CN1880801A - Gear stepping type stepless speed change device - Google Patents
Gear stepping type stepless speed change device Download PDFInfo
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- CN1880801A CN1880801A CN 200610101264 CN200610101264A CN1880801A CN 1880801 A CN1880801 A CN 1880801A CN 200610101264 CN200610101264 CN 200610101264 CN 200610101264 A CN200610101264 A CN 200610101264A CN 1880801 A CN1880801 A CN 1880801A
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Abstract
The invention relates to a gear stepless speed changer, which comprises: planet gear system and one-way bearing as one-way clutch, wherein the gear system comprises an active sun wheel connected to the power input; there are 3-6 output planet wheels meshed with the circumference of active sun wheel; the output planet wheel is mounted on the planet wheel support fixed with the power output; each output planet wheel is meshed with one tooth ring; one-way bearing is arranged on the tooth ring; the output planet wheel and the planet wheel support are the output; the revolution speed of planet wheel support is the output rotation speed; the active sun wheel is the input; the tooth ring is the input used when changing speed; the power of driving tooth ring can be obtained from the input axle; the rotation direction of tooth ring is same as active sun wheel; the one-way bearing sheathes the tooth ring or the element connected to the tooth ring, to rotate the tooth ring at single direction. The invention has simple structure, stepless speed change, and wider speed range.
Description
Technical field
The present invention relates to a kind of speed change gear, specifically a kind of simple in structure, gear stepping type stepless speed change device that slewing range is big.
Background technique
Along with the further in-depth of process of industrialization, the wide model of speed changer be applied in various occasions and field, modal is to be used for machinery such as various vehicles.The speed changer branch has level and stepless two kinds of speed change forms, and major part is to use step change transmission in current automotive field.The efficient height that does not have stepless speed variator again because of the efficient of step change transmission is so people are researching and developing reliability and durability stepless speed variator and substituting existing step change transmission in auto manufacturing always.Be applied in the stepless speed variator on the automobile now, the known steel-belt type stepless speed variator that has only is being used slightly, it shows superior performance is that step change transmission is unrivaled, but also there are some problems, big as easily skidding, wearing and tearing, the life-span short, be difficult to use on the automobile of big discharge capacity etc.So people reach the research and development of power ground, strive developing a kind of stepless speed variator that can remedy above deficiency always.
Summary of the invention
The purpose of this invention is to provide a kind of simple in structure, gear stepping type stepless speed change device that slewing range is big.
Requirement in order to achieve the above object, the present invention adopt following scheme to realize:
A kind of gear stepping type stepless speed change device, comprise that mainly epicyclic train and unilateral bearing are overrunning clutch, this train of gearings comprises that one connects the driving sun gear of power intake, be engaged with 3 to 6 output planetary wheels along the driving sun gear periphery, the output planetary wheel is installed on the planetary wheel carrier, planetary wheel carrier is fixedlyed connected with clutch end, and each output planetary wheel is engaged in the gear ring jointly, and unilateral bearing is that overrunning clutch is arranged on the gear ring.
As a kind of improvement to such scheme, the fixedly connected input shaft in driving sun gear the place ahead, the fixedly connected output shaft of planetary wheel carrier, on input shaft, also be provided with the speed governing sun gear, the outer gearing of speed governing sun gear has 3 to 6 speed governing planet wheels, the speed governing planet wheel is installed on the planetary wheel carrier, planetary wheel carrier is fixedlyed connected with input shaft, each speed governing planet wheel is engaged in the gear ring engagement jointly, and unilateral bearing is that overrunning clutch, gear ring, speed governing sun gear, driving sun gear, planetary wheel carrier and output shaft, input shaft are that same axle center is provided with.
