Synchronous walking and driving mechanism

Abstract

The utility model relates to hoist and lift mechanical equipment technical field discloses a synchronous walking crane mechanism for polyurethane rock wool composite board production line, solves the problem of the synchronous difference of existing crane, the high maintenance cost of the roller skidding and the big energy consumption. It includes crane gantry and crane component: the gantry contains parallel crossbeam, guide rail, transverse rack, is equipped with leveling bottom plate, triangular inclined strut and guardrail, the crane component is the "" character type structure, and single transverse servo motor + mirror image transmission drive transverse gear rack is engaged, single lifting motor + gear box drives lifting shaft, is equipped with bumper, apron and the like. It can improve the transverse movement / lifting synchronization and positioning accuracy, eliminate skidding, reduce maintenance and energy consumption, and adapt to continuous production line.

Description

Technical Field

[0001] This utility model belongs to the technical field of hoisting machinery and equipment, and in particular relates to a synchronous traveling trolley mechanism. Background Technology

[0002] In the production of polyurethane rock wool composite panels, the efficient operation of continuous production lines relies on the stability and reliability of finished panel handling equipment. Among these, the synchronous traveling trolley mechanism, as the core device for finished panel handling, directly affects the stacking quality of the finished panels and the overall efficiency of the production line due to its synchronicity, positioning accuracy, and ease of maintenance. Currently, synchronous traveling trolley mechanisms used in this scenario generally adopt a left-right split-drive structure design. Specifically, each of the left and right trolleys of the trolley mechanism is equipped with a set of active rollers and a set of passive rollers. The two sets of active rollers are each independently driven by a common geared motor. That is, the traveling power of the left and right trolleys comes from their respective geared motors, which drive the active rollers to rotate, thereby enabling the trolleys to move along the guide rails to complete the finished panel handling operation. However, the existing structures described above have many technical shortcomings in practical applications, making it difficult to meet the demands of continuous production lines for efficient and precise material handling. Firstly, the poor synchronization of the left and right trolleys makes it difficult to guarantee positioning accuracy and stacking quality. Since the left and right trolleys are driven by independent ordinary geared motors, the speed of these motors is easily affected by factors such as voltage fluctuations and load changes, making it difficult to achieve perfect synchronization. This directly leads to speed differences between the left and right trolleys during movement, resulting in asynchronous movement. This asynchrony causes inaccurate positioning of the overhead crane mechanism when handling finished boards, ultimately leading to uneven stacking. This not only affects the aesthetics of the stacked boards but may also cause risks such as tipping and damage during subsequent storage and transportation due to stacking deviations, severely restricting product quality and production efficiency on the production line. Secondly, the drive roller is prone to slippage and has high maintenance costs, while also increasing motor energy consumption. In the existing structure, the drive roller serves as the driving source of the traveling mechanism, propelling the trolley through friction with the guide rail. However, during long-term operation, the contact surface between the drive roller and the guide rail is prone to wear and dust accumulation, leading to a decrease in friction and frequent slippage, which affects the normal operation of the traveling mechanism. To alleviate the slippage problem, existing technologies often use rubber coating on the surface of the drive roller to increase friction. However, the rubber coating layer is easily worn under long-term friction with the guide rail and needs to be replaced periodically. Since the traveling mechanism is usually installed at a high altitude, replacing the worn rubber-coated roller requires high-altitude operations, which are difficult and unsafe. Furthermore, the replacement process requires stopping the production line, increasing the labor and time costs of after-sales maintenance and affecting the continuous operation of the production line. In addition, while the rubber coating increases friction, it also increases the resistance when the drive roller rotates. To ensure the normal travel speed of the trolley, a more powerful geared motor needs to be selected. This not only increases the initial purchase cost of the equipment, but also increases the energy consumption during motor operation, which does not meet the requirements of energy conservation, environmental protection and low-cost production. In summary, the existing synchronous traveling crane mechanism used for handling finished panels in continuous production lines of polyurethane rock wool composite panels has significant shortcomings in terms of synchronization, reliability, and economy. It is difficult to meet the production line's requirements for efficient, precise, and low-maintenance handling operations, and its structure urgently needs to be improved and optimized. Utility Model Content

[0003] In view of this, the present invention aims to overcome the defects of the prior art by using a synchronous drive structure and a gear and rack traveling mechanism to ensure synchronous lateral movement, thereby providing a synchronous traveling vehicle mechanism.

