Metal wire paying-off torsion releasing mechanism

Abstract

The invention discloses a metal wire paying-off torsion releasing mechanism which is suitable for machining of precise metal wires such as insulin pump wires. The device comprises a storage device, a tensioning device, a guiding device and a torsion releasing device. The core of the torsion releasing device is as follows: a first part is provided with spaced grooves and convex blocks, a second part is correspondingly provided with accommodating grooves and concave blocks, and the first part and the second part are staggered and meshed to form an S-shaped channel for a metal wire to pass through; the pneumatic adjusting assembly drives the two parts to move relatively, and the channel gap is adjusted and controlled. The tensioning device stabilizes tension, the guiding device accurately guides the metal wire, and the position adjusting device can adjust the space posture in multiple directions. The mechanism realizes controllable torsion release through the S-shaped channel and pneumatic adjustment, solves the problems of poor controllability, incomplete release and low efficiency in the prior art, has the advantages of high processing efficiency, thorough release, high automation degree and high adaptability, and ensures the precision of precision machining.

Description

Technical Field

[0001] This invention relates to the field of metal wire processing equipment technology, specifically to a metal wire feeding torque release mechanism, which is particularly suitable for processing precision metal wires such as insulin pump leads. Background Technology

[0002] In the field of metal wire processing, especially in the production of precision metal wires such as insulin pump leads, the metal wire is prone to instability in shape due to the accumulation of its own torque during unwinding and subsequent processing, affecting product accuracy and quality. Torque release is the core link to ensure the accuracy of metal wire processing. Its implementation requires a combination of mechanical structure design and force control strategies to eliminate the compound torque generated inside the metal wire due to winding, stretching and other processes.

[0003] Currently, most metal wire torque release mechanisms on the market employ two methods: annealing and mechanical vibration. Annealing eliminates internal stress in the metal wire through high temperatures, but it suffers from poor controllability and long processing times, making it unsuitable for high-efficiency production. Mechanical vibration, on the other hand, loosens the internal structure of the metal wire through high-frequency vibration, but its unidirectional and uneven vibration intensity leads to incomplete torque release, easily causing deviations in subsequent processing. Furthermore, for precision metal wires with helical structures, these methods struggle to cover the complex torque distribution along the axial, radial, and helical tangential directions, easily resulting in residual hidden torque.

[0004] Chinese Patent Publication No. CN222182397U discloses a stress relief device for aluminum alloy stranded wire. It uses a worm gear to drive a worm wheel and a rotating sleeve to rotate, and pressure rollers arranged alternately on both sides of the rotating sleeve to compress the aluminum alloy stranded wire to release stress. The degree of compression can be adjusted by a screw to accommodate stranded wires of different diameters. This solution improves upon the limitations of single-direction processing through rotational compression, but it still has significant shortcomings for precision metal wires such as insulin pump leads: First, the rotational compression of the pressure rollers is relatively strong, easily causing deformation of small-diameter precision metal wires; second, the compression direction is still mainly circumferential around the stranded wire, making it difficult to accurately match the complex helical torque distribution of precision metal wires and completely eliminate latent torque; third, the manual adjustment of the screw lacks controllability and cannot meet the torque release accuracy requirements of precision machining.

[0005] With the surge in demand for insulin pumps, the required production capacity and precision of the accompanying lead wires have increased significantly. Existing technologies and the aforementioned comparative solutions can no longer meet the demands for high efficiency, controllability, and thorough torque release in actual production. Therefore, developing a mechanism capable of precise torque control, rapid release, and adaptability to precision machining has become a crucial and urgent issue to be addressed. Summary of the Invention

[0006] To address the problems of poor controllability, long processing time, and incomplete release of metal wire torque in existing technologies, this invention provides a metal wire unloading torque release mechanism to achieve controllable release of metal wire torque, shorten processing time, improve release completeness, and simultaneously meet the capacity and precision requirements of precision machining.

[0007] To achieve the above objectives, the present invention adopts the following technical solution: A wire feeding torque release mechanism, characterized in that it includes a storage device 1, a tensioning device 2, a guiding device 3, and a torque release device 4; wherein, the torque release device 4 includes: The first part 41 is provided with grooves 411 and protrusions 412 at intervals along the extension direction of the metal wire, the grooves being used to support the metal wire; The second part 42 is provided with a receiving groove 421 corresponding to the groove 411 and a concave block 422 corresponding to the protrusion 412; the first part 41 and the second part 42 are interlocked and meshed with each other, and the groove 411 and the receiving groove 421, the protrusion 412 and the concave block 422 cooperate to form an S-shaped channel 40 for the metal wire to pass through. The pneumatic adjustment assembly 43 is connected to the first part 41 or the second part 42 and is used to drive the first part 41 and the second part 42 to move closer or further apart, thereby adjusting the gap of the S-shaped channel 40.

[0008] Preferably, the groove 411 is a V-shaped groove with rounded surfaces on both sides.

[0009] Preferably, the pneumatic adjustment assembly 43 is provided with a guide rail 431 at its bottom, and a first sliding member 45 and a second sliding member 46 driven by the pneumatic adjustment assembly 43 are provided on the guide rail 431; the first sliding member 45 is connected to a first connecting block 47, the second sliding member 46 is connected to a second connecting block 48, and the first connecting block 47 and the second connecting block 48 are respectively connected to a first part 41 and a second part 42; the pneumatic adjustment assembly 43 drives the first sliding member (45) and the second sliding member (46) to move along the guide rail (431), thereby causing the first part (41) and the second part (42) to move relative to each other.

[0010] Preferably, the first connecting block 47 and the second connecting block 48 are both L-shaped metal components. Their horizontal fitting part a is connected to the top surface of the corresponding part, and their vertical fitting part b is connected to a plurality of positioning holes c arranged along the length direction on the outer side of the corresponding part through fasteners, so as to realize the adjustable assembly of the two parts in the direction of the guide rail.

[0011] Preferably, a first drive assembly 11 for rotating the storage device 1 is connected to one side of the storage device 1.

[0012] Preferably, the tensioning device 2 is located above the storage device 1 and includes a control box 21, a fixed guide wheel 22, an intermediate guide wheel group 23, and a swing rod type guide wheel 24. The fixed guide wheel 22, the intermediate guide wheel group 23, and the swing rod type guide wheel 24 are installed sequentially from bottom to top in the vertical direction on one side wall of the control box 21 facing the storage device 1. The control box 21 is provided with a second drive assembly 211, which is connected to the swing rod type guide wheel 24 for driving the swing rod type guide wheel 24 to swing around its hinge point.

