A planetary gear drive mechanism and a cigarette pack conveying and steering device

Abstract

The present invention relates to a planetary gear drive mechanism and a cigarette pack conveying and steering device, including a base, a first shaft, a crank, a second shaft, a first internal gear, a first external gear, a second internal gear, a second external gear, a bracket, a first transmission gear, a second transmission gear, an output shaft, and a motion compensation component. The first shaft is rotatable, the first internal gear is fixed, the first external gear meshes with the first internal gear and the transmission ratio is N:N+1. The second shaft is coaxially fixed to the first external gear, and there is an axial distance L between the second shaft and the first shaft. The crank connects the first shaft and the second shaft. The second internal gear is rotatable, the second external gear is rotatably sleeved on the second shaft, the second external gear meshes with the second internal gear and the transmission ratio is N:N+1. The bracket is fixed to the second external gear, and the second shaft drives the output shaft to rotate through the first transmission gear and the second transmission gear. The motion compensation component drives the second internal gear to rotate, and the axis of the output shaft passes through the motion reference point on the second internal gear.

Description

Technical Field

[0001] The present invention relates to the field of tobacco manufacturing machinery, and particularly relates to a planetary gear drive mechanism and a cigarette packet conveying and steering device. Background Art

[0002] Taking the double-channel as an example, in the prior art, as shown in the appendix Figure 1 The cigarette packet conveying and steering process is as follows: The label paper packaging machine 01 conveys the cigarette packets on two channels to the position of the cigarette packet conveying and steering device 03 through the cigarette packet straight conveyor belt 02; the cigarette packet conveying and steering device 03 catches the cigarette packet 06 and presses the caught cigarette packet 06 onto the lower cigarette packet horizontal conveyor belt 04, and the cigarette packet is conveyed by the conveyor belt 04 into the outer box transparent paper packaging machine 05.

[0003] Refer to the appendix Figure 2 The appendix Figure 2 is the kinematic diagram of the star wheel with six working positions teeth of the cigarette packet conveying and steering device. The star wheel 07 always rotates clockwise. At position a, while the star wheel 07 rotates clockwise, the position of its rotation center starts to move downward, and starts to press the caught cigarette packet 06 downward onto the cigarette packet horizontal conveyor belt; at position b, the star wheel 07 continues the above-mentioned movement and has pressed the cigarette packet 06 down a certain distance, but the cigarette packet 06 on the right remains stationary under the block of the cigarette packet 06 on the left. Therefore, the cigarette packets conveyed by the cigarette packet straight conveyor belt 02 will have a short pause and can only move intermittently; at position c, the star wheel 07 continues to rotate clockwise, and its center position starts to move upward. The cigarette packet 06 on the left has moved downward more than the height of one cigarette packet. Without the block of the cigarette packet 06 on the left, the cigarette packet 06 on the right moves to the position below the working position teeth of the star wheel 07 under the action of the straight conveyor belt, and the star wheel 07 completes the action of catching the cigarette packet 06; at position d, the horizontal conveyor belt has taken away the cigarette packet 06, completing the conveying and steering of the cigarette packet 06, and the cigarette packet 06 on the right enters the downward movement state. The whole movement returns to the same state as position a and enters the next cyclic action, thus realizing a series of cigarette packet conveying and steering actions. Generally speaking, the star wheel 07 completes an up-and-down reciprocating movement while rotating 60°.

[0004] In order to achieve the above-mentioned motion characteristics of the star wheel, currently, the cigarette packet conveying and steering device adopts a composite mechanism of a planetary gear train and a crank-rocker mechanism, which occupies a relatively large space, cannot be sealed and lubricated, and the input cigarette packets can only move intermittently and cannot move continuously, and it is easy to cause damage to the cigarette packets. Summary of the Invention

[0005] In view of the shortcomings of the prior art mentioned above, the technical problem to be solved by the present invention is to provide a planetary gear drive mechanism and a cigarette pack conveying and steering device, which have a compact structure, occupy a relatively small space, and can perform continuous reciprocating linear motion, so that the cigarette pack conveying and steering device is not prone to cigarette pack damage.

