CN111853180A - Input-output coaxial variable-speed transmission mechanism with opposite rotation directions - Google Patents

Input-output coaxial variable-speed transmission mechanism with opposite rotation directions Download PDF

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CN111853180A
CN111853180A CN202010907121.XA CN202010907121A CN111853180A CN 111853180 A CN111853180 A CN 111853180A CN 202010907121 A CN202010907121 A CN 202010907121A CN 111853180 A CN111853180 A CN 111853180A
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input
wheel
output
shaft
planet
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董永岗
华娟
王劲
周力
董俊
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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
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/58—Gearings having only two central gears, connected by orbital gears with sets of orbital gears, each consisting of two or more intermeshing orbital gears
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Friction Gearing (AREA)

Abstract

A speed change transmission mechanism with coaxial input and output shafts and opposite rotation directions belongs to the technical field of mechanical transmission, and is suitable for the working conditions that load torque rises along with the rise of rotating speed and falls along with the fall of the rotating speed. The invention makes the input central wheel/gear ring wheel and the output central wheel/gear ring wheel rotate reversely through the idle wheel, the input planet wheel and the output planet wheel are coaxial and at the same speed, on the vertical distance from the rotating central shaft of the planet carrier, the meshing point B is positioned between the input meshing point A and the axis center O point of the planet wheel, when the rotating speed, the torque or the torque of the output end of the input end changes, the acting force on the point A changes, the point A takes the point B as a fulcrum to generate lever action on the point O, so that the point O revolves, the rotating speed of the output central wheel is adjusted, the rotating speed and the torque of the output end are automatically adjusted by the output end according to the load rotating speed-torque characteristics of the output end when different powers are input at the input end.

