CN116292786A - A general-purpose mechanical continuously variable transmission and a transmission method thereof - Google Patents

Abstract

The invention discloses a general-purpose mechanical continuously variable transmission and a speed change method, comprising: transmission input shaft, shaft end seal, bearing gland, input end bearing, wheel frame bearing, bevel gear sun gear I, bevel gear planet gear I , planetary gear carrier I, bevel planetary gear II, differential shaft, bevel sun gear II, bevel disc ring gear, speed regulating gear, straight tooth ring gear, straight tooth sun gear, intermediate shaft, output shaft, Output connection flange, variable speed motor, variable speed pinion, bevel planetary gear III, needle bearing, input connection flange, bevel planetary gear IV, intermediate shaft support bearing, spur planetary gear and planet carrier II. The present invention utilizes the combination of the planetary differential and the planetary reducer to realize the speed regulating function, realizes the torque balance through the reverse output of two sets of gears of the planetary differential, and adjusts the rotating speed of the balance ring gear through the speed regulating motor to change the transmission ratio.

Description

A general-purpose mechanical continuously variable transmission and a transmission method thereof

technical field

The invention belongs to the technical field of transmissions, and in particular relates to a general-purpose mechanical continuously variable transmission and a transmission method.

Background technique

Continuously Variable Transmission (CVT for short) refers to a transmission method that enables the output shaft speed of a machine to change continuously within a certain range under the action of a certain control. A continuously variable transmission is a device that has two shafts, a driving shaft and a driven shaft, and connects the two shafts directly or indirectly through an intermediate medium (solid, fluid, electromagnetic flow) capable of transmitting torque to transmit power. When the relationship between the input and output shafts is controlled, the transmission ratio between the two shafts can be continuously changed within the range of two extreme values. Compared with constant transmission ratio and stepped transmission, stepless variable transmission has the advantages of being able to continuously change speed within a certain range according to the needs of work, so as to adapt to the needs of output speed and external load changes. Therefore, stepless variable transmission is used in modern transmission The technical field occupies an important position. CVTs are generally divided into three types according to different transmission media: electric type, fluid type and mechanical type.

Electric stepless variable speed transmission realizes stepless speed regulation by controlling the electrical parameters of AC or DC motors, such as changing the magnetic flux, voltage, current or frequency, and adjusting its phase angle, and is controlled by a microprocessor. Power stepless speed regulation mainly includes electromagnetic slip speed regulation, DC and AC speed regulation. At present, AC frequency conversion speed regulation has good performance and high efficiency, so it is most widely used.

There are two types of fluid-type continuously variable transmission: one is hydraulic, which changes the speed by changing the discharge volume of the hydraulic pump or the capacity of the hydraulic motor, which is suitable for small and medium power transmission; the other is hydraulic, which uses hydraulic Coupler or hydraulic torque converter for variable speed transmission, suitable for high power. The common feature of both is that they have a wide range of speed regulation, can absorb shock and prevent overload, but require high manufacturing precision, are expensive, output characteristics are constant torque, and have a large slip rate, which is prone to oil leakage during operation.

Most of the mechanical continuously variable transmissions rely on friction or oil film traction to transmit power, mainly by changing the length (working diameter) ratio between transmission components. Compared with other forms of continuously variable transmission devices, it has the advantages of simple structure, convenient operation, low price, stable transmission, reliable operation, convenient maintenance and strong adaptability. Based on the above applications, the use of continuously variable transmission is beneficial to simplify the transmission scheme, improve productivity and product quality, rationally utilize power and save energy, facilitate remote control and automatic control, and also help reduce labor intensity and improve maneuverability. CVT has become a basic general-purpose transmission type and is widely used in textile, light industry, food, packaging, machine tool, automobile and other industries. With the development of power electronics technology, a variety of AC electric speed regulation methods have appeared. In recent years, a new type of switched reluctance speed regulation motor with better performance has appeared, which has a certain impact on mechanical continuously variable transmissions. But their disadvantages are that they only have constant torque characteristics when the motor's rated speed is lower than the rated speed, the low-speed operation efficiency is low and unstable, and the starting overload performance is poor. Relatively speaking, due to the advantages of good constant power, stable speed, reliable operation, high efficiency, convenient maintenance, and wide application range, mechanical continuously variable transmissions still have broad prospects in industrial applications and are irreplaceable in many occasions. effect.

