Device for converting intermittent movement into continuous movement and cigarette packaging apparatus

Abstract

The utility model belongs to cigarette production technical field discloses a device and cigarette packaging equipment that intermittent motion is converted into continuous motion, the device includes staggered wheel mechanism, transmission shaft, differential mechanism and cam swing lever mechanism, staggered wheel mechanism includes first runner and second runner, first runner and second runner are coaxial and are set in staggered position, differential mechanism includes first differential gear train and second differential gear train, transmission shaft transmission connection between two gear trains, first differential gear train transmission connection in first runner, second differential gear train transmission connection in second runner, cam swing lever mechanism transmission connection in transmission shaft, and transmission connection in first differential gear train's first link and second differential gear train's second link. The device composites the periodic " swing - stop - swing " of cam swing lever mechanism and the continuous circular motion of differential mechanism, forms periodic combination complementary motion, realizes the conversion of the intermittent motion of cigarette push to the continuous motion of cigarette group forming output.

Description

Technical Field

[0001] This utility model relates to the field of cigarette production technology, and in particular to a device for converting intermittent motion into continuous motion and cigarette packaging equipment. Background Technology

[0002] Currently, such as Figures 1 to 3 As shown, the cigarette packing equipment uses a cigarette storage 100 and a certain number of lower cigarette troughs 101 to arrange the cigarettes in a 10-10 (7-6-7 or 7-7-6) pattern. A pusher 102 pushes the cigarettes into empty mold boxes 103 on a synchronous conveyor belt 104 or a rotary wheel 105, forming groups of 20 cigarettes for the next continuous process of inner liner packaging. The cigarette pushing motion is a reciprocating linear motion, while the synchronous conveyor belt 104 or rotary wheel 105 is an intermittent motion. That is, when the pusher 102 pushes the cigarettes, the empty mold box 103 stops; when the pusher 102 returns and stops, the empty mold box 103 moves.

[0003] Currently, cigarette packaging equipment typically uses belt-type radial transmission devices or stepper motors, servo motors, etc., to achieve the conversion from intermittent motion to continuous motion. However, these devices have drawbacks such as large power (torque) loss, low conversion efficiency, and large impact during mechanism operation. As a result, cigarette packaging equipment cannot achieve high-speed, high-efficiency, and stable motion. Furthermore, in actual production, there is a problem of transmission belt deformation, especially changes in length, which affects the running accuracy and causes interference between components.

[0004] Therefore, there is an urgent need for a device and cigarette packaging equipment that can convert intermittent motion into continuous motion to solve the above-mentioned technical problems. Utility Model Content

[0005] The purpose of this invention is to provide a device and cigarette packaging equipment that converts intermittent motion into continuous motion. This device can convert intermittent motion into continuous motion with low power loss, high conversion efficiency, and low operating impact, which is conducive to achieving high-speed, high-efficiency, precise, and reliable stable motion.

[0006] To achieve this objective, the present invention adopts the following technical solution:

[0007] A device for converting intermittent motion into continuous motion includes:

[0008] An interleaved wheel mechanism, comprising a first rotating wheel and a second rotating wheel, the first rotating wheel and the second rotating wheel being coaxially arranged and offset about the axis, and both the first rotating wheel and the second rotating wheel being provided with an empty mold box;

[0009] transmission shaft;

[0010] A differential mechanism, comprising a first differential gear train and a second differential gear train, wherein a drive shaft is drivenly connected to the first differential gear train and the second differential gear train, the first differential gear train is drivenly connected to the first rotating wheel, and the second differential gear train is drivenly connected to the second rotating wheel;

[0011] A cam rocker arm mechanism is driven to the drive shaft and to the first link of the first differential gear train and the second link of the second differential gear train, such that the motion phases of the first wheel and the second wheel are complementary.

[0012] In some embodiments, the output gear angular velocity of the first differential gear train satisfies The output gear angular velocity of the second differential gear train satisfies ,in:

[0013] Let be the angular velocity of the first rotating wheel. Let be the angular velocity of the second rotating wheel. Let be the angular velocity of the first tie rod. The angular velocity of the second tie rod is... The input gear angular velocity of the first differential gear train is... ω is the input gear angular velocity of the second differential gear train.

