A pull whistle inerter damper and design method and application thereof

Abstract

The application discloses a kind of pull whistle inertial damper and its design method and application.The damper uses modular assembly structure, including C type hoop and the multiple pull whistle flywheel units being evenly arranged in its inside along the circumference.Coupled components such as pull whistle flywheel, steering pulley and SMA filament bundle are assembled into C type hoop cavity, horizontal driving cable is coaxially arranged with SMA filament bundle, changes direction through steering pulley, is converted into double-stranded twisted vertical driving cable and passes through the center of pull whistle flywheel horizontally placed, is fixedly connected with the bottom of C type hoop, and damping liquid is added in the inside of pull whistle flywheel unit and sealed.The application is fixed on the flange of columnar electrical equipment when in use, horizontal driving cable is connected with ground, and damping energy dissipation capacity and reset stability under reciprocating load can be considered, and when external excitation decreases or reverses, the tension of SMA filament bundle is used to forcibly drive cable to twist again, to prevent system relaxation failure.

Description

Technical Field

[0001] This invention relates to a pull-inertial capacitive damper, its design method and application, belonging to the field of vibration reduction / damping of electrical equipment with bending load as the main control factor. Background Technology

[0002] Substations and power transmission and distribution networks are critical lifeline projects in modern society. The main electrical equipment (such as surge arresters, instrument transformers, and disconnectors) within these systems, as core nodes, is of paramount importance for their safe and stable operation. These devices typically exhibit a slender and top-heavy structure, with the main insulation often made of brittle materials such as porcelain or composite insulators. The sections are rigidly connected by flanges and high-strength bolts. Under horizontal dynamic loads such as earthquakes or typhoons, the stress characteristics of these devices exhibit a typical cantilever beam effect, with bending failure primarily occurring at the root or flange connections. Due to the extremely low tensile and bending strength of the insulation materials, even a small horizontal relative displacement can generate a large concentrated bending moment at the flange interface, leading to rapid brittle fracture or overturning of the equipment under minimal displacement. This "small deformation - high bending moment stress" bending failure mode poses a significant challenge to traditional passive vibration damping / control technologies.

[0003] Currently, the engineering community commonly uses viscous dampers, friction dampers, or metal yield dampers to improve the wind and seismic (vibration) resistance of structures. However, traditional dampers mainly rely on the large macroscopic relative displacement of the structure to trigger the internal energy dissipation mechanism to perform work. For the mechanical characteristics of column-type electrical equipment, which are primarily subject to bending failure, the relative horizontal displacement of the flange at the point of critical fracture is often only on the order of millimeters. Under this tiny displacement excitation, traditional dampers are easily "locked" due to initial static friction; even if activated, their extremely limited piston stroke results in low damping energy dissipation efficiency. In recent years, inertial capacitance damping technology has received considerable attention in the field of disaster prevention and mitigation due to its "apparent quality" amplification effect. It can convert tiny linear displacements into high-speed rotation of a flywheel. However, existing inertial devices are mostly based on rigid mechanical transmission mechanisms such as ball screws or racks and pinions, resulting in excessive size and weight, greatly increasing the load on the flange nodes of the original equipment; furthermore, rigid transmission mechanisms are prone to mechanical jamming when facing tiny high-frequency bending vibrations of the equipment, making it difficult to provide stable and reliable damping force.

[0004] To address the drawbacks of rigid transmissions, such as susceptibility to jamming and excessive weight, the introduction of flexible cable-driven systems (e.g., pull-whistle transmission mechanisms) has become a promising solution. Flexible cables can adapt flexibly to the complex stress environment at flange joints and significantly reduce the added mass of dampers. However, applying purely flexible cable systems to actual structural vibration reduction / damping faces severe structural dynamic challenges: under random reciprocating earthquake or gust loads, cable drives can only withstand tension and not compression. When the equipment enters the unloading and reverse loading phases during bending vibration, the residual inertia of the flywheel alone cannot guarantee the rapid return of the cable system, easily leading to slackening failure of the flexible cable system. This results in a dead zone in the damper, causing a loss of continuous energy dissipation capacity; even the instant the cable re-tensions can generate a huge dynamic tensile impact, causing fatigue fracture of the high-strength cable system. In summary, given the engineering challenge of beam-type electrical equipment being prone to bending failure under minute deformations, there is an urgent need to develop a new type of damper that can utilize a flexible mechanism to achieve high-magnification of minute displacements and efficient energy dissipation, possess a compact modular installation form, and completely solve the structural problem of rope slack under reciprocating loads. This would provide a highly reliable vibration reduction solution for the disaster prevention and mitigation of electrical equipment. Summary of the Invention

