Dual-float roller mechanism

Abstract

The utility model discloses a double floating roller mechanism, including first support, install the crossbeam of first support, rotatablely install the first pivot of first support, with the first swing arm of first pivot is connected, and one end rotatablely connected with the one end of first swing arm's first guide roller, install the second pivot of first support, one end with the second swing arm of second pivot is connected, and one end rotatablely connected with the other end of second swing arm's second guide roller, the first connecting mechanism of connecting first swing arm and second swing arm, and install the first cylinder of crossbeam, the utility model discloses the linkage cooperation of first swing arm and second swing arm, combines the accurate adjustment of cylinder drive and connecting mechanism, forms double floating roller synchronous action system, can effectively absorb the tension fluctuation caused by the non-roundness of parent roll, has the advantage that promotes tension stability, realizes accurate linkage adjustment.

Description

Technical Field

[0001] This utility model relates to the field of slitting and winding processing, specifically to a double floating roller mechanism. Background Technology

[0002] In the field of slitting and winding, irregularities in the roundness of the slitting master roll and unstable tension are common problems. When processing materials with low tension, these issues can easily lead to stretching and deformation. Such deformation not only reduces the quality of the wound film roll but can also cause defects such as wrinkles and scratches, and in severe cases, can interfere with the normal operation of subsequent production processes.

[0003] To address the aforementioned issues, existing slitting and unwinding machines are typically equipped with floating rollers. The main function of the floating rollers is to establish and maintain stable tension on the material being slit and unwound, while simultaneously buffering fluctuations caused by the non-roundness of the master roll. In this way, the floating rollers ensure that the material released from the master roll is flat, thereby meeting the material quality requirements of subsequent production processes.

[0004] However, existing floating roller designs still have some shortcomings in practical applications. For example, the adaptability and stability of floating rollers need to be improved when handling materials of different materials and thicknesses. Furthermore, the maintenance and adjustment of floating rollers are relatively complex, increasing the difficulty and cost of operation. Therefore, developing a novel floating roller structure to improve the performance and adaptability of slitting machines has become a problem urgently needing to be solved by those skilled in the art. Utility Model Content

[0005] The technical problem to be solved by this utility model is to overcome the defects in the prior art and provide a double floating roller mechanism.

[0006] The present invention solves the above-mentioned technical problems through the following technical solution:

[0007] A dual floating roller mechanism, comprising:

[0008] First support;

[0009] The crossbeam is installed on the first support;

[0010] The first rotating shaft is rotatably mounted on the first support;

[0011] A first swing arm is connected to the first rotating shaft, and the first swing arm is configured to rotate synchronously with the first rotating shaft;

[0012] The first guide roller is rotatably connected at one end to one end of the first swing arm;

[0013] The second rotating shaft is installed on the first support and is spaced apart from both the first rotating shaft and the crossbeam.

[0014] The second swing arm has one end connected to the second rotating shaft, and the second swing arm is configured to rotate around the second rotating shaft or rotate synchronously with the second rotating shaft;

[0015] The second guide roller is rotatably connected at one end to the other end of the second swing arm;

[0016] The first connecting mechanism has one end rotatably connected to the other end of the first swing arm at a first connecting point, and the other end of the first connecting mechanism is rotatably connected to the second swing arm at a second connecting point. The first rotating shaft is located between the first connecting point and the first guide roller, and the second connecting point is located between the second rotating shaft and the second guide roller.

[0017] A first cylinder is mounted on the crossbeam, and the piston rod of the first cylinder is connected to the second swing arm at a third connection point, which is located between the second connection point and the second guide roller.

[0018] Preferably, the first swing arm is in the shape of a long rod; and / or, the first swing arm is in the shape of a long rod.

[0019] Preferably, the first connecting mechanism includes:

[0020] Screw;

[0021] The first ball joint is threaded to one end of the screw and hinged to the first swing arm at the first connection point;

[0022] The second ball joint is threaded to the other end of the screw and hinged to the second swing arm at the second connection point.

[0023] Preferably, it further includes:

[0024] The third ball joint is detachably connected to the piston rod of the first cylinder and hinged to the second rocker arm at the third connection point.

[0025] Preferably, the first rotating shaft is provided with a first anti-rotation feature;

[0026] The first swing arm has a through hole, the first rotating shaft passes through the through hole, and the inner wall of the through hole is provided with a second anti-rotation feature that cooperates with the first anti-rotation feature.

