Double friction double tensioning slip ring

Abstract

This utility model relates to the field of differential ring technology, and in particular to a double-friction, double-tensioning differential ring, comprising a differential ring body for high-tension winding operations. The differential ring body includes a tensioning piston seat, two tensioning wedges, several tensioning blocks, a differential piston component, a differential piston seat, a first friction disc, and a second friction disc. The purpose of this utility model is to provide a double-friction, double-tensioning differential ring that can achieve high-tension winding under low air pressure and has high-precision tension control.

Description

Technical Field

[0001] This utility model relates to the field of differential ring technology, and in particular to a double-friction double-tension differential ring. Background Technology

[0002] In industrial production, especially in high-tension winding applications such as metal coils and high-strength film winding, traditional differential rings have significant limitations: single friction disc designs lack sufficient tension output, requiring reliance on high-pressure air sources, resulting in high energy consumption and bulky equipment; the tensioning structure is often a single-unit design, leading to low force transmission efficiency and difficulty in achieving high tension output under low air pressure; poor air circuit sealing performance easily causes media leakage, leading to tension fluctuations; and high frictional resistance between the friction disc and adjacent components affects winding stability and equipment lifespan. Furthermore, the high resistance during coil loading and unloading easily damages the coil, failing to meet the demands for high-precision, high-efficiency, high-tension winding. Utility Model Content

[0003] Based on this, the purpose of this utility model is to provide a double-friction double-tension slip ring that can achieve high-tension winding under low air pressure and has high-precision tension control.

[0004] The present invention adopts the following technical solution:

[0005] A double-friction, double-tensioning differential ring includes a differential ring body for high-tension winding operations. The differential ring body includes a tensioning piston seat, two tensioning wedges, several tensioning blocks, a differential piston component, a differential piston seat, a first friction disc, and a second friction disc. Piston receiving grooves are provided at both ends of the tensioning piston seat to accommodate the differential piston component. The differential piston component, through axial movement, drives the abutting tensioning wedges to move radially along the tensioning piston seat. The two tensioning wedges are respectively movably engaged on both sides of the tensioning piston seat. Each tensioning wedge abuts against the differential piston component below and is adapted to the tensioning block above, so as to push the tensioning block through radial movement. The differential piston seat is located on one side of the first friction disc. The side of the first friction disc opposite to the differential piston seat abuts against the tensioning piston seat. The second friction disc is located on the side of the tensioning piston seat opposite to the first friction disc, and the side protrusions of the first and second friction discs abut against the tensioning blocks respectively.

[0006] A further improvement to the above technical solution is that the annular wall of the tensioning piston seat is provided with a through main air source channel, and the two ends of the main air source channel are respectively extended with air distribution branches communicating with the piston receiving groove. The air distribution branches are used to guide the air source medium into the piston receiving groove to drive the slip differential piston to make a pushing motion along the axial direction of the piston receiving groove.

[0007] A further improvement to the above technical solution is that an air passage partition ring is connected below the tensioning piston seat, and the air passage partition ring has a through air hole, which is used to guide the air source medium to flow to the bottom of the air source main channel.

[0008] A further improvement to the above technical solution is that a plurality of first sealing rings are embedded on the wall surface of the gas passage isolation ring away from the tensioning piston seat.

[0009] A further improvement to the above technical solution is that a second sealing ring is embedded between the air passage spacer ring and the tensioning piston seat.

[0010] A further improvement to the above technical solution is that a first bearing and a second bearing are respectively assembled below the two axial ends of the tensioning piston seat; the first bearing is adapted to the inner side of the first friction disc, and the second bearing is adapted to the inner side of the second friction disc.

[0011] A further improvement to the above technical solution is that the differential piston component includes a piston body, and a piston sealing ring is embedded in the outer peripheral wall of the piston body.

[0012] A further improvement to the above technical solution is that a third sealing ring is embedded in the inner peripheral wall of the differential piston seat.

