CN213117326U - Constant-power variable-speed output transmission mechanism with coaxial input and output and same steering direction - Google Patents
Constant-power variable-speed output transmission mechanism with coaxial input and output and same steering direction Download PDFInfo
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- CN213117326U CN213117326U CN202021892258.4U CN202021892258U CN213117326U CN 213117326 U CN213117326 U CN 213117326U CN 202021892258 U CN202021892258 U CN 202021892258U CN 213117326 U CN213117326 U CN 213117326U
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Abstract
An input/output coaxial constant-power variable-speed output transmission mechanism with the same rotation direction belongs to the technical field of mechanical transmission, wherein an input/output central wheel is in an external meshing state, the diameter of the input central wheel is smaller than that of the output central wheel, a meshing point B is positioned between a meshing point A and a planetary wheel shaft center O, when a planetary wheel does not revolve, the rotating speed ratio of an input shaft to an output shaft is smaller than 1, and no matter an input end changes input power due to rotating speed change, torque change or simultaneous change of rotating speed and torque, the transmission mechanism can automatically find a power point on an output end load characteristic curve, which is equal to the input power of the input end, automatically adjust the rotating speed and the torque corresponding to the output rotating speed and the torque to the power, and realize mechanical stepless speed change. The utility model is suitable for an output load moment of torsion rises along with the rotational speed, and the operating mode that descends along with the rotational speed descends, whole mechanism is gear drive, simple structure, the stable performance, and transmission power is big, low in manufacturing cost, easily popularization.
Description
Technical Field
The utility model belongs to the technical field of mechanical transmission, a coaxial and the same infinitely variable transmission mechanism that turns to of input output shaft is related to, specific saying so relates to a coaxial and the variable transmission mechanism who realizes the output according to load rotational speed-torque characteristic automatically regulated output rotational speed and moment of torsion of input output shaft when the input inputs with different power input.
Background
The existing mechanical stepless speed change transmission device needs additional adjusting devices besides a power input source to adjust and control the output rotating speed and torque, and the additional adjusting devices can lose part of energy and reduce the transmission efficiency. The additional regulating device artificially regulates the rotating speed-torque characteristic output by the speed changing device, so that the rotating speed-torque characteristic output by the speed changing device cannot completely meet the rotating speed-torque requirement of a load, and the overall efficiency is reduced. The additional adjusting device can increase the complexity and the manufacturing precision of the whole transmission device, and is not suitable for relatively high-power stepless speed change transmission.
At present, under the working conditions that the load torque is increased along with the increase of the rotating speed and is reduced along with the reduction of the rotating speed, when the power of an input end is changed, the output rotating speed cannot be automatically adjusted according to the rotating speed-torque characteristic of the load at the output end, and the constant-power stepless speed change output cannot be realized.
SUMMERY OF THE UTILITY MODEL
The utility model aims at having the infinitely variable transmission now and can not be according to load rotational speed-torque characteristic automatically regulated output rotational speed, can't realize the not enough of constant power infinitely variable output, it is coaxial and turn to the same constant power variable output drive mechanism to provide an input/output, only through gear drive, need not additionally increase speed adjusting device, moreover, the steam generator is simple in structure, under the input power variation circumstances, the automatically regulated of self-adaptation load rotational speed-torque characteristic can be made to output rotational speed and moment of torsion, the transmission performance is stable, realization mechanical infinitely variable speed that can be convenient.
The technical scheme of the utility model: an equal-power variable-speed output transmission mechanism with coaxial input and output and same steering direction comprises a left side frame, a middle frame and a right side frame; the method is characterized in that: the transmission mechanism is also composed of an input shaft, an input wheel center wheel, an input idle wheel, an input planet wheel, an output idle wheel, an output center wheel, an output shaft, a planet carrier shaft, a planet carrier bearing, a planet wheel bearing, an input idle wheel bearing and an output idle wheel bearing; the input shaft is rotationally connected in the left side frame, the planet carrier shaft is rotationally connected in the middle frame, the output shaft is rotationally connected in the right side frame, the input shaft, the planet carrier shaft and the output shaft are arranged on the same axis, the planet carrier is rotationally connected with the planet carrier shaft through planet carrier bearings, the planet carrier bearings are uniformly distributed on the circumference of the planet carrier, the input shaft is fixedly connected with the input central wheel, the input central wheel and the input idle wheel form external meshing transmission connection, the input idle wheel and the input planet wheel form external meshing transmission connection, the center of the input idle wheel is connected with an input idle wheel bearing, an input idle wheel shaft is arranged in the input idle wheel bearing, the input idle wheel shaft is fixedly connected with the planet carrier, and the output shaft is fixedly connected with the output central wheel, the planetary gear mechanism comprises an output idler wheel, an output central wheel, an output idler wheel bearing, a planetary wheel shaft, a planetary gear shaft, an input planetary wheel, an output idler wheel shaft, a planetary carrier, a planetary wheel bearing, a planetary wheel shaft, an input planetary wheel, an output idler wheel and a planetary carrier, wherein the output central wheel and the output idler wheel form external engagement transmission connection, the output idler wheel bearing is connected and arranged at the center of the output idler wheel, the output idler wheel shaft is arranged in the output idler wheel bearing, one end of the planetary wheel shaft is connected and fixed with the input planetary wheel, the other end of the planetary wheel shaft is connected and fixed with the output planetary wheel, the.