[0005] To address the aforementioned problems, this invention proposes a pull-sensor inertial capacitive damper, its design method, and its application. By integrating the high-rate displacement amplification effect of the pull-sensor mechanism with the energy dissipation of the locally sealed damping fluid, and utilizing coaxially nested pure tension SMA filament bundles to provide a superelastic restoring force to force the cable to re-twist, this invention solves the problems of traditional rigid dampers being difficult to trigger and prone to jamming under small deformations, as well as the easy relaxation and failure of purely flexible cables. It achieves zero dead zone, high sensitivity, energy dissipation, and adaptive displacement control throughout the entire vibration cycle.

[0006] The above objectives are achieved through the following technical solutions:

[0007] The present invention first provides a pull-sensor inertial-capacitive damper, comprising: a C-shaped ring hoop, and a plurality of independent damping / energy dissipation units uniformly arranged circumferentially inside the C-shaped ring hoop; each of the damping / energy dissipation units includes a partially independently sealed flywheel cavity and a pull-sensor flywheel and damping fluid disposed in the flywheel cavity, an SMA wire bundle and a steering pulley disposed outside the flywheel cavity, and a horizontal drive cable and a vertical drive cable for driving the pull-sensor flywheel;

[0008] The pull-off flywheel is placed horizontally and immersed in the damping fluid inside the flywheel cavity. The steering pulley is fixed above the flywheel cavity. The outer end of the horizontal drive cable extends out of the C-shaped hoop, and its inner end, before passing around the steering pulley, is coaxially nested with the SMA filament bundle in a horizontal section. One end of the SMA filament bundle is fixed to the horizontal drive cable, and the other end is anchored to the bracket on the side of the steering pulley without contacting the pulley's working groove. After passing around the steering pulley, the horizontal drive cable changes direction to a vertically downward and double-stranded twisted vertical drive cable. The vertical drive cable is formed by two fiber cables intertwined to form a double-stranded twisted structure. The vertical drive cable passes through the central opening of the pull-off flywheel and its bottom end is anchored to the bottom of the flywheel cavity.

[0009] Furthermore, the C-shaped ring is assembled from at least two semi-circular shells; after the C-shaped ring is fixed, the internal shock absorption / vibration energy dissipation units are arranged in a radial circumferential array.

[0010] Furthermore, the SMA filament bundle is in the form of a tubular bundle or a parallel straight filament bundle, covering the periphery of the horizontal drive cable, and is always in a state of pure tension without passing through the steering pulley.

[0011] Furthermore, the horizontal and vertical drive cables are made of high-strength flexible fiber materials, including high-strength polyethylene, aramid fiber, or other high-strength flexible fiber materials; the shell of the independently sealed small cavity assembly is made of high-strength corrosion-resistant metal or engineering plastic; and the SMA filament bundle is composed of multiple nickel-titanium alloy straight wires.

[0012] The present invention also provides an application of the above-mentioned pull-sensor inertial capacitive damper, wherein the pull-sensor inertial capacitive damper is installed at the flange of the electrical equipment section, and the C-type ring is fixed at the flange of the support-type electrical equipment. Multiple horizontal drive cables extend outward from the side wall opening of the C-type ring in a radial manner, and their outer ends are grounded or connected to fixed nodes or adjacent equipment at other elevations of the electrical equipment.

