Pneumatic jacking structure of pay-off rack

Abstract

The invention provides a pneumatic jacking structure of a pay-off rack. The pneumatic jacking structure comprises a shaft body, a movable sleeve, an air cylinder, a push rod, a tension spring, a tensioning head, a tensioning block, a movable head and a connecting rod mechanism. Therefore, through the superposition design of the deformation quantity of the tension spring and the moving distance of the limiting end face, the moving distance d of the piston rod of the air cylinder is equal to d1 + d2. Compared with the stroke requirement of a traditional small-stroke air cylinder, the effective stroke of the air cylinder in the structure is prolonged to the sum of d1 and d2, the stroke length is completely matched with an air cylinder of a conventional specification in the market, a small high-precision air cylinder does not need to be customized, the manufacturing cost and the purchasing cost of equipment are remarkably reduced, and large-scale application and popularization are facilitated.

Description

Technical Field

[0001] This invention relates to the field of air shaft technology, and more specifically to a pneumatic clamping structure for a wire feeding frame. Background Technology

[0002] As a B65H type structure for handling filamentous materials, the air shaft can be used in the wire feeding frame for wire feeding and take-up operations. The air shaft of this B65H type structure achieves stable positioning of the wire feeding frame through a tensioning structure, and then rotates to achieve wire feeding and take-up. During this process, the tensioning design of the B65H type structure ensures the stability of the wire feeding and take-up process, thereby ensuring the stable handling of filamentous materials in the wire feeding frame.

[0003] In existing technology, a typical air shaft structure usually includes a shaft body, with several circumferentially rotatably connected to the ends of the shaft body. An axially movable push rod is installed inside the shaft body, and the push rod is connected to each of the rotatable components via a linkage assembly. During operation, by driving the push rod to move axially along the shaft body, the linkage assembly drives the rotatable components to rotate around their rotational connection points, causing the end of the rotatable component away from the shaft body to expand outwards, thereby achieving tensioning and positioning of the wire feeder sleeved on the outer circumference of the air shaft.

[0004] In the aforementioned push rod drive structure of the air shaft, cylinder drive is widely used due to its fast response speed and simple structure. However, in the scenario of small wire racks, due to the smaller size of the wire rack, the corresponding air shaft specifications are reduced, and the required axial movement stroke of the push rod is smaller. If the standard cylinder drive method is still used in this case, the following technical defects will exist: Firstly, the air pressure transmission efficiency is low, resulting in insufficient and unstable clamping force output. Small-stroke cylinders typically have a small cylinder diameter, leading to limited air pressure chamber volume and making them prone to pressure loss and fluctuations during transmission. When there are slight fluctuations in the air source pressure, the output force of the small-stroke cylinder will change significantly, failing to generate a stable clamping force and thus affecting the wire feeding accuracy.

[0005] Secondly, the equipment has poor adaptability to low-pressure conditions, limiting its applicability. In some remote production scenarios or under conditions of unstable air pressure supply, the air source pressure may be lower than the rated value. Due to its low efficiency in acting on air pressure, the short-stroke cylinder is extremely sensitive to changes in air pressure. When the air pressure is below the critical value, its output force will drop sharply, making it unable to complete the clamping action. On the other hand, if the air source pressure is forcibly increased to improve adaptability to low-pressure conditions, it will cause the cylinder seals to bear excessive pressure, accelerating wear and causing air leakage failures, further reducing the reliability and service life of the equipment.

[0006] Third, customization costs are high. If a customized small and high-precision cylinder is used to adapt to the short stroke requirements of a small wire feeding frame, the manufacturing cost of the equipment will be greatly increased, which is not conducive to large-scale application.

[0007] Therefore, there is an urgent need for a low-cost pneumatic tensioning structure that is compatible with small wire feeding frames to solve the problem of unstable tensioning driven by small-stroke cylinders. Summary of the Invention

[0008] The purpose of this invention is to provide a pneumatic clamping structure for a wire feeding frame that does not have at least one of the disadvantages mentioned above.

