CN202118198U - Combined type planet speed changing mechanism - Google Patents
Combined type planet speed changing mechanism Download PDFInfo
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- CN202118198U CN202118198U CN2011202673239U CN201120267323U CN202118198U CN 202118198 U CN202118198 U CN 202118198U CN 2011202673239 U CN2011202673239 U CN 2011202673239U CN 201120267323 U CN201120267323 U CN 201120267323U CN 202118198 U CN202118198 U CN 202118198U
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- gear
- small teeth
- gear pair
- teeth difference
- tooth
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Abstract
A combined type planet speed changing mechanism can stably achieve step speed change in rotation under the situation that power is not cut off, simultaneously finish separation and reunion of speed reduction and power with a large or small speed ratio and is large in change range of the speed ratio, simple in structure, easy to manufacture and low in cost. The combined type planet speed changing mechanism comprises several gear pair with less tooth difference with different tooth number ratios, an eccentric shaft, several balancing pieces, a 2K-H minus planet transmission mechanism, several brakes and the like.
Description
Technical field
The utility model relates to a kind of combined type planet speed change mechanism, is a kind ofly can not interrupt power, and step change reposefully in fully loaded or no-load running, and can accomplish the gear of clutch of deceleration and the power of bigger or less speed ratio simultaneously.
Background technique
Existing planet speed change mechanism all is to adopt several 2K-H negative sign planetary mechanisms to combine, and each planetary mechanism all is made up of sun gear, several planet wheel, internal gear and planet carrier, complex structure, and number of gears is many.
Its shortcoming is:
1. complete machine structure is complicated, and manufacture difficulty is high, and cost is high.
2. in step change, can not realize that large speed ratio slows down, can only realize less reduction speed ratio.And the excursion of speed ratio is less.
The series-connection type small tooth number difference speed-change mechanism that proposes in the patent 2009200729092 mainly is applicable to the use occasion than large speed ratio, and is to the occasion of less speed ratio, not too suitable.
The model utility content
The purpose of the utility model is to design a kind ofly can not interrupt the on-stream step change reposefully of power; Can accomplish the deceleration of bigger or less speed ratio and the clutch of power simultaneously again, the excursion of speed ratio is big, and simple in structure; Be easy to make the combined type planet speed change mechanism that cost is low.
The task of the utility model realizes through following technological scheme:
By the different gear pair with small teeth difference of several gear ratios, an eccentric shaft, several balancing patches, a 2K-H negative sign epicyclic transmission mechanism and several break are formed a combined type planet speed change mechanism.
Each gear pair with small teeth difference all is that coaxial line is arranged on the eccentric shaft, and each gear pair with small teeth difference is formed by an internal gear and with a planetary pinion of its engagement, and the gear ratio of each gear pair is different.
Eccentric shaft is that each gear pair with small teeth difference is shared, and each planetary pinion all is contained on the eccentric shaft through bearing housing, and eccentric shaft rotates relatively, and several balancing patches are housed on the eccentric shaft, connects firmly with eccentric shaft.
2K-H negative sign epicyclic transmission mechanism is positioned at a termination of gear pair with small teeth difference group, and the shaft axis of its sun gear is coaxial with the main axis of eccentric shaft, and rotating speed is identical.
On the planetary side in each gear pair with small teeth difference, all be processed with the tooth inserted tooth, after the assembling, the tooth inserted tooth all engages, and can guarantee that each planetary pinion is all with identical rotational speed.
Simultaneously, on the side of the internal gear in the 2K-H negative sign planetary mechanism, also be processed with the tooth inserted tooth; Equally also be processed with the tooth inserted tooth on the side of the internal gear of a gear pair with small teeth difference that is adjacent; After the assembling, this both sides tooth inserted tooth engages, and can guarantee that these two internal gears are with identical rotational speed.
The internal gear of the internal gear of gear pair with small teeth difference and 2K-H negative sign planetary mechanism all is bearing on the frame through bearing separately, and frame is rotated relatively.
