CN216923067U - 3K-II type planetary reducer - Google Patents
3K-II type planetary reducer Download PDFInfo
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- CN216923067U CN216923067U CN202220245729.5U CN202220245729U CN216923067U CN 216923067 U CN216923067 U CN 216923067U CN 202220245729 U CN202220245729 U CN 202220245729U CN 216923067 U CN216923067 U CN 216923067U
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Abstract
A3K-II type planetary reducer comprises a planetary gear mechanism arranged in a shell, wherein an output inner gear ring is a cup-shaped flexible output inner gear ring, and the flexible output inner gear ring comprises a cup-shaped gear ring wall, a cup bottom perpendicular to the gear ring wall and an output shaft perpendicular to the central position of the cup bottom; the wall of the gear ring is of a thin-wall structure, a circle of internal teeth is arranged on the inner wall of the cup opening, and the inner wall close to the cup bottom is a smooth inner wall; the wall thickness of the tooth root of the inner tooth is a, the wall thickness of the smooth inner wall is b, and the outer diameter of the gear ring wall is d; root wall thickness a = (0.01-0.02) d; the wall thickness b = (0.8-1) a of the smooth inner wall. The output inner gear ring is a flexible output inner gear ring which is thin-walled and can radially deform, so that the planet gear can be always meshed with the flexible output inner gear ring in the rotating process, the backlash generated by factors such as machining errors is eliminated, and the return difference of the speed reducer is effectively reduced.
Description
Technical Field
The utility model belongs to the technical field of speed reducers, and particularly relates to a 3K-II type planetary speed reducer.
Background
As shown in fig. 1, the 3K-ii planetary reducer is mainly composed of a sun gear 1, an end cover 2, a housing 3, a gear fixing ring 4, a fixed steel wheel 5, a planetary gear 6, a planet carrier 7, and an output internal gear 8.
As shown in fig. 2, the transmission principle of the 3K-ii type planetary reducer is as follows: because the number of teeth of the fixed steel wheel 5 is not equal to that of the output inner gear 8, when the input shaft drives the central wheel 1 to rotate at a high speed, the motion of the central wheel 1 can be transmitted to the output inner gear 8 through the planet wheel 6, and then the output inner gear 8 with reduced rotating speed drives the output shaft to rotate, so that the increased torque is output.
At present, a 3K-II type planetary reducer is used as a novel planetary gear transmission, and compared with a common planetary reducer, the transmission ratio range of the 3K-II type planetary reducer is 50-330. The transmission mechanism has the characteristics of compact structure, large transmission ratio and high transmission efficiency. The method is widely applied to the industries of aerospace, electronic instruments, ships and the like.
Although the existing 3K-II type planetary reducer has the advantages, the existing 3K-II type planetary reducer not only needs high transmission precision, but also needs small return difference and long service life in some special use environments, such as a speed reducing mechanism used as a sensor. The existing 3K-II type planetary reducer has the problems of low transmission precision and large return difference (not less than 20') due to the fact that the structure is not optimized enough, and is only suitable for short-term and intermittent work. These problems arise because: the accumulation of machining errors causes backlash between the output inner gear and the planetary gear tooth part, and the backlash is a main reason for large return difference. Although the machining error can be reduced by the machining accuracy, the machining error inevitably occurs. Therefore, how to eliminate the backlash between the output inner gear and the tooth part of the planet gear is a problem which needs to be solved urgently.
In addition, the structure of the existing 3K-II type planetary reducer has defects in details: the fixed steel wheel 5 and the gear fixing ring 4 are theoretically coaxial, but because the two independent components are used, the gear fixing ring 4 is fixedly connected with the shell 3 firstly and then fixedly connected with the fixed steel wheel 5 in a coaxial mode in actual connection, and good coaxiality of the two parts is difficult to guarantee. In addition, the output internal gear 8 and the housing 3 are connected through only one pair of bearings, so that the output internal gear 8 is easy to generate radial deflection under the action of load, and the transmission precision is influenced.
Disclosure of Invention
In view of this, the present invention provides a 3K-ii type planetary reducer, which can effectively eliminate the gap between the output inner gear and the tooth portion of the planet gear, so as to reduce the backlash.