[0009] To achieve the above objectives, the present invention provides the following technical solution: a pneumatic clamping structure for a wire feeding frame, comprising a first clamping unit, the first clamping unit comprising a shaft, a movable sleeve slidably connected to the shaft, a push rod slidably connected inside the shaft and driven by a cylinder, a tension head fixed to the end of the movable sleeve, a tension spring having its two ends fixedly connected to the end face of the shaft and the inner end face of the tension head respectively, a tension block rotatably connected to the tension head, and a linkage mechanism disposed at the end of the push rod and used to connect the movable head and the tension block; the linkage mechanism converts the linear movement of the movable head into the rotational movement of the tension block; When the limiting end face of the moving head separates from the end face of the tensioning head, the tension spring is stretched by force, and the tensioning block rotates to achieve relaxation. When the limiting end face of the moving head abuts against the end face of the tensioning head, the limiting end face restricts the rotation of the tensioning block to achieve tensioning. During this process, the tension spring retracts, and the piston rod in the cylinder moves a distance d = d1 + d2; where d1 is the deformation of the tension spring and d2 is the distance the limiting end face moves.

[0010] Furthermore, the shaft is connected to a rotating sleeve via a first bearing; a rotating disk driven by a rotating mechanism is fixedly connected to one end of the rotating sleeve away from the tensioning head, and the rotating disk rotates synchronously with the wire feeding frame; the movable sleeve is slidably connected to the rotating sleeve; a synchronous rotation assembly is provided between the movable sleeve and the rotating sleeve, and the synchronous rotation assembly is used to restrict the movement of the movable sleeve within a preset length range; the movable head is rotatably connected to the end of the push rod via a second bearing.

[0011] Furthermore, the end of the rotating sleeve is threadedly connected to a bottom cover, one end of the bottom cover presses against the outer ring of the first bearing, and a limiting post is provided at the end of the bottom cover away from the first bearing. The tension spring is sleeved outside the limiting post and one end of the tension spring is fixed to the bottom cover.

[0012] Furthermore, a plurality of adjusting plates are provided between the bottom cover and the tension spring. The bottom cover is provided with threaded holes, and the adjusting plates are provided with through holes aligned with the threaded holes. After the stud of the clamping bolt is fitted with the pressure plate, it passes through the through hole and is threadedly connected to the threaded hole. The pressure plate is inserted between the two elastic rings of the tension spring. When the clamping bolt is tightened, the pressure plate presses the bottom elastic ring of the tension spring onto the adjusting plate.

[0013] Furthermore, it also includes a fixing frame, on which a fixing plate is provided, and the cylinder is fixedly connected to the fixing plate, and the shaft is fixedly connected to the fixing plate.

[0014] Furthermore, it also includes a second clamping unit with the same structure as the first clamping unit. The first clamping unit and the second clamping unit are symmetrically distributed about the fixed plate. The fixed plate is cross-shaped, and a cylinder is fixedly connected to each of the four ends of the fixed plate. The piston rods of the two symmetrically distributed cylinders face the same direction. Each shaft has two notches at one end near the fixed plate. A connecting rod is fixedly connected to each piston rod, and the connecting rod passes through the notch and is fixedly connected to the push rod. The width of the notch is h > 1.5d.

[0015] Furthermore, the wire feeding frame is provided with a positioning hole, and a rotating rod matching the positioning hole is fixedly connected to the side of the rotating disk near the tensioning head.

[0016] Furthermore, the linkage mechanism includes a connecting rod with one end rotatably connected to the moving head and the other end rotatably connected to the tensioning block; the moving head drives the tensioning block to rotate through the connecting rod.

[0017] Furthermore, the tensioning head is provided with a plurality of slots, the tensioning block is located inside the slots, and the width of the end face of the tensioning block near the moving head is greater than the width of the slot along the axis direction, and the tensioning block is provided with a pressing surface. When the tension spring is stretched to a preset threshold length, the pressing surface presses against the slot.

[0018] Furthermore, the moving head is provided with several positioning rods inside, and the push rod is provided with an annular groove. Several balls are embedded on the side wall of the positioning rod located inside the annular groove, and the spherical surface of the balls abuts against the inner wall of the annular groove.

[0019] Compared with the prior art, the beneficial effects of this invention are as follows: This invention, through the superposition design of the spring deformation and the moving distance of the limiting end face, makes the moving distance of the cylinder piston rod d = d1 + d2. Compared with the stroke requirements of traditional small-stroke cylinders, the effective stroke of the cylinder in this structure is extended to the sum of d1 and d2. This stroke length is fully compatible with conventional cylinders on the market, eliminating the need for customized small high-precision cylinders, significantly reducing the manufacturing and procurement costs of the equipment, and facilitating large-scale promotion and application. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram of the structure of the wire feeding frame after it is hidden in this invention; Figure 3 This is a schematic diagram of the structure after the tensioning head and the moving head exploded; Figure 4 This is a partial cross-sectional view of the present invention; Figure 5 for Figure 4 A magnified view of a portion of the image.

