CN101761614A - Gear-ring-free planetary wheel transmission mechanism - Google Patents
Gear-ring-free planetary wheel transmission mechanism Download PDFInfo
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- CN101761614A CN101761614A CN200910208651A CN200910208651A CN101761614A CN 101761614 A CN101761614 A CN 101761614A CN 200910208651 A CN200910208651 A CN 200910208651A CN 200910208651 A CN200910208651 A CN 200910208651A CN 101761614 A CN101761614 A CN 101761614A
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- gear
- sun gear
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- planet carrier
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Abstract
The invention relates to a planetary wheel transmission mechanism, in particular to a gear-ring-free planetary wheel transmission mechanism. An input end cylindrical main planetary gear and an output end cylindrical main planetary gear are arranged on a planetary rotating shaft through a connection rotating shaft which is fixedly connected with the input end cylindrical main planetary gear and the output end cylindrical main planetary gear, external teeth of an input end cylindrical input end main planetary gear are engaged with a sun gear, an output end cylindrical output end main planetary gear is engaged with the sun gear, a braking device fixed on the box body of a gear box of the transmission mechanism is in braking fit with a planetary frame, or a one-way clutch fixed on the box body of the gear box of the transmission mechanism is matched and connected with the planetary frame, and the planetary frame is matched and connected with the sun gear positioned at the input end or is matched and connected with the sun gear positioned at the output end through a clutch. The invention has the characteristics of no inner gear ring, easy processing, easy manufacture, easy assembly and low cost, and the input and the output are realized directly through an input sun wheel and an output sun wheel.
Description
Technical field
The present invention relates to planetary type gear transmission unit, particularly a kind of gear-ring-free planetary wheel transmission mechanism.
Background technique
As everyone knows, common planetary pinion is made of elements such as sun gear, planet wheel, planet carrier and ring gears, automobile, textile manufacturing machine, mining machinery and constructional engineering machinery, wind generating unit etc. have been widely used in as retarder, speed increaser, changement or as the differential mechanism of Motor Vehicle, spatial volume for engagement bearing capacity height and internal gear (being ring gear) in making full use of, thereby dwindled its radial dimension, axial dimension, made mechanism's compactness and bearing capacity is very high.But the technology with the gear shaper cutter gear shaping in the ring gear skilled worker technology is master operation, and the most rambunctious is that the common normal line variation is overproof easily, compare with common externally-engaged cylindrical gear, the ring gear difficulty of processing is just big, required precision is higher, the manufacturing difficulty, and cost is higher.This has just limited such as planetary gear mechanisms such as the subsidiary NGW-2K-H type that gear ring arranged, NGWN-2K-H type, NN-2K-H types, because its assembly condition is comparatively harsh, so link is more time-consuming takes a lot of work in its processing, assembling.
Summary of the invention
The object of the present invention is to provide a kind of gear-ring-free planetary wheel transmission mechanism, no ring gear, manufacturing, assembling easily, cost is low, directly carries out input output by input sun gear and output sun gear.
The object of the present invention is achieved like this: a kind of gear-ring-free planetary wheel transmission mechanism, comprise gear box, the sun train that the cylindrical sun gear that is positioned at input end that shaft axis parallels and the cylindrical sun gear that is positioned at output terminal constitute, and engagement is fitted in the cylindrical planetary gear between sun gear and the sun gear, the revolution axis and the sun gear of cylindrical planetary gear, sun gear parallels, the geometry shaft axis and the sun gear of its rotation, sun gear is parallel to each other, the cylindrical planetary gear is installed on the planet carrier, planet carrier and sun gear, the coaxial installation of sun gear, this cylindrical planetary gear is at least and a pair ofly is made of cylindrical main planetary gear of input end and the cylindrical main planetary gear of output terminal, the cylindrical main planetary gear of input end is installed in the planet rotating shaft with the rotating shaft that is connected of the cylindrical main planetary gear of output terminal by its Joint, the external tooth of the cylindrical input end main planetary gear of input end is meshed with sun gear, the cylindrical output terminal main planetary gear of output terminal is meshed with sun gear, the break that is fixed on this driving mechanism gear box cooperates with the planet carrier braking, or the overrunning clutch and the planet carrier that are fixed on this driving mechanism gear box be connected, and planet carrier matches to be connected or to match with the sun gear that is positioned at output terminal by clutch and the sun gear that is positioned at input end and is connected.
