CN113007294A - Modular speed change system - Google Patents

Abstract

A modularized speed change system belongs to the technical field of automobile speed change systems and comprises a planet wheel assembly, wherein the planet wheel assembly is coupled with a brake mechanism, an input shaft, an output shaft and an output gear to form a module unit; an input shaft of the module unit is coupled with an output gear through a planetary wheel assembly, and power is transmitted to an output shaft through controlling the action of a braking mechanism, so that the power transmission and the speed transmission are realized; the planetary wheel assembly in the module unit is coupled with the brake mechanism, the input shaft and the output gear in various ways to form different modules for different combinations, so that the modules form a whole with a simple structure, the purposes of transmitting power and increasing or reducing torque are achieved, and the speed transmission and reversing are further realized; the system has stable and reliable performance, can realize the linear adjustment of the time of the process of synchronizing the rotating speed of the output shaft into the rotating speed of the input shaft by controlling the action time of the braking mechanism, can also realize the quick switching of forward and reverse rotation, and has the characteristic of large transmission torque.

Description

Modular speed change system

Technical Field

The invention belongs to the technical field of automobile speed change systems, and particularly relates to a modular speed change system.

Background

The speed changing device of the existing automobile speed changing system comprises an MT manual speed changing box, a CVT stepless speed changing box, an AT automatic speed changing box, a DCT dual clutch speed changing box, a sequential speed changing box and the like, but the speed changing device has various problems.

Such as: the MT manual gearbox has a very obvious defect that the manual gearbox is not flexible enough to operate on a road with urban congestion, and the starting can be achieved only by stepping on a clutch and engaging a gear again after each parking, so that a plurality of novice drivers are in a busy and disorderly hand and foot; the CVT stepless speed changing box has the disadvantages that the steel belt is used for transmitting power, so that large torque cannot be output, the steel belt slips once the large torque is output, the power is transmitted by using the steel belt for a long time, the service life of the steel belt is short, the manufacturing cost of the CVT stepless speed changing box is higher, and most importantly, the CVT stepless speed changing box can only be integrally replaced and cannot be adjusted and maintained once problems occur, so that the manufacturing cost is high, and the maintenance cost is also high; the DCT double-clutch transmission has the same pause and strong frustration and the inherent defect of gear shifting logic. The AT automatic gearbox has the advantages of precise structure, high cost, difficult mechanical manufacture and generally lower efficiency compared with DCT (discrete cosine transformation); the sequential gearbox has strong gear shifting and jerking feeling, and particularly the loss of a synchronizer is serious.

Disclosure of Invention

The invention aims to provide a modular speed change system to solve the technical problems that a speed change device is complex to operate, strong in pause and frustration, high in manufacturing cost, easy to damage parts and weak in use.

In order to solve the above technical problem, a specific technical solution of the modular transmission system of the present invention is as follows:

a modular speed change system, a planet wheel assembly, the planet wheel assembly is coupled with a brake mechanism, an input shaft, an output shaft and an output gear to form a modular unit; the input shaft of the module unit is coupled with the output gear through the planetary wheel assembly and transmits power to the output shaft through controlling the action of the brake mechanism, so that the purpose of power transmission is achieved; the planet wheel assembly comprises a sun wheel, an outer gear ring, a planet wheel and a planet wheel carrier, wherein the periphery of the sun wheel is meshed with the planet wheel, the planet wheel is also meshed with the inner teeth of the outer gear ring, and the planet wheel is connected with the planet wheel carrier, so that the planet wheel can rotate and can also revolve around the sun wheel in the outer gear ring, and the planet wheel carrier is driven to rotate; the input shaft and the output shaft are coupled through the planetary wheel assembly and the output gear, so that the input shaft and the output shaft in the module unit are not in the same axis position, and the purposes of simple manufacture and power transmission are achieved.

Further, the module unit is a first module, and an input shaft of the first module is coupled with a sun gear to input power; the outer gear ring is coupled with the output gear to output power; the planet wheel carrier is coupled with the braking mechanism, and the change of the output torque is realized through the action of the braking mechanism.

Further, the module unit is a second module, and an input shaft of the second module is coupled with a sun gear to input power; the planet wheel carrier is coupled with the output gear to output power; the outer gear ring is coupled with the braking mechanism, and the change of the output torque is realized through the action of the braking mechanism.

Furthermore, the module unit is a module III, and an input shaft of the module III is coupled with the planet wheel carrier to input power; the sun gear extends out of the planet gear carrier and is coupled with the output gear to output power; the input shaft passes through the sun gear through a bearing, so that the input shaft does not drive the sun gear to rotate; the outer gear ring is coupled with the braking mechanism, and the change of the output torque is realized through the action of the braking mechanism.