[0022] The components are: 1. Pay-off frame; 2. Tensioning block; 3. Push rod; 4. Shaft; 5. Fixing plate; 6. Notch; 7. Cylinder; 8. Connecting rod; 9. Rotating disc; 10. Moving head; 11. Moving sleeve; 12. Through groove; 13. Rotating sleeve; 14. Rotating rod; 15. First bearing; 16. Second bearing; 17. Tension spring; 18. Connecting rod; 19. Tensioning head; 20. Adjusting plate; 21. Bottom cover. Detailed Implementation

[0023] To further illustrate the technical means and effects of the present invention in achieving its intended purpose, the following detailed description of the specific implementation methods, structures, features and effects of the present invention, in conjunction with the accompanying drawings and preferred embodiments, is provided below. Example

[0024] In existing technology, a typical air shaft structure usually includes a shaft body, with several circumferentially rotatably connected to the ends of the shaft body. An axially movable push rod is installed inside the shaft body, and the push rod is connected to each of the rotatable components via a linkage assembly. During operation, by driving the push rod to move axially along the shaft body, the linkage assembly drives the rotatable components to rotate around their rotational connection points, causing the end of the rotatable component away from the shaft body to expand outwards, thereby achieving tensioning and positioning of the wire feeder sleeved on the outer circumference of the air shaft.

[0025] In the aforementioned push rod drive structure of the air shaft, cylinder actuation is widely used due to its fast response speed and simple structure. However, in the scenario of small wire feeding frame, due to the small size of the wire frame, the corresponding air shaft specifications are reduced, and the required axial movement stroke of the push rod is small. At this time, the cylinder actuation method has significant technical defects: Firstly, the air pressure transmission efficiency is low, resulting in insufficient and unstable clamping force output. Small-stroke cylinders typically have a small cylinder diameter, leading to limited air pressure chamber volume and making them prone to pressure loss and fluctuations during transmission. When there are slight fluctuations in the air source pressure, the output force of the small-stroke cylinder will change significantly, failing to generate a stable clamping force and thus affecting the wire feeding accuracy.

[0026] Secondly, the equipment has poor adaptability to low-pressure conditions, limiting its applicability. In some remote production scenarios or under conditions of unstable air pressure supply, the air source pressure may be lower than the rated value. Due to its low efficiency in acting on air pressure, the short-stroke cylinder is extremely sensitive to changes in air pressure. When the air pressure is below the critical value, its output force will drop sharply, making it unable to complete the clamping action. On the other hand, if the air source pressure is forcibly increased to improve adaptability to low-pressure conditions, it will cause the cylinder seals to bear excessive pressure, accelerating wear and causing air leakage failures, further reducing the reliability and service life of the equipment.

[0027] Third, customization costs are high. If a customized small and high-precision cylinder is used to adapt to the short stroke requirements of a small wire feeding frame, the manufacturing cost of the equipment will be greatly increased, which is not conducive to large-scale application.

[0028] Therefore, based on the above issues, please refer to... Figures 1-5This invention discloses a pneumatic clamping structure for a wire feeder, comprising a first clamping unit. The first clamping unit includes a shaft 4, a movable sleeve 11 slidably connected to the shaft 4, a push rod 3 slidably connected inside the shaft 4 and driven by a cylinder 7, a tension head 19 fixed to the end of the movable sleeve 11, a tension spring 17 with its two ends fixed to the end face of the shaft 4 and the inner end face of the tension head 19 respectively, a tension block 2 rotatably connected to the tension head 19, and a moving head 10 located at the end of the push rod 3 and a linkage mechanism for connecting the moving head 10 and the tension block 2. The linkage mechanism includes a connecting rod 18 with one end rotatably connected to the moving head 10 and the other end rotatably connected to the tension block 2. The moving head 10 drives the tension block 2 to rotate through the connecting rod 18, thereby converting the linear movement of the moving head 10 into the rotational movement of the tension block 2. Therefore, when the wire feeder 1 needs to be inserted into the shaft 4, the cylinder 7 is activated, and the push rod... 3 will push the moving head 10 to the right, thereby separating the limiting end face of the moving head 10 from the end face of the tensioning head 19. At this time, the tension spring 17 is stretched, and the tensioning block 2 rotates to relax, so that the wire feeder 1 can be inserted into the shaft 4 or pulled out of the shaft 4. When it is necessary to tighten the wire feeder 1, the cylinder 7 is vented in the reverse direction, and the push rod 3 will push the moving head 10 to the left. The limiting end face of the moving head 10 will abut against the end face of the tensioning head 19. At this time, the end face of the tensioning block 2 will also abut against the limiting end face of the moving head 10, thereby limiting the rotation of the tensioning block 2 to achieve tension. In the above process, due to the retraction and stretching of the tension spring 17, the moving distance d of the piston rod in the cylinder 7 is d = d1 + d2; where d1 is the deformation of the tension spring 17 and d2 is the moving distance of the limiting end face; thus greatly improving the moving distance of the piston rod of the cylinder 7.