The technical scheme adopted by the utility model is as follows: A3K-II type planetary reducer comprises a planetary gear mechanism arranged in a shell, wherein the planetary gear mechanism comprises a central wheel, a planet carrier, three planet wheels, a fixed inner gear and an output inner gear ring; the method is characterized in that: the flexible output inner gear ring comprises a cup-shaped gear ring wall, a cup bottom perpendicular to the gear ring wall and an output shaft perpendicular to the central position of the cup bottom; the wall of the gear ring is of a thin-wall structure, a circle of internal teeth are arranged on the inner wall of the cup opening of the wall of the gear ring, and the inner wall of the gear ring, close to the cup bottom, is a smooth inner wall; the wall thickness of the tooth root of the inner tooth in the wall of the gear ring is a, the wall thickness of the transition fillet between the wall of the gear ring and the cup bottom is c, and the outer diameter of the wall of the gear ring is d;
root wall thickness a = (0.01-0.02) d;
the wall thickness b = (0.8-1) a of the smooth inner wall.
Furthermore, one side of the cup bottom, which is located on the gear ring wall, is a vertical plane, one side of the cup bottom, which is located on the output shaft, is an inclined plane, the wall thickness of the cup bottom is linearly increased from the joint of the gear ring wall and the cup bottom to the joint of the cup bottom and the output shaft, and the inclination angle alpha of the cup bottom is 2-5 degrees.
Further, the wall of the gear ring and the cup bottom are in transition through a fillet, the wall thickness of the transition fillet of the gear ring wall and the cup bottom is c, and the wall thickness of the transition fillet is c = b.
Furthermore, a circle of step circle is arranged at the joint of the cup bottom and the output shaft, and the cup bottom and the step circle are transited through a fillet.
Furthermore, the planet carrier is connected with a shaft lever of the central wheel through a bearing, the three planet wheels are positioned on the planet carrier through shaft pins and deep groove ball bearings, and the three planet wheels are engaged among the central wheel, the fixed inner gear and the output inner gear ring at equal intervals. An end cover is fixed at the front end of the shell, a front-section shaft lever of the central wheel is fixed at the central position of the end cover through a deep groove ball bearing, a rear-section shaft lever of the central wheel is coaxially connected with an output shaft of the flexible output inner gear ring through a bearing, the fixed inner gear is fixedly connected with the shell through a screw, the fixed inner gear ring is coaxial with the flexible output inner gear ring, and the output shaft of the flexible output inner gear ring is connected with the shell through a bearing.
Furthermore, the output shaft of the flexible output inner gear ring is connected with the shell through two pairs of bearings.
The utility model has the beneficial effects that: the output inner gear ring is a flexible output inner gear ring which is thin-walled and can radially deform, so that the planet gear can be always meshed with the flexible output inner gear ring in the rotating process, the backlash generated by factors such as machining errors is eliminated, and the return difference of the speed reducer is effectively reduced. In addition, the cup bottom of the flexible output inner gear ring is designed to be of a structure with the thickness increasing gradually, so that the stress concentration at the bent part of the cup bottom and the output shaft is effectively reduced, the overall structural strength of the flexible output inner gear ring is improved, and the bearing capacity and the service life of the speed reducer are further improved.
Drawings
Fig. 1 is a schematic structural view of a conventional 3K-ii type planetary reduction gear.
Fig. 2 is a schematic diagram of a 3K-ii type planetary reduction gear.
Fig. 3 is a schematic structural diagram of the present invention.
Fig. 4 is a schematic view of the connection structure of the planetary wheel, the central wheel and the flexible output steel wheel in the 3K-ii type planetary reducer.
Fig. 5 is a structural schematic diagram of the flexible output ring gear in the utility model.
In the figure: 1. the device comprises a central wheel, 2, end covers, 3, a shell, 4, a gear fixing ring, 5, a fixing steel wheel, 6, a planet wheel, 7, a planet carrier, 8, an output inner gear, 9, a deep groove ball bearing, 10, a pin shaft, 11, a screw, 12, a fixing inner gear, 13, a deep groove ball bearing, 14, a bearing, 15, a flexible output inner gear, 16, a gear ring wall, 17, a cup bottom, 18, an output shaft, 19 and a bearing.
Detailed Description
In order to make the technical solutions of the present invention better understood by those skilled in the art, the present invention will be further described in detail with reference to the accompanying drawings and specific embodiments.
