CN114789813A - Planetary gear drive mechanism and tobacco bale conveying and steering device - Google Patents

Abstract

The invention relates to a planetary gear driving mechanism and a tobacco bale conveying and steering device, which comprise 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 assembly, wherein the first shaft can rotate, the first internal gear is fixed, the first external gear is meshed with the first internal gear, and the transmission ratio is N: n +1, the second shaft and the coaxial rigid coupling of first external gear, the second shaft has wheel base L with the first shaft, the crank is connected the first shaft and second shaft, the second internal gear is rotatable, the rotatable cup joint in the second shaft of second external gear, the meshing of second external gear and second internal gear and drive ratio are N: n +1, the bracket is fixedly connected with a second external gear, and a second shaft drives the output shaft to rotate through the output first transmission gear and the second transmission gear; the motion compensation assembly drives the second internal gear to rotate, and the axis of the output shaft penetrates through a motion base point on the second internal gear.

Description

Planetary gear drive mechanism and tobacco bale conveying and steering device

Technical Field

The invention relates to the field of tobacco manufacturing machinery, in particular to a planetary gear driving mechanism and a tobacco bale conveying and steering device.

Background

Taking a double channel as an example, in the prior art, as shown in fig. 1, the conveying and turning process of cigarette packets is as follows: the label paper packing machine 01 conveys the cigarette packets on the two channels to the position of the cigarette packet conveying and steering device 03 through the cigarette packet straight-going conveying belt 02; the cigarette packet conveying and steering device 03 receives the cigarette packets 06, presses the received cigarette packets 06 to the cigarette packet transverse conveying belt 04 below, and the cigarette packets are conveyed to the outer box transparent paper packaging machine 05 by the conveying belt 04.

Referring to fig. 2, fig. 2 is a schematic motion diagram of a star wheel with six-station teeth of a cigarette packet conveying and steering device, the star wheel 07 rotates clockwise all the time, and when in a position a, the star wheel 07 rotates clockwise and the rotation center position starts to move downwards at the same time, and the received cigarette packet 06 starts to be pressed downwards onto a cigarette packet transverse conveying belt; in the position b, the star wheel 07 continues the movement, presses the cigarette packet 06 down for a certain distance, but the cigarette packet 06 on the right side is kept still under the blockage of the cigarette packet 06 on the left side, so that the cigarette packet conveyed by the cigarette packet straight-moving conveying belt 02 is temporarily stopped and can only move intermittently; when the star wheel 07 rotates clockwise, the center position of the star wheel 07 starts to move upwards, the cigarette packet 06 on the left side descends by a distance exceeding the height of the cigarette packet, the cigarette packet 06 on the right side moves to a position below the station teeth of the star wheel 07 under the action of the straight-moving conveying belt without the blockage of the cigarette packet 06 on the left side, and the star wheel 07 completes the packet receiving action on the cigarette packet 06; and when the cigarette packet 06 is taken away by the transverse conveying belt at the position d, the conveying and steering of the cigarette packet 06 are completed, the cigarette packet 06 on the right side enters a downward movement state, and the whole movement returns to the state same as the position a and enters the next circulation action, so that a series of cigarette packet conveying and steering actions are realized. To summarize, the star wheel 07 performs an up-and-down reciprocating motion while rotating 60 °.

In order to realize the motion characteristics of the star wheels, the conventional tobacco bale conveying and steering device is realized by a compound mechanism of a planetary gear train and a crank rocker mechanism, the occupied space is large, the sealing and the lubrication cannot be realized, the input tobacco bale can only intermittently move and cannot continuously move, and the tobacco bale is easy to damage.

Disclosure of Invention

In view of the above disadvantages of the prior art, the technical problem to be solved by the present invention is to provide a planetary gear driving mechanism and a cigarette packet conveying and steering device, which have compact structure, small occupied space and continuous motion of reciprocating linear motion, so that the cigarette packet conveying and steering device is not easy to damage the cigarette packet.