[0014] In some embodiments, the first differential gear train further includes a first bevel gear, a second bevel gear, a third bevel gear, and a fourth bevel gear. The first bevel gear is driven to the drive shaft and configured as the input gear of the first differential gear train. The second bevel gear is driven to the first rotating wheel and configured as the output gear of the first differential gear train. The third bevel gear and the fourth bevel gear are both connected between the first bevel gear and the second bevel gear and configured as planetary gears of the first differential gear train. The third bevel gear and the fourth bevel gear are coaxially connected to the first connecting rod.

[0015] In some embodiments, the second differential gear train further includes a fifth bevel gear, a sixth bevel gear, a seventh bevel gear, and an eighth bevel gear. The fifth bevel gear is driven to the drive shaft and configured as the input gear of the second differential gear train. The sixth bevel gear is driven to the second rotating wheel and configured as the output gear of the second differential gear train. The seventh bevel gear and the eighth bevel gear are both connected between the fifth bevel gear and the sixth bevel gear and configured as planetary gears of the second differential gear train. The seventh bevel gear and the eighth bevel gear are coaxially connected to the second connecting rod.

[0016] In some embodiments, a connecting sleeve, a rotating shaft, and a hub are connected between the second bevel gear and the first rotating wheel to connect the second bevel gear and the first rotating wheel with equal angular velocities.

[0017] In some embodiments, a first bushing is connected between the sixth bevel gear and the second rotating wheel to connect the sixth bevel gear and the second rotating wheel with equal angular velocities, and the rotating shaft is rotatably passed through the first bushing via a roller bearing.

[0018] In some embodiments, the drive shaft is connected to a second bushing, one end of which is fixedly connected to the first bevel gear, and the other end of which is fixedly connected to the fifth bevel gear.

[0019] In some embodiments, the cam rocker mechanism includes a cylindrical cam, a first connecting rod, a first rocker arm, a second connecting rod, a second rocker arm, and two rollers. The cylindrical cam is connected to the drive shaft, and the outer circumferential surface of the cylindrical cam is provided with a groove. The two rollers are rolled in the groove. The two rollers are connected to the first connecting rod through the first rocker arm and the first connecting rod, and are connected to the second connecting rod through the second rocker arm and the second connecting rod. The cylindrical cam can rotate to drive the first connecting rod and the second connecting rod, and drive the drive shaft through gear meshing.

[0020] In some embodiments, the contour curve of the wheel groove conforms to a fifth-order polynomial motion law.

[0021] Cigarette packaging equipment, including the aforementioned device for converting intermittent motion into continuous motion.

[0022] The above-mentioned technical solution has the following advantages or beneficial effects: This device combines the periodic "oscillation-stop-oscillation" driven by the cam lever mechanism with the continuous circular motion implemented by the differential mechanism, forming a regular periodic combined motion. This achieves the conversion from the intermittent motion of cigarette pushing to the continuous motion of cigarette forming and output. Furthermore, compared to belt-type radial transmission devices or stepper motors, servo motors, etc., this device features low power loss, high conversion efficiency, and low operational impact. It can achieve high-speed, efficient, and stable motion, and avoids problems such as transmission belt deformation that affect motion accuracy, thereby maintaining the device's lifespan and operational reliability. Attached Figure Description

[0023] Figure 1 This is a front view of a smoke-forming mechanism using a synchronous conveyor belt in existing related technologies;

[0024] Figure 2 This is a front view of a smoke-forming mechanism using a rotary wheel in existing related technologies;

[0025] Figure 3 It is along Figure 2 A cross-sectional schematic diagram of AA in the middle;

[0026] Figure 4 This is a schematic diagram of the misaligned installation of the first and second rotating wheels in an embodiment of this utility model;

[0027] Figure 5 It is along Figure 4 Assembly diagram of the first and second rotating wheels and differential mechanism of the BB;

[0028] Figure 6 This is a schematic diagram of the cam rocker arm mechanism in an embodiment of this utility model;

[0029] Figure 7 yes Figure 5 A magnified view of a section at point C;

[0030] Figure 8 This is a transmission diagram of the motion conversion mechanism in an embodiment of this utility model;

[0031] Figure 9 This is a phase diagram showing the motion relationship between the first and second rotating wheels in an embodiment of this utility model.