Simultaneously, such scheme also can be done following improvement, the fixedly connected input shaft in driving sun gear the place ahead, the fixedly connected output shaft of planetary wheel carrier, on input shaft, also be provided with the speed governing sun gear, the outer gearing of speed governing sun gear has 3 to 6 speed governing planet wheels, each speed governing planet wheel is installed on the planetary wheel carrier, the revolution diameter of speed governing planet wheel is greater than the revolution diameter of planet wheel, each output planetary wheel and gear ring engagement, on output shaft, be fixed with an output sun gear, the outer gearing of output sun gear has 3 to 6 planet wheels, the planetary wheel carrier of planet wheel is fixed in the gear ring, is engaged in the gear ring two gear rings in speed governing planet wheel and planet wheel are common, unilateral bearing is an overrunning clutch, the speed governing sun gear, driving sun gear, the output sun gear, planetary wheel carrier and output shaft, input shaft is that same axle center is provided with
Principle of the invention novelty, simple and direct practicality, simple in structure, easily manufacturing, low, the easy control of cost can effectively realize stepless change, and slewing range is big, and the intensity height can high-power transmission
Description of drawings
Accompanying drawing 1 is the basic stepping theory structure of the present invention schematic representation; Accompanying drawing 2 is wherein a kind of basic structure schematic representation of the present invention; Accompanying drawing 3 is the another kind of basic structure schematic representation of the present invention; Accompanying drawing 4 is the specific embodiment of the invention one structural representation; Accompanying drawing 5 is the specific embodiment of the invention two structural representations.
Embodiment
For the ease of understanding, structural principle of the present invention is further described in detail below in conjunction with specific embodiment and accompanying drawing:
At first stepping principle and basic structure are narrated: as accompanying drawing 1, accompanying drawing 2 shown in the accompanying drawing 3, is the present invention's one better simply structural type, comprises that mainly planetary gear train and unilateral bearing are the basic device structure that overrunning clutch is formed.Train of gearings comprises that one connects the driving sun gear 31 of power intake, be engaged with 3 to 6 output planetary wheels 41 along driving sun gear 31 peripheries, output planetary wheel 41 is installed on the planetary wheel carrier 51, planetary wheel carrier 51 is connected with clutch end, be engaged in the gear ring 101 in each output planetary wheel 41 is common, also being provided with the unilateral bearing of realizing gear ring 101 one-way rotation on gear ring 101 is overrunning clutch 111.
The present invention is a kind of gear stepping type it's too late speed change gear, its output planetary wheel 41 and planetary wheel carrier 51 are output terminal, the revolution speed of planetary wheel carrier 51 is an output speed, driving sun gear 31 is an input end, the input end that gear ring 101 is used during as speed change, the power that drives gear ring 101 can be obtained from input shaft or output shaft, and the direction of gear ring 101 rotations is with moving sun gear 31 same directions.Unilateral bearing be overrunning clutch 111 be sleeved on the gear ring 101 or with the affixed member of gear ring 101 on, make gear ring 101 can only folk prescription to rotation.Suppose the revolution ratio of the rotating speed of driving sun gear 31 and output planetary wheel 41 was set in 3.5: 1, the speed ratio of the rotating speed of gear ring 101 and 41 revolution of output planetary wheel is 1: 0.7.If on certain value, as 1000 rev/mins, gear ring 101 does not add running the invariablenes turning speed of driving sun gear 31, this moment, the rotating speeds of output planetary wheel 41 revolution were 286 rev/mins, the rotating speed of output terminal for the slowest, torsion is maximum.In the time will improving the rotating speed of output terminal, only need make gear ring 101 have certain rotating speed, the rotating speed of gear ring 101 will be added to rotating speed on the output terminal by speed ratio by planet wheel 41, rotating speed such as gear ring 101 is 200 rev/mins, then the revolution of output planetary wheel 41 has just increased by the rotating speed of 200 rev/mins * 0.7=140 rev/min, add 286 rev/mins of the rotating speeds of original output planetary wheel 41 revolution, the rotating speed of output planetary wheel 41 revolution is just brought up to 286 rev/mins+140 rev/mins=426 rev/mins, and the rotating speed of whole output has just improved.If gear ring 101 adds 1400 rev/mins, the revolution of output planetary 41 just reaches 1266 rev/mins, and the rotating speed of output terminal has just reached at a high speed.