[0027] Preferably, both the first anti-rotation feature and the second anti-rotation feature are planar.

[0028] Preferably, the second rotating shaft is fixedly connected to the first support, the second rotating shaft is a tapered rotating shaft, and a bearing is sandwiched between the second rotating shaft and the second swing arm.

[0029] Preferably, it further includes:

[0030] The base includes a triangular portion and a base plate portion. The base plate portion is connected to one side of the triangular portion and to the crossbeam. The end of the first cylinder opposite to the piston is rotatably connected to one corner of the triangular portion via a pivot.

[0031] Preferably, it further includes:

[0032] The second support is provided, and the two ends of the crossbeam are respectively connected to the first support and the second support;

[0033] The third shaft is rotatably mounted on the second support;

[0034] A third swing arm is connected to the third rotating shaft, and the third swing arm is configured to rotate synchronously with the third rotating shaft; the other end of the first guide roller is rotatably connected to one end of the third swing arm;

[0035] The fourth rotating shaft is installed on the second support and is spaced apart from both the third rotating shaft and the crossbeam;

[0036] The fourth swing arm has one end connected to the fourth rotating shaft, and the fourth swing arm is configured to rotate about the fourth rotating shaft or rotate synchronously with the fourth rotating shaft; the other end of the second guide roller is rotatably connected to the other end of the fourth swing arm.

[0037] The second connecting mechanism has one end rotatably connected to the other end of the third swing arm at a fourth connecting point, and the other end of the second connecting mechanism is rotatably connected to the fourth swing arm at a fifth connecting point. The third rotating shaft is located between the fourth connecting point and the first guide roller, and the fifth connecting point is located between the fourth rotating shaft and the second guide roller.

[0038] The second cylinder is installed on the crossbeam, and the piston rod of the second cylinder is connected to the fourth swing arm at the sixth connection point, which is located between the fifth connection point and the second guide roller.

[0039] Preferably, it also includes a PLC and a controller, which automatically calculate the required air pressure based on the set unwinding tension value and output it to the cylinder through an electro-pneumatic converter.

[0040] Based on common knowledge in the field, the above-mentioned preferred conditions can be combined arbitrarily to obtain various preferred embodiments of this utility model.

[0041] The positive and progressive effects of this utility model are as follows: This utility model forms a double floating roller synchronous action system by linking the first swing arm and the second swing arm, combined with the precise adjustment of the cylinder drive and the connecting mechanism. It can effectively absorb the tension fluctuations caused by the non-roundness of the master roll, and has the advantages of improving tension stability and realizing precise linkage adjustment. Attached Figure Description

[0042] Figure 1 This is a perspective view of the double floating roller mechanism of a preferred embodiment of the present invention.

[0043] Figure 2 This is a front view of the double floating roller mechanism of a preferred embodiment of the present invention.

[0044] Figure 3 This is a perspective view of the double floating roller mechanism of a preferred embodiment of the present invention.

[0045] Figure 4 This is a perspective view of the first rod and the base of a preferred embodiment of the present invention.

[0046] Figure 5 This is a perspective view of the first connecting mechanism of a preferred embodiment of the present utility model.

[0047] Figure 6 This is a schematic diagram of the first anti-rotation feature of a preferred embodiment of the present invention.

[0048] Explanation of reference numerals in the attached figures:

[0049] First support 1

[0050] Horizontal beam 2

[0051] First pivot 3

[0052] First swing arm 4

[0053] First guide roller 5

[0054] Second pivot 6

[0055] Second swing arm 7

[0056] Second guide roller 8

[0057] First connecting mechanism 9

[0058] Screw 91

[0059] First ball joint 92

[0060] Second ball joint 93

[0061] Cylinder 10

[0062] Third ball joint 11

[0063] First anti-rotation feature 12

[0064] Base 13

[0065] Triangle part 131

[0066] Base plate 132

[0067] Third pivot 14

[0068] Third swing arm 15

[0069] Fourth pivot 16

[0070] Fourth swing arm 17

[0071] Second connecting mechanism 18

[0072] Second cylinder 19 Detailed Implementation

[0073] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present utility model or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the scope of protection of the present utility model.

[0074] It should be noted that in the claims and specification of this patent, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one" does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes the element.

