TWI416022B - Transmission mechanism having coaxial cam assemblies - Google Patents

Abstract

A transmission mechanism having coaxial cam assemblies is provided and has a first transmission shaft, an inner conjugate cam assembly, an outer conjugate cam assembly, at least one roller wheel assembly, at least one planet carrier and a second transmission shaft. These elements can match with each other to provide various input/output transmission modes for increasing the application variety of the transmission mechanism. Meanwhile, because the installation of these elements has no backlash and abrasion problem existing between traditional gears, it is advantageous to be applied to power transmission of high precision dynamic machines for enhancing the abrasion-resistant strength and transmission precision of the transmission mechanism.

Description

Coaxial cam shifting mechanism

BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a coaxial cam shifting mechanism, and more particularly to a coaxial cam shifting mechanism having a plurality of input/output transmission modes by means of first and second conjugate cam sets and a roller wheel set and a carrier.

A transmission mechanism is a medium mechanism used to change or adjust the output speed of various machine equipment or power equipment. It is also an indispensable mechanism for the transmission, and is used in many powers for production, processing, manufacturing, and transportation. There are different transmission mechanisms and gearbox designs in the machine. For example, in a car or a locomotive, a gearbox with a transmission mechanism is usually provided between the engine and the wheel for deceleration or speed increase, so that the engine can output the power with the appropriate speed by the speed regulation of the transmission mechanism. Turn. Most of the existing transmission mechanisms use ordinary gears to drive the speed of each other, and there are also designs that use planetary gears or cams to drive the speed of each other.

For example, U.S. Patent No. 5,247,847 discloses a Cam Gear Assembly which uses a cam gear and a roller gear to match each other, and thus belongs to a planetary gear transmission. Type of transmission mechanism.

Further, U.S. Patent No. 6,902,507 discloses a Roller Cam Assembly which uses a roller ring and a cam gear to match each other, and thus belongs to another planetary gear transmission type. Transmission mechanism.

In addition, U.S. Patent No. 2,986,949 discloses an indexing cam structure that uses a set of conjugate cams to mate with a set of runners having a plurality of followers, and thus belongs to a type of cam. Transmission type transmission mechanism.

In addition, U.S. Patent No. 6,382,038 discloses a transmission device that uses a set of conjugate gears to mate with a rotating shaft having two cam plates, and thus belongs to a gear and cam combined transmission type transmission mechanism.

All of the above-mentioned existing transmission mechanisms have the function of deceleration or speed increase, but if a higher deceleration or speed increase ratio is to be achieved, the mechanism size will be too large, and if the gear and the gear are meshed with each other, the operation mode must be The problem of backlash error and easy wear between the convex teeth of the two gears is not conducive to the application of high-precision transmission in high-precision power machinery. Moreover, the above various conventional transmission mechanisms have only a single power input end and a power output end design, and cannot select different power input ends and power output ends in the same configuration, thereby relatively narrowing the applicable range.

Therefore, it is still necessary to provide an improved transmission mechanism to solve the problems of the conventional technology.

The main object of the present invention is to provide a coaxial cam shifting mechanism which is configured by a plurality of input/output transmission modes by combining first and second conjugate cam groups and a roller wheel set with a carrier. It is used to increase the application diversity of the transmission mechanism.

A secondary object of the present invention is to provide a coaxial cam shifting mechanism in which the assembly between the first conjugate cam group, the second conjugate cam group and the roller wheel set is free from the mutual engagement between the conventional gear and the gear. The resulting backlash and wear problems are beneficial to the power transmission of high-precision power machinery to improve the wear resistance and transmission accuracy of the transmission mechanism.

Another object of the present invention is to provide a coaxial cam shifting mechanism in which the ratio of the number of blunt teeth of the first cam and the second cam can be adjusted according to the transmission demand, so as to design an appropriate ratio of deceleration or speed increase, thereby facilitating application. In the high-load, high-torque output power machine, to increase the load bearing strength and torque output value of the transmission mechanism.