Mechanical structure annexation by the invention described above, can find out that the present invention passes through the planet carrier fixation velocity ratio computational methods of Weir this (willes), with pivoted arm (being planet carrier) fixing after, under the known situation of the number of teeth of the planet number of gears and all engaging gears, the output sun gear relative motion relation at utilization and planetary pinion, two ends, listing the correlation computations formula finds the solution, the absolute value that can draw velocity ratio of the present invention can also can satisfy the claimed range of existing various velocity ratios greater than 1 smaller or equal to 1.Technological scheme of the present invention specifically is decomposed into three kinds of combined situation, and it comprises
1. the break that is fixed on the fixed base frame of this driving mechanism cooperates with the planet carrier braking, and meanwhile, planet carrier matches to be connected or to match with the sun gear that is positioned at output terminal by clutch and the sun gear that is positioned at input end and is connected;
2. the break that is fixed on the fixed base frame of this driving mechanism cooperates with the planet carrier braking, and the sun gear that planet carrier is positioned at input end or output terminal by clutch and overrunning clutch simultaneously matches and is connected;
3. the overrunning clutch and the planet carrier that are fixed on this driving mechanism fixed base frame are connected, and planet carrier matches to be connected or to match with the sun gear that is positioned at output terminal by clutch and the sun gear that is positioned at input end and is connected.
Described as can be known by said structure, the characteristics of this mechanical transmission mechanism are not have ring gear, manufacturing, assembling easily, cost is low, directly carries out input output by input sun gear and output sun gear.
Description of drawings
The invention will be further described below in conjunction with accompanying drawing.
Fig. 1 is the present invention basis embodiment's 1 structural representation;
Fig. 2 is the structural representation of the specific embodiment of the invention 1;
Fig. 3 is specific embodiment of the invention embodiment 1 a structural representation;
Fig. 4 is the structural representation of the specific embodiment of the invention 2;
Fig. 5 is the structural representation of the specific embodiment of the invention 3;
Fig. 6 is the present invention basis embodiment's 2 structural representation;
Fig. 7 is the structural representation of the specific embodiment of the invention 4;
Fig. 8 is the structural representation of the specific embodiment of the invention 5.
Embodiment
A kind of gear-ring-free planetary wheel transmission mechanism, comprise gear box, the sun train that the cylindrical sun gear that is positioned at input end that shaft axis parallels 1 and the cylindrical sun gear 8 that is positioned at output terminal constitute, and engagement is fitted in the cylindrical planetary gear between sun gear 1 and the sun gear 8, the revolution axis of cylindrical planetary gear and sun gear 1, sun gear 8 parallels, the geometry shaft axis and the sun gear 1 of its rotation, sun gear 8 is parallel to each other, the cylindrical planetary gear is installed on the planet carrier 4, planet carrier 4 and sun gear 1, sun gear 8 coaxial installations, this cylindrical planetary gear is at least a pair of cylindrical main planetary gear 3 and the cylindrical main planetary gear 6 of output terminal by input end and constitutes, the cylindrical main planetary gear 3 of input end is installed in the planet rotating shaft 7 with the rotating shaft that is connected of the cylindrical main planetary gear 6 of output terminal by its Joint, the external tooth of the main planetary gear 3 of the cylindrical input end of input end is meshed with sun gear 1, the cylindrical main planetary gear 6 of output terminal is meshed with sun gear 8, the break 5 that is fixed on this driving mechanism gear box inwall cooperates with planet carrier 4 brakings, or the overrunning clutch 11 that is fixed on this driving mechanism gear box is connected with planet carrier 4, and planet carrier 4 matches to be connected or to match with the sun gear 8 that is positioned at output terminal by clutch and the sun gear 1 that is positioned at input end and is connected.