[0006] To achieve the above-mentioned purpose, the present invention provides a planetary gear drive mechanism, which is used to drive a driven member to rotate itself by 360° / N angle and complete a reciprocating linear motion at the same time, wherein N is a positive integer greater than or equal to 2, and the planetary gear drive mechanism includes a base, a first shaft, a crank, a second shaft, a first internal gear, a first external gear, a second internal gear, a second external gear, a bracket, a first transmission gear, a second transmission gear, an output shaft, and a motion compensation component, wherein the first shaft is rotatably mounted on the base, the first internal gear is fixed to the base and is coaxial with the first shaft, the first external gear is meshed with the first internal gear and the transmission ratio of the two is N:N+1, the second shaft passes through the axis of the first external gear and the two are fixedly connected, the second shaft is parallel to the first shaft and the two have a wheelbase L, one end of the crank is fixed to the first shaft and the other end is hinged to the second shaft, the second internal gear is rotatably mounted on the base, the second external gear is coaxially sleeved on the second shaft, and can be rotated on the second shaft The second external gear is freely rotated on the upper surface, the second external gear is meshed with the second internal gear and the transmission ratio of the two is N:N+1, the bracket is fixedly connected to the end face of the second external gear, the first transmission gear is coaxially fixed to the second shaft, the output shaft is rotatably mounted on the bracket and is parallel to the second shaft, the output shaft is used to be fixedly connected to the driven member, the second transmission gear is coaxially fixed to the output shaft, the second transmission gear is directly meshed with the first transmission gear for transmission, or is indirectly meshed through an intermediate gear rotatably mounted on the bracket, and the transmission ratio of the second transmission gear to the first transmission gear is 1:1; the motion compensation component is transmission-connected with the second internal gear, and is used to drive the second internal gear to rotate in the opposite direction to the first shaft, and the speed ratio of the second internal gear to the first shaft is N-1:N+1; a motion base point is provided on the second external gear at a distance L from its axis, and the axis of the output shaft passes through the motion base point; when the second external gear rotates, the motion base point reciprocates in a straight line along the center of the second internal gear.

[0007] Furthermore, the motion compensation component includes a third transmission gear coaxially fixed with the second internal gear, and a compensation driving structure driving the third transmission gear to rotate.

[0008] Further, the compensating driving structure includes a third shaft rotatably mounted on the base, and a fourth transmission gear coaxially fixed to the third shaft, wherein the fourth transmission gear meshes with the third transmission gear.

[0009] Further, both the fourth transmission gear and the third transmission gear are external gears, and the transmission ratio between the fourth transmission gear and the third transmission gear is N + 1:N - 1.

[0010] Further, a linkage assembly is further included between the third shaft and the first shaft, and the third shaft rotates in the same direction and at the same speed as the first shaft through the linkage assembly.

[0011] Further, the linkage assembly includes a first pulley coaxially fixed to the first shaft, a second pulley coaxially fixed to the third shaft, and a transmission belt connecting the first pulley and the second pulley, and the transmission ratio between the first pulley and the second pulley is 1:1.

[0012] Further, the second transmission gear and the first transmission gear are indirectly meshed through an intermediate gear rotatably mounted on the bracket, and the intermediate gear, the second transmission gear and the first transmission gear are all external gears.

[0013] The present invention further provides a cigarette packet conveying and steering device, which includes a star wheel, N working teeth are arranged on the star wheel, and the above planetary gear drive mechanism is further included, and the star wheel is coaxially fixed to the output shaft of the planetary gear drive mechanism.

[0014] As described above, the planetary gear drive mechanism and the cigarette packet conveying and steering device involved in the present invention have the following beneficial effects:

[0015] By setting a base, a first shaft, a crank, a second shaft, a first internal gear, a first external gear, a second internal gear, a second external gear, a bracket, a first transmission gear, a second transmission gear, an output shaft, and a motion compensation component, during operation, the first shaft rotates, driving the second shaft to revolve through the crank. The first external gear revolves within the first internal gear while also rotating on its own axis. Meanwhile, the motion compensation component operates to drive the second internal gear to rotate in a direction opposite to that of the first shaft. The second external gear revolves within the second internal gear at an angular velocity of ω and also rotates on its own axis at an angular velocity of 2ω. During the rotation of the second external gear, the motion base point moves in a reciprocating linear motion along the vertical direction. The output shaft always remains relative to the motion base point and also performs a reciprocating linear motion. At the same time, the first transmission gear drives the second transmission gear to rotate. Since the rotation directions of the first transmission gear for revolution and rotation are opposite, with a difference of ω / N, the first transmission gear drives the second transmission gear and the output shaft to rotate on their own axes at an angular velocity of ω / N. When the second shaft and the first transmission gear complete one revolution, the output shaft exactly completes one cycle of reciprocating linear motion, and at the same time, the angle of rotation on its own axis is 360° / N. The planetary gear drive mechanism of the present invention has a compact structure, occupies a relatively small space, and the reciprocating linear motion can be continuous. Moreover, the key motion structure adopts a gear pair, which can be well sealed and lubricated. In the cigarette packet conveying and steering device using the planetary gear drive mechanism, the input straight cigarette packets can move continuously, which is beneficial to the segmentation of carton packaging and also reduces the probability of cigarette packet jams. Description of the Drawings

[0016] Figure 1 It is a working schematic diagram of the cigarette packet conveying and steering process in the prior art.

[0017] Figure 2 It is a working schematic diagram of the star wheel in the prior cigarette packet conveying and steering device.

[0018] Figure 3 It is a structural schematic diagram of the planetary gear drive mechanism of the present invention.

[0019] Figure 4 It is a side sectional view of the planetary gear drive mechanism of the present invention.

[0020] Figure 5 It is a working schematic diagram of the second external gear and the second internal gear in the present invention.

[0021] Figure 6 It is a working schematic diagram of the cigarette packet being input to the star wheel of the cigarette packet conveying and steering device of the present invention at an inclined angle.

[0022] Description of the Reference Numerals of Components

[0023] 01 Labeling Machine

[0024] 02 Straight Cigarette Packet Conveyor Belt

[0025] 03 Cigarette packet conveying and steering device

[0026] 04 Cigarette packet horizontal conveyor belt

[0027] 05 Outer transparent paper packaging machine for cigarette packets

[0028] 06 Cigarette packet

[0029] 07 Star wheel

[0030] 1 Base

[0031] 2 Third shaft

[0032] 3 First shaft

[0033] 4 Second pulley

[0034] 5 First pulley

[0035] 6 Transmission belt

[0036] 7 Crank

[0037] 8 First external gear

[0038] 9 First internal gear

[0039] 10 Second external gear

[0040] 11 Second internal gear

[0041] 12 Third transmission gear

[0042] 13 Fourth transmission gear

[0043] 14 Second shaft

[0044] 15 Bracket

[0045] 16 First transmission gear

[0046] 17 Second transmission gear

[0047] 18 Intermediate gear

[0048] 19 Star wheel

[0049] 20 Output shaft Specific implementation manners

[0050] The following specific embodiments illustrate the implementation manners of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification.

[0051] It should be noted that the structures, proportions, sizes, etc. depicted in the attached drawings of this specification are only used to cooperate with the content disclosed in the specification for those familiar with this technology to understand and read, and are not used to limit the limiting conditions under which the present invention can be implemented. Therefore, they do not have substantial technical significance. Any modification of the structure, change in the proportional relationship, or adjustment of the size, without affecting the efficacy that the present invention can produce and the purpose that can be achieved, should still fall within the scope covered by the technical content disclosed in the present invention. At the same time, the terms such as "upper", "lower", "left", "right", "middle", etc. cited in this specification are also only for the convenience of clear description and are not used to limit the scope under which the present invention can be implemented. The change or adjustment of their relative relationship, without substantial change in the technical content, should also be regarded as the scope under which the present invention can be implemented.

[0052] Refer to Figures 3 to 5 , the present invention provides a planetary gear drive mechanism for driving a driven member to rotate 360° / N angles by itself while completing a reciprocating linear motion, where N is a positive integer greater than or equal to 2. For example, the driven member can be the star wheel 19 in the cigarette pack conveying and steering device. The star wheel 19 has N working teeth. During operation, it is required that the star wheel 19 rotates 360° / N angles by itself while completing a reciprocating linear motion.