[0013] Under external loads such as earthquakes or strong winds, the minute relative bending deformation of the support-type electrical equipment pulls the horizontal drive cable outward. This tension is converted into a vertical upward tension by the steering pulley, causing the double-strand twisted vertical drive cable inserted into the flywheel cavity to untwist. Relying on the displacement amplification effect of the pull mechanism, this minute linear translation is converted into high-frequency rotation of the pull flywheel. The vibration mechanical energy is efficiently dissipated by high-speed shearing of the damping fluid in the sealed cavity, actively suppressing destructive large displacements of the equipment. At the same time, the SMA filament bundle, which is coaxially nested with the horizontal drive cable, undergoes synchronous displacement stretching and stores energy. When the external load enters unloading or reverses... During the half-cycle loading, the SMA filaments undergo a reverse phase transition due to their superelasticity, generating a strong horizontal pull force that inwardly pulls the horizontal drive cable, forcibly overcoming the residual inertia of the flywheel and simultaneously pulling back the vertical drive cable to re-twist it, restoring the initial tension of the transmission cable system and solving the problems of cable slack and dynamic tension impact during reciprocating vibration. Under extreme and rare disaster conditions, if the input displacement approaches the limit, the rigid wall of the C-shaped hoop and the independent cavity module work together to provide base limiting and anti-overturning functions, effectively preventing internal components from coming off and equipment from disintegrating. Moreover, the fully assembled structure allows for convenient maintenance of damaged units by simply opening the C-shaped hoop after vibration.

[0014] The present invention also provides a design method for the above-mentioned pull-out inertial capacitive damper, the method comprising the following steps:

[0015] S1. Determine vibration reduction / target parameters: Based on the seismic design requirements of support-type electrical equipment and relevant specifications, determine the design displacement of the target structure under the target working conditions. and maximum allowable displacement ;

[0016] S2. Set the inertial mass parameters of the puller: Set the helical lead L of the double-strand twisted structure of the vertical drive cable (3), and the moment of inertia of the puller flywheel (1) about its vertical central axis to J. Calculate the equivalent inertial mass b of the puller flywheel system, as shown in equation (1): (1);

[0017] S3. Determine the equivalent viscous damping parameters: Based on the surface area of ​​the pull-off flywheel (1) and its contact parameters with the damping fluid, determine the viscous damping parameters under rotational conditions. Calculate the equivalent damping coefficient of the damper in the horizontal direction. As shown in equation (2): (2);

[0018] S4. Determine the system's anti-slackening reset parameters: Analyze the extreme inertia and internal mechanical resistance of the reverse rotation of the whistle flywheel (1) to determine the minimum restoring force for system reset. Based on this, the total cross-sectional area of ​​the SMA filament bundle (4) was designed. With effective length Based on the superelastic properties of SMA, the tensile force provided during the unloading phase is ensured. Always greater than This forces the vertical drive cable (3) to twist again and return to its initial state, as shown in equation (3): (3);

[0019] S5. Parameter optimization and anti-collision design: Using optimization algorithms, combined with the maximum energy consumption objective function and the constraint conditions such as strain exceeding the limit, the flywheel rotational inertia J, vertical drive cable lead L, and horizontal drive cable stroke are iteratively optimized to ensure that the damper does not experience flywheel bottoming-out collision, cable breakage, or derailment failure under the maximum allowable displacement. The objective function and constraint conditions are shown in equations (4)-(7).

[0020] Total system energy consumption: (4); (5); (6); Strain exceeding limits: (7); In the formula: Total energy consumption Energy is consumed by the viscous shear of the damping fluid. Energy consumption for SMA filament bundles For the load loading period, To determine the rotational viscous damping parameters of the flywheel, The stress of a single SMA wire, For time, The maximum strain of the SMA wire. This refers to the maximum permissible displacement of support-type electrical equipment. This represents the initial effective length of the SMA filament bundle. This represents the maximum allowable strain for SMA materials.

[0021] Furthermore, the aforementioned flywheel vibration damping / energy dissipation unit can also achieve a smaller starting trigger force by designing the lead L of the vertical drive cable, the friction interface, and the viscosity of the damping fluid. This allows the flywheel to rotate and dissipate energy within the sealed cavity under minor earthquakes or normal wind loads; the initial starting force mechanism is shown in equation (8): (8); In the formula, This is the frictional resistance torque; This is the viscous resistance torque.