[0075] like Figures 1-6As shown, this application proposes a double floating roller mechanism, including a first support 1, a crossbeam 2 mounted on the first support 1, a first rotating shaft 3 rotatably mounted on the first support 1, a first swing arm 4 connected to the first rotating shaft 3, a first guide roller 5 rotatably connected at one end to one end of the first swing arm 4, a second rotating shaft 6 mounted on the first support 1, a second swing arm 7 connected at one end to the second rotating shaft 6, a second guide roller 8 rotatably connected at one end to the other end of the second swing arm 7, a first connecting mechanism 9 connecting the first swing arm 4 and the second swing arm 7, and a first cylinder 10 mounted on the crossbeam 2. The first connecting mechanism 9 is rotatably connected at both ends to the first swing arm 4 and the second swing arm 7, respectively. The first rotating shaft 3 is located between the first connecting point and the first guide roller 5, the second connecting point is located between the second rotating shaft 6 and the second guide roller 8, and the piston rod of the first cylinder 10 is connected to the second swing arm 7 at a third connecting point located between the second connecting point and the second guide roller 8.

[0076] The first support 1 refers to the rigid support component that bears the overall structure. The crossbeam 2 refers to the bridging component connecting the first support 1, which can be an I-beam steel beam. Both ends are fixed to the support bolts via flanges, providing an installation reference surface for the cylinder. The first rotating shaft 3 refers to the shaft component that drives the first swing arm 4 to rotate. It can be a stepped shaft structure with self-aligning roller bearings at both ends to achieve rotational support and axial positioning. The first connecting mechanism 9 refers to the connecting rod assembly that transmits the movement between the swing arms. The third connection point refers to the position where the cylinder force is applied, specifically located at one-third of the length of the end of the second swing arm 7, balancing the driving force and displacement accuracy through optimized leverage ratio.

[0077] Specifically, when the material tension changes, the second guide roller 8 is displaced by traction, causing the second swing arm 7 to rotate around the second rotating shaft 6. The rotation of the second swing arm 7 is transmitted to the first swing arm 4 through the first connecting mechanism 9, forcing the first swing arm 4 to rotate synchronously around the first rotating shaft 3, thereby changing the spatial position of the first guide roller 5. During this process, the first cylinder 10 adjusts its output thrust according to the tension change, acting on the third connection point of the second swing arm 7 to form a dynamic balance adjustment. The rotatable design at both ends of the first connecting mechanism 9 allows for asymmetrical motion trajectories between the swing arms, enabling the double guide rollers to form a parallelogram motion pattern. The layout design of the cylinder thrust acting on the third connection point ensures that the direction of the force forms an optimal angle with the direction of the swing arm movement, improving energy conversion efficiency.

[0078] Compared with existing technologies, traditional single floating rollers adjust tension by changing the position of a single guide roller, while this solution uses the linkage of two guide rollers to form a composite displacement field, thus expanding the tension adjustment range. In existing technologies, cylinders often directly drive the guide rollers, which can easily cause impact loads. This solution applies the cylinder driving force to a specific position of the swing arm, amplifying the force through leverage, thereby increasing the effective output force with the same cylinder specifications. This application, through the linkage of the first swing arm 4 and the second swing arm 7, combined with the precise adjustment of the cylinder drive and connecting mechanism, forms a synchronous double floating roller system. This system effectively absorbs tension fluctuations caused by the non-roundness of the master roll, offering advantages such as improved tension stability and precise linkage adjustment.

[0079] This application further proposes that the first swing arm 4 is in the shape of a long rod.

[0080] Among them, the long rod-shaped structure refers to a rod structure whose length is much greater than its width and thickness. It can be made of steel or aluminum alloy materials and is achieved through a one-piece molding process or a segmented welding process. Its cross-sectional shape can be rectangular, circular, or polygonal. When subjected to material tension, this structure can resist bending deformation through its own rigidity, ensuring the synchronous rotation accuracy between the swing arm and the rotating shaft.

[0081] The parallel selection relationship of "and / or" means that the technical solution allows the use of a single long rod-shaped first swing arm 4, or the simultaneous use of two sets of long rod-shaped swing arms, which can be achieved by adjusting the number of swing arms and their installation positions. This design provides options for the mechanism layout under different working conditions. For example, when space is limited on one side, only a single long rod-shaped swing arm can be used, while two sets of structures can be used to enhance balance when installed symmetrically on both sides.