[0013] Preferably, the intermediate guide wheel group 23 includes at least three guide wheels 231, each guide wheel 231 being mounted on the side wall of the control box 21 via an elastic element. A tension sensor is mounted on the guide wheel located in the middle of the intermediate guide wheel group 23, and the tension sensor is used to detect the real-time tension of the metal wire.

[0014] Preferably, the guiding device 3 and the tensioning device 2 are located in the same vertical plane, and include a first guide wheel 31, a second guide wheel 32, a gap unit 33, a first limiting unit 34 and a second limiting unit 35; The first guide wheel 31 is used to receive the metal wire output from the swing-arm type guide wheel 24 of the tensioning device 2 and change its transmission direction. The second guide wheel 32 is used to receive the metal wire output from the first guide wheel 31 and output the metal wire to the gap unit 33. The gap unit 33 is composed of two limiting bodies 331 that are perpendicular to the transmission direction of the metal wire and are arranged opposite to each other, forming a first gap 3a extending along the transmission direction of the metal wire between them. The first limiting unit 34 includes four cylindrical limiting posts 341, which are arranged in two sets of spatially orthogonal distribution: one set is arranged along the Y-axis direction, and the center lines of the two limiting posts 341 have a preset angle and are not coplanar, forming a second through-slit 3b with a gradient width feature; the other set is arranged along the Z-axis direction, and the center lines of the two limiting posts 341 have a preset angle and are not coplanar, forming a third through-slit 3c with a gradient width feature; the second limiting unit 35 includes an L-shaped spatial constraint body 351, whose L-shaped bending portion 351a is inclined inward.

[0015] Preferably, it further includes a position adjustment device 5, which includes a first mounting plate 51, a second mounting plate 52, and a third mounting plate 53; the first mounting plate 51 is provided with at least two first guide rails 511 along the X-axis, which are slidably connected to the third movable seat 512 and the fourth movable seat 513 respectively, and both are connected to the bottom of the second mounting plate 52, driving the second mounting plate 52 to move along the X-axis; the second mounting plate 52 is provided with at least two second guide rails 521 along the Y-axis, which are slidably connected to the fifth movable seat 522 and the sixth movable seat 523 respectively, and both are connected to the bottom of the third mounting plate 53, driving the third mounting plate 53 to move along the Y-axis; the third mounting plate 53 supports the storage device 1, the tensioning device 2, the guiding device 3, and the torque release device 4 above it.

[0016] Preferably, the third mounting plate 53 is connected to a third drive assembly 54 for driving its movement along the Y-axis in the negative direction near the Y-axis, and a handle 55 is provided on the side near the positive direction of the X-axis, which is consistent with its own length direction.

[0017] Compared with the prior art, the beneficial effects of the present invention are: 1. Controllable torque release: The torque release device drives the first and second parts to move relative to each other through pneumatic components, thereby achieving precise adjustment of the gap between the S-shaped channels and effectively controlling the degree of torque release, solving the problem of poor controllability in existing technologies.

[0018] 2. High processing efficiency: The metal wire can be passively vibrated to release torque as it passes through the channel, eliminating the need for long-term annealing or vibration treatment, which greatly improves processing efficiency and meets the demand for high production capacity.

[0019] 3. Thorough torque release: The S-shaped channel design and the staggered meshing structure of the symmetrical toothed pressure blocks can exert a uniform and sufficient force on the metal wire, ensuring thorough torque release and improving product quality.

[0020] 4. High degree of automation: The various devices work together to realize the automated processing of metal wire from storage, tensioning, guiding to torque release, thereby improving processing accuracy and stability.

[0021] 5. High adaptability: The position adjustment device can adjust the spatial posture of the metal wire in multiple directions to ensure coaxial alignment with subsequent devices, and is suitable for metal wire products of different specifications and processing requirements. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the overall structure of this case; Figure 2 This is a schematic diagram of the explosion of the torque release device in this case; Figure 3 This is a schematic diagram of the S-shaped channel in this case; Figure 4This is a structural schematic diagram of the torque release device in this case; Figure 5 This is a structural schematic diagram of the material storage device and tensioning device in this case; Figure 6 This is a structural schematic diagram of the guiding device in this case; Figure 7 This is a partial structural schematic diagram of the guiding device in this case; Figure 8 This is a schematic diagram of the position adjustment device in this case; Detailed Implementation

[0023] The technical solutions of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. The components of this application described and shown in the accompanying drawings can generally be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of this application provided in the accompanying drawings is not intended to limit the scope of the claimed application, but merely represents selected embodiments of this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application without inventive effort are within the scope of protection of this application. It should be noted that similar reference numerals and letters in the following drawings indicate similar items; therefore, once an item is defined in one drawing, it does not need to be further defined and explained in subsequent drawings. Furthermore, in the description of this application, the terms "first," "second," etc., are used only to distinguish descriptions and should not be construed as indicating or implying relative importance.

[0024] In existing technologies, during the precision metal wire processing, the accumulated torque during wire laying and subsequent processing leads to unstable shape, affecting product accuracy. Current technologies use annealing or mechanical vibration to release torque; however, the former has drawbacks such as long processing time and poor controllability, while the latter suffers from incomplete torque release, leading to processing deviations. For example, in the production of insulin pump leads, the metal wire requires multiple processing steps, and existing technologies struggle to meet the demands of high-efficiency production.

[0025] To address the aforementioned issues, a mechanism capable of dynamically adjusting the metal wire transmission path is needed to eliminate torque accumulation through multi-stage coordinated control. Based on the analysis of the relationship between tension fluctuations, path deviation, and contact friction during metal wire transmission, it was found that torque can be effectively released by changing the length of the metal wire bending path and the contact pressure. Therefore, an adjustable S-shaped channel is proposed in the transmission path, combined with tension control and spatial attitude adjustment, forming a systematic solution.

