CN215171932U

CN215171932U - Pure mechanical stepless speed change transmission device with output self-adaptive load characteristic

Info

Publication number: CN215171932U
Application number: CN202023022432.2U
Authority: CN
Inventors: 董永岗; 董俊; 华娟; 周力
Original assignee: Individual
Current assignee: Individual
Priority date: 2020-12-15
Filing date: 2020-12-15
Publication date: 2021-12-14
Anticipated expiration: 2030-12-15

Abstract

A pure mechanical stepless speed change transmission device with output self-adaptive load characteristics belongs to the technical field of mechanical transmission and comprises a double planetary transmission mechanism and a planetary carrier-output shaft transmission mechanism, the utility model discloses can self-adaptively change the total transmission ratio, when the input end changes respectively or simultaneously by the input rotating speed and the input torque, the output end can automatically adjust the rotating speed and the torque corresponding to the point on the load characteristic curve which is equal to the input power; when the input power is not changed and the load torque is changed, the device can automatically adjust the output rotating speed to make the output power equal to the input power. The whole device is in gear transmission, and has the advantages of simple structure, low manufacturing cost, stable performance, large transmission power, wide application range and easy popularization.

Description

Pure mechanical stepless speed change transmission device with output self-adaptive load characteristic

Technical Field

The utility model belongs to the technical field of mechanical transmission, a can change total drive ratio's infinitely variable transmission device automatically is related to, specific saying so relates to one kind when the input is with different power input, the output realizes the equipower output according to load rotational speed-torque characteristic automatically regulated output rotational speed, when load resistance changes, the variable transmission device that automatically regulated output rotational speed so that output and input power equal.

Background

The traditional gear transmission device has a fixed transmission ratio, and the high efficiency of a power input source can be exerted only under the design working condition because the characteristics of the input source such as a diesel engine, a motor and the like cannot be superposed with the load characteristics. In actual application, a large number of non-design point operation conditions exist, so that the efficiency of the power source is reduced, and the energy consumption is increased.

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. Meanwhile, the complexity and the manufacturing precision of the whole transmission device can be increased by additionally adding an adjusting device, and the transmission device is not suitable for relatively high-power stepless variable transmission. Therefore, it is important to design a stepless speed change mechanical transmission device to meet the requirement of automatically adapting the output rotating speed-torque to the load.

SUMMERY OF THE UTILITY MODEL

The utility model aims at having pure mechanical transmission can not the automatic total drive ratio of change to current, can not be according to load rotational speed-torque characteristic automatically regulated output rotational speed, can't realize the not enough of equipower infinitely variable output, a pure mechanical infinitely variable transmission who exports self-adaptation load characteristic is proposed, only through gear drive, need not additionally increase speed adjusting device, moreover, the steam generator is simple in structure, under input power variation and load resistance change condition, the total drive ratio of automatic change device, make output rotational speed and moment of torsion can do the automatically regulated of self-adaptation load rotational speed-torque characteristic, can make the power source move all the time in the high efficiency district, the transmission performance is stable, can be convenient realization pure mechanical infinitely variable.

The technical scheme of the utility model: a pure mechanical stepless speed change transmission device with an output self-adaptive load characteristic comprises a device box body; the method is characterized in that: the variable speed transmission device consists of a double-planetary transmission mechanism and a planet carrier-output shaft transmission mechanism;

the double-planetary transmission mechanism consists of an input shaft, an input central wheel, an input planetary wheel, a planetary wheel shaft, an output planetary wheel, an output central wheel, an output shaft and a planetary frame; the input shaft is fixedly connected with the center of the input central wheel, the input central wheel is in external meshing transmission connection with the input planetary wheel, the output central wheel is in external meshing transmission connection with the output planetary wheel, the output shaft is fixedly connected with the output central wheel, and the input planetary wheel is coaxially connected with the output planetary wheel through a planetary wheel shaft;

the planet carrier-output shaft transmission mechanism consists of a planet carrier meshing wheel, a middle transmission gear I, a middle transmission gear shaft I, a middle transmission gear II, a middle transmission gear III, a middle transmission gear shaft II, an output shaft meshing central wheel, an output shaft and a planet carrier; the planet carrier meshing wheel is coaxially fixed on the planet carrier, the planet carrier meshing wheel and the first intermediate transmission gear form external meshing transmission connection, the first intermediate transmission gear is coaxially connected and fixed with the second intermediate transmission gear through a first transmission gear shaft, the second intermediate transmission gear and the third intermediate transmission gear form external meshing transmission connection, the second intermediate transmission gear shaft is connected and fixed at the center of the third intermediate transmission gear, and the output shaft meshing center wheel and the third intermediate transmission gear form external meshing transmission connection;

