CN101997361A - Motor speed change mechanism - Google Patents
Motor speed change mechanism Download PDFInfo
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- CN101997361A CN101997361A CN2009101636738A CN200910163673A CN101997361A CN 101997361 A CN101997361 A CN 101997361A CN 2009101636738 A CN2009101636738 A CN 2009101636738A CN 200910163673 A CN200910163673 A CN 200910163673A CN 101997361 A CN101997361 A CN 101997361A
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/003—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion the gear-ratio being changed by inversion of torque direction
- F16H3/005—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion the gear-ratio being changed by inversion of torque direction for gearings using gears having orbital motion
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Abstract
A motor speed change mechanism is used for transmission through a power input end. The motor speed change mechanism comprises a first planetary gear set, a second planetary gear set and a lantern ring, wherein the lantern ring is sleeved on the peripheries of the first and second planetary gear sets; and the motor speed change mechanism also comprises a first one-way clutch, a second one-way clutch and a power output end. The power input end rotates in the forward direction or reversal direction to drive the first planetary gear set and second planetary gear set in the lantern ring and separately correspond to the meshings of the first one-way clutch and the second one-way clutch, thus the power output end can be driven to switch the revolution speed.
Description
Technical field
The present invention relates to a kind of motor speed varying mechanism, refer to especially a kind ofly utilize positive and negative rotation of motor and cooperate a plurality of planetary gearsets to change the multisection type trasmission shifting system of speed.
Background technology
Speed changer is to be considerable spare part in general speed change electric motor car or the electronic hand tool etc., rough half that accounts for production cost of its whole speed change system, so one of research and development about gear in electric motor car or electronic hand tool industry all are the key projects of each factory, and good speed changer can make the rider in response to the difference of environment the different rotating ratio of conversion, and then reach the purpose of suitable rotating speed or torsional forces.
For the speed change electric motor car, the planetary gear group is the speed changer of using always.Planetary internal speed changer is then with the main body of planetary gear as gear, and gear is placed in the trailing wheel hub, changes planetary gear ratio by different input components, output and fixture, to reach different rotating ratios.
The internal speed changer that with the planetary gear is the gear main body has following advantage: 1. volume is little and structure is accurate, is difficult for being subject to that narrow and small rear-wheel hub is installed and the restriction of usage space; 2. the gear shift start is stable, and chain can effectively not improve shortcoming and raising transmission efficiency that chain takes off chain because of the gear shift conversion is connected with different sprocket wheel; 3. gear has the shell protection of hub for vehicle wheel, can not be subjected to the influence of external environment and then improves useful life; 4. be loaded in the gear in the hub for vehicle wheel, can not producing noise big as outer speed changer in the gearshift procedure.
According to planetary gear is in the transmission principle for speed changer, its central gear, planetary gear, outer ring gear distinctly have an axle, three kinds of gears twine rotation mutually, when different gear, it is that driving shaft, another axle then are output shafts that three gear shafts must have an axle to maintain static moving, axle.Under the various combination, just cause rotating speed can be slowed down, the required gear ratio of different gears such as acceleration, reverse gear.Wherein, the possibility that has six kinds of combinations of states is as shown in following:
| Combinations of states | 1 | 2 | 3 | 4 | 5 | 6 |
| Central gear | Fixing | Output | Fixing | Drive | Output | Drive |
| Planetary gear | Drive | Drive | Output | Output | Fixing | Fixing |
| Outer ring gear | Output | Fixing | Drive | Fixing | Drive | Output |
Therefore, the present invention on the mechanical realization of wheel car or electric motor car with planetary internal speed-changing mechanism as the development core, adding in recent years makes electric bicycle and electric motor car be able to large-scale popularization because of environmental issue, and the internal speed changer of arranging in pairs or groups mostly of electric bicycle and electric motor car at present, so internal speed changer becomes the emphasis that each big depot researches and develops gradually.
Summary of the invention
The objective of the invention is to be to provide a kind of motor speed varying mechanism, is the gear that utilizes positive and negative rotation of motor and cooperate a plurality of planetary gearsets to constitute, to reach the shifted purpose of multistage.
In order to achieve the above object, motor speed varying of the present invention mechanism, it includes:
One first planetary gearsets, it comprises: one first central gear, a plurality of first planetary gear, one first planet carrier and one first outer ring gear; Wherein, described power intake is to be connected with described first central gear;
One second planetary gearsets, it comprises: a secondary sun wheel, a plurality of second planetary gear, one second planet carrier and one second outer ring gear; Wherein, described first outer ring gear is connected with transferring power with described secondary sun wheel; And
One collar is the periphery that cover invests described first and second planetary gearsets, and it comprises: one first one-way clutch, one second one-way clutch and a clutch end; Wherein, described first one-way clutch is meshed with first outer ring gear, and described second one-way clutch is meshed with second outer ring gear, and described first and second one-way clutch is equidirectional one-way clutch; In addition, described clutch end is connected in the described collar with outputting power.
In order to achieve the above object, the present invention also provides a kind of motor speed varying mechanism, and it includes:
One first planetary gearsets, it comprises: one first central gear, a plurality of first planetary gear, one first planet carrier and one first outer ring gear; Wherein, described power intake is to be connected with described first outer ring gear;
One second planetary gearsets, it comprises: a secondary sun wheel, a plurality of second planetary gear, one second planet carrier and one second outer ring gear; Wherein, described first central gear is connected with transferring power with described second outer ring gear; And
One collar is the periphery that cover invests described first and second planetary gearsets, and it comprises: one first one-way clutch, one second one-way clutch and a clutch end;
Wherein, one first clutch-plate that described first one-way clutch is with described first central gear rotates synchronously is meshed, and described second one-way clutch then is meshed with one second clutch-plate that described secondary sun wheel rotates synchronously, and described first and second one-way clutch is equidirectional one-way clutch; In addition, described clutch end is connected in the collar with outputting power.
Forward or reverse by described power intake drives described first planetary gearsets and described second planetary gearsets in the described collar, and cooperate the engagement of described first and second one-way clutch in the described collar respectively, produce different speed reducing ratio or speed-up ratio, and the power of described power intake is slowed down or quicken output by the described collar, to reach the effect that the multistage rotating speed switches.