[0026] Therefore, this application proposes a wire unloading torque release mechanism, such as... Figures 1-8As shown, it includes a storage device 1, a tensioning device 2, a guiding device 3, and a torque release device 4. These devices are arranged sequentially along the direction of metal wire transmission. The storage device 1 stores and outputs the metal wire to the tensioning device 2. The tensioning device 2 adjusts the tension of the metal wire and buffers tension fluctuations. The guiding device 3 guides the metal wire into the torque release device 4, which enables the controlled release of the metal wire's torque. The torque release device 4 includes a first part 41, a second part 42, and a pneumatic adjustment assembly 43. The first part 41 is provided with grooves 411 and protrusions 412 at intervals along the extension direction of the metal wire. The grooves 411 are used to carry the metal wire. The second part 42 is provided with a receiving groove 421 corresponding to the groove 411 and a concave block 422 corresponding to the protrusion 412. The first part 41 and the second part 42 are interlocked and meshed with each other. The grooves 411 and the receiving grooves 421, and the protrusions 412 and the concave blocks 422 cooperate to form an S-shaped channel 40 for the metal wire to pass through. The pneumatic adjustment assembly 43 is connected to the first part 41 or the second part 42 and is used to drive the two to move closer or further apart to adjust the gap of the S-shaped channel 40.

[0027] The storage device 1 is used to store metal wire coils and achieve continuous output. Specifically, it can be implemented using a rotating tray with a drive motor, controlling the rotation speed to ensure continuous feeding. The tensioning device 2 is used to maintain stable tension during metal wire transmission. Specifically, it can be implemented using a multi-guide wheel assembly with a swing-arm guide wheel, dynamically adjusting the guide wheel position to absorb tension fluctuations. The guiding device 3 is used to precisely guide the direction of metal wire transmission. Specifically, it can be implemented using a combination of limiting posts to form a gradually widening channel, correcting metal wire misalignment through spatial constraints. In the torque release device 4, the groove 411 of the first part 41 is precision ground, and its curvature is customized according to the diameter of the metal wire to ensure that the metal wire is stably engaged and does not fall off; the accommodating groove 421 of the second part 42 is deeper than the groove 411, providing sufficient matching space for the groove; the protrusion 412 and the concave block 422 are clearance fit to ensure that a tight upper and lower wrapping constraint is formed when embedded; the pneumatic adjustment component 43 can be implemented by using a precision cylinder in conjunction with a displacement sensor, which drives the part to move through air pressure adjustment and precisely controls the channel gap.

[0028] Specifically, after the metal wire is output from the storage device 1, it enters the tensioning device 2. The swing of the rocker arm guide wheel compensates for tension fluctuations, ensuring that the metal wire enters the guide device 3 with stable tension. The guide device 3 precisely guides the metal wire into the S-shaped channel 40 of the torque release device 4. At this time, the metal wire is engaged in the groove 411 of the first part 41. The curvature of the groove 411 prevents the metal wire from slipping out. At the same time, the groove 411 is embedded in the receiving groove 421 of the second part 42. The space reserved in the receiving groove 421 avoids direct rigid collision between the two. The protrusion 412 of the first part 41 is correspondingly embedded in the concave block 422 of the second part 42, forming a wrapping constraint in the vertical direction, so that the metal wire will not deviate laterally when it is forcibly bent and transmitted along the S-shaped path. According to the specifications of the metal wire and torque requirements, the pneumatic adjustment component 43 drives the first part 41 and the second part 42 to move closer or further apart: when it is necessary to enhance the torque release effect, the channel gap is reduced, increasing the contact area between the metal wire and the groove 411. Combined with the squeezing effect generated by the upper and lower wrapping constraints, the internal torque is released through multi-segment bending and friction effects; when it is necessary to reduce the intensity of action, the channel gap is increased, reducing contact friction and squeezing force. In this structure, the locking effect of the groove, the reserved space of the receiving groove, and the wrapping constraints of the protrusions and concave blocks work together to ensure that the force on each segment of the metal wire is balanced and the transmission is stable.

[0029] Compared to existing technologies, current annealing processes cannot adjust the processing intensity in real time, mechanical vibration can only eliminate local torque, and traditional extrusion structures mostly involve single-plane contact, which can easily lead to metal wire slippage or uneven stress. This solution, through the engaging positioning of the groove 411, the adaptation space reserved in the receiving groove 421, and the upper and lower wrapping constraints of the protrusions 412 and concave blocks 422, combined with the dynamic gap control of the pneumatic adjustment components, can achieve stable load-bearing and precise torque release for metal wires of different diameters. The multi-segment bending of the S-shaped channel, combined with uniform constraint, can more thoroughly eliminate the combined torque in the axial, radial, and helical tangential directions compared to single-direction processing, avoiding the residual hidden torque.

[0030] Through the above technical solution, this application achieves precise, controllable, efficient, and thorough torque release of the metal wire. The cooperative structure of grooves and receiving slots, and protrusions and concave blocks ensures uniform force on the metal wire. The geometric design of the S-shaped channel extends the torque release path, and the pneumatic adjustment component enables dynamic control of the gap. The synergistic effect of these three elements effectively solves the problem of morphological instability caused by torque accumulation in precision metal wire processing, ensuring that the product's dimensional accuracy meets the requirements of precision processing scenarios such as insulin pump leads.

[0031] like Figure 2 and Figure 3 As shown, this application further proposes that the groove 411 of the first part 41 is a V-shaped groove with arc surfaces on both sides; the bottom surface of the concave block 422 has arc surfaces on both sides.

[0032] The rounded surfaces on both sides of the V-groove refer to the rounded transition design of the V-shaped inclined sidewalls of groove 411. This can be achieved through precision grinding, with the radius of the rounded surface preferably being 0.3-1mm (adapted to the diameter of the metal wire; for example, a 0.2mm diameter metal wire corresponds to a radius of 0.1-0.3mm), ensuring surface contact rather than line contact with the metal wire surface. The rounded surfaces on both sides of the bottom surface of the concave block 422 are adapted to the curvature of the rounded surface of groove 411, and their machining accuracy is controlled within ±0.01mm. The material is a high-hardness alloy that has been heat-treated to enhance wear resistance and prevent deformation from long-term contact. The included angle of the V-groove is designed to be 60°-120° according to the diameter of the metal wire, forming a "sharp outside, round inside" composite structure with the rounded surfaces on both sides. This ensures stable engagement of the metal wire and disperses contact stress through the rounded surfaces.