In order to achieve the above object, the present invention provides a planetary gear driving mechanism for driving a to-be-driven member to rotate 360 °/N degrees and simultaneously perform a reciprocating linear motion, where N is a positive integer greater than or equal to 2, the planetary gear driving mechanism 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 carrier, a first transmission gear, a second transmission gear, an output shaft, and a motion compensation assembly, the first shaft being rotatably mounted on the base, the first internal gear being fixed on the base and coaxial with the first shaft, the first external gear being engaged with the first internal gear and having a transmission ratio of N: n +1, the second shaft passes first external gear axle center and both rigid couplings, the second shaft parallels with the first shaft and both have wheel base L, crank one end rigid coupling is on the first shaft, the other end is articulated with the second shaft, the second internal gear rotationally installs in the base, the second external gear cup joints on the second shaft coaxially, and can be at the epaxial free rotation of second, the second external gear meshes with the second internal gear and both drive ratios are N: n +1, support fixed connection is in the outer gear end face of second, the coaxial rigid coupling of first drive gear in second axle, the output shaft rotationally installs in the support, and parallels with the second axle, the output shaft be used for with treat driving piece fixed connection, the coaxial rigid coupling of second drive gear in the output shaft, second drive gear and the transmission of first drive gear direct mesh, perhaps through the indirect meshing of the intermediate gear of rotatable installation in the support, the drive ratio of second drive gear and first drive gear is 1: 1; the motion compensation component is in transmission connection with the second internal gear and is used for driving the second internal gear to rotate in the opposite direction of the first shaft, and the rotating speed ratio of the second internal gear to the first shaft is N-1: n + 1; a movement base point which is L away from the axle center of the second external gear is arranged on the second external gear, and the axis of the output shaft penetrates through the movement base point; the second external gear moves the base point in a reciprocating linear motion along the center of the second internal gear when rotating.

Further, the motion compensation assembly comprises a third transmission gear coaxially fixed with the second internal gear and a compensation driving structure for driving the third transmission gear to rotate.

Furthermore, the compensation driving structure comprises a third shaft which is rotatably arranged on the base and a fourth transmission gear which is coaxially and fixedly connected with the third shaft, the fourth transmission gear is meshed with the third transmission gear,

further, the fourth transmission gear and the third transmission gear are external gears, and the transmission ratio of the fourth transmission gear to the third transmission gear is N + 1: n-1.

Further, the linkage assembly is arranged between a third shaft and the first shaft, and the third shaft and the first shaft rotate in the same direction and at the same speed through the linkage assembly.

Further, the linkage assembly comprises a first belt wheel coaxially and fixedly connected to the first shaft, a second belt wheel coaxially and fixedly connected to the third shaft, and a transmission belt connecting the first belt wheel and the second belt wheel, wherein the transmission ratio of the first belt wheel to the second belt wheel is 1: 1.

furthermore, the second transmission gear is indirectly meshed with the first transmission gear through an intermediate gear which is rotatably arranged on the bracket, and the intermediate gear, the second transmission gear and the first transmission gear are external gears.

The invention also provides a cigarette packet conveying and steering device, which comprises a star wheel and the planetary gear driving mechanism, wherein the star wheel is provided with N station teeth, and the star wheel is coaxially and fixedly connected with an output shaft of the planetary gear driving mechanism.

As described above, the planetary gear drive mechanism and the cigarette packet conveying and steering apparatus according to the present invention have the following advantageous effects:

by arranging the base, the first shaft, the crank, the second shaft, the first internal gear, the first external gear, the second internal gear, the second external gear, the support, the first transmission gear, the second transmission gear, the output shaft and the motion compensation assembly, when the device works, the first shaft rotates, the crank can drive the second shaft to revolve, the first external gear revolves in the first internal gear and rotates, the motion compensation assembly moves to drive the second internal gear to rotate, the rotation direction is opposite to that of the first shaft, the second external gear revolves in the second internal gear at the speed of omega, and simultaneously, the rotation at the speed of 2 omega is generated, in the rotation process of the second external gear, the motion base point can do reciprocating linear motion along the vertical direction, and the output shaft and the motion base point are always opposite and do reciprocating linear motion. Meanwhile, the first transmission gear drives the second transmission gear to rotate, the rotation direction and the revolution direction of the first transmission gear are opposite and have a omega/N difference value, the first transmission gear can drive the second transmission gear and the output shaft to rotate at the omega/N speed, when the second shaft and the first transmission gear revolve for one circle, the output shaft just finishes one reciprocating linear motion period, and meanwhile, the rotation angle is 360 degrees/N. The planetary gear driving mechanism has the advantages of compact structure, small occupied space, capability of continuously moving in reciprocating linear motion, adoption of a gear pair as a key motion structure, and capability of adopting good sealing lubrication. The cigarette packet conveying and steering device adopting the planetary gear drive mechanism can continuously move the input straight cigarette packet, is beneficial to cutting carton packages and also reduces the probability of cigarette packet blockage.

