 4023, the primary planet wheel shaft 4021 is arranged between the primary planet auxiliary frame 403 and the primary planet carrier 401, the primary planet gear outer gear ring 4023 is rotatably sleeved on the primary planet wheel shaft 4021, the primary planet gear outer gear ring 4023 is simultaneously meshed with the primary central gear 404 and the primary inner gear ring 405, the roller pins 4022 are arranged between the outer circumferential surface of the primary planet wheel shaft 4021 and the inner circumferential surface of the primary planet gear outer gear ring 4023, the roller pins 4022 are provided with a plurality of roller pins 4022, the diameter of the roller pins 4022 is equal to the difference between the inner diameter of the primary planet gear outer gear ring 4023 and the outer diameter of the primary planet wheel shaft 4021, the primary retainer 406 is used for limiting the left and right movement of the roller pins 4022, the primary retainer 406 is arranged between the primary planet auxiliary frame 401/403 and, a gap of 0.3-0.8mm is formed between the inner side face of the primary retainer ring 406 and the end face of the roller needle 4022, so that the roller needle 4022 can move left and right at a certain distance when rolling but cannot protrude out of the end face of the primary planet wheel 402, lubricating oil is filled in a gap between the roller needle 4022 and the inner circumferential face of the primary planet wheel outer gear ring 4023 and the outer circumferential face of the primary planet wheel shaft 4021, and the lubricating oil flows in from a primary axial oil hole 4024 at the center of the primary planet wheel shaft 4021 and a primary radial oil hole 4025 which extends inwards from the outer circumferential face of the primary planet wheel shaft 4021 and is communicated with the primary axial oil hole;

the secondary planetary transmission mechanism is arranged in the main body 101 and comprises a secondary planet carrier 501, a secondary planet wheel 502, a secondary planet auxiliary carrier 503, a secondary sun gear 504, a secondary ring gear 505 and a secondary retainer ring 506, wherein the secondary planet carrier 501 is rotatably connected to the end cover 102 positioned on the right end face of the main body 101 through a bearing, the secondary planet carrier 501 is provided with a shaft end which extends rightwards through the end cover 102 and is used for outputting power, the secondary planet auxiliary carrier 503 and the secondary planet carrier 501 are respectively positioned on the left side and the right side of the secondary planet wheel 502, the middle part of the primary planet carrier 401 is provided with a shaft end which extends rightwards into the secondary planetary transmission mechanism 500, the secondary planet auxiliary carrier 503 is rotatably connected to the shaft end through a bearing, the secondary sun gear 504 is in key connection with the shaft end, the secondary sun gear 504 is positioned between the secondary planet auxiliary carrier 503 and the, the structure of the secondary planet wheel 502 is the same as that of the primary planet wheel 402, and the difference is that two sets of needle rollers are included in the secondary planet wheel 502, namely a first needle roller 5022a and a second needle roller 5022b, and the two sets of needle rollers can adapt to a secondary planet wheel outer gear ring 5023 with a wider tooth surface in the left-right direction under the condition that the length of the needle rollers is shorter, the secondary planet wheel outer gear ring 5023 is simultaneously meshed with the secondary sun gear 504 and the secondary inner gear ring 505, and the secondary retainer ring 506 has the same function and structure as the primary retainer ring 406, which is not described again.

In the above embodiments, the needle roller 4022, the first needle roller 5022a and the second needle roller 5022b have the same structure and the same characteristics, and are collectively referred to as needle rollers hereinafter, the needle rollers are made of plug gauges cut according to required lengths, the plug gauges are standard parts, are widely available and low in cost, and are suitable for mass use, the surface roughness of the outer circumferential surface of the needle rollers is less than 0.2 μm, the hardness of the outer circumferential surface is HRC58-63, the diameter of the outer circumferential surface is 5-10mm, the length of the needle rollers is determined according to the tooth width of the outer ring gear of the planet wheel in the left-right direction, and generally, the length of the needle rollers is less than 0.5-1mm of the.

The two end faces of the needle roller 4022 can also be made into convex hemispheres, as shown in fig. 2, which has the following advantages:

1. the contact area of the end face of the rolling needle roller and the inner wall of the retainer ring is reduced, and the friction force is reduced;

2. the contact area between the adjacent needle rollers in the left-right direction is reduced, and the friction force is reduced.

The above embodiments are merely illustrative of the technical concept and features of the present invention, and the purpose thereof is to enable those skilled in the art to understand the content of the present invention and implement the invention, and not to limit the scope of the invention, and all equivalent changes or modifications made according to the spirit of the present invention should be covered by the scope of the present invention.