[0033] Specifically, when the metal wire engages with the V-groove 411 of the first part 41, the two arc surfaces form a uniform surface contact area with the metal wire surface. Compared to traditional right-angled or sharp-edged V-grooves, the arc surfaces can distribute the radial constraint force on the metal wire to a larger contact area, avoiding plastic deformation or surface scratches caused by local stress concentration. At the same time, when the arc surfaces on both sides of the bottom surface of the concave block 422 contact the side of the protrusion 412 of the first part 41, a smooth sliding fit is formed, reducing mechanical wear when the parts are interlocked, and ensuring that the S-shaped channel 40 maintains stable constraint accuracy during gap adjustment. When the pneumatic adjustment component 43 drives the parts to move relative to each other, the arc surfaces of the V-groove adaptively adjust the contact pressure with the metal wire according to the channel gap change, forming a continuous "constraint-release" cycle with the arc surfaces of the concave block, so that the metal wire releases torque evenly during bending transmission.

[0034] Through the above technical solution, this application effectively solves the problem of metal wire damage caused by the sharp edges of traditional V-grooves. The arc surfaces on both sides of the V-groove and the arc surface of the bottom of the concave block form a cooperative constraint structure. This structure not only ensures that the metal wire does not slip through the guiding property of the V-groove, but also reduces stress concentration through the surface contact characteristics of the arc surfaces, protecting the surface integrity of the precision metal wire. At the same time, the appropriate arc curvature makes the frictional resistance during the meshing of parts more uniform, avoiding torque release fluctuations caused by local jamming. This further improves the adaptability of the mechanism to high-precision metal wires such as insulin pump leads, ensuring the stability and thoroughness of the torque release process.

[0035] like Figure 4As shown, this application further proposes that the bottom of the pneumatic component 43 is provided with a guide rail 431, and the guide rail 43 is provided with a first sliding member 45 and a second sliding member 46 driven by the pneumatic component 43; the first sliding member 45 is connected to a first connecting block 47, and the second sliding member 46 is connected to a second connecting block 48, and the first connecting block 47 and the second connecting block 48 are respectively connected to the first part 41 and the second part 42. The pneumatic component 43 drives the first sliding member 45 and the second sliding member 46 to move along the guide rail 431, thereby causing the first part 41 and the second part 42 to move relative to each other.

[0036] Among them, guide rail 431 refers to a linear guide structure, which can be implemented using a linear slide rail or a dovetail groove structure. Its function is to provide a directional movement trajectory for the sliding component and prevent movement deviation. First sliding component 45 and second sliding component 46 are moving parts that cooperate with the guide rail, which can be implemented using a slider or slide block structure. Their function is to convert the driving force of the pneumatic component into linear motion. First connecting block 47 and second connecting block 48 are transmission connecting components, which can be implemented using metal castings or machined parts. Their function is to transmit the linear displacement of the sliding component to the corresponding part, forming synchronous reverse motion.

[0037] Specifically, when the pneumatic component 43 is activated, it generates driving force, pushing the first sliding member 45 and the second sliding member 46 to move linearly in opposite directions along the guide rail. The first connecting block 47 and the second connecting block 48 are rigidly connected to the two sliding members respectively, converting the linear displacement of the sliding members into the relative displacement of the first part 41 and the second part 42. Because the guide rail constrains the movement trajectory of the sliding members, the two sliding members always maintain a parallel movement state during the movement, avoiding misalignment of parts due to deviation of the movement trajectory. The first part 41 and the second part 42 form a split driving structure through the connecting blocks, achieving synchronous reverse movement under the action of the pneumatic component 43, thereby precisely controlling the gap change of the S-shaped channel.

[0038] Compared to existing technologies, traditional torque release mechanisms often use a single drive source to directly push symmetrical parts, which can easily lead to asynchronous movement on both sides due to transmission chain errors. This solution uses a separate sliding component and connecting block structure to decompose the transmission path of the driving force into two independent and symmetrical transmission branches. By utilizing the guiding characteristics of the guide rail, motion deviation is eliminated, ensuring that the two parts maintain a symmetrical relationship during movement.

[0039] Through the above technical solution, this application achieves synchronous reverse movement of symmetrical parts during gap adjustment, solving the problem of uneven channel gap caused by asynchronous movement and improving the accuracy of releasing the torque of the metal wire. The cooperative structure of the guide rail and the sliding component effectively suppresses the deviation of the part's movement trajectory, ensuring the stability of the gap adjustment process. The split connecting block design ensures a balanced force distribution on the two parts, avoiding deformation or wear of the parts caused by excessive force on one side.

[0040] like Figure 4 As shown, this application further proposes that the first connecting block 47 and the second connecting block 48 have the same structure and are both L-shaped metal components, respectively connecting the first part 41 and the second part 42. The L-shaped connecting block includes a horizontal fitting part a and a vertical fitting part b. The horizontal fitting part a fits against the top surface of the corresponding part, and the vertical fitting part b fits against the outer surface of the corresponding part. The outer surfaces of the first part 41 and the second part 42 are provided with threaded holes evenly distributed along their own length direction; the vertical fitting part b of the first connecting block 47 is connected to the threaded hole on the outer surface of the first part 41 by bolts; the vertical fitting part b of the second connecting block 48 is connected to the threaded hole on the outer surface of the second part 42 by bolts.

[0041] Among them, the L-shaped metal component refers to a connecting part with a vertical bending structure made of metal material, which can be specifically manufactured by aluminum alloy casting. Its horizontal and vertical fitting parts form a right-angle support structure. The equally spaced threaded holes refer to an array of threaded holes arranged at fixed intervals on the outer surface, which can be specifically manufactured by CNC machine tool drilling. The hole spacing can be set to, for example, 10mm to 30mm. Fastener fixing refers to the rigid connection achieved by the cooperation of bolts and nuts, which can be specifically achieved by a combination of stainless steel hexagonal socket head cap screws and anti-loosening washers.

[0042] Specifically, the horizontal contact portion forms a planar support by contacting the top surface of the part, while the vertical contact portion forms a vertical constraint by contacting the outer surface of the part. This dual contact surface effectively disperses the shear force generated during pneumatic component operation. The threaded holes are evenly spaced along the length of the part, allowing for multi-position adjustment of the connecting block's installation position along the part's axial direction. For example, when it's necessary to increase the S-shaped channel clearance, the connecting block can be moved two hole positions towards the end of the part. Fasteners apply pre-tightening force after penetrating the vertical contact portion and the threaded holes, ensuring a gapless fit between the connecting block and the part, preventing loosening due to high-frequency vibration. During adjustment, the symmetrical L-shaped structure ensures that the two parts always move parallel, preventing channel misalignment caused by asymmetrical forces.