Description of drawings
Fig. 1 is the perspective exploded view of motor speed varying of the present invention mechanism first preferred embodiment;
Fig. 2 is the first deceleration mode schematic diagram of motor speed varying of the present invention mechanism first preferred embodiment;
Fig. 3 is the second deceleration mode schematic diagram of motor speed varying of the present invention mechanism first preferred embodiment;
Fig. 4 is the second preferred embodiment transmission schematic diagram of motor speed varying of the present invention mechanism;
Fig. 5 is the 3rd preferred embodiment transmission schematic diagram of motor speed varying of the present invention mechanism;
Fig. 6 is the 4th preferred embodiment transmission schematic diagram of motor speed varying of the present invention mechanism;
Fig. 7 is the first aero mode schematic diagram of motor speed varying of the present invention mechanism the 4th preferred embodiment;
Fig. 8 is the second aero mode schematic diagram of motor speed varying of the present invention mechanism the 4th preferred embodiment.
Description of reference numerals: 1,1a～motor speed varying mechanism; 11～the first planetary gearsets; 111～the first central gears; 112～the first planetary gears; 113～the first planet carriers; 114～the first outer ring gears; 115～the first protrude piece; 12～the second planetary gearsets; 121～secondary sun wheel; 122～the second planetary gears; 123～the second planet carriers; 124～the second outer ring gears; 125～the second protrude piece; 13～the third line star gear train; 131～the 3rd central gears; 132～the third line star gear; 133～the third line star frame; 134～the 3rd outer ring gears; 135～the 3rd protrude piece; 14～collar; 141～the first one-way clutch; 142～the second one-way clutch, 143～clutch end; 15～electric control clutch; 151～fixed block; 16～the 3rd one-way clutch; 17,17a, 17b～concentric shafts; 2,2a, 2b～power intake; 21a～motor body; 22a～driven wheel; 23a～driven gear; 3～flower drum shell; 4～central shaft; 116 first clutch-plates; 126～the second clutch-plates.
Embodiment
In order more clearly to describe motor speed varying mechanism proposed by the invention, below will cooperate graphic detailed description.
See also shown in Figure 1, wherein, described motor speed varying mechanism 1 is to carry out transmission by a power intake 2, and it includes: one first planetary gearsets 11, one second planetary gearsets 12, the third line star gear train 13, a collar 14 and an electric control clutch 15.
It more comprises described first planetary gearsets 11: one first central gear 111, a plurality of first planetary gear 112, one first planet carrier 113 and one first outer ring gear 114.It more comprises described second planetary gearsets 12: a secondary sun wheel 121, a plurality of second planetary gear 122, one second planet carrier 123 and one second outer ring gear 124.It comprises described the third line star gear train 13: one the 3rd central gear 131, a plurality of the third line star gear 132 (not shown), the third line star frame 133 and one the 3rd outer ring gear 134; Wherein, described the 3rd outer ring gear 134 is in shelly is coated on described the 3rd central gear 131 and a plurality of the third line star gear 132 (not shown), and is provided with one the 3rd in described the third line star frame 133 peripheries and protrudes piece 135.
In the present invention, described first planetary gearsets 11, second planetary gearsets 12 and the third line star gear train 13, just so-called " planetary gearsets (Planetary gear) " also is called " pinion gear reductor " or " epicyclic reduction gear of planetary type machine " on the market.In above-mentioned planetary gear reducing mechanism, the gear that is positioned at the center is called " central gear (sun gear) ", just first, second and third central gear 111,121,131; The gear that is positioned at the position, outer ring is called " outer ring gear (ring gear) ", just first, second and third outer ring gear 114,124,134; The gear that is surrounded on first, second and third central gear 111,121,131 rotations respectively is called " planetary gear (planet pinion) ", just first, second and third planetary gear 112,122,132.
Described first, two, three planet gear trains 11,12, in 13 described first, two, three planet gears 112,122, the 132nd, be one group with three or four mostly, and respectively with " planet carrier (Carrier Arm) " just first, two, three planet carriers 113,123,133 with each other described first, two, three planet gears 112,122,132 keep relative position to each other, and described first, two, three central gears 111,121,131 respectively with described first, two, three planet gears 112,122, during 132 interlocks rotation, its both direction of rotation must be opposite; Yet when described first, second and third outer ring gear 114,124,134 and described first, second and third planetary gear 112,122,132 interlocks rotation, both direction of rotation but are consistent
The described collar 14 is peripheries that cover invests described first planetary gear 11 and described second planetary gearsets 12, and it more comprises: one first one-way clutch 141, one second one-way clutch 142 and a clutch end 143.Described first one-way clutch 141 is set one first to protrude piece 115 and be meshing with each other on the described outer ring gear 114 with described first planetary gearsets 11; And described second one-way clutch 142 is set one second to protrude piece 125 and be meshing with each other on the described outer ring gear 124 with described second planetary gearsets 12.143 of described clutch ends are connected with described the 3rd central gear 131 of described the third line star gear train 13.
Described first one-way clutch 141 of the described collar 14 and described second one-way clutch 142 be equidirectional ratchet or ratchet one of them, and, in the present embodiment, described first and second one-way clutch 141,142 boths are equidirectional and can are the unidirectional ratchet of integrally formed (but clockwise direction transmission, counterclockwise then not transmission), and described first protrudes piece 115 and described second, and to protrude piece 125 then can be that a ratchet and described first and second one-way clutch 141,142 (ratchet) are meshing with each other.
When described first planetary gearsets 11 or second planetary gearsets 12 are just being changeed, described first protrudes piece 115 or second protrudes piece 125 and is engaged in described first one-way clutch 141 or second one-way clutch 142 in the described collar 14, and and then drives the described collar 14 and just transporting work.Otherwise, when described first planetary gearsets 11 or 12 counter-rotatings of second planetary gearsets, because the characteristic that described first one-way clutch 141 that meshes out of the ordinary or second one-way clutch 142 only limit to one-directional rotation, make described first planetary gearsets 11 or second planetary gearsets 12 in the described collar 14, be the phenomenon of idle running, just can't drive the running of reversing of the described collar 14.
Described first central gear 111 of described first planetary gearsets 11 is to combine with described power intake 2, the described outer ring gear 114 of described first planetary gearsets 11 then with 121 coaxial connections of described secondary sun wheel of described second planetary gearsets 12.When described power intake 2 drives at described first planetary gearsets 11 in the described collar 14, make at least described first planetary gearsets 11 in the described collar 14 or described second planetary gearsets 12 one of them by described first one-way clutch 141 or second one-way clutch 142 the described collar 14 is just being changeed driving.