Defects and deficiencies of the prior art: the structure of the mechanical continuously variable transmission can be optimized through chain belts and conical wheels; the disadvantage of the speed-regulating motor is that it only has constant torque characteristics when it is lower than the rated speed of the motor, and the low-speed operation efficiency is low And it is unstable, the starting overload performance is poor, and the torque is unbalanced.

Contents of the invention

The purpose of the present invention is to provide a general-purpose mechanical continuously variable transmission and a speed change method to solve the problem that the existing speed-regulating motor only has constant torque characteristics when the speed is lower than the rated speed of the motor, low-speed operation efficiency is low and unstable, and starting overload Poor performance, problems with torque imbalance.

The present invention adopts the following technical solutions: a general-purpose mechanical continuously variable transmission, including: transmission input shaft, shaft end seal, bearing gland, input end bearing, wheel frame bearing, bevel gear sun gear I, bevel gear planet gear I , planetary gear carrier I, bevel planetary gear II, differential shaft, bevel sun gear II, bevel disc ring gear, speed regulating gear, straight tooth ring gear, straight tooth sun gear, intermediate shaft, output shaft, Output connection flange, variable speed motor, variable speed pinion, bevel planetary gear III, needle bearing, input connection flange, bevel planetary gear IV, intermediate shaft support bearing, spur planetary gear and planetary carrier II.

Wherein, the input connection flange is sleeved on the transmission input shaft, the input end bearing is arranged at the joint between the input connection flange and the transmission input shaft, and the bearing gland is sleeved on the transmission input shaft and fixed on the input connection flange , the joint between the bearing gland and the transmission input shaft is provided with a shaft end seal; the wheel frame bearing is sleeved and limited on the transmission input shaft, the planetary wheel carrier I is sleeved and rotated on the transmission input shaft, and the wheel frame bearing is set on the transmission input shaft The connection between the planetary carrier I and the transmission input shaft; the intermediate shaft support bearing is arranged on the transmission input shaft; the bevel gear sun gear I is sleeved on the transmission input shaft, and is fixedly connected with the transmission input shaft through a key; the bevel gear planetary gear I and The bevel planetary gear IV is meshed with the bevel sun gear I, and is symmetrically distributed on both sides of the transmission input shaft; the differential gear shaft is symmetrically supported on both sides of the planetary gear carrier I through needle bearings; the bevel planetary gear I and The bevel planetary gear II is nested and fixed on the differential shaft on one side of the planetary gear carrier I; the bevel planetary gear IV and the bevel planetary gear III are nested and fixed on the differential shaft on the other side of the planetary gear carrier I. On the wheel shaft; the bevel-toothed disc ring gear is fixedly connected with the speed-regulating large gear; the speed-regulating large gear and the bevel-toothed disc ring gear form a planetary gear carrier, and a straight-toothed planetary gear is installed on it; the straight-toothed planetary gear and the straight-toothed sun gear The straight-toothed sun gear is fixedly connected to the intermediate shaft; the straight-toothed ring gear is sleeved on the intermediate shaft, one end of the intermediate shaft is supported in the output shaft through a bearing, and the other end is supported in the transmission input through an intermediate shaft support bearing. On the shaft, the bevel-toothed sun gear II and the straight-toothed sun gear are respectively set on both ends of the intermediate shaft and fixedly connected to the intermediate shaft by keys, so that the intermediate shaft, the output shaft and the transmission input shaft can perform relative rotation to form a rotating pair ;The tail end of the intermediate shaft is nested in the output connecting shaft; the bevel sun gear II and the bevel planet gear III are nested and fixed on the differential shaft; the bevel planet gear III connects with the straight planet gear through the planet gear carrier II Connection, the speed regulating pinion is set on the output shaft of the speed regulating control motor and fixedly connected by a key; the output shaft and the spur ring gear are processed as one.