[0043] Compared with existing technologies, traditional connection structures mostly use single-point welding or integral casting, which cannot achieve flexible adjustment of the part position and are prone to deformation after repeated stress. In contrast, this solution uses a modular L-shaped connecting block with an adjustable threaded hole to achieve linear adjustment of the part position while ensuring connection rigidity, thus solving the problems of low adjustment accuracy and difficult maintenance of traditional structures.

[0044] Through the above technical solution, this application achieves stable load-bearing of the connection structure under dynamic working conditions, ensuring the synchronous movement accuracy of the two parts during the pneumatic component drive process. The adjustable installation method of the connecting block can adapt to the processing requirements of metal wires with different diameters. The initial gap of the S-shaped channel can be quickly changed by adjusting the position of the threaded hole, avoiding the cumbersome operation of disassembling and replacing parts. The rigid connection of the double contact surface effectively suppresses the displacement deviation caused by vibration, ensuring the uniformity of force on the metal wire during torque release.

[0045] like Figure 5 As shown, this application further proposes that a first drive assembly 11 for rotating the storage device is connected to one side of the storage device 1.

[0046] The connection on one side of the storage device 1 refers to the asymmetrical layout of the drive assembly and the rotation axis of the storage device. Specifically, a flange or coupling can be used to achieve a mechanical connection with the side wall of the storage device, thereby optimizing the torque transmission path within a limited space. The first drive assembly 11 is a power source independent of the storage device 1. Specifically, a servo motor and reducer can be used to adjust the rotation speed of the storage device in real time through a closed-loop control algorithm, thereby directly intervening in the dynamic characteristics of the metal wire output process.

[0047] Specifically, during the release of the metal wire, the rotation of the storage device 1 is actively controlled by the first drive component 11. When the metal wire output rate needs adjustment, the output shaft of the first drive component 11 drives the storage device to rotate around its axis, changing the linear speed at which the wire reel releases the metal wire. For example, when a subsequent process requires a reduction in the metal wire supply, the first drive component 11 can reduce the rotational speed of the storage device, so that the metal wire forms a pre-tension when it leaves the storage device, avoiding slack caused by free release. This active control method ensures that the metal wire has a basic tension before entering the tensioning device 2, thereby reducing the compensation range of the subsequent tension adjustment mechanism and suppressing the influence of inertial fluctuations caused by the passive rotation of the storage device 1 on the torque of the metal wire.

[0048] Compared to existing technologies, traditional material storage devices rely on the passive rotation of the metal wire traction force, and their rotation speed cannot be matched with the requirements of subsequent processes in real time, resulting in periodic fluctuations in the output tension of the metal wire. This solution applies active rotation control to the material storage device through a drive component, enabling the metal wire release rate to be dynamically adjusted according to processing needs. For example, the rotation speed can be increased in advance to reserve wire during the acceleration phase, and a constant speed output can be maintained during the precision processing phase, thereby eliminating the cause of tension fluctuations at the source.

[0049] Through the above technical solution, this application achieves active adjustment of the metal wire output. By precisely controlling the rotation speed of the storage device through the drive component, a stable initial tension is formed in the metal wire during the release phase. This control method effectively reduces the adjustment load of the subsequent tensioning device and avoids the accumulation of metal wire torque caused by the passive rotation of the storage device, thus providing stable wire supply conditions for precision machining.

[0050] like Figure 5 As shown, this application further proposes a tensioning device 2 located above the storage device 1, including a control box 21, a fixed guide wheel 22, an intermediate guide wheel group 23, and a swing rod type guide wheel 24. The fixed guide wheel 22, the intermediate guide wheel group 23, and the swing rod type guide wheel 24 are installed sequentially from bottom to top in the vertical direction on one side wall of the control box 21 facing the storage device 1. The control box 21 is provided with a second drive assembly 211, which is connected to the swing rod type guide wheel 24 for driving the swing rod type guide wheel 24 to swing around its hinge point.

[0051] The control box 21 refers to the housing structure that carries the guide wheel assembly and drive mechanism. It can be implemented using a welded metal housing, with guide wheel mounting positions on its side walls and a drive component mounting cavity inside to isolate external environmental interference. The intermediate guide wheel group 23 refers to a vertically stacked structure composed of multiple guide wheels. Specifically, it can consist of three guide wheels mounted via elastic elements, such as springs or rubber buffers, to absorb sudden tension changes during metal wire transmission. The swing-arm guide wheel 24 refers to a guide wheel structure that swings around a hinge point. It can be implemented by hinged guide wheels with bearings to a swing arm, with the end of the swing arm connected to the second drive component. The swing angle range is controlled by the stroke of the drive component. The second drive component 211 refers to the actuator that drives the swing-arm guide wheel. It can be implemented using a servo motor and a reducer. The reducer output shaft is connected to the swing arm of the swing-arm guide wheel via a linkage mechanism to achieve precise angle control.

[0052] Specifically, after the metal wire is output from the storage device 1, it first passes through the fixed guide wheel 22 to form an initial tension reference. The intermediate guide wheel group 23 extends the contact path of the metal wire by vertically stacking them. The elastically installed guide wheels can shift with the tension changes, buffering tension fluctuations. The swing-arm type guide wheel 24 swings around the hinge point under the drive of the second drive component 211, changing the wrapping angle of the metal wire, thereby dynamically adjusting the path length and tension. The control box integrates the drive component and the guide wheel system in a closed space to avoid external vibration interference. When the tension sensor detects an abnormal tension, the second drive component adjusts the angle of the swing-arm type guide wheel in real time, forming a closed-loop control mechanism.

[0053] Compared to existing technologies, traditional tensioning devices often employ a single guide wheel or a simple pulley system, failing to achieve dynamic adjustment and fluctuation absorption. This solution constructs a multi-stage tension adjustment mechanism through a vertically layered guide wheel layout combined with an elastic buffer structure. The linkage design between the pendulum-type guide wheel and the drive assembly transforms tension adjustment from a passive response to active control, solving the problem of lag in traditional devices.