[0022] The advantages of this invention compared to the prior art are:

[0023] 1. By introducing a whistle mechanism, the displacement amplification effect of the double-strand torsion cable is cleverly utilized to transform the minute horizontal bending deformation at the flange of the support-type electrical equipment into the high-speed rotation of the flywheel in the sealed cavity, generating considerable equivalent inertial mass and viscous damping force. This enables the damper to be triggered and dissipated with high sensitivity under micro-vibration / oscillation or normal wind load, avoiding the defect of traditional rigid dampers that are difficult to activate due to static friction locking.

[0024] 2. By coaxially nesting the SMA filament bundle and the horizontal drive cable in the horizontal direction at the leading edge of the pulley, and avoiding the working groove of the pulley, the SMA filament bundle is ensured to always be in the most efficient pure tension working state. Utilizing the superelastic properties of SMA material, a continuous horizontal return force is provided during the unloading phase of the external load, forcing the vertical drive cable to re-twist. This solves the problem of easy relaxation failure of pure flexible transmission under reciprocating dynamic loads within a compact structural space.

[0025] 3. By setting up a fixed steering pulley, a smooth and seamless transition from horizontal translational motion to vertical torsional motion is achieved. The smooth transition at multiple angles effectively eliminates the instantaneous dynamic tension concentration and mechanical impact that may occur during force direction conversion; at the same time, the rigid support on the side of the pulley serves as the fixed reaction end of the SMA filament bundle, realizing a reasonable distribution of mechanical forces under coaxial stress, ensuring that the high-strength fiber drive cable does not experience fatigue shearing or slippage failure under high-frequency vibration.

[0026] 4. The parameters of the core components of the damper can be optimized through dynamic simulation. After determining the design parameters according to the seismic requirements of the electrical equipment, a mechanical model of the damper is established, and the lead, moment of inertia, and SMA cross-sectional area are initially calculated. Then, an optimization algorithm is used in conjunction with the objective function (maximum energy dissipation capacity) and constraints (drive cable strain not exceeding limits, no collision or derailment under maximum displacement, etc.) to perform parametric analysis and numerical simulation verification, so as to achieve the scientific determination and optimization of the device parameters, taking into account both vibration reduction performance and engineering economy.

[0027] 5. The entire damper adopts a fully assembled modular structure, rigidly fixed to the equipment flange by C-shaped ring clamps. The internal damping / energy dissipation units are arranged in a radial circumferential array, which can capture the multi-directional bending deformation of the structure from all directions. Each sealed flywheel cavity assembly and SMA wire bundle can be disassembled and assembled as an independent module, facilitating the precise replacement of damaged parts after an earthquake and reducing post-earthquake maintenance costs. At the same time, the rigid outer wall of the chamber has a limiting function. When the equipment is subjected to local tension or has a tendency to overturn due to an extremely rare earthquake, it effectively prevents the internal delicate components from falling out, playing a role in anti-overturning and structural preservation. Attached Figure Description

[0028] Figure 1 This is a schematic diagram of the overall structure of the present invention;

[0029] Figure 2 This is a schematic diagram of the structural arrangement of the present invention; Figure 2 In the diagram, (a) is a 45° oblique view, (b) is a top view, and (c) is a front view;

[0030] Figure 3 This is a detailed diagram of a single flywheel assembly of the present invention; to clearly show the internal structure, the flywheel cavity is shown in an open form, but it is actually a sealed cavity;

[0031] Figure 4 This is a schematic diagram showing the installation position of the device according to the present invention.

[0032] The following are the labels in the attached diagram: 1. Trigger flywheel; 2. Horizontal drive cable; 3. Vertical drive cable; 4. SMA cable bundle; 5. Steering pulley; 6. Damping fluid; 7. C-ring. Detailed Implementation

[0033] The principles and features of the present invention are described below with reference to the accompanying drawings. The examples given are only for explaining the present invention and are not intended to limit the scope of the present invention.