[0082] Specifically, the longitudinal extension direction of the long rod-shaped swing arm is perpendicular to the axis of the first rotating shaft 3. When the material tension acts on the guide roller, the rigid structure of the long rod-shaped swing arm can evenly transmit the torque to the rotating shaft, avoiding structural deformation caused by local stress concentration. During the rotation of the swing arm around the rotating shaft, its long rod shape can maintain the horizontal movement trajectory of the guide roller, thereby offsetting the tension fluctuations caused by the non-roundness of the master roll.

[0083] Through the above technical solution, compared with the prior art, the swing arm of the traditional floating roller usually adopts an irregular structure, which has limited bending resistance and is prone to guide roller displacement due to local deformation when dealing with materials of different materials or thicknesses. In contrast, the long rod-shaped swing arm significantly improves the structural rigidity by optimizing the geometry, so that the swing arm can maintain a stable posture when subjected to dynamic loads.

[0084] This application further proposes a first connecting mechanism 9 including a screw 91, a first ball joint 92 and a second ball joint 93. The first ball joint 92 is threadedly connected to one end of the screw 91 and hinged to the first swing arm 4 at a first connection point. The second ball joint 93 is threadedly connected to the other end of the screw 91 and hinged to the second swing arm 7 at a second connection point.

[0085] Here, screw 91 refers to a rod-shaped component with external threads, which can be implemented using a thread structure with opposite directions of rotation at both ends. By rotating screw 91, the axial distance between the ball joints at both ends can be changed. A ball joint is a connecting component that includes a ball socket and a ball head, allowing the connection point to deflect at an angle.

[0086] Compared with existing technologies, traditional floating roller mechanisms often use connecting rods of fixed length, which suffers from the problem of non-adjustable length. This solution achieves precise control of the connection length through a threaded adjustment mechanism, allowing for adaptability to tension variations in materials of different specifications and enabling online adjustment of the transmission ratio between the swing arms to meet the needs of different material characteristics.

[0087] This application further proposes that the third ball joint 11 is detachably connected to the piston rod of the first cylinder 10 and hinged to the second swing arm 7 at the third connection point.

[0088] Among them, detachable connection refers to the assembly and separation of the piston rod end and the ball joint by bolts or quick-release pins. Specifically, it can be achieved by using a flange docking and positioning pin structure, which facilitates the independent disassembly and assembly of the cylinder or hinge components during maintenance.

[0089] By adopting the above technical solution, compared with the prior art, the detachable connection design of this application eliminates the need for overall disassembly of the cylinder or articulated component replacement, thereby shortening downtime and reducing maintenance costs.

[0090] This application further proposes that the first rotating shaft 3 is provided with a first anti-rotation feature 12, the first swing arm 4 is provided with a through hole, the first rotating shaft 3 passes through the through hole, and the inner wall of the through hole is provided with a second anti-rotation feature that cooperates with the first anti-rotation feature 12.

[0091] The first anti-rotation feature 12 refers to a non-circular cross-section structure set on the surface of the rotating shaft, which can be implemented by using a plane, a polygonal protrusion or a groove, to limit the relative rotation between the rotating shaft and the swing arm.

[0092] The second anti-rotation feature refers to a corresponding non-circular cross-section structure set on the inner wall of the through hole of the swing arm. Specifically, it can be implemented by using a plane, a polygonal groove, or a protrusion. By matching the shape of the first anti-rotation feature 12, the synchronous rotation of the shaft and the swing arm can be achieved.

[0093] Specifically, when the first rotating shaft 3 rotates, the planar or other non-circular cross-sectional structure on its surface engages with the corresponding structure on the inner wall of the through hole of the swing arm, forcing the swing arm and the rotating shaft to rotate synchronously. The through hole structure allows the rotating shaft and the swing arm to maintain assembly freedom in the axial direction, avoiding stress concentration caused by machining errors or assembly deviations. As a preferred embodiment, the planar feature can be formed by milling or grinding processes. The tight fit between the contact surfaces can uniformly transmit torque while reducing transmission errors caused by gaps.

[0094] Compared with existing technologies, traditional keyway or pin connections require complex mating structures to be machined on the shaft and rocker arm, resulting in accumulated clearance errors and localized stress concentrations. This solution, however, employs a planar mating structure, which is easier to machine and eliminates the need for precise clearance. By distributing the load through a large contact surface, it improves transmission stability. This application effectively solves the transmission failure problem caused by asynchronous rotation between the rocker arm and shaft, avoiding vibration or slippage caused by clearance errors in traditional connection methods. The planar mating structure further enhances the shear resistance of the connection parts and simplifies the disassembly and reassembly process during maintenance.