[0054] Through the above technical solutions, this application achieves real-time dynamic adjustment and fluctuation buffering of metal wire tension, effectively eliminating the impact of sudden tension changes on precision machining. The elastic mounting structure of the intermediate guide wheel assembly 23 can absorb high-frequency micro-fluctuations, and the active angle adjustment of the swing-arm guide wheel 24 can cope with low-frequency, large-range tension changes. The enclosed design of the control box 21 ensures the stability of the drive mechanism's operation and avoids external interference causing tension control deviations, thereby meeting the high-precision metal wire machining requirements of insulin pump leads and other similar products.

[0055] like Figure 5 As shown, this application further proposes that the intermediate guide wheel group 23 includes at least three guide wheels 231, each guide wheel 231 being mounted on the side wall of the control box 21 by an elastic element, wherein a tension sensor is mounted on the guide wheel located in the middle of the intermediate guide wheel group 23, and the tension sensor is used to detect the real-time tension of the metal wire.

[0056] The elastic element refers to a mechanical component with elastic deformation capability, specifically a spring or elastic rubber pad. Its function is to allow the guide wheel to displace when the tension of the metal wire changes, thereby buffering the impact of sudden tension changes on the system. The tension sensor is a detection device that converts mechanical tension into an electrical signal, specifically a strain gauge or piezoelectric sensor. Its function is to capture the change in tension on the guide wheel in real time, providing data feedback for tension adjustment. The guide wheel in the middle of the intermediate guide wheel group refers to the guide wheel located in the middle position of the three guide wheels. This can be achieved through a symmetrical arrangement of the guide wheel group. Its function is to utilize the characteristic that the guide wheel in the middle position is affected by the tension on both sides, so that the guide wheel bears the greatest range of tension changes, thereby improving the sensor's detection sensitivity.

[0057] Specifically, the metal wire sequentially winds around three guide rollers in a serpentine path. When tension fluctuations occur during wire transmission, the elastic element allows the guide rollers to displace along the tension direction, absorbing the energy from sudden tension changes. Due to the interaction of the tension on both sides of the metal wire, the displacement amplitude of the middle guide roller is positively correlated with the tension fluctuation. At this point, a tension sensor mounted on this guide roller converts the displacement into an electrical signal output. By monitoring the tension data of the middle guide roller in real time, it is possible to accurately determine whether the current tension exceeds a set threshold, thereby triggering the adjustment action of the tensioning device. The synergistic effect of the elastic element and the sensor forms a dual control mechanism of passive buffering and active detection, ensuring that tension fluctuations are quickly suppressed.

[0058] Compared to existing technologies, traditional solutions often use fixed guide wheels with a single sensor for tension detection, which cannot effectively distinguish between normal tension fluctuations and abnormal abrupt changes, and the lack of a buffer structure makes the sensor prone to overload damage. This solution, through the flexible installation of guide wheels and the arrangement of multi-stage guide wheels, not only achieves graded dissipation of tension energy, but also utilizes the mechanical properties of the intermediate guide wheels to amplify the tension change signal, thereby improving the sensor's detection accuracy by at least one order of magnitude.

[0059] Through the above technical solution, this application can identify tension anomalies caused by equipment vibration, sudden speed changes, or external interference during metal wire transmission in real time, and activate a compensation mechanism before the tension exceeds the safety threshold. In the production of insulin pump leads, this technology can control tension fluctuations within ±0.5N, avoiding deviations in the metal wire twisting angle caused by unstable tension, and ensuring that the processing accuracy of subsequent torque release processes meets medical-grade product standards.

[0060] like Figure 6 and Figure 7 As shown, this application further proposes that the guiding device 3 and the tensioning device 2 are located in the same vertical plane, including a first guide wheel 31, a second guide wheel 32, a gap unit 33, a first limiting unit 34, and a second limiting unit 35; the first guide wheel 31 is used to receive the metal wire output from the swing-arm type guide wheel of the tensioning device and change its transmission direction, and the second guide wheel 32 is used to receive the metal wire output from the first guide wheel and output the metal wire to the gap unit 33; the gap unit 33 is composed of two limiting bodies 331 that are perpendicular to the transmission direction of the metal wire and are arranged opposite each other, forming a gap between them. The first gap 3a extends along the direction of metal wire transmission; the first limiting unit 34 includes four cylindrical limiting posts 341, which are arranged in two sets of spatially orthogonal distribution: one set is arranged along the Y-axis direction, and the center lines of the two limiting posts have a preset angle and are not coplanar, forming a second through gap 3b with a gradient width feature; the other set is arranged along the Z-axis direction, and the center lines of the two limiting posts 341 have a preset angle and are not coplanar, forming a third through gap 3c with a gradient width feature; the second limiting unit 35 includes an L-shaped spatial constraint body 351, whose L-shaped bend 351a is inclined inward.

[0061] The first gap 3a refers to a lateral constraint channel formed by two parallel limiting bodies 331, which can be implemented using adjustable-spacing hard alloy plates to limit the horizontal deviation of the metal wire. The second and third through gaps refer to a gradually decreasing constraint channel formed by two sets of orthogonally distributed limiting posts, which can be implemented by installing cylinders at an axial angle of 5°-15°. The structure, with the channel width gradually decreasing along the transmission direction, corrects the three-dimensional attitude of the metal wire. The L-shaped spatial constraint body 351 refers to the end constraint structure, which can be implemented using a stainless steel bent part. The inward tilt of the bent part at 15°-30° creates an asymmetric constraint, suppressing the spatial sway of the metal wire end.

[0062] Specifically, after the metal wire completes its vertical plane turning via the first guide wheel 31, it enters the second guide wheel 32, where the dual guide wheel structure achieves planar positioning of the transmission path. The metal wire then passes through the first slot 3a of the slot unit 33, eliminating lateral offset. Upon entering the first limiting unit 34, the second through slot 3b in the Y-axis direction progressively adjusts the vertical plane attitude of the metal wire through a gradually changing width, while the third through slot 3c in the Z-axis direction performs three-dimensional spatial correction. Finally, the asymmetric channel formed by the inclined L-shaped constraint bending section of the second limiting unit further suppresses end-effector sway. The synergistic effect of the multi-level constraint structure ensures that the metal wire remains within controlled physical boundaries, avoiding torque accumulation caused by path deviation.

[0063] Compared with existing technologies, traditional guiding devices only use single-level limiting structures or planar constraints, which cannot achieve precise control of three-dimensional spatial attitude. This solution constructs a three-dimensional multi-level constraint system by combining planar guide wheels, lateral limiting gaps, orthogonal gradient limiting posts, and end asymmetric constraint bodies, thus solving the problem of incomplete torque release caused by spatial displacement of metal wires in traditional technologies.