Furthermore, the module unit is a module IV, and an input shaft of the module IV is coupled with the planet wheel carrier to input power; the outer gear ring is coupled with the output gear to output power; the sun gear extends out of the planet carrier and is coupled with the braking mechanism, and the change of the output torque is realized through the action of the braking mechanism. The input shaft passes through the sun gear through a bearing, so that the input shaft does not drive the sun gear to rotate.

Further, the module unit is a module V, and an input shaft of the module V is coupled with the outer gear ring to input power; the planet wheel carrier is coupled with the output gear to output power; the sun gear extends out of the planet carrier and is coupled with the braking mechanism, and the change of the output torque is realized through the action of the braking mechanism. The output shaft passes through the sun gear through a bearing, so that the output shaft does not drive the sun gear to rotate.

Further, the module unit is a module six, and an input shaft of the module six is coupled with the outer gear ring to input power; the sun gear is coupled with the output gear to output power; the planet wheel carrier is coupled with the braking mechanism, and the change of the output torque is realized through the action of the braking mechanism.

Furthermore, the output shaft is provided with at least 2 output gears, and the input shaft is provided with at least 2 groups of planetary gear assemblies of the same module corresponding to the output gears and matched with the brake mechanism, so that the speed is increased or decreased and is controlled according to gears.

Furthermore, a first module and a second module, a third module and a fourth module, or a fifth module and a sixth module are arranged on the input shaft and the output shaft, and the combination of every two groups of modules and the braking mechanism in the corresponding module are mutually matched to form a structure with variable forward and reverse rotation directions and variable rotating speed.

Furthermore, at least two groups of modules I and two groups of modules II, at least two groups of modules III and one group of modules IV, or at least two groups of modules V and one group of modules VI are arranged on the input shaft and the output shaft, and the combined modules are mutually matched with braking mechanisms in corresponding modules to achieve forward and reverse control speed according to gears.

Furthermore, the input shaft comprises a driving shaft and a driven shaft, multi-shaft transmission is realized through the matching of the driving shaft and the driven shaft, and one or more groups of module units are arranged on the driven shaft and the output shaft for speed change or reverse rotation, so that the control of more gears is realized.

The modular gear shift system of the present invention has the following advantages:

1. compared with the complex operation of stepping on the clutch when the MT manual transmission shifts gears, the invention does not need the clutch, and the smoothness of the gear shifting is realized by linearly adjusting the braking action time of the braking mechanism;

2. compared with the CVT, the gear transmission of the invention has large transmission torque, the structural characteristics of the CVT cause the steel belt and the conical surface to be easy to slip when the friction force is insufficient, and the wearing parts are easy to damage;

3. the modular design structure of the invention is simple, compared with the AT automatic gearbox which has lower manufacturing difficulty, the AT automatic gearbox is combined by nesting and series connection of a plurality of planet wheels, the manufacturing difficulty is large, the processing precision is high, the transmission power loss is large by adding the preposed hydraulic torque converter, each module of the invention is independent, no nesting and complex combination is provided, and the relative manufacturing difficulty and the cost are greatly reduced

4. The braking mechanism of the invention has linear and adjustable action, and has smooth gear shifting compared with a DCT dual-clutch transmission, and simple and rapid gear shifting logic. The DCT double-clutch transmission is essentially a variant of a manual gear, a group of clutches are added, the pause of gear shifting is not substantially improved, only two groups of clutches can only prepare one group of gears in advance, the logic of gear shifting is naturally defective, the problem of continuous acceleration is solved, if a high-speed gear is prepared during sudden deceleration, the prepared high-speed gear is disconnected, a low-speed gear is engaged, and then gear shifting is carried out, the action steps are complicated and the gear shifting is slow, the gears of the invention are all in a modularized design, and all the gears are in a preparation state during driving, so that the rapid plus-minus gear action can be realized.

5. The gear shifting of the invention is operated by the flexible braking mechanism, the gear shifting is smooth compared with the rigid hard connection of the sequential dog tooth synchronizer, and the service life of each part is longer because the braking mechanism is not arranged in the transmission gear system during the gear shifting. The dog tooth synchronizer of the sequential type gearbox has very large loss in the working state of gear shifting, the material requirement of the dog tooth synchronizer is very high, dog teeth are damaged, the gearbox cannot be used, and the rigid connection action of the dog teeth during synchronous rotating speed has no smoothness. The modular nature of the present invention also allows upshifts to skip shifts (e.g., all gears are in stock when the brake mechanism is electronically controlled) to achieve faster shift speeds than sequential upshifts are necessary.

The input shaft and the output shaft are connected in parallel through the planetary wheel set by adopting a single module or various combination forms for coupling the modules together, so that the input shaft and the output shaft form a whole, the structure is simple, the performance is stable and reliable, the linear adjustability of the speed can be realized according to the action time of the braking mechanism when the rotating speed is synchronously increased (namely the speed of the output shaft is synchronously transmitted to the speed of the input shaft), and meanwhile, the forward and reverse rotation can be quickly switched, and the characteristic of large transmission torque is achieved; in various combination modes, if parts are failed during speed change, the work of other modules cannot be influenced, and the working reliability is higher.