[0095] This application further proposes that both the first anti-rotation feature 12 and the second anti-rotation feature are planar.

[0096] The first anti-rotation feature 12 refers to a planar structure on the outer surface of the rotating shaft, which can be achieved by machining a single-sided cutting plane in the circumferential direction of the rotating shaft. This plane forms a directional limit with the contact surface between it and the swing arm. The second anti-rotation feature refers to a planar structure on the inner wall of the through hole of the swing arm, which can be achieved by machining a mating surface on the inner wall of the through hole that matches the plane of the rotating shaft. The relative rotational freedom of the rotating shaft and the swing arm is constrained by the contact between the two planes.

[0097] Specifically, the rotating shaft and the swing arm form a surface contact constraint through the cooperation of planar structures. When the rotating shaft is subjected to external torque, the plane of the first anti-rotation feature 12 and the plane of the second anti-rotation feature generate normal contact pressure, and the frictional resistance between the contact surfaces forms an anti-rotation torque. Since the planar contact area is significantly larger than the point-line contact area of ​​traditional keyways or splines, it can provide greater torsional stiffness under the same assembly precision. At the same time, the planar structure can be realized through simple machining, without the need for high-precision fitting tolerances, reducing the machining difficulty.

[0098] This application further proposes that the second rotating shaft 6 and the first support 1 in the double floating roller mechanism are fixedly connected. The second rotating shaft 6 is designed as a tapered structure, and a bearing is set between the second rotating shaft 6 and the second swing arm 7.

[0099] Among them, a tapered shaft refers to a shaft-like part whose outer surface forms a tapered geometric profile. This can be achieved by turning to create the tapered surface. The tapered surface contact improves the coaxiality of the shaft and support through self-centering. A fixed connection refers to a non-movable assembly between the shaft and support, which can be achieved through bolting, welding, or interference fits, preventing displacement of the shaft under dynamic loads. A bearing is a mechanical component consisting of rolling elements and inner and outer rings. It can be implemented using deep groove ball bearings or tapered roller bearings. The rolling element contact converts sliding friction into rolling friction.

[0100] Specifically, the second rotating shaft 6 and the first support 1 are fixedly connected to form a rigid support structure, eliminating the gaps caused by vibration in traditional movable rotating shafts. The conical surface of the tapered rotating shaft and the mating surface of the support create a self-centering effect, automatically correcting the shaft axis position during installation and ensuring the radial positioning accuracy of the rotation trajectory of the second swing arm 7. The bearing is installed between the rotating shaft and the swing arm, dispersing the load during swing arm rotation through rolling contact, reducing the coefficient of friction and suppressing heat accumulation. These three technical features work synergistically to improve the stability of the swing arm rotation process by limiting shaft displacement through rigid support, compensating for assembly errors through the conical surface mating, and optimizing the friction mode through the bearing structure.

[0101] Compared with existing technologies, the second rotating shaft 6 in traditional floating roller mechanisms typically uses a cylindrical shaft with sliding bearings, which suffers from problems such as assembly coaxiality depending on machining accuracy and increased wear due to sliding friction. This solution reduces assembly accuracy requirements by utilizing the self-centering characteristics of a tapered rotating shaft, reduces frictional loss using rolling bearings, and enhances structural rigidity through a fixed connection method, resulting in multi-dimensional stability improvements. This application can effectively suppress radial offset during swing arm rotation, reduce frictional loss at the contact surface between the rotating shaft and the swing arm, improve the stability of the swing arm's motion trajectory, reduce abnormal wear caused by assembly deviations, and extend the service life of the rotating shaft assembly.

[0102] This application further proposes a base 13, including a triangular portion 131 and a base plate portion 132. The base plate portion 132 is connected to one side of the triangular portion 131 and is connected to the crossbeam 2. The end of the first cylinder 10 away from the piston is rotatably connected to one corner of the triangular portion 131 via a pivot.

[0103] The triangular section 131 refers to a geometric support frame formed by three sides, which can be made by welding steel plates or casting aluminum alloy. The closed structure formed by its three sides can form a stable mechanical support system. The base plate section 132 refers to a flat plate structure that extends perpendicularly to the sides of the triangular section 131. It can be connected to the crossbeam 2 by bolt fixing, and is used to evenly transfer the force borne by the base 13 to the crossbeam 2. The rotatable connection of the rotating shaft refers to the use of a hinged pivot structure, which can be achieved by the cooperation of a pin and a bearing, so that the cylinder maintains rotational freedom during the swinging process.

[0104] Specifically, the three sides of the triangular portion 131 form a rigid frame, and its vertex is connected to the tail of the cylinder via a rotating shaft, forming a stable three-point support structure. When the cylinder applies thrust, the force is transmitted to the three sides of the triangular portion 131 through the rotating shaft, causing the stress to be evenly distributed along the sides. The rigid connection between the base plate 132 and the crossbeam 2 forms a two-way load-bearing platform, and the load of the crossbeam 2 is distributed to each side of the triangular portion 131 through the base plate 132. The rotatable connection between the cylinder and the vertex of the triangular portion 131 allows the cylinder to freely adjust its angle during extension and retraction, while the triangular frame absorbs the vibration energy generated by the cylinder's operation, preventing stress concentration at a single connection point.

[0105] Compared to existing technologies, the cylinders in traditional floating roller mechanisms are typically directly fixed to the flat base 13 or bracket, resulting in ineffective dispersion of vibration energy, and requiring the entire base 13 to be disassembled for installation position adjustments. This solution utilizes a combined structure of the triangular section 131 and the base plate section 132, leveraging the multi-directional force characteristics at the apex of the triangle to convert the cylinder thrust into tensile or compressive loads on the three sides, avoiding localized stress concentrations caused by traditional direct-connection structures. Furthermore, the rotating shaft connection allows for fine-tuning of the cylinder angle without disassembly, simplifying maintenance.

[0106] Through the above technical solutions, this application has improved the stability of the cylinder mounting base, and the shaft connection design makes cylinder angle adjustment more convenient, reducing downtime for maintenance.

[0107] This application further proposes a dual floating roller mechanism, including a second support, a third rotating shaft 14, a third swing arm 15, a fourth rotating shaft 16, a fourth swing arm 17, a second connecting mechanism 18, and a second cylinder 19.

[0108] The two ends of the crossbeam 2 are respectively connected to the first support 1 and the second support; the third rotating shaft 14 is rotatably mounted on the second support; the third swing arm 15 is connected to the third rotating shaft 14 and is configured to rotate synchronously with the third rotating shaft 14; the other end of the first guide roller 5 is rotatably connected to one end of the third swing arm 15; the fourth rotating shaft 16 is mounted on the second support and is spaced apart from both the third rotating shaft 14 and the crossbeam 2; one end of the fourth swing arm 17 is connected to the fourth rotating shaft 16 and is configured to rotate around the fourth rotating shaft 16 or rotate synchronously with the fourth rotating shaft 16; the second guide roller 8... The other end is rotatably connected to the other end of the fourth swing arm 17; one end of the second connecting mechanism 18 is rotatably connected to the other end of the third swing arm 15 at the fourth connecting point, and the other end of the second connecting mechanism 18 is rotatably connected to the fourth swing arm 17 at the fifth connecting point; the third rotating shaft 14 is located between the fourth connecting point and the first guide roller 5, and the fifth connecting point is located between the fourth rotating shaft 16 and the second guide roller 8; the second cylinder 19 is mounted on the crossbeam 2, and the piston rod of the second cylinder 19 is connected to the fourth swing arm 17 at the sixth connecting point, which is located between the fifth connecting point and the second guide roller 8.

[0109] The second support refers to the support structure located on the other side of the crossbeam 2. It can be fixed to the crossbeam 2 by welding or bolting to construct a symmetrical support system, preventing bending deformation of the crossbeam 2 caused by unilateral stress. The third rotating shaft 14 refers to the rotating shaft passing through the second support. The fourth rotating shaft 16 refers to a rotating shaft spaced apart from the third rotating shaft 14. Specifically, it can be a tapered shaft with rolling bearings, allowing the fourth swing arm 17 to rotate around the shaft or rotate synchronously, forming the floating adjustment fulcrum of the second guide roller 8. The second connecting mechanism 18 refers to the connecting rod assembly connecting the third swing arm 15 and the fourth swing arm 17. The sixth connection point refers to the connection position between the piston rod of the second cylinder 19 and the fourth swing arm 17.