[0034] like Figure 1 , Figure 2 as well as Figure 4 As shown, the present invention provides a pull-out inertial capacitive damper, which adopts a fully assembled modular structure. Its external base component is a C-shaped hoop 7, which is composed of at least two semi-annular high-strength shells assembled together. Through reserved bolt holes and fastening bolts, the horizontal rigid hoop is fixed to the bottom flange of the main insulator or the segment connection flange of the support-type electrical equipment (such as surge arresters, instrument transformers, etc.).

[0035] Inside the C-shaped ring 7, along the circumferential direction (e.g.) Figure 1 and Figure 2 Multiple (6 in this embodiment) independent vibration damping / energy dissipation units are evenly arranged in a 60° angle.

[0036] Each of the aforementioned damping / vibration energy dissipation units includes a partially independently sealed flywheel cavity, a pulley flywheel 1, a horizontal drive cable 2, a vertical drive cable 3, an SMA filament bundle 4, a steering pulley 5, and a damping fluid 6.

[0037] The whistle flywheel 1 is placed horizontally and immersed in the damping fluid 6 within the flywheel cavity. The steering pulley 5 is fixed above the flywheel cavity. The outer end of the horizontal drive cable 2 extends out of the C-shaped hoop 7, and its inner end, before passing over the steering pulley 5, is coaxially nested with the SMA filament bundle 4 in a horizontal section. One end of the SMA filament bundle 4 is fixed to the horizontal drive cable 2, and the other end is anchored to the bracket on the side of the steering pulley 5 without contacting the pulley's working groove. After passing over the steering pulley 5, the horizontal drive cable 2 reverses direction to a vertically downward direction and is in a double-strand twisted state. The vertical drive cable 3 is formed by two intertwined fiber cables to create a double-strand twisted structure. The vertical drive cable 3 passes through the central opening of the pull-off flywheel 1 and is anchored at the bottom of the flywheel cavity. When the horizontal drive cable 2 is stretched horizontally by an external force, it simultaneously drives the SMA filament bundle 4 to undergo equal displacement stretching, and pulls the vertical drive cable 3 to untwist through the steering pulley 5, driving the pull-off flywheel 1 to rotate in the flywheel cavity to dissipate energy by shearing the damping fluid. When the external force is unloaded, the vertical drive cable 3 is forced to re-twist and return to its initial state by relying on the superelastic restoring force of the SMA filament bundle 4.

[0038] The SMA filament bundle 4 is in the form of a tubular bundle or a parallel straight filament bundle, covering the periphery of the horizontal drive cable 2, and is always in a state of pure tension without passing through the steering pulley 5, ensuring that its hyperelastic phase change is not affected by bending stress.

[0039] In this embodiment, the horizontal drive cable 2 and the vertical drive cable 3 are made of high-strength flexible fiber materials such as high-strength polyethylene or aramid fiber; the shell of the independently sealed small cavity assembly is made of high-strength corrosion-resistant metal or engineering plastic; the SMA filament bundle 4 is composed of multiple thin-diameter nickel-titanium alloy straight wires to increase the heat dissipation area and improve the phase change efficiency.

[0040] In this embodiment, the entire device adopts a modular structure. Each sealed small cavity assembly containing the whistle flywheel 1 and damping fluid 6 can be disassembled and replaced as an independent unit. The horizontally coaxially arranged SMA filament bundle 4 can also be tensioned, maintained, or replaced individually, which can reduce the maintenance cost and difficulty throughout the entire life cycle.

[0041] like Figure 4 As shown, in this embodiment, the inertial-capacitive damper has a C-shaped ring fixed to the flange of the support-type electrical equipment. Multiple horizontal drive cables 2 extend radially outward from the side wall opening of the C-shaped ring 7, and their outer ends can be grounded or connected to fixed nodes or adjacent equipment at other elevations of the electrical equipment. When the support equipment undergoes horizontal bending deformation in any direction under frequent earthquakes or strong winds, the corresponding damping / vibration unit can be triggered, which can absorb and dissipate earthquake and wind load energy, effectively reducing the impact of horizontal dynamic loads on the upper equipment.