In low speed (except minimum and the most at a high speed) in whole stepping speed-change process at a high speed, the running of gear ring 101 be constantly in rotation, pause replace between the two, conversion.Concrete condition is: raise speed or be stabilized under the situation of a certain speed, again because will overcome the resistance of output terminal, when the torsion of gear ring 101 can't overcome this resistance again, at this moment unilateral bearing is that overrunning clutch 111 can automatic blockings be lived gear ring 101 and made its can not reverse (resistance bounce-back), driving sun gear 31 has just had one and drive the rotation of output planetary wheel 41 and the revolution of drive 51 for the of short duration and firm force of borrowing like this, to reducing of output planetary frame 51 resistances, the rotation of gear ring 101 is then gone forward one by one, when having arrived gear ring 101 and can not overcome the resistance of output terminal, unilateral bearing is that overrunning clutch 111 again can automatic blocking be lived gear ring 101 and made its can not reverse (resistance bounce-back), the resistance that overcomes output terminal is finished by driving sun gear and output planetary wheel 41 again, resistance to output terminal reduces, gear ring 101 goes forward one by one once more, in the process of going forward one by one, the span of going forward one by one when resistance is big is just little, and the span that resistance hour goes forward one by one is just big, has produced linking up of whole from low speed to high speed speed-change process rotating ratio.Progressive step by step like this step-operated, in the running of stepping, gear ring 101 can obtain the support of main sun gear 31 torsion in different rotating speeds, and same main sun gear 31 can obtain the support of gear ring 101 rotating speeds again, and the molten mutually and complementation of two rotating speeds has promptly produced infinite variable speed effect.
Embodiment one: as shown in Figure 4, this device mainly comprises supporting frame 11, in the supporting frame 11 epicyclic train is installed, train of gearings comprises: driving sun gear 31, driving sun gear 31 fixedly connected input shafts 21, be engaged with 3 to 6 output planetary wheels 41 along driving sun gear 31 peripheries, output planetary wheel 41 is installed on the planetary wheel carrier 51, planetary wheel carrier 51 connects output shaft 61, on the input shaft 21 in driving sun gear 31 the place aheads, also be provided with a speed governing sun gear 71,71 outer gearings of speed governing sun gear have 3 to 6 speed governing planet wheels 91, speed governing planet wheel 91 is installed on the planetary wheel carrier 81, planetary wheel carrier 81 is fixed on the input shaft 21, speed governing planet wheel 91, output planetary wheel 41 and gear ring 101 engagements, it is that overrunning clutch 111 is installed on the gear ring 101 that unilateral bearing is arranged, unilateral bearing is that overrunning clutch 111 is fixed in the supporting frame, speed governing sun gear 71, driving sun gear 31, planetary wheel carrier 81,51 and output shaft 61, input shaft 21, gear ring 101, unilateral bearing is that overrunning clutch 111 is provided with for same axle center.
Its working procedure and principle are as follows: input shaft 21, planet carrier 81, driving sun gear 31 be rotation in the direction of the clock together, each output planetary wheel 41 of driving sun gear 31 drives counterclockwise rotation while output planetary is separately taken turns the inner ring clockwise direction revolution of 41 integral body along gear ring 101, the integral body revolution of output planetary wheel 41 drives planetary wheel carrier 51 and output shaft 61 rotates, this moment, the counter-rotating of gear ring 101 was overrunning clutch 111 lockings by unidirectional bearing, and output shaft 61 is with regard to dynamic output.If gear ring 101 does not add the rotation of up time direction, then be not used in the power (being that gear ring 101 does not rotate) of speed-raising, we can set, and the rotating speed of output shaft 61 this moment is the slowest, torsion is maximum, promptly exports as one grade rotating speed.The rotation of input shaft 21 drives planetary wheel carrier 81 equidirectional revolving simultaneously, counterclockwise rotation and speed governing planet wheel 91 integral body are along the clockwise revolution of the inner ring of gear ring 101 separately to drive speed governing planet wheel 91 again, and speed governing planet wheel 91 drives speed governing sun gear 71 again and does the rotation of high speed clockwise direction.When output shaft 61 need overcome big resistance, the counter-rotating of gear ring 101 is overrunning clutch 111 lockings by unidirectional bearing, a temporary transient fixing force of borrowing so just can be provided, promote planetary wheel carrier 51 for anti-clockwise output planetary wheel 41 and output shaft 61 is made clockwise direction low speed, big torsion ground rotates.If the resistance of output shaft 61 not quite need improve the rotating speed of output, then can utilize an arrestment mechanism, regulate the rotating speed of speed governing sun gear 71 according to the demand of output shaft 61 rotating speeds, the rotating speed that speed governing sun gear 71 is braked will pass to gear ring 101 through speed governing planet wheel 91, gear ring 101 drives output planetary 41 again, rotating speed is delivered on the output shaft 61 by the speed ratio up time direction rotation of setting, and adds up with output shaft 61 original rotating speeds, and the rotating speed of output shaft 61 has just improved.The rotating speed of speed governing sun gear 71 is controlled many more, and the rotating speed that is added in output shaft 61 is just many more, otherwise the rotating speed of speed governing sun gear 71 is fast more, and the rotating speed of output shaft 61 is just slow more.So very effectively, can change the rotating speed and the torsion of output incessantly, reach infinite variable speed purpose.