[0032] In the picture:

[0033] 100. Tobacco storage; 101. Lower tobacco trough; 102. Push rod; 103. Empty mold box; 104. Synchronous conveyor belt; 105. Rotary wheel; 106. Tobacco group mold box; 107. Drive shaft;

[0034] 200. Housing; 201. First rotating wheel; 202. Second rotating wheel; 203. Shaft; 204. Hub;

[0035] 300. First bushing; 301. First bearing housing; 302. Sixth bevel gear; 303. Seventh bevel gear; 304. Second tie rod; 305. Fifth bevel gear; 306. Second bushing; 307. Ninth bevel gear; 308. Tenth bevel gear; 309. Bracket; 310. First bevel gear; 311. First tie rod; 312. Third bevel gear; 313. Second bevel gear; 314. Connecting sleeve; 315. Second bearing housing; 316. Fourth bevel gear; 317. Eighth bevel gear; 318. Round nut; 319. Four-tooth semi-circular key; 320. Bearing; 321. Four-tooth semi-circular keyway; 322. Four-tooth flat keyway; 323. Four-tooth flat key;

[0036] 401. Second connecting rod; 402. Second rocker arm; 403. Double roller; 404. Rib plate; 405. Fixed spindle; 406. First gear; 407. Cylindrical cam; 408. Wheel groove; 409. First rocker arm; 410. First connecting rod; 411. Second gear; 412. Third gear;

[0037] 700, roller bearing; 800, drive shaft. Detailed Implementation

[0038] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, not the entire structure.

[0039] In the description of this utility model, unless otherwise explicitly specified and limited, the terms "connected," "linked," "fixed," and "abutting" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0040] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0041] In the description of this embodiment, the terms "upper," "lower," "right," and "left," etc., refer to the orientation or positional relationship shown in the accompanying drawings. They are used only for ease of description and simplification of operation, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. In addition, the terms "first" and "second" are only used for distinction in description and have no special meaning.

[0042] The following is based on Figures 4 to 9This invention introduces a device (hereinafter referred to as the device) for converting intermittent motion into continuous motion and a cigarette packaging equipment provided in the embodiments of the present invention.

[0043] like Figure 4 , Figure 5 As shown, the device mainly includes an interleaved wheel mechanism, a drive shaft 800, a differential mechanism, and a cam rocker arm mechanism. The interleaved wheel mechanism includes a first rotating wheel 201 and a second rotating wheel 202, both rotatably mounted at one end of the device and coaxially arranged. Each of the first and second rotating wheels 201 and 202 has two mold box mounting portions. The two mold box mounting portions of the first rotating wheel 201 are symmetrically arranged at 180° intervals around the axis, and the two mold box mounting portions of the second rotating wheel 202 are also symmetrically arranged at 180° intervals around the axis. Multiple empty mold boxes 103 are provided on the mold box mounting portions. As the first and second rotating wheels 201 and 202 rotate, when the mold box mounting portion rotates to a preset angle, the cigarette can enter the empty mold box 103 under the action of the push rod 102 (for convenience, the empty mold box 103 containing the cigarette is simply referred to as the cigarette set mold box 106). Furthermore, as... Figure 4 As shown, the first rotating wheel 201 and the second rotating wheel 202 are offset around the axis, so that the mold mounting part of the first rotating wheel 201 does not overlap the mold mounting part of the second rotating wheel 202 along the axis. Figure 4 As shown, along the axial direction, the mold box mounting part of the first rotating wheel 201 is bent towards the second rotating wheel 202, and the mold box mounting part of the second rotating wheel 202 is bent towards the first rotating wheel 201, so that the rotation trajectory of the multiple empty mold boxes 103 is the same circular trajectory, which facilitates the cigarettes to enter different empty mold boxes 103. For example, in this embodiment, each mold box mounting part is provided with four empty mold boxes 103.