[0042] Working process: Under external loads such as earthquakes or strong winds, the slight relative bending deformation of the support-type electrical equipment will pull the horizontal drive cable 2 outward. This tension is converted into a vertical upward tension by the steering pulley 5, causing the double-strand twisted vertical drive cable 3, which passes through the flywheel cavity, to untwist. Relying on the displacement amplification effect of the pull mechanism, this slight linear translation is converted into high-frequency rotation of the pull flywheel 1. The vibration mechanical energy is efficiently dissipated by the high-speed shearing of the damping fluid 6 in the sealed cavity, actively suppressing the destructive large displacement of the equipment. At the same time, the SMA filament bundle 4, which is coaxially nested with the horizontal drive cable 2, undergoes uniform displacement stretching and stores energy. When the external load enters unloading or reverse loading, the energy is released. During the half-cycle, the SMA filament bundle 4 undergoes a reverse phase transition due to its superior superelasticity, generating a strong horizontal pull force to traction the horizontal drive cable 2 inward. This overcomes the residual inertia of the flywheel 1 and simultaneously pulls back the vertical drive cable 3, causing it to twist again and restoring the initial tension of the transmission cable system. This solves the problems of cable slack and dynamic tension impact during reciprocating vibration. Under extreme and rare disaster conditions, if the input displacement approaches the limit, the rigid wall of the C-shaped hoop 7 and the independent cavity module work together to limit the base and prevent overturning, effectively preventing internal components from coming out and the equipment from disintegrating, thus playing a role in structural preservation. Furthermore, the fully assembled structure allows for convenient maintenance of the damaged unit after vibration by simply opening the C-shaped hoop 7.

[0043] The steering pulley 5 not only provides a stable reversing fulcrum, but its side rigid support also serves as the fixed reaction end of the SMA filament bundle 4, realizing the coordinated distribution of the driving cable tension between reversing and resetting; the driving tension is smoothly converted into a torsional driving force through the pulley reversing, ensuring that the high-strength fiber driving cable does not experience dynamic tension concentration breakage under high-frequency vibration.

[0044] The design method of the pull-out inertial capacitive damper of the present invention includes the following steps:

[0045] S1. Determine vibration reduction / target parameters: Based on the seismic design requirements of support-type electrical equipment and relevant specifications, determine the design displacement of the target structure under the target working conditions. and maximum allowable displacement ;

[0046] S2. Set the inertial mass parameters of the puller: Set the helical lead L of the double-strand twisted structure of the vertical drive cable 3, and the rotational inertia of the puller flywheel 1 about its vertical central axis to J. Calculate the equivalent inertial mass b of the puller flywheel system, as shown in equation (1): (1);

[0047] S3. Determine the equivalent viscous damping parameters: Based on the surface area of ​​the pull-off flywheel 1 and its contact parameters with the damping fluid, determine the viscous damping parameters under rotational conditions. Calculate the equivalent damping coefficient of the damper in the horizontal direction. As shown in equation (2): (2);

[0048] S4. Determine the system's anti-slackening reset parameters: Analyze the extreme inertia and internal mechanical resistance of the reverse rotation of the whistle flywheel 1 to determine the minimum restoring force for system reset. Based on this, the total cross-sectional area of ​​SMA tow 4 was designed. With effective length Based on the superelastic properties of SMA, the tensile force provided during the unloading phase is ensured. Always greater than This forces the vertical drive cable 3 to twist again and return to its initial state, as shown in equation (3): (3);

[0049] S5. Parameter optimization and anti-collision design: Using optimization algorithms, combined with the maximum energy consumption objective function and the constraint conditions such as strain exceeding the limit, the flywheel rotational inertia J, vertical drive cable lead L, and horizontal drive cable stroke are iteratively optimized to ensure that the damper does not experience flywheel bottoming-out collision, cable breakage, or derailment failure under the maximum allowable displacement. The objective function and constraint conditions are shown in equations (4)-(7).

[0050] Total system energy consumption: (4); (5); (6);

[0051] Strain exceeding limits: (7); In the formula: Total energy consumption Energy is consumed by the viscous shear of the damping fluid. Energy consumption for SMA filament bundles For the load loading period, To determine the rotational viscous damping parameters of the flywheel, The stress of a single SMA wire, For time, The maximum strain of the SMA wire. This refers to the maximum permissible displacement of support-type electrical equipment. This represents the initial effective length of the SMA filament bundle. This represents the maximum allowable strain for SMA materials.