Embodiment two; As shown in Figure 5, this stepless speed changes devices mainly comprises supporting frame 11, in the supporting frame 11 epicyclic train is installed, train of gearings comprises driving sun gear 31, driving sun gear 31 is fixedly connected on input shaft 21, be engaged with 3 to 6 output planetary wheels 41 along driving sun gear 31 peripheries, output planetary wheel 41 is installed on the planetary wheel carrier 51, planetary wheel carrier 51 connects output shaft 61, on the input shaft 21 in driving sun gear 31 the place aheads, also be provided with a speed governing sun gear 71,71 outer gearings of speed governing sun gear have 3 to 6 speed governing planet wheels 92, each speed governing planet wheel 92 is installed on the planetary wheel carrier 51, the revolution diameter of speed governing planet wheel 92 is greater than the revolution diameter of planet wheel 41, each output planetary wheel 41 and gear ring 101 engagements, on output shaft 61, be fixed with output sun gear 122,122 outer gearings of output sun gear have 3 to 6 planet wheels 131, the planetary wheel carrier of planet wheel 131 is fixed in the gear ring 101, it is overrunning clutch 111 that gear ring 101 is equipped with unilateral bearing, unilateral bearing is that overrunning clutch 111 is fixed in the supporting frame, speed governing planet wheel 92 is engaged in the gear ring 141 speed governing sun gear 71 simultaneously with planet 131, driving sun gear 31, output sun gear 122, planetary wheel carrier 51, output shaft 61, input shaft 21, gear ring 141,101, unilateral bearing is that overrunning clutch 111 is provided with for same axle center.
Its working procedure and principle are as follows: input shaft 21, driving sun gear 31, rotation in the direction of the clock, driving sun gear 31 drive output planetaries wheel 41 separately counterclockwise rotation simultaneously output planetary take turns 41 integral body and revolve round the sun along gear ring 101 inner ring clockwise directions, the integral body revolution of output planetary wheel 41 drives planet carrier 51 and output sun gear 122 and output shaft 61 and rotates, gear ring 101 is overrunning clutch 111 lockings by unidirectional bearing oppositely at this moment, and output shaft 61 is with regard to dynamic output.If gear ring 101 does not add the clockwise direction rotation, the power of the usefulness that then do not raise speed, this moment, the rotating speed of output shaft 61 was the slowest, the torsion maximum, output sun gear 122 equidirectional rotations of the rotation of planetary wheel carrier 51 drive simultaneously and speed governing planet wheel 92 counterclockwise rotation separately revolve round the sun along gear ring 141 inner ring clockwise directions with whole, speed governing planet wheel 92 drives speed governing sun gear 71 again and does the rotation of high speed clockwise direction, the 122 clockwise rotations of output sun gear are driving planet wheel 131 counterclockwise rotations, planet wheel 131 counterclockwise rotations promotion gear rings 141 also counterclockwise direction are put commentaries on classics, its power passes on the speed governing sun gear 71 through speed governing planet wheel 92 again, and the rotating speed of speed governing sun gear 71 can further be accelerated.When if output shaft 61 need overcome very big resistance, speed governing sun gear 71 is not just controlled at random and is rotated freely, the