Description

Input-output coaxial variable-speed transmission mechanism with opposite rotation directions
Technical Field
The invention belongs to the technical field of mechanical transmission, relates to a speed change transmission mechanism with coaxial input and output shafts and opposite rotation directions, and particularly relates to a speed change transmission mechanism with coaxial input and output shafts and capable of realizing automatic regulation of output rotation speed of an output end according to load rotation speed-torque characteristics when input ends input with different powers.
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.
Disclosure of Invention
The invention aims to provide a variable speed transmission mechanism with coaxial input and output and opposite rotation directions, aiming at the defects that the existing continuously variable transmission cannot automatically adjust the rotation speed of an output end according to the load rotation speed-torque characteristic and cannot realize constant-power continuously variable output, and the variable speed transmission mechanism has a simple structure, can automatically adjust the rotation speed and the torque of the output end in a self-adaptive manner according to the load rotation speed-torque characteristic under the condition of the power change of an input end, has stable transmission performance and can conveniently realize mechanical continuously variable transmission by only adopting gear transmission without additionally adding a speed adjusting device.
The technical scheme of the invention is as follows: a variable speed transmission mechanism with coaxial input and output and opposite rotation directions comprises a left side frame, a middle frame and a right side frame; the method is characterized in that: the transmission mechanism also comprises an input shaft, an input wheel central wheel, an input planet wheel, an output planet wheel, a planet wheel shaft, an idle wheel shaft, an output central wheel, an output shaft, a planet carrier shaft, a planet carrier bearing, a planet bearing and an idle wheel bearing; the input shaft is rotationally connected in the left side machine frame, the planet carrier shaft is rotationally connected in the middle machine frame, the output shaft is rotationally connected in the right side machine frame, the input shaft, the output shaft and the planet carrier shaft are arranged on the same axis, the input shaft is fixedly connected with the input central wheel, the input central wheel and the input planet wheel form an external engagement transmission connection, the output shaft is fixedly connected with the output central wheel, the output central wheel and the idle wheel form an external engagement transmission connection, the idle wheel and the output planet wheel form an external engagement transmission connection, the planet carrier is rotationally connected with the planet carrier shaft through a planet carrier bearing, the planet bearings are uniformly distributed and arranged in the circumferential direction of the planet carrier, the planet carrier shaft passes through the planet bearing, and one end of the planet carrier shaft is fixedly connected with the input planet wheel, the other end of the planetary gear is fixedly connected with the output planetary gear, the input planetary gear, the output planetary gear and the idler rotate, and the input planetary gear, the output planetary gear, the idler and the planet carrier as a whole revolve around the axis of the planet carrier.
At least 2 groups of input planet wheels are meshed and connected with the input central wheel; the output planetary gears are not less than 2 groups and are in meshed connection with the output central gear through idle gears.
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 internally meshed.
The input shaft and the output shaft are opposite in rotation direction under the action of an idler wheel, the idler wheel is arranged on one side of the input planetary gear set or one side of the output planetary gear set, one end of the idler wheel shaft is fixedly connected with the planet carrier, and the other end of the idler wheel shaft is movably connected with the idler wheel bearing.
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 planet wheel shaft and the planet carrier shaftoIs larger than the distance between the meshing point B of the output central wheel and the idle wheel and the planet carrier shaftIs a vertical distance LbThe vertical distance L between the meshing point B of the output central wheel and the idle 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 planet wheel and the input shafta。
The invention is suitable for the working conditions that the load torque and the resistance of the output end increase along with the increase of the load rotating speed and decrease along with the decrease of the load rotating speed.
The invention has the beneficial effects that: the invention provides a variable speed transmission mechanism with coaxial input and output and opposite rotation directions, wherein an input shaft is fixedly connected with an input central wheel, an output shaft is fixedly connected with an output central wheel, the axes of the input shaft, the output shaft and a planet carrier are on the same straight line, two ends of the planet carrier shaft are respectively and fixedly connected with an input planet wheel and an output planet wheel, the planet carrier penetrates between the two planet wheels and is connected with the planet carrier by a bearing and can rotate freely, the input central wheel is meshed with the input planet wheel, the output planet wheel is meshed with an idle wheel, the idle wheel is meshed with the output sun wheel, the input planet wheel, the output planet wheel and the idle wheel can rotate automatically, the input planet wheel, the output planet wheel, the idle wheel and the planet carrier as a whole can revolve around the axis of the planet carrier, the input planet wheel and the output planet wheel rotate in, in the vertical distance from the rotating central shaft of the planet carrier, the meshing point B is positioned between the input meshing point A and the central point O of the planet wheel shaft, when the rotating speed, the torque or the torque of the output end of the input end changes, the acting force on the point A changes, the point A takes the point B as a fulcrum to generate leverage on the point O, so that the point O generates revolution, the rotating speed of the output central wheel is adjusted, the purpose that the rotating speed and the input torque of the input end can be combined at will when different powers of the input end are input and corresponding input powers are output is achieved, and the rotating speed and the torque of the output end are automatically adjusted according to the load rotating speed-torque characteristics of the output end, so that the constant-.