the double planetary transmission mechanism and the planetary carrier-output shaft transmission mechanism share a planetary gear shaft, a planetary carrier and an output shaft, the input shaft, the output shaft and the rotation center of the planet carrier are coaxially arranged, a planet carrier bearing is fixedly arranged at the center of the planet carrier, after the output shaft passes through the planet carrier bearing, one end of the output shaft is fixedly connected with the output central wheel, the other end of the output shaft is fixedly connected with the output shaft meshing central wheel, a planet wheel bearing is fixedly arranged on the circumference of the planet carrier, the planet wheel shaft is fixedly connected with the inner ring of the planet wheel bearing, the input shaft, the output shaft, the first middle transmission gear shaft and the second middle transmission gear shaft are in rotary connection with a bearing arranged on a box body of the device, the input planet wheel and the output planet wheel revolve around the center of the planet carrier after forming a whole with the planet carrier while rotating and moving.

The revolution rotation direction of the planet carrier is opposite to the rotation direction of the output shaft; when the total transmission ratio i of the planet carrier-output shaft transmission mechanism is more than or equal to 1, the total transmission ratio of the double planetary transmission mechanisms must be 1/(1+ i); when the total transmission ratio i of the planet carrier and the output shaft transmission mechanism is less than 1, the total transmission ratio of the double planetary transmission mechanisms is required to be 1/(1+ 1/i).

An input central wheel and an output central wheel in the double-planetary transmission mechanism are external gear or internal gear ring; the rotation direction between the input shaft and the output shaft is the same or opposite rotation direction by adding an idler wheel between the input central wheel and the input planetary wheel or between the output planetary wheel and the output central wheel.

The planet carrier-output shaft transmission mechanism ensures that the revolution direction of the planet carrier is opposite to the direction of the output shaft under the combined action of the planet carrier meshing wheel, at least one intermediate transmission gear and the output shaft meshing central wheel; the planet carrier meshing wheel is an external gear or an internal gear ring.

Any transmission link on the planet carrier-output shaft transmission mechanism can be used as an output component of the transmission device, and the functions of the whole transmission device are not influenced except that the total transmission ratio of the transmission device is influenced by the output of other transmission links except the output shaft.

The input planet gears and the output planet gears are not less than 2 groups and are circumferentially and uniformly distributed on the planet carrier.

The first intermediate transmission gear, the second intermediate transmission gear and the third intermediate transmission gear are not less than 2 groups and are uniformly distributed on the box body of the transmission device around the circumferential direction of the output shaft.

The utility model has the advantages that: the utility model provides a pure mechanical stepless speed change transmission device with self-adaptive output load characteristics, which can change the total transmission ratio in a self-adaptive way, when the input end changes respectively or simultaneously due to the input rotating speed and the input torque, the output end can automatically adjust the output rotating speed and the torque to the rotating speed and the torque which correspond to the same point with the input power on the load characteristic curve; when the input power is not changed and the load torque is changed, the device can automatically adjust the output rotating speed to make the output power equal to the input power. The whole device is in gear transmission, and has the advantages of simple structure, low manufacturing cost, stable performance, large transmission power, wide application range and easy popularization.

Drawings

Fig. 1 is a schematic structural view of the planet carrier engaging wheel in the present invention in an external engaging state.

Fig. 2 is a schematic structural view of the middle planet carrier engaging wheel of the present invention in an inner engaging state.

In the figure: the double-planet transmission mechanism A, a planet carrier-output shaft transmission mechanism B, an input shaft 1, an input central gear 2, an input planet gear 3, a planet gear shaft 4, an output planet gear 5, an output central gear 6, a planet carrier meshing wheel 7, a middle transmission gear I8, a middle transmission gear shaft I9, a middle transmission gear II 10, a middle transmission gear III 11, a middle transmission gear shaft II 12, an output shaft meshing central gear 13, an output shaft 14, a planet carrier bearing 15, a planet carrier bearing 16, a planet carrier 17, a device box 18 and a load 19.

