CN109751368B - Hollow planetary reducer with large speed ratio - Google Patents
Hollow planetary reducer with large speed ratio Download PDFInfo
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- CN109751368B CN109751368B CN201910131263.9A CN201910131263A CN109751368B CN 109751368 B CN109751368 B CN 109751368B CN 201910131263 A CN201910131263 A CN 201910131263A CN 109751368 B CN109751368 B CN 109751368B
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Abstract
A large-speed ratio hollow planetary reducer is characterized in that a large gear is arranged 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; the output end of the large gear is fixed with a second connecting disc, 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 large gear, the hollow gear shaft is provided with a fixed sun gear, and an output sun gear is sleeved in the hollow gear shaft; 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 power input shaft is offset from the central shaft, so that the central shaft can be designed in a hollow mode, a layout space is reserved for other accessories of the equipment such as cables, air pipes and the like, and the whole size of the speed reducer is reduced.
Description
Technical Field
The invention relates to the technical field of precision speed reducers, in particular to a large-speed-ratio hollow planetary speed reducer.
Background
The planetary reducer has the characteristics of light weight, small volume, large transmission ratio range, high efficiency, stable operation, low noise, strong adaptability and the like, and is widely applied to the industrial field. In order to obtain a larger transmission ratio, the planetary reducer in the prior art is often designed into a two-stage or three-stage step-by-step speed reducing transmission structure, the multi-stage speed reducing transmission structure inevitably causes the problems of increased parts, complex structure, increased appearance and the like of the reducer, the multi-stage structure often cannot be designed into a larger reduction ratio under the limit of the appearance structure of the reducer, moreover, if the planetary reducer is used as a robot reducer, the size is required to be smaller, and other auxiliary devices such as power lines or air pipes are required to be arranged, but the devices must occupy additional space for accommodating, so that the whole size of the reducer is increased, and the requirement of the robot reducer cannot be met.
Disclosure of Invention
The invention provides a large-speed-ratio hollow planetary reducer, which overcomes the defects of the prior art.
In order to achieve the above purpose, the present invention provides the following technical solutions: the large-speed-ratio hollow planetary reducer comprises a shell, wherein a large gear is arranged 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 is arranged on the input end pressing cover and meshed with the large gear; the input end of the large gear is provided with first planet wheel shaft mounting holes uniformly distributed in the angular direction, and the output end of the large gear is provided with a cavity; the output end of the large gear is fixed with a second connecting disc, and second planetary gear shaft mounting holes uniformly distributed in the angle direction are formed in the second connecting disc; a planetary shaft is arranged between the first planetary shaft mounting hole and the second planetary shaft mounting hole through bearings, a first planetary gear and a second planetary gear are fixed in the middle of the planetary shaft, and the first planetary gear and the second planetary gear are positioned in the cavity; an output end gland is fixed at the output end of the shell, a transition disc is sleeved above the second connecting disc, 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; the end part of the transition disc is fixed with a power output disc, and the power output disc protrudes from a 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 pressing cover, and the other end of the hollow gear shaft is sleeved with an output sun gear; 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 smaller than that of the large gear, the number of teeth of the fixed sun gear is smaller than that of the output sun gear, and the number of teeth of the first planetary gear is larger than that of the second planetary gear.
The number of the first planet wheel shaft mounting holes and the second planet wheel shaft mounting holes is 3-5, and the first planet wheel shaft mounting holes and the second planet wheel shaft mounting holes are in one-to-one correspondence.
The difference of the teeth numbers of the fixed sun gear and the output sun gear is 2-4 teeth, and the difference of the teeth numbers of the first planetary gear and the second planetary gear is 2-4 teeth.
The input end bearing and the output end bearing are crossed roller bearings.
The invention has the advantages and effects that:
1. the power input shaft is offset from the central shaft, so that the central shaft can be designed in a hollow mode, a layout space is reserved for other accessories of the equipment such as cables, air pipes and the like, and the whole volume of the speed reducer is reduced;
2. the input gear and the large gear are meshed by the external gear, and the external gear is simple and convenient to process and assemble relative to the internal gear, low in cost and high in precision;
3. different transmission ratios are obtained by changing the number of teeth of the input gear, and a larger reduction ratio can be obtained relative to the existing planetary speed reducer, and the transmission ratio range of the invention reaches 3-300;
4. compared with the RV reducer which utilizes the transmission of a flexible gear, the invention adopts cylindrical spur gear meshing, can transfer larger torque and has low manufacturing cost;
5. compared with the existing two-stage transmission planetary reducer, the planetary reducer has fewer internal parts and is more convenient to assemble.