Drawings

FIG. 1 is a schematic block diagram of a modular transmission system according to the present invention;

FIG. 2 is a schematic view of a first configuration A of a modular transmission system according to the present invention;

FIG. 3 is a schematic structural diagram of a second module of the modular transmission system of the present invention;

FIG. 4 is a schematic view of a second module configuration B of the modular transmission system of the present invention;

FIG. 5 is a schematic view of a modular transmission system according to the present invention;

FIG. 6 is a schematic view of a modular gear shifting system of the present invention in the direction of "C";

FIG. 7 is a schematic block diagram of a modular transmission system according to the present invention;

FIG. 8 is a schematic view of a modular four-configuration D of a modular transmission system of the present invention;

FIG. 9 is a schematic block diagram of a modular transmission system according to the present invention;

FIG. 10 is a schematic view of a modular five configuration E of a modular transmission system of the present invention;

FIG. 11 is a schematic block diagram of a modular transmission system according to the present invention;

FIG. 12 is a schematic view of a modular six configuration F of a modular transmission system of the present invention;

FIG. 13 is a schematic view of a first module and a second module combination of a modular transmission system of the present invention;

FIG. 14 is a schematic view of a three-group module-to-module assembly of a modular transmission system of the present invention;

FIG. 15 is a schematic view of a four-group module one and a module two combination configuration of a modular transmission system of the present invention;

FIG. 16 is a schematic view of a multi-axle and multi-module combination of a modular transmission system of the present invention;

the notation in the figure is: 1. an input shaft; 11 driving shaft; 111. a driving gear; 12. a first driven shaft; 121. a first driven gear; 13. a second driven shaft; 131. a driven gear II; 14. a driven shaft; 141. a driven gear; 2. a planet wheel assembly; 21. an outer ring gear; 22. a planet carrier; 23. a planet wheel; 24. a sun gear; 3. an output shaft; 31. an output gear; 4. a brake mechanism; 5. a hydraulic torque converter; 6. a bearing;

d1, first gear; d2, second gear; d3, third gear; d4, fourth gear; d5, fifth gear; d6, sixth gear; r and reverse gear.

Detailed Description

For a better understanding of the objects, structure and function of the present invention, a modular transmission system according to the present invention will be described in further detail with reference to the accompanying drawings.

As shown in fig. 1 to 16, the modular transmission system provided by the invention can realize the advantages of simple operation and high transmission efficiency of the sequential transmission case dedicated for racing cars, and relatively eliminate the jerking feeling of gear shifting, and is a transmission system with simple structure and low cost;

the modular speed change system comprises modules, wherein each module comprises a planetary wheel assembly 2, an input shaft 1, an output shaft 3, an output gear 31 and a brake mechanism 4, and the aims of power transmission, torque increase and decrease and direction change are achieved by parallel coupling between the input shaft 1 and the output shaft 3.

A modular speed change system comprises a planet wheel assembly 2, wherein the planet wheel assembly 2 is coupled with a brake mechanism 4, an input shaft 1, an output shaft 3 and an output gear 31 to form a modular unit; an input shaft 1 of the module unit is coupled with an output gear 31 through a planet wheel assembly 2, and then power is transmitted to an output shaft 3 through the action of a control brake mechanism 4, so that the purpose of power transmission is achieved; the planet wheel assembly 2 comprises a sun wheel 24, an outer gear ring 21, a planet wheel 23 and a planet wheel carrier 22, the periphery of the sun wheel 24 is meshed with the planet wheel 23, the planet wheel 23 is also meshed with the inner teeth of the outer gear ring 21, the planet wheel 23 is connected with the planet wheel carrier 22, so that the planet wheel 23 can rotate and revolve around the sun wheel 24 in the outer gear ring 21, and the planet wheel carrier 22 is driven to rotate; the output gear 31 is fixedly connected with the output shaft 3, so that the output gear 31 and the output shaft 3 rotate in the same direction. The input shaft 1 and the output shaft 3 are coupled through the planet wheel assembly 2 and the output gear 31, so that the input shaft 1 and the output shaft 3 in the module unit are not in the same axial position, and the purposes of simple manufacture and power transmission are achieved.

As shown in fig. 1-2, further, the module unit is a module one, and an input shaft 1 of the module one is coupled with a sun gear 24 to input power; the outer gear ring 21 is coupled with the output gear 31 to output power; the planetary carrier 22 is coupled with the brake mechanism 4, and the change of the output torque is realized through the action of the brake mechanism 4. Because the other end of the output shaft 3 is connected with large load resistance, after power is transmitted to the sun gear 24 from the input shaft 1, the planet gear 23 drives the planet gear carrier 22 to rotate rapidly, and the brake mechanism 4 connected with the planet gear carrier 22 linearly decelerates the planet gear carrier 22 to stop so as to linearly accelerate the outer gear ring 21 and achieve the effect of synchronously transmitting the rotating speed.