Detailed Description

The invention will be further explained with reference to the following figures and examples:

the first implementation mode comprises the following steps: the planet carrier meshing wheel is externally meshed with a gear;

as shown in figure 1, the transmission device is a pure mechanical stepless speed change transmission device with an output self-adaptive load characteristic, and comprises a double-planetary transmission mechanism A, a planet carrier-output shaft transmission mechanism B and a device box body 18. The double-planetary transmission mechanism is composed of an input shaft 1, an input central wheel 2, an input planetary wheel 3, a planetary wheel shaft 4, an output planetary wheel 5, an output central wheel 6, an output shaft 14 and a planetary carrier 17, wherein the input shaft 1 is fixedly connected with the input central wheel 2, the input central wheel 2 and the input planetary wheel 3 form external meshing transmission connection, the output shaft 14 is fixedly connected with the output central wheel 6, and the output central wheel 6 and the output planetary wheel 5 form external meshing transmission connection; the planet carrier-output shaft transmission mechanism B is composed of a planet carrier 17, a planet carrier meshing wheel 7, a middle transmission gear I8, a middle transmission gear shaft I9, a middle transmission gear II 10, a middle transmission gear III 11, a middle transmission gear shaft II 12, an output shaft meshing central wheel 13 and an output shaft 14, the planet carrier 17 is fixedly connected with the planet carrier meshing wheel 7, the planet carrier meshing wheel 7 is in external meshing transmission connection with the first intermediate transmission gear 8, the first intermediate transmission gear 8 and the second intermediate transmission gear 10 are fixedly connected with the first intermediate transmission gear shaft 9, the third intermediate transmission gear 11 is fixedly connected with the second intermediate transmission gear shaft 12, the second intermediate transmission gear 10 is in external meshing transmission connection with the third intermediate transmission gear 11, the output shaft 14 is fixedly connected with the output shaft meshing central wheel 13, and the output shaft meshing central wheel 13 is in external meshing transmission connection with the third intermediate transmission gear 11. The double planetary transmission mechanism A and the planet carrier-output shaft transmission mechanism B share the planet wheel shaft 4, the planet carrier 17 and the output shaft 14. The rotation centers of the input shaft 1, the output shaft 14, and the carrier 17 are arranged on the same axis. The planet wheel shafts 4 are rotationally connected with the planet carrier 17 through planet shaft-planet carrier bearings 16, and the planet wheel shafts 4 are uniformly distributed on the circumference of the planet carrier 17; the output shaft 14 is rotationally connected to a planet carrier 17 via an output shaft, planet carrier bearing 15. The input planet wheel 3 and the output planet wheel 5 are coaxial and at the same speed and are fixedly connected with the planet wheel shaft 4; the output central wheel 6 and the output shaft meshing central wheel 13 are coaxial and have the same speed, and are connected and fixed with the output shaft 14. The input shaft 1, the output shaft 14, the first intermediate transmission gear shaft 9 and the second intermediate transmission gear shaft 12 are fixed on a transmission device box 18 through bearings and rotate freely; the input planetary gear 3 and the output planetary gear 5 rotate and, at the same time, revolve together with the carrier 17 around the rotational center of the carrier 17.

As shown in fig. 1, the transmission ratio of the planet carrier meshing wheel to the first intermediate transmission gear 8 is 1, the transmission ratio of the second intermediate transmission gear 10 to the output shaft meshing central wheel 13 is 2, that is, the total transmission ratio i of the planet carrier-output shaft transmission mechanism B is 2; the transmission ratio of the input sun wheel 2 to the input planet wheels 3 is 1 and the transmission ratio of the output planet wheels 5 to the output sun wheel 6 is 1/3, i.e. the overall transmission ratio of the double planetary transmission a is 1/3, equal to 1/(1+ i).

As shown in fig. 1, the input central gear 2 and the output central gear 6 of the double planetary transmission mechanism a are external gears; the input shaft 1 and the output shaft 14 in the double planetary transmission A rotate in the same direction. The planet carrier-output shaft transmission mechanism B enables the revolution rotation direction of the planet carrier 17 to be opposite to the rotation direction of the output shaft 14 through the combined action of a planet carrier meshing wheel 7, a first intermediate transmission gear 8, a second intermediate transmission gear 10, a third intermediate transmission gear 11 and an output shaft meshing central wheel 13 between the planet carrier 17 and the output shaft 14; the planet carrier-output shaft transmission mechanism B adopts an external gear as a planet carrier meshing wheel 7; the total transmission of the planet carrier-output shaft transmission mechanism B is more than 1; the output shaft 14 is a transmission output component of the transmission device; the input planet gears 3 and the output planet gears 5 are arranged into 2 groups and are uniformly distributed in the circumferential direction of the planet carrier 17; the first intermediate transmission gear 8, the first intermediate transmission gear shaft 9, the second intermediate transmission gear 10, the third intermediate transmission gear 11 and the second intermediate transmission gear shaft 12 are arranged into 2 groups and are circumferentially and uniformly distributed on the device box body 18 around the output shaft 14.