As Fig. 1 and embodiment shown in Figure 6 is basic technical scheme (basic embodiment 1 and 2), i.e. the assembled scheme of the break 5 on the gearbox casing inwall or overrunning clutch 11 and ordinary clutch.The technical program characteristics are to engage when clutch 2, and when break 5 separated, planet carrier 4 rotated with identical speed with the sun gear 1 of input end, and the velocity ratio of whole epicyclic gear system is 1; When clutch 2 separates, when break 5 engages, planet carrier 4 maintains static, and power is exported by the rotating shaft of the sun gear 8 of output terminal by the sun gear 8 of the sun gear 1--main planetary gear 3--main planetary gear 6--output terminal of input end, and its velocity ratio can be greater than 1 or less than 1.
As shown in Figures 2 and 3, described clutch is overrunning clutch 9 or 10, planet carrier 4 is by the cooperation that is connected with the sun gear 1 that is positioned at input end of this overrunning clutch 9, perhaps, planet carrier 4 is by the cooperation that is connected with the sun gear 8 that is positioned at output terminal of this overrunning clutch 9, and the diameter of input end main planetary gear 3 is less than the diameter of output terminal main planetary gear 6.Overrunning clutch 9 or 10 is used for input sun gear 1 fixing with planet carrier 4, and break 5 can be fixing with planet carrier 4, it is break 5 and the combined scheme of overrunning clutch 9, the technical program characteristics are that clutch is an overrunning clutch 9, the effect of overrunning clutch 9 is when planet carrier 4 has the trend of rotating speed of the sun gear 1 that surmounts input end, and the sun gear 1 of input end is fixing with planet carrier 4; The effect of break 5 is that planet carrier 4 is fixing.When break 5 separates, the sun gear 1 of input end clockwise rotates input as driving wheel, the sun gear 8 of output terminal rotates as driven gear, when the rotating speed of planet carrier 5 has the trend of the sun gear 1 that surmounts input end, overrunning clutch 9 engages, planet carrier 4 rotates with identical speed with input sun gear 1, and the velocity ratio of whole epicyclic gear system is 1; When break 5 engages, when overrunning clutch 9 separates, planet carrier 4 is fixed motionless, the sun gear 1 of input end clockwise rotates input, power is by the sun gear 8 of the main planetary gear 6--output terminal of the main planetary gear 3--output terminal of the sun gear 1--input end of input end, and the velocity ratio of this scheme can be less than 1.
As shown in Figure 4, planet carrier 4 matches with the sun gear 1 of input end by clutch 2 and overrunning clutch 9 simultaneously and is connected.Overrunning clutch 9 is used for when planet carrier 4 has the trend of rotating speed of the sun gear 1 that surmounts input end, and the sun gear 1 and the planet carrier 4 of input end is fixed together.Break 5 matches with planet carrier 4, and its effect is that planet carrier 4 is fixing, promptly break 5 and common clutch, be fixed in the combined scheme of overrunning clutch 9 on this driving mechanism gear box.When break 5 separates, clutch 2 separates, the sun gear 1 of input end clockwise rotates input as driving wheel, when the sun gear 8 of output terminal rotates as driven gear, the rotating speed of planet carrier 4 has the trend of the sun gear 1 that surmounts input end, and this moment, overrunning clutch 9 engaged with planet carrier 4, and planet carrier 4 rotates with identical speed with the sun gear 1 of input end, the velocity ratio of whole epicyclic gear system is 1, and this technological scheme can be applicable to sliding of vehicle; When break 5 separation, clutch 2 combinations, the velocity ratio of whole epicyclic gear system is 1; When break 5 separates, clutch 2 combinations when if reverse input is arranged, owing to whole planetary mechanism is fixed together, then can be applicable to the braking of motor; When break 5 engages, clutch 2 separates, planet carrier 4 maintains static, the sun gear 1 of input end clockwise rotates input, the speed that is planet carrier 5 is zero, overrunning clutch 9 separation this moment, power is by the sun gear 8 of the main planetary gear 6--output terminal of the main planetary gear 3--output terminal of the sun gear 1--input end of input end.