3-4, further, the module unit is a second module, and the input shaft 1 of the second module is coupled with the sun gear 24 to input power; the planetary carrier 22 is coupled with the output gear 31 to output power; the external gear ring 21 is coupled with the brake mechanism 4, and the change of the output torque is realized through the action of the brake mechanism 4. Because the other end of the output shaft 3 is connected with large load resistance, after power is transmitted to the sun gear 24 from the input shaft 1, the planet gears 23 drive the outer gear ring 21 to rotate rapidly, and the brake mechanism 4 connected with the outer gear ring 21 linearly decelerates the outer gear ring 21 to stop so as to linearly accelerate the planet gear carrier 22 and achieve the effect of synchronously transmitting the rotating speed.

As shown in fig. 5-6, further, the module unit is a module three, and the input shaft 1 of the module three is coupled with the planetary carrier 22 to input power; the sun gear 24 extends out of the planet carrier 22 and is coupled with the output gear 31 to output power; the input shaft 1 passes through the sun gear 24 through the bearing 6, so that the rotation of the sun gear 24 is not influenced; the external gear ring 21 is coupled with the brake mechanism 4, and the change of the output torque is realized through the action of the brake mechanism 4. Because the other end of the output shaft 3 is connected with large load resistance, after power is transmitted to the planet wheel carrier 22 from the input shaft 1, the planet wheels 23 drive the outer gear ring 21 to rotate rapidly, and the outer gear ring 21 is linearly decelerated to stop through the braking mechanism 4 connected with the outer gear ring 21, so that the sun wheel 24 is linearly accelerated, and the effect of synchronously transmitting the rotating speed is achieved.

As shown in fig. 7-8, further, the module unit is a module four, and the input shaft 1 of the module four is coupled with the planetary carrier 22 to input power; the outer gear ring 21 is coupled with the output gear 31 to output power; the sun gear 24 extends out of the planet carrier 22 and is coupled with the brake mechanism 4, and the change of the output torque is realized through the action of the brake mechanism 4. The input shaft 1 passes through the sun gear 24 through the bearing 6, so that the rotation of the sun gear 24 is not influenced; because the other end of the output shaft 3 is connected with large load resistance, after power is transmitted to the planet wheel carrier 22 from the input shaft 1, the planet wheel 23 drives the sun wheel 24 to rotate rapidly, and the brake mechanism 4 connected with the sun wheel 24 linearly decelerates the sun wheel 24 to stop so as to linearly accelerate the outer gear ring 21 and achieve the effect of synchronously transmitting the rotating speed.

As shown in fig. 9-10, further, the module unit is a module five, and the input shaft 1 of the module five is coupled with the external gear ring 21 to input power; the planetary carrier 22 is coupled with the output gear 31 to output power; the sun gear 24 extends out of the planet carrier 22 and is coupled with the brake mechanism 4, and the change of the output torque is realized through the action of the brake mechanism 4. The input shaft 1 passes through the sun gear 24 through the bearing 6, so that the rotation of the sun gear 24 is not influenced; one side of the outer gear ring 21 protrudes out of the planet wheel 23 and is connected with the input shaft 1 through a plurality of rib plates. So that it does not affect the rotation of the planet wheel 23; because the other end of the output shaft 3 is connected with large load resistance, after power is transmitted to the outer gear ring 21 from the input shaft 1, the planet wheel 23 drives the sun wheel 24 to rotate rapidly, and the brake mechanism 4 connected with the sun wheel 24 linearly decelerates the sun wheel 24 to stop so as to linearly accelerate the planet wheel carrier 22 and achieve the effect of synchronously transmitting the rotating speed.

As shown in fig. 11-12, further, the module unit is a module six: the input shaft 1 of the module six is coupled with the outer gear ring 21, and power is input; the sun gear 24 extends out of the planet carrier 22 and is coupled with the output gear 31 to output power; the planetary carrier 22 is coupled with the brake mechanism 4, and the change of the output torque is realized through the action of the brake mechanism 4. The input shaft 1 passes through the sun gear 24 through the bearing 6, so that the rotation of the sun gear 24 is not influenced; one side of the outer gear ring 21 protrudes out of the planet wheel 23 and is connected with the input shaft 1 through a plurality of rib plates. So that it does not affect the rotation of the planet wheel 23; because the other end of the output shaft 3 is connected with large load resistance, after power is transmitted to the external gear ring 21 from the input shaft 1, the planet wheel 23 drives the planet wheel carrier 22 to rotate rapidly, and the brake mechanism 4 connected with the planet wheel carrier 22 linearly decelerates the planet wheel carrier 22 to stop so as to linearly accelerate the sun wheel 24 and achieve the effect of synchronously transmitting the rotating speed.