Drawings
Figure 1 is an exploded view of the structure of the present invention,
figure 2 is a cross-sectional view of the structure of the present invention,
figure 3 is a schematic structural view of an input gear of the present invention,
figure 4 is a schematic structural view of the hollow gear shaft of the present invention,
figure 5 is a schematic diagram of the structure of the output sun gear of the present invention,
fig. 6 and 7 are schematic structural views of the large gear of the present invention.
Detailed Description
The invention is described in detail below with reference to fig. 1-7 and the detailed description.
The large-speed-ratio hollow planetary reducer comprises a shell 4, wherein a large gear 3 is arranged 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 large gear 3 is provided with four first planet shaft mounting holes 16 uniformly distributed in the angular direction, and the output end is provided with a cavity 18; the output end of the large gear 3 is fixedly provided with a second connecting disc 14, and the second connecting disc 14 is provided with four second planet shaft mounting holes 19 uniformly distributed in the angular direction; four planetary shafts 15 are respectively arranged between the four first planetary shaft mounting holes 16 and the four second planetary shaft mounting holes 19 through bearings, a first planetary gear 7 and a second planetary gear 6 are fixed in the middle of each of the four planetary shafts 15, and the first planetary gear 7 and the second planetary 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 on the second connecting disc 14 in a hollow 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; the end part of the transition disc 10 is fixed with a power output disc 12, 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 is sleeved with an output sun gear 9; the fixed sun gear 20 is meshed with the four first planetary gears 7 at the same time, and the output sun gear 9 is meshed with the four second planetary 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 smaller than that of the large gear 3, the number of teeth of the fixed sun gear 20 is smaller than that of the output sun gear, and the number of teeth of the first planetary gear 7 is larger than that of the second planetary gear 6.
The difference between the teeth numbers of the fixed sun gear 20 and the output sun gear 9 is (2-4 teeth), and the difference between the teeth numbers of the first planetary gear 7 and the second planetary gear 6 is (2-4 teeth). The input end bearing 2 and the output end bearing 11 are crossed roller bearings.
The invention forms a first-stage fixed-shaft speed reducing mechanism through the large gear 3 and the input gear 8; the fixed sun gear 21, the output sun gear 9, the first planetary gears 7 and the second planetary gears 6 form a second-stage planetary reduction mechanism, so that transmission with a larger reduction ratio is realized.
The working principle of the invention is as follows: the prime mover is coaxially connected with the input gear 8, the input gear 8 is meshed with the large gear 3 to form primary speed reduction, meanwhile, the large gear rotates to drive two groups of planetary gears (four first planetary gears 7 are in a first group, four second planetary gears 6 are in a second group) to revolve along with the large gear through four planetary shafts, the two groups of planetary gears revolve around the fixed sun gear 20 and the output sun gear 9 respectively and rotate simultaneously, the fixed sun gear and the output sun gear have tooth number differences (2-4 teeth), the two groups of planetary gears also have tooth number differences (2-4 teeth), the first group of planetary gears are meshed with the fixed sun gear, the second group of planetary gears are meshed with the output sun gear, and the first planetary gears 7 and the second planetary gears 6 are coaxially fixed (connected through flat keys), so that the rotation speed of the first group of planetary gears becomes the input power of the second group of planetary gears, and the second group of planetary gears drives the output sun gear to form secondary speed reduction; according to the differential reduction principle, the output sun gear is greatly reduced in terms of the gear ratio, and torque is output through the power output disc 12. Different transmission ratios can be obtained by changing the number of teeth of the input gear, and a larger reduction ratio can be obtained relative to the existing planetary speed reducer, and the transmission ratio range of the invention reaches 3-300.
In addition, the hollow axial structure 21 provided in the hollow gear shaft 5 of the present invention accommodates wires, such as cables, air pipes, and the like. The whole occupied volume of the planetary reducer can be effectively reduced, so that the purpose of product miniaturization is achieved.
The above embodiments are only preferred embodiments of the present invention and are not intended to limit the scope of the present invention, so that all equivalent modifications made by the appended claims shall be included in the scope of the present invention.
