CN210034302U - Large-speed-ratio hollow planetary reducer - Google Patents
Large-speed-ratio hollow planetary reducer Download PDFInfo
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- CN210034302U CN210034302U CN201920222075.2U CN201920222075U CN210034302U CN 210034302 U CN210034302 U CN 210034302U CN 201920222075 U CN201920222075 U CN 201920222075U CN 210034302 U CN210034302 U CN 210034302U
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Abstract
A large-speed-ratio hollow planetary reducer is characterized in that a large gear is mounted in an inner cavity of a shell, an input gear is arranged below the inner cavity of the shell, and the input gear is meshed with the large gear; a second connecting disc is fixed at the output end of the large gear, and a first planetary gear and a second planetary gear are fixed between the large gear and the second connecting disc through planetary shafts; a transition disc is sleeved above the second connecting disc, and a power output disc is fixed at the end part of the transition disc; the hollow gear shaft is arranged on the axis of the big gear, a fixed sun gear is arranged on the hollow gear shaft, and an output sun gear is sleeved in the hollow gear shaft in an empty mode; the fixed sun gear is meshed with the first planetary gear, the output sun gear is meshed with the second planetary gear, and the output sun gear is fixedly connected with the power output disc. The utility model discloses power input shaft and center pin biasing have guaranteed that the center pin can the cavity design, for other annex of equipment leave like cable, trachea etc. and arrange the space, have reduced the whole volume of speed reducer moreover.
Description
Technical Field
The utility model relates to an accurate speed reducer technical field, concretely relates to cavity formula planetary reducer in big velocity ratio.
Background
The planetary reducer has been widely used in the industrial field because of its characteristics of light weight, small size, large transmission ratio range, high efficiency, stable operation, low noise, strong adaptability, etc. In order to obtain a larger transmission ratio, a planetary reducer in the prior art is often designed into a two-stage or three-stage step-by-step reduction transmission structure, the multi-stage reduction transmission structure inevitably causes the problems of increased parts of the reducer, complex structure, increased appearance and the like, and the multi-stage structure is often incapable of designing a larger reduction ratio under the limitation of the appearance structure of the reducer.
SUMMERY OF THE UTILITY MODEL
The utility model provides a hollow planetary reducer with large speed ratio, which overcomes the defects of the prior art.
In order to achieve the above object, the utility model provides a following technical scheme: a large-speed-ratio hollow planetary reducer comprises a shell, wherein a large gear is mounted in an inner cavity of the shell through an input end bearing, a first connecting disc is fixed at the input end of the large gear, an input end gland is fixed at the input end of the shell, and the input end bearing is axially positioned through the input end gland and the first connecting disc; an input gear is arranged below the inner cavity of the shell, and the input gear is arranged on the input end gland and meshed with the large gear; the input end of the large gear is provided with first planet wheel shaft mounting holes which are uniformly distributed in an angular direction, and the output end of the large gear is provided with a cavity; a second connecting disc is fixed at the output end of the large gear, and second planet shaft mounting holes are formed in the second connecting disc and are distributed uniformly in an angular direction; a planet shaft is arranged between the first planet shaft mounting hole and the second planet shaft mounting hole through a bearing, a first planet gear and a second planet gear are fixed in the middle of the planet shaft, and the first planet gear and the second planet gear are positioned in the cavity; an output end gland is fixed at the output end of the shell, a transition disc is sleeved on the second connecting disc in a hollow manner, an output end bearing is arranged between the transition disc and the shell, and the output end bearing is axially positioned through the output end gland; a power output disc is fixed at the end part of the transition disc and protrudes out of the through hole of the output end gland;
the hollow gear shaft is arranged on the axis of the large gear, and two ends of the hollow gear shaft respectively penetrate through the power output disc and the input end gland; the hollow gear shaft is provided with a fixed sun gear, one end of the hollow gear shaft is fixed on the input end pressure cover, and the other end of the hollow gear shaft is sleeved with an output sun gear in an empty mode; the fixed sun gear is meshed with the first planetary gear, and the output sun gear is meshed with the second planetary gear; the output sun gear is arranged in the center of the second connecting disc through a bearing and is fixedly connected with the power output disc;
the number of teeth of the input gear is less than that of the gear wheel, the number of teeth of the fixed sun gear is less than that of the output sun gear, and the number of teeth of the first planetary gear is more than that of the second planetary gear.