The input idler, the input planet wheel, the output planet wheel and the output idler are not less than 2 groups.
The input central wheel and the output central wheel which are connected in an external meshing transmission way can be replaced by an input gear ring and an output gear ring which are connected in an internal meshing transmission way.
The diameter of the input central wheel is smaller than that of the output central wheel in an external meshing state; the diameter of the input center wheel is larger than that of the output center wheel in an inner meshing state.
The input planet wheel and the output planet wheel are coaxial and have the same speed.
The vertical distance L between the center O point of the output planet wheel and the axis of the planet carrieroIs greater than the vertical distance L between the meshing point B of the output idle wheel and the output central wheel and the planet carrier shaftbAnd the vertical distance L between the meshing point B of the output idle wheel and the output central wheel and the planet carrier shaftbIs greater than the vertical distance L between the meshing point A of the input central wheel and the input idle wheel and the input shaftaI.e. Lo＞Lb＞La。
The utility model has the advantages that: the utility model provides a coaxial isopower variable speed output drive mechanism that just turns to the same of input/output, its input shaft is the same with turning to of output shaft, input planet wheel and output planet wheel are coaxial with fast, under input centre wheel is the external gearing state, meshing point B is in between meshing point A and the planet wheel axle center O, when the planet wheel does not revolve round, the input shaft is less than 1 with the rotational speed ratio of output shaft, the input no matter is the rotational speed change, the moment of torsion changes or rotational speed, the moment of torsion changes simultaneously and leads to the input power to change, the utility model discloses drive mechanism can find automatically that power point that equals with input power on the output load characteristic curve, and automatically regulated output rotational speed, the moment of torsion is to the corresponding rotational speed and the moment of torsion of that power, realize mechanical infinitely variable speed. The utility model discloses the device is applicable to output load moment of torsion and rises along with the rotational speed rises, and the operating mode that descends along with the rotational speed descends, and whole drive mechanism is gear drive, simple structure, the stable performance, and transmission power is big, and the range of application is wide, low in manufacturing cost, easily popularization.
Drawings
Fig. 1 is a schematic diagram of the external engagement state structure of the input/output center wheel of the present invention.
Fig. 2 is a schematic diagram of the distribution of each meshing point in the external meshing state of the present invention.
Fig. 3 is a schematic view of the structure in the direction a in fig. 2.
Fig. 4 is a schematic view of the acting force of each engagement point in the external engagement state of the present invention.
Fig. 5 is a schematic diagram of the structure of the present invention showing the inner engagement state of the input/output center wheel.
Fig. 6 is a schematic view of the structure in direction B in fig. 5.
Fig. 7 is a schematic view of the acting force of each engagement point in the internal engagement state of the present invention.
In the figure: the planetary gear set comprises an input shaft 1, an input central gear 2, an input idle gear 3, an input idle gear shaft 4, an input planetary gear 5, an output planetary gear 6, a planetary gear shaft 7, an output idle gear 8, an output idle gear shaft 9, an output central gear 10, an output shaft 11, a planetary carrier 12, a planetary carrier shaft 13, a planetary carrier bearing 14, a planetary gear bearing 15, an input idle gear bearing 16, an output idle gear bearing 17, a left side frame 18, a middle frame 19 and a right side frame 20.