[0053] The planetary gear drive mechanism of the present invention includes a base 1, a first shaft 3, a crank 7, a second shaft 14, a first internal gear 9, a first external gear 8, a second internal gear 11, a second external gear 10, a bracket 15, a first transmission gear 16, a second transmission gear 17, an output shaft 20, and a motion compensation component. The first shaft 3 is rotatably installed on the base 1 ( Figure 4Only the local structure is shown as a schematic diagram), the first internal gear 9 is fixed to the base 1 and is coaxial with the first shaft 3, the first external gear 8 is meshed with the first internal gear 9 and the transmission ratio of the two is N:N+1, the second shaft 14 passes through the axis of the first external gear 8 and the two are fixedly connected, the second shaft 14 is parallel to the first shaft 3 and the two have a wheelbase L, one end of the crank 7 is fixed to the first shaft 3, and the other end is hinged to the second shaft 14, the second internal gear 11 is rotatably installed on the base 1, the second external gear 10 is coaxially sleeved on the second shaft 14, and can rotate freely on the second shaft 14, the second external gear 10 is meshed with the second internal gear 11 and the transmission ratio of the two is N:N+1, the bracket 15 is fixedly connected to the end face of the second external gear 10, the first transmission gear 16 is coaxially fixed to the second shaft 14, and the output shaft 20 is rotatably installed The second gear 10 is connected to the bracket 15 and is parallel to the second shaft 14. The output shaft 20 is used to be fixedly connected to the driven member. The second transmission gear 17 is coaxially fixed to the output shaft 20. The second transmission gear 17 is directly meshed with the first transmission gear 16 for transmission, or is indirectly meshed with the intermediate gear 18 rotatably mounted on the bracket 15. The transmission ratio of the second transmission gear 17 to the first transmission gear 16 is 1:1; the motion compensation component is connected to the second internal gear 11 for driving the second internal gear 11 to rotate in the opposite direction to the first shaft 3, and the speed ratio of the second internal gear 11 to the first shaft 3 is N-1:N+1; the second external gear 10 is provided with a motion base point with a distance L from its axis, and the axis of the output shaft 20 passes through the motion base point; when the second external gear 10 rotates, the motion base point reciprocates in a straight line along the center of the second internal gear 11.

[0054] The basic working principle of the planetary gear drive mechanism of the present invention is as follows: when working, the first shaft 3 is the power input shaft. When the first shaft 3 rotates, the crank 7 drives the second shaft 14 to revolve around the axis of the first shaft 3. At the same time, the second shaft 14 drives the first external gear 8 to revolve in the first internal gear 9. At the same time, the first external gear 8 rotates on its own. Figure 3 and Figure 4 , viewed from the left side, set the first shaft 3 to rotate counterclockwise with a speed of ω, then the second shaft 14 and the first external gear 8 will synchronously revolve counterclockwise with a speed of ω, and the second shaft 14 and the first external gear 8 will rotate clockwise with a speed of (N+1)*ω / N, and the second shaft 14 will drive the second external gear 10 to revolve counterclockwise in the second internal gear 11 with a speed of ω. At the same time, the motion compensation component will act to drive the second internal gear 11 to rotate in the opposite direction to the first shaft 3, that is, the second internal gear 11 will rotate clockwise with a speed of [(N-1) / (N+1)]*ω. At this time, the situation of the second external gear 10 in the second internal gear 11 can be seen in Figure 5As shown, the second internal gear 11 rotates clockwise with its axis at O1, where O2 is the axis of the second external gear 10. The distance between the axes O1 and O2 is L. The second external gear 10 revolves counterclockwise around O1 in the second internal gear 11 at a speed of ω, and at the same time, it also rotates with a speed of 2ω. Point X is the motion reference point, and its distance from the axis O1 of the second internal gear 11 is L. The motion reference point is set according to the assembly position of the second external gear 10 and the second internal gear 11. See Figure 5 In the position shown in (A), that is, when the second external gear 10 is located at the top of the second internal gear 11, namely when the axis O2 is directly above the axis O1, the motion reference point X is directly above the axis O1. During the rotation of the second external gear 10, its rotation speed of 2ω is twice the revolution speed of ω. The motion reference point X will move in a reciprocating straight line along the vertical direction with the axis O1 as the center point. Since the bracket 15 is fixed to the second external gear 10 and the two move synchronously, and the axis of the output shaft 20 is located at the motion reference point X, the output shaft 20 always remains relative to the motion reference point X and will also move in a reciprocating straight line with the axis O1 as the center point. The distance between the uppermost position and the lowermost position is 4L. At the same time, the first transmission gear 16 drives the second transmission gear 17 to rotate directly or indirectly in an engaged manner. The first transmission gear 16 moves completely synchronously with the second shaft 14. Since the rotation speed and revolution speed of the second shaft 14 and the first transmission gear 16 are (N + 1)ω / N and ω respectively, and their directions are opposite, with a difference of ω / N, the first transmission gear 16 will drive the second transmission gear 17 and the output shaft 20 to rotate at a speed of ω / N. See Figure 5 In the process shown, when the second external gear 10 makes one revolution, that is, when the second shaft 14 and the first transmission gear 16 make one revolution, the output shaft 20 just completes a reciprocating straight line motion cycle, and at the same time, the rotation angle is 360° / N. When N = 6, the rotation angle is 60°.