Break all is equipped with on the planet carrier of the internal gear of each gear pair with small teeth difference and 2K-H negative sign planetary mechanism,, the rotation of the planet carrier of each few tooth difference internal gear of may command and 2K-H negative sign planetary mechanism or fixing.
Each internal gear can be selected when design according to the needs in the work as output.
Power from selected internal gear output, is drawn power from the sun gear or the eccentric shaft input of 2K-H negative sign mechanism during work.
Situation one, the internal gear of selected this gear pair with small teeth difference adjacent with 2K-H negative sign planetary mechanism are as output:
At this moment, do not change if the planet carrier in the braking 2K-H mechanism makes it fixing, other each breaks all unclamp, and then gear is just pressed the output of 2K-H Speed Ratio.
At this moment; If some internal gears in other gear pair with small teeth difference of braking; And the break outside this break all unclamps; Then gear is just exported by gear pair with small teeth difference that is braked and the synthetic speed ratio as this gear pair with small teeth difference of exporting, and other each gear pair with small teeth difference and 2K-H mechanism all dally, and is irrelevant with output.
Situation two, the internal gear of the gear pair with small teeth difference outside the selected situation one are as output:
At this moment, if the planet carrier in the braking 2K-H mechanism, other each breaks all unclamp, and then gear just press 2K-H mechanism, that gear pair with small teeth difference adjacent with 2K-H and as the gear pair with small teeth difference of exporting, this three's synthetic speed ratio is exported.
At this moment; If brake the internal gear of another gear pair with small teeth difference, and other break unclamps all, then gear is just exported by this gear pair with small teeth difference and the synthetic speed ratio as the gear pair with small teeth difference of exporting; Other each gear pair with small teeth difference and 2K-H mechanism all dally, and be irrelevant with output.
Select different breaks to brake, can obtain different output speed ratios.
When needing velocity transformation, the break that this rotating speed that control is being turned round is relevant unclamps gradually; Simultaneously, control a back break that the rotating speed of wanting to get into is relevant, braking is stopped tight gradually; Both cooperate suitably, can steadily transform to a back rotating speed from this rotating speed that is turning round; Power does not interrupt during speed change, has realized power gear shifting.
The characteristics of few tooth difference transmission are that speed ratio is big, are to be prone to be difficult for greatly little, and the ratio change scope is also bigger, and the speed ratio minimum is about 10, and is as needing the transmission of littler speed ratio in the work, just not competent.Simultaneously, it is simple in structure, is easy to make.
The characteristics of 2K-H negative sign planetary mechanism transmission are that speed ratio is less comparatively speaking, and excursion is also less, generally about 3～8, as not competent.In addition, structure is complicated slightly.
The characteristics of combined type planet speed change mechanism are the advantages that has absorbed these two kinds of mechanisms simultaneously, become complementation, have avoided shortcoming.
The utility model has the advantages that:
1. simple in structure, volume is little, be easy to make, cost is low.
2. in realizing the unbroken running of power, in steady speed change and the power clutch, can realize from less speed ratio to gearing down than large speed ratio.Enlarge the excursion of speed ratio, also enlarged the using scope of speed changer.
Description of drawings
Accompanying drawing 1 is the structure diagram of one 4 fast type combined type planet speed change mechanism.
Accompanying drawing 2 is structure diagrams of one 3 fast type combined type planet speed change mechanism.
Accompanying drawing 3 is structure diagrams of one 2 fast type combined type planet speed change mechanism.
The main member implication of each numbering is following in the accompanying drawing:
1. sun gear 2. planetary pinions 3 breaks 4. Brake drums
5. internal gear 6. planet carriers 7. tooth inserted tooths 8. tooth inserted tooths
9. tooth inserted tooth 10. tooth inserted tooths 11. eccentric shafts 12. balancing patches
13. break 14. internal gears 15. planetary pinions 16. breaks
17. internal gear 18. planetary pinions 19. breaks 20. internal gears
21. planetary pinion 22. breaks 23. internal gears 24. planetary pinions
25. balancing patch 26. flat keys
Embodiment
Below in conjunction with embodiment's accompanying drawing the utility model is described further.