Carrier bearing, bevel sun gear I, bevel planet gear I, planet carrier I, bevel planet gear II, differential shaft and bevel sun gear II form a planetary differential; straight tooth ring gear, straight tooth The sun gear and the spur planetary gear together form a planetary reducer; the speed regulation function is realized by combining the planetary differential and the planetary reducer.

Preferably, the bevel-toothed disc ring gear, the speed-regulating large gear and the planetary carrier II are fixedly connected, and can be processed as one or separately processed and then bolted together.

The present invention adopts another technical solution: a speed change method of a general-purpose mechanical continuously variable transmission, the speed change method includes two speed regulation methods, and these two speed regulation methods are respectively:

(1) When the speed control motor is not powered on, the continuously variable transmission outputs at a constant speed ratio:

When the speed control motor is not energized, the power-off brake at the end of the speed control motor is locked, the speed control pinion and the speed control large gear do not rotate, and the bevel tooth disc fixedly connected with the transmission input shaft speed control large gear The ring gear does not rotate, and the bevel gear planetary gears I-IV do planetary motion, and at the same time drive the bevel gear sun gear II and the straight gear sun gear fixedly connected with it to rotate. It is the ratio of the number of teeth of the spur sun gear to the number of teeth of the spur ring gear.

(2) When the speed control motor is energized, the continuously variable transmission adjusts the output speed through the joint action of two stages:

When the speed regulating motor has speed and torque output, the transmission is divided into two stages when calculating the input/output speed relationship.

The first-stage input is: input speed from the transmission input shaft, which is sequentially transmitted to the bevel gear sun gear I and bevel gear planetary gear I, and then the transmission input shaft bevel gear planetary gear I drives the differential wheel shaft to rotate, and the transmission input shaft differential wheel shaft It is transmitted to the bevel-toothed disc ring gear, and the bevel-toothed planetary gear I of the transmission input shaft is also transmitted to the bevel-toothed sun gear II.

The second-level input is: the output shaft of the transmission input shaft speed regulating motor drives the speed regulating pinion gear and transmits to the speed regulating large gear; the transmission input shaft speed regulating large gear drives to the bevel disc ring gear; the transmission input shaft transmission Both the input shaft and the speed-regulating motor have speed input, and after the two speeds are synthesized, they are output from the bevel sun gear II to the straight sun gear, and finally output through the straight tooth ring gear and the output shaft fixedly connected with it.

The calculation of the input/output speed relationship of the first stage input is:

The number of teeth of bevel gear sun gear I is Y _O , the number of teeth of bevel gear planetary gear I is Y _n , the number of teeth of planetary gear carrier I and bevel gear planet gear II is Y _{m , the number of teeth of bevel gear sun gear II is Y O} , and the number of teeth of bevel gear sun gear II is Y _O . The number of teeth of the disc ring gear is Y _h , the number of teeth of the bevel planetary gear III is Y _m , and the number of teeth of the bevel planetary gear IV is Y _n .

Using the arm fixing method to regard the planetary carrier I as fixed after rotation, then:

ω _o1 -ω ₈ =-(ω _o2 -ω ₈ )

Among them, ω _o1 : the speed of the bevel sun gear I; ω _o2 : the speed of the bevel sun gear II; ω _h : the speed of the bevel disc ring gear.

The calculation of the input/output speed relationship of the second stage input is:

The number of teeth of the speed-regulating pinion (20) is z ₁ , the number of teeth of the speed-regulating gear (13) is z _x , the number of teeth of the spur sun gear (15) z _a , and the number of teeth of the spur ring gear (14) z _b , then have:

ω _a : the speed of the straight-toothed sun gear (15); ω _x : the speed of the speed-regulating bull gear (13); ω _b : the speed of the straight-toothed ring gear (14).