The power that described the 3rd protrusion piece 135 of described the third line star gear train 13 will come from the described clutch end 143 of the described collar 14 limits kinetic energy to unidirectional exporting on the flower drum shell 3 through one the 3rd one-way clutch 16.That is to say, described one-way clutch 16 is arranged at the inner edge of described flower drum shell 3 and protrudes with the described the 3rd that piece 135 is meshing with each other and corresponding, in order to guarantee that described flower drum shell 3 carries out single direction and rotates, described flower drum shell 3 then roughly is arranged on the driving wheel of general wheel car, rotates in order to drive wheels.Because it is can be ratchet and the cooperating of unidirectional ratchet that described the 3rd one-way clutch 16 and the described the 3rd protrudes piece 135, be not that emphasis of the present invention is died and just no longer given unnecessary details at this.
Described electric control clutch 15 is and described power intake 2 synchronous operations, described electric control clutch 15 can be a normal-open electromagnetic valve, importing a predetermined current makes the fixed block 151 on the described electric control clutch 15 produce axial displacement, whether fix in order to described the 3rd outer ring gear 134 of controlling described the third line star gear train 13, when described power intake 2 operates, form stiff end to reach described the 3rd outer ring gear 134 of control, and then the power of described power intake 2 is output on the described flower drum shell 3 by described the third line star frame 133.Because described electric control clutch 15 is to belong to the spare part that can buy on the market, be not that emphasis of the present invention is so just no longer given unnecessary details at this.
In preferred embodiment of the present invention, described power intake 2 can be a DC direct-current electric motor, and described direct-current electric motor is the direction that can change its input current both positive and negative polarity, and then the described central gear 111 that drives described first planetary gearsets 11 carries out forward or reverse.Described power intake 2 starts described electric control clutch 15 synchronously when running, make described the 3rd outer ring gear 134 be fixed; And described power intake 2 is when shutting down, 15 of described electric control clutch are discharged described the 3rd outer ring gear 134, described the 3rd outer ring gear 134 can freely be rotated, described the third line star gear train 13 internal gears are stuck with described the third line star frame 133 of avoiding described flower drum shell 3 to be connected because of revolution.
Certainly, no matter during the output of described power intake 2 (DC direct-current electric motor) forward or reverse, all can utilize described first planetary gearsets 11 or described second planetary gearsets 12 to drive the described collar 14 and carry out the equidirectional work of just transporting, the described the third line star frame 133 that further drives described the third line star gear train 13 carries out deceleration transmission with described flower drum shell 3.
See also shown in Figure 2ly, Fig. 2 is the first deceleration mode schematic diagram of motor speed varying of the present invention mechanism first preferred embodiment, and wherein, the dotted line A in Fig. 2 is the power transmission path of the described power intake 2 of representative, the just power transmission path of first deceleration mode.When described power intake 2 (DC d.c. motor) just change (following graphic just the commentaries on classics with symbol :+, counter-rotating is with symbol :-representative), described first central gear 111 that drives described first planetary gearsets 11 carries out forward running (just changeing), and described first planetary gear 112 that is meshed with described first central gear 111 then operates (counter-rotating) in the opposite direction.
Because described first planetary gear 112 is to be fixed by described first planet carrier 113, so according to the planetary gear transmission principle, the power that described first central gear 111 is exported is passed on described first outer ring gear 114 by described first planetary gear 112, and because described first outer ring gear 114 is to be meshed with described first planetary gear 112.Therefore, described first outer ring gear 114 is to be same oppositely running (counter-rotating) with described first planetary gear 112.
Because described first outer ring gear 114 is with reverse running (counter-rotating), therefore, described first one-way clutch 141 that described first outer ring gear, the 114 peripheral set described first protrusion pieces 115 can't drive in the described collar 14 carry out forward running (just changeing), make described first one-way clutch 141 present idling conditions (symbol * represent transmission of power invalid), just the kinetic energy of described first planetary gearsets 11 can't be transferred on the described collar 14 by described first one-way clutch 141, and then by a concentric shafts 17 (seeing also shown in Figure 1) with described secondary sun wheel 121 coaxial are connected of described first outer ring gear 114 with described second planetary gearsets 12, making described first outer ring gear 114 and described secondary sun wheel 121 is running (counter-rotating) in the same way, makes the kinetic energy of described power intake 2 be able to by directly being passed on described second planetary gearsets 12 after 11 decelerations of described first planetary gearsets.
And then, the kinetic energy that the described secondary sun wheel 121 (counter-rotating) of described second planetary gearsets 12 will come from described first planetary gearsets 11 is passed on described second planetary gear 122 that is meshed, make described second planetary gear 122 be in reverse running with described secondary sun wheel 121, this moment, described second planetary gear 122 presented forward running (just changeing).
More because described second planetary gear 122 is to be fixed by described second planet carrier 123, so according to the planetary gear transmission principle, the kinetic energy that described secondary sun wheel 121 is exported is passed on described second outer ring gear 124 by described second planetary gear 122, and because described second outer ring gear 124 is to be meshed with described second planetary gear 122.Therefore, described second outer ring gear 124 is to be same forward running (just changeing) with described second planetary gear 122.
Hold above-mentioned, because described second outer ring gear 124 is with forward running (just changeing), therefore, described second one-way clutch 142 that described second outer ring gear, the 124 peripheral set described second protrusion pieces 125 will drive in the described collar 14 carry out forward running (just changeing), just the kinetic energy with described second planetary gearsets 12 transfers on the described collar 14 by described second one-way clutch 142, and then the kinetic energy after described first planetary gearsets 11 and described second planetary gearsets 12 accumulation slowed down is by described three central gear 131 coaxial are connected of described clutch end 143 with described the third line star gear train 13, and the kinetic energy after more described the 3rd protrusion piece 135 by described the third line star gear train 13 will slow down passes through described the 3rd one-way clutch 16 kinetic energy is limited the unidirectional described flower drum shell 3 that exports to.
That is to say, in the present invention's first deceleration mode, described power intake 2 (DC d.c. motor) is for just transferring out, via described first, second planetary gearsets 11,12 are passed to described the third line star gear train 13 with the kinetic energy the imported described clutch end 143 by the described collar 14, but because described first one-way clutch 141 that described first outer ring gear 114 (counter-rotating) of described first planetary gearsets 11 can't drive in the described collar 14 is just changeing (being reverse idling conditions), so the kinetic energy after 11 decelerations of described first planetary gearsets is output in described second planetary gearsets 12 by described concentric shafts 17, and described second one-way clutch 142 that utilizes described second outer ring gear 124 (just changeing) to drive in the described collar 14 is just changeing, and then the described clutch end 143 that drives the described collar 14 is just changeing, and pass through described clutch end 143 with described first in the described collar 14, second planetary gearsets 11,12 accumulate described the 3rd central gear 131 (just changeing) that the kinetic energy that slows down is passed to described the third line star gear train 13, and described the 3rd outer ring gear 134 is fixed by described electric control clutch 15, kinetic energy after the third line star frame 133 of the fixing described the third line star gear 132 (counter-rotating) of order will slow down protrudes piece 135 by the described the 3rd and is passed to described the 3rd one-way clutch 16, makes unidirectional the exporting on the described flower drum shell 3 of kinetic energy restriction.