Another object of the present invention is to provide a coaxial cam shifting mechanism, wherein the first conjugate cam set, the second conjugate cam set and the roller wheel set are relatively simple in construction, and are easily designed to be different in size or different cams. The shape of the face is thus advantageous in reducing manufacturing costs and increasing component design margin.

In order to achieve the above object, the present invention provides a coaxial cam shifting mechanism including: a first transmission shaft; a first conjugate cam set that rotates synchronously with the first transmission shaft and has at least two conjugates combined a first cam, each of the first cams has a first cam surface; a second conjugate cam set, the ring is disposed at a periphery of the first conjugate cam group, and has at least two conjugated second cams, The second cams each have a second cam surface corresponding to the first cam surface; at least one roller wheel set each having at least two roller wheels, each of the roller wheels having a plurality of rollers The roller wheels are respectively disposed between the first and second cam faces and passively rotate between the first and second cam faces; at least one planet carrier, each of which is pivotally supported to support the roller a sub-wheel set; and a second drive shaft that rotates in synchronization with the carrier.

In an embodiment of the invention, the number of the first cam, the second cam, and the roller wheel are equal to each other.

In an embodiment of the present invention, each of the planet carriers has a first bracket and a second bracket, and the two ends of the first bracket are pivotally coupled to the first transmission shaft and the roller wheel set respectively. One side of the second bracket is pivotally connected to the other side of the roller set, and the other end thereof rotates synchronously with the second transmission shaft.

In an embodiment of the invention, each of the roller wheel sets further includes a plurality of rotating disks, which together with the plurality of rollers constitute the at least two roller wheels.

In an embodiment of the present invention, each of the roller sets further includes a rotating shaft, wherein the at least two roller wheels are rotatably disposed on the rotating shaft, and the two ends of the rotating shaft are respectively pivotally connected to the rotating shaft The first and second brackets of the planet carrier.

In an embodiment of the invention, the first transmission shaft is used as a power input end, the second transmission shaft is used as a power output end, and the second conjugate cam group is used as a power output end. Fixed end. A transmission speed ratio of the power output end to the power input end is equal to N1/(N1+N2), wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of blunt teeth of the second cam surface.

In an embodiment of the invention, the second transmission shaft is used as a power input end, the first transmission shaft is used as a power output end, and the second conjugate cam group is used as a power input end. Fixed end. The transmission speed ratio of the power output end to the power input end is equal to (N1+N2)/N1, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of blunt teeth of the second cam surface.

In an embodiment of the invention, the first transmission shaft is used as a power input end, the second conjugate cam group is used as a power output end, and the second transmission shaft is used as a power transmission end. Fixed end. A transmission speed ratio of the power output end to the power input end is equal to N1/N2, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of blunt teeth of the second cam surface.

In an embodiment of the invention, the second transmission shaft is used as a power input end, the second conjugate cam group is used as a power output end, and the first transmission shaft is used as a power transmission end. Fixed end. The transmission speed ratio of the power output end to the power input end is equal to (N1+N2)/N2, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of blunt teeth of the second cam surface.

In an embodiment of the invention, the second conjugate cam group is used as a power input end, the second transmission shaft is used as a power output end, and the first transmission shaft is used as a power transmission end. Fixed end. A transmission speed ratio of the power output end to the power input end is equal to N2 / (N1 + N2), wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of blunt teeth of the second cam surface.

In an embodiment of the invention, the second conjugate cam group is used as a power input end, the first transmission shaft is used as a power output end, and the second transmission shaft is used as a power transmission end. Fixed end. The transmission speed ratio of the power output end to the power input end is equal to N2/N1, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of blunt teeth of the second cam surface.

The above and other objects, features and advantages of the present invention will become more <RTIgt; Furthermore, the directional terms mentioned in the present invention, such as "upper", "lower", "before", "after", "left", "right", "inside", "outside" or "side", etc. Just refer to the direction of the additional schema. Therefore, the directional terminology used is for the purpose of illustration and understanding of the invention.