The total speed input/output relationship, is

ω _a =ω _o2 : the speed of the straight sun gear (15) is equal to the speed of the bevel sun gear II (11).

ω _x =ω _h : the speed of the speed-regulating bull gear (13) is equal to the speed of the bevel-toothed disc ring gear (12).

The output speed is:

Beneficial effects of the present invention: the present invention adopts full-gear transmission stepless speed regulation, the transmission ratio in the whole transmission process is controllable and calculable, and there is no differential slip in the transmission process. The invention adopts full gear transmission, which is superior to friction transmission in terms of transmission stability and reliability; since there is no differential slip in the gear transmission process, transmission errors are eliminated, the transmission ratio can be accurately calculated, and it has the advantages of seamless transmission in precision transmission and servo control systems comparable advantages.

Description of drawings

Fig. 1 is the sectional view of universal type mechanical continuously variable transmission of the present invention;

Fig. 2 is a sectional view of the planetary gear carrier in the universal mechanical continuously variable transmission of the present invention;

Fig. 3 is the cross-sectional view of the spur ring gear and the output shaft in the universal mechanical continuously variable transmission of the present invention;

Fig. 4 is the cross-sectional view of the bevel-tooth disc ring gear, the speed-regulating gear and the planetary carrier II in the general-purpose mechanical continuously variable transmission of the present invention;

Fig. 5 is the sectional view of the transmission input shaft in the universal mechanical continuously variable transmission of the present invention;

Figure 6 is a sectional view of the intermediate shaft of the universal mechanical continuously variable transmission of the present invention;

Fig. 7 is a cross-sectional view of the differential axle of the universal mechanical continuously variable transmission of the present invention.

Among them, 1. Transmission input shaft, 2. Shaft end seal, 3. Bearing gland, 4. Input end bearing, 5. Wheel frame bearing, 6. Bevel gear sun gear I, 7. Bevel gear planet gear I, 8. Planetary carrier I, 9. Bevel planetary gear II, 10. Differential wheel shaft, 11. Bevel sun gear II, 12. Bevel disc ring gear, 13. Speed regulating large gear, 14. Straight tooth ring gear, 15. Straight tooth sun gear, 16. Intermediate shaft, 17. Output shaft, 18. Output connecting flange, 19. Speed regulating motor, 20. Speed regulating pinion, 21. Bevel planetary gear III, 22. Needle roller bearing , 23. Input connection flange, 24. Bevel planetary gear IV, 25. Intermediate shaft support bearing, 26. Spur planetary gear, 27. Planetary gear carrier II.

Detailed ways

The technical solutions in the embodiments of the present invention will be clearly and completely described below. Obviously, the described embodiments are only some of the embodiments of the present invention, but not all of them. Based on the embodiments of the present invention, all other embodiments obtained by persons of ordinary skill in the art without making creative efforts belong to the protection scope of the present invention.

Example 1

As shown in Figure 1-7, a general-purpose mechanical continuously variable transmission includes: transmission input shaft 1, shaft end seal 2, bearing gland 3, input end bearing 4, wheel carrier bearing 5, bevel gear sun gear I 6. Bevel planetary gear I 7. Planetary carrier I8, bevel planetary gear II9, differential shaft 10, bevel sun gear II 11, bevel disc ring gear 12, speed regulating gear 13, straight tooth gear 14. Straight tooth sun gear 15, intermediate shaft 16, output shaft 17, output connecting flange 18, speed regulating motor 19, speed regulating pinion 20, bevel planetary gear III 21, needle roller bearing 22, input connecting flange 23 , bevel planetary gear IV 24, intermediate shaft support bearing 25, spur planetary gear 26 and planetary gear carrier II 27.