[0029] Therefore, this invention, through the collaborative design of the tension spring 17 and the cylinder 7, decomposes the total movement distance of the piston rod of the cylinder 7 into the deformation d1 of the tension spring 17 and the movement distance d2 of the limiting end face. Here, d2 is the small stroke required to achieve tension (adapting to the requirements of the small wire feeding frame 1), and d1 is the additional stroke brought by the tension spring 17. This makes the total movement distance d of the piston rod significantly greater than the small stroke d2 required for simple tensioning; thus extending the effective stroke of the cylinder 7, facilitating adaptation to conventional cylinders 7, and reducing costs. Therefore, this invention, through the superposition design of the deformation of the tension spring 17 and the movement distance of the limiting end face, makes the movement distance d of the piston rod of the cylinder 7 d = d1 + d2. Compared to the stroke requirements of traditional small-stroke cylinders 7, the effective stroke of the cylinder 7 in this structure is extended to the sum of d1 and d2. This stroke length is fully compatible with conventionally sized cylinders 7 on the market, eliminating the need for customized small high-precision cylinders 7, significantly reducing the manufacturing and procurement costs of the equipment, and facilitating large-scale promotion and application. Furthermore, the cylinder 7 required in this invention has two advantages: First, compared to the small-stroke cylinder 7, it has a larger cylinder diameter and a more sufficient air pressure chamber volume, resulting in higher air pressure transmission efficiency and less pressure loss and fluctuation. Even with slight fluctuations in the air source pressure, the output force of the conventional cylinder 7 changes relatively smoothly, forming a stable clamping force, effectively solving the problem of unstable clamping force of the traditional small-stroke cylinder 7 and improving the wire feeding accuracy. Second, it has higher air pressure efficiency and is less sensitive to air pressure changes. Under low air pressure conditions, the conventional cylinder 7 can still output sufficient driving force to complete the clamping action without forcibly increasing the air source pressure. At the same time, the sealing design of the conventional cylinder 7 is more mature, capable of withstanding a more reasonable pressure range, reducing seal wear and leakage failures, and significantly improving the reliability and service life of the equipment.

[0030] To ensure the stability of the overall relaxation process during the rotation and relaxation of the tension block 2, i.e., the release of tension on the wire feeder 1, in one embodiment, the tension head 19 is provided with several slots, the tension block 2 is located inside the slots, and the width of the end face of the tension block 2 near the moving head 10 is greater than the width of the slot along the shaft 4. The tension block 2 is provided with a pressing surface. When the tension spring 17 is stretched to a preset threshold, the pressing surface presses against the slot, thereby playing a limiting role. When the pressing surface presses against the slot, it indicates that the tension block 2 is at the limit of rotation and relaxation. At this time, the wire feeder 1 can be directly taken out or inserted.

[0031] Furthermore, the tension spring 17 not only provides additional stroke, but its pre-stretched state also provides continuous pre-tension force to the tensioning structure. When the pay-off frame 1 is subjected to instantaneous load fluctuations, the elastic buffering effect of the tension spring 17 can offset some of the fluctuations, preventing instantaneous changes in tension force. At the same time, the tight fit between the limiting end face and the tensioning head 19 achieves mechanical hard limiting, further restricting the displacement of the tensioning block 2, ensuring tensioning positioning accuracy, and effectively solving the problem of tension force fluctuation in the existing structure. Similarly, this invention only adds the tension spring 17 and the matching connecting structure to the existing pneumatic tensioning structure, with minimal structural changes and low cost, and no need for complex modifications to the cylinder 7 itself. Moreover, by adjusting the elastic coefficient and initial tension of the tension spring 17, it can flexibly adapt to the tensioning requirements of small pay-off frames 1 of different specifications, and is especially suitable for scenarios with high tensioning accuracy requirements, such as microelectronic component packaging and precision film winding.