Referring to Figures 1 and 2, the coaxial cam shifting mechanism of the first embodiment of the present invention can be applied to various power machines, automobiles, locomotives or other power machines as a gearbox or other deceleration/speed increase. A mechanism is used to provide an appropriate deceleration/growth function between a power input and a power wheel outlet. The coaxial cam shifting mechanism of the first embodiment of the present invention mainly comprises: a first drive shaft 1, a first conjugate cam set 2, a second conjugate cam set 3, at least one roller set 4, at least one Planet carrier 5 and a second transmission shaft 6. The present invention will be described in detail below with reference to Figs. 1 to 8 in detail of the detailed construction of the above-described respective elements of the first embodiment and the principle of operation thereof.

Referring to Figures 1, 2 and 3, the first transmission shaft 1 of the first embodiment of the present invention is a shaft made of metal or alloy, wherein one end (outer end) of the first transmission shaft 1 is a product. The design requirement can be selected as a power input end, a power output end or a fixed end, and the other end (inner end) of the first transmission shaft 1 is fixedly coupled to the geometric center position of the first conjugate cam group 2 In order to enable the first transmission shaft 1 to rotate synchronously with the first conjugate cam group 2.

Referring to FIGS. 1, 2 and 3 again, the first conjugate cam set 2 of the first embodiment of the present invention rotates synchronously with the first transmission shaft 1, and the first transmission shaft can be selected according to product design requirements. 1 drives the first conjugate cam group 2 to rotate, or the first conjugate cam group 2 drives the first transmission shaft 1 to rotate. Furthermore, the first conjugate cam set 2 has at least two conjugated first cams 21, 22, which are cam plates made of metal or alloy, which are fixedly coupled to each other and It can rotate synchronously, so it is called "conjugated bonding". In this embodiment, the number of the first cams 21, 22 is two, but it may be three or more. The first cams 21, 22 each have a first cam surface 211, 221 which is an outer peripheral surface similar to a blunt-toothed, wavy or petal-like shape, respectively, which have the same configuration as each other. At the same time, the blunt-toothed sections of the at least two first cam faces 211, 221 are in a staggered relationship with each other, wherein a blunt-toothed section of the first cam surface 211 corresponds to another one. One of the cam faces 221 has a blunt-like section, and the blunt-groove section of the first cam face 211 also corresponds to one of the other cam faces 221.

Referring to Figures 1, 2 and 4 again, the second conjugate cam set 3 of the first embodiment of the present invention is disposed around the periphery of the first conjugate cam set 2, and the second conjugate cam set 3 a second cam 31, 32 having at least two conjugates, the second cams 31, 32 being ring bodies made of metal or alloy, which are fixedly coupled to each other and can rotate synchronously, so called "conjugation" Combine." In the present embodiment, the number of the second cams 31, 32 corresponds to the first cams 21, 22, and is also two, but may be three or more. The second cams 31, 32 each have a second cam surface 311, 321 which is an inner peripheral surface similar to a blunt, wavy or petal shape, respectively, which have the same configuration as each other. At the same time, the blunt-toothed sections of the at least two second cam faces 311, 321 are also in a staggered relationship with each other, wherein one of the blunt-toothed sections of the second cam surface 311 corresponds to the other one. One of the two cam faces 321 is a blunt-like section, and the blunt-groove section of the second cam face 311 also corresponds to one of the blunt-toothed sections of the other second cam face 321 .