[0052] The aforementioned flywheel damping / vibration unit can also achieve a smaller starting trigger force by designing the lead L of the vertical drive cable 3, the friction interface, and the viscosity of the damping fluid. This allows the flywheel 1 to rotate and dissipate energy within the sealed cavity under minor earthquakes or normal wind loads; the initial starting force mechanism is shown in equation (8): (8); In the formula, This is the frictional resistance torque; This is the viscous resistance torque.

[0053] To limit the scope of this invention, any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this invention should be included within the protection scope of this invention.

Claims

1. A type of capacitive inertial damper, characterized in that, include: C-shaped ring (7), and multiple independent damping / energy dissipation units evenly arranged circumferentially inside the C-shaped ring (7); each damping / energy dissipation unit includes a partially independently sealed flywheel cavity and a pull-whistle flywheel (1) and damping fluid (6) disposed in the flywheel cavity, an SMA wire bundle (4) and a steering pulley (5) disposed outside the flywheel cavity, and a horizontal drive cable (2) and a vertical drive cable (3) for driving the pull-whistle flywheel (1); The pull-off flywheel (1) is placed horizontally and immersed in the damping fluid (6) in the flywheel cavity. The steering pulley (5) is fixed above the flywheel cavity. The outer end of the horizontal drive cable (2) extends out of the C-shaped hoop (7). Its inner end is arranged coaxially with the SMA filament bundle (4) before passing around the steering pulley (5). One end of the SMA filament bundle (4) is fixed to the horizontal drive cable (2), and the other end is anchored to the bracket on the side of the steering pulley (5) without contacting the working groove of the pulley. After passing around the steering pulley (5), the horizontal drive cable (2) changes direction to a vertical drive cable (3) that is vertically downward and in a double-strand twisted state. The vertical drive cable (3) is formed by two fiber cables intertwined to form a double-strand twisted structure. The vertical drive cable (3) passes through the central opening of the pull-off flywheel (1) and its bottom end is anchored to the bottom of the flywheel cavity.

2. The pull-out inertial capacitive damper according to claim 1, characterized in that, The C-shaped hoop (7) is assembled from at least two semi-circular shells; after the C-shaped hoop (7) is fixed, the internal shock absorption / vibration energy dissipation units are arranged in a radial circumferential array.

3. A pull-out inertial capacitive damper according to claim 1, characterized in that, The SMA filament bundle (4) is in the form of a tubular bundle or a parallel straight filament bundle, covering the periphery of the horizontal drive cable (2), and is always in a state of pure tension without passing through the steering pulley (5).

4. A pull-out inertial capacitive damper according to claim 1, characterized in that, The horizontal drive cable (2) and the vertical drive cable (3) are made of high-strength flexible fiber material, including high-strength polyethylene or aramid fiber or other high-strength flexible fiber material; the shell of the independently sealed small cavity assembly is made of high-strength corrosion-resistant metal or engineering plastic; the SMA filament bundle (4) is composed of multiple nickel-titanium alloy straight wires.