As shown in fig. 3, a 3K-ii type planetary reducer includes a planetary gear mechanism provided in a housing 3, the planetary gear mechanism including a sun gear 1, a planet carrier 7, three planet gears 6, a fixed internal gear 12, and a flexible output internal gear 15 as an input shaft. The flexible output inner gear ring 15 is of a cup-shaped structure and comprises a cup-shaped gear ring wall 16, a cup bottom 17 perpendicular to the gear ring wall 16 and an output shaft 18 perpendicular to the central position of the cup bottom 17. The planet carrier 7 is connected with the shaft of the center wheel 1 through a bearing. Three planet wheels 6 are positioned on the planet carrier 7 by means of axle pins 10 and deep groove ball bearings 13. As shown in fig. 4, three planetary gears 6 are engaged at equal intervals between the sun gear 1 and the fixed inner gear 12 and the output inner gear. The end cap 2 is fixed to the front end of the housing 3. The front section shaft lever of the central wheel 1 is fixed at the central position of the end cover 2 through a deep groove ball bearing 9. The rear end shaft rod of the central wheel 1 is coaxially connected with an output shaft 18 of the flexible output inner gear ring 15 through a bearing 14. The fixed ring gear 12 is fixedly connected to the housing 3. An output shaft 18 of the flexible output ring gear 15 is connected with the shell 3 through a bearing 19.
The transmission principle of the utility model is consistent with the prior art, and is shown in figure 2. The utility model mainly improves the structure of the output internal gear 8, and changes the original output internal gear 8 into the flexible output internal gear 15. The gear ring wall 16 of the flexible output inner gear ring 15 has the characteristics of thin wall and easy deformation, and can be meshed with the planet gear 6, so that the purpose of eliminating backlash is achieved, and return difference is reduced. The concrete structure is as follows:
as shown in fig. 5, the flexible output ring gear 15 is a cup-shaped structure, and includes a cup-shaped ring gear wall 16, a cup bottom 17 perpendicular to the ring gear wall 16, and an output shaft 18 perpendicular to the central position of the cup bottom 17. The ring gear wall 16 is of thin-walled construction. The inner wall of the cup opening of the gear ring wall 16 is provided with a circle of internal teeth, and the inner wall of the gear ring wall 16 close to the cup bottom 17 is a smooth inner wall. The ring gear wall 16, the cup bottom 17, and the output shaft 18 are integrally formed, and have no welding point or connecting seam.
In order to ensure that the flexible output inner gear ring 15 has flexible deformability and deformation strength at the same time. The rim wall 16 and the cup bottom 17 are in transition through a fillet. As shown in fig. 4, the thickness of the root of the internal teeth in the ring gear wall 16 is a, the thickness of the smooth inner wall in the ring gear wall 16 is b, the thickness of the transition fillet between the ring gear wall 16 and the cup bottom 17 is c, and the outer diameter of the ring gear wall 16 is d.
Root wall thickness a = (0.01-0.02) d.
The wall thickness b = (0.8-1) a of the smooth inner wall.
The wall thickness of the transition fillet c = b.
When the cup bottom 17 of the flexible output inner gear ring 15 bears a certain torque, under the condition that the wall thickness of the cup bottom 17 is uniform, the tangential stress of the cup bottom 17 is gradually increased from the bending point of the gear ring wall 16 and the cup bottom 17 to the bending point of the cup bottom 17 and the output shaft 18. It can be seen that the tangential stress is mainly concentrated at the bending point of the cup bottom 17 and the output shaft 18. From which a fracture is likely to occur under a continuous load.
In order to improve the structural strength of the flexible output inner gear ring 15 and improve the stress concentration degree of the cup bottom 17, the cup bottom 17 is designed to be of a structure with gradually increased wall thickness. The specific structure is shown in fig. 5.
The side of the cup bottom 17 on the gear ring wall 16 is a vertical plane, and the side of the cup bottom 17 on the output shaft 18 is an inclined plane. The wall thickness of the cup bottom 17 increases linearly from the transition fillet of the ring gear wall 16 and the cup bottom 17 to the fillet of the cup bottom 17 and the output shaft 18. The inclination angle alpha of the cup bottom 17 is designed to be 2-5 degrees. In order to further enhance the bearing strength of the cup bottom 17 and the output shaft 18, a circle of step circle is arranged at the bending point of the cup bottom 17 and the output shaft 18, and the cup bottom 17 and the step circle are also transited through a fillet.
The design of gradually increasing the wall thickness of the cup bottom 17 and increasing the step circle ensures that when the flexible output inner gear ring 15 bears torque, the tangential stress of all parts of the cup bottom 17 is basically the same, as shown by arrows in fig. 5. The stress concentration at the bent part of the cup bottom 17 and the output shaft 18 is effectively reduced, the overall structural strength of the flexible output inner gear ring 15 is improved, and the bearing capacity and the service life of the speed reducer are further improved.