As shown in figure 1, a pure mechanical stepless speed change transmission device with self-adaptive output load characteristics is provided, when an input shaft 1 has power W_{Input device}=Q_{Input device}×N_{Input device}When the transmission device is used for inputting, the middle transmission gear shaft I9 and the middle transmission gear shaft II 12 in the planet carrier-output shaft transmission mechanism B are fixed on the transmission device box body 18, so that the whole transmission device cannot rotate integrally. Input torque Q_{Input device}The double-planetary transmission mechanism A is divided into two strands, the first strand drives an output shaft 14 to rotate through an input shaft 1, an input central wheel 2, an input planet wheel 3, a planet wheel shaft 4, an output planet wheel 5 and an output central wheel 6, and the second strand drives an input row through the input shaft 1, the input central wheel 2 and the input rowThe planetary gears 3 and the planetary gear shaft 4 drive the planetary gear carrier 17 to rotate in the direction opposite to the direction of the output shaft 14. The planet carrier 17 rotates in the direction opposite to the direction of the output shaft 14 and drives the output shaft 14 to rotate through the planet carrier-output shaft transmission mechanism B via the planet carrier meshing wheel 7, the intermediate transmission gear I8, the intermediate transmission gear II 10, the intermediate transmission gear III 11 and the output shaft meshing central wheel 13, and the driving direction is the same as the driving direction of the output central wheel 6. Because the planet carrier-output shaft transmission mechanism B forces the planet carrier 17 and the output shaft 14 to rotate in opposite directions at the same time according to the transmission ratio i, the first torque and the second torque are converged on the output shaft 14 through the output central wheel 6 and the output shaft meshing central wheel 13 to form output torque.

As shown in figure 1, the total transmission ratio i of a planet carrier-output shaft transmission mechanism B is 2 and is more than 1, the total transmission ratio of a double-planet transmission mechanism A is 1/3, and the input power W of an input shaft 1 is_{Input 0}=Q_{Input 0}×N_{Input 0}Will first tend towards the rotational speed N of the output shaft 14_{Output of}=N_{Input 0}The carrier 17 revolves in the reverse direction at the revolution speed N_{Revolution of the sun}=2×N_{Input 0}W is known from conservation of power_{Input 0}=Q_{Input 0}×N_{Input 0}=Q_{Output of}×N_{Output of}+Q_{Revolution of the sun}×N_{Revolution of the sun}The planetary carrier 17 revolves Q_{Revolution of the sun}Overcoming only frictional resistance and lubricating resistance, negligible, then Q_{Input 0}×N_{Input 0}=Q_{Output of}×N_{Output of}Due to N_{Input 0}=N_{Output of}Therefore, Q is_{Input 0}=Q_{Output of}. Since the output speed of the transmission is identical to the load speed, i.e. N_{Output of}=N_Load(s)At this time, the load torque Q_Load(s)If greater than Q_{Input device}The transmission cannot be started; if Q_Load(s)Is equal to Q_{Input device}Then the transmission goes into balance, we call this time N_{Output of}Is N_{Input 0}Minimum output speed N at speed input_{Minimum output 0}，N_{Revolution of the sun}Is N_{Input 0}Minimum revolution speed N under rotation speed input_{Minimum revolution 0}At this time, Q_{Output of}Is Q_{Input 0}Maximum output torque Q at torque input_{Maximum output 0}(ii) a If Q_Load(s)Less than Q_{Output of}The extra torque drives the output shaft 14 to rotate at an accelerated speed (and also drives the planet carrier 17 to accelerate in the direction opposite to the direction of the output shaft 14), and the output shaft 14 rotates at an accelerated speed, that is, the load speed is accelerated. As the output speed of the transmission increases, the output torque of the transmission correspondingly decreases according to the power conservation principle; as the load speed increases, the load torque increases, remains constant, or the rate at which the load torque decreases is less than the rate at which the transmission output torque decreases, and both the transmission output torque and the load torque tend to be the same. When this state changes to a load torque equal to the output torque, the transmission enters an initial equilibrium state, equilibrium state 0. Output speed N at this time_{Output 0}＞N_{Minimum output 0}Output torque Q_{Output 0}＜Q_{Maximum output 0}And W neglecting the friction resistance and the lubrication resistance of the device_{Input 0}=Q_{Input 0}×N_{Input 0}=Q_{Output 0}×N_{Output 0}=W_{Output 0}，Q_{Output 0}=Q_{Load 0}。