Implement row 1:
Shown in Figure 1 is the structure diagram of one 4 fast type combined type planet speed change mechanism, form by 4 different gear pair with small teeth difference and 2K-H negative sign planetary mechanisms of gear ratio, and from the sun gear input on right side, few tooth difference internal gear 20 outputs that mediate.The outer garden of internal gear 20 is processed with external tooth on week, with the gear engagement in the external world, outputting power.
Eccentric shaft is that these 4 gear pair with small teeth difference are shared, and each planetary pinion all is contained on the eccentric shaft through bearing housing, and eccentric shaft rotates relatively, and balancing patch 12 is equipped with in the left side of eccentric shaft, and 25, two balancing patches of balance are equipped with on the right side and eccentric shaft connects firmly.
2K-H negative sign planetary mechanism is positioned at the right side of these 4 gear pair with small teeth difference.By sun gear 1, planetary pinion 2, internal gear 5, and planet carrier 6 form, Brake drum 4 connects firmly on planet carrier through flat key 26.The shaft axis of sun gear is coaxial with the main axis of eccentric shaft, and rotating speed is identical.
On the side of each small teeth number difference planet gear, all be processed with the tooth inserted tooth, after small teeth number difference planet gear assembled vertically, the tooth inserted tooth all engaged, and the tooth inserted tooth 8,9 after engaging among Fig. 1, shown in 10, can guarantee that these these planetary pinions are all with identical rotational speed.
Simultaneously; On the side of the internal gear 5 of 2K-H planetary mechanism, also be processed with the tooth inserted tooth, equally also be processed with the tooth inserted tooth on the side of the internal gear 23 of the gear pair with small teeth difference that is adjacent; After the assembling; This bi-side tooth inserted tooth engages, and shown in the tooth inserted tooth 7 after engaging among Fig. 1, can protect these two internal gears with identical rotational speed.
The internal gear of the internal gear of each gear pair with small teeth difference and 2K-H negative sign planetary mechanism all is bearing on the frame through bearing separately, and frame is rotated relatively.
On the internal gear of each gear pair with small teeth difference, all be equipped with break, be equipped with break 22 on the internal gear 23; The rotation of may command internal gear 23 or fixing likewise, is equipped with break 19 on the internal gear 20; Be equipped with break 16 on the internal gear 17, be equipped with break 13 on the internal gear 14.
Power is imported from sun gear during work.
At this moment, if braking Brake drum 4, simultaneously, other each breaks all unclamp, and then gear is just exported with 2K-H mechanism, gear pair 24,23 and gear pair 21,20 these threes' synthetic speed ratio.Gear pair 18,17 and 15,14 idle running.
This moment, if other each breaks all unclamped the few tooth difference internal gear 23 of braking, and then gear is just by gear pair 24,23 and 21,20 the two close or speed ratio output, gear pair 18,17 and 15,14 and 2K-H negative sign planetary mechanism dally.
Likewise, if braking internal gear 17, then press gear pair 18,17 and 21,20 the two synthetic speed ratios are exported other idle running.If braking internal gear 14 is then pressed the synthetic speed ratio of gear pair 15,14 and 21,20 and is exported other idle running.
Like this, can obtain 4 kinds of different speed ratios outputs.
If output inner gear 20 brakings, other breaks all unclamp, the then unpowered output of speed changer.
The process (other breaks all unclamp) of some break brakings in the break 3,13,16,22 is exactly the process of the power connection of the corresponding speed ratio of this break, and the process of unclamping is exactly that power separates the process of disconnection.
When needing velocity transformation; Unclamp the corresponding break of this rotating speed that is turning round gradually, braking is stopped tight back one and is wanted the corresponding break of rotating speed that gets into gradually simultaneously, cooperates suitably; Can steadily transform to a back output speed from this output speed that is turning round, not interrupt power.
Embodiment 2:
Fig. 2 is the structure diagram of one 3 fast type combined type planet speed change mechanism, is made up of 3 different gear pair with small teeth difference and 2K-H negative sign planetary mechanisms of gear ratio, from the sun gear input on right side, is in the spindle nose output of few tooth difference internal gear 14 of leftward position.