The braking mechanism 4 may be a physical brake such as: disc brake, drum brake, etc., and can also be electromagnetic brake, etc. The brake device can be composed of an oil brake, a gas brake, a wire-pulling brake shoe and other power-on parts or a pure machine according to requirements, the time for completing the action is linearly controllable, and therefore when the speed ratio is switched, the slower and smoother the braking action are. The brake mechanism 4 is provided with an opening door at the corresponding part of the shell of the gearbox, and can quickly replace and install easily damaged friction parts, such as: the brake of connection adopts the dish to stop, is exactly the friction disc in the middle of the dish stops, and the maintenance of being convenient for promotes whole life.

As shown in fig. 13, further, a first module and a second module, a third module and a fourth module, or a fifth module and a sixth module are arranged on the input shaft 1 and the output shaft 3, so that the two groups of modules are combined in opposite directions, and the combination of each two groups of modules and the braking mechanism 4 in the corresponding module cooperate with each other to form a structure with variable forward and reverse rotation directions and variable rotation speed:

for example: the input shaft 1 and the output shaft 3 are provided with a first module and a second module, power is connected with sun gears 24 of the first module and the second module through the input shaft 1, 2 output gears 31 of the output shaft 3 are respectively connected with an outer gear ring 21 of the first module and a planet gear carrier 22 of the second module, if the action of a braking mechanism 4 connected with the planet gear carrier 22 of the first module is positive rotation, the action of a mechanism connected with the outer gear ring 21 of the second module is stopped, and otherwise, the action of the braking mechanism 4 of the second module is reverse rotation.

Specifically, the sun gear 24 of the first module on the input shaft 1 has 40 teeth, the outer gear ring 21 has 80 teeth, and the speed ratio is 2: 1; if the modulus is 1, the external teeth of the external gear ring 21 have 90 teeth, the gear of the corresponding module I on the output shaft 3 has 198 teeth, and the speed ratio is 2.2:1, so that the speed ratio from the input shaft 1 to the output shaft 3 is 4.4: 1. The sun gear 24 in the planetary gear assembly 2 of the second module on the input shaft 1 is 40 teeth, the planet gear 23 is 120 teeth, the speed ratio is 3:1, if the modulus is 1, the gear 140 externally connected with the planet gear carrier 22 is 140 teeth, the output gear 31 of the corresponding second module on the output shaft 3 is 140 teeth, the speed ratio is 1:1, and therefore the speed ratio from the input shaft 1 to the output shaft 3 is 3: 1. The brake mechanism 4 externally connected with the planet carrier 22 in the first module can obtain the rotating speed ratio of 4.4:1 input to output, the brake mechanism 4 in the first module stops acting while the input shaft 1 is unchanged in rotating direction, the brake mechanism 4 externally connected with the outer gear ring 21 of the module acts, and the output 3 with opposite rotating direction can be obtained on the output shaft 3:1, and the function of positive and negative rotation is realized.

As shown in fig. 14, further, at least 2 output gears 31 are arranged on the output shaft 3, and at least 2 sets of planetary wheel assemblies 2 of the same module corresponding to the output gears 31 are arranged on the input shaft 1 and are matched with the brake mechanism 4, so that the purposes of keeping the steering direction unchanged, changing the rotating speed, increasing and decreasing the speed and controlling the speed according to the gear are achieved.

The module can be concretely understood as a structure that any one of the modules which are the same as the module I, the module II, the module III, the module IV, the module V and the module VI can realize constant steering to form variable rotating speed; after the n groups of modules are connected in parallel, the gear ratios of the input gear or the output gear 31 on the input shaft 1 and the output shaft 3 are adjusted differently, and when the braking mechanism 4 acts independently, n different rotating speeds can be obtained on the output shaft 3.

For example: the output shaft 3 is provided with three output gears 31, the input shaft 1 is provided with three groups of planet wheel assemblies 2 which are a module I, the sun gear 24 of each planet wheel assembly 2 is 40 teeth, the internal teeth of the outer gear ring 21 are 80 teeth, and the speed ratio is 2: 1; if the modulus is 1, the number of teeth of the external gear ring 21 of each group of modules and the corresponding output gear 31 on the output shaft 3 is respectively as follows: 90 teeth, 198 teeth; 122 teeth, 158 teeth; 156 teeth and 124 teeth, the speed ratio is 2.2:1 respectively; 1.29: 1; 0.79:1, so that the speed ratio of each module from the input shaft 1 to the output shaft 3 is (4.4:1) (2.58:1) (1.58:1), respectively. When the brake mechanisms 4 connected with the planet carrier 22 in the planet wheel assembly 2 respectively act independently, 3 rotation speed ratios with the same direction and different rotation speeds can be obtained under the condition that the input rotation speed is not changed, and further the speed regulation control of a first gear D1, a second gear D2 and a third gear D3 is achieved.