From the above, the precondition that the transmission must operate at the same time is: (1) the output speed of the transmission must be greater than or equal to the minimum output speed N_{Minimum output}(ii) a (2) At a minimum output speed N_{Minimum output}Time, maximum output torque Q_{Maximum output}Is required to be greater than or equal to the minimum output speed N on the load characteristic curve_{Minimum output}Corresponding load torque Q_Load(s)(ii) a (3) The speed is equal to or greater than the minimum output speed N on the load characteristic curve_{Minimum output}Has a power point equal to the input power and the power point is equal to the minimum output rotating speed N_{Minimum output}The load characteristic curve between corresponding power points is continuous and smooth.

As shown in fig. 1, a purely mechanical continuously variable transmission with adaptive output load characteristics, after the transmission reaches a steady state of equilibrium 0, the first change is: q_{Input 0}Invariable, N_{Input 0}Is increased to N_{Input 1}，N_{Input 1}＞N_{Input 0}Then N is_{Minimum output 1}Is equal to N_{Input 1}. Assuming that the load characteristic is that the torque rises along with the rise of the rotating speed, the input torque is unchanged, the increase of the input rotating speed is converted into the simultaneous increase of the output rotating speed and the output torque through the transmission device, the rotating speed and the torque of the load are increased along the load characteristic curve because the output rotating speed of the transmission device is the same as the rotating speed of the load, and the transmission device reaches a balance 1 stable state when the output power (the absorbed power of the load) of the transmission device is equal to the input power. At the moment, W is ignored on the premise of friction force of the device_{Input 1}=Q_{Input 0}×N_{Input 1}=Q_{Output 1}×N_{Output 1}=W_{Output 1}Output torque Q_{Output 1}=Q_{Load 1}，Q_{Output 1}＞Q_{Output 0}Output rotational speed N_{Output 1}＞N_{Output 0}While N is present_{Output 1}≥N_{Minimum output 1}If N is present_{Output 1}＜N_{Minimum output 1}The apparatus stops operating. If Q_{Input 0}Invariable, N_{Input 0}Decrease and vice versa.

As shown in fig. 1, a purely mechanical continuously variable transmission with output adaptive load characteristics, after the transmission reaches a steady state of equilibrium 0, changes in the second way: n is a radical of_{Input 0}Invariable, Q_{Input 0}Increase to Q_{Input 2}，Q_{Input 2}＞Q_{Input 0}Then N is_{Minimum output 2}Is invariably equal to N_{Input 0}. Assuming that the load characteristic is that the torque rises along with the rise of the rotating speed, the input torque increases, the input rotating speed is changed into the output rotating speed and the output torque increases simultaneously through the transmission device without changing, the rotating speed and the torque of the load increase along the load characteristic curve because the rotating speed of the transmission device is the same as the rotating speed of the load, and the transmission device reaches the equilibrium 2 stable state when the output power (load absorption power) of the transmission device is equal to the input power. At the moment, W is ignored on the premise of friction force of the device_{Input 2}=Q_{Input 2}×N_{Input 0}=Q_{Output 2}×N_{Output 2}=W_{Output 2}Output torque Q_{Output 2}=Q_{Load 2}，Q_{Output 2}＞Q_{Output 0}Output rotational speed N_{Output 2}＞N_{Output 0}While N is present_{Output 2}≥N_{Minimum output 2}If N is present_{Output 2}＜N_{Minimum output 2}The apparatus stops operating. If Q_{Input 0}Reduction of N_{Input 0}And vice versa, unchanged.