[0004] To achieve the above objectives, the technical solution of this utility model is implemented as follows: A synchronous traveling crane mechanism includes a crane gantry and a crane component, wherein the crane component is movably mounted on the top of the crane gantry; The top of the overhead gantry has two parallel crossbeams, each with a guide rail. The guide rail body is entirely laid on the top of the crossbeams. The length of the guide rail is less than the length of the crossbeam. The two sets of guide rails are parallel to each other. The inner sides of the two crossbeams are mirrored with transverse racks. The transverse racks are parallel to the crossbeams, and the two transverse racks are parallel to each other. The crane components include a main beam, trolley beams, roller assembly, lifting reduction motor, lifting transmission mechanism, lifting gearbox, lifting rack, lifting shaft, lateral gear, lateral transmission mechanism, lateral servo reduction motor, and motor base. A trolley beam is vertically fixed to each end of the main beam, and the main beam and the two trolley beams are connected in an "I" shape. The roller assembly is located at the bottom of the trolley beams, partially embedded in them. Each trolley beam has a roller assembly at both its front and rear ends, and the trolley beams are supported on guide rails via the roller assemblies. The lifting reduction motor is fixed to the upper middle of the main beam, and two sets of lifting gearboxes are fixed to the main beams on both sides of the lifting reduction motor, close to the adjacent... The trolley beam has a lifting rack fixed on its lifting shaft. The lifting shaft is vertically inserted into and passes through the lifting gearbox. The lifting rack meshes with the gears inside the lifting gearbox. The lifting reduction motor is connected to the lifting gearboxes on both sides through the lifting transmission mechanism. Different grippers or suction cup mechanisms can be connected to the lower end of the lifting shaft. The transverse servo reduction motor is fixed to the middle of the side of the trolley beam through the motor base. Two sets of transverse gears mesh with the transverse racks on both sides. The output ends of the transverse servo reduction motor on both sides are connected to the transverse gears through the transverse transmission mechanism. There are two sets of transverse transmission mechanisms, which are connected to the transverse gears and then synchronously connected to the output ends of the transverse servo reduction motor. The structures on both sides of the transverse servo reduction motor are mirrored.

[0005] In a structure that optimizes the aforementioned solution, the overhead gantry also includes uprights, horizontal braces, diagonal braces, and guardrails. Two sets of horizontal braces and two sets of horizontal beams are arranged opposite each other and connected perpendicularly to form a rectangular plane. The tops of the four sets of uprights are perpendicularly connected to the four vertices of the rectangular plane. The guardrails are set within the plane formed by the horizontal braces and the two uprights, and are connected to these two uprights. The guardrails are located below the horizontal braces. Diagonal braces are provided at the adjacent positions of the uprights and horizontal braces, and the uprights and horizontal beams. "Adjacent" means adjacent or contacting, and the diagonal braces form a triangular stable structure. Figure 1 The system employs a combination of a rectangular planar frame and triangular braces. A rigid skeleton is formed by vertical connections between the cross braces and beams, while the columns and braces constitute a triangular stability system, significantly enhancing the overall torsional and bending resistance of the overhead gantry. This design can offset structural deformation caused by eccentric loads or inertial forces during handling, ensuring the installation accuracy of the guide rails and transverse racks, thereby guaranteeing the synchronicity and positioning accuracy of the gantry components. Four sets of columns evenly bear the weight of the gantry components, and the diagonal braces distribute concentrated loads to the cross braces and beams, avoiding stress concentration at single points. For example, when the gantry components are fully loaded, the diagonal braces can convert the vertical load into a horizontal component, reducing the bending moment at the column base and extending the structural service life.

[0006] In a structure that optimizes the aforementioned solution, the gantry crane further includes leveling base plates, with each of the four sets of uprights having a leveling base plate between its bottom and the supporting surface. These four sets of leveling base plates are positioned at the bottom of the uprights, and by adjusting the height of the base plates, they compensate for deviations in ground flatness, ensuring that the parallelism error of the guide rails on the top surface of the crossbeam is controlled within allowable limits. This precision directly affects the smooth operation of the roller device, preventing roller slippage due to guide rail tilt. The increased contact area between the base plate and the ground, typically 2-3 times the cross-sectional area of ​​the uprights, reduces pressure per unit area and minimizes vibration transmission to the main structure of the gantry crane. For scenarios involving high-frequency, high-inertia loads (such as stacked sheet metal), this effectively suppresses structural resonance.

[0007] In a structure that optimizes the aforementioned solution, a limiting buffer component is also included. This limiting buffer component comprises a stop and a buffer. The stop is fixed to both ends of the crossbeam, and the buffer is fixed to both ends of the trolley beam. The buffer and the stop are positioned to cooperate. The buffer is a spring or a structure with an elastic buffer component. The stop, fixed to both ends of the crossbeam, cooperates with the buffer of the trolley beam to limit the lateral movement limit of the traveling component, preventing overtravel collisions caused by servo motor malfunction. For example, when the lateral servo reduction motor experiences a communication failure, the buffer can absorb the remaining kinetic energy, preventing the rack and gear from being forcibly disengaged. The buffer uses a spring or elastic material (such as polyurethane) to convert the impact load into elastic deformation energy. Taking a spring buffer as an example, its stiffness design needs to match the inertial force of the traveling component, such as mass × acceleration under full load, to ensure that the maximum impact force during a collision does not exceed the allowable stress of the structure. Simultaneously, the buffer can reduce mechanical noise during shutdown, improving the workshop environment. For fragile polyurethane rock wool composite panels, the buffer can prevent edge damage caused by the panel tilting forward due to inertia during emergency stops. In addition, elastic buffering can reduce the instantaneous impact load on the transverse gear and rack, and extend the tooth surface life.

[0008] In a structure that optimizes the aforementioned solution, the lifting transmission mechanism includes a lifting transmission shaft, a rigid coupling, and a roller chain coupling A. Roller chain coupling A is connected to the output end of the lifting gear motor. One end of the lifting transmission shaft is connected to roller chain coupling A, and the other end is connected to the rigid coupling. The rigid coupling is connected to the input end of the lifting gearbox. The double-row roller chain structure of roller chain coupling A can compensate for radial misalignment (±0.5mm) and angular misalignment (±1°) between shafts, while transmitting torque up to 5000 N·m. This characteristic accommodates minor misalignment during the installation of the lifting gear motor and gearbox, avoiding bearing overload or gear wear caused by rigid connections. When the lifting shaft is obstructed by foreign objects or overloaded, the roller chain coupling can achieve overload protection through chain slippage, preventing motor burnout. Furthermore, the coupling requires no lubrication and is easy to disassemble, extending the maintenance cycle to more than 6 months, significantly reducing the frequency of high-altitude operations. The rigid coupling directly connects the drive shaft and the gearbox input shaft, ensuring that the lifting gearboxes on both sides move synchronously, so that the displacement deviation of the lifting racks at both ends of the lifting shaft is ≤0.2mm, which meets the requirements of high-precision stacking.

[0009] In a structure that optimizes the aforementioned solution, the lateral transmission mechanism includes a lateral transmission shaft, a bearing housing, and a roller chain coupling B. The lateral transmission shaft is fixed to the side of the crane beam via the bearing housing. The roller chain coupling B is connected to the output end of the lateral servo geared motor. One end of the lateral transmission shaft is connected to the roller chain coupling B, and the other end is connected to the lateral gears. The lateral servo geared motor drives the lateral gears on both sides via the roller chain coupling B, achieving a speed difference of ≤0.1% between the left and right lateral gears, greatly improving displacement synchronization accuracy. This high-precision synchronous control completely solves the asynchrony problem of traditional dual-motor independent drives. The lateral transmission shaft is supported by the bearing housing, reducing shaft deflection. The lubrication-free design of the roller chain coupling B is suitable for dusty environments, extending the maintenance cycle to more than one year, meeting the continuous operation requirements of the production line. The rapid start-stop characteristics of the servo motor, combined with the elastic buffer of the roller chain coupling, suppresses the inertial impact during lateral start / brake, reducing wear on the rack.

[0010] In a structure that optimizes the aforementioned solution, a cover plate is also included. The cover plate is fixed to the shaft hole on the side of the transverse gear that is not connected to the transverse drive shaft. The cover plate is fastened to the gear shaft end by bolts, restricting the axial movement of the transverse gear and ensuring that the meshing depth between the gear and the rack is maintained at the design value, thus avoiding transmission failure caused by movement.

[0011] In a structure that optimizes the aforementioned solution, the roller device includes a roller, a roller shaft, a bushing, and a bearing. The bearing is embedded in the shaft hole of the roller, and the roller portion is embedded in a slot in the lower part of the carriage beam. The roller shaft passes through an opening on the side of the carriage beam and the bearing, rotatably fixing the roller to the bottom of the carriage beam. A bushing is fixed to one end of the roller shaft. The bushing restricts the axial movement of the roller shaft, ensuring full-width contact between the roller and the guide rail and avoiding localized wear. The roller portion is embedded in the slot of the carriage beam, and the interference fit between the shaft hole and the bearing ensures installation rigidity. This design can control the roller runout within a fixed range, meeting the stability requirements during high-speed lateral movement.

[0012] The synchronous traveling mechanism provided by this utility model addresses the core shortcomings of existing synchronous traveling mechanisms, namely "poor synchronization, easy slippage, high maintenance costs, and high energy consumption." Through innovative structural design, it achieves comprehensive optimization and realizes the following significant technical advantages: To address the problems of synchronization issues, inaccurate positioning, and uneven stacking caused by independent motor drives for the left and right trolleys in existing technologies, as well as the slippage of friction-driven rollers, the need for frequent replacement of the coating layer (difficult for high-altitude operations, significant production downtime), and the high energy consumption due to increased resistance from coating, this utility model adopts a single transverse servo geared motor + mirror transmission mechanism on both sides. The transverse gears are synchronously driven by symmetrical transmission shafts and couplings, avoiding speed discrepancies between the two motors through a single power source and symmetrical path. Combined with a rigid "I"-shaped connection between the trolley beam and the carriage beam, and rollers guided along guide rails, synchronous transverse movement is ensured. Lifting is also synchronously driven by a single motor through a gearbox, combined with rack and pinion meshing to prevent board tilting, fundamentally solving the problem of uneven stacking, reducing the risk of finished board damage, and improving production quality and efficiency. Furthermore, replacing friction drive with rack and pinion meshing eliminates wear and dust impacts on transmission, eradicates slippage, and the rollers only provide support and guidance, eliminating the need for coating. This saves on high-altitude maintenance costs and production downtime losses, while also reducing motor power and energy consumption, meeting energy conservation and environmental protection requirements. In addition, the gantry frame's "column + horizontal brace + diagonal brace" triangular system enhances its torsional and bending resistance, the leveling base plate compensates for ground deviations and protects the rollers, the coupling protects the motor from overload, the buffer components absorb collision kinetic energy and reduce noise, the cover plate prevents dust and protects the gears, and extends the equipment's lifespan. In terms of operation, the guardrail ensures safety at heights, the buffer prevents damage to the sheet metal from sudden stops, the lifting shaft can flexibly connect to the gripper to adapt to different sheet metal, and the coupling requires no lubrication to adapt to dusty environments, meeting the needs of continuous production lines. Attached Figure Description