[0032] Since most standard cylinders 7 have a minimum stroke limitation, they are difficult to adapt to the extremely small stroke drive requirements of small wire frames. Customizing micro cylinders would lead to soaring costs and long delivery cycles. Furthermore, the thrust output of cylinder 7 is greatly affected by air pressure fluctuations. During the short-stroke tensioning process, even a small change in air pressure can cause significant fluctuations in tension force, making it impossible to provide a constant tension force for the wire frame. This, in turn, affects the uniformity of tension during subsequent wire winding and unwinding, resulting in quality defects such as wire movement and tensile deformation. Therefore, the introduction of the aforementioned tension spring 17 can ensure that the piston rod of cylinder 7 obtains sufficient stroke to meet the forming requirements. In this case, standard cylinder 7 can be used directly without customization, thereby greatly reducing the cost of the structure while ensuring a constant tension force.

[0033] In addition to the aforementioned effects, this invention, through the coordinated design of the tension spring 17 and the cylinder 7, effectively resolves the contradiction between the lag in the pneumatic control system and the requirement for short-stroke response. To achieve precise control during short strokes, a precision pressure regulating valve is required. However, the cylinder 7 has an extremely short response time (typically milliseconds) during short strokes. Conventional pneumatic control systems inherently exhibit response lag. When the pay-off frame 1 needs fine-tuning of tension due to fluctuations in wire tension, the pneumatic adjustment signal has not yet fully reached the cylinder 7, and the pay-off frame has already momentarily loosened or become too tight. Furthermore, this lag accumulates in high-frequency tension fine-tuning scenarios (such as small pay-off frames for high-speed winding of precision films), leading to uneven winding density. The coordinated design of tension spring 17 and cylinder 7 increases the short stroke of cylinder 7, that is, increases the internal adjustable gas capacity, thereby improving the response speed of conventional air pressure control system (the larger the gas capacity, the more significant the adjustment of air pressure changes, and the more sensitive the observation of air pressure magnitude); secondly, it effectively solves the problem of easy fluctuation of tension force; because the thrust output of conventional cylinder 7 is greatly affected by air pressure fluctuations, even a small change in air pressure during short stroke tensioning will cause significant fluctuations in tension force, thus failing to provide a constant tension force for the wire frame, which in turn affects the tension uniformity of subsequent winding and unwinding of the coil, leading to quality defects such as wire shaking or tensile deformation.

[0034] In one embodiment, the shaft 4 is connected to a rotating sleeve 13 via a first bearing 15; a rotating disk 9 driven by a rotating mechanism is fixedly connected to the end of the rotating sleeve 13 away from the tensioning head 19, and the rotating disk 9 rotates synchronously with the wire feeding frame 1; a movable sleeve 11 is slidably connected to the rotating sleeve 13; a synchronous rotation assembly is provided between the movable sleeve 11 and the rotating sleeve 13, and the synchronous rotation assembly is used to limit the movement of the movable sleeve 11 within a preset length range; the movable head 10 is rotatably connected to the end of the push rod 3 via a second bearing 16, wherein the rotating mechanism can be a common belt drive mechanism. The belt meshes with the rotating disk 9. Therefore, when the tensioning block 2 tensions the pay-off frame 1, the belt drive mechanism is activated, thereby driving the rotating disk 9 to rotate, which in turn drives the rotating sleeve 13 to rotate, realizing the winding of the pay-off frame 1. The movable sleeve 11 is provided with a through groove 12. The synchronous rotation component includes a limit key fixed to the rotating sleeve 13 by bolts. The limit key passes through the through groove 12, and the sidewalls of the limit key abut against the sidewalls of the through groove 12. The length of the through groove 12 is the width of a preset length range, so that the movable sleeve 11 can move and can also rotate synchronously with the rotating sleeve 13. In addition, the pay-off frame 1 is provided with a positioning hole. A rotating rod 14 matching the positioning hole is fixed to the side of the rotating disk 9 near the tensioning head 19, thereby realizing the synchronous rotation of the rotating disk 9 and the pay-off frame 1.