[0013] A further improvement to the above technical solution is that a number of rollers are evenly distributed around the outer periphery of the slip piston seat. The rollers are used to reduce the resistance during the winding process of pushing or pushing the material roll.

[0014] A further improvement to the above technical solution is that the radial outer wall of the tensioning wedge is provided with a plurality of driving inclined surfaces, and the radial inner wall of the tensioning block is provided with a force-receiving inclined surface, wherein the force-receiving inclined surface and the driving inclined surface are in a complementary wedge-shaped fit.

[0015] The beneficial effects of this utility model are as follows:

[0016] This invention utilizes a dual-friction disc and dual-tensioning synergistic structure comprised of a tensioning piston seat, two tensioning wedges, several tensioning blocks, a differential piston component, a differential piston seat, a first friction disc, and a second friction disc. Combined with a highly efficient air path system formed by the main air source channel, branch air paths, air path separators, and air passage holes, it achieves high tension output under low air pressure input. The first sealing ring, second sealing ring, piston sealing ring, and third sealing ring ensure a complete seal throughout the air path, preventing pressure loss. The first and second bearings reduce the rotational resistance of the friction discs, improving transmission efficiency. The rollers on the outer periphery of the differential piston seat reduce the resistance during material loading and unloading, protecting the quality of the roll material. The synergistic effect of these components not only meets the high tension and high stability requirements of high-tension winding but also reduces energy consumption and equipment wear, extends service life, and significantly improves the efficiency and reliability of high-tension winding operations. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the structure of the double-friction double-tension slip ring of this utility model;

[0018] Figure 2 for Figure 1 Side view of a double-friction, double-tensioning differential ring;

[0019] Figure 3 for Figure 2 A cross-sectional view of a double-friction, double-tensioning differential ring along the AA direction;

[0020] Figure 4 for Figure 1 A three-dimensional sectional view of a double-friction, double-tensioning differential ring;

[0021] Figure 5 for Figure 4 A magnified view of circle A of the double-friction, double-tensioning differential ring.

[0022] The numbers on the map are:

[0023] 10. Slip ring body; 11. First friction disc; 12. Second friction disc; 13. Side protrusion; 20. Tensioning piston seat; 21. Piston receiving groove; 22. Main air supply channel; 23. Branch air supply channel; 24. Second sealing ring; 25. First bearing; 26. Second bearing; 30. Tensioning wedge; 31. Driving inclined surface; 40. Tensioning block; 41. Force-bearing inclined surface; 50. Slip piston component; 51. Piston body; 52. Piston sealing ring; 60. Slip piston seat; 61. Third sealing ring; 62. Roller; 70. Air passage spacer ring; 71. First sealing ring. Detailed Implementation

[0024] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0025] In the description of this utility model, it should be noted that the terms "vertical direction," "up," "down," and "horizontal," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. In addition, "first," "second," "third," and "fourth" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0026] In the description of this utility model, it should also be noted that, unless otherwise explicitly specified and limited, the terms "set," "install," "connect," and "link" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or a connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0027] like Figures 1 to 5 The image shows an embodiment of the present invention, relating to a double-friction, double-tensioning differential ring, comprising a differential ring body 10 for high-tension winding operations. The differential ring body 10 includes a tensioning piston seat 20, two tensioning wedges 30, several tensioning blocks 40, a differential piston component 50, a differential piston seat 60, a first friction disc 11, and a second friction disc 12. Piston receiving grooves 21 are provided at both ends of the tensioning piston seat 20, which are used to accommodate the differential piston component 50. The differential piston component 50, through axial movement, drives the abutting tensioning wedges 30 to move radially along the tensioning piston seat 20. The tensioning wedges 30 are respectively movably engaged on both sides of the tensioning piston seat 20. Each tensioning wedge 30 abuts against the slip piston 50 below and is adapted to the tensioning block 40 above, so as to push the tensioning block 40 through radial movement. The slip piston seat 60 is located on one side of the first friction disc 11. The side of the first friction disc 11 away from the slip piston seat 60 abuts against the tensioning piston seat 20. The second friction disc 12 is located on the side of the tensioning piston seat 20 away from the first friction disc 11, and the side protrusions 13 of the first friction disc 11 and the second friction disc 12 abut against the tensioning block 40 respectively.