counter-rotating of gear ring 101 is that overrunning clutch 111 pins by unidirectional bearing, so just can provide a temporary transient firm force of borrowing to promote planet carrier 51 and output shaft 61 clockwise directions with low speed, torsion rotates greatly to anti-clockwise output planetary wheel 41.If the resistance of output shaft 61 not quite need improve the rotating speed of output, then can utilize arrestment mechanism, control the rotating speed of speed governing sun gear 71 according to the demand of output shaft 61 rotating speeds, the controlled rotating speeds of speed governing sun gear 71 drive gear rings 141, planet wheel 131, gear ring 101, drive output planetary wheel 41 again through speed governing planet wheels 92, the rotating speed that controls to speed governing sun gear 71 is added on the output shaft 61 by speed ratio (loop attenuation) clockwise direction of setting, and add up mutually with output shaft 61 original rotating speeds, the rotating speed of output has just improved.The controlled rotating speed of adding more on the output shaft 61 of the rotating speed of speed governing sun gear 71 is just fast more, otherwise the rotating speed of speed governing sun gear 71 is fast more, and the rotating speed of output shaft 61 is just slow more, so very effectively, can change the rotating speed and the torsion of output incessantly, reach infinite variable speed purpose.
Above-mentioned arrestment mechanism can be a kind of oil hydraulic pump or motor and generator of load.Above-described speed change gear all has the fine inertia that slides, can more effective minimizing energy consumption.
The above embodiments only are the part form of specific implementation of the present invention, are not breaking away from any conspicuous conversion on the structural principle of the present invention all in protection scope of the present invention.
Claims (3)
1. gear stepping type stepless speed change device, comprise that mainly epicyclic train and unilateral bearing are overrunning clutch (111), it is characterized in that: this train of gearings comprises that one connects the driving sun gear (31) of power intake, be engaged with 3 to 6 output planetary wheels (41) along driving sun gear (31) periphery, output planetary wheel (41) is installed on the planetary wheel carrier (51), planetary wheel carrier (51) is fixedlyed connected with clutch end, each output planetary wheel (41) is engaged in the gear ring (101) jointly, and unilateral bearing is that overrunning clutch (111) is arranged on the gear ring (101).
2. gear stepping type stepless speed change device according to claim 1, it is characterized in that: the fixedly connected input shaft in driving sun gear (31) the place ahead (21), the fixedly connected output shaft of planetary wheel carrier (51) (61), on input shaft (21), also be provided with speed governing sun gear (71), speed governing sun gear (71) outer gearing has 3 to 6 speed governing planet wheels (91), speed governing planet wheel (91) is installed on the planetary wheel carrier (81), planetary wheel carrier (81) is fixedlyed connected with input shaft (21), each speed governing planet wheel (91) is engaged in gear ring (101) engagement jointly, and unilateral bearing is overrunning clutch (111), gear ring (101), speed governing sun gear (71), driving sun gear (31), planetary wheel carrier (81,51) and output shaft (61), input shaft (21) is that same axle center is provided with.