[0064] Through the above technical solution, this application achieves precise three-dimensional spatial constraint of the metal wire transmission path, eliminates horizontal offset and vertical plane attitude deviation, corrects the three-dimensional spatial distortion of the metal wire, and suppresses the swaying phenomenon at the transmission end, thereby effectively reducing the torque accumulation caused by path offset and improving the subsequent processing accuracy.

[0065] like Figure 8As shown, this application further proposes a position adjustment device 5 including a first mounting plate 51, a second mounting plate 52, and a third mounting plate 53; the first mounting plate 51 is provided with at least two first guide rails 511 along the X-axis, which are respectively slidably connected to a third movable seat 512 and a fourth movable seat 513, and both are connected to the bottom of the second mounting plate 52, driving the second mounting plate 52 to move along the X-axis; the second mounting plate 52 is provided with at least two second guide rails 521 along the Y-axis, which are respectively slidably connected to a fifth movable seat 522 and a sixth movable seat 523, and both are connected to the bottom of the third mounting plate 53, driving the third mounting plate 53 to move along the Y-axis; the third mounting plate 53 carries a material storage device 1, a tensioning device 2, a guiding device 3, and a torque release device 4 above it.

[0066] The first mounting plate refers to the base structure that supports the X-axis moving component. Specifically, it can be implemented using an aluminum alloy plate with T-slots, with two first guide rails parallel to each other on both sides of the plate to form symmetrical support. The third and fourth movable seats refer to the moving parts that cooperate with the guide rails, such as a slider structure with ball bearings. The connection between the two sets of movable seats and the second mounting plate forms a dual-point drive, avoiding offset caused by single-point force.

[0067] The second mounting plate is a transition structure that supports the Y-axis moving component. It can be implemented using a steel plate with reinforcing ribs, and its two second guide rails are arranged perpendicular to the first guide rail. The fifth and sixth movable seats adopt the same slider structure as the third and fourth movable seats. The connection between the two sets of movable seats and the third mounting plate forms a planar sliding pair, ensuring the stability of longitudinal adjustment.

[0068] The third mounting plate forms an integrated adjustment unit by supporting core components such as a material storage device and a tensioning device.

[0069] Specifically, when it is necessary to adjust the alignment of the metal wire transmission axis with the subsequent processing device, the operator can push the second mounting plate along the X-axis. At this time, the third and fourth movable seats slide synchronously on the first guide rail, causing the second mounting plate to move laterally as a whole. Subsequently, the third mounting plate is pushed along the Y-axis, and the fifth and sixth movable seats slide synchronously on the second guide rail, achieving longitudinal position adjustment. Through independent control of the X and Y axes, the components such as the storage device and tensioning device carried on the third mounting plate can move freely in the plane, ensuring that the spatial orientation of the metal wire transmission path precisely coincides with the axis of the subsequent device.

[0070] Compared with existing technologies, traditional position adjustment mechanisms mostly adopt single-axis movement or asymmetrical support structures, which suffer from low adjustment accuracy and poor movement stability. This solution constructs a precise adjustment system with two degrees of freedom in a plane by combining dual-axis independent guide rails and symmetrically arranged movable seats, thus solving the offset error problem caused by single-point drive. For example, the single-guide rail adjustment devices commonly found in existing technologies are prone to lateral sway during movement, while the symmetrical distribution of the two sets of movable seats in this solution can counteract the lateral torque, keeping the movement trajectory linear.

[0071] Through the above technical solution, this application achieves precise in-plane positioning of the metal wire transmission path, eliminating lateral and longitudinal positional deviations through independent adjustment along the X and Y axes. When the third mounting plate moves, the metal wire guide assembly it carries remains coaxially aligned with the subsequent processing device, avoiding residual torque due to spatial orientation deviations. This adjustment process eliminates the need for repeated trial and error; operators can quickly complete alignment through visual observation or auxiliary positioning devices, effectively improving the thoroughness of torque release and processing efficiency.

[0072] like Figure 8 As shown, this application further proposes that a third drive assembly 54 for driving the third mounting plate 53 to move along the Y-axis is connected in the negative direction near the Y-axis, and a handle 55 is provided on the side near the positive direction of the X-axis, which is consistent with its own length direction.

[0073] The third mounting plate is an integrated support platform that supports all functional modules. It can be made of aluminum alloy and features a rectangular flat plate structure. Its bottom is slidably connected to the second mounting plate via guide rails, enabling composite displacement adjustment in the XY plane. The third drive assembly is a power device that applies driving force along the Y-axis. It can be implemented using a servo motor and ball screw transmission mechanism. The displacement of the third mounting plate in the Y-axis direction is precisely adjusted by controlling the rotation angle of the motor. The handle is a manually operated component located on the edge of the mounting plate. It can be made of a metal rod with anti-slip texture, its axis parallel to the X-axis guide rail. Manual pushing or pulling allows the third mounting plate to slide along the X-axis.

[0074] Specifically, the parallel layout of the handle and the X-axis guide rail allows the operator to simultaneously drive the entire integrated unit to slide along the guide rail with a single push-pull motion when making lateral position adjustments. The electric drive in the Y-axis direction and the manual adjustment in the X-axis direction form a complementary control mode. The encoder built into the Y-axis drive component can achieve position feedback at the ±0.1 mm level, while the precision ball-slider structure of the X-axis guide rail ensures displacement stability during manual adjustment. The combined effect of the two allows the spatial posture adjustment of the metal wire transmission path to have both automated precision and manual fine-tuning flexibility.

[0075] Compared with existing technologies, traditional position adjustment devices mostly adopt single-axis electric adjustment or fully manual operation modes, which have the problems of limited adjustment dimensions and slow operation response. This solution, through the spatial separation layout of a dual-axis independent drive system, achieves programmed precise positioning in the Y-axis direction while retaining the ability for real-time manual intervention in the X-axis direction. This overcomes the drawback of traditional equipment that requires repeated switching of control modes when adjusting in multiple dimensions, and improves the efficiency of composite adjustment of the spatial posture of the metal wire by about 40%.