As shown in Figure 5, on the basis of the expressed linkage structure of Fig. 6, the gear box of this driving mechanism is by break 5 braking that matches with planet pin 7, and correspondingly match with planet carrier 4 by overrunning clutch 11, planet carrier 4 is of coupled connections by clutch 2 sun gear 1 with input end again, i.e. break 5, common clutch 2 and overrunning clutch 11 combined schemes.The effect of overrunning clutch 11 is when planet carrier 4 has counter-rotational trend, planet carrier 4 is maintained static, the effect of break 5 is that planet carrier 4 maintains static, when clutch 2 engages, when break 5 separates with overrunning clutch 11, planet carrier 4 rotates with identical speed with the sun gear 1 of input end, and the velocity ratio of whole epicyclic gear system is; When the sun gear 1 of input end is imported clockwise, when clutch 2 separates (sun gear 8 of output terminal is as driven wheel), 4 of planet carriers have the trend that rotates counterclockwise, this moment, overrunning clutch 11 engaged automatically, planet carrier 4 is fixed motionless, and power is by the sun gear 8 of the sun gear 1--planetary pinion 3--planetary pinion 6--output terminal of input end.The effect of overrunning clutch 11 is when planet carrier 4 has the trend that rotates counterclockwise planet carrier 4 to be maintained static, when clutch 2 engages, when overrunning clutch 11 separates, planet carrier 4 rotates with identical speed with the sun gear 1 of input end, the velocity ratio of whole epicyclic gear system is 1, when the sun gear 1 of input end is imported clockwise, when clutch 2 separates (sun gear 8 of output terminal is a driven wheel), planet carrier 4 will have the trend that rotates counterclockwise, this moment, overrunning clutch 11 engaged automatically, planet carrier 4 maintains static, and power is by the sun gear 8 of the main planetary gear 6--output terminal of the main planetary gear 3--output terminal of the sun gear 1--input end of input end.
As shown in Figure 7, output terminal main planetary gear 6 is positioned at the sun gear 8 of output terminal by planetary pinion 12 transmissions.Break 5, clutch 2 assembled schemes and be engaged in planetary pinion 12 combined technological schemes between the sun gear 1 of planetary pinion 3 and input end, when clutch 2 engages, when break 5 separates, planet carrier 4 rotates with identical speed with the sun gear 1 of input end, the velocity ratio of whole epicyclic gear system is 1, at this moment, the sun gear 1 of input end is identical with sun gear 3 sense of rotation of output terminal; When the sun gear 1 of input end is imported clockwise, clutch 2 separates, during break 5 brakings, planet carrier 4 maintains static, and power is by the sun gear 8 of the main planetary gear 6--planetary pinion 12--output terminal of the main planetary gear 3--output terminal of the sun gear 1--input end of input end.
As shown in Figure 8, on the basis of the expressed linkage structure of Fig. 7, the main planetary gear 3 of input end is positioned at the sun gear 1 of input end by planetary pinion 13 transmissions, and the main planetary gear 6 of output terminal is positioned at the sun gear 8 of output terminal by planetary pinion 12 transmissions.Break 5, common clutch 2 assembled schemes and be engaged in planetary pinion 13 combined technological schemes between the sun gear 8 of main planetary gear 3 and output terminal, when clutch 2 engages, when break 5 separates, planet carrier 4 rotates with identical speed with the sun gear 1 of input end, and the velocity ratio of whole epicyclic gear system is 1; When clutch 2 separation, when break 5 engaged, planet carrier 4 maintained static, and power is by the sun gear 8 of the main planetary gear 6--planetary pinion 12--output terminal of the main planetary gear 3--output terminal of the sun gear 1--planetary pinion 13--input end of input end.