[0028] Specifically, through the overall layout of the tensioning piston seat 20, two tensioning wedges 30, several tensioning blocks 40, a differential piston component 50, a differential piston seat 60, a first friction disc 11, and a second friction disc 12, a core structure for the coordinated operation of the dual friction discs and dual tensioning components is constructed. The dual tensioning wedges 30 are symmetrically distributed on both sides of the tensioning piston seat 20, forming a bidirectional force mechanism with the dual friction discs, significantly improving the tension output capability; the contact transmission design between the differential piston component 50 and the tensioning wedges 30 achieves efficient conversion of axial force to radial force, laying the structural foundation for high tension output under low air pressure and meeting the coordinated requirements of the core transmission components for high tension winding.

[0029] like Figure 3 and Figure 5 As shown, the annular wall of the tensioning piston seat 20 has a through-flow main air source channel 22. Both ends of the main air source channel 22 extend into branch air paths 23 that communicate with the piston receiving groove 21. These branch air paths 23 guide the air source medium into the piston receiving groove 21 to drive the slip differential piston 50 to perform a pushing motion along the axial direction of the piston receiving groove 21. Specifically, the design of the main air source channel 22 and branch air paths 23 ensures that the air source medium can be precisely guided to the piston receiving groove 21, providing stable power for the axial movement of the slip differential piston 50. This precise air path layout ensures the high efficiency and stability of air pressure transmission, thereby ensuring the reliability of the slip differential piston 50 driving the tensioning wedge 30. It is a key air path guarantee for achieving high tension winding with low air pressure, and helps improve the accuracy and response speed of tension control. In this embodiment, the upper part of the main air source channel 22 is sealed by a sealing element.

[0030] like Figure 3 As shown, an air passage partition ring 70 is connected below the tensioning piston seat 20. The air passage partition ring 70 has a through-hole (not shown in the figure) to guide the air source medium to the bottom of the air source main channel 22. Specifically, the air passage partition ring 70 and the through-hole (not shown in the figure) optimize the flow path of the air source medium, enabling the air source to smoothly reach the bottom of the air source main channel 22 and enter the air source main channel 22, ensuring the integrity and smoothness of the entire air passage system. This helps to balance the air pressure distribution, avoid air pressure loss or unevenness caused by air passage obstruction, and further improve the working stability and reliability of the slip ring under low air pressure input, which is of great significance for achieving stable operation of high tension winding. At the same time, the air passage partition ring 70 provides axial support to the tensioning piston seat 20, enhances the overall structural rigidity, reduces component deformation during high tension winding, and ensures the coordinated stability of the air passage and transmission system.

[0031] like Figure 3As shown, the gas passage diaphragm 70 has several first sealing rings 71 embedded on its wall surface away from the tension piston seat 20. Specifically, the first sealing rings 71 effectively block the leakage path of the gas source medium from the outside of the diaphragm. By tightly fitting with adjacent components, a radial sealing barrier is formed, maintaining the pressure balance between the air passage (not shown in the figure) and the main gas source channel 22, avoiding the attenuation of driving force due to air leakage, and ensuring the stability of tension output under low air pressure.

[0032] like Figure 5 As shown, a second sealing ring 24 is embedded between the air passage spacer ring 70 and the tensioning piston seat 20. Specifically, the second sealing ring 24 enhances the sealing performance at the connection between the two. Through the axial sealing design, leakage of the air source from the mating gap between the spacer ring and the piston seat is prevented, ensuring the overall airtightness of the air passage system, enabling the air distribution branch 23 to stably supply air to the piston receiving groove 21, and providing continuous driving force for the slip differential piston component 50.