The number of the first planet wheel shaft mounting holes and the number of the second planet wheel shaft mounting holes are 3-5, and the first planet wheel shaft mounting holes and the second planet wheel shaft mounting holes correspond to each other one by one.
The number difference of the teeth of the fixed sun gear and the output sun gear is 2-4 teeth, and the number difference of the teeth of the first planetary gear and the second planetary gear is 2-4 teeth.
The input end bearing and the output end bearing are both crossed roller bearings.
The utility model has the advantages and effects:
1. the power input shaft and the central shaft are offset, so that the central shaft can be designed in a hollow manner, arrangement space is reserved for other accessories of equipment such as cables, air pipes and the like, and the overall volume of the speed reducer is reduced;
2. the input gear and the large gear are meshed with each other through the external gear, and the external gear is simple and convenient to machine and assemble relative to the internal gear, low in cost and high in precision;
3. different transmission ratios can be obtained by changing the number of teeth of the input gear, and a larger reduction ratio can be obtained compared with the existing planetary reducer, and the transmission ratio range of the utility model reaches 3-300;
4. compared with the transmission of a RV speed reducer by utilizing a flexible gear, the utility model totally adopts the engagement of a straight cylindrical gear, can transmit larger torque and has low manufacturing cost;
5. for having secondary drive planetary reducer now, the utility model discloses internals still less, it is more convenient to assemble.
Drawings
Figure 1 is an exploded view of the structure of the utility model,
figure 2 is a structural section view of the utility model,
figure 3 is a schematic structural diagram of the input gear of the invention,
FIG. 4 is a schematic structural view of the hollow gear shaft of the present invention,
figure 5 is a schematic structural view of the output sun gear of the present invention,
fig. 6 and 7 are schematic structural views of the gear wheel of the present invention.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings 1-7 and the detailed description.
A large-speed-ratio hollow planetary reducer comprises a shell 4, wherein a large gear 3 is installed in an inner cavity of the shell 4 through an input end bearing 2, a first connecting disc 17 is fixed at the input end of the large gear 3, an input end gland 1 is fixed at the input end of the shell 4, and the input end bearing 2 is axially positioned through the input end gland 1 and the first connecting disc 17; an input gear 8 is arranged below the inner cavity of the shell 4, and the input gear 8 is arranged on the input end gland 1 and meshed with the large gear 3; the input end of the gearwheel 3 is provided with four first planet shaft mounting holes 16 which are distributed evenly at an angle, and the output end is provided with a cavity 18; a second connecting disc 14 is fixed at the output end of the large gear 3, and four second planet shaft mounting holes 19 which are uniformly distributed at an angle are formed in the second connecting disc 14; four planetary shafts 15 are respectively mounted between the four first planetary shaft mounting holes 16 and the four second planetary shaft mounting holes 19 through bearings, first planetary gears 7 and second planetary gears 6 are fixed in the middle parts of the four planetary shafts 15, and the first planetary gears 7 and the second planetary gears 6 are positioned in the cavities 18; an output end gland 13 is fixed at the output end of the shell 4, a transition disc 10 is sleeved on the second connecting disc 14 in an empty mode, an output end bearing 11 is arranged between the transition disc 10 and the shell 4, and the output end bearing 11 is axially positioned through the output end gland 13; a power output disc 12 is fixed at the end part of the transition disc 10, and the power output disc 12 protrudes from a through hole of an output end gland 13;
the hollow gear shaft 5 is arranged on the axis of the large gear 3, and two ends of the hollow gear shaft respectively penetrate through the power output disc 12 and the input end gland 1; the hollow gear shaft 5 is provided with a fixed sun gear 20, one end of the hollow gear shaft 5 is fixed on the input end gland 1, and the other end of the hollow gear shaft is sleeved with an output sun gear 9 in an empty mode; the fixed sun gear 20 meshes with the four first planet gears 7 at the same time, and the output sun gear 9 meshes with the four second planet gears 6 at the same time; the output sun gear 9 is arranged in the center of the second connecting disc 14 through a bearing, and the output sun gear 9 is fixedly connected with the power output disc 12; the number of teeth of the input gear 8 is less than that of the large gear 3, the number of teeth of the fixed sun gear 20 is less than that of the output sun gear, and the number of teeth of the first planetary gear 7 is more than that of the second planetary gear 6.