As shown in fig. 1, a purely mechanical stepless speed change transmission with an output adaptive load characteristic changes in a third way after the transmission reaches a stable state of equilibrium 0: n is a radical of_{Input 0}Increase to Q_{Input 3}，Q_{Input 3}＞Q_{Input 0}While N is present_{Input 0}Is increased to N_{Input 3}，N_{Input 3}＞N_{Input 0}Then N is_{Minimum output 3}Is equal to N_{Input 3}. Assuming that the load characteristic is that the torque rises along with the rise of the rotating speed, the simultaneous increase of the input torque and the input rotating speed is converted into the simultaneous increase of the output rotating speed and the output torque through the transmission device, because the output rotating speed of the transmission device is the same as the rotating speed of the load, the rotating speed and the torque of the load will increase along the load characteristic curve, and when the output power (the absorbed power of the load) of the transmission device is equal to the input power, the output power (the absorbed power of the load) of the transmission device is transmitted to the device to reach a stable state of balance 3. At this time, W is the same as W on the premise of neglecting the friction force of the device_{Input 3}=Q_{Input 3}×N_{Input 3}=Q_{Output 3}×N_{Output 3}=W_{Output 3}Output torque Q_{Output 3}=Q_{Load 3}，Q_{Output 3}＞Q_{Output 0}Output rotational speed N_{Output 3}＞N_{Output 0}While N is present_{Output 3}≥N_{Minimum output 3}If N is present_{Output 3}＜N_{Minimum output 3}The apparatus stops operating. If Q_{Input 0}Reduction of, while N_{Input 0}Decrease and vice versa.

As shown in fig. 1, a purely mechanical stepless speed change transmission device with an output adaptive load characteristic changes in a fourth way after the transmission device reaches a balanced 0 stable state: q_{Input 0}Invariable, N_{Input 0}Constant, load torque Q_Load(s)Increase by Q_{Load 4}Then N is_{Minimum output 4}Is invariably equal to N_{Input 0}. Suppose that the load characteristic is that torque increases as the rotational speed increases, due to Q_{Load 4}Increase Q_{Output 0}Less than Q_{Load 4}The output torque less than the load torque causes a reduction in the transmission output speed, which is known from power conservation to increase the transmission output torque, when the output torque increases to equal the load torque Q_{Load 4}The device reaches equilibrium 4 steady state. At the moment, W is ignored on the premise of neglecting the friction resistance and the lubrication resistance of the device_{Input 0}=Q_{Input 0}×N_{Input 0}=Q_{Output 4}×N_{Output 4}=W_{Output 4}Output torque Q_{Output 4}＞Q_{Output 0}Output rotational speed N_{Output 4}＜N_{Output 0}And is also simultaneously N_{Output 4}≥N_{Minimum output 4}If N is present_{Output 4}＜N_{Minimum output 4}The apparatus stops operating. If Q_{Input 0}Invariable, N_{Input 0}Constant, load torque Q_Load(s)Decrease and vice versa.

As shown in fig. 1, in a purely mechanical stepless speed change transmission device with an output adaptive load characteristic, after the transmission device reaches a stable state of balance 0, other changes can be made, and as long as the input working condition and the output working condition meet 3 preconditions which must be possessed by the operation of the transmission device, the transmission device can reach a new balanced state operation.

The second embodiment: the planet carrier meshing wheel is internally meshed with the gear ring;

as shown in fig. 2, in a pure mechanical stepless speed change transmission device with an output adaptive load characteristic, the total transmission ratio i of the planet carrier-output shaft transmission mechanism is smaller than 1, which is 1/2, and the difference from the total transmission ratio i of the planet carrier-output shaft transmission mechanism being greater than or equal to 1 is that: minimum output speed N_{Minimum output}Equal to 2 XN_{Input device}Minimum revolution speed N of planetary carrier_{Minimum revolution}Equal to input speed N_{Input device}And counter-rotates to the output shaft. The implementation principle is the same as that of the first embodiment.