This embodiment's constituted mode and working principle are identical with embodiment 1, and difference is that gear pair with small teeth difference has lacked one, and therefore, output speed has also been lacked one grade, totally 3 grades, in addition, have selected to be in the spindle nose output of the internal gear 14 of leftward position.
Embodiment 3:
Fig. 3 is the structure diagram of one 2 fast type combined type planet speed change mechanism; Be made up of 2 different gear pair with small teeth difference and 2K-H negative sign planetary mechanisms of gear ratio, different with embodiment 2 is that gear pair with small teeth difference has lacked one, therefore; Output speed has also lacked one grade, totally 2 grades.
Claims (1)
1. combined type planet speed change mechanism; Can step change reposefully in fully loaded or no-load running; And can accomplish the deceleration of bigger or less speed ratio and the clutch of power simultaneously; Form by the different gear pair with small teeth difference of several gear ratios, an eccentric shaft, several balancing patch, a 2K-H negative sign epicyclic transmission mechanism and several break
It is characterized in that:
(1). have a plurality of gear pair with small teeth difference that coaxial line is arranged, each gear pair with small teeth difference is formed by an internal gear and with a planetary pinion of its engagement, and the gear ratio of each gear pair is different;
(2). have an eccentric shaft, shared for each gear pair with small teeth difference, the planetary pinion of each gear pair with small teeth difference all is contained on the eccentric shaft through bearing housing, and eccentric shaft rotates relatively, and several balancing patches are housed on the eccentric shaft, connects firmly with eccentric shaft;
(3). have a 2K-H negative sign epicyclic transmission mechanism, be positioned at a termination of gear pair with small teeth difference group, the shaft axis of its sun gear is coaxial with the main axis of eccentric shaft, and rotating speed is identical;
(4). on the planetary side in each gear pair with small teeth difference, all be processed with the tooth inserted tooth, after the assembling; The tooth inserted tooth all engages; Can guarantee that planetary pinion in each gear pair with small teeth difference all with identical rotational speed, simultaneously, also is processed with the tooth inserted tooth on the side of the internal gear in the 2K-H negative sign planetary mechanism; Equally also be processed with the tooth inserted tooth on the side of the internal gear of a gear pair with small teeth difference that is adjacent; After the assembling, this both sides tooth inserted tooth engages, and can guarantee that internal gear in internal gear and the adjacent gear pair with small teeth difference in the 2K-H negative sign planetary mechanism is with identical rotational speed;
(5). the internal gear of the internal gear of gear pair with small teeth difference and 2K-H negative sign planetary mechanism all is bearing on the frame through bearing separately; Frame is rotated relatively; On the planet carrier in internal gear in each gear pair with small teeth difference and the 2K-H negative sign planetary mechanism; Break all is equipped with, the rotation of the planet carrier in each few tooth difference internal gear of may command and the 2K-H negative sign planetary mechanism or fixing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202673239U CN202118198U (en) | 2011-07-25 | 2011-07-25 | Combined type planet speed changing mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202673239U CN202118198U (en) | 2011-07-25 | 2011-07-25 | Combined type planet speed changing mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202118198U true CN202118198U (en) | 2012-01-18 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011202673239U Expired - Fee Related CN202118198U (en) | 2011-07-25 | 2011-07-25 | Combined type planet speed changing mechanism |
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| CN (1) | CN202118198U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102401094A (en) * | 2011-07-06 | 2012-04-04 | 徐至辉 | Combined planetary gear mechanism |
| CN104235281A (en) * | 2013-06-14 | 2014-12-24 | 现代自动车株式会社 | Automated manual transmission for vehicle |
-
2011
- 2011-07-25 CN CN2011202673239U patent/CN202118198U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102401094A (en) * | 2011-07-06 | 2012-04-04 | 徐至辉 | Combined planetary gear mechanism |
| CN104235281A (en) * | 2013-06-14 | 2014-12-24 | 现代自动车株式会社 | Automated manual transmission for vehicle |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20120118 Termination date: 20140725 |
|
| EXPY | Termination of patent right or utility model |