Drawings
Fig. 1 is a schematic view of the overall structure of the present invention.
FIG. 2 is a schematic diagram showing the distribution of the meshing points according to the present invention.
Fig. 3 is a schematic view of the structure in the direction a in fig. 2.
Fig. 4 is a schematic diagram of the force applied at each engagement point in the present invention.
Fig. 5 is a schematic structural diagram of a second embodiment of the present invention.
Fig. 6 is a schematic view of the structure in direction B in fig. 5.
Fig. 7 is a schematic diagram of the acting force of each meshing point in the second embodiment of the invention.
In the figure: the planetary gear set comprises an input shaft 1, an input central gear 2, an input planetary gear 3, an output planetary gear 4, a planetary gear shaft 5, an idle gear 6, an idle gear shaft 7, an output central gear 8, an output shaft 9, a planetary carrier 10, a planetary carrier shaft 11, a planetary carrier bearing 12, a planetary bearing 13, an idle gear bearing 14, a left side frame 15, an intermediate frame 16 and a right side frame 17.
Detailed Description
The invention is further illustrated by the following examples in conjunction with the accompanying drawings:
the first implementation mode comprises the following steps:
as shown in fig. 1, in a speed change transmission mechanism with coaxial input and output and opposite rotation directions, an input shaft 1 is fixedly connected with an input central wheel 2, an output shaft 9 is fixedly connected with an output central wheel 8, and the axes of the input shaft 1, an output shaft 9 and a planet carrier 10 are on the same straight line. The input planet 3 and the output planet 4 are fixedly connected at both ends of a planet axle 5. The planetary gear shaft 5 passes through the planetary carrier 10 between the input planetary gear 3 and the output planetary gear 4, is connected with the planetary carrier 10 through the planetary bearing 13, and can rotate freely. Input sun gear 2 meshes with input planet gears 3, output planet gears 4 mesh with idler gear 6, and idler gear 6 meshes with output sun gear 8. The idler shaft 7 is fixedly connected with the planet carrier 10 and is connected with the idler 6 through an idler bearing 14. Idler 6 is free to rotate. The planet carrier 10 is connected to a planet carrier shaft 11 via a planet carrier bearing 12, the planet carrier 10 being freely rotatable around the planet carrier shaft 11. The input planetary wheel 3, the output planetary wheel 4 and the idler wheel 6 can rotate; the input planetary gear 3, the output planetary gear 4, the idler gear 6, and the planet carrier 10 as a whole can revolve around a carrier shaft 11.
As shown in FIGS. 1 to 4, the center point O of the planetary gear shaft 5 of the present embodiment is at a vertical distance L from the carrier shaft 11oGreater than the output centre wheel 8 andperpendicular distance L of meshing point B of idler 6 from planet carrier shaft 11bThe vertical distance L between the meshing point B of the output central wheel 8 and the idle wheel 6 and the planet carrier shaft 11bIs greater than the vertical distance L between the meshing point A of the input central wheel 2 and the input planet wheel 3 and the planet carrier shaft 11aI.e. Lo＞Lb＞LaI.e. with respect to the perpendicular distance from the planet carrier shaft 11, point B lies between points a and O.
As shown in fig. 1 to 4, in the present embodiment, at the initial stage of start, without external resistance, the rotation speed of the input sun gear 2 increases, and the rotation speed of the output sun gear 8 increases by the rotation of the planetary gear, and the planetary gear shaft 5 does not revolve because of no external torque. Resistance F generated by load as the rotational speed of the output center wheel 8 increasesZAnd passed to point a. If the planetary gear shaft 5 does not revolve, the transmission ratio of the input shaft 1 to the output shaft 9 is i, if the input shaft 1 rotates in the forward direction and the rotating speed is N, the output shaft 9 rotates in the reverse direction and the rotating speed is-N/i; at point A, the driving force F transmitted from the 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 5 is pried to carry out reverse revolution acceleration. Suppose that the reverse revolution acceleration of the planetary wheel shaft 5 is-NPublicThe output shaft 9 will increase the reverse rotation speed (-N)Public-NPublicI), the output shaft 9 is accelerated in reverse. As the rotational speed of the output shaft 9 increases, FZIt will increase. The planetary wheel shaft 5 revolves reversely and accelerates, and simultaneously the relative rotating speed of the input central wheel 2 at the meshing point A is increased, under the same power, the increase of the relative rotating speed of the input central wheel 2 can cause the torque of the input shaft 2 to be reduced, namely, the torque F is reducedQWith FZContinuously rising and FQConstantly decreasing, FZAnd FQThe difference between the outputs will be reduced continuously until the two are equal, at this time, the planetary gear shaft will not accelerate any more in reverse revolution, the reverse rotation speed of the output shaft 9 will not increase any more, and the embodiment is in a stable state. At point A, if FQLess than FZAnd vice versa. At this time, if the transmission process is not consideredFriction loss, input power at input being equal to output power, 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. 