The difference between the number of teeth of the fixed sun gear 20 and the output sun gear 9 is 2-4 teeth, and the difference between the number of teeth of the first planetary gear 7 and the number of teeth of the second planetary gear 6 is 2-4 teeth. The input end bearing 2 and the output end bearing 11 are both cross roller bearings.
The utility model forms a first level dead axle speed reducing mechanism by the big gear 3 and the input gear 8; a second-stage planetary reduction mechanism is formed by the fixed sun gear 21, the output sun gear 9, the first planetary gear 7 and the second planetary gear 6, and transmission with a large reduction ratio is achieved.
The utility model discloses the theory of operation: the prime motor is coaxially connected with an input gear 8, the input gear 8 is meshed with a gearwheel 3 to form primary speed reduction, simultaneously, the gearwheel rotates to drive two groups of planet gears (four first planet gears 7 are a first group, four second planet gears 6 are a second group) to revolve along with the gearwheel through four planet shafts, the two groups of planet gears rotate while revolving around a fixed sun gear 21 and an output sun gear 9 respectively, because the fixed sun gear and the output sun gear have the tooth number difference (2-4 teeth) and the two groups of planet gears also have the tooth number difference (2-4 teeth), the first group of planet gears are meshed with the fixed sun gear, the second group of planet gears are meshed with the output sun gear, and in addition, the first planet gears 7 and the second planet gears 6 are coaxially fixed (connected through plain keys), the rotation speed of the first group of planet gears becomes the input power of the second group of planet gears, the second group of planetary gears drives the output sun gear to form two-stage speed reduction; according to the differential deceleration principle, the output sun gear is greatly decelerated in accordance with the relationship of the gear ratio, and torque is output through the power output disc 12. Through changing the number of teeth of the input gear, different transmission ratios can be obtained, and a larger reduction ratio can be obtained compared with the existing planetary reducer, the utility model discloses a transmission ratio scope has reached 3-300.
Furthermore, the hollow gear shaft 5 of the present invention has an axial hollow structure 21 for accommodating wires, such as cables and air pipes. The overall occupied volume of the planetary reducer can be effectively reduced, and the purpose of product miniaturization is achieved.
The above-mentioned embodiments are merely preferred embodiments of the present invention, and not intended to limit the scope of the present invention, so that all equivalent changes made by the contents of the claims of the present invention should be included in the scope of the claims of the present invention.