[0076] Through the above technical solution, this application effectively solves the contradiction between the ease of operation and the adjustment accuracy of the position adjustment device. The electric longitudinal adjustment provided by the third drive component ensures the repeatability of positioning accuracy for large stroke displacement, while the manual lateral fine adjustment function in the X-axis direction allows the operator to quickly correct the offset of the metal wire transmission path according to the on-site working conditions. The combination of the two reduces the coaxial alignment operation time between the metal wire and the subsequent processing device to 1 / 3 of the traditional method, while controlling the spatial posture adjustment error within ±0.05 mm.

[0077] The above description is merely an embodiment of this application and is not intended to limit the scope of protection of this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of protection of this application.

Claims

1. A wire pay-off torque release mechanism, characterized by, The device comprises a storage device (1), a tensioning device (2), a guiding device (3) and a torsion releasing device (4), wherein the torsion releasing device (4) comprises: A first part (41) is provided with a groove (411) and a protrusion (412) at intervals along the extension direction of the metal wire, and the groove is used for bearing the metal wire; A second part (42) is provided with a receiving groove (421) corresponding to the groove (411) and a recess (422) corresponding to the protrusion (412); the first part (41) and the second part (42) are interlocked, and the groove (411) and the receiving groove (421) and the protrusion (412) and the recess (422) cooperatively form an S-shaped channel (40) for the metal wire to pass through; An air-operated adjusting assembly (43) is connected to the first part (41) or the second part (42) and is used for driving the first part (41) and the second part (42) to relatively approach or move away from each other to regulate the gap of the S-shaped channel (40).

2. A wire line payout torsion release mechanism according to claim 1 wherein, The groove (411) is a V-shaped groove, and the two sides thereof are circular arc surfaces.

3. A wire line payout torsion release mechanism according to claim 1 wherein, The air-operated adjusting assembly (43) is provided with a guide rail (431) at the bottom, the guide rail (431) is provided with a first sliding member (45) and a second sliding member (46) driven by the air-operated adjusting assembly (43); the first sliding member (45) is connected with a first connecting block (47), the second sliding member (46) is connected with a second connecting block (48), and the first connecting block (47) and the second connecting block (48) are connected with the first part (41) and the second part (42) respectively; the air-operated adjusting assembly (43) drives the first sliding member (45) and the second sliding member (46) to move along the guide rail (431), and then drives the first part (41) and the second part (42) to relatively move.

4. A wire line payout torsion release mechanism according to claim 3 wherein, The first connecting block (47) and the second connecting block (48) are both L-shaped metal members, the horizontal adhering part (a) thereof is connected with the top surface of the corresponding part, and the vertical adhering part (b) is connected to the plurality of positioning holes (c) provided along the length direction on the outer side surface of the corresponding part by fasteners, so as to realize the position-adjustable assembly of the two parts in the guide rail direction.

5. A wire line payout torsion release mechanism according to claim 1 wherein, One side of the storage device (1) is connected with a first driving assembly (11) used for rotating the storage device (1).

6. A wire line payout torsion release mechanism according to claim 1 wherein, The tensioning device (2) is arranged above the storage device (1) and comprises a control box (21), a fixed guide wheel (22), an intermediate guide wheel set (23) and a swing lever type guide wheel (24); the fixed guide wheel (22), the intermediate guide wheel set (23) and the swing lever type guide wheel (24) are sequentially installed on the side wall of the control box (21) in the vertical direction from bottom to top; the control box (21) is provided with a second driving assembly (211) therein, the second driving assembly (211) is in transmission connection with the swing lever type guide wheel (24) and is used for driving the swing lever type guide wheel (24) to swing around the hinge point thereof.

7. A wire line payout torsion release mechanism according to claim 6 wherein, The intermediate guide wheel set (23) comprises at least three guide wheels (231), each of which is mounted to the side wall of the control box (21) by an elastic member, and a tension sensor is mounted on the guide wheel located in the middle of the intermediate guide wheel set (23) to detect the real-time tension of the metal wire.

8. A wire line payout torsion release mechanism according to claim 1 wherein, The guiding device (3) and the tensioning device (2) are located in the same vertical plane and comprise a first guide wheel (31), a second guide wheel (32), a gap unit (33), a first limiting unit (34), and a second limiting unit (35). The first guide wheel (31) is used to receive the metal wire output by the swing lever type guide wheel (24) of the tensioning device (2) and change the transmission direction of the metal wire, and the second guide wheel (32) is used to receive the metal wire output by the first guide wheel (31) and output the metal wire to the gap unit (33). The gap unit (33) is composed of two limiting bodies (331) arranged opposite to each other and perpendicular to the transmission direction of the metal wire, and a first gap (3a) extending along the transmission direction of the metal wire is formed between the two limiting bodies (331). The first limiting unit (34) comprises four cylindrical limiting columns (341) arranged in two groups of space orthogonal distribution: one group is arranged along the Y-axis direction, the axis lines of the two limiting columns (341) have a preset included angle and are not coplanar, forming a second through gap (3b) with a gradually changing width characteristic; the other group is arranged along the Z-axis direction, the axis lines of the two limiting columns (341) have a preset included angle and are not coplanar, forming a third through gap (3c) with a gradually changing width characteristic; the second limiting unit (35) comprises an L-shaped space constraint body (351), and the L-shaped bending part (351a) is inclined inward.

9. The wire line payout torsion release mechanism of claim 1, wherein, The position adjusting device (5) comprises a first mounting plate (51), a second mounting plate (52), and a third mounting plate (53); the first mounting plate (51) is provided with at least two first guide rails (511) along the X-axis, respectively connected with a third movable seat (512) and a fourth movable seat (513) in sliding connection, and the two are connected with the bottom of the second mounting plate (52) to drive the second mounting plate (52) to move along the X-axis; the second mounting plate (52) is provided with at least two second guide rails (521) along the Y-axis, respectively connected with a fifth movable seat (522) and a sixth movable seat (523) in sliding connection, and the two are connected with the bottom of the third mounting plate (53) to drive the third mounting plate (53) to move along the Y-axis; the third mounting plate (53) bears the storage device (1), the tensioning device (2), the guiding device (3), and the torsion releasing device (4) above.

10. The wire line payout torsion release mechanism of claim 9, wherein, The third mounting plate (53) is connected with a third driving assembly (54) near the negative direction of the Y-axis for driving the third mounting plate (53) to move along the Y-axis, and a handle (55) consistent with the length direction of the third mounting plate (53) is arranged on one side of the third mounting plate (53) near the positive direction of the X-axis.

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