An 8-shaped track swinging mechanism for flag display, an intermittent transmission mechanism with a 1:1 rotation ratio and a control method thereof

Abstract

This invention discloses a figure-eight trajectory swing mechanism for flag-waving displays, a 1:1 rotational speed ratio intermittent transmission mechanism, and its control method, relating to the field of dynamic display device technology. The intermittent transmission mechanism can serve as a core component of the flag-waving display mechanism or be independently assembled into various intermittent swing devices. Addressing the problems of existing flag-waving machines that can only achieve single-plane reciprocating swing, have limited dynamic effects, and suffer from large reversing impacts, this invention employs a single power source drive. Through an innovative 1:1 rotational speed ratio intermittent transmission mechanism, it precisely superimposes continuous reciprocating swing motion with 180° intermittent reversing motion, enabling the swing component to draw a smooth, angle-free figure-eight trajectory. This invention features a simple structure, low manufacturing cost, and stable, shock-free operation, making it widely applicable in advertising, safety warnings, and other fields.

Description

Technical Field

[0001] This invention relates to the field of dynamic display device technology, and in particular to an 8-track swing mechanism and an intermittent transmission mechanism with a 1:1 rotation ratio that can be used for flag waving displays. Background Technology

[0002] A flag-waving machine is a dynamic display device widely used in advertising, sports events, safety warnings, and other fields. It attracts people's attention by driving the flag to swing periodically, thereby achieving the purpose of publicity or warning.

[0003] Existing flag-waving machines use a crank-rocker mechanism or similar structure, which can only drive the flag to swing back and forth in a single plane. The dynamic effect is monotonous, the visual impact is weak, and the warning effect is poor in complex environments. In addition, the reversing action of existing flag-waving machines usually occurs at the extreme position of the swing, which will generate severe impact and noise, resulting in severe wear and tear on the mechanism and a short service life.

[0004] To improve the dynamic effect of flag waving machines, some people have tried to design flag waving machines that can achieve complex trajectories. However, these solutions usually require multiple power sources and complex transmission mechanisms, resulting in complex structures, high costs, poor reliability, and difficulty in large-scale promotion and application.

[0005] Therefore, there is an urgent need for a new type of flag-waving display mechanism that is simple in structure, low in cost, stable in operation, and capable of swinging in a figure-eight trajectory. Summary of the Invention

[0006] To address these issues, the present invention provides an 8-track swing mechanism for flag waving displays, an intermittent transmission mechanism with a 1:1 rotational speed ratio, and a control method thereof, in order to solve one or more of the aforementioned problems.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] The first aspect of this invention provides a figure-eight trajectory swinging mechanism that can be used for flag-waving displays, comprising:

[0009] frame;

[0010] A power input device is fixedly mounted on the frame;

[0011] The drive wheel is coaxially fixed to the output shaft of the power input device and is used to perform continuous rotational motion.

[0012] The passive gear disc is rotatably mounted on the frame and is parallel to the axis of rotation of the active wheel;

[0013] The driving crank is coaxially and fixedly connected to the driving wheel;

[0014] The driven swing arm is coaxially and fixedly connected to the driven gear plate;

[0015] A reversing drive pin is fixedly mounted on the driven swing arm;

[0016] A reversing guide plate is rotatably mounted on the frame via a guide plate pivot. The reversing drive pin is embedded in the slide groove of the reversing guide plate to drive the reversing guide plate to reciprocate in an arc around the guide plate pivot.

[0017] The drive linkage is hinged at one end to the active crank and at the other end to the swing assembly;

[0018] The swing assembly is hinged to the frame at its lower end via a universal hinge mechanism, and its middle part is embedded in the guide groove of the reversing guide plate.

[0019] The drive wheel is alternately provided with two transmission zones and two locking zones along the circumferential direction. The central angles of the two transmission zones are equal, and the central angles of the two locking zones are equal.

[0020] Each of the transmission zones is provided with multiple driving components along the circumferential direction. The axis of the driving component is parallel to the axis of the driving wheel and is used to mesh sequentially with the tooth grooves of the driven gear to drive the driven gear to rotate.

[0021] The outer contour of each locking zone is a locking arc surface of the driving wheel that is coaxial with the driving wheel. The radius of the locking arc surface of the driving wheel matches the radius of the locking arc surface of the passive gear plate, so that when the driving member engages the tooth groove, it forms a surface contact lock with the locking arc surface of the passive gear plate.

[0022] When the driving wheel completes one full rotation, the driven gear plate rotates one full rotation in segments within two independent transmission intervals, while the locking interval remains stationary.

[0023] A second aspect of the present invention provides an intermittent transmission mechanism with a 1:1 speed ratio, comprising:

[0024] The drive wheel is connected to the power source and is used to perform continuous rotational motion;

[0025] The passive gear disc is rotatably mounted on the mounting base and is parallel to the axis of rotation of the active gear.

[0026] The drive wheel is alternately provided with two transmission zones and two locking zones along the circumferential direction. The central angles of the two transmission zones are equal, and the central angles of the two locking zones are equal.

[0027] Each of the transmission zones is provided with multiple driving components along the circumferential direction. The axis of the driving component is parallel to the axis of the driving wheel and is used to mesh sequentially with the tooth grooves of the driven gear to drive the driven gear to rotate.

[0028] The outer contour of each locking zone is a locking arc surface of the driving wheel that is coaxial with the driving wheel. The radius of the locking arc surface of the driving wheel matches the radius of the locking arc surface of the passive gear plate, so that when the driving member engages the tooth groove, it forms a surface contact lock with the locking arc surface of the passive gear plate.

[0029] When the driving wheel completes one full rotation, the driven gear plate rotates one full rotation in segments within two independent transmission intervals, while the locking interval remains stationary.

[0030] Furthermore, the central angles of the two transmission zones are equal to the central angles of the two locking zones.

[0031] Furthermore, each transmission zone of the driving wheel can drive the driven gear disc to rotate 180°.

[0032] Furthermore, the number of driving components in each transmission zone is N, and the number of teeth on the passive gear disk is 2N. Preferably, the value of N is 5, that is, the number of driving components in each transmission zone is 5, and the number of teeth on the passive gear disk is 10.

[0033] Furthermore, the passive gear disc includes engagement teeth and disengagement teeth. Guide structures are provided on the engagement side of the engagement teeth and the disengagement side of the engagement teeth to guide the drive component to smoothly engage and disengage from the tooth grooves. Preferably, the guide structure is a single-sided chamfer, and the chamfers of the engagement teeth and the disengagement teeth are opened in opposite directions.

[0034] Furthermore, the transmission zone and locking zone of the drive wheel are arranged axially offset, the drive member is disposed on the axial end face of the transmission zone on the same side as the power input device, and the locking arc surface of the drive wheel is disposed on the outer circumferential surface of the drive wheel.

[0035] Furthermore, the swinging component is used to mount the display object, preferably a flagpole component, to realize the flag-waving display function.

[0036] A third aspect of the present invention provides a control method for a figure-eight trajectory swing mechanism that can be used for flag-waving displays, comprising the following steps:

[0037] a. The power input device drives the drive wheel to rotate continuously;

[0038] b. The drive wheel drives the drive crank to rotate synchronously, and the drive crank pulls the swing assembly to slide continuously back and forth along the slide groove of the reversing guide plate through the drive connecting rod;

[0039] c. When the driving wheel rotates to the point where the first driving element in any transmission zone engages with the tooth groove of the driven gear, the locking state is released;

[0040] d. The driving wheel continues to rotate, and the locking arc surface of the driving wheel gradually disengages from the locking arc surface of the driven tooth plate. The driving component meshes with the tooth groove of the driven tooth plate in sequence, pushing the driven tooth plate to rotate. The driven tooth plate drives the reversing guide plate to swing in a positive arc shape around the rotation axis of the guide plate through the driven swing arm and the reversing drive pin. At the same time, the swing component enters the reversing state along the sliding groove of the reversing guide plate.

[0041] e. When the driving wheel rotates to the point where the last driving component in the current transmission zone engages the tooth groove of the driven gear, the driven gear completes a 180° rotation and enters the locked state, the reversing guide plate completes a forward swing, and the swing assembly completes a forward reversal.

[0042] f. The driving wheel continues to rotate, and the locking arc surface of the driving wheel fits against the locking arc surface of the driven gear plate;

[0043] g. When the driving wheel continues to rotate until the first driving element in the next transmission zone engages with the tooth groove of the driven gear, the locking state is released again;

[0044] h. The driving wheel continues to rotate, and the locking arc surface of the driving wheel gradually disengages from the locking arc surface of the driven tooth plate. The driving component meshes with the tooth groove of the driven tooth plate in sequence, pushing the driven tooth plate to rotate. The driven tooth plate drives the reversing guide plate to swing in the opposite arc shape with the guide plate rotation axis as the center through the driven swing arm and the reversing drive pin. At the same time, the swing component enters the reversing state again along the slide groove of the reversing guide plate.

[0045] i. When the driving wheel rotates to the point where the last driving component in the current transmission zone engages the tooth groove of the driven gear, the driven gear completes the next 180° rotation and enters the locked state. The reversing guide plate completes the reverse swing, and the swing assembly completes the reverse reversal.

[0046] j. Repeat steps b to i above to make the oscillating component continuously reciprocate in two sets of mutually perpendicular planes, thereby drawing a smooth figure-eight trajectory.

[0047] The beneficial effects of this invention are as follows:

[0048] 1. It adopts a single power source to simultaneously drive two motions: continuous reciprocating oscillation and intermittent reversal. It has a simple structure, few parts, and low manufacturing cost.

[0049] 2. The innovative 1:1 rotational speed ratio intermittent transmission mechanism features a continuous rotation of the drive wheel throughout its entire range, while the driven gear rotates intermittently in two stages and locks in two stages. The locking stage employs surface contact locking, eliminating wobbling and ensuring a regular and stable flag posture. The mechanism operates without impact, with low noise and wear, further improving its service life.

[0050] 3. Equipped with a universal hinge structure, it allows the swinging component to freely deflect in two mutually perpendicular vertical planes. The combination of linear sliding and arc swing of the slot plate outputs a smooth figure-eight trajectory without sharp corners, and the visual display effect for advertising and safety warnings is superior to that of traditional single-plane flag-waving equipment.

[0051] 4. The core intermittent transmission mechanism has independent product value. It can be used independently without the flag-waving machine frame, crank connecting rod and other supporting parts. It is suitable for advertising swing signs, dynamic decorations and industrial intermittent swing equipment, and has a wider range of patent commercial protection.

[0052] The above overview is for illustrative purposes only and is not intended to be limiting in any way. In addition to the illustrative aspects, embodiments, and features described above, further aspects, embodiments, and features of this application will become readily apparent from the accompanying drawings and the following detailed description. Attached Figure Description

[0053] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings in the following description are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0054] The structures, proportions, sizes, etc. illustrated in this specification are only for the purpose of assisting those skilled in the art in understanding and reading the content disclosed herein, and are not intended to limit the conditions under which the present invention can be implemented. Therefore, they have no substantial technical significance. Any modifications to the structure, changes in the proportions, or adjustments to the size, without affecting the effects and objectives that the present invention can produce, should still fall within the scope of the technical content disclosed in the present invention.

[0055] Figure 1 This is a schematic diagram of a figure-eight trajectory swing mechanism that can be used for flag-waving displays, provided by an embodiment of the present invention.

[0056] Figure 2 This is an enlarged schematic diagram of a figure-eight trajectory swing mechanism structure that can be used for flag-waving displays, provided by an embodiment of the present invention.

[0057] Figure 3 This is an enlarged schematic diagram of the intermittent transmission mechanism with a 1:1 speed ratio, which is the core of this invention.

[0058] In the diagram: 1-Frame; 2-Power input device; 3-Driving wheel; 4-Drive component; 5-Driven gear; 6-Guide structure; 7-Driving crank; 8-Driven swing arm; 9-Reversing drive pin; 10-Reversing guide slot; 11-Guide slot shaft; 12-Drive connecting rod; 13-Swing assembly; 14-Universal hinge mechanism; 15-Driven gear locking arc surface; 16-Driving wheel locking arc surface; 17-Transmission zone; 18-Flagpole assembly Detailed Implementation

[0059] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention, and as those skilled in the art will recognize, the described embodiments can be modified in various ways without departing from the spirit or scope of this application. Therefore, the drawings and description are considered exemplary in nature and not restrictive, and are not intended to limit the invention.

[0060] This embodiment provides a figure-eight trajectory swinging mechanism, a 1:1 rotational speed ratio intermittent transmission mechanism, and a control method thereof for use in flag-waving displays, achieving a smooth figure-eight motion trajectory. The flag-waving display mechanism uses a 1:1 rotational speed ratio intermittent transmission mechanism to achieve the figure-eight trajectory motion, but this 1:1 rotational speed ratio intermittent transmission mechanism can be detached from the other supporting structures of the flag-waving display mechanism and assembled independently onto any equipment base.

[0061] like Figure 1-3 As shown, an 8-track swing mechanism for flag waving displays includes a frame 1, a power input device 2, a drive wheel 3, a drive component 4, a driven gear 5, a guide structure 6, a drive crank 7, a driven swing arm 8, a reversing drive pin 9, a reversing guide groove plate 10, a guide groove plate shaft 11, a drive connecting rod 12, a swing assembly 13, a universal joint mechanism 14, a driven gear plate locking arc surface 15, a drive wheel locking arc surface 16, a transmission zone 17, and a flagpole assembly 18.

[0062] The frame 1 is a sheet metal bending structure used to mount the power input device 2, the drive wheel 3, the driven gear 5, the guide slot plate shaft 11, and the universal joint mechanism 14. Exemplarily, the frame 1 has a double-layer structure, with the upper layer being a plate structure with slots and the lower layer being a plate structure with through holes. Of course, the frame 1 can also be a single-layer structure, a multi-layer structure, or a box structure, etc.

[0063] The power input device 2 is a geared motor, which is fixedly installed at the bottom of the frame 1 by bolts. The output shaft is coaxially connected to the drive wheel 3. This is existing technology and is the only power source in this embodiment.

[0064] The driving wheel 3 has a disc-shaped structure and is coaxially fixed to the output shaft of the geared motor via gears. Driven by the geared motor, it rotates continuously at a uniform speed. The driving wheel 3 has two alternating transmission zones 17 and two locking zones along its circumference, with each transmission zone 17 and each locking zone having a central angle of 90°. Five driving components 4, cylindrical pins, are evenly mounted on the lower end face of each transmission zone 17 along its circumference. These components are parallel to the axis of the driving wheel 3 and are used to engage and disengage the driven gear disc 5, transmitting torque and driving the driven gear disc 5 to rotate uniformly with the driving wheel. The outer contour of each locking zone is a driving wheel locking arc surface 16 coaxial with the driving wheel 3. The radius of the driving wheel locking arc surface 16 precisely matches the radius of the driven gear disc locking arc surface 15 of the driven gear disc 5, used to restrict the circumferential rotation of the driven gear disc 5 when it stops rotating.

[0065] The drive crank 7 is fixedly mounted on the upper end face of the drive wheel 3 by welding, and rotates synchronously with the drive wheel 3 on the same axis. Exemplarily, the free end of the drive crank 7 is fixedly oriented toward the third drive member 4 of any of the transmission zones 17 of the drive wheel 3.

[0066] The passive gear disk 5 is a disc-shaped component integrally machined and rotatably mounted on the frame 1. Its axis is parallel to the axis of the drive wheel 3, and the two are arranged side by side laterally along the frame. The passive gear disk 5 is divided into upper and lower layers along the axial direction, namely, a locking engagement layer and a tooth meshing layer from top to bottom; the two layers are coaxial and do not require assembly. The locking engagement layer is precisely aligned with the axial height range of the locking arc surface 16 of the drive wheel, and the outer circumferential contour is provided with a passive gear disk locking arc surface 15. The passive gear disk locking arc surface 15 is a circular arc cylindrical surface coaxial with the central axis of the passive gear disk, and the arc radius is precisely matched with the arc radius of the locking arc surface 16 of the drive wheel. When the drive component 4 completely disengages from the tooth groove and completes engagement, the passive gear disk 5 stops rotating, and the locking arc surface 16 of the drive wheel is fully engaged with the locking arc surface 15 of the passive gear disk to restrict the circumferential rotation of the passive gear disk 5. The toothed meshing layer is precisely aligned with the axial height range of the drive component 4 of the drive wheel 3, and has a 10-tooth structure with the teeth evenly distributed along the circumference. It includes 2 meshing teeth and 2 meshing teeth, which are arranged alternately and symmetrically along the circumference, respectively corresponding to the first drive component 4 that meshes into the passive toothed disc 5 and the last drive component 4 that meshes out of the passive toothed disc 5 in the two transmission zones.

[0067] In this embodiment, each engagement tooth of the passive gear disk 5 has a guide chamfer on the tooth tip edge on the transmission entry side, and each disengagement tooth has a guide chamfer on the tooth tip edge on the transmission exit side. The chamfers are in opposite directions to guide the drive component 4 to smoothly engage and disengage from the tooth groove, eliminate rigid impact at the moment of engagement, and prevent the mechanism from jamming.

[0068] In this embodiment, the remaining 6 teeth of the passive gear disk 5 are standard transmission teeth with no guide chamfer at the tooth tip, which are used to mesh with the drive component 4 to transmit torque during the transmission stage.

[0069] The driven rocker arm 8 is fixedly mounted on the upper end face of the driven gear disk 5 by rivets, and rotates synchronously with the driven gear disk 5 on the same axis. Exemplarily, the free end of the driven rocker arm 8 is fixedly oriented at the center position between any two adjacent standard transmission teeth of any set of teeth on the driven gear disk 5.

[0070] One end of the drive link 12 is hinged to the free end of the drive crank 7 via a ball joint, and moves in a circular motion with the drive crank 7. The other end of the drive link 12 is hinged to the middle of the swing assembly 13 via a ball joint, and is used to push and pull the swing assembly 13 to swing back and forth along a lateral trajectory.

[0071] The reversing drive pin 9 is fixedly installed at the free end of the driven rocker arm 8, and its axis is parallel to the axis of the driven gear disk 5, and it moves in a circular motion with the driven rocker arm 8.

[0072] The reversing guide plate 10 is a long strip-shaped plate structure that is rotatably fitted onto the guide plate shaft 11. Two independent long strip-shaped guide grooves are formed in the middle of the plate. The guide plate shaft 11 is fixedly mounted on the frame 1. The reversing drive pin 9 is embedded in one of the guide grooves of the reversing guide plate 10, allowing it to slide within the groove and abut against the groove wall. This applies a lateral thrust to the reversing guide plate 10, causing it to oscillate back and forth along an arc-shaped trajectory with the guide plate shaft 11 as the center.

[0073] The lower end of the swing assembly 13 is connected to the frame 1 via a universal hinge mechanism 14. The middle part is embedded in a different guide groove of the reversing guide plate 10 than the reversing drive pin 9. The universal hinge mechanism 14 is a spring, with one end sleeved on the lower shaft of the swing assembly 13 and the other end fixed to the frame 1. The universal hinge mechanism 14 allows the swing assembly 13 to swing freely in two mutually perpendicular planes. Driven by the reversing guide plate 10, the swing assembly 13 reciprocates along a longitudinal trajectory, and simultaneously reciprocates along a transverse trajectory driven by the drive link 12. These two movements are precisely superimposed, resulting in a smooth, figure-eight motion trajectory for the swing assembly 13.

[0074] In this embodiment, the universal joint mechanism 14 also provides a preload force to keep the swing assembly 13 in contact with the inner wall of the guide groove of the reversing guide groove plate 10, so as to stabilize the swing process, present a smoother and more fluid figure-eight motion trajectory, and avoid trajectory deviation caused by shaking.

[0075] The flagpole assembly 18 is fixedly installed on the upper end of the swing assembly 13 to fix the flag and to present the final display effect of the figure-eight trajectory swing mechanism of the flag-waving display.

[0076] 1:1 speed ratio symmetrical interval intermittent transmission mechanism independent implementation section:

[0077] like Figure 3 As shown, an intermittent transmission with a 1:1 speed ratio includes a driving wheel 3, a driving component 4, a driven gear 5, a guide structure 6, a locking arc surface of the driven gear 15, a locking arc surface of the driving wheel 16, and a transmission zone 17.

[0078] The driving wheel 3 has a disc-shaped structure and is coaxially fixed to the output shaft of the geared motor via gears. Driven by the geared motor, it rotates continuously at a uniform speed. The driving wheel 3 has two alternating transmission zones 17 and two locking zones along its circumference, with each transmission zone 17 and each locking zone having a central angle of 90°. Five driving components 4, cylindrical pins, are evenly mounted on the lower end face of each transmission zone 17 along its circumference. These components are parallel to the axis of the driving wheel 3 and are used to engage and disengage the driven gear disc 5, transmitting torque and driving the driven gear disc 5 to rotate uniformly with the driving wheel. The outer contour of each locking zone is a driving wheel locking arc surface 16 coaxial with the driving wheel 3. The radius of the driving wheel locking arc surface 16 precisely matches the radius of the driven gear disc locking arc surface 15 of the driven gear disc 5, used to restrict the circumferential rotation of the driven gear disc 5 when it stops rotating.

[0079] The passive gear disk 5 is a disc-shaped component integrally machined and rotatably mounted on the frame 1. Its axis is parallel to the axis of the drive wheel 3, and the two are arranged side by side laterally along the frame. The passive gear disk 5 is divided into upper and lower layers along the axial direction, namely, a locking engagement layer and a tooth meshing layer from top to bottom; the two layers are coaxial and do not require assembly. The locking engagement layer is precisely aligned with the axial height range of the locking arc surface 16 of the drive wheel, and the outer circumferential contour is provided with a passive gear disk locking arc surface 15. The passive gear disk locking arc surface 15 is a circular arc cylindrical surface coaxial with the central axis of the passive gear disk, and the arc radius is precisely matched with the arc radius of the locking arc surface 16 of the drive wheel. When the drive component 4 completely disengages from the tooth groove and completes engagement, the passive gear disk 5 stops rotating, and the locking arc surface 16 of the drive wheel is fully engaged with the locking arc surface 15 of the passive gear disk to restrict the circumferential rotation of the passive gear disk 5. The toothed meshing layer is precisely aligned with the axial height range of the drive component 4 of the drive wheel 3, and has a 10-tooth structure with the teeth evenly distributed along the circumference. It includes 2 meshing teeth and 2 meshing teeth, which are arranged alternately and symmetrically along the circumference, respectively corresponding to the first drive component 4 that meshes into the passive toothed disc 5 and the last drive component 4 that meshes out of the passive toothed disc 5 in the two transmission zones.

[0080] In this embodiment, each engagement tooth of the passive gear disk 5 has a guide chamfer on the tooth tip edge on the transmission entry side, and each disengagement tooth has a guide chamfer on the tooth tip edge on the transmission exit side. The chamfers are in opposite directions to guide the drive component 4 to smoothly engage and disengage from the tooth groove, eliminate rigid impact at the moment of engagement, and prevent the mechanism from jamming.

[0081] In this embodiment, the remaining 6 teeth of the passive gear disk 5 are standard transmission teeth with no guide chamfer at the tooth tip, which are used to mesh with the drive component 4 to transmit torque during the transmission stage.

[0082] When the driving wheel completes one full rotation, the driven gear disc rotates one full rotation in segments within two independent transmission intervals.

[0083] A control method for a figure-eight trajectory swing mechanism that can be used for flag-waving displays includes the following steps:

[0084] When the mechanism is in a stationary locked state, and the driving crank 7 and the driven swing arm 8 are parallel and both are facing vertically upward, the position of the driving crank (7) at this time is defined as the 0° reference position.

[0085] After the geared motor starts, it drives the drive wheel 3 to rotate continuously clockwise. The drive wheel 3 drives the drive crank 7 to make circular motion, and the drive crank 7 pulls the swing assembly 13 to slide to the right along the guide groove of the reversing guide plate 10 through the drive connecting rod 12. Since the reversing guide plate 10 is fixed at this time, the motion of the swing assembly 13 is constrained within the first swing plane, completing the right half of the figure-eight trajectory.

[0086] When the driving crank 7 rotates to approximately 45° relative to the 0° reference position, the first drive member 4 of the first transmission zone 17 of the driving wheel 3 engages with the tooth groove of the driven gear 5, the locking state ends, the transmission state begins, and the reversing action of the swing assembly 13 begins; the driving wheel 3 continues to rotate clockwise, and the drive member 4 engages with the tooth groove of the driven gear 5 in sequence, pushing the driven gear 5 to rotate counterclockwise. The driven gear 5 drives the driven swing arm 8 to rotate synchronously, and the reversing drive pin 9 on the driven swing arm 8 slides in the groove of the reversing guide plate 10, while pushing the reversing guide plate 10 to rotate clockwise around the guide plate pivot 11. The swing assembly 13 moves in an arc-shaped motion trajectory as the reversing guide plate rotates and superimposes the longitudinal swing plane motion.

[0087] When the driving crank 7 rotates to a 90° angle relative to the 0° reference position, the driven gear 5 rotates exactly 90°, and the reversing guide plate 10 completes a half-stroke clockwise rotation. At this time, the swing assembly 13 reaches its right limit position. When the driving crank 7 rotates to a 135° angle, the last driving member 4 disengages from the tooth groove of the driven gear 5, and the next locking arc surface of the driving wheel engages with the next tooth tip arc surface of the driven gear 5. The driven gear 5 rotates to 180° and re-enters the locking state. At this time, the reversing guide plate 10 reaches its clockwise rotation limit position, and the swing assembly 13 completes the right limit position reversal.

[0088] The drive wheel 3 continues to rotate, and the drive crank 7 rotates from an angle of 135° to an angle of 225° relative to the 0° reference position. This drives the swing assembly 13 to slide to the left via the drive link 12, while the passive gear 5 remains locked.

[0089] When the driving crank 7 rotates to an angle of 225° relative to the 0° reference position, the first drive member 4 of the second transmission zone 17 of the driving wheel 3 engages with the tooth groove of the driven gear 5, the locking state ends, the transmission state begins, and the reversing action of the swing assembly 13 begins; the driving wheel 3 continues to rotate clockwise, and the drive member 4 engages with the tooth groove of the driven gear 5 in sequence, pushing the driven gear 5 to rotate counterclockwise. The driven gear 5 drives the driven swing arm 8 to rotate synchronously, and the reversing drive pin 9 on the driven swing arm 8 slides in the groove of the reversing guide plate 10, while pushing the reversing guide plate 10 to rotate counterclockwise around the guide plate pivot 11. The swing assembly 13 moves in an arc-shaped motion trajectory as the reversing guide plate rotates and superimposes the movement of the longitudinal swing plane.

[0090] When the driving crank 7 rotates to 270° relative to the 0° reference position, the driven gear 5 rotates exactly 270°, and the reversing guide plate 10 completes a half-stroke counterclockwise rotation. At this time, the swing assembly 13 reaches its left limit position. When the driving crank 7 rotates to 315°, the last driving component 4 disengages from the tooth groove of the driven gear 5, and the next locking arc surface of the driving wheel engages with the next tooth tip arc surface of the driven gear 5. The driven gear 5 rotates to 360° and re-enters the locking state. At this time, the reversing guide plate 10 reaches its counterclockwise rotation limit position, and the swing assembly 13 completes the left limit position reversal.

[0091] The drive wheel 3 continues to rotate, and the drive crank 7 rotates from an angle of 315° to 360° relative to the 0° reference position. This drives the swing assembly 13 to slide to the right via the drive link 12, while the passive gear 5 remains locked.

[0092] In this cycle, the oscillating component 13 will continuously reciprocate within two alternating oscillating planes, thus drawing a standard smooth figure-eight (∞) trajectory.

[0093] This invention employs a single power source and an innovative 1:1 intermittent transmission mechanism to achieve a smooth figure-eight flag swing, with a gentle transition in reversing motion, a smooth display trajectory without sharp corners, and no hard reversing impact. The dynamic display effect of the flag swing is more natural and beautiful, the advertising visual expression is stronger, the parts are simplified, the manufacturing cost is low, the service life is long, and the processing, assembly and subsequent maintenance are convenient.

[0094] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any person skilled in the art can easily conceive of various variations or substitutions within the technical scope disclosed in this application, and these should all be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. An 8-shaped trajectory swinging mechanism for a flag display, characterized in that, include: Rack (1); A power input device (2) is fixedly installed on the frame (1); The drive wheel (3) is coaxially fixed to the output shaft of the power input device (2) and is used to perform continuous rotational motion; The passive gear disc (5) is rotatably mounted on the frame (1) and is parallel to the rotation axis of the drive wheel (3); The driving crank (7) is coaxially fixed to the driving wheel (3); The driven swing arm (8) is coaxially fixedly connected to the driven gear plate (5); The reversing drive pin (9) is fixedly mounted on the driven swing arm (8); The reversing guide plate (10) is rotatably mounted on the frame (1) via the guide plate pivot (11). The reversing drive pin (9) is embedded in the groove of the reversing guide plate (10) to drive the reversing guide plate (10) to reciprocate in an arc around the guide plate pivot (11). The drive link (12) is hinged at one end to the drive crank (7) and at the other end to the swing assembly (13); The swing assembly (13) is hinged to the frame (1) at its lower end via a universal hinge mechanism (14), and its middle part is embedded in the guide groove of the reversing guide plate (10). The drive wheel (3) is alternately provided with two transmission zones (17) and two locking zones along the circumferential direction. The central angles of the two transmission zones (17) are equal, and the central angles of the two locking zones are equal. Each of the transmission zones (17) is provided with a plurality of driving members (4) along the circumferential direction. The axis of the driving member (4) is parallel to the axis of the driving wheel (3) and is used to mesh with the tooth groove of the passive gear plate (5) in sequence to drive the passive gear plate (5) to rotate. The outer contour of each locking zone is a locking arc surface (16) of the driving wheel (3) that is coaxial with the driving wheel (3). The radius of the locking arc surface (16) of the driving wheel matches the radius of the locking arc surface (15) of the passive gear disk (5) so that when the driving member (4) engages the tooth groove, it forms a surface contact lock with the locking arc surface (15) of the passive gear disk. When the driving wheel (3) completes a full rotation, the driven gear (5) rotates a full rotation in segments within the two independent transmission intervals, while the locking interval remains stationary.

2. An intermittent transmission mechanism of 1 : 1 revolution ratio, characterized by include: The drive wheel (3) is connected to the power source and is used to perform continuous rotational motion; The passive gear disc (5) is rotatably mounted on the mounting base and is parallel to the rotation axis of the driving wheel (3); The drive wheel (3) is alternately provided with two transmission zones (17) and two locking zones along the circumferential direction. The central angles of the two transmission zones (17) are equal, and the central angles of the two locking zones are equal. Each of the transmission zones (17) is provided with a plurality of driving members (4) along the circumferential direction. The axis of the driving member (4) is parallel to the axis of the driving wheel (3) and is used to mesh with the tooth groove of the passive gear plate (5) in sequence to drive the passive gear plate (5) to rotate. The outer contour of each locking zone is a locking arc surface (16) of the driving wheel (3) that is coaxial with the driving wheel (3). The radius of the locking arc surface (16) of the driving wheel matches the radius of the locking arc surface (15) of the passive gear disk (5) so that when the driving member (4) engages the tooth groove, it forms a surface contact lock with the locking arc surface (15) of the passive gear disk. When the driving wheel (3) completes a full rotation, the driven gear (5) rotates a full rotation in segments within the two independent transmission intervals, while the locking interval remains stationary.

3. The mechanism according to claim 1 or 2, characterized in that The central angles of the two transmission zones (17) are equal to the central angles of the two locking zones.

4. According to the mechanism of claim 3, each transmission zone (17) of the drive wheel (3) can drive the passive gear disc (5) to rotate 180°.

5. The mechanism of claim 1 or 2, wherein, The number of driving elements (4) in each transmission zone (17) is N, and the number of teeth of the passive gear disk (5) is 2N. Preferably, the value of N is 5, that is, the number of driving elements (4) in each transmission zone (17) is 5, and the number of teeth of the passive gear disk (5) is 10.

6. The mechanism of claim 1 or 2, wherein, The passive toothed disc (5) includes engagement teeth and disengagement teeth. Guide structures (6) are provided on the engagement side of the engagement teeth and the disengagement side of the engagement teeth to guide the drive component (4) to smoothly engage and disengage from the tooth groove. Preferably, the guide structure (6) is a single-sided chamfer, and the chamfers of the engagement teeth and the disengagement teeth are opened in opposite directions.

7. The mechanism of claim 1 or 2, wherein The transmission zone (17) and locking zone of the drive wheel (3) are arranged axially offset. The drive member (4) is located on the axial end face of the transmission zone (17) and the power input device (2) on the same side. The locking arc surface (16) of the drive wheel is located on the outer circumferential surface of the drive wheel (3).

8. The 8-shaped trajectory swinging mechanism for flag display according to claim 1, wherein, The swinging component (13) is used to install the display object. Preferably, the display object is a flagpole component (18) to realize the flag-waving display function.

9. A control method of an 8-shaped trajectory swinging mechanism that can be used for a flag display, characterized by, Includes the following steps: a. The power input device (2) drives the drive wheel (3) to rotate continuously; b. The drive wheel (3) drives the drive crank (7) to rotate synchronously. The drive crank (7) pulls the swing assembly (13) through the drive connecting rod (12) to continuously reciprocate along the slide groove of the reversing guide plate (10). c. When the driving wheel (3) rotates to the first driving member (4) of any transmission zone (17) and engages with the tooth groove of the driven tooth plate (5), the locking state is released; d. The driving wheel (3) continues to rotate, and the locking arc surface (16) of the driving wheel gradually disengages from the locking arc surface (15) of the passive gear plate. The driving component (4) meshes with the tooth groove of the passive gear plate (5) in sequence, pushing the passive gear plate (5) to rotate. The passive gear plate (5) drives the reversing guide plate (10) to swing in a positive arc with the guide plate shaft (11) as the center through the driven swing arm (8) and the reversing drive pin (9). At the same time, the swing component (13) enters the reversing state along the sliding groove of the reversing guide plate (10). e. When the driving wheel (3) rotates to the last driving member (4) of the current transmission zone (17) and disengages from the tooth groove of the passive gear plate (5), the passive gear plate (5) completes a 180° rotation and enters the locking state, the reversing guide plate (10) completes the forward swing, and the swing assembly (13) completes the forward reversal. f. The driving wheel (3) continues to rotate, and the locking arc surface (16) of the driving wheel fits against the locking arc surface (15) of the driven gear plate. g. When the driving wheel (3) continues to rotate until the first driving member (4) of the next transmission zone (17) engages with the tooth groove of the driven gear (5), the locking state is released again; h. The driving wheel (3) continues to rotate, and the locking arc surface (16) of the driving wheel gradually disengages from the locking arc surface (15) of the passive gear plate. The driving component (4) meshes with the tooth groove of the passive gear plate (5) in sequence, pushing the passive gear plate (5) to rotate. The passive gear plate (5) drives the reversing guide plate (10) to swing in the opposite arc with the guide plate shaft (11) as the center through the driven swing arm (8) and the reversing drive pin (9). The swing component (13) enters the reversing state again along the slide groove of the reversing guide plate (10). i. When the driving wheel (3) rotates to the last driving member (4) of the current transmission zone (17) and disengages from the tooth groove of the passive gear plate (5), the passive gear plate (5) completes the next 180° rotation and enters the locking state, the reversing guide plate (10) completes the reverse swing, and the swing assembly (13) completes the reverse reversal. j. Repeat steps b to i above to make the swing component (13) move back and forth continuously in two sets of mutually perpendicular planes, thereby drawing a smooth figure-eight trajectory.

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