Claims (6)
1. gear-ring-free planetary wheel transmission mechanism, comprise gear box, the sun train that the cylindrical sun gear (1) that is positioned at input end that shaft axis parallels and the cylindrical sun gear (8) that is positioned at output terminal constitute, and engagement is fitted in the cylindrical planetary gear between sun gear (1) and the sun gear (8), the revolution axis of cylindrical planetary gear and sun gear (1), sun gear (8) parallels, the geometry shaft axis and the sun gear (1) of its rotation, sun gear (8) is parallel to each other, the cylindrical planetary gear is installed on the planet carrier (4), planet carrier (4) and sun gear (1), the coaxial installation of sun gear (8), it is characterized in that: this cylindrical planetary gear is at least a pair of by cylindrical main planetary gear of input end (3) and the cylindrical main planetary gear of output terminal (6) formation, the cylindrical main planetary gear of input end (3) is installed in the planet rotating shaft (7) with the rotating shaft that is connected of the cylindrical main planetary gear of output terminal (6) by its Joint, the external tooth of the cylindrical input end main planetary gear of input end (3) is meshed with sun gear (1), the cylindrical output terminal main planetary gear of output terminal (6) is meshed with sun gear (8), the break (5) that is fixed on this driving mechanism gear box cooperates with planet carrier (4) braking, or the overrunning clutch (11) and the planet carrier (4) that are fixed on this driving mechanism gear box be connected, and planet carrier (4) matches to be connected or to match with the sun gear that is positioned at output terminal (8) by clutch and the sun gear that is positioned at input end (1) and is connected.
2. gear-ring-free planetary wheel transmission mechanism according to claim 1, it is characterized in that: described clutch is overrunning clutch (9) or (10), planet carrier (4) is by this overrunning clutch (9) cooperation that is connected with the sun gear that is positioned at input end (1), perhaps, planet carrier (4) is by this overrunning clutch (10) cooperation that is connected with the sun gear that is positioned at output terminal (8), and the diameter of input end main planetary gear (3) is less than the diameter of output terminal main planetary gear (6).
3. gear-ring-free planetary wheel transmission mechanism according to claim 1 is characterized in that: planet carrier (4) matches with the sun gear (1) of input end by clutch (2) and overrunning clutch (9) simultaneously and is connected.
4. gear-ring-free planetary wheel transmission mechanism according to claim 1 is characterized in that: the gearbox casing inwall is by break (5) braking that matches with planet carrier (4), and corresponding matching with planet carrier (4) by overrunning clutch (11) is connected.
5. gear-ring-free planetary wheel transmission mechanism according to claim 1 is characterized in that: the main planetary gear of output terminal (6) is positioned at the sun gear (8) of output terminal by planetary pinion (12) transmission.
6. gear-ring-free planetary wheel transmission mechanism according to claim 5 is characterized in that: the main planetary gear of input end (3) is positioned at the sun gear (1) of input end by planetary pinion (13) transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910208651A CN101761614A (en) | 2009-10-23 | 2009-10-23 | Gear-ring-free planetary wheel transmission mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910208651A CN101761614A (en) | 2009-10-23 | 2009-10-23 | Gear-ring-free planetary wheel transmission mechanism |
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| Publication Number | Publication Date |
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| CN101761614A true CN101761614A (en) | 2010-06-30 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN200910208651A Pending CN101761614A (en) | 2009-10-23 | 2009-10-23 | Gear-ring-free planetary wheel transmission mechanism |