Wherein, the input connection flange 23 is sleeved on the transmission input shaft 1, the connection between the input connection flange 23 and the transmission input shaft 1 is provided with an input end bearing 4, the bearing gland 3 is sleeved on the transmission input shaft 1, and It is fixed on the input connection flange 23, and the shaft end seal 2 is arranged at the connection between the bearing gland 3 and the transmission input shaft 1; the wheel frame bearing 5 is sleeved and limited on the transmission input shaft 1, and the planetary wheel frame I 8 is sleeved And rotate and be arranged on the transmission input shaft 1, the wheel frame bearing 5 is arranged on the junction of the planetary wheel frame 18 and the transmission input shaft 1; the intermediate shaft support bearing 25 is set on the transmission input shaft 1; the bevel gear sun gear 16 is sleeved on on the transmission input shaft 1, and is fixedly connected with the transmission input shaft 1 through a key; both the bevel planetary gear I 7 and the bevel planetary gear IV 24 are meshed with the bevel gear sun gear I 6, and are symmetrically distributed on the transmission input shaft 1 Both sides; the differential axle 10 is symmetrically supported on both sides of the planetary carrier I 8 through needle bearings 22; the bevel planetary gear I 7 and the bevel planetary gear II 9 are sleeved and fixed on one side of the planetary carrier I 8 on the differential wheel shaft 10; the bevel planetary gear IV 24 and the bevel planetary gear III 21 are sleeved and fixed on the differential wheel shaft 10 on the other side of the planet carrier I 8; The large speed gear 13 is fixedly connected; the large speed gear 13 and the bevel disc ring gear 12 form a planetary gear carrier 27, on which a spur planetary gear 26 is installed; the spur planetary gear 26 is connected with the spur sun gear 15 and the spur gear ring 14 meshing connection; straight tooth sun gear 15 and intermediate shaft 16 are fixedly connected; straight tooth ring gear 14 is sleeved on the intermediate shaft 16, one end of the intermediate shaft 16 is supported in the output shaft 17 through a bearing, and the other end is supported by the intermediate shaft 25 is supported on the transmission input shaft 1, the bevel gear sun gear II 11 and the straight gear sun gear 15 are respectively set on the two ends of the intermediate shaft 16 and are fixedly connected to the intermediate shaft 16 by keys, so that the intermediate shaft 16, the output shaft 17, the transmission The input shafts 1 can rotate relative to each other to form a rotating pair; the tail end of the intermediate shaft 16 is nested in the output connecting shaft 17; the bevel gear sun gear II 11 and the bevel gear planet gear III 21 are sleeved and fixed on the differential shaft 10; the bevel-toothed planetary gear III 21 is connected with the spur-toothed planetary gear 26 through the planetary carrier II 27, and the speed-regulating pinion 20 is set on the output shaft of the speed-regulating control motor 19 and fixedly connected by a key; The ring gear 14 is processed as one;

Wheel carrier bearing 5, bevel gear sun gear I 6, bevel gear planet gear I 7, planet gear carrier I 8, bevel gear planet gear II 9, differential wheel shaft 10 and bevel gear sun gear II 11 form a planetary differential; The straight-toothed ring gear 14, the straight-toothed sun gear 15 and the straight-toothed planetary gear 26 together form a planetary reducer; the speed regulation function is realized by combining the planetary differential and the planetary reducer.

The speed change method of the general-purpose mechanical continuously variable transmission:

When the speed regulating control motor is not powered on, the power-off brake at the tail end of the motor is locked, the speed regulating pinion 20 and the speed regulating large gear 13 do not rotate, and the bevel tooth disc ring gear 12 fixedly connected with the speed regulating large gear 13 Without turning, the bevel gear planetary gears I--IV do planetary motion, and simultaneously drive the bevel gear sun gear II 11 and its fixedly connected straight gear sun gear 15 to rotate. The ratio of the number of teeth of the sun gear to the number of teeth of the spur ring gear.