Detailed Description
The invention will be further explained with reference to the following figures and examples:
example 1:
as shown in fig. 1-4, the input central wheel and the output central wheel are externally engaged, the input shaft 1 is fixedly connected with the input central wheel 2, the output shaft 11 is fixedly connected with the output central wheel 10, and the axes of the input shaft 1, the output shaft 11 and the planet carrier 12 are on the same straight line. The input planet wheel 5 and the output planet wheel 6 are fixedly connected at two ends of a planet wheel shaft 7. The planetary gear shaft 7 passes through the carrier 12 between the input planetary gear 5 and the output planetary gear 6, is connected to the carrier 12 via a planetary gear bearing 15, and is freely rotatable. Input sun gear 2 meshes with input idler 3, input planet gear 3 meshes with input planet gear 5, output planet gear 6 meshes with output idler 8, and output idler 8 meshes with output sun gear 10. The input idle gear shaft 4 is fixedly connected with the planet carrier 12 and is connected with the input idle gear 3 through an idle gear shaft bearing 16; the output idle gear shaft 9 is fixedly connected with the planet carrier 12 and is connected with the output idle gear 8 through an idle gear shaft bearing 17; input idler 3 and output idler 8 are free to rotate. The carrier 12 is connected to the carrier shaft 13 by a carrier bearing 14, and the carrier 12 is freely rotatable about the carrier shaft 13. The input planet wheel 5, the output planet wheel 6, the input idler wheel 3 and the output idler wheel 8 rotate; the input planetary gear 5, the output planetary gear 6, the input idler 3, the output idler 8, and the carrier 12 revolve as a whole around a carrier shaft 13.
As shown in FIGS. 1-4, the input center wheel diameter D in this exampleIntoSmaller than the diameter D of the output central wheelGo out. The vertical distance L between the central point O of the planet wheel shaft 7 and the planet carrier shaft 13oIs greater than the vertical distance L between the meshing point B of the output central wheel 10 and the output idle wheel 8 and the planet carrier shaft 13bThe vertical distance L between the meshing point B of the output central wheel 10 and the output idle wheel 8 and the planet carrier shaft 13bIs greater than the vertical distance L between the meshing point A of the input central wheel 2 and the input idle wheel 3 and the planet carrier shaft 13aI.e. Lo＞Lb＞LaI.e. with respect to the perpendicular distance from the planet carrier shaft 13, point B lies between points a and O.
As shown in fig. 1-4, the input shaft 1 and the output shaft 11 of the present embodiment are rotated in the same direction. An input idler 3 is arranged between the input central wheel 2 and the input planet wheel 5, and an output idler 8 is arranged between the output planet wheel 6 and the output central wheel 10 to ensure that the speed ratio of the input shaft 1 and the output shaft 11 is less than 1 under the condition that the planet wheels do not revolve. The present embodiment is directed to the fact that the load torque and the resistance at the output end increase with the increase of the load rotation speed and decrease with the decrease of the load rotation speed.
As shown in fig. 1 to 4, in the present embodiment, at the initial stage of start, the rotation speed of the input sun gear 2 increases, and the rotation speed of the output sun gear 10 increases by the rotation of the planetary gear without external resistance, and the planetary gear shaft 7 does not revolve because of no external torque. Resistance F generated by load as the rotation speed of the output center wheel 10 increasesZAnd passed to point a. If the input shaft 1 rotates in the forward direction and the rotation speed is N, the output shaft 11 rotates in the same direction and the rotation speed is N/i. At the point a of the process, the first,driving force F transmitted from input shaft 1QResistance F in the immediate vicinity of load transferZMaking a comparison if FQGreater than FZThen a value equal to (F) is generated at point AQ-FZ) The forward acting force can generate lever action on the point O by taking the point B as a fulcrum, and the planetary wheel shaft 7 is pried to carry out reverse revolution acceleration. Suppose that the reverse revolution acceleration of the planetary wheel shaft 7 is-NPublicThen the output shaft 11 will increase the forward rotation speed (-N)Public+NPublicI), the output shaft 11 is accelerated in the forward direction because i is smaller than 1. As the rotational speed of the output shaft 11 increases, FZIt will increase. The planetary wheel shaft 7 revolves reversely and accelerates, and at the same time, the relative rotation speed of the input sun gear 2 at the meshing point a is increased, and at the same power, the increase of the relative rotation speed of the input sun gear 2 causes the torque of the input sun gear 2 to be reduced, namely, the torque F is reducedQWith FZContinuously rising and FQConstantly decreasing, FZAnd FQThe difference between the outputs is continuously reduced until the two are equal, at this time, the planetary wheel shaft 7 revolves reversely and is not accelerated any more, the forward rotating speed of the output shaft 11 is not increased any more, and the device of the embodiment is in a stable state. At point A, if FQLess than FZAnd vice versa. At this time, the input power at the input end is equal to the output power without considering the friction loss during the transmission, i.e., (N)Into×QInto=NGo out×QGo out) In the formula, NIntoFor input of rotational speed, QIntoFor input torque, NGo outTo output rotational speed, QGo outIs the output torque.