Referring to Figures 1, 2 and 5, at least one of the roller sets 4 of the first embodiment of the present invention has at least two roller wheels 41 and a rotating shaft 42, both of which are made of metal or alloy. The number of the roller wheels 41 corresponds to the number of the first cams 21, 22 and the second cams 31, 32, and each of the roller wheels 41 includes a plurality of rollers 411 and a plurality of rotating disks 412. In the present embodiment, the roller wheel set 4 has two roller wheels 41, and the number of the rollers 411 of each of the roller wheels 41 is three, and the two roller wheels 41 share three rotating disks 412. Each of the rollers 411 is rotatably equiangularly arranged and pivoted between two adjacent rotating disks 412. Furthermore, the at least two roller wheels 41 are rotatably disposed on the same rotating shaft 42. The two ends of the rotating shaft 42 are respectively pivotally connected to the carrier 5. The roller wheel 41 and the roller 411 are respectively disposed between the first cam faces 211 and 221 of the first conjugate cam group 2 and the second cam faces 311 and 321 of the second conjugate cam group 3, The first cam faces 211, 221 and the second cam faces 311, 321 are passively rotated. In addition, the rollers 411 of the at least two roller wheels 41 are also arranged in a staggered relationship with each other, and the staggered relationship corresponds to the blunt teeth of the first cam faces 211 and 221 and the second cam faces 321 and 322. The staggered relationship of segments and blunt grooves.

Referring to Figures 1, 2 and 6, the at least one carrier 5 of the first embodiment of the present invention is configured to rotatably pivotally support the rotating shaft 42 and the roller wheel 41 of the roller wheel set 4, Each of the first carrier 51 has a first bracket 51 and a second bracket 52, both of which are made of metal or alloy. The first end 511 and the second end 512 of the first bracket 51 are respectively Rotating pivotally connected to one side of the roller set 4 (ie, one end of the rotating shaft 42) and the first transmission shaft 1, wherein the second end 512 is preferably a bearing (not shown) Rotating pivotally connected to the first transmission shaft 1; at the same time, one of the first ends 521 of the second bracket 52 is pivotally connected to the other side of the roller wheel set 4 (that is, the other end of the rotating shaft 42) And a second end 522 thereof is fixedly coupled to the second transmission shaft 6 and rotatable in synchronization with the second transmission shaft 6.

Referring to Figures 7 and 8, there is shown a schematic operation diagram of the coaxial cam shifting mechanism of the first embodiment of the present invention. As shown in the first, second, seventh and eighth embodiments, in the present embodiment, the first transmission shaft 1 is defined as a power input end, and the second transmission shaft 6 is defined as a power output end. And defining the second conjugate cam group 3 as a fixed end. When the first transmission shaft 1 is driven by an external mechanism (for example, a crankshaft of an engine) to rotate counterclockwise, since the first transmission shaft 1 is fixedly coupled to the first conjugate cam group 2 (as shown in FIG. 1 Therefore, the first conjugate cam set 2 will rotate counterclockwise in synchronization with the first transmission shaft 1. Then, the first cams 21 and 22 of the first conjugate cam group 2 are used to push the three rollers of the two roller wheels 41 of the roller wheel set 4 by the two first cam faces 211 and 221 when rotating. Sub 411. In this way, the roller 411 can rotate clockwise between the two first cam faces 211, 221 and the second cam faces 311, 321 of the second conjugate cam group 3, and along the second and second The cam faces 311, 321 perform counterclockwise planetary motion and can synchronously push the rotating disk 412 to rotate counterclockwise. Subsequently, the roller wheel set 4 can push the second bracket 52 on the other side of the carrier 5 to rotate counterclockwise via the rotating disk 412 and the rotating shaft 42. Since the second end 522 of the second bracket 52 is fixedly coupled to the second transmission shaft 6, the second transmission shaft 6 will be synchronously counterclockwise rotated to drive another external mechanism via the second transmission shaft 6 (eg The wheel) rotates at the adjusted speed.

It should be noted that the transmission speed ratio of the power output end (the second transmission shaft 6) and the power input end (the first transmission shaft 1) is equal to N1/(N1+N2), wherein N1 is the first The number of blunt teeth of the cam faces 211, 221, and N2 are the number of blunt teeth of the second cam faces 311, 321 . For example, in the reference examples of FIGS. 5 and 6, the number of blunt teeth of the first cam faces 211 and 221 is six, and the number of blunt teeth of the second cam faces 311 and 321 is nine, respectively. The power input end (the first transmission shaft 1) transmits power to the power output end (the second transmission shaft 6), and the speed will become 6/(6+9) of the original rotation speed, that is, the transmission mechanism It belongs to a reduction drive design.