As shown in fig. 15, at least two groups of modules, i.e., a first module and a second module, or at least two groups of modules, i.e., a third module and a fourth module, or at least two groups of modules, i.e., a fifth module and a sixth module, are arranged on the input shaft 1 and the output shaft 3, and are combined with the braking mechanism 4 in the corresponding modules to be matched with each other, so that the forward and reverse directions can be changed, the speed can be increased or decreased, and the forward and reverse speeds can be controlled according to the.

Specifically, a plurality of modules I and modules II are connected in parallel, or a plurality of groups of modules III and modules IV are connected in parallel, or a plurality of groups of modules V and modules VI are connected in parallel, and the like, so that n changes of the rotation speed are formed; after n groups of modules are connected in parallel, the gear ratio of the input gear or the output gear 31 on the input shaft 1 and the output shaft 3 is adjusted differently, and different rotating speeds can be obtained on the output shaft 3 when the same braking mechanism 4 of each group of modules acts independently. It is also possible to realize a reversing function when the different module braking mechanisms 4 are actuated.

For example: the input shaft 1 and the output shaft 3 are provided with a first four-group module and a second four-group module, each first four-group module and the second four-group module input power from the sun gear 24, the first module realizes positive rotation and the second module realizes reverse rotation, the first four-group module is provided with four forward gears, the sun gear 24 of the first four-group module is provided with 40 teeth, the internal teeth of the gear ring are 80 teeth, when the brake of each group acts to make the planet gear carrier 22 stationary, the speed ratio of the input power to the gear ring of the planet gear 23 is 2:1, and the speed ratio of the four-group modules is 4.4: 1. 2.58:1, 1.58:1 and 0.98:1, the speed ratio of the external teeth of the external gear ring 21 and the corresponding output gear 31 is as follows: 2.2:1, 1.29:1, 0.79: 1. 0.49: 1; the ratios of the external teeth of the outer ring gear 21 to the corresponding output gear 31 at a module of 1 are 90:198, 122:158, 156:124, 187:93, respectively. And when the sun gear 24 of the second module has 40 teeth and the planet carrier 22 has 120 teeth, and the brake acts to make the outer gear ring 21 stationary, the speed ratio of the input power to the planet carrier 22 is 3:1, the gear ratio of the planet carrier 22 on the input shaft 1 and the output gear 31 on the output shaft 3 corresponding to each other is 1:1, and the number of teeth is 140:140 when the modulus is 1. If the speed ratio of the first group of modules is 4.4:1 when the engine rotates at 1500, the output speed of the output shaft 3 is 341, and the like, the functions of four-gear speed change and reverse rotation reverse gear are realized.

A hydraulic torque converter 5 is arranged between the output gears 31 on the output shaft 3 to improve the comfort of congested road sections and reduce the frequent action of the brake mechanism 4; the comfort mode and the sport mode can be realized by switching the time of the brake mechanism 4.

As shown in fig. 16, further, the input shaft 1 includes a driving shaft 11 and a driven shaft 14, a multi-shaft transmission is realized by the cooperation of a driving gear 111 on the driving shaft 11 and a driven gear 141 on the driven shaft 14, and modular units are arranged on the driven shaft 14 and the output shaft 3 for speed change or reverse rotation, so as to achieve control of more gears.

It can be specifically understood that: the driving shaft 11 transmits power to the driven shaft 14, the driven shaft 14 is matched with the output shaft 3 through the driven gear 141 and the output gear 31, different rotation number adjustment is achieved through different gear ratios of the output gear 31, the driven shaft 14 can be arranged in a plurality of modes, and the modules are arranged on the driven shaft for speed change, so that control of more gears is achieved.

For example: a driving shaft 11 and a driving gear 111 are arranged to be matched with a driven shaft gear I and a driven shaft gear II on a driven shaft I12 and a driven shaft II 13, the driven shaft I12 and the driven shaft II 13 are matched with an output gear 31 through a planet gear assembly 2 of the module I to form a module I with 6 different speed ratios, and a module II enabling the rotation direction to be opposite, if the driving shaft 11 gear and two driven gears are both gears with the module number of 1 and the tooth number of 145, the speed ratios of the driving shaft 11 gear and the driven shafts are all 1:1, the rotating speed is unchanged, the tooth number of a sun gear 24 of the module I is 40, the tooth number of an inner tooth of a gear ring is 80, the speed ratios are all 2:1, and when the module is 1, the outer tooth number 21 and the tooth number of an output gear 31 of 3 modules I formed by gears on the driven shaft 1' and an output shaft 3 are respectively A (90,198), B (122,158), C (156,124), b (1.29:1), C (0.79: 1); the number of teeth of 3 modules, namely an outer gear ring 21 and an output gear 31, which are formed by gears on the driven shaft 1' and the output shaft 3 is A1(102,198), B1(142,158) and C1(179,124), and the speed ratios are A1(1.94:1), B1(1.11:1) and C1(0.69: 1); thus, the ratio progression of the first 6 sets of modules from input shaft 1 to output shaft 3 is A (4.4:1) A1 (3.88: 1) B (2.58:1) B1(2.22:1) C (1.58:1) C1(1.38:1), respectively. The gears on the driven shaft 1' and the output shaft 3 also form a module II to realize the speed ratio with opposite rotation directions, the sun gear 24 in the module II is 40 teeth, the planet gear 23 is 120 teeth, the speed ratio is 3:1, when the modulus is 1, the output gear 31 externally connected with the planet gear carrier 22 in the module II and the corresponding gear teeth on the output shaft 3 are D (140 ), and the speed ratio is 1: 1. Thus the reverse speed ratio of input shaft 1 to output shaft 3 is 3: 1. Therefore, when the braking mechanism 4 in any one of the 6 modules I and the 1 module II acts, a different speed ratio can be realized, and the speed control of more gears can be realized.