[0044] like Figure 5 , Figure 6As shown, the differential mechanism includes a first differential gear train and a second differential gear train. A drive shaft 800 is driven to the power input ends of both the first and second differential gear trains. The power output end of the first differential gear train is driven to the first rotating wheel 201, and the power output end of the second differential gear train is driven to the second rotating wheel 202. Simultaneously, a cam rocker arm mechanism is driven to the drive shaft 800 and to the first connecting rod 311 of the first differential gear train and the second connecting rod 304 of the second differential gear train. The first differential gear train combines the continuous rotation input from the drive shaft 800 with the periodic "oscillation-pause-oscillation" of the first connecting rod 311 under the action of the cam rocker arm mechanism, thereby outputting a regular combined motion of the first rotating wheel 201. The second differential gear train combines the continuous rotation input from the drive shaft 800 with the periodic "oscillation-pause-oscillation" of the second connecting rod 304 under the action of the cam rocker arm mechanism, thereby outputting a regular combined motion of the second rotating wheel 202. The drive shaft 800 can couple the movements of the first differential gear train, the second differential gear train, and the cam rocker mechanism to achieve timing coordination. In turn, it works with the first differential gear train, the second differential gear train, and the cam rocker mechanism to achieve complementary movement phases of the first rotating wheel 201 and the second rotating wheel 202, so that the first rotating wheel 201 and the second rotating wheel 202 can alternately stop and move, which is equivalent to achieving a continuous conveying effect.

[0045] This device combines the periodic "oscillation-pause-oscillation" driven by the cam lever mechanism with the continuous circular motion implemented by the differential mechanism to form a regular periodic combined motion, realizing the conversion from the intermittent motion of cigarette pushing to the continuous motion of cigarette forming and output. Furthermore, compared to belt-type radial transmission devices or stepper motors, servo motors, etc., this device features low power loss, high conversion efficiency, and low operational impact, enabling high-speed, efficient, and smooth motion, and avoiding problems such as transmission belt deformation that affect motion accuracy, thus maintaining the device's lifespan and operational reliability.

[0046] Specifically, such as Figure 4 , Figure 5As shown, in this embodiment, the first differential gear train further includes a first bevel gear 310, a second bevel gear 313, a third bevel gear 312, and a fourth bevel gear 316. The first bevel gear 310 is connected to the drive shaft 800 and serves as the input gear of the first differential gear train. The second bevel gear 313 is connected to the first rotating wheel 201 and serves as the output gear of the first differential gear train. The third bevel gear 312 and the fourth bevel gear 316 are both connected between the first bevel gear 310 and the second bevel gear 313 and serve as planetary gears of the first differential gear train. The third bevel gear 312 and the fourth bevel gear 316 are coaxially connected by a first connecting rod 311. Continuous circular motion is input to the first differential gear train from the first bevel gear 310, while periodic "oscillation-stop-oscillation" is input to the first differential gear train from the first connecting rod 311, ultimately combining and outputting from the second bevel gear 313.

[0047] Furthermore, a connecting sleeve 314, a rotating shaft 203, and a hub 204 are connected between the second bevel gear 313 and the first rotating wheel 201 to connect the second bevel gear 313 and the first rotating wheel 201 with equal angular velocities. Specifically, the second bevel gear 313 and the connecting sleeve 314 are fixedly connected, and one end of the rotating shaft 203 passes through the connecting sleeve 314 and is fixedly connected to the connecting sleeve 314. The other end of the rotating shaft 203 passes through the second differential gear train and is connected to the hub 204, which is fixedly connected to the first rotating wheel 201. At the same time, in this embodiment, both ends of the rotating shaft 203 are also fixedly connected to the bracket 309 of the housing 200 through the first bearing seat 301 and the second bearing seat 315, respectively, thereby installing both the first differential gear train and the second differential gear train in the housing 200.

[0048] The second differential gear train also includes a fifth bevel gear 305, a sixth bevel gear 302, a seventh bevel gear 303, and an eighth bevel gear 317. The fifth bevel gear 305 is connected to the drive shaft 800 and serves as the input gear of the second differential gear train. The sixth bevel gear 302 is connected to the second rotating wheel 202 and serves as the output gear of the second differential gear train. The seventh bevel gear 303 and the eighth bevel gear 317 are both connected between the fifth bevel gear 305 and the sixth bevel gear 302 and serve as planetary gears of the second differential gear train. The seventh bevel gear 303 and the eighth bevel gear 317 are coaxially connected by a second connecting rod 304. Continuous circular motion is input to the second differential gear train from the fifth bevel gear 305, while periodic "oscillation-stop-oscillation" is input to the second differential gear train from the second connecting rod 304, ultimately combining and outputting from the sixth bevel gear 302.

[0049] Furthermore, a first bushing 300 connects the sixth bevel gear 302 and the second rotating wheel 202 to connect them with equal angular velocities. A rotating shaft 203 rotatably passes through the first bushing 300 via a ball bearing 700. The first bushing 300 is rotatably connected to the housing 200 via the aforementioned first bearing seat 301, allowing the rotating shaft 203 to rotatably pass through the first bushing 300, and the first bushing 300 to rotatably pass through the housing 200. In this way, the first rotating wheel 201 and the second rotating wheel 202 can move independently with complementary motion phases.

[0050] like Figure 6 As shown, the cam-rocker mechanism includes a cylindrical cam 407, a first connecting rod 410, a first rocker arm 409, a second connecting rod 401, a second rocker arm 402, and a double roller 403. The cylindrical cam 407 is connected to the drive shaft 800. The outer circumferential surface of the cylindrical cam 407 is provided with a groove 408. The double roller 403 rolls within the groove 408. The double roller 403 is connected to the first tie rod 311 via the first rocker arm 409 and the first connecting rod 410, and is connected to the second tie rod 304 via the second rocker arm 402 and the second connecting rod 401. The cylindrical cam 407 can rotate to drive the first tie rod 311, the second tie rod 304, and the drive shaft 800. The contour curve of the wheel groove 408 includes a push section, a rest section, and a return section. The double rollers 403 roll in the wheel groove 408 and can push the first rocker arm 409 and the second rocker arm 402 in a direction close to the differential mechanism in the push section, move the first rocker arm 409 and the second rocker arm 402 in a direction away from the differential mechanism in the return section, and keep the distance between the first rocker arm 409, the second rocker arm 402 and the differential mechanism unchanged in the rest section, thereby realizing the periodic "swing-stop-swing" of the first and second tie rods.

[0051] More specifically, such as Figure 6As shown, the cylindrical cam 407 is connected to a first gear 406 and a second gear 411, while the drive shaft 800 is connected to a third gear 412. Along the axial direction of the cylindrical cam 407, the first gear 406 is located at one end of the cylindrical cam 407, and the second gear 411 is located at the other end of the cylindrical cam 407. The first gear 406 is used to connect to the drive device, thereby inputting continuous circular motion into the cylindrical cam 407. The second gear 411 and the third gear 412 are connected in a transmission, thereby inputting continuous circular motion into the drive shaft 800, and then into the differential mechanism. That is to say, in this embodiment, the power input by the first gear 406 is divided into two paths. One path drives the first connecting rod 311 and the second connecting rod 304 to periodically "oscillate-stop-oscillate" through the cylindrical cam 407 and other structures. The other path drives the first bevel gear 310 and the fifth bevel gear 305 to rotate through the drive shaft 800. The two paths are connected by the meshing of the second gear 411 and the third gear 412, enabling timing coordination. This, in conjunction with the first differential gear train, the second differential gear train, and the cam rocker arm mechanism, achieves complementary motion phases between the first rotating wheel 201 and the second rotating wheel 202. This allows the first rotating wheel 201 and the second rotating wheel 202 to alternately stop and move, effectively achieving a continuous conveying effect. Optionally, the housing 200 is also provided with a rib plate 404, and both the first rocker arm 409 and the second rocker arm 402 are rotatably connected to the rib plate 404 via a fixed spindle 405.

[0052] Preferably, in this embodiment, the contour curve of the wheel groove 408 conforms to a fifth-order polynomial motion law. The fifth-order polynomial motion law defines the variation of the displacement (s), velocity (v), and acceleration (a) of the follower with time (or cam rotation angle) through a fifth-order polynomial function, so that the first rocker arm 409 and the second rocker arm 402 have relatively stable acceleration changes during the motion, thereby achieving smoothness and low impact in the motion process and improving the operational stability of the device.

[0053] like Figure 5 , Figure 7 As shown, in this embodiment, the transmission shaft 800 is connected to a ninth bevel gear 307, a tenth bevel gear 308, and a second bushing 306. One end of the second bushing 306 is fixedly connected to the first bevel gear 310, and the other end is fixedly connected to the fifth bevel gear 305. Through the ninth bevel gear 307, the tenth bevel gear 308, and the second bushing 306, continuous circular motion can be simultaneously input to the first bevel gear 310 and the fifth bevel gear 305. The aforementioned rotating shaft 203 rotatably passes through the second bushing 306, allowing relative rotation between the two without interference. Optionally, both ends of the second bushing 306 are connected to the bracket 309 of the housing 200 via bearings 320, thereby rotatably mounting the second bushing 306 to the housing 200.

[0054] More specifically, one end of the second bushing 306 is provided with a four-tooth semi-circular keyway 321, and the fifth bevel gear 305 is provided with a four-tooth semi-circular key 319. The four-tooth semi-circular keyway 321 and the four-tooth semi-circular key 319 mate and are connected by a round nut 318 and the inner ring of the bearing 320 located at one end of the second bushing 306, forming a force-form locking seal. The second bushing 306 is also provided with a four-tooth flat keyway 322, and the tenth bevel gear 308 is provided with a four-tooth flat key 323 and a four-tooth semi-circular key 319. Among them, the four-tooth flat key 323 of the tenth bevel gear 308 is connected to the four-tooth flat keyway 322 of the second bushing 306, and the four-tooth semi-circular key 319 of the tenth bevel gear 308 mates with the four-tooth semi-circular keyway 321 on the first bevel gear 310. Meanwhile, the bearing 320 located at the other end of the second bushing 306 is also connected to a round nut 318, thereby forming a force-form locking seal, fixing and transmitting the second bushing 306 and the first bevel gear 310. The connection between the first bushing 300 and the sixth bevel gear 302, the connecting sleeve 314 and the second bevel gear 313 is also achieved using a similar method of tightening with a round nut 318, which will not be elaborated upon further in this invention.

[0055] like Figure 8 , Figure 9 As shown, in this embodiment, when the cylindrical cam 407 rotates, it drives the first connecting rod 311 to periodically "oscillate-pause-oscillate" via the first rocker arm 409 and the first connecting rod 410, and drives the second connecting rod 304 to periodically "oscillate-pause-oscillate" via the second rocker arm 402 and the second connecting rod 401. Both the first differential gear train and the second differential gear train have two degrees of freedom, and when the input is two motions, its output motion is determined, that is, it is a combination of two motions.

[0056] At this point, let the angular velocities of the first tie rod 311 and the second tie rod 304 relative to their centers of rotation be respectively and Let the number of teeth of the sixth bevel gear 302, the seventh bevel gear 303, the fifth bevel gear 305, the ninth bevel gear 307, the tenth bevel gear 308, the first bevel gear 310, the third bevel gear 312, the second bevel gear 313, the fourth bevel gear 316, and the eighth bevel gear 317 correspond to the following values: , , , , , , , , and The rotational angular velocities are respectively as follows: , , , , , , , , and At this point, for the first differential gear train, there exists ,as well as For the second differential gear train, there exists ,as well as .

[0057] According to the differential gear train transmission ratio formula, for the first differential gear train:

[0058]

[0059] Therefore, we can conclude that:

[0060]

[0061] Furthermore, since the first rotating wheel 201 is fixedly connected to the second bevel gear 313 via structures such as the rotating shaft 203, and both have the same rotational angular velocity, therefore:

[0062]

[0063] Similarly, for the second differential gear train, we can obtain:

[0064]

[0065] Since the second rotating wheel 202 is fixedly connected to the first bushing 300 and the sixth bevel gear 302, and both have the same rotational angular velocity, therefore:

[0066]

[0067] For the first rotating wheel, we have:

[0068] when When the angular velocity of the first connecting rod is half the rotational angular velocity of the input gear (i.e., the first bevel gear 310), In other words, the first rotating wheel 201 is in a stopped state and can accept the smoke group being pushed into the empty mold box 103.

[0069] when When the rotation direction of the first connecting rod 311 is opposite to that of the first bevel gear 310, the fourth bevel gear 316 accelerates its rotation, driving the second bevel gear 313 and the first rotating wheel 201 to accelerate their rotation.