In addition, in other embodiments, the present invention may also define the second transmission shaft 6 as a power input end, define the first transmission shaft 1 as a power output end, and define the second conjugate cam. Group 3 is used as a fixed end. At this time, the transmission speed ratio of the power output end (the first transmission shaft 1) and the power input end (the second transmission shaft 6) will become opposite, that is, (N1+N2)/N1, where N1 is The number of blunt teeth of the first cam faces 211, 221, N2 is the number of blunt teeth of the second cam faces 311, 321 . For example, in the reference examples of FIGS. 5 and 6, the transmission speed ratio is (6+9). ) / 6, thus making the transmission a design for a speed increase transmission.

Furthermore, the present invention may also define the first transmission shaft 1 as a power input end, define the second conjugate cam group 3 as a power output end, and define the second transmission shaft 6 as a fixed end. . At this time, the power output end (the second transmission shaft 6) and the power input end (the first transmission shaft 1) have a transmission speed ratio N1/N2, wherein N1 is the bluntness of the first cam surface 211, 221 The number of convex teeth, N2 is the number of blunt teeth of the second cam faces 311, 321 . For example, in the reference examples of FIGS. 5 and 6, the transmission speed ratio is 6/9, thereby making the transmission mechanism a reduction transmission design. .

Alternatively, the present invention may also define the second transmission shaft 6 as a power input end, define the second conjugate cam group 3 as a power output end, and define the first transmission shaft 1 as a fixed end. At this time, the power output end (the second conjugate cam group 3) and the power input end (the second transmission shaft 6) have a transmission speed ratio (N1+N2)/N2, wherein N1 is the first cam The number of blunt teeth of the faces 211, 221, N2 is the number of blunt teeth of the second cam faces 311, 321 , for example, in the reference examples of Figs. 5 and 6, the transmission speed ratio is (6 + 9) / 9, Therefore, the transmission mechanism becomes a speed increasing transmission design.

In addition, the present invention may also define the second conjugate cam set 3 as a power input end, define the second drive shaft 6 as a power output end, and define the first drive shaft 1 as a fixed end. At this time, the power output end (the second transmission shaft 6) and the power input end (the second conjugate cam group 3) have a transmission speed ratio N2 / (N1 + N2), wherein N1 is the first cam The number of blunt teeth of the faces 211 and 221, and N2 is the number of blunt teeth of the second cam faces 311 and 321 . For example, in the reference examples of FIGS. 5 and 6, the transmission speed ratio is 9/(6+9). Thus, the transmission mechanism becomes a reduction transmission design.

In addition, the present invention may also define the second conjugate cam group 3 as a power input end, define the first transmission shaft 1 as a power output end, and define the second transmission shaft 6 as a fixed end. At this time, one of the power output end (the first transmission shaft 1) and the power input end (the second conjugate cam group 3) has a transmission speed ratio N2/N1, wherein N1 is the first cam surface 211, 221 The number of blunt teeth, N2 is the number of blunt teeth of the second cam faces 311, 321 . For example, in the reference examples of FIGS. 5 and 6, the transmission speed ratio is 9/6, thereby making the transmission mechanism an increase. Speed drive design.

Referring to FIG. 9, a schematic diagram of a schematic operation of a coaxial cam shifting mechanism according to a second embodiment of the present invention is disclosed. The second embodiment is similar to the first embodiment of the present invention, and substantially uses the same component name and figure. No., but the difference between the two is characterized by: as shown in FIG. 9 and referring to FIGS. 1 and 2 simultaneously, the coaxial cam shifting mechanism of the second embodiment includes three roller wheel sets 4 and three planet carriers. 5. The coaxial cam shifting mechanism different from the first embodiment includes only one roller wheel set 4 and one planet carrier 5. In the second embodiment, by increasing the number of corresponding groups of the roller wheel set 4 and the carrier 5 to two, three or more, the coaxial cam shifting mechanism can be relatively increased during the transmission period such as deceleration or speed increase. Drive stability and reliability.