[0110] Specifically, the second support and the first support 1 are symmetrically arranged at both ends of the crossbeam 2, forming a double-support frame, which can balance the lateral load distribution when processing wide-width materials. The synchronous rotation design of the third swing arm 15 and the third rotating shaft 14 ensures that the swing trajectories of the two ends of the first guide roller 5 are strictly symmetrical, preventing the guide roller from tilting and causing tension imbalance at the material edge. The rotational cooperation of the fourth rotating shaft 16 and the fourth swing arm 17 makes the second guide roller 8 form a floating adjustment point on the other side of the material, which, together with the first guide roller 5, constitutes a double floating roller layout, synchronously absorbing tension fluctuations in both the upper and lower directions. The second connecting mechanism 18 can maintain the parallelism of the guide rollers. The second cylinder 19 and the first cylinder 10 symmetrically drive the fourth swing arm 17 and the second swing arm 7, and the tension on both sides can be controlled separately by independent air pressure adjustment.

[0111] Compared to existing technologies, current floating roller mechanisms typically employ a single-sided support structure. When handling wide materials, the deflection of the crossbeam 2 can cause the guide roller axis to shift, leading to uneven tension on both sides of the material. This solution, through a double-sided support and symmetrical swing arm design, ensures consistent support stiffness at both ends of the guide roller, eliminating tension fluctuations caused by unilateral deformation. Compared to the traditional single-cylinder driven single-swing arm structure, this solution's dual-cylinder drive allows for independent adjustment of the swing arm angles on both sides. For example, when handling material edge thickness differences, asymmetric tension compensation can be achieved by adjusting the pressure of the two cylinders, improving material adaptability.

[0112] Through the above technical solution, this application can eliminate the problem of uneven tension distribution caused by insufficient rigidity of one side support when processing wide materials, ensuring that the guide rollers maintain parallel movement in the material width direction. By using a combination of double-sided swing arms and independent cylinder drive, it can adapt to the adjustment needs of different material widths and thicknesses, reducing material edge wrinkles or tensile deformation. The symmetrical support structure reduces the risk of bending deformation of the crossbeam 2, extends the service life of the equipment, and simplifies the calibration operation of the guide roller parallelism during maintenance.

[0113] This application further proposes a technical solution including a PLC and a controller, wherein the PLC and controller automatically calculate the required air pressure based on the set unwinding tension value and output it to the cylinder through an electro-pneumatic converter.

[0114] Here, PLC refers to a programmable logic controller, which can be implemented using an industrial-grade controller with analog input / output modules. It is used to receive tension sensor signals and execute control algorithms. The electro-pneumatic converter is a device that converts electrical signals into pneumatic signals. It can be implemented using a proportional valve or a current-to-pressure converter, used to accurately convert control signals into the required pneumatic pressure.

[0115] Specifically, the PLC and controller automatically calculate the required air pressure based on the unwinding tension value set on the screen and output it to the cylinder via an electro-pneumatic converter. When the unwinding tension deviates from the set value, the balance between the tension and the cylinder thrust is broken, causing the floating roller to shift. The potentiometer connected to it transmits the position deviation to the controller, which, after PD adjustment, outputs a speed correction command to change the speed of the unwinding motor, causing the floating roller to return to the set position and achieve a new balance. Because the adjustment process is very rapid, the tension error caused by the change in wrap angle can be ignored within a small swing angle range, thus the unwinding tension can fully meet the process requirements.

[0116] Compared to existing technologies, traditional floating roller mechanisms rely on manual experience to adjust cylinder pressure, failing to respond to tension changes in real time. This solution, however, achieves dynamic matching of pressure parameters through an electrical linkage control system. In existing technologies, the pressure regulation accuracy of pneumatic systems is limited by mechanical structural errors, while this solution improves control accuracy through the linear signal conversion characteristics of the electro-pneumatic converter. Existing manual adjustment methods require machine shutdown, while this solution can automatically optimize parameters during equipment operation.

[0117] Through the above technical solution, this application achieves real-time closed-loop control of the floating roller tension, effectively suppressing tension fluctuations caused by the non-roundness of the master roll. When processing materials with large differences in elastic modulus, the system can automatically match the optimal air pressure parameters to eliminate material tensile deformation. During continuous production, the system can autonomously compensate for air pressure attenuation caused by mechanical wear, maintaining tension control stability. For materials with varying thickness, the control algorithm can quickly adjust the cylinder output pressure to avoid defects such as film breakage or wrinkles.