[0070] when When the first tie rod 311 is stationary, meaning the double rollers 403 are at rest and the first pendulum rod 409 has stopped swinging, the first differential gear train can be considered a fixed-axis gear train, and the first rotating wheel 201 will... The rotational angular velocity is constant.

[0071] when When the first connecting rod 311 rotates in the same direction as the first bevel gear 310, the fourth bevel gear 316 decelerates and rotates, driving the second bevel gear 313 and the first rotating wheel 201 to decelerate and rotate.

[0072] when Increase to At that time, and The first rotor 201 is in a resting state and can accept the smoke group being pushed in. In this way, the first rotor 201 can complete the working cycle of "(rest-acceleration)-(constant speed)-(deceleration-rest)".

[0073] The fifth bevel gear 305, the tenth bevel gear 308, and the first bevel gear 310 are fixedly connected to the second bushing 306. Therefore, the rotational angular velocities of the fifth bevel gear 305 and the first bevel gear 310 are the same. Therefore, by determining the motion law of the second tie rod 304, the motion law of the second rotating wheel 202 can be determined. The periodic "oscillation-stop-oscillation" pattern of the second tie rod 304 is determined by the contour curve of the wheel groove 408 and the motion phase of the cylindrical cam 407. Therefore, by setting the contour curve of the wheel groove 408 and the motion phase of the cylindrical cam 407, the second tie rod 304 can drive the second rotating wheel 202, forming a working cycle of "(constant speed motion) - (deceleration motion - stop - acceleration) - (constant speed motion)" that is complementary to the motion phase of the first rotating wheel 201.

[0074] In actual production, based on the actual working needs of cigarette packaging equipment, and referring to... Figure 9 As shown, the constant-speed motion duration can be set to 0.5T for outputting smoke packs; deceleration and acceleration motions are non-working times, with a set duration of 0.125T; and the rest duration is 0.25T for receiving input smoke packs. When the first rotor 201 is resting or accelerating, the second rotor 202 is in a constant-speed motion state; when the first rotor 201 begins constant-speed motion, the second rotor 202 is in a deceleration-rest-acceleration motion state, thus ensuring seamless connection between the movements of the first rotor 201 and the second rotor 202.

[0075] This utility model also provides a cigarette packaging device, which includes the aforementioned device for converting intermittent motion into continuous motion. In this cigarette packaging device, the periodic "oscillation-stop-oscillation" driven by the cam lever mechanism and the continuous circular motion implemented by the differential mechanism are combined to form a regular periodic combined motion, realizing the conversion from the intermittent motion of cigarette pushing to the continuous motion of cigarette forming and output. Furthermore, compared to belt-type radial transmission devices or stepper motors, servo motors, etc., this cigarette packaging device features low power loss, high conversion efficiency, and low operational impact, enabling high-speed, high-efficiency, and stable motion, and avoiding problems such as transmission belt deformation that affect motion accuracy, thereby maintaining the lifespan and operational reliability of the cigarette packaging device.

[0076] It should be noted that, in addition to cigarette packaging equipment, this device can also be applied to various packaging machines, filling machines, and various mechanical equipment that require the conversion of intermittent motion into continuous motion. This utility model does not make any specific limitations in this regard.

[0077] In the description of this specification, references to terms such as "some embodiments," "other embodiments," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0078] Obviously, the above embodiments of this utility model are merely examples for clearly illustrating the present utility model, and are not intended to limit the implementation of the present utility model. Those skilled in the art can make various obvious changes, readjustments, and substitutions without departing from the protection scope of this utility model. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this utility model should be included within the protection scope of the claims of this utility model.

Claims

1. A device for converting intermittent motion into continuous motion, characterized in that, include: An interleaved wheel mechanism is provided, comprising a first rotating wheel (201) and a second rotating wheel (202). The first rotating wheel (201) and the second rotating wheel (202) are coaxially arranged and offset about the axis. Both the first rotating wheel (201) and the second rotating wheel (202) are provided with empty mold boxes (103). Drive shaft (800); A differential mechanism, comprising a first differential gear train and a second differential gear train, wherein the drive shaft (800) is driven to the first differential gear train and the second differential gear train, the first differential gear train is driven to the first rotating wheel (201), and the second differential gear train is driven to the second rotating wheel (202). The cam rocker mechanism is driven to the drive shaft (800) and to the first link (311) of the first differential gear train and the second link (304) of the second differential gear train, such that the motion phases of the first wheel (201) and the second wheel (202) are complementary.