When the speed-regulating motor 19 has speed and torque output, the transmission can be divided into two stages when calculating the input/output speed relationship; the first stage is the transmission input shaft 1 to the bevel planetary gear II 9 and the bevel gear sun gear II 11 parts; The stage is from the bevel gear sun gear II11 to the output shaft 17; the transmission input shaft 1 and the speed regulating motor 19 have speed input, and after the two speeds are synthesized, the bevel gear sun gear II 11 is output to the straight tooth sun gear 15; The toothed ring gear 14 and the output shaft 17 fixedly connected therewith output;

Input/Output Speed Relationship Calculation:

First level:

The number of teeth of the bevel sun gear I 6 is Y _O , the number of teeth of the bevel planetary gear I7 is Y _n , the planetary carrier I8 , the number of teeth of the bevel planetary gear II9 is Y _m , and the number of teeth of the bevel sun gear II 11 is Y _O , the number of teeth of the bevel disc ring gear 12 is Y _h , the number of teeth of the bevel planetary gear III21 is Y _m , the number of teeth of the bevel planetary gear IV 24 is Y _n ;

Using the arm fixing method to regard the planetary carrier I8 as fixed after rotation, there are:

ω _o1 -ω ₈ =-(ω _o2 -ω ₈ )

Among them, ω _o1 : the speed of the bevel sun gear I; ω _o2 : the speed of the bevel sun gear II; ω _h : the speed of the bevel disc ring gear;

second level:

The number of teeth of the speed-regulating pinion 20 is z ₁ , the number of teeth of the speed-regulating gear 13 is z _x , the number of teeth of the spur sun gear 15 is z _a , and the number of teeth of the spur ring gear 14 is z _b , then

ω _a : the speed of the spur sun gear 15;

ω _x : the speed of the speed-regulating bull gear 13;

ω _b : the speed of the spur ring gear 14;

Overall speed input/output relationship:

ω _a =ω _o2 : the speed of the straight sun gear 15 is equal to the speed of the bevel sun gear II;

ω _x = ω _h : the speed of the speed-regulating bull gear 13 is equal to the speed of the bevel-toothed disc ring gear;

The output speed is:

Among them, bevel sun gear I 6, bevel sun gear II 11, bevel planet gear I 7, bevel planet gear II 9, bevel planet gear III 21, bevel planet gear IV 24 and planet gear carrier I 8, The differential gear shaft 10 forms a differential gear train, the differential gear train 11 bevel gear sun gear II is connected with the straight gear sun gear 15 through the intermediate shaft; the bevel gear planetary gear II 9, the bevel gear planet gear III 21 and the bevel gear circle The disc ring gear 12 meshes; the bevel disc ring gear 12 is fixedly connected with the planetary carrier II 27; the output shaft 17 is fixedly connected with the spur gear ring, and the speed regulating motor is equipped with a power-off brake.

As an ideal transmission type generally respected by the machinery industry, continuously variable transmission can maximize the optimal distribution of output torque and improve energy utilization. Its research has a long history. At present, stepless speed governors are mainly divided into "belt drive type" and "traction drive type". Among them, the "belt drive type" transmits power through the friction between flexible parts such as belts or chains and the pulley; while the "traction drive type" transmits power through friction between rigid rotating bodies; "traction drive type" is divided into It is double cone disc type, double cone ring type, planetary cone disc type, roller half ring type, roller full ring type, spherical friction type, etc. Regardless of the "belt drive type" and "traction drive type", because the power is transmitted through friction, there is inevitably a differential slip, which has defects in transmission stability and reliability.

Although the content of the present invention has been described in detail through the above preferred embodiments, it should be understood that the above description should not be considered as limiting the present invention. Various modifications and alterations to the present invention will become apparent to those skilled in the art upon reading the above disclosure. Therefore, the protection scope of the present invention should be defined by the appended claims.