[0035] Since the push rod 3 moves by pushing the moving head 10 through the second bearing 16, the second bearing 16 is subjected to a large axial force during this process, which reduces the life of the second bearing 16. Therefore, in one embodiment, the moving head 10 is provided with several positioning rods inside, and the push rod 3 is provided with an annular groove. Several balls are embedded on the side wall of the positioning rod located inside the annular groove. The spherical surface of the balls abuts against the inner wall of the annular groove. When the push rod 3 moves, the annular groove will push the balls to move axially, thereby pushing the positioning rod and the moving head 10 to move. When the moving head 10 rotates, the balls roll and rub against the inner wall of the annular groove. This achieves the pushing of the moving head 10 by the push rod 3, avoids the push rod 3 affecting the rotation quality of the moving head 10, and also greatly improves the service life of the second bearing 16.

[0036] In one embodiment, a bottom cover 21 is threadedly connected to the end of the rotating sleeve 13. One end of the bottom cover 21 presses against the outer ring of the first bearing 15. A limiting post is provided at the end of the bottom cover 21 away from the first bearing 15. A tension spring 17 is sleeved outside the limiting post, and one end of the tension spring 17 is fixed to the bottom cover 21. This ensures that when the rotating sleeve 13 rotates, the tension spring 17 can rotate synchronously, thus preventing the tension spring 17 from twisting and ensuring its normal use. Several adjusting plates 20 are provided between the bottom cover 21 and the tension spring 17. The bottom cover is provided with... The device has a threaded hole, and the adjusting plate 20 has a through hole aligned with the threaded hole. After the stud of the clamping bolt is fitted with the pressure plate, it passes through the through hole and is threadedly connected to the threaded hole. The pressure plate is inserted between the two elastic rings of the tension spring 17. When the clamping bolt is tightened, the pressure plate presses the bottom elastic ring of the tension spring 17 onto the adjusting plate 20, thereby realizing the adjustment of the initial tension of the tension spring 17 mentioned above. It can flexibly adapt to the tensioning requirements of small wire feeders 1 of different specifications, and is especially suitable for scenarios with high tensioning accuracy requirements such as microelectronic component packaging and precision film winding.

[0037] In one embodiment, a fixing frame is also included, on which a fixing plate 5 is provided. A cylinder 7 is fixedly connected to the fixing plate 5, and the shaft 4 is fixedly connected to the fixing plate 5 to ensure that the shaft 4 is fixed and facilitates the stable transmission of other components. In addition, the present invention also includes a second clamping unit with the same structure as the first clamping unit. The first clamping unit and the second clamping unit are symmetrically distributed about the fixing plate 5. The fixing plate 5 is cross-shaped, and a cylinder 7 is fixedly connected to each of the four ends of the fixing plate 5. The piston rods of the two symmetrically distributed cylinders 7 face the same direction. Each shaft 4 has two notches 6 at one end near the fixing plate 5. A connecting rod 8 is fixedly connected to each piston rod, and the connecting rod 8 passes through the notch 6 and is fixedly connected to the push rod 3. Through the symmetrical design, the number of wire feeding frames 1 installed in the present invention is increased while the overall structure of the present invention is more compact. The width of the notch 6, h>1.5d, ensures the effective extension and retraction range of the piston rod and avoids collision.

[0038] It should be noted that when a component is said to be "fixed to" another component, it can be directly attached to the other component or there may be an intervening component. When a component is said to be "connected to" another component, it can be directly connected to the other component or there may be an intervening component. The terms "upper," "lower," "left," "right," "front," "back," and similar expressions used in this document are for illustrative purposes only.

[0039] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention in any way. Although the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make some modifications or alterations to the above-disclosed technical content to create equivalent embodiments without departing from the scope of the present invention. Any simple modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present invention without departing from the scope of the present invention shall still fall within the scope of the present invention.