For instance, in preferred embodiment of the present invention, be that 4000rpm (per minute turn-take number) is an example, and that the number of teeth of described first, second and third planetary gearsets 11,12,13 is joined tooth is as follows with described power intake 2 (DC d.c. motor) rotating speed:
First, second, third central gear, 111,121,131 numbers of teeth are: 25 teeth;
First, second, third planetary gear, 112,122,132 numbers of teeth are: 26 teeth; And
First, second, third outer ring gear, 114,124,134 numbers of teeth are: 77 teeth.
Learnt that by above data computation described first, second planetary gearsets 11,12 each other gear reduction ratios are 3.08, the gear reduction ratio of described the third line star gear train 13 then is 4.08.
And in first deceleration mode of motor speed varying of the present invention mechanism 1, described power intake 2 (DC d.c. motor) be with just transfer into, through first, second planetary gearsets 11,12 in the described collar 14 and after cooperating described the third line star gear train 13 to slow down, become the slow-revving described motor speed varying of high torsion mechanism 1; Wherein, to export the calculating formula of rotating speed rpm of described flower drum shell 3 to as follows for described power intake 2 (DC d.c. motor):
3.08 * 3.08 * 4.08=38.7[is via the gear reduction ratio of first, second and the third line star gear train accumulation]
4000 (rpm) [power intake rotating speed] ÷ 38.7=103.35 (rpm) [flower drum shell rotating speed]
Therefore, in first deceleration mode, described power intake 2 (DC d.c. motor) is reduced to 103.35rpm and exports flower drum shell 3 to by described motor speed varying mechanism 1 by script 4000rpm output, reaches the purpose of the high torsion of the slow-speed of revolution.
See also shown in Figure 3ly, Fig. 3 is the second deceleration mode schematic diagram of motor speed varying of the present invention mechanism first preferred embodiment, and wherein, the dotted line B in Fig. 2 is the power transmission path of the described power intake 2 of representative, the just power transmission path of second deceleration mode.Described power intake 2 just the DC d.c. motor oppositely during (counter-rotating) outputting power (following graphic just the commentaries on classics with symbol :+, counter-rotating is with symbol :-represent), described first central gear 111 that drives described first planetary gearsets 11 oppositely operates (counter-rotating), and described first planetary gear 112 that is meshed with described first central gear 111 then operates (just changeing) with forward.
Because described first planetary gear 112 is to be fixed by described first planet carrier 113, so according to the planetary gear transmission principle, the power that described first central gear 111 is exported is passed on described first outer ring gear 114 by described first planetary gear 112, and because described first outer ring gear 114 is to be meshed with described first planetary gear 112.Therefore, described first outer ring gear 114 is to be same forward running (just changeing) with described first planetary gear 112.
Because described first outer ring gear 114 is with forward running (just changeing), therefore, described first one-way clutch 141 that described first outer ring gear, the 114 peripheral set described first protrusion pieces 115 will drive in the described collar 14 carry out forward running (just changeing), and the kinetic energy of described first planetary gearsets 11 is transferred on the described collar 14 by described first one-way clutch 141.
Described first outer ring gear 114 makes described first outer ring gear 114 and described secondary sun wheel 121 be running (just changeing) in the same way by 121 coaxial connections of described secondary sun wheel of described concentric shafts 17 with described second planetary gearsets 12.And will coming from the kinetic energy of described first planetary gearsets 11, the described secondary sun wheel 121 (just changeing) of described second planetary gearsets 12 is passed on described second planetary gear 122 that is meshed, make described second planetary gear 122 be in reverse running with described secondary sun wheel 121, this moment, described second planetary gear 122 presented forward running (counter-rotating).
More because described second planetary gear 122 is to be fixed by described second planet carrier 123, so according to the planetary gear transmission principle, the kinetic energy that described secondary sun wheel 121 is exported is passed on described second outer ring gear 124 by described second planetary gear 122, and because described second outer ring gear 124 is to be meshed with described second planetary gear 122.Therefore, described second outer ring gear 124 is to be same oppositely running (counter-rotating) with described second planetary gear 122.
Because described second outer ring gear 124 is with reverse running (counter-rotating), therefore, described second one-way clutch 142 that described second outer ring gear, the 124 peripheral set described second protrusion pieces 125 can't drive in the described collar 14 carry out forward running (just changeing), make described second one-way clutch 142 present idling conditions (symbol * represent transmission of power invalid), just the kinetic energy of described second planetary gearsets 11 can't be transferred on the described collar 14 by described second one-way clutch 141.At this moment, in the described collar 14, only there is described first planetary gearsets 11 effectively described power intake 2 to be carried out speed-down action by described first one-way transmission 141, and then the kinetic energy after described first planetary gearsets 11 slowed down is by described three central gear 131 coaxial are connected of described clutch end 143 with described the third line star gear train 13, kinetic energy after the more described the third line star frame 133 by described the third line star gear train 13 will slow down protrudes piece 135 by the described the 3rd and is passed to described the 3rd one-way clutch 16, makes unidirectional the exporting on the described flower drum shell 3 of kinetic energy restriction.
That is to say, in the present invention's second deceleration mode, described power intake 2 (DC d.c. motor) is counter-rotating output, because described second planetary gearsets 12 is to be reverse idling conditions in the described collar 14, can't drive the described collar 14 and carry out forward running (just changeing), only the kinetic energy the imported described clutch end 143 by the described collar 14 is passed to described the third line star gear train 13 by described first planetary gearsets 11 in the described collar 14, and be passed to described the 3rd central gear 131 (just changeing) of described the third line star gear train 13 by the kinetic energy that described clutch end 143 is slowed down described first planetary gearsets 11 in the described collar 14, and described the 3rd outer ring gear 134 is fixed by described electric control clutch 15, kinetic energy after the third line star frame 133 of the fixing described the third line star gear 132 (counter-rotating) of order will slow down protrudes piece 135 by the described the 3rd and is passed to described the 3rd one-way clutch 16, makes unidirectional the exporting on the described flower drum shell 3 of kinetic energy restriction.