Claims (3)

1. A general-purpose mechanical continuously variable transmission, characterized in that it comprises: transmission input shaft (1), shaft end seal (2), bearing gland (3), input end bearing (4), wheel carrier bearing ( 5), bevel gear sun gear I (6), bevel gear planet gear I (7), planet carrier I (8), bevel gear planet gear II (9), differential gear shaft (10), bevel gear sun gear II (11), bevel disc ring gear (12), speed regulating gear (13), straight tooth ring gear (14), straight tooth sun gear (15), intermediate shaft (16), output shaft (17), Output connecting flange (18), speed regulating motor (19), speed regulating pinion (20), bevel planetary gear III (21), needle bearing (22), input connecting flange (23), bevel planet Wheel IV (24), intermediate shaft support bearing (25), spur planetary gear (26) and planetary gear carrier II (27); Wherein, the input connection flange (23) is sleeved on the transmission input shaft (1), and the connection between the input connection flange (23) and the transmission input shaft (1) is provided with an input end bearing (4 ), the bearing gland (3) is sleeved on the transmission input shaft (1) and fixed on the input connection flange (23), the bearing gland (3) and the transmission input shaft ( 1) A shaft end seal (2) is provided at the joint; the wheel carrier bearing (5) is nested and limited on the transmission input shaft (1), and the planet wheel carrier I (8) is nested and rotated It is arranged on the transmission input shaft (1), and the wheel carrier bearing (5) is arranged at the connection between the planetary wheel carrier I (8) and the transmission input shaft (1); the transmission input shaft (1) The intermediate shaft support bearing (25) is arranged on the top; the bevel gear sun gear I (6) is sleeved on the transmission input shaft (1), and is fixedly connected with the transmission input shaft (1) through a key; the bevel gear planetary gear I (7) and the bevel planetary gear IV (24) are meshed with the bevel sun gear I (6), and are symmetrically distributed on both sides of the transmission input shaft (1); the differential wheel shaft (10) passes through The needle roller bearings (22) are symmetrically supported on both sides of the planetary gear frame I (8); 8) On the differential wheel shaft (10) on one side; the bevel planetary gear IV (24) and bevel planetary gear III (21) are sleeved and fixed on the differential gear on the other side of the planetary gear carrier I (8) on the speed wheel shaft (10); the bevel-toothed disc ring gear (12) is fixedly connected with the speed-regulating bull gear (13); A planetary carrier (27) is formed, on which a spur planetary gear (26) is installed; the spur planetary gear (26) is meshed with the spur sun gear (15) and the spur ring gear (14); The toothed sun gear (15) is fixedly connected with the intermediate shaft (16); the straight-toothed ring gear (14) is sleeved on the intermediate shaft (16), and one end of the intermediate shaft (16) is supported on the output shaft (17) through a bearing. ), the other end is supported on the transmission input shaft (1) through the intermediate shaft support bearing (25), the bevel sun gear II (11) and the straight sun gear (15) are respectively set on both ends of the intermediate shaft (16) and Fixedly connected on the intermediate shaft (16) by a key, so that relative rotation can be done between the intermediate shaft (16), the output shaft (17), and the transmission input shaft (1), forming a revolving pair; the intermediate shaft (16) The tail end is sleeved in the output connecting shaft (17); the bevel sun gear II (11) and the bevel planetary gear III (21) are sleeved and fixed on the differential wheel shaft (10); the bevel planetary gear III (21) is connected with the spur planetary gear (26) by the planetary carrier II (27), and the speed-regulating pinion (20) is sleeved on the output shaft of the speed-regulating control motor (19) and is fixedly connected by a key; the output shaft ( 17) It is processed as one with the spur ring gear (14); The wheel carrier bearing (5), the bevel gear sun gear I (6), the bevel planet gear I (7), the planet gear carrier I (8), the bevel planet gear II (9 ), the differential axle (10) and the bevel sun gear II (11) form a planetary differential; the spur ring gear (14), the spur sun gear (15) and the The spur-toothed planetary gears (26) together form a planetary reducer; the speed regulation function is realized by combining the planetary differential and the planetary reducer. 