[0055] The planetary gear drive mechanism of the present invention has a compact structure, occupies a relatively small space, and the reciprocating straight line motion can be continuous. Moreover, the key motion structure adopts a gear pair, and good sealing and lubrication can be achieved.

[0056] In this embodiment, see Figure 3 and Figure 4, As a preferred design, the second transmission gear 17 and the first transmission gear 16 are indirectly meshed and driven through an intermediate gear 18. The intermediate gear 18 is rotatably mounted on the bracket 15 through a pin shaft. During operation, the intermediate gear 18 moves with the bracket 15 and rotates freely at the same time. The positions of the intermediate gear 18, the second transmission gear 17 and the first transmission gear 16 remain fixed, and they can always remain meshed. Since the center distance between the second transmission gear 17 and the first transmission gear 16 is generally small, the transmission method using the intermediate gear 18 is convenient for design and installation. Of course, in other embodiments, when the reciprocating linear motion stroke of the output shaft 20 is large, the center distance L between the second transmission gear 17 and the first transmission gear 16 is large. When the size permits, the second transmission gear 17 and the first transmission gear 16 can also be directly meshed. In this embodiment, referring to Figure 3 and Figure 4 , the intermediate gear 18, the second transmission gear 17 and the first transmission gear 16 are all external gears, and the self-rotation directions of the second transmission gear 17 and the first transmission gear 16 are the same. Of course, under appropriate circumstances, the second transmission gear 17, the first transmission gear 16 and the intermediate gear 18 can also adopt the meshing method of internal gears, or the combination method of internal and external gears, and it is required to be able to realize the function of driving the second transmission gear 17 to rotate at a speed of ω / N.

[0057] In this embodiment, referring to Figure 2 and Figure 3 , as a preferred design, the motion compensation assembly includes a third transmission gear 12 coaxially fixed with the second internal gear 11, and a compensation drive structure for driving the third transmission gear 12 to rotate. The compensation drive structure includes a third shaft 2 rotatably mounted on the base 1, and a fourth transmission gear 13 coaxially fixed to the third shaft 2. The fourth transmission gear 13 meshes with the third transmission gear 12. During operation, while driving the first shaft 3, the third shaft 2 is driven to rotate at an appropriate speed, and the third transmission gear 12 is driven by the fourth transmission gear 13 to rotate clockwise at a speed of [(N - 1) / (N + 1)]*ω, so that the second internal gear 11 can rotate clockwise at a speed of [(N - 1) / (N + 1)]*ω.

[0058] In this embodiment, further, referring to Figure 2 and Figure 3, the fourth transmission gear 13 and the third transmission gear 12 are both external gears, and their rotation directions are opposite. The transmission ratio between the fourth transmission gear 13 and the third transmission gear 12 is N + 1:N - 1. In this way, when the first shaft 3 and the second shaft 14 rotate in the same direction and at the same speed during operation, the second internal gear 11 can be ensured to rotate clockwise at a speed of [(N - 1) / (N + 1)]*ω. Preferably, a linkage assembly is provided between the third shaft 2 and the first shaft 3. The third shaft 2 is kept rotating synchronously, in the same direction, and at the same speed as the first shaft 3 through the linkage assembly. The linkage assembly includes a first pulley 5 fixedly connected coaxially to the first shaft 3, a second pulley 4 fixedly connected coaxially to the third shaft 2, and a transmission belt 6 connecting the first pulley 5 and the second pulley 4. The transmission ratio between the first pulley 5 and the second pulley 4 is 1:1. During operation, only one of the first shaft 3 and the third shaft 2 needs to be driven counterclockwise, so only one power source such as a motor needs to be provided for driving. Of course, the linkage assembly can also be set as other suitable transmission structures.