And in second deceleration mode of motor speed varying of the present invention mechanism 1, described power intake 2 (DC d.c. motor) is with 4000rpm counter-rotating input, and the gear reduction ratio of described first, second, third planetary gearsets 11,12,13 is all identical with described first slowdown module, by described first planetary gearsets 11 in the described collar 14 and after cooperating described the third line star gear train 13 to slow down, become the high-revolving described motor speed varying of low torsion mechanism 1; Wherein, to export the calculating formula of rotating speed rpm of described flower drum shell 3 to as follows for described power intake 2 (DC d.c. motor):
3.08 * 4.08=12.57[via first and the gear reduction ratio of the third line star gear train accumulation]
4000 (rpm) [power intake rotating speed] ÷ 12.57=318.22 (rpm) [flower drum shell rotating speed]
Therefore, in second deceleration mode, described power intake 2 (DC d.c. motor) is reduced to 318.22rpm and exports flower drum shell 3 to by described motor speed varying mechanism 1 by script 4000rpm output, reaches the purpose of the low torsion of high rotating speed.
Hold above-mentioned, motor speed varying of the present invention mechanism 1 as shown in Figures 2 and 3 can change the speed that described power intake 2 is exported by controlling the DC d.c. motor rotating just of described power intake 2, forming first and second deceleration mode switches alternately so that different speed reducing ratio to be provided, further reach the output of conversion rate and torsion, can select the conversion of different gears (deceleration mode) according to start to walk, climb, cruise required different qualities and different road conditions, make described power intake 2 more efficient performances.
Utilize described power intake 2 rotatings and carry out the speed change transmission by first planetary gearsets 11, second planetary gearsets 12 and the third line star gear train 13, also having another benefit is exactly to handle the frictional force that clutch or power path are produced when switching when not having general existing gear graduation gear shift in the process of speed-change and gearshift, to reduce the abrasion loss between actuated element, more provide the user gear shift easily.
In other preferred embodiments of the present invention of the following stated, because of most element is the same as or similar to previous embodiment, so components identical and will repeating no more below the structure, and components identical will directly give identical title and numbering, and for similar elements then give same names but after former numbering, increase in addition an English alphabet as a means of the difference and will not give unnecessary details, close chat earlier bright.
See also shown in Figure 4ly, wherein, the difference of second preferred embodiment of the present invention and aforementioned first preferred embodiment is that described power intake 2a is the motor of an inner rotator type, and is positioned within the described flower drum shell 3 and is fixed on the central shaft 4.Described power intake 2a more comprises: a motor body 21a, a driven wheel 22a and a driven gear 23a.
Described driven gear 23a and described first, second, the 3rd central gear 111,121,131 and the described clutch end 143 of the described collar 14 be articulated in respectively on the described central shaft 4, and described motor body 21a and described driven wheel 22a are concentric to link, further drive the described driven gear 23a that described driven wheel 22a is meshed, and described first central gear, 111 concentrics of described driven gear 23a and described first planetary gearsets 11 link, the power that makes described motor body 21a be exported transfers to described the third line star gear 132 indirectly, turns round to drive described flower drum shell 3.
See also shown in Figure 5, wherein, the difference of the 3rd preferred embodiment of the present invention and aforementioned second preferred embodiment is, the motor that described power intake 2b is an external rotor type (for example: the wheel hub motor), be to be positioned within the described flower drum shell 3 and with described first, second, the 3rd central gear 111,121,131 and the described clutch end 143 of the described collar 14 be articulated in respectively on the described central shaft 4, the described power intake 2b (motor of external rotor type) and described first central gear, 111 concentrics of described first planetary gearsets 11 are linked, the power that makes described power intake 2b (motor of external rotor type) be exported transfers to described the third line star gear 132 indirectly, turns round to drive described flower drum shell 3.
See also shown in Figure 6, wherein, the difference of the 4th preferred embodiment of the present invention and aforementioned first preferred embodiment is, to be power that described power intake 2 is exported carry out two-part by described motor speed varying mechanism 1 slows down in described first preferred embodiment, the 4th preferred embodiment of the present invention then is to utilize described power intake 2 by the described motor speed varying 1a of mechanism described flower drum shell 3 to be carried out two sections aero modes by changing the different power transmission combination of the described motor speed varying 1a of mechanism inner member to reach, and then the purpose of user's speed-change and gearshift is provided.
The described motor speed varying 1a of mechanism of the present invention's the 4th preferred embodiment, it more comprises: one first clutch-plate 116 and one second clutch-plate 126.The two ends of described concentric shafts 17a are fixed in the center of described first central gear 111 and described second outer ring gear 124 respectively with transferring power, and described first clutch-plate 116 is fixed on the described concentric shafts 17a, and it is be positioned at the central interval of described first central gear 111 and described second outer ring gear 124, and corresponding mutually and mesh with described first one-way clutch 141 in the described collar 14.
Described second clutch-plate 126 is fixed on another concentric shafts 17b, and described concentric shafts 17b is connected in the center of described secondary sun wheel 121 and with described concentric shafts 17a to be same axial line, described second clutch-plate 126 is to be synchronous rotation with described secondary sun wheel 121, is positioned at the described collar 14 and the corresponding mutually and engagement of described second one-way clutch 142 simultaneously.
The described motor speed varying 1a of mechanism carries out transmission by described power intake 2, and described power intake 2 is to be concentric with described first outer ring gear 114 to be connected, continuous action relation by described first planetary gearsets 11, make described first planetary gear 112 drive described first central gear 111, and drive described first clutch-plate 116 that is fixed on the described concentric shafts 17a simultaneously and be meshing with each other with described first one-way clutch 141 in the described collar 14.
And then kinetic energy is passed to described second planetary gearsets 12 that is connected by described concentric shafts 17a, continuous action relation by described second planetary gearsets 12 inside, make described second outer ring gear 124 drive described second planetary gears 122 and the described secondary sun wheel 121 that is meshed carried out interlock, make be positioned on the described concentric shafts 17b described second one-way clutch 142 of affixed described second clutch-plate 126 and the described collar 14 be meshing with each other.
Because described first and second one-way clutch 141,142 is equidirectional one-way clutch, that is to say when described first clutch-plate 116 or second clutch-plate 126 are just changeing (+) synchronously by described first central gear 111 or secondary sun wheel 121 drives, is to drive described first one-way clutch 141 or second one-way clutch 142 that is meshed respectively; Otherwise, described first clutch-plate 116 or second clutch-plate 126 then can't drive described first one-way clutch 141 or second one-way clutch 142 that is meshed when counter-rotating (-), make described first clutch-plate 116 or second clutch-plate 126 be idling conditions in the described collar 14.