Drawings

Fig. 1 is a schematic working diagram of a cigarette packet conveying and turning process in the prior art.

Fig. 2 is a working schematic of a star wheel in the existing cigarette packet conveying and steering device.

Fig. 3 is a schematic view of the planetary gear drive mechanism of the present invention.

Fig. 4 is a side cross-sectional view of the planetary gear drive mechanism of the present invention.

FIG. 5 is a schematic diagram of the operation of the second external gear and the second internal gear of the present invention.

Fig. 6 is a schematic working diagram of the cigarette packet input to the star wheel of the cigarette packet conveying and steering device in an inclined angle mode.

Description of the element reference numerals

01 trademark paper packing machine

02 tobacco bale craspedodrome conveyer belt

03 tobacco bale conveying and steering device

04 cigarette packet transverse conveyer belt

05 box external transparent paper packaging machine

06 cigarette packet

07 star wheel

1 base

2 third axis

3 first shaft

4 second belt wheel

5 first pulley

6 driving belt

7 crank

8 first external gear

9 first internal gear

10 second external gear

11 second internal gear

12 third transmission gear

13 fourth driving gear

14 second axis

15 support

16 first transmission gear

17 second transmission gear

18 intermediate gear

19 Star wheel

20 output shaft

Detailed Description

The following description of the embodiments of the present invention is provided for illustrative purposes, and other advantages and effects of the present invention will become apparent to those skilled in the art from the present disclosure.

It should be understood that the structures, proportions, and dimensions shown in the drawings and described in the specification are for illustrative purposes only and are not intended to limit the scope of the present invention, which is defined by the claims. In addition, the terms such as "upper", "lower", "left", "right", "middle", etc. used in the present specification are for convenience of description, and are not intended to limit the scope of the present invention, and the relative relationship between the terms and the terms may be changed or adjusted without substantial technical change.

Referring to fig. 3 to 5, the present invention provides a planetary gear driving mechanism for driving a to-be-driven member to rotate 360 °/N degrees and perform a reciprocating linear motion, where N is a positive integer greater than or equal to 2, for example, the to-be-driven member may be a star wheel 19 in a cigarette packet conveying and steering device, the star wheel 19 has N station teeth, and in operation, the star wheel 19 is required to perform a reciprocating linear motion while rotating 360 °/N degrees.

The planetary gear driving mechanism comprises 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 support 15, a first transmission gear 16, a second transmission gear 17, an output shaft 20 and a motion compensation assembly, wherein the first shaft 3 is rotatably arranged on the base 1 (only a partial structure is shown as an illustration in fig. 4), the first internal gear 9 is fixed on 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 first external gear to the first internal gear 9 is N: n +1, the second axle 14 passes 8 axle centers of first external gear and both rigid couplings, the second axle 14 is parallel with the first axle 3 and both have wheel base L, 7 one end rigid couplings of crank are on the first axle 3, the other end is articulated with the second axle 14, second internal gear 11 rotationally installs in base 1, second external gear 10 cup joints on the second axle 14 coaxially, and can freely rotate on the second axle 14, second external gear 10 meshes and both drive ratios are N with second internal gear 11: 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 and fixedly connected 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 a to-be-driven member, the second transmission gear 17 is coaxially and fixedly connected to the output shaft 20, the second transmission gear 17 is directly meshed with the first transmission gear 16 for transmission or indirectly meshed with the intermediate gear 18 rotatably mounted on the bracket 15, and the transmission ratio of the second transmission gear 17 to the first transmission gear 16 is 1: 1; the motion compensation component is in transmission connection with the second internal gear 11 and is used for driving the second internal gear 11 to rotate reversely with the first shaft 3, and the rotating speed ratio of the second internal gear 11 to the first shaft 3 is N-1: n + 1; a movement base point which is at a distance L from the axis of the second external gear 10 is arranged on the second external gear 10, and the axis of the output shaft 20 passes through the movement base point; the second external gear 10 reciprocates linearly with its base point along the center of the second internal gear 11 while rotating.