As shown in fig. 1 to 4, after the apparatus of the present embodiment enters the steady state, the first variation: if the input rotation speed of the input shaft 1 increases, the input torque is not changed, and the initial factor A of acceleration is at the point FQ、FZAnd the balance state is realized, the lever acting force is not generated at the point O, and the planetary wheel shaft 7 does not revolve. The rotation speed of the input shaft 1 is increased and is directly transmitted to the output shaft 11 through the rotation of the planet wheel, so that the positive rotation speed of the output shaft 11 is increased; as the forward rotational speed of the output shaft 11 increases, the load resistance increases and is transmitted to point a, causing point FZGreater than FQSo that A generates a reverse force, taking point B as a pointAnd the supporting point prizes the central O point of the planetary wheel shaft 7 to accelerate the positive revolution. Assuming that the forward revolution of the planetary gear shaft 7 is accelerated to NPublicThen the output shaft 11 will reduce the forward rotation speed (N)Public-NPublicI), the output shaft 11 is decelerated in the forward direction because i is smaller than 1. The positive revolution acceleration of the planetary wheel shaft 7 weakens the positive acceleration of the output shaft 11, and simultaneously reduces the relative rotation speed of the input shaft 2 at the point A, and under the same power, the reduction of the relative rotation speed of the input sun gear 2 can cause the torque of the input sun gear 2 to increase, namely, increase FQ. When F is presentQIncreased value of and FZThe increase values are equal, the device of the embodiment enters a new balanced state, the forward revolution of the planetary wheel shaft is not accelerated any more, and the forward rotating speed of the output shaft 9 is not increased any more. If the input speed of the input shaft 1 is reduced, the input torque is unchanged, and vice versa. At this time, the input power at the input end is equal to the output power without considering the friction loss during the transmission, i.e., (N)Into×QInto=NGo out×QGo out). This state is suitable for the working conditions of constant torque and variable rotating speed of the input end.
As shown in fig. 1 to 4, after the apparatus of the present embodiment enters the steady state, the second variation: if the input rotation speed of the input shaft 1 is not changed, the input torque is increased, and the increase of the input torque directly increases F of the point AQLet F stand forQGreater than FZAt point A, a value equal to (F) is generatedQ-FZ) The positive acting force can generate lever action on the point O by taking the point B as a fulcrum, the planetary wheel shaft 7 is pried to carry out reverse revolution acceleration, and the reverse revolution acceleration of the planetary wheel shaft 7 is assumed to be-NPublicThen the output shaft 11 will increase the forward rotation speed (-N)Public+NPublicI) because i is less than 1, the output shaft 11 accelerates. As the rotational speed of the output shaft 11 increases, FZIt will increase. The planetary wheel shaft 7 revolves reversely and accelerates, and at the same time, the relative rotation speed of the input sun gear 2 at the meshing point a is increased, and at the same power, the increase of the relative rotation speed of the input sun gear 2 causes the torque of the input sun gear 2 to be reduced, namely, the torque F is reducedQ. With FZContinuously rising and FQConstantly decreasing, FZAnd FQThe difference between the outputs will be reduced continuously until the two are equal, the planet wheelThe shaft 7 does not accelerate any more in the reverse revolution, the rotating speed of the output shaft 11 does not increase any more, and the device of the embodiment is in a new stable state. If the input speed of the input shaft 1 is unchanged, the input torque is reduced, and vice versa. At this time, the input power at the input end is equal to the output power without considering the friction loss during the transmission, i.e., (N)Into×QInto=NGo out×QGo out). This state is suitable for the working conditions of variable torque and constant rotating speed of the input end.