As described above, the present invention has the first and second aspects of FIGS. 1 to 8 in comparison with various conventional transmission mechanisms having problems of backlash error and easy wear and which generally have only a single power input/output design. The conjugate cam sets 2, 3 and the roller wheel set 4 are matched with the carrier 5 to form a plurality of input/output transmission modes for selective use, thereby facilitating an increase in the application diversity of the transmission mechanism. Furthermore, the assembly between the first conjugate cam group 2, the second conjugate cam group 3 and the roller wheel set 4 does not have the backlash and wear problems caused by the mutual meshing between the conventional gear and the gear, thereby being advantageous. It is applied to the power transmission of high-precision power machinery to improve the wear resistance and transmission accuracy of the transmission mechanism. In addition, the present invention can selectively adjust the ratio of the number of blunt teeth of the first cams 21, 22 and the second cams 31, 32 according to the transmission requirements, so as to design an appropriate ratio of deceleration or speed increase, thereby facilitating application at high load and high. Torque output in the power machine to increase the load bearing strength and torque output value of the transmission mechanism. In addition, the structures of the first conjugate cam group 2, the second conjugate cam group 3, and the roller wheel set 4 are relatively simple, and are easily changed to be designed to have different sizes or different cam surface shapes, thereby also contributing to reduction in manufacturing cost and Increase component design margins.

The present invention has been disclosed in its preferred embodiments, and is not intended to limit the invention, and the present invention may be modified and modified without departing from the spirit and scope of the invention. The scope of protection is subject to the definition of the scope of the patent application.

1. . . First drive shaft

2. . . First conjugate cam set

twenty one. . . First cam

211. . . First cam surface

221. . . First cam surface

twenty two. . . First cam

3. . . Second conjugate cam set

31. . . Second cam

311. . . Second cam surface

32. . . Second cam

321. . . Second cam surface

4. . . Roller wheel set

41. . . Roller wheel

411. . . Roller

412. . . Rotating disk

42. . . Rotary axis

5. . . Planet carrier

51. . . First bracket

511. . . First end

512. . . Second end

52. . . Second bracket

521. . . First end

522. . . Second end

6. . . Second drive shaft

Fig. 1 is a front elevational view showing the combination of the coaxial cam shifting mechanism of the first embodiment of the present invention.

Fig. 2 is an exploded perspective view showing the coaxial cam shifting mechanism of the first embodiment of the present invention.

Fig. 3 is a partially enlarged view showing the first transmission shaft and the first conjugate cam group of the first embodiment of the present invention.

Fig. 4 is a partially enlarged view showing a second conjugate cam group of the first embodiment of the present invention.

Fig. 5 is a partially enlarged view of the roller wheel set of the first embodiment of the present invention.

Figure 6 is a partial enlarged view of the carrier and the second transmission shaft of the first embodiment of the present invention.

7 and 8 are schematic views showing the operation of the coaxial cam shifting mechanism of the first embodiment of the present invention.

Fig. 9 is a schematic view showing the operation of the coaxial cam shifting mechanism of the second embodiment of the present invention.