[0033] like Figure 5 As shown, a first bearing 25 and a second bearing 26 are respectively mounted below the axial ends of the tensioning piston seat 20; the first bearing 25 is adapted to the inner side of the first friction disc 11, and the second bearing 26 is adapted to the inner side of the second friction disc 12. Specifically, the first bearing 25 and the second bearing 26 are adapted to the inner sides of the first friction disc 11 and the second friction disc 12, respectively, converting the sliding friction between the friction disc and the piston seat into rolling friction, significantly reducing rotational resistance. This design reduces energy loss, allows the friction disc to rotate smoothly and synchronously with the material roll, avoids tension instability caused by resistance fluctuations, and extends the service life of the friction disc and the piston seat.

[0034] like Figure 4 and Figure 5 As shown, the differential piston component 50 includes a piston body 51, and a piston sealing ring 52 is embedded in the outer peripheral wall of the piston body 51. Specifically, the piston sealing ring 52 on the outer peripheral wall of the differential piston component 50 achieves dynamic sealing between the piston body 51 and the piston receiving groove 21. During the axial movement of the differential piston component 50, the sealing ring always fits against the inner wall of the receiving groove, preventing air leakage from the piston gap, ensuring stable air pressure in the receiving groove, and enabling the differential piston component 50 to accurately transmit driving force to the tensioning wedge block 30, ensuring the consistency of the force amplification effect.

[0035] like Figure 4 As shown, a third sealing ring 61 is embedded in the inner circumferential wall of the differential piston seat 60. Specifically, the third sealing ring 61 enhances the sealing performance between the piston seat and adjacent components such as the main shaft. By blocking possible leakage paths, it maintains a stable internal air pressure environment of the differential ring, prevents external impurities from entering and affecting transmission accuracy, and prevents internal air source loss, indirectly ensuring the continuity of high tension output.

[0036] like Figure 1 and Figure 4 As shown, the outer periphery of the differential piston seat 60 is circumferentially distributed with several rollers 62. These rollers 62 are used to reduce the resistance during the winding process of pushing or pushing the material roll. Specifically, the rollers 62 circumferentially distributed on the outer periphery of the differential piston seat 60 replace the sliding contact between the material roll and the piston seat through rolling contact, significantly reducing the frictional resistance during the pushing or pushing of the material roll. This design reduces damage to the material roll during loading and unloading, enables the material roll to be positioned quickly, and avoids the interference of sudden changes in resistance on the winding tension, thereby improving the operational efficiency of high-tension winding.

[0037] like Figure 5 As shown, the radially outer wall of the tensioning wedge 30 is provided with several driving inclined surfaces 31, and the radially inner wall of the tensioning block 40 is provided with a force-receiving inclined surface 41. The force-receiving inclined surface 41 and the driving inclined surface 31 are in a complementary wedge-shaped fit. Specifically, the driving inclined surface 31 of the tensioning wedge 30 and the force-receiving inclined surface 41 of the tensioning block 40 form a complementary wedge-shaped fit, utilizing the wedge surface mechanics principle to achieve a force amplification. When the tensioning wedge 30 moves radially, the component force generated by the inclined surface contact gives the tensioning block 40 an axial pressure far exceeding the input force. Combined with the double tensioning structure, the double friction discs can generate frictional force sufficient for high-tension winding under low air pressure, which is the core transmission design for achieving high tension under low air pressure.

[0038] The working principle of this utility model is as follows:

[0039] During operation, the gas source medium enters the main gas source channel 22 of the tensioning piston seat 20 through the air passage hole (not shown in the figure) of the gas passage partition ring 70, and then enters the piston receiving groove 21 through the gas distribution branch 23, driving the slip differential piston 50 to move axially. The slip differential piston 50 pushes the tensioning wedges 30 on both sides, causing them to move radially along the tensioning piston seat 20. The driving inclined surface 31 of the tensioning wedge 30 and the force-receiving inclined surface 41 of the tensioning block 40 are mutually complementary wedge-shaped, converting the radial force into the axial pressure of the tensioning block 40 on the first friction disk 11 and the second friction disk 12. The double friction disks generate friction under pressure. Through the force amplification effect of the double tensioning structure and the superposition of the friction of the double friction disks, a large tension output under a small air pressure input is achieved. Meanwhile, the first bearing 25 and the second bearing 26 reduce the rotational resistance of the friction disc, and the first sealing ring 71, the second sealing ring 24, the piston sealing ring 52, and the third sealing ring 61 ensure the air passage is sealed. The roller 62 on the outer periphery of the differential piston seat 60 reduces the resistance of loading and unloading the material roll, together ensuring the stability and efficiency of high-tension winding.

[0040] The above description merely illustrates the preferred technical solution of this utility model, and while the description is relatively specific and detailed, it should not be construed as limiting the scope of the utility model patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this utility model, and this utility model also intends to include these modifications and variations.

Claims

1. A double-friction, double-tensioning differential ring, characterized in that, The device includes a differential ring body for high-tension winding operations. The differential ring body comprises a tensioning piston seat, two tensioning wedges, several tensioning blocks, a differential piston component, a differential piston seat, a first friction disc, and a second friction disc. The tensioning piston seat has piston receiving grooves at both ends to accommodate the differential piston component. The differential piston component, through axial movement, drives the abutting tensioning wedges to move radially along the tensioning piston seat. The two tensioning wedges are movably engaged on both sides of the tensioning piston seat, with each wedge abutting the differential piston component below and fitting with a tensioning block above, so as to push the tensioning block through radial movement. The differential piston seat is located on one side of the first friction disc. The side of the first friction disc opposite to the differential piston seat abuts against the tensioning piston seat. The second friction disc is located on the side of the tensioning piston seat opposite to the first friction disc, and the side protrusions of the first and second friction discs abut against the tensioning blocks.

2. The double-friction, double-tensioning differential ring according to claim 1, characterized in that, The annular wall of the tensioning piston seat has a through main air source channel, and the two ends of the main air source channel have air distribution branches that communicate with the piston receiving groove. The air distribution branches are used to guide the air source medium into the piston receiving groove to drive the slip differential piston to make a pushing motion along the axial direction of the piston receiving groove.

3. The double-friction, double-tensioning differential ring according to claim 2, characterized in that, Below the tensioning piston seat is a gas passage partition ring, which has a through-hole for guiding the gas source medium to the bottom of the main gas source channel.

4. The double-friction, double-tensioning differential ring according to claim 3, characterized in that, The gas passage spacer ring is fitted with several first sealing rings on the wall surface away from the tensioning piston seat.

5. The double-friction, double-tensioning differential ring according to claim 3, characterized in that, A second sealing ring is fitted between the gas passage spacer ring and the tensioning piston seat.

6. The double-friction, double-tensioning differential ring according to claim 1, characterized in that, The tensioning piston seat is equipped with a first bearing and a second bearing at its two axial ends respectively; the first bearing is adapted to the inner side of the first friction disc, and the second bearing is adapted to the inner side of the second friction disc.

7. The double-friction, double-tensioning differential ring according to claim 1, characterized in that, The differential piston assembly includes a piston body, and a piston sealing ring is embedded in the outer peripheral wall of the piston body.

8. The double-friction, double-tensioning differential ring according to claim 1, characterized in that, The inner circumferential wall of the differential piston seat is fitted with a third sealing ring.

9. The double-friction, double-tensioning differential ring according to claim 8, characterized in that, The outer peripheral edge of the differential piston seat is evenly distributed with several rollers, which are used to reduce the resistance during the winding process of pushing or pushing the material roll.

10. The double-friction, double-tensioning differential ring according to claim 1, characterized in that, The outer radial wall of the tensioning wedge is provided with several driving inclined surfaces, and the inner radial wall of the tensioning block is provided with a force-receiving inclined surface. The force-receiving inclined surface and the driving inclined surface are in a complementary wedge-shaped fit.

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