3. gear stepping type stepless speed change device according to claim 1, it is characterized in that: the fixedly connected input shaft in driving sun gear (31) the place ahead (21), the fixedly connected output shaft of planetary wheel carrier (51) (61), on input shaft (21), also be provided with a speed governing sun gear (71), speed governing sun gear (71) outer gearing has 3 to 6 speed governing planet wheels (92), each speed governing planet wheel (92) is installed on the planetary wheel carrier (51), the revolution diameter of speed governing planet wheel (92) is greater than the revolution diameter of planet wheel (41), each output planetary wheel (41) and gear ring (101) engagement, on output shaft (61), be fixed with an output sun gear (122), the outer gearing of output sun gear (122) has 3 to 6 planet wheels (131), the planetary wheel carrier of planet wheel (131) is fixed in the gear ring (101), be engaged in the gear ring (141) gear ring (141) in speed governing planet wheel (92) and planet wheel (131) are common, gear ring (101), unilateral bearing is overrunning clutch (111), speed governing sun gear (71), driving sun gear (31), output sun gear (122), planetary wheel carrier (51) and output shaft (61), input shaft (21) is that same axle center is provided with.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200610101264 CN1880801A (en) | 2006-01-14 | 2006-06-27 | Gear stepping type stepless speed change device |
| PCT/CN2007/000121 WO2007079694A1 (en) | 2006-01-14 | 2007-01-12 | Gear type steeping stepless speed change device |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200610033000.7 | 2006-01-14 | ||
| CN 200610033000 CN1804430A (en) | 2006-01-14 | 2006-01-14 | Gear type stepping stepless transmission |
| CN 200610101264 CN1880801A (en) | 2006-01-14 | 2006-06-27 | Gear stepping type stepless speed change device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1880801A true CN1880801A (en) | 2006-12-20 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200610101264 Pending CN1880801A (en) | 2006-01-14 | 2006-06-27 | Gear stepping type stepless speed change device |
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| CN (1) | CN1880801A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103485780A (en) * | 2013-09-05 | 2014-01-01 | 中传重型装备有限公司 | Insertion board star-wheel driving device in heading machine and application thereof |
| CN103671741A (en) * | 2013-12-26 | 2014-03-26 | 重庆川仪自动化股份有限公司 | Planetary speed reducer |
| CN105387135A (en) * | 2014-09-04 | 2016-03-09 | 劲力工业有限公司 | Speed-increasing device used for power recharging of vehicle |
| CN108730435A (en) * | 2018-08-03 | 2018-11-02 | 重庆瑞阳科技股份有限公司 | The double dynamical infinitely variable transmission of electric vehicle |
| CN109826912A (en) * | 2017-11-23 | 2019-05-31 | 赵继瑛 | Gear arrangement, the electric vehicle including the device and the method for driving the device |
| CN110848345A (en) * | 2019-12-05 | 2020-02-28 | 重庆帕特龙智通电子科技有限公司 | Self-adaptive mechanical transmission of electric motor vehicle |
| CN114233816A (en) * | 2021-11-12 | 2022-03-25 | 北京航空航天大学 | Mechanical motion rectifier based on planetary gear train |
-
2006
- 2006-06-27 CN CN 200610101264 patent/CN1880801A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103485780A (en) * | 2013-09-05 | 2014-01-01 | 中传重型装备有限公司 | Insertion board star-wheel driving device in heading machine and application thereof |
| CN103485780B (en) * | 2013-09-05 | 2015-12-23 | 中传重型装备有限公司 | Star wheel driving device for shovel board and application thereof in development machine |
| CN103671741A (en) * | 2013-12-26 | 2014-03-26 | 重庆川仪自动化股份有限公司 | Planetary speed reducer |
| CN103671741B (en) * | 2013-12-26 | 2016-05-04 | 重庆川仪自动化股份有限公司 | A kind of planetary reduction gear |
| CN105387135A (en) * | 2014-09-04 | 2016-03-09 | 劲力工业有限公司 | Speed-increasing device used for power recharging of vehicle |
| CN109826912A (en) * | 2017-11-23 | 2019-05-31 | 赵继瑛 | Gear arrangement, the electric vehicle including the device and the method for driving the device |
| CN109826912B (en) * | 2017-11-23 | 2022-03-29 | 赵继瑛 | Transmission device, electric vehicle comprising the device and method for driving the device |
| CN108730435A (en) * | 2018-08-03 | 2018-11-02 | 重庆瑞阳科技股份有限公司 | The double dynamical infinitely variable transmission of electric vehicle |
| CN110848345A (en) * | 2019-12-05 | 2020-02-28 | 重庆帕特龙智通电子科技有限公司 | Self-adaptive mechanical transmission of electric motor vehicle |
| CN114233816A (en) * | 2021-11-12 | 2022-03-25 | 北京航空航天大学 | Mechanical motion rectifier based on planetary gear train |
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