2. The device for converting intermittent motion into continuous motion according to claim 1, characterized in that, The output gear angular velocity of the first differential gear train satisfies The output gear angular velocity of the second differential gear train satisfies ,in: The angular velocity of the first rotor (201) is... The angular velocity of the second rotor (202) is... The angular velocity of the first tie rod (311) is the swing angle. The angular velocity of the second tie rod (304) is the swing angle. The input gear angular velocity of the first differential gear train is... ω is the input gear angular velocity of the second differential gear train.

3. The device for converting intermittent motion into continuous motion according to claim 2, characterized in that, The first differential gear train further includes a first bevel gear (310), a second bevel gear (313), a third bevel gear (312), and a fourth bevel gear (316). The first bevel gear (310) is connected to the drive shaft (800) and is configured as the input gear of the first differential gear train. The second bevel gear (313) is connected to the first rotating wheel (201) and is configured as the output gear of the first differential gear train. The third bevel gear (312) and the fourth bevel gear (316) are both connected between the first bevel gear (310) and the second bevel gear (313) and are configured as planetary gears of the first differential gear train. The third bevel gear (312) and the fourth bevel gear (316) are coaxially connected to the first connecting rod (311).

4. The device for converting intermittent motion into continuous motion according to claim 3, characterized in that, The second differential gear train also includes a fifth bevel gear (305), a sixth bevel gear (302), a seventh bevel gear (303), and an eighth bevel gear (317). The fifth bevel gear (305) is connected to the drive shaft (800) and is configured as the input gear of the second differential gear train. The sixth bevel gear (302) is connected to the second rotating wheel (202) and is configured as the output gear of the second differential gear train. The seventh bevel gear (303) and the eighth bevel gear (317) are both connected between the fifth bevel gear (305) and the sixth bevel gear (302) and are configured as planetary gears of the second differential gear train. The seventh bevel gear (303) and the eighth bevel gear (317) are coaxially connected to the second connecting rod (304).

5. The device for converting intermittent motion into continuous motion according to claim 4, characterized in that, A connecting sleeve (314), a rotating shaft (203), and a hub (204) are connected between the second bevel gear (313) and the first rotating wheel (201) to connect the second bevel gear (313) and the first rotating wheel (201) with equal angular velocities.

6. The device for converting intermittent motion into continuous motion according to claim 5, characterized in that, A first bushing (300) is connected between the sixth bevel gear (302) and the second rotating wheel (202) to connect the sixth bevel gear (302) and the second rotating wheel (202) with equal angular velocities, and the rotating shaft (203) is rotatably passed through the first bushing (300) via a roller bearing (700).

7. The device for converting intermittent motion into continuous motion according to claim 4, characterized in that, The drive shaft (800) is connected to the second bushing (306), one end of the second bushing (306) is fixedly connected to the first bevel gear (310), and the other end of the second bushing (306) is fixedly connected to the fifth bevel gear (305).

8. The device for converting intermittent motion into continuous motion according to claim 4, characterized in that, The cam rocker mechanism includes a cylindrical cam (407), a first connecting rod (410), a first rocker arm (409), a second connecting rod (401), a second rocker arm (402), and a double roller (403). The cylindrical cam (407) is connected to the drive shaft (800) for transmission. The outer circumferential surface of the cylindrical cam (407) is provided with a wheel groove (408). The double roller (403) is rolled in the wheel groove (408). The double roller (403) is connected to the first tie rod (311) through the first rocker arm (409) and the first connecting rod (410). The double roller (403) is connected to the second tie rod (304) through the second rocker arm (402) and the second connecting rod (401). The cylindrical cam (407) can rotate to drive the first tie rod (311) and the second tie rod (304) and drive the drive shaft (800) through gear meshing transmission.

9. The device for converting intermittent motion into continuous motion according to claim 8, characterized in that, The contour curve of the wheel groove (408) conforms to the fifth-order polynomial motion law.

10. Cigarette packaging equipment, characterized in that, Includes a device for converting intermittent motion into continuous motion as described in any one of claims 1-9.

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