As shown in fig. 1 to 4, after the apparatus of the present embodiment enters the steady state, the third variation: if the input rotation speed and the torque of the input shaft 1 are simultaneously increased, the rotation speed of the output shaft 1 is increased, so that the forward rotation speed and the load resistance of the output shaft 11 are increased, namely, the point F is the point AZIncreasing, the input torque increases to result in point A, FQIncrease when FZIs increased by less than FQWhen the rotational speed of the output shaft 11 is increased, the planetary gear shaft 7 is accelerated in the reverse revolution, and the rotational speed of the output shaft 11 is increased to cause the point A FZFurther increasing. Meanwhile, the planet shaft 7 revolves reversely and accelerates, the relative rotating speed of the input central wheel 2 at the meshing point A is increased, and the increase of the relative rotating speed of the input central wheel 2 can cause F under the same powerQAnd decreases. With FZContinuously rising and FQConstantly decreasing, FZAnd FQThe difference between the outputs is continuously reduced until the two are equal, the planetary wheel shaft 7 does not accelerate any more in the reverse revolution, the rotating speed of the output shaft 11 does not increase any more, and the device of the embodiment is in a new stable state. If the input speed and the input torque of the input shaft 1 are reduced simultaneously, and vice versa. At this time, the input power at the input end is equal to the output power without considering the friction loss during the transmission, i.e., (N)Into×QInto=NGo out×QGo out). The state is suitable for the working condition that the torque and the rotating speed of the input end change simultaneously.
As shown in fig. 1 to 4, after the apparatus of the present embodiment enters the steady state, a fourth variation: if the load torque increases, i.e. the resistance increases, the increased resistance is transmitted to point A, causing point A to be FZGreater than FQ。Therefore, the A generates a reverse force, and the point O of the planetary wheel shaft is pried to revolve and accelerate by taking the point B as a fulcrum. Suppose a planet wheelThe positive revolution of the shaft 7 is accelerated to NPublicThen the output shaft 11 reduces the forward rotation speed (N)Public-NPublicI), the output shaft 11 is decelerated in the forward direction because i is smaller than 1. The acceleration of the planetary gear shaft positive revolution reduces the relative rotation speed of the input sun gear 2 at the point a while reducing the positive rotation speed of the output shaft 11, thereby increasing the torque of the input shaft 2, that is, increasing FQ. When F is presentQIncrease of (a) and FZThe increment values of the two planetary gear sets are equal, the planetary gear shaft does not accelerate any more in positive revolution, the positive rotating speed of the output shaft 11 is not reduced any more, and the device of the embodiment enters a new balanced state. If the load torque and drag are reduced, and vice versa. At this time, the input power at the input end is equal to the output power without considering the friction loss during the transmission, i.e., (N)Into×QInto=NGo out×QGo out). The state is suitable for the working condition that the torque of the output end is actively changed, namely the load rotating speed-torque characteristic curve of the output end is changed.
Example 2:
as shown in FIGS. 5-7, the input center wheel and the output center wheel of the device of the present embodiment are inner-meshing ring gears, and the distance between the meshing point A of the input center ring gear and the input idle gear, the meshing point B of the output center ring gear and the output idle gear, and the central point O of the planetary shaft and the shaft of the planet carrier is La、Lb、LoThe relationship is La>Lb>Lo. The other steps are the same as those of the embodiment 1, the device of the embodiment can automatically find a power point which is equal to the input end power on a load speed-torque characteristic curve, and automatically adjust the corresponding rotating speed and torque; the input end rotating speed and the input torque can be combined at random at the corresponding input power; the input end can be variable-speed and variable-torque input, variable-speed and constant-torque input, and constant-speed and constant-torque input; the stepless speed change output does not need an additional adjusting device, and the output rotating speed and the torque of the output end are automatically adjusted according to the self-adaptive load rotating speed-torque characteristic; the device of the embodiment has the advantages that the energy loss of the additional adjusting device is avoided, the transmission efficiency is high, and if the friction loss in the transmission process is not considered, the device can be regarded as equal-power transmission with the input power equal to the output power.
Claims (6)
1. An equal-power variable-speed output transmission mechanism with coaxial input and output and same steering direction comprises a left side frame (18), a middle frame (19) and a right side frame (20); the method is characterized in that: the transmission mechanism is also composed of an input shaft (1), an input central wheel (2), an input idle wheel (3), an input planetary wheel (5), an output planetary wheel (6), an output idle wheel (8), an output central wheel (10), an output shaft (11), a planetary carrier (12), a planetary carrier shaft (13), a planetary carrier bearing (14), a planetary wheel bearing (15), an input idle wheel bearing (16) and an output idle wheel bearing (17); the input shaft (1) is rotationally connected in the left side rack (18), the planet carrier shaft (13) is rotationally connected in the middle rack (19), the output shaft (11) is rotationally connected in the right side rack (20), the input shaft (1), the planet carrier shaft (13) and the output shaft (11) are arranged on the same axis, the planet carrier (12) is rotationally connected with the planet carrier shaft (13) through a planet carrier bearing (14), the planet wheel bearings (15) are uniformly distributed on the circumferential direction of the planet carrier (12), the input shaft (1) is fixedly connected with the input central wheel (2), the input central wheel (2) is in external meshing transmission connection with the input idle wheel (3), the input idle wheel (3) is in external meshing transmission connection with the input planet wheel (5), the center of the input idle wheel (3) is connected with an input idle wheel bearing (16), an input idler shaft (4) is arranged in the input idler bearing (16), the input idler shaft (4) is fixedly connected with the planet carrier (12), the output shaft (11) is fixedly connected with the output central wheel (10), the output central wheel (10) is in external-meshing transmission connection with the output idler wheel (8), an output idler bearing (17) is arranged in the center of the output idler wheel (8), an output idler shaft (9) is arranged in the output idler bearing (17), the output idler shaft (9) is fixedly connected with the planet carrier (12), the output idler wheel (8) is in external-meshing transmission connection with the output planet wheel (6), a planet wheel shaft (7) is connected inside the planet wheel bearing (15), one end of the planet wheel shaft (7) is fixedly connected with the input planet wheel (5), and the other end of the planet wheel shaft (7) is fixedly connected with the output planet wheel (6), the planetary gear set comprises an input planetary gear (5), an output planetary gear (6), an input idler gear (3) and an output idler gear (8) which rotate, wherein the input planetary gear (5), the output planetary gear (6), the input idler gear (3), the output idler gear (8) and a planet carrier (12) revolve around a planet carrier shaft (13) as a whole.
2. An input-output coaxial constant-power variable-speed output transmission mechanism with the same direction of rotation as the input-output coaxial constant-power variable-speed output transmission mechanism according to claim 1, wherein: the number of the input idler (3), the number of the input planet wheels (5), the number of the output planet wheels (6) and the number of the output idler (8) are not less than 2.
3. An input-output coaxial constant-power variable-speed output transmission mechanism with the same direction of rotation as the input-output coaxial constant-power variable-speed output transmission mechanism according to claim 1, wherein: the input central wheel (2) and the output central wheel (10) which are connected in an external meshing transmission way can be replaced by an input gear ring and an output gear ring which are connected in an internal meshing transmission way.
4. An input-output coaxial constant-power variable-speed output transmission mechanism with the same direction of rotation as the input-output coaxial constant-power variable-speed output transmission mechanism according to claim 1, wherein: the diameter of the input central wheel (2) is smaller than that of the output central wheel (10) in an external meshing state; the diameter of the input center wheel (2) is larger than that of the output center wheel (10) in an inner meshing state.
5. An input-output coaxial constant-power variable-speed output transmission mechanism with the same direction of rotation as the input-output coaxial constant-power variable-speed output transmission mechanism according to claim 1, wherein: the input planetary gear (5) and the output planetary gear (6) are coaxial and have the same speed.
6. An input-output coaxial constant-power variable-speed output transmission mechanism with the same direction of rotation as the input-output coaxial constant-power variable-speed output transmission mechanism according to claim 1, wherein: the vertical distance L between the center O point of the output planet wheel (6) and the planet carrier shaft (13)oIs greater than the vertical distance L between the meshing point B of the output idle wheel (8) and the output central wheel (10) and the planet carrier shaft (13)bThe vertical distance L between the meshing point B of the output idle wheel (8) and the output central wheel (10) and the planet carrier shaft (13)bIs larger than the input central wheel (2)) The vertical distance L between the meshing point A of the input idle wheel (3) and the input shaft (1)aI.e. Lo＞Lb＞La。
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021892258.4U CN213117326U (en) | 2020-09-02 | 2020-09-02 | Constant-power variable-speed output transmission mechanism with coaxial input and output and same steering direction |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202021892258.4U CN213117326U (en) | 2020-09-02 | 2020-09-02 | Constant-power variable-speed output transmission mechanism with coaxial input and output and same steering direction |
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| CN213117326U true CN213117326U (en) | 2021-05-04 |
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| CN (1) | CN213117326U (en) |
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