When the speed changing system of the present invention works, as shown in fig. 16 as an example, the specific working process is as follows: the power is transmitted from the driving shaft 11 and the driving gear 111 to the driven shafts one 12 and two 13, the first gear D1, the second gear D2, the third gear D3, the fourth gear D4, the fifth gear D5 and the sixth gear D6 through the driven gears one 121 and two 131, and the power is transmitted in the form of the module one, namely the sun gear 24 of the first gear D1, the third gear D3 and the fifth gear D5 rotates when the power reaches the driven shaft one 12, the sun gear 24 of the second gear D2, the fourth gear D4 and the sixth gear D6 rotates when the power reaches the driven shaft two 13, because the outer ring gears 21 of the module one are all meshed with the gear of the loaded output shaft 3, the power runs on the planet carrier 22 of the module one in an idle rotation mode, and the braking mechanisms 4 in the module one six can only have one action at the same time. The specific situation when each gear is operated during the gear shifting process of the same-direction gear shifting is as follows:

the brake mechanism 4 in the first gear D1 actuates the carrier 22 to lock, and power is transmitted from the outer ring gear 21 in the first gear D1 to the output gear 31 in the first gear D1, so that the output shaft 3 rotates at the speed of the first gear D1.

The brake mechanism 4 in the second gear D2 operates the carrier 22 to lock (the brake mechanism 4 in the first gear D1 stops operating), power is transmitted from the outer ring gear 21 in the second gear D2 to the output gear 31 in the second gear D2, and the output shaft 3 rotates at the speed of the second gear D2.

The brake mechanism 4 in the third gear D3 operates the carrier 22 to lock (the brake mechanism 4 in the second gear D2 stops operating), power is transmitted from the outer ring gear 21 in the third gear D3 to the output gear 31 of the third gear D3, and the output shaft 3 rotates at the speed of the third gear D3.

The brake mechanism 4 in the fourth gear D4 operates to lock the carrier 22 (the brake mechanism 4 in the third gear D3 stops operating), power is transmitted from the outer ring gear 21 in the fourth gear D4 to the output gear 31 of the fourth gear D4, and the output shaft 3 rotates at the speed of the fourth gear D4.

The brake mechanism 4 in the fifth gear D5 operates to lock the carrier 22 (the brake mechanism 4 in the fourth gear D4 stops operating), power is transmitted from the outer ring gear 21 in the fifth gear D5 to the output gear 31 of the fifth gear D5, and the output shaft 3 rotates at the speed of the fifth gear D5.

The brake mechanism 4 in the sixth gear D6 operates to lock the carrier 22 (the brake mechanism 4 in the fifth gear D5 stops operating), power is transmitted from the outer ring gear 21 in the sixth gear D6 to the output gear 31 in the sixth gear D6, and the output shaft 3 rotates at the speed of the sixth gear D6.

When the speed change system changes direction, power is also transmitted from the driven shaft I12 to the sun gear 24 in the module II of the reverse gear R, because the planet gear carrier 22 of the reverse gear R is meshed with the output gear 31 of the reverse gear R, the output shaft 3 has load resistance, the power runs in a no-load rotation mode from the outer gear ring 22 of the reverse gear R, when the brake mechanism 4 externally connected with other gear modules does not act, the brake mechanism 4 in the reverse gear R acts, the power is transmitted to the output gear 31 of the reverse gear R from the outer gear ring 22, and the output shaft 3 changes the rotation direction and runs in the speed and the direction of the reverse gear R.

Furthermore, the gear increase can be single-shaft multi-gear or multi-shaft multi-gear; each of the 6 modules can form a multi-input shaft speed change system of a plurality of input modules through a multi-gear speed change system with single input shaft 1 input formed in parallel, or an output gear 31 on a multi-shaft input common output shaft 3.

The modular speed change system provided by the invention forms a whole by adopting a single module or various combination forms for coupling the modules together, has simple structure and stable and reliable performance, can realize linear adjustment of speed according to the action time of the brake mechanism 4 when synchronously increasing the rotating speed, can realize high forward and reverse switching speed at the same time, and has the characteristic of large transmission torque; in the parallel combination mode, each modularized unit does not influence the work of other modules if a component fails during speed change, and the working reliability is higher.