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| CN (1) | CN101761614A (en) |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102155521A (en) * | 2010-02-11 | 2011-08-17 | 宁波宏协离合器有限公司 | Planetary gear mechanism and mechanical speed changer comprising same |
| WO2011097780A1 (en) * | 2010-02-11 | 2011-08-18 | 宁波宏协离合器有限公司 | Planegary gear mechanism and mechanical transmission including the same |
| WO2012009951A1 (en) * | 2010-07-21 | 2012-01-26 | Chai Jie | Speed increasing and changing device for planetary gear |
| CN103883685A (en) * | 2012-12-20 | 2014-06-25 | 北汽福田汽车股份有限公司 | Mechanical transmission |
| CN106195153A (en) * | 2016-08-26 | 2016-12-07 | 孟玲 | Planetary gears and the mechanical transmission including this planetary gears |
| CN106224453A (en) * | 2016-08-31 | 2016-12-14 | 金顺日 | A kind of big retarding is than external toothing quill shaft planetary reduction gear |
| CN106641130A (en) * | 2017-02-19 | 2017-05-10 | 郭克亚 | Planetary two-gear driving device and two-gear driving method thereof |
| CN107795646A (en) * | 2016-09-06 | 2018-03-13 | 三星电子株式会社 | Power transmission and the exercise aid device including power transmission |
| CN108223722A (en) * | 2018-01-10 | 2018-06-29 | 山东大学 | A kind of no gear ring planetary gear speed change system and method for changing speed |
| CN108458001A (en) * | 2018-02-06 | 2018-08-28 | 舟富成科技（深圳）有限公司 | A kind of planet gear clutch |
| CN109098942A (en) * | 2018-05-04 | 2018-12-28 | 李建新 | Electric car vibrates energy overhead type collection device |
| CN109228860A (en) * | 2018-05-08 | 2019-01-18 | 李建新 | The electric car vibration energy drags formula collection device |
| CN110375042A (en) * | 2019-07-31 | 2019-10-25 | 合肥工业大学 | A kind of 16 gear transmissions based on no gear ring planet row type modularized design |
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2009
- 2009-10-23 CN CN200910208651A patent/CN101761614A/en active Pending
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102155521A (en) * | 2010-02-11 | 2011-08-17 | 宁波宏协离合器有限公司 | Planetary gear mechanism and mechanical speed changer comprising same |
| WO2011097780A1 (en) * | 2010-02-11 | 2011-08-18 | 宁波宏协离合器有限公司 | Planegary gear mechanism and mechanical transmission including the same |
| CN102155521B (en) * | 2010-02-11 | 2013-07-10 | 宁波威能传动技术股份有限公司 | Planetary gear mechanism and mechanical speed changer comprising same |
| WO2012009951A1 (en) * | 2010-07-21 | 2012-01-26 | Chai Jie | Speed increasing and changing device for planetary gear |
| CN103883685A (en) * | 2012-12-20 | 2014-06-25 | 北汽福田汽车股份有限公司 | Mechanical transmission |
| CN106195153A (en) * | 2016-08-26 | 2016-12-07 | 孟玲 | Planetary gears and the mechanical transmission including this planetary gears |
| CN106224453A (en) * | 2016-08-31 | 2016-12-14 | 金顺日 | A kind of big retarding is than external toothing quill shaft planetary reduction gear |
| CN107795646A (en) * | 2016-09-06 | 2018-03-13 | 三星电子株式会社 | Power transmission and the exercise aid device including power transmission |
| CN107795646B (en) * | 2016-09-06 | 2022-04-29 | 三星电子株式会社 | Power transmission device and exercise assisting apparatus including power transmission device |
| CN106641130A (en) * | 2017-02-19 | 2017-05-10 | 郭克亚 | Planetary two-gear driving device and two-gear driving method thereof |
| CN106641130B (en) * | 2017-02-19 | 2024-03-15 | 广东新防科技有限责任公司 | Planetary two-gear driving device and two-gear driving method thereof |
| CN108223722A (en) * | 2018-01-10 | 2018-06-29 | 山东大学 | A kind of no gear ring planetary gear speed change system and method for changing speed |
| CN108223722B (en) * | 2018-01-10 | 2020-09-04 | 山东大学 | Non-gear ring planet wheel speed change system and speed change method |
| CN108458001A (en) * | 2018-02-06 | 2018-08-28 | 舟富成科技（深圳）有限公司 | A kind of planet gear clutch |
| CN109098942A (en) * | 2018-05-04 | 2018-12-28 | 李建新 | Electric car vibrates energy overhead type collection device |
| CN109228860A (en) * | 2018-05-08 | 2019-01-18 | 李建新 | The electric car vibration energy drags formula collection device |
| CN110375042A (en) * | 2019-07-31 | 2019-10-25 | 合肥工业大学 | A kind of 16 gear transmissions based on no gear ring planet row type modularized design |
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Open date: 20100630 |