Claims (4)
1. The utility model provides a big speed ratio cavity formula planetary reducer, includes casing (4), characterized by:
the inner cavity of the shell (4) is internally provided with a large gear (3) through an input end bearing (2), the input end of the large gear (3) is fixedly provided with a first connecting disc (17), the input end of the shell (4) is fixedly provided with an input end gland (1), 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 large gear (3) is provided with first planet wheel shaft mounting holes (16) uniformly distributed in the angle direction, and the output end is provided with a cavity (18); the output end of the large gear (3) is fixedly provided with a second connecting disc (14), and second planetary gear shaft mounting holes (19) which are uniformly distributed in the angle direction are formed in the second connecting disc (14); a planetary shaft (15) is arranged between the first planetary shaft mounting hole (16) and the second planetary shaft mounting hole (19) through bearings, a first planetary gear (7) and a second planetary gear (6) are fixed in the middle of the planetary shaft (15), and the first planetary gear (7) and the second planetary 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 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); 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 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 smaller than that of the large gear (3), the number of teeth of the fixed sun gear (20) is smaller than that of the output sun gear, and the number of teeth of the first planetary gear (7) is larger than that of the second planetary gear (6).
2. The large-speed-ratio hollow planetary reducer according to claim 1, characterized in that: 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 large speed ratio hollow planetary reducer according to claim 1 or 2, characterized in that: the difference of the teeth number of the fixed sun gear (20) and the output sun gear is 2-4 teeth, and the difference of the teeth number of the first planetary gear (7) and the second planetary gear (6) is 2-4 teeth.
4. A large speed ratio hollow planetary reducer according to claim 3, characterized in that: the input end bearing (2) and the output end bearing (11) are crossed roller bearings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910131263.9A CN109751368B (en) | 2019-02-22 | 2019-02-22 | Hollow planetary reducer with large speed ratio |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910131263.9A CN109751368B (en) | 2019-02-22 | 2019-02-22 | Hollow planetary reducer with large speed ratio |
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| CN109751368A CN109751368A (en) | 2019-05-14 |
| CN109751368B true CN109751368B (en) | 2023-06-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201910131263.9A Active CN109751368B (en) | 2019-02-22 | 2019-02-22 | Hollow planetary reducer with large speed ratio |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5993348A (en) * | 1995-07-06 | 1999-11-30 | Asea Brown Boveri Ab | Compact toothed wheel gearing with large gear ratio |
| CN105114535A (en) * | 2015-08-10 | 2015-12-02 | 重庆清平机械有限责任公司 | Hollow planetary speed reducer with eccentric input |
| CN108019472A (en) * | 2018-01-29 | 2018-05-11 | 王维 | Planetary reducer |
| CN210034302U (en) * | 2019-02-22 | 2020-02-07 | 陕西捷泰智能传动股份有限公司 | Large-speed-ratio hollow planetary reducer |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE602004008288T2 (en) * | 2004-09-29 | 2008-05-15 | Nexxtdrive Ltd. | Hub with a drive with variable ratio |
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2019
- 2019-02-22 CN CN201910131263.9A patent/CN109751368B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5993348A (en) * | 1995-07-06 | 1999-11-30 | Asea Brown Boveri Ab | Compact toothed wheel gearing with large gear ratio |
| CN105114535A (en) * | 2015-08-10 | 2015-12-02 | 重庆清平机械有限责任公司 | Hollow planetary speed reducer with eccentric input |
| CN108019472A (en) * | 2018-01-29 | 2018-05-11 | 王维 | Planetary reducer |
| CN210034302U (en) * | 2019-02-22 | 2020-02-07 | 陕西捷泰智能传动股份有限公司 | Large-speed-ratio hollow planetary reducer |
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| CN109751368A (en) | 2019-05-14 |
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Address after: 721008 No. 13 Jufu East Road, Weibin District, Baoji City, Shaanxi Province Applicant after: Shaanxi Jietai intelligent transmission Co.,Ltd. Address before: 721008 No. 13 Jufu East Road, Weibin District, Baoji City, Shaanxi Province Applicant before: SHAANXI JIETAI INTELLIGENT TRANSMISSION Co.,Ltd. |
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| PE01 | Entry into force of the registration of the contract for pledge of patent right |
Denomination of invention: A hollow planetary reducer with a large speed ratio Effective date of registration: 20230728 Granted publication date: 20230602 Pledgee: Bank of Communications Co.,Ltd. Baoji Branch Pledgor: Shaanxi Jietai intelligent transmission Co.,Ltd. Registration number: Y2023980050296 |
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