[0059] The present invention also provides a cigarette packet conveying and steering device, which includes a star wheel 19. There are N working teeth on the star wheel 19. The device also includes the above planetary gear drive mechanism. The star wheel 19 is fixedly connected coaxially to the output shaft 20 of the planetary gear drive mechanism. Refer to Figure 2 and Figure 3 . Among them, the number of working teeth N on the star wheel 19 is 6. Each star wheel 19 is driven by one planetary gear drive mechanism. For a double-channel tobacco packaging machine, when two star wheels 19 work simultaneously, two planetary gear drive mechanisms are provided for driving respectively. During the working process, in one reciprocating linear motion cycle of the star wheel 19, the motion conditions of the key moving parts in the planetary gear drive mechanism and the star wheel 19 are shown in the following table:

[0060]

[0061] Among them, the counterclockwise and clockwise directions in the above table are the directions observed from the Figure 3 and Figure 4 left side (the side where the star wheel 19 is located).

[0062] Refer to Figure 6 , when the cigarette packet conveying and steering device in the present invention is adopted, the cigarette packets 20 conveyed by the cigarette packet straight conveyor belt to the star wheel 19 are conveyed to the lower part of the star wheel 19 at an inclined angle, rather than being conveyed horizontally as in the existing design. The inclined angle between the conveying direction of the cigarette packets 20 and the horizontal direction is determined according to the shape of the working teeth of the star wheel 19. In this way, refer to Figure 6 the schematic diagram from position a to position b in Figure 6When the cigarette pack 20 on the left side of the drawing (in the middle figure) is pressed down by the working teeth of the star wheel 19, it will deflect to a certain extent, and its rear end can leave the front end of the next cigarette pack 20 in time, so as not to affect the movement of the next cigarette pack 20. In this way, the cigarette pack 20 moves continuously on the straight conveyor belt 02 of the cigarette pack, with a constant speed, which can reduce the risk of blockage of the cigarette pack 20. Correspondingly, the star wheel 19 can work continuously, that is, only a continuous and constant-speed power input is required for the planetary gear drive mechanism.

[0063] The planetary gear drive mechanism of the present invention, in addition to being applied to the cigarette pack conveying and steering device to drive the movement of the star wheel 19, can also be used in other mechanical equipment to drive the driven part to rotate 360° / N angles by itself while completing a reciprocating linear motion.

[0064] As can be seen from the above, the planetary gear drive mechanism and the cigarette pack conveying and steering device of the present invention have the following beneficial effects:

[0065] 1. The planetary gear drive mechanism has a compact structure, occupies a relatively small space, and the reciprocating linear motion can be continuous.

[0066] 2. The key transmission structure adopts a gear pair, and reliable sealed lubrication can be used. The first internal gear 9, the first external gear 8, the second internal gear 11, the second external gear 10, the third transmission gear 12 and the fourth transmission gear 13 can be installed in the base 1 for sealed lubrication. The first transmission gear 16, the second transmission gear 17 and the intermediate gear 18 can be installed in the support for sealed lubrication. The whole mechanism moves more stably and reliably and has a long service life.

[0067] 3. The cigarette pack conveying and steering device with this planetary gear drive mechanism can make the input straight cigarette packs move continuously, which is beneficial to the segmentation of the strip box packaging and also reduces the probability of cigarette pack blockage.

[0068] In summary, the present invention effectively overcomes various disadvantages in the prior art and has high industrial utilization value.

[0069] The above embodiments are only illustrative of the principles and effects of the present invention, and are not used to limit the present invention. Any person familiar with this technology can modify or change the above embodiments without departing from the spirit and scope of the present invention. Therefore, all equivalent modifications or changes made by those with ordinary knowledge in the technical field without departing from the spirit and technical ideas disclosed by the present invention should still be covered by the claims of the present invention.