In other words, no matter be described power intake 2 when just changeing (+) or counter-rotating (-) outputting power, all driving described first clutch-plate 116 or second clutch-plate 126 one of them and described first one-way clutch 141 or second one-way clutch 142 at least meshes and just changes (+), and further kinetic energy is passed on the described collar 14, the acceleration kinetic energy that makes the described clutch end 143 on the described collar 14 be able to described power intake 2 is exported is passed on the described flower drum shell 3 by described the third line star gear train 13.
See also shown in Figure 7ly, Fig. 7 is the first aero mode schematic diagram of the present invention's the 4th preferred embodiment, and wherein, the dotted line C in Fig. 7 is the power transmission path of the described power intake 2 of representative, the just power transmission path of first aero mode.When described power intake 2 is exported for just changeing (+), described first outer ring gear 114 of described first planetary gearsets 11 is just changeing (+) for just changeing described first planetary gear 112 of (+) drive, and then described first central gear 111 of interlock reverse (-), make described concentric shafts 17a go up affixed described first clutch-plate 116 of concentric and described second outer ring gear 124 reverse (-) simultaneously, at this moment, described first clutch-plate 116 that 111 of described first central gears drive synchronously can't just change drive with the described collar 14 by described first one-way clutch 141 (only limiting to just changes clockwise) for counter-rotating (-), so further power is transmitted on described second planetary gearsets 12 by described concentric shafts 17a.
In addition, described second outer ring gear 124 of described second planetary gearsets 12 is will come from kinetic energy that described first planetary gearsets 11 accumulated by described concentric shafts 17a to be sent to described second planetary gear 122 reverse (-), and then drive described secondary sun wheel 121 and just changeing (+), make described concentric shafts 17b go up affixed described second clutch-plate 126 of concentric simultaneously and just changeing (+), at this moment, described second clutch-plate 126 is just changeing (+) and by described second one-way clutch 142 the described collar 14 is just being changeed (+) drive clockwise.
Therefore, described power intake 2 carries out twice accumulation by described first and second planetary gearsets 11,12 with speed to quicken, and further kinetic energy being passed to described the third line star gear train 13 by the described clutch end 143 on the described collar 14, the described flower drum shell 3 that described the third line star gear 132 of described the third line star gear train 13 is connected carries out interlock.Because described the third line star gear train 13 is identical with the present invention's first preferred embodiment with the detailed interlock mode of described flower drum shell 3, so give unnecessary details no longer in detail at this.
See also shown in Figure 8ly, Fig. 8 is the second aero mode schematic diagram of the present invention's the 4th preferred embodiment, and wherein, the dotted line D in Fig. 8 is the power transmission path of the described power intake 2 of representative, the power transmission path of just described second aero mode.When described power intake 2 is exported for counter-rotating (-), described first outer ring gear 114 of described first planetary gearsets 11 is for counter-rotating (-) and drive described first planetary gear 112 reverse (-), and then described first central gear 111 of interlock is just changeing (+), make described concentric shafts 17a go up affixed described first clutch-plate 116 of concentric simultaneously and just changeing (+) with described second outer ring gear 124, at this moment, described first clutch-plates 116 that 111 of described first central gears drive synchronously are for just changeing (+), and by described first one-way clutch 141 with the described collar 14 further drives for just changeing (+) (clockwise).
In addition, by described concentric shafts 17a described second planetary gear of described second outer ring gear, 124 interlocks that drives synchronously just changeing (+), and then drive described secondary sun wheel 121 reverse (-), make described concentric shafts 17b go up affixed described second clutch-plate 126 of concentric reverse (-) simultaneously, at this moment, described second clutch-plate 126 can't just change (clockwise) with the described collar 14 by described second one-way clutch 142 and drive and to form idling conditions, so only there is described first planetary gearsets 11 that the kinetic energy of described power intake 2 is carried out speed change one time.
Therefore, because second aero mode of Fig. 8 has lacked the twice accumulation acceleration that described second planetary gearsets 12 is produced than described first aero mode of Fig. 7, so the speed that described first aero mode is passed to described flower drum shell 3 is more very fast than described second aero mode, further reaches and user's gear shift is provided and switches different aero modes to form two-part aero mode (that is: first aero mode and second aero mode) so control the described motor speed varying 1a of mechanism with the forward or reverse of described power intake 2.
In sum, a kind of motor speed varying of the present invention mechanism 1 is the both positive and negative polarity that utilizes described power intake 2 (DC d.c. motor) conversion input current, change the forward or reverse of described power intake 2 thus, make described motor speed varying mechanism 1 form having first and second deceleration mode providing different speed reducing ratio to switch alternately, further reach the output of conversion rate and torsion.
In first deceleration mode, it utilizes described power intake 2 (DC d.c. motor) just changeing and cooperates described first in the described collar 14, second planetary gearsets 11,12 accumulate deceleration, because described first, second planet carrier 113,123 is stiff end, and described first on the described collar 14, second one-way clutch 141,142 all only limit to based on forward running (just changeing), so described first outer ring gear 114 is oppositely running (counter-rotating), further make described first projection 115 on described first outer ring gear 114 on described first one-way clutch 141, present idling conditions, and the kinetic energy after will slowing down is accumulated and be passed to described second planetary gearsets 12, protrude described second one-way clutch 142 of piece 125 drives by described second on the described second outer ring gear group 124 and carry out forward running (just changeing), and then described the 3rd central gear 131 of described the third line star gear train 13 of 143 coaxial connections of described clutch end that makes the described collar 14 is with forward running (just changeing), and by described electric control clutch 15 described the 3rd outer ring gear 134 is fixed, the kinetic energy after the third line star frame 133 of the fixing described the third line star gear 132 (counter-rotating) of order will slow down passes through described the 3rd one-way clutch 16 kinetic energy is limited the unidirectional described flower drum shell 3 that exports to.
In addition, in second deceleration mode, it utilizes described power intake 2 (DC d.c. motor) to operate with counter-rotating and cooperates described first planetary gearsets 11 in the described collar 14 to slow down, because described first, second planet carrier 113,123 are made as stiff end, and described first in the described collar 14, second one-way clutch 141,142 all only limit to based on forward running (just changeing), oppositely then being idling conditions can't drive the described collar 14 and just transporting work, so when described first outer ring gear 114 operates (just changeing) for forward, further make described first projection 115 on described first outer ring gear 114 carry out forward running (just changeing) by the described collar 14 of described first one-way clutch, 141 drives.