Claims

1. A double floating roller mechanism, characterized in that, include: First support; The crossbeam is installed on the first support; The first rotating shaft is rotatably mounted on the first support; A first swing arm is connected to the first rotating shaft, and the first swing arm is configured to rotate synchronously with the first rotating shaft; The first guide roller is rotatably connected at one end to one end of the first swing arm; The second rotating shaft is installed on the first support and is spaced apart from both the first rotating shaft and the crossbeam. The second swing arm has one end connected to the second rotating shaft, and the second swing arm is configured to rotate around the second rotating shaft or rotate synchronously with the second rotating shaft; The second guide roller is rotatably connected at one end to the other end of the second swing arm; The first connecting mechanism has one end rotatably connected to the other end of the first swing arm at a first connecting point, and the other end of the first connecting mechanism is rotatably connected to the second swing arm at a second connecting point. The first rotating shaft is located between the first connecting point and the first guide roller, and the second connecting point is located between the second rotating shaft and the second guide roller. A first cylinder is mounted on the crossbeam, and the piston rod of the first cylinder is connected to the second swing arm at a third connection point, which is located between the second connection point and the second guide roller.

2. The dual floating roller mechanism as described in claim 1, characterized in that, The first swing arm is in the shape of a long rod; and / or, the first swing arm is in the shape of a long rod.

3. The dual floating roller mechanism as described in claim 1, characterized in that, The first connecting mechanism includes: Screw; The first ball joint is threaded to one end of the screw and hinged to the first swing arm at the first connection point; The second ball joint is threaded to the other end of the screw and hinged to the second swing arm at the second connection point.

4. The dual floating roller mechanism as described in claim 3, characterized in that, Also includes: The third ball joint is detachably connected to the piston rod of the first cylinder and hinged to the second rocker arm at the third connection point.

5. The dual floating roller mechanism as described in claim 1, characterized in that, The first rotating shaft is provided with a first anti-rotation feature; The first swing arm has a through hole, the first rotating shaft passes through the through hole, and the inner wall of the through hole is provided with a second anti-rotation feature that cooperates with the first anti-rotation feature.

6. The dual floating roller mechanism as described in claim 5, characterized in that, Both the first anti-rotation feature and the second anti-rotation feature are planar.

7. The dual floating roller mechanism as described in claim 1, characterized in that, The second rotating shaft is fixedly connected to the first support. The second rotating shaft is a tapered rotating shaft, and a bearing is sandwiched between the second rotating shaft and the second swing arm.

8. The dual floating roller mechanism as described in claim 1, characterized in that, Also includes: The base includes a triangular portion and a base plate portion. The base plate portion is connected to one side of the triangular portion and to the crossbeam. The end of the first cylinder opposite to the piston is rotatably connected to one corner of the triangular portion via a pivot.

9. The dual floating roller mechanism as described in claim 1, characterized in that, Also includes: The second support is provided, and the two ends of the crossbeam are respectively connected to the first support and the second support; The third shaft is rotatably mounted on the second support; A third swing arm is connected to the third rotating shaft, and the third swing arm is configured to rotate synchronously with the third rotating shaft; the other end of the first guide roller is rotatably connected to one end of the third swing arm; The fourth rotating shaft is installed on the second support and is spaced apart from both the third rotating shaft and the crossbeam; The fourth swing arm has one end connected to the fourth rotating shaft, and the fourth swing arm is configured to rotate about the fourth rotating shaft or rotate synchronously with the fourth rotating shaft; the other end of the second guide roller is rotatably connected to the other end of the fourth swing arm. The second connecting mechanism has one end rotatably connected to the other end of the third swing arm at a fourth connecting point, and the other end of the second connecting mechanism is rotatably connected to the fourth swing arm at a fifth connecting point. The third rotating shaft is located between the fourth connecting point and the first guide roller, and the fifth connecting point is located between the fourth rotating shaft and the second guide roller. The second cylinder is installed on the crossbeam, and the piston rod of the second cylinder is connected to the fourth swing arm at the sixth connection point, which is located between the fifth connection point and the second guide roller.

10. The dual floating roller mechanism as described in claim 1, characterized in that, It also includes a PLC and a controller. The PLC and controller automatically calculate the required air pressure based on the set unwinding tension value and output it to the cylinder through an electro-pneumatic converter.

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