Claims

1. A pneumatic clamping structure for a wire feeding frame, characterized in that, The device includes a first clamping unit, which comprises a shaft, a movable sleeve slidably connected to the shaft, a push rod slidably connected inside the shaft and driven by a cylinder, a tension head fixed to the end of the movable sleeve, a tension spring with its two ends fixed to the end face of the shaft and the inner end face of the tension head, a tension block rotatably connected to the tension head, and a linkage mechanism located at the end of the push rod for connecting the movable head and the tension block; the linkage mechanism converts the linear movement of the movable head into the rotational movement of the tension block. When the limiting end face of the moving head separates from the end face of the tensioning head, the tension spring is stretched by force, and the tensioning block rotates to achieve relaxation. When the limiting end face of the moving head abuts against the end face of the tensioning head, the limiting end face restricts the rotation of the tensioning block to achieve tensioning. During this process, the tension spring retracts, and the piston rod in the cylinder moves a distance d = d1 + d2; where d1 is the deformation of the tension spring and d2 is the distance the limiting end face moves.

2. The pneumatic clamping structure of the wire feeding frame according to claim 1, characterized in that, The shaft is connected to a rotating sleeve via a first bearing; a rotating disk driven by a rotating mechanism is fixedly connected to one end of the rotating sleeve away from the tensioning head, and the rotating disk rotates synchronously with the wire feeding frame; the movable sleeve is slidably connected to the rotating sleeve; a synchronous rotation component is provided between the movable sleeve and the rotating sleeve, and the synchronous rotation component is used to limit the movement of the movable sleeve within a preset length range; the movable head is rotatably connected to the end of the push rod via a second bearing.

3. The pneumatic clamping structure of the wire feeding frame according to claim 2, characterized in that, The rotating sleeve is threaded to a bottom cover at one end. One end of the bottom cover presses against the outer ring of the first bearing. A limiting post is provided at the end of the bottom cover away from the first bearing. The tension spring is sleeved outside the limiting post and one end of the tension spring is fixed to the bottom cover.

4. The pneumatic clamping structure of the wire feeding frame according to claim 3, characterized in that, Several adjusting plates are provided between the bottom cover and the tension spring. The bottom cover has a threaded hole, and the adjusting plate has a through hole aligned with the threaded hole. After the stud of the clamping bolt is fitted with the pressure plate, it passes through the through hole and is threadedly connected to the threaded hole. The pressure plate is inserted between the two elastic rings of the tension spring. When the clamping bolt is tightened, the pressure plate presses the bottom elastic ring of the tension spring onto the adjusting plate.

5. The pneumatic clamping structure of the wire feeding frame according to claim 2, characterized in that, It also includes a fixing frame, on which a fixing plate is provided, and the cylinder is fixedly connected to the fixing plate, and the shaft is fixedly connected to the fixing plate.

6. The pneumatic clamping structure of the wire feeding frame according to claim 5, characterized in that, It also includes a second clamping unit with the same structure as the first clamping unit. The first clamping unit and the second clamping unit are symmetrically distributed about the fixed plate. The fixed plate is cross-shaped, and a cylinder is fixedly connected to each of the four ends of the fixed plate. The piston rods of the two symmetrically distributed cylinders face the same direction. Each shaft has two notches at one end near the fixed plate. A connecting rod is fixedly connected to each piston rod, and the connecting rod passes through the notch and is fixedly connected to the push rod. The width of the notch is h > 1.5d.

7. The pneumatic clamping structure of the wire feeding frame according to claim 2, characterized in that, The wire feeding frame is provided with a positioning hole, and a rotating rod matching the positioning hole is fixedly connected to the side of the rotating disk near the tensioning head.

8. The pneumatic clamping structure of the wire feeding frame according to claim 1, characterized in that, The linkage mechanism includes a connecting rod with one end rotatably connected to the moving head and the other end rotatably connected to the tensioning block; the moving head drives the tensioning block to rotate through the connecting rod.

9. The pneumatic clamping structure of the wire feeding frame according to claim 1, characterized in that, The tensioning head is provided with a plurality of slots, the tensioning block is located inside the slots, and the width of the end face of the tensioning block near the moving head is greater than the width of the slot along the axis, and the tensioning block is provided with a pressing surface. When the tension spring is stretched to a preset threshold length, the pressing surface presses against the slot.

10. The pneumatic clamping structure of the wire feeding frame according to claim 1, characterized in that, The moving head has several positioning rods inside, and the push rod has an annular groove. Several balls are embedded on the side wall of the positioning rod inside the annular groove, and the spherical surface of the balls abuts against the inner wall of the annular groove.

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