And utilize described concentric shafts 17 with 121 coaxial connections of described secondary sun wheel of described first outer ring gear 114 with described second planetary gearsets 12, make the described second outer ring gear group 124 oppositely operate (counter-rotating), make the described second protrusion piece 125 can't drive described second one-way clutch 142 and carry out forward running (presenting idling conditions), making only has described first planetary gearsets 11 effectively described power intake 2 to be carried out speed-down action by described first one-way transmission 141 in the described collar 14, and then the kinetic energy after described first planetary gearsets 11 slowed down is connected and operates (just changeing) with forward by described the 3rd central gear 131 of described clutch end 143 and described the third line star gear train 13 is coaxial, and by described electric control clutch 15 described the 3rd outer ring gear 134 is fixed, the kinetic energy after the third line star frame 133 of the fixing described the third line star gear 132 (counter-rotating) of order will slow down limits kinetic energy to the unidirectional described flower drum shell 3 that exports to through described the 3rd one-way clutch 16.
In one embodiment, described power intake 2a is the motor of an inner rotator type, is to be positioned within the described flower drum shell 3 and to be fixed on the central shaft 4.Described power intake 2a more comprises: a motor body 21a, a driven wheel 22a and a driven gear 23a.Described motor body 21a drives the described driven gear 23a that described driven wheel 22a is meshed, and described first central gear, 111 concentrics of described driven gear 23a and described first planetary gearsets 11 link, the power that makes the described motor body 21a of described power intake 2a be exported transfers to described the third line star gear 132 indirectly, turns round to drive described flower drum shell 3.
In one embodiment, the motor that described power intake 2b is an external rotor type (wheel hub motor), be to be positioned within the described flower drum shell 3, described first central gear, 111 concentrics of described power intake 2b and described first planetary gearsets 11 are linked, the power that makes described power intake 2b be exported transfers to described the third line star gear 132 indirectly, turns round to drive described flower drum shell 3.
In one embodiment, be to utilize described power intake 2 that described flower drum shell 3 is carried out two sections aero modes so that the purpose of gear shift to be provided to reach by changing the different transmission combination of the described motor speed varying 1a of mechanism inner member.The described motor speed varying 1a of mechanism more comprises: one first clutch-plate 116 and one second clutch-plate 126.The two ends of described concentric shafts 17a are fixed in the center of described first central gear 111 and described second outer ring gear 124 respectively, and described first clutch-plate 116 is fixed on the described concentric shafts 17a, and be positioned at the central interval of described first central gear 111 and described second outer ring gear 124, and be meshing with each other with described first one-way clutch 141 in the described collar 14.
Described second clutch-plate 126 is fixed on another concentric shafts 17b, and described concentric shafts 17b is connected in the center of described secondary sun wheel 121 and with described concentric shafts 17a and is same axial line, described second clutch-plate 126 is to be synchronous rotation with described secondary sun wheel 121, is positioned at the described collar 14 simultaneously and is meshing with each other with described second one-way clutch 142.
The described motor speed varying 1a of mechanism carries out transmission by described power intake 2, and described power intake 2 is to be concentric with described first outer ring gear 114 to be connected, continuous action relation by described first planetary gearsets 11, make described first planetary gear 112 drive described first central gear 111, and drive described first clutch-plate 116 that is fixed on the described concentric shafts 17a simultaneously and be meshing with each other with described first one-way clutch 141 in the described collar 14.
And then kinetic energy is passed to described second planetary gearsets 12 that is connected by described concentric shafts 17a, continuous action relation by described second planetary gearsets 12 inside, make described second outer ring gear 124 drive described second planetary gears 122 and the described secondary sun wheel 121 that is meshed carried out interlock, make be positioned on the described concentric shafts 17b described second one-way clutch 142 of affixed described second clutch-plate 126 and the described collar 14 be meshing with each other.
Described power intake 2 utilizes the input mode of forward or reverse and then makes described first, second clutch-plate 116,126 and described first, second one-way clutch 141,142 produce the transmission combination of different engagements, and the speed-up ratio that described first, second planetary gearsets 11,12 is produced transfers on the described flower drum shell 3 by described the third line star gear 13, and first aero mode and second aero mode purpose to provide user's gear shift to quicken further is provided.
More than explanation is just illustrative for the purpose of the present invention, and nonrestrictive, those of ordinary skills understand; under the situation of the spirit and scope that do not break away from following claims and limited, can make many modifications, change; or equivalence, but all will fall within the scope of protection of the present invention.
Claims (10)
1. a motor speed varying mechanism is characterized in that, is to carry out transmission by a power intake, and it includes:
One first planetary gearsets, it comprises: one first central gear, a plurality of first planetary gear, one first planet carrier and one first outer ring gear; Wherein, described power intake is to be connected with described first central gear;
One second planetary gearsets, it comprises: a secondary sun wheel, a plurality of second planetary gear, one second planet carrier and one second outer ring gear; Wherein, described first outer ring gear is connected with transferring power with described secondary sun wheel; And
One collar is the periphery that cover invests described first and second planetary gearsets, and it comprises: one first one-way clutch, one second one-way clutch and a clutch end; Wherein, described first one-way clutch is meshed with first outer ring gear, and described second one-way clutch is meshed with second outer ring gear, and described first and second one-way clutch is equidirectional one-way clutch; In addition, described clutch end is connected in the described collar with outputting power.
2. motor speed varying according to claim 1 mechanism, it is characterized in that, it more includes: the third line star gear train, and it comprises: one the 3rd central gear, a plurality of the third line star gear, the third line star frame, one the 3rd outer ring gear and one the 3rd one-way clutch; Wherein, described the 3rd central gear is to link with described clutch end, and a plurality of the third line star gears are contacted by described the third line star frame, and kinetic energy is output in a flower drum shell, and utilizes described the 3rd one-way clutch to control described the third line star frame described flower drum shell restriction single direction is rotated.
3. motor speed varying according to claim 1 mechanism is characterized in that described power intake is a direct current electric notor, and first one-way clutch of the described collar and described second one-way clutch be equidirectional ratchet or ratchet one of them.
4. motor speed varying according to claim 2 mechanism, it is characterized in that, more comprise an electric control clutch, described electric control clutch is and described power intake synchronous operation, whether control described the 3rd outer ring gear of described the third line star gear train fixes, and described electric control clutch is a normal-open electromagnetic valve, imports a predetermined current and makes described electromagnetically operated valve produce axial displacement, and then described the 3rd outer ring gear of described the third line star gear train is fixed.