Claims (4)
1. The utility model provides a hollow planetary reducer of big velocity ratio, includes casing (4), characterized by:
the input end bearing (2) is axially positioned through the input end gland (1) and the first connecting disc (17); an input gear (8) is arranged below the inner cavity of the shell (4), and the input gear (8) is arranged on the input end gland (1) and meshed with the large gear (3); the input end of the large gear (3) is provided with first planet wheel shaft mounting holes (16) which are uniformly distributed at an angle, and the output end of the large gear is provided with a cavity (18); a second connecting disc (14) is fixed at the output end of the large gear (3), and second planet wheel shaft mounting holes (19) which are distributed evenly in an angular direction are formed in the second connecting disc (14); a planet shaft (15) is arranged between the first planet shaft mounting hole (16) and the second planet shaft mounting hole (19) through a bearing, a first planet gear (7) and a second planet gear (6) are fixed in the middle of the planet shaft (15), and the first planet gear (7) and the second planet gear (6) are positioned in the cavity (18); an output end gland (13) is fixed at the output end of the shell (4), a transition disc (10) is sleeved above the second connecting disc (14), an output end bearing (11) is arranged between the transition disc (10) and the shell (4), and the output end bearing (11) is axially positioned through the output end gland (13); a power output disc (12) is fixed at the end part of the transition disc (10), and the power output disc (12) protrudes from a through hole of the output end gland (13);
the hollow gear shaft (5) is arranged on the axis of the large gear (3), and two ends of the hollow gear shaft respectively penetrate through the power output disc (12) and the input end gland (1); a fixed sun gear (20) is arranged on the hollow gear shaft (5), one end of the hollow gear shaft (5) is fixed on the input end gland (1), and the other end of the hollow gear shaft is sleeved with an output sun gear (9) in an empty way; the fixed sun gear (20) is meshed with the first planetary gear (7), and the output sun gear (9) is meshed with the second planetary gear (6); the output sun gear (9) is mounted in the center of the second connecting disc (14) through a bearing, and the output sun gear (9) is fixedly connected with the power output disc (12);
the number of teeth of input gear (8) is less than the number of teeth of gear wheel (3), the number of teeth of fixed sun gear (20) is less than the number of teeth of output sun gear, and the number of teeth of first planetary gear (7) is more than the number of teeth of second planetary gear (6).
2. The high-speed-ratio hollow planetary reducer according to claim 1, wherein: the number of the first planet wheel shaft mounting holes (16) and the number of the second planet wheel shaft mounting holes (19) are 3-5, and the first planet wheel shaft mounting holes and the second planet wheel shaft mounting holes correspond to each other one by one.
3. The high-speed-ratio hollow planetary reducer according to claim 1 or 2, wherein: the difference between the number of teeth of the fixed sun gear (20) and the output sun gear is 2-4 teeth, and the difference between the number of teeth of the first planetary gear (7) and the number of teeth of the second planetary gear (6) is 2-4 teeth.
4. The high-speed-ratio hollow planetary reducer according to claim 3, wherein: the input end bearing (2) and the output end bearing (11) are both crossed roller bearings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920222075.2U CN210034302U (en) | 2019-02-22 | 2019-02-22 | Large-speed-ratio hollow planetary reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920222075.2U CN210034302U (en) | 2019-02-22 | 2019-02-22 | Large-speed-ratio hollow planetary reducer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210034302U true CN210034302U (en) | 2020-02-07 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920222075.2U Withdrawn - After Issue CN210034302U (en) | 2019-02-22 | 2019-02-22 | Large-speed-ratio hollow planetary reducer |
Country Status (1)
| Country | Link |
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| CN (1) | CN210034302U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109751368A (en) * | 2019-02-22 | 2019-05-14 | 陕西捷泰智能传动股份有限公司 | A kind of large speed ratio hollow type planetary reducer |
-
2019
- 2019-02-22 CN CN201920222075.2U patent/CN210034302U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109751368A (en) * | 2019-02-22 | 2019-05-14 | 陕西捷泰智能传动股份有限公司 | A kind of large speed ratio hollow type planetary reducer |
| CN109751368B (en) * | 2019-02-22 | 2023-06-02 | 陕西捷泰智能传动有限公司 | Hollow planetary reducer with large speed ratio |
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Legal Events
| Date | Code | Title | Description |
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| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 721008 No. 13 Jufu East Road, Weibin District, Baoji City, Shaanxi Province Patentee after: Shaanxi Jietai intelligent transmission Co.,Ltd. Address before: 721008 No. 13 Jufu East Road, Weibin District, Baoji City, Shaanxi Province Patentee before: SHAANXI JIETAI INTELLIGENT TRANSMISSION Co.,Ltd. |
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| CP01 | Change in the name or title of a patent holder | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20200207 Effective date of abandoning: 20230602 |
|
| AV01 | Patent right actively abandoned |
Granted publication date: 20200207 Effective date of abandoning: 20230602 |
|
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |