CN104455228A - Variable-torque planet wheel transmission system - Google Patents
Variable-torque planet wheel transmission system Download PDFInfo
- Publication number
- CN104455228A CN104455228A CN201410712434.4A CN201410712434A CN104455228A CN 104455228 A CN104455228 A CN 104455228A CN 201410712434 A CN201410712434 A CN 201410712434A CN 104455228 A CN104455228 A CN 104455228A
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- China
- Prior art keywords
- wheel
- sun gear
- planet
- star
- variables
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
A variable-torque planet wheel transmission system comprises an input planet wheel train and an output planet wheel train which are not provided with planet carriers. A planet wheel of the input wheel train is meshed with the inner portion of a dead axle sun wheel, and in addition the planet wheel is meshed with the outer portion of a planet wheel in the output wheel train. The planet wheels are used as a main guiding executing component. Force input points which are relatively constant in space during revolution are selected, the planet wheel radius is increased, the active force arm is increased, the input torque is increased, transmission efficiency is improved, and input force is saved. The structure is novel, simple and reasonable, transmission performance is stable and reliable, and the system can be widely used in mechanical transmission of various power machines.
Description
Technical field: the present invention relates to a kind of planet gear transmission system, specifically a kind of change torque, improves the planet gear transmission system of transmission efficiency.
Background technique: at present, known planetary gear train transmission is just used as speed change, turns to, along separate routes, the composition and decomposition etc. of power, planet wheel is not as leading dirivig member, and feature advantage is failed to play and utilized; Planet wheel is supported by planet carrier, adds dirivig member, increases raw material manufacture cost and power transmission cost; Torque can not change, and can not improve transmission efficiency.
Summary of the invention: in order to change the state of the art, the invention provides one to be made up of two or more planetary gear train, planet wheel is as leading dirivig member and be directly installed on driving wheel sun gear, save planet carrier, in the input point of Input Forces set direction power, strengthen planet wheel radius, increase the initiatively arm of force, improve the bending moment planet gear transmission system of input torque.
The technological scheme that technical solution problem of the present invention adopts is: bending moment planet gear transmission system, comprise variable planet 2, line of input star wheel series that moving axis sun gear 1, dead axle sun gear 5 are formed and the quantitative output planetary train that forms of planet wheel 3, moving axis sun gear 4, the geometrical central axis that two trains are arranged on same coincidence forms transmission system.Row of variables star-wheel 2 in output wheel train do not have planet carrier to be directly installed on moving axis sun gear 1 and respectively with dead axle sun gear 5, in quantitative planet wheel 3, outer gearing, quantitative planet wheel 3 do not have planet carrier to be directly installed on moving axis sun gear 4 yet and with row of variables star-wheel 2 outer gearing of input train, moving axis sun gear 1 and moving axis sun gear 4 are respectively original wheel for inputting and terminal output wheel, row of variables star-wheel 2 increases radius, moving axis sun gear 1, quantitative planet wheel 3 is constant, quantitative planet wheel 3 does not also change, the active arm of force that dead axle sun gear 5 and moving axis sun gear 4 radius strengthen moving axis sun gear 4 simultaneously strengthens, achieve and strengthen initiatively pivoted arm, improve transmission efficiency object.
Radius row of variables star-wheel 2 claims force bearing point with the contact points 7 of quantitative planet wheel 3, and force bearing point 7 to be selected and force bearing point 7 is less than the radius of row of variables star-wheel 2 to the crow flight distance of row of variables star-wheel 2 and dead axle sun gear 5 contact points 10 at the action direction of the Input Forces of row of variables star-wheel 2.The radius size of row of variables star-wheel 2 will be determined according to system working space size, when row of variables star-wheel 2 increases, in input train rule torque M=F.L quantitatively Input Forces F and pivoted arm L and moving axis sun gear 1 center of circle to row of variables star-wheel mounting points 8 apart from constant, rule torque is constant, when row of variables star-wheel 2 radius doubles and is less than the radius of moving axis sun gear 1, moving axis sun gear 4 radius increases by 7.57%.
Beneficial effect of the present invention is: novel form, simple and reasonable, and transmission performance is reliable and stable, and test proves; When inputting, output line speed ratio equal, achieve the increase of input torque, improve transfer efficiency, save the object of Input Forces.
Accompanying drawing illustrates: below in conjunction with Figure of description, the invention will be further described.
Fig. 1 is plan view of the present invention.
Fig. 2 is the left view of Fig. 1.
Fig. 3 is that row of variables star-wheel strengthens plan view.
In Fig. 1,1. input train moving axis sun gear, 2. variable system planet wheel, 3. quantitatively planet wheel, 4. output wheel train moving axis sun gear, 5. input train dead axle sun gear (gear ring), 6. the geometrical axis overlapped, 7. the contact points of planet wheel 2 and planet wheel 3,8. planet wheel (2) mounting points, 9. planet wheel (3) mounting points.10. row of variables star-wheel 2 and dead axle sun gear (gear ring) 5 contact points.
Embodiment:
In the embodiment shown in fig. 1, row of variables star-wheel 2, moving axis sun gear 1, dead axle sun gear 5 are input train, and quantitative planet wheel 3 and moving axis sun gear 4 are output wheel train.Row of variables star-wheel 2 do not have planet carrier to be directly installed on moving axis sun gear 1 and with dead axle sun gear 5, quantitatively planet wheel 3 is inside and outside engages.Fixed wheel planet wheel 3 do not have planet carrier to be directly installed on moving axis sun gear 4 yet and with row of variables star-wheel 2 outer gearing.Moving axis sun gear 1 is taken turns for initial input and is docked with power engine, driving wheel sun gear 4 is that terminal output wheel docks with working machine, driving wheel sun gear 1 drives variable planet 2 along pin, utilizes row of variables star-wheel 2 characteristic that revolves round the sun to roll and drive quantitative planet wheel 3, drive moving axis sun gear 4 to rotate along pin.In order to ensure row of variables star-wheel 2 one aspect and dead axle sun gear 5 internal messing, on the other hand with the outer gearing of quantitative planet wheel 3, increase transverse tooth thickness, widened section and quantitative planet wheel 3 outer gearing.Two planet wheel contact pointss 7 are called force bearing point, force bearing point 7 will be selected at the force direction of the moving axis sun gear 1 of row of variables star-wheel 2, force bearing point 7, contact points .10 and row of variables star-wheel 2 center of circle angle 45 °, namely force bearing point 7 is less than the radius of row of variables star-wheel 2 to the crow flight distance of contact points 10.
In specific embodiment shown in Fig. 2, left apparent variable planet wheel 3, the quantitatively engagement of planet wheel 2 are overlapping, but cannot show in figure.
In specific embodiment shown in Fig. 3, strengthen row of variables star-wheel 2 radius, moving axis sun gear 1 is change not, namely the center of circle does not change to the distance in row of variables star-wheel 2 center of circle, in line of input star wheel series rule torque W=F.L, quantitative original Input Forces F and pivoted arm L does not change, contact points 7, contact points 10 remain 45 ° with row of variables star-wheel 2 center of circle angle, and force structure does not also change, but dead axle sun gear 5 and moving axis sun gear 4 radius but increase simultaneously.In the oblique triangle that row of variables star-wheel 2 center of circle 8, quantitatively planet wheel 3 center of circle 9 and 3, driving wheel sun gear 4 center of circle line are formed, the angle of row of variables star-wheel is 135 °, according to oblique triangle principle, on one side quantitatively, quantitative change on one side, another side also quantitative change certainly, test proves; When row of variables star-wheel 2 radius doubles and equals driving wheel sun gear 1 radius, the radius of moving axis sun gear 4 increases by 7.57%.Row of variables star-wheel 2 radius increases, and speed of autorotation is slack-off, but revolution speed does not change, and also do not change by the rotating speed rolling the moving axis sun gear 4 driven, therefore row of variables star-wheel 2 increases, and train torque also strengthens thereupon.Row of variables star-wheel 2 radius changes and will determine according to the working space of train system, such as; Micro-transmission such as robot, clock and watch is relatively little; Train, steamer, engineering machinery etc. want large relatively.
In order to stability of rotation with reduce tooth and damage, row of variables star-wheel 2, quantitatively planet wheel 3 can be severally be evenly distributed on moving axis sun gear, because drive mechanism is identical, do not mark in this Figure of description.
Claims (3)
1. bending moment planet gear transmission system, comprise variable planet (2), moving axis sun gear (1), the line of input star wheel series that dead axle sun gear (5) is formed and quantitative planet wheel (3), many planet gear transmission system of the output planetary train composition that moving axis sun gear (4) is formed, it is characterized in that: in the geometrical central axis that two trains are arranged on same coincidence row of variables star-wheel (2) do not have planet carrier be directly installed on moving axis sun gear (1) upper and respectively with dead axle sun gear (5), in quantitative planet wheel (3), outer gearing, quantitative planet wheel (3) does not have planet carrier to be directly installed on moving axis sun gear (4) and row of variables star-wheel (2) outer gearing yet, moving axis sun gear (1) and moving axis sun gear (4) are respectively original wheel for inputting and terminal output wheel, row of variables star-wheel (2) radius increases, moving axis sun gear (1), quantitatively planet wheel (3) is constant for quantitative planet wheel (3), dead axle sun gear (5) and moving axis sun gear (4) radius increase simultaneously, achieve and strengthen initiatively pivoted arm, improve input torque object.
2. bending moment planet gear transmission system according to claim 1, it is characterized in that: row of variables star-wheel (2) claims force bearing point with the contact points (7) of quantitative planet wheel (3), force bearing point (7) is selected at the action direction of Input Forces and is less than row of variables star-wheel (2) radius to row of variables star-wheel (2) and the crow flight distance of dead axle sun gear (5) contact points (10).
3. according to claim 1, bending moment planet gear transmission system described in 2, it is characterized in that: the size of described row of variables star-wheel (2) will be determined according to system working space size, when row of variables star-wheel (2) increases, in input train rule torque M=F.L quantitatively Input Forces F and pivoted arm L and moving axis sun gear (1) center of circle to row of variables star-wheel (2) mounting points (8) apart from constant, rule torque is constant, row of variables star-wheel (2) radius doubles and equals moving axis sun gear (1) radius, when row of variables star-wheel angle equals 135 °, moving axis sun gear (5) radius increases by 7.57%, active torque increases by 7.57%.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410712434.4A CN104455228A (en) | 2014-11-20 | 2014-11-20 | Variable-torque planet wheel transmission system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410712434.4A CN104455228A (en) | 2014-11-20 | 2014-11-20 | Variable-torque planet wheel transmission system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104455228A true CN104455228A (en) | 2015-03-25 |
Family
ID=52901778
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410712434.4A Pending CN104455228A (en) | 2014-11-20 | 2014-11-20 | Variable-torque planet wheel transmission system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104455228A (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR700237A (en) * | 1930-08-09 | 1931-02-26 | Motion transmission | |
| CN101778734A (en) * | 2007-08-16 | 2010-07-14 | 达思股份公司 | Reclining device of seat for vehicle |
| CN101846155A (en) * | 2010-03-01 | 2010-09-29 | 吴声震 | Megawatt-stage dwarf planet semi-direct driving wind-power speed-increasing box |
| CN202280799U (en) * | 2011-09-08 | 2012-06-20 | 江阴克威齿轮箱制造有限公司 | Multi-gear transmission case |
| CN202468862U (en) * | 2012-03-04 | 2012-10-03 | 佳木斯大学 | Two-stage planetary gear transmission device |
| CN104132102A (en) * | 2014-08-06 | 2014-11-05 | 张秘来 | Planetary gear train transmission mechanism without carrier |
| CN204344826U (en) * | 2014-11-20 | 2015-05-20 | 张秘来 | Bending moment planet gear transmission system |
-
2014
- 2014-11-20 CN CN201410712434.4A patent/CN104455228A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR700237A (en) * | 1930-08-09 | 1931-02-26 | Motion transmission | |
| CN101778734A (en) * | 2007-08-16 | 2010-07-14 | 达思股份公司 | Reclining device of seat for vehicle |
| CN101846155A (en) * | 2010-03-01 | 2010-09-29 | 吴声震 | Megawatt-stage dwarf planet semi-direct driving wind-power speed-increasing box |
| CN202280799U (en) * | 2011-09-08 | 2012-06-20 | 江阴克威齿轮箱制造有限公司 | Multi-gear transmission case |
| CN202468862U (en) * | 2012-03-04 | 2012-10-03 | 佳木斯大学 | Two-stage planetary gear transmission device |
| CN104132102A (en) * | 2014-08-06 | 2014-11-05 | 张秘来 | Planetary gear train transmission mechanism without carrier |
| CN204344826U (en) * | 2014-11-20 | 2015-05-20 | 张秘来 | Bending moment planet gear transmission system |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20150325 |