The basic working principle of the planetary gear driving mechanism provided by the invention is as follows: in operation, the first shaft 3 is a 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, the second shaft 14 drives the first external gear 8 to revolve in the first internal gear 9, the first external gear 8 rotates at the same time, referring to fig. 3 and 4, when viewed from the left side, the first shaft 3 is set to rotate counterclockwise, the rotation speed is ω, the second shaft 14 and the first external gear 8 revolve counterclockwise synchronously, and the rotation speed is ω, and the second shaft 14 and the first external gear 8 rotate clockwise, the rotation speed is (N +1) × ω/N, and the second shaft 14 drives the second external gear 10 to revolve counterclockwise, and the rotation speed is ω, and at the same time, the motion compensation component acts to drive the second internal gear 11 to rotate, and the rotation direction is opposite to that of the first shaft 3, that is, the second internal gear 11 rotates clockwise, the rotation speed is [ (N-1)/(N +1) ]. omega., and at this time, the second external gear 10 is in the second internal gear 11 as shown in fig. 5, the second internal gear 11 rotates clockwise, the axis thereof is O1, wherein O2 is the axis of the second external gear 10, the distance between the axis O1 and the axis O2 is L, the second external gear 10 revolves around O1 in the second internal gear 11 at the speed of omega while generating rotation at the speed of 2 omega, the point X is the base point of motion, the distance between the point X and the axis O1 of the second internal gear 11 is L, the base point of motion is set according to the assembly position of the second external gear 10 and the second internal gear 11, and referring to the position shown in fig. 5(a), when the second external gear 10 is located at the top position of the second internal gear 11, that is, when the axis O2 is located directly above the axis O1, the base point X is located directly above the axis O1. In the process of rotating the second external gear 10, the rotation speed 2 ω is twice the revolution speed ω, the movement base point X will make reciprocating linear movement along the vertical direction with the axis O1 as the center point, since the bracket 15 is fixed to the second external gear 10, both of them are moving synchronously, and the axis of the output shaft 20 is located on the movement base point X, the output shaft 20 and the movement base point X will keep always opposite, and also make reciprocating linear movement with the axis O1 as the center point, the distance between the uppermost position and the lowermost position is 4L, meanwhile, the first transmission gear 16 directly or indirectly engages to drive the second transmission gear 17 to rotate, the first transmission gear 16 and the second shaft 14 move completely synchronously, since the rotation speed and the revolution speed of the second shaft 14 and the first transmission gear 16 are (N +1) ω/N and ω respectively, the directions are opposite, and there is a difference of ω/N, the first transmission gear 16 drives the second transmission gear 17 and the output shaft 20 to rotate at the speed of omega/N. Referring to the process shown in fig. 5, when the second external gear 10 revolves one revolution, that is, the second shaft 14 and the first transmission gear 16 revolve one revolution, the output shaft 20 just completes one cycle of reciprocating linear motion, and the rotation angle is 360 °/N, and when N is 6, the rotation angle is 60 °.

The planetary gear driving mechanism has the advantages of compact structure, small occupied space and continuous motion due to reciprocating linear motion. And moreover, a key movement structure adopts a gear pair, and good sealing lubrication can be adopted.

In the present embodiment, referring to fig. 3 and fig. 4, as a preferable design, the second transmission gear 17 and the first transmission gear 16 are in indirect meshing transmission through an intermediate gear 18, the intermediate gear 18 is rotatably mounted on the bracket 15 through a pin, during the operation, the intermediate gear 18 moves along with the bracket 15 and simultaneously freely rotates, and the positions of the intermediate gear 18, the second transmission gear 17 and the first transmission gear 16 are fixed and can be always kept in meshing. Because the center distance between the second transmission gear 17 and the first transmission gear 16 is generally smaller, the intermediate gear 18 is adopted for transmission, and the design and the installation are convenient. Of course, in other embodiments, when the stroke of the reciprocating linear motion 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, and the second transmission gear 17 and the first transmission gear 16 may also be directly meshed if the size allows. In the present embodiment, referring to fig. 3 and 4, the intermediate gear 18, the second transmission gear 17, and the first transmission gear 16 are all external gears, and the rotation directions of the second transmission gear 17 and the first transmission gear 16 are the same. Of course, under appropriate conditions, the second transmission gear 17, the first transmission gear 16 and the intermediate gear 18 are also engaged by an internal gear, or the internal gear and the external gear are combined, so that the function of driving the second transmission gear 17 to rotate at the speed of ω/N is required to be realized.

In the present embodiment, referring to fig. 2 and 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 driving structure for driving the third transmission gear 12 to rotate, wherein 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, and the fourth transmission gear 13 is engaged with the third transmission gear 12, and in operation, while driving the first shaft 3, the third shaft 2 is driven to rotate at a proper speed, and the fourth transmission gear 13 drives the third transmission gear 12 to rotate clockwise at a rotation speed of [ (N-1)/(N +1) ], i.e. the second internal gear 11 can rotate clockwise at a rotation speed of [ (N-1)/(N +1) ], i.