It is to be understood that the present invention has been described with reference to certain embodiments, and that various changes in the features and embodiments, or equivalent substitutions may be made therein by those skilled in the art without departing from the spirit and scope of the invention. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiment disclosed, but that the invention will include all embodiments falling within the scope of the appended claims.

Claims (11)

1. A modular speed change system, characterized in that it comprises a planetary wheel assembly (2) coupled with a braking mechanism (4), an input shaft (1), an output shaft (3), an output gear (31) forming a modular unit; an input shaft of the module unit is coupled with an output gear (31) through a planet wheel assembly (2), and then power is transmitted to an output shaft (3) through controlling the action of a braking mechanism (4), so that the purpose of power transmission is achieved; the planet wheel assembly (2) comprises a sun wheel (21), an outer gear ring (21), planet wheels (23) and a planet wheel carrier (22), the periphery of the sun wheel (24) is meshed with the planet wheels (23), the planet wheels (23) are also meshed with the inner teeth of the outer gear ring (22), the planet wheels (23) are connected with the planet wheel carrier (22), so that the planet wheels (23) can rotate and revolve around the sun wheel (24) in the outer gear ring (21) to further drive the planet wheel carrier (22) to rotate.

2. A modular transmission system as claimed in claim 1, characterized in that the modular unit is a first module, the input shaft (1) of which is coupled to the sun gear (24) for power input; the outer gear ring (21) is coupled with an output gear (31) to output power; the planet wheel carrier (22) is coupled with the brake mechanism (4), and the change of the output torque is realized through the action of the brake mechanism (4).

3. A modular transmission system according to claim 1, wherein the modular unit is a second module, and the input shaft (1) of the second module is coupled with a sun gear (24) to input power; the planet carrier (22) is coupled with the output gear (31) to output power; the outer gear ring (21) is coupled with the brake mechanism (4), and the change of the output torque is realized through the action of the brake mechanism (4).

4. A modular gear change system according to claim 1, characterized in that the modular unit is a third module, the input shaft (1) of which is coupled to the planet wheel carrier (22) for power input; the sun gear (24) is coupled with the output gear (31) to output power; the outer gear ring (21) is coupled with the brake mechanism (4), and the change of the output torque is realized through the action of the brake mechanism (4).

5. A modular gear change system according to claim 1, characterized in that the modular unit is module four, the input shaft (1) of which is coupled to the planet wheel carrier (22) for power input; the outer gear ring (21) is coupled with an output gear (31) to output power; the sun gear (24) is coupled with the brake mechanism (4), and the change of the output torque is realized through the action of the brake mechanism (4).

6. A modular transmission system according to claim 1, characterized in that the modular unit is a module five, the input shaft (1) of which is coupled with an external ring gear (21) for power input; the planet carrier (22) is coupled with the output gear (31) to output power; the sun gear (24) extends out of the planet carrier (22) and is coupled with the brake mechanism (4), and the change of the output torque is realized through the action of the brake mechanism (4).

7. A modular transmission system as claimed in claim 1, characterized in that the modular unit is a module six, the input shaft (1) of which is coupled with an external ring gear (21) to input power; the sun gear (24) is coupled with the output gear (31) to output power; the planet wheel carrier (22) is coupled with the brake mechanism (4), and the change of the output torque is realized through the action of the brake mechanism (4).

8. A modular speed-change system according to any one of claims 2-7, characterised in that the output shaft (3) is provided with at least 2 output gears (31), and that the input shaft is provided with at least 2 sets of planet wheel assemblies (2) of the same module corresponding to the output gears (31) for cooperation with a brake mechanism (4) for effecting speed increase and decrease and speed control in gear.

9. A modular gear shift system according to any one of claims 2-7, characterized in that the input shaft (1) and the output shaft (3) are provided with a module I and a module II, a module III and a module IV, or a module V and a module VI, and the combination of each two groups of modules and the brake mechanism (4) in the corresponding module cooperate to form a structure with variable forward and reverse rotation directions and variable rotation speed.

10. A modular gear shift system according to any of claims 2-7, characterized in that at least two sets of modules I and II, or at least two sets of modules III and one set of modules IV, or at least two sets of modules V and one set of modules VI are arranged on the input shaft (1) and the output shaft (3), and after combination, they are mutually matched with the brake mechanism (4) in the corresponding modules to achieve forward and reverse speed control according to the gear.

11. The modular speed change system as claimed in claim 1, wherein the input shaft (1) comprises a driving shaft (11) and a driven shaft (14), multi-shaft transmission is realized by matching the driving shaft (11) and the driven shaft (14), and one or more groups of modular units are arranged on the driven shaft (14) and the output shaft (3) for speed change or reverse rotation, so as to achieve control of more gears.

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