[0013] The accompanying drawings, which form part of this utility model, are used to provide a further understanding of the utility model. The illustrative embodiments of the utility model and their descriptions are used to explain the utility model and do not constitute an undue limitation of the utility model. In the drawings: Figure 1 This is a schematic diagram of the synchronous traveling trolley mechanism described in this utility model.

[0014] Figure 2 This is a schematic diagram of the synchronous traveling trolley mechanism described in this utility model.

[0015] Figure 3 This is a front view structural diagram of the synchronous traveling trolley mechanism described in this utility model.

[0016] Figure 4 This is a cross-sectional structural diagram of the roller device described in this utility model.

[0017] Explanation of reference numerals in the attached figures: 1-Leveling base plate, 2-Column, 3-Horizontal brace, 4-Diagonal brace, 5-Guardrail, 6-Crossbeam, 7-Stop, 8-Guide rail, 9-Transverse rack, 10-Tractor components, 11-Tractor main beam, 12-Trolley beam, 13-Roller device, 14-Buffer, 15-Lifting reduction motor, 16-Lifting drive shaft, 17-Rigid coupling, 18-Lifting gearbox, 19-Lifting rack, 20-Lifting shaft, 21-Roller chain coupling A, 22-Cover plate, 23-Transverse gear, 24-Transverse drive shaft, 25-Bearing seat, 26-Roller chain coupling B, 27-Transverse servo reduction motor, 28-Motor seat, 29-Roller, 30-Roller shaft, 31-Shaft sleeve, 32-Bearing. Detailed Implementation

[0018] It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments of the present invention can be combined with each other.

[0019] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientation or positional relationships based on the orientation or positional relationships shown in the accompanying drawings, are only for the convenience of describing this utility model and simplifying the description, 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, and therefore should not be construed as a limitation of this utility model. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, features defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more.

[0020] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; 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; and they can refer to the internal connection of 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.

[0021] The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0022] The synchronous traveling crane mechanism disclosed in this embodiment aims to solve the problems of poor synchronization, inaccurate positioning, and high maintenance costs in the handling of finished panels in a continuous production line of polyurethane rock wool composite panels. Its specific structure is as follows: Figure 1-4 As shown, the synchronous traveling crane mechanism described in this embodiment includes a crane gantry and a crane component 10, with the crane component 10 movably mounted on the top of the crane gantry. The overhead crane gantry is an integral support frame, comprising 4 sets of leveling base plates 1, 4 sets of uprights 2, 2 sets of cross braces 3, 8 sets of diagonal braces 4, 2 sets of guardrails 5, 2 sets of crossbeams 6, 4 sets of stop seats 7, 2 sets of guide rails 8, and 2 sets of transverse racks 9. The leveling base plate 1 is a square steel plate with bolt holes, located between the bottom of the uprights 2 and the ground. Its height is adjusted to compensate for ground flatness deviations and ensure a horizontal reference. The uprights 2 are square tubular structures. The cross braces 3 are perpendicularly connected to the crossbeams 6, with diagonal deviations meeting requirements. The top of the uprights is fixed to the apex of the rectangular planar frame formed by welding the cross braces 3 and crossbeams 6, and the bottom is connected to the leveling base plate. Plate 1 is connected; diagonal brace 4 is fixed at the adjacent positions of column 2 and cross brace 3, and column 2 and cross beam 6, forming a triangular stable structure to distribute eccentric load and reduce bending moment at the root of column 2; guardrail 5 is a protective railing welded from round steel, located below cross brace 3 and fixed to column 2; guide rail 8 is a crane-specific guide rail, fixed to the top surface of cross beam 6 by bolts and kept parallel, with a length less than cross beam 6; transverse rack 9 is fixed to the inner side of cross beam 6 by bolts, parallel to cross beam 6 and with compliant tooth pitch deviation; stop seat 7 is fixed to both ends of cross beam 6 and has a buffer pad pasted on the inner side, used to cooperate with buffer 14 to achieve limit.

[0023] The traveling unit 10 is an "I"-shaped movable transport execution unit, comprising a traveling beam 11, two sets of trolley beams 12, four sets of roller devices 13, four sets of buffers 14, a lifting system, and a traverse system. The two sets of trolley beams 12 are vertically fixed to both ends of the traveling beam 11. The roller devices 13 are located near the lower front and rear ends of each trolley beam 12, and consist of cast steel rollers 29, steel roller shafts 30, brass bushings 31, and deep groove ball bearings 32. The rollers 29 are partially embedded in the slots of the trolley beams 12 and are rotatably fixed to the bearings 32 via the roller shafts 30. The bushings 31 restrict axial movement to ensure full-width contact between the rollers 29 and the guide rails 8. The lifting system includes a variable frequency lifting reduction motor 15, a lifting transmission shaft 16, a rigid coupling 17, two sets of hard-tooth cylindrical lifting gearboxes 18, a lifting rack 19, a lifting shaft 20, and a roller chain coupling A21. The motor 15 is fixed to the traveling beam. In the middle of beam 11, drive shaft 16 connects motor 15 and gearbox 18 via coupling (to compensate for shaft misalignment). Lifting shaft 20 is welded with rack 19 and meshes with gearbox 18. A flange interface is reserved at the lower end to connect to a vacuum suction cup mechanism adapted to polyurethane rock wool composite board. The transverse system includes servo transverse servo reduction motor 27, motor base 28, two sets of transverse drive shafts 24, bearing housing 25, roller chain coupling B26, two sets of transverse gears 23, and circular steel plate cover 22. Motor 27 is fixed to the side of the traveling beam 11 via motor base 28. Drive shaft 24 connects motor 27 and transverse gear 23 via coupling. Gear 23 meshes with transverse rack 9 and ensures meshing depth. Cover 22 is fixed to the shaft hole of gear 23. Buffer 14 is a spring buffer, fixed at both ends of trolley beam 12 and corresponding to stop seat 7. It can absorb overtravel collision kinetic energy to prevent gear rack from disengaging.

[0024] Workflow: This synchronous traveling crane mechanism is based on the core principle of "coordinated lateral movement and lifting action." Relying on the fixed support of the crane gantry and the movable execution of the crane component 10, it solves the problems of poor synchronization, slippage, and high maintenance costs in existing technologies through single power source drive, gear and rack meshing transmission, and symmetrical structural design. During operation, the crane gantry is used to ensure structural reference before operation. In this embodiment, the adjusting base plate 1 compensates for deviations in the flatness of the workshop floor by adjusting its height, ensuring that the parallelism of the guide rail 8 on the top surface of the crossbeam 6 meets the requirements. The triangular stabilization system composed of "column 2 + cross brace 3 + diagonal brace 4" offsets the eccentric load and inertial force during handling, preventing the guide rail 8 and lateral movement rack 9 from deviating from the reference due to deformation. When lateral movement is required, the mechanism is fixed to the crane... The lateral servo reduction motor 27 on the side of the main beam 11 starts, and the power on both sides is synchronously transmitted to two sets of lateral gears 23 through the symmetrical lateral transmission mechanism roller chain coupling B26 and lateral transmission shaft 24. The lateral transmission shaft 24 is fixed by the bearing seat 25 to reduce shaft deflection. The roller chain coupling B26 compensates for the misalignment between shafts and is lubrication-free and suitable for dusty environments. Then, the lateral gear 23 meshes with the lateral rack 9 on the inner side of the crossbeam 6 (the meshing depth of the gear and rack is compliant, and the cover plate 22 is at the shaft hole of the lateral gear 23), driving the traveling component 10 to move horizontally along the guide rail 8. The weight of the traveling component 10 is borne by the roller device 13 at the bottom of the trolley beam 12. The cast steel roller 29 rotates through the deep groove ball bearing 32, and the brass bushing 31 restricts the movement of the roller shaft 30 to ensure that it is in contact with the roller. When the guide rail 8 is in full-width contact and approaches the extreme positions at both ends of the crossbeam 6, the spring buffers 14 at both ends of the trolley beam 12 contact the stop seat 7 (with a buffer pad on the inside) to absorb energy, preventing the gear rack from disengaging and the plate from breaking due to sudden stop. Furthermore, because the lateral movement power originates from the same motor and the transmission mechanism is symmetrical, the speed deviation of the two motors is completely avoided. When it is necessary to grab / release the plate, the lifting reduction motor 15 on the upper part of the overhead beam 11 starts, and the power is synchronously transmitted to the lifting gearboxes 18 on both sides through the lifting transmission mechanism (roller chain coupling A21, lifting transmission shaft 16, rigid coupling 17). The roller chain coupling A21 compensates for the shaft misalignment and can overload and slip to protect the motor, while the rigid coupling 17 ensures efficient power transmission. Subsequently, the gears inside the lifting gearbox 18 and the lifting shaft 20... The lifting rack 19 engages with the lifting shaft 20, which is vertically lifted and lowered (the flange at the lower end of the lifting shaft 20 is connected to a vacuum suction cup adapted to the polyurethane rock wool composite board, which can be flexibly replaced). The lifting gear boxes 18 on both sides are driven by the same motor and have the same transmission path, ensuring synchronous lifting and avoiding tilting of the board. In this embodiment, the mechanism completes the transportation through a cycle of "lifting and gripping → synchronous lateral movement → lifting and releasing → resetting and waiting". In the initial state, the trolley component 10 is stopped above the finished product output end of the production line and the lifting shaft 20 is at a high position. When lifting and gripping, the lifting shaft 20 descends, the suction cup adsorbs the board and then rises to a safe height. When synchronously laterally moving, the trolley component 10 is driven to move to the stacking area. When lifting and releasing, the lifting shaft 20 descends, the suction cup releases the board and then rises. Finally, the trolley component 10 resets and waits.During operation, the gantry guardrail 5 ensures safety during high-altitude maintenance, the buffer 14 reduces mechanical noise, the roller chain couplings A21 and B26 require no lubrication and are suitable for dusty environments, and the cover plate 22, stop seat, and buffer pad extend the equipment's lifespan. In summary, this operating method, through "single power source synchronous drive + gear and rack meshing + symmetrical structural support," achieves efficient, precise, and low-maintenance handling of polyurethane rock wool composite panels, completely resolving the core defects of existing technologies.