1-4, after the present embodiment enters the steady state, the first variation: the input speed of the input shaft 1 is increased, the input torque is not changed, and the point F is at the initial point A of accelerationQ、FZAnd the balance state is realized, the lever acting force is not generated at the point O, and the revolution acceleration and deceleration of the planetary wheel shaft 5 are not generated. The rotation speed of the input shaft 1 is increased and is directly transmitted to the output shaft 9 through the autorotation of the planet wheel, so that the reverse rotation speed of the output shaft 9 is increased; as the reverse rotation speed of the output shaft 9 increases, the load resistance FZWill be added and transmitted to point a, causing point a to be FZGreater than FQTherefore, a reverse force is generated at the point A, and the point B is taken as a fulcrum to pry the central point O of the planetary gear shaft 5 to perform positive revolution and acceleration. Assuming that the forward revolution of the planetary gear shaft 5 is accelerated to NPublicThe output shaft 9 will reduce the reverse rotation speed (N)Public+NPublicI), the output shaft 9 decelerates in the reverse direction. The positive revolution acceleration of the planetary wheel shaft 5 weakens the reverse rotation acceleration of the output shaft, 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 central wheel 2 can cause the torque of the input shaft 2 to increase, namely increase FQ. When F is presentQIncreased value of and FZThe increase values are equal, the embodiment enters a new equilibrium state, the reverse revolution of the planetary wheel shaft is not accelerated any more, and the reverse 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. 1-4, after the embodiment enters the steady state, the second variation: the input rotation speed of the input shaft 1 is unchanged, 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 5 is pried to carry out reverse revolution acceleration, and the reverse revolution acceleration of the planetary wheel shaft 5 is assumed to be-NPublicThe output shaft 9 will increase the reverse rotation speed (-N)Public-NPublicI), the output shaft 9 is accelerated. As the rotational speed of the output shaft 9 increases, FZIt will increase. The planetary wheel shaft 5 revolves reversely and accelerates, and simultaneously the relative rotating speed of the input central wheel 2 at the meshing point A is increased, under the same power, the increase of the relative rotating speed of the input central wheel 2 can cause the torque of the input shaft 2 to be reduced, namely, the torque F is reducedQ. With FZContinuously rising and FQConstantly decreasing, FZAnd FQThe difference between the outputs is continuously reduced until the two are equal, the planetary wheel shaft 5 does not accelerate any more in the reverse revolution, the rotating speed of the output shaft 9 does not increase any more, and 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. 1-4, after the embodiment enters the steady state, the third variation: 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, the reverse rotation speed of the output shaft 9 is increased and the load resistance is increased, namely, a point FZIncreasing, the input torque increases to result in point A, FQIncrease when FZIs increased by less than FQWhen the rotation speed of the planetary gear shaft 5 is increased, the planetary gear shaft 5 is revolved reversely and accelerated, so that the reverse rotation speed of the output shaft 9 is increased, and the reverse rotation speed of the output shaft 9 is increased to cause a point A FZFurther increasing. Meanwhile, the relative rotation speed of the input central wheel 2 at the meshing point A is increased along with the acceleration of the reverse revolution of the planet shaft 5, and the increase of the relative rotation speed of the input central wheel 2 can cause F under the same powerQAnd decreases. With FZContinuously rising and FQConstantly decreasing, FZAnd FQTransporting deviceThe difference between the two values will be reduced continuously until the two values are equal, the planetary wheel shaft 5 will not accelerate again in the reverse revolution, the output shaft 9 will not increase in the reverse rotation speed, and 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. 1-4, after the present embodiment enters the steady state, the fourth variation: the load torque increases, i.e. the resistance increases, and the increased resistance is transmitted to point A, which is point 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. Assuming that the forward revolution of the planetary gear shaft 5 is accelerated to NPublicThe output shaft 9 will reduce the reverse rotation speed (N)Public+NPublicI), the output shaft 9 decelerates in the reverse direction. The acceleration of the positive revolution of the planetary wheel shaft reduces the reverse rotation speed of the output shaft 9 and simultaneously reduces the relative rotation speed of the input central wheel 2 at the point A, thereby increasing the torque of the input shaft 2, namely increasing FQ. When F is presentQIncrease of (a) and FZThe increase values of the two are equal, the forward revolution of the planetary wheel shaft is not accelerated any more, the reverse rotating speed of the output shaft 9 is not reduced any more, and 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.
The embodiment can automatically find the power point which is equal to the power of the input end on the 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 embodiment does not generate energy loss of an external adjusting device, has high transmission efficiency, and can be regarded as equal-power transmission with input power equal to output power if friction loss in the transmission process is not considered.
Second embodiment
As shown in fig. 5 to 7, the embodiment is one in which the input center wheel and the output center wheel are ring-in-gear wheels. The input central wheel and the output central wheel of the device of the embodiment are internally meshed gear ring wheels, the meshing point A of the input central gear ring wheel and the input idle wheel, the meshing point B of the output central gear ring wheel and the output idle wheel and the central point O of a planet shaft are respectively at the distance L from a planet carrier shafta、Lb、LoThe relationship is La>Lb>Lo. The other steps are the same as the first step, a power point which is equal to the power of the input end can be automatically found on a load speed-torque characteristic curve, and the corresponding rotating speed and torque can be automatically adjusted; 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, or constant speed and variable 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 embodiment does not generate energy loss of an external adjusting device, has high transmission efficiency, and can be regarded as equal-power transmission with input power equal to output power if friction loss in the transmission process is not considered.