1. . . First drive shaft

2. . . First conjugate cam set

3. . . Second conjugate cam set

4. . . Roller wheel set

5. . . Planet carrier

6. . . Second drive shaft

Claims (10)

A coaxial cam shifting mechanism comprising: a first transmission shaft; a first conjugate cam set, rotating synchronously with the first transmission shaft, and having at least two conjugated first cams, the first cams Having a first cam surface having the same configuration with each other, and each having a plurality of blunt teeth and a plurality of blunt grooves, the blunt teeth of the first cam faces being staggered with each other a relationship, wherein a blunt tooth of the first cam surface corresponds to a blunt groove of the other first cam surface; a second conjugate cam set is disposed at a periphery of the first conjugate cam group and has At least two conjugated second cams each having a second cam surface, the second cam faces respectively corresponding to the first cam faces, and the second cam faces having the same configuration with each other, and Each has a plurality of blunt teeth and a plurality of blunt grooves, and the blunt teeth of the second cam faces are in a staggered relationship with each other, wherein one of the second cam faces has a blunt tooth corresponding to the other second a blunt groove of the cam surface; at least one roller wheel set, each having a two roller wheel, each of the roller wheels having a plurality of rollers, the roller wheels being respectively disposed between the first and second cam faces and passively rotating between the first and second cam faces And the rollers of the at least two roller wheels are arranged in a staggered relationship with each other, and the staggered relationship corresponds to a staggered relationship with the blunt teeth and the blunt grooves of the first and second cam faces; at least one planet carrier, each pivotally supporting the roller wheel set; and a second drive shaft, and the planet carrier Rotate synchronously. The coaxial cam shifting mechanism of claim 1, wherein each of the planet carriers has a first bracket and a second bracket, and the two ends of the first bracket are pivotally coupled to the first transmission One side of the shaft and the roller set; one end of the second bracket is rotatably pivoted to the other side of the roller set, and the other end thereof rotates synchronously with the second drive shaft. The coaxial cam shifting mechanism of claim 1, wherein each of the roller sets further comprises a plurality of rotating discs, which together with the plurality of rollers constitute the at least two roller wheels. The coaxial cam shifting mechanism of claim 2, wherein each of the roller sets further comprises a rotating shaft, wherein the at least two roller wheels are rotatably disposed on the rotating shaft, and the rotating shaft The two ends are respectively pivotally connected to the first and second brackets of the carrier. The coaxial cam shifting mechanism of claim 1, wherein the first transmission shaft is used as a power input end, the second transmission shaft is used as a power output end, and the second total The yoke cam set is used as a fixed end, the power A transmission speed ratio of the output end to the power input end is equal to N1/(N1+N2), wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of blunt teeth of the second cam surface. The coaxial cam shifting mechanism of claim 1, wherein the second transmission shaft is used as a power input end, the first transmission shaft is used as a power output end, and the second total The yoke cam set is used as a fixed end, and the transmission speed ratio of the power output end and the power input end is equal to (N1+N2)/N1, wherein N1 is the number of blunt teeth of the first cam surface, N2 Is the number of blunt teeth of the second cam surface. The coaxial cam shifting mechanism of claim 1, wherein the first transmission shaft is used as a power input end, the second conjugate cam group is used as a power output end, and the first The second transmission shaft is used as a fixed end, and the transmission speed ratio of the power output end and the power input end is equal to N1/N2, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the second The number of blunt teeth on the cam surface. The coaxial cam shifting mechanism according to claim 1, wherein the second transmission shaft is used as a power input end, and the second conjugate cam group is used as a power output end, and the first A transmission shaft is used as a fixed end, and a transmission speed ratio of the power output end to the power input end is equal to (N1+N2)/N2, wherein N1 is a blunt convex tooth of the first cam surface The number of N2 is the number of blunt teeth of the second cam surface. The coaxial cam shifting mechanism of claim 1, wherein the second conjugate cam set is used as a power input end, and the second drive shaft is used as a power output end, and the first A transmission shaft is used as a fixed end, and a transmission speed ratio of the power output end to the power input end is equal to N2 / (N1 + N2), wherein N1 is the number of blunt teeth of the first cam surface, N2 Is the number of blunt teeth of the second cam surface. The coaxial cam shifting mechanism of claim 1, wherein the second conjugate cam set is used as a power input end, the first drive shaft is used as a power output end, and the first The second transmission shaft is used as a fixed end, and the transmission speed ratio of the power output end to the power input end is equal to N2/N1, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the second The number of blunt teeth on the cam surface.