2. A kind of universal mechanical continuously variable transmission as claimed in claim 1, characterized in that, the bevel-toothed disc ring gear (12), the speed-adjusting bull gear (13) and the planetary carrier II (27) For fixed connection, it can be processed as one or separately processed and then bolted as one. 3. A speed change method based on the universal mechanical continuously variable transmission as claimed in claim 1 or 2, characterized in that, the speed change method comprises two speed regulation modes, and these two speed regulation methods are respectively: (1) When the speed control motor is not powered on, the continuously variable transmission outputs at a constant speed ratio: When the speed control motor was not energized, the power-off brake at the end of the speed control motor was locked, and the speed control pinion (20) and the speed control gear (13) did not turn, and the speed control gear (13) did not turn. ) fixedly connected bevel-toothed disc ring gear (12) does not turn, and bevel-toothed planetary gears I-IV do planetary motion, and simultaneously drive bevel-toothed sun gear II (11) and the straight-toothed sun gear (15) fixedly connected with it ) rotates, and now the continuously variable transmission is a constant speed ratio output, and the output speed ratio is the ratio of the number of teeth of the straight-toothed sun gear (15) to the number of teeth of the straight-toothed ring gear (14); (2) When the speed control motor is energized, the continuously variable transmission adjusts the output speed through the joint action of two stages: When the speed-regulating motor (19) has rotational speed and torque output, the speed changer is divided into two stages when calculating the input/output rotational speed relationship; The first stage input is: the input speed from the transmission input shaft (1), which is sequentially transmitted to the bevel gear sun gear I (6), bevel gear planet gear I (7), and then driven by the bevel gear planet gear I (7) The differential axle (10) rotates, and the differential axle (10) is transmitted to the bevel disc ring gear (12), and the bevel planetary gear I (7) is also transmitted to the bevel sun gear II (11); The second stage input is: the output shaft of the speed regulating motor (19) drives the speed regulating pinion (20) to transmit, and transmits to the speed regulating large gear (13); the described speed regulating large gear (13) transmits to the cone Tooth disc ring gear (12); the transmission input shaft (1) and the speed regulating motor (19) both have speed input, and after the two speeds are synthesized, the bevel sun gear II (11) is output to the straight sun gear ( 15), and finally output through the spur ring gear (14) and the output shaft (17) fixedly connected therewith; The calculation of the input/output speed relationship of the first stage input is: The number of teeth of the bevel sun gear I(6) is Y _O , the number of teeth of the bevel planetary gear I(7) is Y _n , the number of teeth of the planet carrier I(8) and the bevel planetary gear II(9) is Y _m , The number of teeth of the bevel sun gear II (11) is Y _O , the number of teeth of the bevel disc ring gear (12) is Y _h , the number of teeth of the bevel planetary gear III (21) is Y _m , and the number of teeth of the bevel planetary gear IV The number of teeth of (24) is Y _n ; Using the arm fixing method to regard the planetary carrier I (8) as fixed after rotation, then: ω _o1 -ω ₈ =-(ω _o2 -ω ₈ )

Among them, ω _o1 : the speed of the bevel sun gear I; ω _o2 : the speed of the bevel sun gear II; ω _h : the speed of the bevel disc ring gear; The calculation of the input/output speed relationship of the second stage input is: The number of teeth of the speed-regulating pinion (20) is z ₁ , the number of teeth of the speed-regulating gear (13) is z _x , the number of teeth of the spur sun gear (15) z _a , and the number of teeth of the spur ring gear (14) z _b , then have:

ω _a : the speed of the straight toothed sun gear (15); ω _x : the speed of the speed regulating bull gear (13); ω _b : the speed of the straight toothed ring gear (14); The total speed input/output relationship is ω _a = ω _o2 : the speed of the spur sun gear (15) is equal to the speed of the bevel sun gear II (11); ω _x = ω _h : the speed of the large gear (13) The speed is equal to the speed of the bevel disc ring gear (12); the output speed is:

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