Claims (6)

1. A variable speed transmission mechanism with coaxial input and output and opposite rotation directions comprises a left side frame (15), a middle frame (16) and a right side frame (17); the method is characterized in that: the transmission mechanism is also composed of an input shaft (1), an input wheel central wheel (2), an input planet wheel (3), an output planet wheel (4), a planet wheel shaft (5), an idle wheel (6), an idle wheel shaft (7), an output central wheel (8), an output shaft (9), a planet carrier (10), a planet carrier shaft (11), a planet carrier bearing (12), a planet bearing (13) and an idle wheel bearing (14); the input shaft (1) is rotationally connected in the left side rack (15), the planet carrier shaft (11) is rotationally connected in the middle rack (16), the output shaft (9) is rotationally connected in the right side rack (17), the input shaft (1), the output shaft (9) and the planet carrier shaft (11) are arranged on the same axis, the input shaft (1) is fixedly connected with the input central wheel (2), the input central wheel (2) and the input planet wheel (3) form an external meshing transmission connection, the output shaft (9) is fixedly connected with the output central wheel (8), the output central wheel (8) and the idle wheel (6) form an external meshing transmission connection, the idle wheel (6) and the output planet wheel (4) form an external meshing transmission connection, and the planet carrier (10) is rotationally connected with the planet carrier shaft (11) through a planet carrier bearing (12), the planetary bearings (13) are uniformly distributed in the circumferential direction of the planet carrier (10), the planetary wheel shaft (5) penetrates through the planetary bearings (13), one end of each planetary wheel shaft is fixedly connected with the input planetary wheel (3), the other end of each planetary wheel shaft is fixedly connected with the output planetary wheel (4), the input planetary wheel (3), the output planetary wheel (4) and the idler wheel (6) rotate, and the input planetary wheel (3), the output planetary wheel (4), the idler wheel (6) and the planet carrier (10) as a whole revolve around the planet carrier shaft (11).
2. A continuously variable transmission mechanism with coaxial input and output and opposite rotation directions, as claimed in claim 1, wherein: at least 2 groups of input planet wheels (3) are meshed with the input central wheel (2); the output planetary wheels (4) are not less than 2 groups and are in meshed connection with the output central wheel (8) through idle wheels (6).
3. A continuously variable transmission mechanism with coaxial input and output and opposite rotation directions, as claimed in claim 1, wherein: the input central wheel (2) and the output central wheel (8) which are in external meshing transmission connection can be replaced by an input gear ring and an output gear ring which are in internal meshing.
4. A continuously variable transmission mechanism with coaxial input and output and opposite rotation directions, as claimed in claim 1, wherein: the input shaft (1) and the output shaft (9) are opposite in rotation direction under the action of the idler (6), the idler (6) is arranged on one side of the input planetary gear set or on one side of the output planetary gear set, one end of the idler shaft (7) is fixedly connected with the planet carrier (10), and the other end of the idler shaft is movably connected with the idler bearing (14).
5. A continuously variable transmission mechanism with coaxial input and output and opposite rotation directions, as claimed in claim 1, wherein: the input planet wheel (3) and the output planet wheel (4) are coaxial and have the same speed.
6. A continuously variable transmission mechanism with coaxial input and output and opposite rotation directions, as claimed in claim 1, wherein: the vertical distance L between the center O point of the planet wheel shaft (5) and the planet carrier shaft (11)oIs greater than the vertical distance L between the meshing point B of the output central wheel (8) and the idle wheel (6) and the planet carrier shaft (11)bThe vertical distance L between the meshing point B of the output central wheel (8) and the idle wheel (6) and the planet carrier shaft (11)bIs greater than the vertical distance L between the meshing point A of the input central wheel (2) and the input planet wheel (3) and the input shafta。
CN202010907121.XA 2020-09-02 2020-09-02 Input-output coaxial variable-speed transmission mechanism with opposite rotation directions Pending CN111853180A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112576709A (en) * 2020-12-15 2021-03-30 董永岗 Pure mechanical stepless speed change transmission device with output self-adaptive load characteristic

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CN103032534A (en) * 2011-10-06 2013-04-10 汤思查 Force transfer continuously variable transmission with two-sided gear rings
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CN112576709A (en) * 2020-12-15 2021-03-30 董永岗 Pure mechanical stepless speed change transmission device with output self-adaptive load characteristic

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Application publication date: 20201030