The fixed internal gear 12 is directly and fixedly connected with the shell 3 through the screw 11, the outer circle of the fixed internal gear 12 is positioned, the original connecting structure of the gear fixing ring 4 is removed, and the coaxiality of the fixed internal gear 12, the central wheel 1 and the flexible output inner gear ring 15 is improved. The transmission precision of the 3K-II type planetary reducer is further improved.
The output shaft 18 of the flexible output ring gear 15 is connected with the shell 3 through two pairs of bearings 19. The radial deflection of the output shaft 18 of the flexible output inner gear ring 15 can be eliminated, so that the transmission precision and the transmission stability are improved.
The structural design of the flexible output inner gear ring 15 ensures that the gear ring wall 16 can generate slight deformation in the radial direction, thereby ensuring that the inner gear ring and the planet wheel 6 are always in zero-clearance engagement and the return difference is less than or equal to 6'. The 3K-II type planetary reducer has the advantages of large transmission ratio, high transmission precision and small return difference. In addition, the service life of the 3K-II type planetary speed reducer is prolonged by optimizing the structural design.
Claims (6)
1. A3K-II type planetary reducer comprises a planetary gear mechanism arranged in a shell, wherein the planetary gear mechanism comprises a central wheel, a planet carrier, three planet wheels, a fixed inner gear and an output inner gear ring; the method is characterized in that: the flexible output inner gear ring comprises a cup-shaped gear ring wall, a cup bottom perpendicular to the gear ring wall and an output shaft perpendicular to the central position of the cup bottom; the wall of the gear ring is of a thin-wall structure, a circle of internal teeth are arranged on the inner wall of the cup opening of the wall of the gear ring, and the inner wall of the gear ring, close to the cup bottom, is a smooth inner wall; the wall thickness of the tooth root of the inner tooth in the wall of the gear ring is a, the wall thickness of the smooth inner wall in the wall of the gear ring is b, and the outer diameter of the wall of the gear ring is d;
root wall thickness a = (0.01-0.02) d;
the wall thickness b = (0.8-1) a of the smooth inner wall.
2. A 3K-ii type planetary reducer according to claim 1, wherein: one side of the cup bottom, which is located on the gear ring wall, is a vertical plane, one side of the cup bottom, which is located on the output shaft, is an inclined plane, the wall thickness of the cup bottom is linearly increased from the joint of the gear ring wall and the cup bottom to the joint of the cup bottom and the output shaft, and the inclination angle alpha of the cup bottom is 2-5 degrees.
3. A 3K-ii type planetary reducer according to claim 1, wherein: the wall of the gear ring and the cup bottom are in transition through a fillet, the wall thickness of the transition fillet of the wall of the gear ring and the cup bottom is c, and the wall thickness of the transition fillet is c = b.
4. A 3K-ii type planetary reducer according to claim 1, wherein: a circle of step circle is arranged at the joint of the cup bottom and the output shaft, and the cup bottom and the step circle are transited through a fillet.
5. A 3K-ii type planetary reducer according to claim 1, characterized in that: the planet carrier is connected with a shaft lever of the central wheel through a bearing, the three planet wheels are positioned on the planet carrier through shaft pins and deep groove ball bearings, and the three planet wheels are engaged among the central wheel, the fixed inner gear and the output inner gear ring at equal intervals; an end cover is fixed at the front end of the shell, a front-section shaft lever of the central wheel is fixed at the central position of the end cover through a deep groove ball bearing, a rear-section shaft lever of the central wheel is coaxially connected with an output shaft of the flexible output inner gear ring through a bearing, the fixed inner gear is fixedly connected with the shell through a screw, the fixed inner gear ring is coaxial with the flexible output inner gear ring, and the output shaft of the flexible output inner gear ring is connected with the shell through a bearing.
6. A 3K-ii type planetary reducer according to claim 5, wherein: the output shaft of the flexible output inner gear ring is connected with the shell through two pairs of bearings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220245729.5U CN216923067U (en) | 2022-01-30 | 2022-01-30 | 3K-II type planetary reducer |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220245729.5U CN216923067U (en) | 2022-01-30 | 2022-01-30 | 3K-II type planetary reducer |
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| Publication Number | Publication Date |
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| CN216923067U true CN216923067U (en) | 2022-07-08 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202220245729.5U Active CN216923067U (en) | 2022-01-30 | 2022-01-30 | 3K-II type planetary reducer |
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| CN (1) | CN216923067U (en) |
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- 2022-01-30 CN CN202220245729.5U patent/CN216923067U/en active Active
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