5. An application of the pull-in inertial capacitive damper according to any one of claims 1-4, characterized in that, The inertial capacitive damper is installed at the flange of the electrical equipment section, and the C-type ring is fixed at the flange of the support-type electrical equipment. Multiple horizontal drive cables (2) extend outward from the side wall opening of the C-type ring (7) in a radial pattern, and their outer ends are grounded or connected to fixed nodes or adjacent equipment at other elevations of the electrical equipment. Under external loads such as earthquakes or strong winds, the slight relative bending deformation of the support-type electrical equipment will pull the horizontal drive cable (2) outward. This tension is converted into a vertical upward tension through the steering pulley (5), causing the double-strand twisted vertical drive cable (3) inserted into the flywheel cavity to untwist. Relying on the displacement amplification effect of the pull mechanism, this slight linear translation is converted into the high-frequency rotation of the pull flywheel (1), which efficiently dissipates the vibration mechanical energy through the high-speed shearing of the damping fluid (6) in the sealed cavity, actively suppressing the destructive large displacement of the equipment. At the same time, the SMA filament bundle (4) arranged coaxially with the horizontal drive cable (2) undergoes uniform displacement stretching and stores energy. When the external load enters the unloading or reverse phase, the energy is released. During the half-cycle of loading, the SMA filament bundle (4) undergoes a reverse phase transition due to its superelasticity, generating a strong horizontal pull force to pull the horizontal drive cable (2) inward, forcibly overcoming the residual inertia of the pull flywheel (1) and simultaneously pulling back the vertical drive cable (3) to twist it again, restoring the initial tension of the transmission cable system, and solving the problems of cable slack and dynamic tension impact in reciprocating vibration; under extreme rare disaster conditions, if the input displacement is close to the limit, the rigid wall of the C-shaped hoop (7) and the independent cavity module work together to play the role of base limiting and anti-overturning, effectively preventing the internal components from coming out and the equipment from disintegrating, and the fully assembled structure makes it possible to conveniently maintain the damaged unit by simply opening the C-shaped hoop (7) after vibration.

6. A design method for the pull-out inertial capacitive damper according to claims 1-4, characterized in that, The method includes the following steps: S1. Determine vibration reduction / target parameters: Based on the seismic design requirements of support-type electrical equipment and relevant specifications, determine the design displacement of the target structure under the target working conditions. and maximum allowable displacement ; S2. Set the inertial mass parameters of the puller: Set the helical lead L of the double-strand twisted structure of the vertical drive cable (3), and the moment of inertia of the puller flywheel (1) about its vertical central axis to J. Calculate the equivalent inertial mass b of the puller flywheel system, as shown in equation (1): (1) ； S3. Determine the equivalent viscous damping parameters: Based on the surface area of ​​the pull-off flywheel (1) and its contact parameters with the damping fluid, determine the viscous damping parameters under rotational conditions. Calculate the equivalent damping coefficient of the damper in the horizontal direction. As shown in equation (2): (2)； S4. Determine the system's anti-slackening reset parameters: Analyze the extreme inertia and internal mechanical resistance of the reverse rotation of the whistle flywheel (1) to determine the minimum restoring force for system reset. Based on this, the total cross-sectional area of ​​the SMA filament bundle (4) was designed. With effective length Based on the superelastic properties of SMA, the tensile force provided during the unloading phase is ensured. Always greater than This forces the vertical drive cable (3) to twist again and return to its initial state, as shown in equation (3): (3)； S5. Parameter optimization and anti-collision design: Using optimization algorithms, combined with the maximum energy consumption objective function and the constraint conditions such as strain exceeding the limit, the flywheel rotational inertia J, vertical drive cable lead L, and horizontal drive cable stroke are iteratively optimized to ensure that the damper does not experience flywheel bottoming-out collision, cable breakage, or derailment failure under the maximum allowable displacement. The objective function and constraint conditions are shown in equations (4)-(7). Total system energy consumption: (4) ； (5) ； (6) ； Strain exceeding limits: (7) ； In the formula: Total energy consumption Energy is consumed by the viscous shear of the damping fluid. Energy consumption for SMA filament bundles For the load loading period, To determine the rotational viscous damping parameters of the flywheel, The stress of a single SMA wire, For time, The maximum strain of the SMA wire. This refers to the maximum permissible displacement of support-type electrical equipment. This represents the initial effective length of the SMA filament bundle. This represents the maximum allowable strain for SMA materials.

7. The design method of the pull-out inertial capacitive damper according to claim 6, characterized in that, The aforementioned flywheel damping / energy dissipation unit can also achieve a smaller starting trigger force by designing the lead L, friction interface, and damping fluid viscosity of the vertical drive cable (3). This allows the flywheel (1) to rotate and dissipate energy within the sealed cavity under minor earthquakes or normal wind loads; the initial starting force mechanism is shown in equation (8): (8) ； In the formula, This is the frictional resistance torque; This is the viscous resistance torque.

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