In the present embodiment, further, referring to fig. 2 and 3, the fourth transmission gear 13 and the third transmission gear 12 are external gears, the rotation directions of the two are opposite, and the transmission ratio of the fourth transmission gear 13 to 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 the rotational speed of [ (N-1)/(N +1) ] × ω. Preferably, a linkage assembly is arranged between the third shaft 2 and the first shaft 3, the third shaft 2 and the first shaft 3 are kept synchronously rotating at the same speed and in the same direction through the linkage assembly, wherein the linkage assembly comprises a first belt pulley 5 coaxially fixedly connected to the first shaft 3, a second belt pulley 4 coaxially fixedly connected to the third shaft 2, and a transmission belt 6 connecting the first belt pulley 5 and the second belt pulley 4, and the transmission ratio of the first belt pulley 5 to the second belt pulley 4 is 1: 1, during the work, only need drive one of first axle 3 and third axle 2 anticlockwise rotation, consequently only need set up power supplies such as a motor to drive can. Of course, the linkage assembly may be configured in other suitable transmission configurations.

The invention also provides a cigarette packet conveying and steering device, which comprises a star wheel 19, wherein N station teeth are arranged on the star wheel 19, the cigarette packet conveying and steering device also comprises the planetary gear driving mechanism, and the star wheel 19 is coaxially and fixedly connected with an output shaft 20 of the planetary gear driving mechanism, as shown in the figure 2 and the figure 3. The number of station teeth N on the star wheel 19 is 6. Each star wheel 19 is driven by a planetary gear drive, and for a double-channel tobacco packaging machine, if two star wheels 19 are simultaneously in operation, two planetary gear drives are provided for each drive. In operation, the star wheel 19 completes a reciprocating linear motion cycle, and the motion conditions of key moving parts in the planetary gear driving mechanism and the star wheel 19 are shown as follows:

the counterclockwise direction and the clockwise direction in the above table are directions viewed from the left side (the side on which the star wheel 19 is located) in fig. 3 and 4.

Referring to fig. 6, when the cigarette packet conveying and steering device of the present invention is used, the cigarette packet 20 conveyed to the star wheel 19 by the cigarette packet straight conveyer belt is conveyed to the lower part of the star wheel 19 at an inclined angle, rather than being conveyed from a horizontal angle in the existing design, the inclined angle between the conveying direction of the cigarette packet 20 and the horizontal direction is determined according to the station tooth shape of the star wheel 19, in this way, referring to the schematic diagram from position a to position b in fig. 6, when the cigarette packet 20 at the front side (left side of the drawing in fig. 6) along the conveying direction is pressed down by the station tooth of the star wheel 19, a certain deflection occurs, and the rear end of the cigarette packet can leave from the front end of the next cigarette packet 20 in time, so that the movement of the next cigarette packet 20 is not influenced, so that the cigarette packet 20 continuously moves on the cigarette packet straight conveyer belt 02, the speed is not changed, so that the risk of cigarette packet 20 blockage can be reduced, correspondingly, the star wheel 19 can work continuously, namely, the planetary gear driving mechanism can be subjected to continuous constant-speed power input.

The planetary gear driving mechanism is not only applied to a cigarette packet conveying and steering device to drive the star wheel 19 to move, but also can be applied to other mechanical equipment to drive a to-be-driven piece to rotate 360 DEG/N and complete reciprocating linear motion.

Therefore, the planetary gear driving mechanism and the cigarette packet conveying and steering device have the following beneficial effects:

1. the planetary gear driving mechanism has a compact structure, occupies a small space, and can continuously move in a reciprocating linear motion.

2. The key transmission structure adopts a gear pair, reliable sealing 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 sealing lubrication, the first transmission gear 16, the second transmission gear 17 and the intermediate gear 18 can be installed in a support for sealing lubrication, the whole mechanism is more stable and reliable in motion, and the service life is long.

3. The tobacco bale conveying and steering device with the planetary gear driving mechanism has the advantages that the input straight tobacco bale can continuously move, the cutting of carton packages is facilitated, and the probability of tobacco bale blockage is reduced.

In conclusion, the present invention effectively overcomes various disadvantages of the prior art and has high industrial utility value.