Claims

1. A purely mechanical continuously variable transmission with output adaptive load characteristics, comprising a device case (18); the method is characterized in that: the variable speed transmission device consists of a double-planetary transmission mechanism (A) and a planet carrier-output shaft transmission mechanism (B);

the double-planetary transmission mechanism (A) is composed of an input shaft (1), an input central wheel (2), an input planet wheel (3), a planet wheel shaft (4), an output planet wheel (5), an output central wheel (6), an output shaft (14) and a planet carrier (17); the input shaft (1) is fixedly connected with the center of the input central wheel (2), the input central wheel (2) is in external meshing transmission connection with the input planet wheel (3), the output central wheel (6) is in external meshing transmission connection with the output planet wheel (5), the output shaft (14) is fixedly connected with the output central wheel (6), and the input planet wheel (3) is coaxially connected and fixed with the output planet wheel (5) through a planet wheel shaft (4);

the planet carrier-output shaft transmission mechanism (B) is composed of a planet carrier meshing wheel (7), a middle transmission gear I (8), a middle transmission gear shaft I (9), a middle transmission gear II (10), a middle transmission gear III (11), a middle transmission gear shaft II (12), an output shaft meshing central wheel (13), an output shaft (14) and a planet carrier (17); the planet carrier meshing wheel (7) is coaxially fixed on the planet carrier (17), the planet carrier meshing wheel (7) and the intermediate transmission gear I (8) form external meshing transmission connection, the intermediate transmission gear I (8) is coaxially connected and fixed with the intermediate transmission gear II (10) through a transmission gear shaft I (9), the intermediate transmission gear II (10) and the intermediate transmission gear III (11) form external meshing transmission connection, the intermediate transmission gear shaft II (12) is connected and fixed at the center of the intermediate transmission gear III (11), and the output shaft meshing central wheel (13) and the intermediate transmission gear III (11) form external meshing transmission connection;

the double-planetary transmission mechanism (A) and the planetary carrier-output shaft transmission mechanism (B) share a planetary gear shaft (4), a planetary carrier (17) and an output shaft (14), the input shaft (1), the output shaft (14) and the planetary carrier (17) are coaxially arranged at the rotation center, a planetary carrier bearing (15) is fixedly arranged at the center of the planetary carrier (17), after the output shaft (14) penetrates through the planetary carrier bearing (15), one end of the output shaft is fixedly connected with the output central wheel (6), the other end of the output shaft is fixedly connected with the output shaft meshing central wheel (13), a planetary gear bearing (16) is fixedly arranged on the circumferential direction of the planetary carrier (17), the planetary gear shaft (4) is fixedly connected with an inner ring of the planetary gear bearing (16), and the input shaft (1), the output shaft (14), a first intermediate transmission gear shaft (9) and a second intermediate transmission gear shaft (12) are in rotating connection with a bearing arranged on a device box body (18), the input planet wheel (3) and the output planet wheel (5) revolve around the center of the planet carrier (17) after forming a whole with the planet carrier (17) while rotating.

2. An output adaptive load characteristic purely mechanical continuously variable transmission device as claimed in claim 1, wherein: an input central wheel (2) and an output central wheel (6) in the double-planetary transmission mechanism (A) are external gear or internal gear rings; the rotation direction between the input shaft (1) and the output shaft (14) is the same or opposite rotation direction by adding an idler wheel between the input central wheel (2) and the input planet wheel (3) or between the output planet wheel (5) and the output central wheel (6).

3. An output adaptive load characteristic purely mechanical continuously variable transmission device as claimed in claim 1, wherein: the planet carrier-output shaft transmission mechanism (B) ensures that the revolution direction of the planet carrier (17) is opposite to the direction of the output shaft (14) under the combined action of the planet carrier meshing wheel (7), at least one intermediate transmission gear and the output shaft meshing central wheel (13); the planet carrier meshing wheel (7) is an external gear or an internal gear ring.

4. An output adaptive load characteristic purely mechanical continuously variable transmission device as claimed in claim 1, wherein: any transmission link on the planet carrier-output shaft transmission mechanism (B) can be used as an output component of the transmission device, and the functions of the whole transmission device are not influenced except the total transmission ratio of the transmission device which is output by other transmission links except the output shaft (14).

5. An output adaptive load characteristic purely mechanical continuously variable transmission device as claimed in claim 1, wherein: the input planetary gears (3) and the output planetary gears (5) are not less than 2 groups and are circumferentially and uniformly distributed on the planetary carrier (17).

6. An output adaptive load characteristic purely mechanical continuously variable transmission device as claimed in claim 1, wherein: the number of the intermediate transmission gears I (8), the number of the intermediate transmission gears II (10) and the number of the intermediate transmission gears III (11) are not less than 2, and the intermediate transmission gears I, the intermediate transmission gears II (10) and the intermediate transmission gears III (11) are uniformly distributed on the transmission device box body (18) around the circumferential direction of the output shaft (14).