5. motor speed varying according to claim 2 mechanism, it is characterized in that, described power intake is the motor of an inner rotator type, be to be positioned within the described flower drum shell and to be fixed on the central shaft, described power intake more comprises: a motor body, a driven wheel and a driven gear; Wherein, the described clutch end of described driven gear and described first, second, third central gear and the described collar is articulated in respectively on the described central shaft, and described motor body and described driven wheel are to be concentric to link, and then drive the described driven gear that described driven wheel meshes, and the described first central gear concentric of described driven gear and described first planetary gearsets links, the power that makes described motor body export transfers to described the third line star gear indirectly, turns round to drive described flower drum shell.
6. motor speed varying according to claim 2 mechanism, it is characterized in that, described power intake is the motor of an external rotor type, be to be positioned within the described flower drum shell and to be articulated in respectively on the central shaft with the described clutch end of described first, second, third central gear and the described collar, the described first central gear concentric of described power intake and described first planetary gearsets is linked, the power that makes described power intake export transfers to described the third line star gear indirectly, turns round to drive described flower drum shell.
7. a motor speed varying mechanism is characterized in that, is to carry out transmission by a power intake, and it includes:
One first planetary gearsets, it comprises: one first central gear, a plurality of first planetary gear, one first planet carrier and one first outer ring gear; Wherein, described power intake is to be connected with described first outer ring gear;
One second planetary gearsets, it comprises: a secondary sun wheel, a plurality of second planetary gear, one second planet carrier and one second outer ring gear; Wherein, described first central gear is connected with transferring power with described second outer ring gear; And
One collar is the periphery that cover invests described first and second planetary gearsets, and it comprises: one first one-way clutch, one second one-way clutch and a clutch end;
Wherein, one first clutch-plate that described first one-way clutch is with described first central gear rotates synchronously is meshed, and described second one-way clutch then is meshed with one second clutch-plate that described secondary sun wheel rotates synchronously, and described first and second one-way clutch is equidirectional one-way clutch; In addition, described clutch end is connected in the collar with outputting power.
8. motor speed varying according to claim 7 mechanism, it is characterized in that, it more includes: the third line star gear train is to comprise: one the 3rd central gear, a plurality of the third line star gear, the third line star frame, one the 3rd outer ring gear and one the 3rd one-way clutch; Wherein, described the 3rd central gear is to link with described clutch end, and a plurality of the third line star gears are contacted by described the third line star frame, and kinetic energy is output in a flower drum shell, and describedly utilize described the 3rd one-way clutch to control described the third line star frame described flower drum shell restriction single direction is rotated.
9. motor speed varying according to claim 7 mechanism is characterized in that described power intake is a direct current electric notor, and described first one-way clutch of the described collar and described second one-way clutch be equidirectional ratchet or ratchet one of them.
10. motor speed varying according to claim 8 mechanism, it is characterized in that, more comprise an electric control clutch, described electric control clutch is and described power intake synchronous operation, whether control described the 3rd outer ring gear of described the third line star gear train fixes, and described electric control clutch is a normal-open electromagnetic valve, imports a predetermined current and makes described electromagnetically operated valve produce axial displacement, and then described the 3rd outer ring gear of described the third line star gear train is fixed.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910163673.8A CN101997361B (en) | 2009-08-10 | 2009-08-10 | Motor speed change mechanism |
| US12/788,287 US8622865B2 (en) | 2009-05-27 | 2010-05-26 | Speed change mechanism |
| EP10275055.1A EP2256368B1 (en) | 2009-05-27 | 2010-05-26 | Speed change mechanism |
| US12/842,890 US8226517B2 (en) | 2009-08-10 | 2010-07-23 | Speed change mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910163673.8A CN101997361B (en) | 2009-08-10 | 2009-08-10 | Motor speed change mechanism |
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| CN101997361A true CN101997361A (en) | 2011-03-30 |
| CN101997361B CN101997361B (en) | 2014-05-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910163673.8A Expired - Fee Related CN101997361B (en) | 2009-05-27 | 2009-08-10 | Motor speed change mechanism |
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| CN (1) | CN101997361B (en) |
Cited By (7)
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| CN102878257A (en) * | 2012-08-31 | 2013-01-16 | 王榕生 | Basic driver for three-planetary-gear transmission |
| CN102951251A (en) * | 2011-08-09 | 2013-03-06 | Lg伊诺特有限公司 | Transmission and traction motor module using the same |
| WO2016011921A1 (en) * | 2014-07-21 | 2016-01-28 | 严振华 | Reduction ratio variable hub motor for electric bicycle |
| CN107559387A (en) * | 2016-07-01 | 2018-01-09 | 行安机电股份有限公司 | motor reducer |
| CN109606736A (en) * | 2018-12-06 | 2019-04-12 | 哈尔滨工业大学 | A kind of single-motor double swing rod swing mechanism, celestial body vehicle and moving method |
| CN109606735A (en) * | 2018-12-06 | 2019-04-12 | 哈尔滨工业大学 | A kind of single-motor double swing rod swing mechanism, celestial body vehicle and moving method |
| CN110864004A (en) * | 2019-11-29 | 2020-03-06 | 郑州财经学院 | Case fan control device |
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| TW202321104A (en) * | 2021-11-16 | 2023-06-01 | 姚立和 | Two-stage speed-variable output device and an electric vehicle using it |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102951251A (en) * | 2011-08-09 | 2013-03-06 | Lg伊诺特有限公司 | Transmission and traction motor module using the same |
| CN102951251B (en) * | 2011-08-09 | 2016-11-02 | Lg伊诺特有限公司 | Actuating device and use the traction electric machine module of this actuating device |
| CN102878257A (en) * | 2012-08-31 | 2013-01-16 | 王榕生 | Basic driver for three-planetary-gear transmission |
| CN102878257B (en) * | 2012-08-31 | 2015-05-06 | 王榕生 | Three-planetary-gear transmission |
| WO2016011921A1 (en) * | 2014-07-21 | 2016-01-28 | 严振华 | Reduction ratio variable hub motor for electric bicycle |
| CN107559387A (en) * | 2016-07-01 | 2018-01-09 | 行安机电股份有限公司 | motor reducer |
| CN107559387B (en) * | 2016-07-01 | 2020-09-01 | 行安机电股份有限公司 | Motor speed reducer |
| CN109606736A (en) * | 2018-12-06 | 2019-04-12 | 哈尔滨工业大学 | A kind of single-motor double swing rod swing mechanism, celestial body vehicle and moving method |
| CN109606735A (en) * | 2018-12-06 | 2019-04-12 | 哈尔滨工业大学 | A kind of single-motor double swing rod swing mechanism, celestial body vehicle and moving method |
| CN110864004A (en) * | 2019-11-29 | 2020-03-06 | 郑州财经学院 | Case fan control device |
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| CN101997361B (en) | 2014-05-14 |
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