Claims

1. A planetary gear drive mechanism is used to drive a driven member to rotate 360° / N angles by itself while completing a reciprocating linear motion, where N is a positive integer greater than or equal to 2. Characterized in that: The planetary gear drive mechanism includes a base (1), a first shaft (3), a crank (7), a second shaft (14), a first internal gear (9), a first external gear (8), a second internal gear (11), a second external gear (10), a bracket (15), a first transmission gear (16), a second transmission gear (17), an output shaft (20), and a motion compensation assembly. The first shaft (3) is rotatably mounted on the base (1). The first internal gear (9) is fixed to the base (1) and coaxial with the first shaft (3). The first external gear (8) meshes with the first internal gear (9) and the transmission ratio between the two is N:N + 1. The second shaft (14) passes through the axis of the first external gear (8) and is fixedly connected thereto. The second shaft (14) is parallel to the first shaft (3) and the distance between their axes is L. One end of the crank (7) is fixedly connected to the first shaft (3) and the other end is hinged to the second shaft (14). The second internal gear (11) is rotatably mounted on the base (1). The second external gear (10) is coaxially sleeved on the second shaft (14) and can rotate freely on the second shaft (14). The second external gear (10) meshes with the second internal gear (11) and the transmission ratio between the two is N:N + 1. The bracket (15) is fixedly connected to the end face of the second external gear (10). The first transmission gear (16) is coaxially fixed to the second shaft (14). The output shaft (20) is rotatably mounted on the bracket (15) and is parallel to the second shaft (14). The output shaft (20) is used for fixedly connecting with the component to be driven. The second transmission gear (17) is coaxially fixed to the output shaft (20). The second transmission gear (17) is directly meshed with the first transmission gear (16) for transmission, or indirectly meshed through an intermediate gear (18) rotatably mounted on the bracket (15). The transmission ratio between the second transmission gear (17) and the first transmission gear (16) is 1:

1. The motion compensation assembly is in transmission connection with the second internal gear (11) and is used for driving the second internal gear (11) to rotate in the opposite direction to the first shaft (3), and the rotational speed ratio between the second internal gear (11) and the first shaft (3) is N - 1:N + 1. A motion reference point is provided on the second external gear (10) at a distance L from its axis. The axis of the output shaft (20) passes through the motion reference point. When the second external gear (10) rotates, the motion reference point moves linearly back and forth along the center of the second internal gear (11). The motion compensation assembly includes a third transmission gear (12) coaxially fixed to the second internal gear (11), and a compensation driving structure for driving the third transmission gear (12) to rotate. The compensation driving structure includes a third shaft (2) rotatably mounted on the base (1), and a fourth transmission gear (13) coaxially fixed to the third shaft (2). The fourth transmission gear (13) meshes with the third transmission gear (12). Both the fourth transmission gear (13) and the third transmission gear (12) are external gears, and the transmission ratio between the fourth transmission gear (13) and the third transmission gear (12) is N + 1:N - 1;It further includes a linkage assembly disposed between the third shaft (2) and the first shaft (3), and the third shaft (2) rotates in the same direction and at the same speed as the first shaft (3) through the linkage assembly; the second transmission gear (17) and the first transmission gear (16) are indirectly engaged through an intermediate gear (18) rotatably mounted on the bracket (15), and the intermediate gear (18), the second transmission gear (17) and the first transmission gear (16) are all external gears.

2. The planetary gear drive mechanism according to claim 1, Characterized in that: The linkage assembly includes a first pulley (5) coaxially fixed to the first shaft (3), a second pulley (4) coaxially fixed to the third shaft (2), and a transmission belt (6) connecting the first pulley (5) and the second pulley (4). The transmission ratio of the first pulley (5) and the second pulley (4) is 1:

1.

3. A cigarette pack conveying and steering device includes a star wheel (19), and N working teeth are provided on the star wheel (19). Characterized in that: It further includes the planetary gear drive mechanism according to any one of claims 1 to 2, and the star wheel (19) is coaxially fixed to the output shaft (20) of the planetary gear drive mechanism.

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