The foregoing embodiments are merely illustrative of the principles and utilities of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or change the above-mentioned embodiments without departing from the spirit and scope of the present invention. Accordingly, it is intended that all equivalent modifications or changes which can be made by those skilled in the art without departing from the spirit and technical spirit of the present invention be covered by the claims of the present invention.

Claims (8)

1. A planetary gear driving mechanism is used for driving a to-be-driven piece to rotate 360 DEG/N degrees and complete a reciprocating linear motion, wherein N is a positive integer greater than or equal to 2, and the planetary gear driving mechanism is characterized in that: planetary gear actuating mechanism includes base (1), primary shaft (3), crank (7), secondary shaft (14), first internal gear (9), first external gear (8), second internal gear (11), second external gear (10), support (15), first transmission gear (16), second transmission gear (17), output shaft (20) and motion compensation subassembly, primary shaft (3) rotationally installs in base (1), first internal gear (9) are fixed in base (1) and coaxial with primary shaft (3), first external gear (8) and first internal gear (9) meshing and both drive ratios are N: n +1, second axle (14) pass first external gear (8) axle center and both rigid couplings, second axle (14) and first axle (3) parallel and both have wheel base L, crank (7) one end rigid coupling is on first axle (3), the other end is articulated with second axle (14), second internal gear (11) rotationally install in base (1), second external gear (10) cup joint on second axle (14) coaxially, and can be on second axle (14) free rotation, second external gear (10) and second internal gear (11) meshing and both drive ratios are N: n +1, support (15) fixed connection is in second external gear (10) terminal surface, the coaxial rigid coupling of first drive gear (16) in second axle (14), output shaft (20) rotationally install in support (15), and parallel with second axle (14), output shaft (20) are used for with treat driving piece fixed connection, the coaxial rigid coupling of second drive gear (17) in output shaft (20), second drive gear (17) and first drive gear (16) direct mesh transmission, perhaps through rotatable intermediate gear (18) indirect meshing of installing in support (15), the drive ratio of second drive gear (17) and first drive 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) and the first shaft (3) to rotate reversely, and the rotating speed ratio of the second internal gear (11) to the first shaft (3) is N-1: n + 1; a movement base point which is L away from the axle center of the second external gear (10) is arranged on the second external gear, and the axis of the output shaft (20) penetrates through the movement base point; the second external gear (10) moves a base point in a reciprocating linear motion along the center of the second internal gear (11) when rotating.

2. The planetary gear drive mechanism according to claim 1, wherein: the motion compensation assembly comprises a third transmission gear (12) coaxially fixed with the second internal gear (11) and a compensation driving structure for driving the third transmission gear (12) to rotate.

3. A planetary gear drive mechanism according to claim 2, wherein: the compensation driving structure comprises a third shaft (2) rotatably mounted on the base (1) and a fourth transmission gear (13) coaxially and fixedly connected to the third shaft (2), and the fourth transmission gear (13) is meshed with the third transmission gear (12).

4. A planetary gear drive as claimed in claim 3, wherein: the fourth transmission gear (13) and the third transmission gear (12) are external gears, and the transmission ratio of the fourth transmission gear (13) to the third transmission gear (12) is N + 1: n-1.

5. The planetary gear drive mechanism according to claim 4, wherein: the connecting device is characterized by further comprising a linkage assembly arranged between the third shaft (2) and the first shaft (3), wherein the third shaft (2) and the first shaft (3) keep rotating in the same direction and at the same speed through the linkage assembly.

6. The planetary gear drive mechanism according to claim 5, wherein: the linkage subassembly includes coaxial rigid coupling in first band pulley (5) of primary shaft (3), coaxial rigid coupling in second band pulley (4) of third axle (2) and drive belt (6) of connecting first band pulley (5) and second band pulley (4), the drive ratio of first band pulley (5) and second band pulley (4) is 1: 1.

7. a planetary gear drive mechanism according to claim 1, wherein: the second transmission gear (17) and the first transmission gear (16) are indirectly meshed through an intermediate gear (18) which is rotatably arranged on the support (15), and the intermediate gear (18), the second transmission gear (17) and the first transmission gear (16) are all external gears.

8. The utility model provides a tobacco bale is carried and is turned to device, includes star gear (19), be equipped with a N station tooth on star gear (19), its characterized in that: further comprising a planetary drive according to any of claims 1 to 7, the star wheel (19) being coaxially fast with the output shaft (20) of the planetary drive.

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