[0025] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A synchronous traveling crane mechanism, characterized in that: Includes a crane gantry and a crane component (10), the crane component (10) being movably mounted on top of the crane gantry; The top of the overhead gantry has two horizontal beams (6) arranged in parallel, and guide rails (8) are respectively installed on the two horizontal beams (6). The inner sides of the two horizontal beams (6) are mirrored with transverse racks (9). The crane component (10) includes a main beam (11), a trolley beam (12), a roller device (13), a lifting reduction motor (15), a lifting transmission mechanism, a lifting gearbox (18), a lifting rack (19), a lifting shaft (20), a transverse gear (23), a transverse transmission mechanism, a transverse servo reduction motor (27), and a motor base (28). A trolley beam (12) is vertically fixed to each end of the main beam (11). The roller device (13) is located at the bottom of the trolley beam (12), and the trolley beam (12) is mounted on the guide rail (8) via the roller device (13). The lifting reduction motor (15) is fixed in the middle of the upper part of the main beam (11), and two sets of lifting gearboxes (18) are respectively... The lifting shaft (20) is fixed on the crane beam (11) on both sides of the lifting reduction motor (15). The lifting shaft (20) is fixed with a lifting rack (19). The lifting shaft (20) is vertically inserted into the lifting gear box (18) and passes through it. The lifting rack (19) meshes with the gear in the lifting gear box (18). The lifting reduction motor (15) is connected to the lifting gear box (18) on both sides through the lifting transmission mechanism. The transverse servo reduction motor (27) is fixed in the middle of the side of the crane beam (11) through the motor base (28). The two sets of transverse gears (23) mesh with the transverse racks (9) on both sides. The output ends of the transverse servo reduction motor (27) on both sides are connected to the transverse gears (23) through the transverse transmission mechanism.

2. The synchronous traveling crane mechanism according to claim 1, characterized in that: The overhead gantry also includes columns (2), cross braces (3), diagonal braces (4), and guardrails (5). Two sets of cross braces (3) and two sets of cross beams (6) are arranged opposite to each other and connected vertically to form a rectangular plane. The tops of the four sets of columns (2) are connected vertically to the four vertices of the rectangular plane. The guardrails (5) are set in the plane formed by the cross braces (3) and the two columns (2) and are connected to the two columns (2). Diagonal braces (4) are set at the adjacent positions of the columns (2) and the cross braces (3) and the columns (2) and the cross beams (6).

3. The synchronous traveling crane mechanism according to claim 2, characterized in that: The overhead gantry also includes a leveling base plate (1), and the bottom of the four sets of columns (2) are respectively provided with leveling base plates (1) between them and the support surface.

4. The synchronous traveling crane mechanism according to claim 1, characterized in that: It also includes a limiting buffer component, which includes a stop (7) and a buffer (14). The stop (7) is fixed at both ends of the crossbeam (6), and the buffer (14) is fixed at both ends of the trolley beam (12). The buffer (14) and the stop (7) are in position to cooperate.

5. The synchronous traveling crane mechanism according to claim 1, characterized in that: The lifting transmission mechanism includes a lifting transmission shaft (16), a rigid coupling (17), and a roller chain coupling A (21). The roller chain coupling A (21) is connected to the output end of the lifting reduction motor (15). One end of the lifting transmission shaft (16) is connected to the roller chain coupling A (21), and the other end is connected to the rigid coupling (17). The rigid coupling (17) is connected to the input end of the lifting gearbox (18).

6. The synchronous traveling crane mechanism according to claim 1, characterized in that: The transverse transmission mechanism includes a transverse transmission shaft (24), a bearing housing (25), and a roller chain coupling B (26). The transverse transmission shaft (24) is fixed to the side of the crane beam (11) through the bearing housing (25). The roller chain coupling B (26) is connected to the output end of the transverse servo reduction motor (27). One end of the transverse transmission shaft (24) is connected to the roller chain coupling B (26), and the other end of the transverse transmission shaft (24) is connected to the transverse gear (23).

7. The synchronous traveling crane mechanism according to claim 6, characterized in that: It also includes a cover plate (22), which is fixed on the side of the transverse gear (23) that is not connected to the transverse drive shaft (24).

8. The synchronous traveling crane mechanism according to claim 1, characterized in that: The roller device (13) includes a roller (29), a roller shaft (30), a bushing (31), and a bearing (32). The bearing (32) is embedded in the shaft hole of the roller (29). The roller (29) is partially embedded in the slot at the bottom of the trolley beam (12). The roller shaft (30) passes through the opening on the side of the trolley beam (12) and the bearing (32). One end of the roller shaft (30) is fixed to the bushing (31).

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