Electromagnetic damping vibration damper

Abstract

The application relates to an electromagnetic damping vibration damper, which comprises a wire clamp, a sleeve, permanent magnet hammers and springs. One end of the sleeve is fixedly connected with the wire clamp, the inside of the sleeve is provided with a buffer cavity, and the inner wall of the buffer cavity is entirely covered with an eddy current copper plate. The permanent magnet hammers are arranged in the buffer cavity along the axial direction of the sleeve, the permanent magnet hammers can slide along the axial direction of the sleeve, and a working gap is arranged between the permanent magnet hammers and the eddy current copper plate. One end of the spring is fixedly connected with the permanent magnet hammer, and the other end is fixedly connected with the permanent magnet hammer or the end of the buffer cavity. Four permanent magnet hammers and two adjacent springs are matched to form four groups of electromagnetic energy dissipation units, the natural frequencies of the four groups of electromagnetic energy dissipation units are F1, F2, F3 and F4, and the damping ratio of the four groups of electromagnetic energy dissipation units is between 0 and 1. Each group of electromagnetic energy dissipation units corresponds to an independent natural frequency, four discrete resonance frequency points are formed, and the core frequency band 0-150Hz of the overhead transmission line wind vibration is covered.

Description

Technical Field

[0001] This application relates to the field of vibration damping technology for overhead power transmission lines, and in particular to an electromagnetic damping vibration damper. Background Technology

[0002] Currently, overhead transmission lines, as the core carriers of power transmission, are exposed to complex weather environments in the field for extended periods. When stable laminar winds sweep across the conductors laterally, alternating Karman vortex streets are formed on the leeward side of the conductors, causing continuous micro-wind vibrations in the conductors with a frequency range of 0-150Hz. Long-term, repetitive micro-wind vibrations can lead to problems such as conductor fatigue breakage, loosening and wear of hardware connections, and fatigue damage to tower components, seriously threatening the operational safety of transmission lines and significantly shortening their service life.

[0003] Currently, the most widely used vibration damper in transmission lines is the traditional Stockbridge type. Its core structure consists of a steel strand connected to two hammers at both ends. The steel strand drives the hammers to resonate, and the internal friction of the steel strand dissipates the energy of wind-induced vibration. This type of vibration damper can only effectively dissipate energy within a very narrow resonant frequency range. For a wide range of light wind vibrations from 0-150Hz, its vibration suppression effect decreases significantly in the non-resonant frequency band, and it cannot achieve uniform vibration suppression across the entire frequency band. Summary of the Invention

[0004] This application provides an electromagnetic damping vibration damper that can form four discrete resonant frequency points, covering the core frequency band of 0-150Hz for wind-induced vibration of overhead power transmission lines.

[0005] To achieve the above objectives, the main technical solution adopted in this application includes an electromagnetic damping vibration damper, comprising a clamp, a sleeve, permanent magnet hammers, and springs. The clamp is used for fixed connection with the overhead power transmission line. One end of the sleeve is fixedly connected to the clamp. Along the axial direction of the sleeve, a buffer cavity is provided inside the sleeve, and the inner wall of the buffer cavity is fully covered with eddy current copper plates. The permanent magnet hammers are arranged in the buffer cavity along the axial direction of the sleeve. The permanent magnet hammers can slide along the axial direction of the sleeve, and a working gap is provided between the permanent magnet hammers and the eddy current copper plates. One end of the spring is fixedly connected to the permanent magnet hammers, and the other end is fixedly connected to the end of the permanent magnet hammers or the buffer cavity. Four permanent magnet hammers cooperate with two adjacent springs to form four sets of electromagnetic energy dissipation units. The natural frequency of the four sets of electromagnetic energy dissipation units is... F1, F2, F3, and F4 are the damping ratios of the four groups of electromagnetic energy dissipation units. Between 0 and 1.

[0006] The embodiment of this application proposes an electromagnetic damping anti-vibration hammer, in which four sets of electromagnetic energy dissipation units constitute four relatively independent tuned mass damping systems. Each set of electromagnetic energy dissipation units corresponds to an independent natural frequency, forming four discrete resonant frequency points, covering the core frequency band of 0-150Hz for wind vibration of overhead transmission lines.

[0007] Understandably, when the frequency of the conductor's wind vibration is close to any of the frequencies F1, F2, F3, and F4, the electromagnetic energy dissipation unit corresponding to the natural frequency resonates. The relative motion amplitude of the permanent magnet hammer head of this unit is maximized, and the electromagnetic damping energy dissipation efficiency reaches its peak, specifically dissipating the conductor's vibration energy at that frequency. The frequency coverage bandwidth of each electromagnetic energy dissipation unit is interconnected, achieving uniform coverage of the entire 0-150Hz frequency band, avoiding the problem of a significant decrease in the vibration suppression effect of traditional vibration dampers between resonance points.

[0008] Optionally, the design method of the electromagnetic energy dissipation unit includes the following steps: Step 1: Predetermine the natural frequencies of the four sets of electromagnetic energy dissipation units as F1, F2, F3, and F4, and determine the damping ratio of all the electromagnetic energy dissipation units. Between 0 and 1; Step 2: Based on the mass of each permanent magnet hammerhead Given a fixed sum, the masses of each permanent magnet hammer are allocated to form a mass matrix. Combined with the natural frequency in step 1 Derive the stiffness coefficient matrix of the springs in each of the electromagnetic energy dissipation units. ; Step 3: Optimize based on electromagnetic simulation, according to the damping ratio of each electromagnetic energy-consuming unit. Mass matrix of permanent magnet hammer Natural frequency And the stiffness coefficient matrix k of the spring d To calculate the electromagnetic damping coefficient of each electromagnetic energy dissipation unit. ; Step 4: Select N specific points in the 0-150Hz range and assign them to the vibration frequency of the overhead transmission line. Based on the data from steps 1, 2, and 3, the total energy consumption of the four sets of electromagnetic energy-consuming units at each specific point within one motion cycle T is calculated. Next, calculate the vibration frequency of the overhead transmission line. The total energy consumption corresponding to F1, F2, F3 and F4. Total energy consumption Total energy consumption Total energy consumption ; Step 5: Based on the total energy consumption of the four groups of electromagnetic energy-consuming units described in Step 4. The average energy consumption of the four sets of electromagnetic energy-consuming units was calculated in the 0-150Hz range. , If average energy consumption Greater than 1.5w, and , , and If all are greater than 20,000, then based on the current four groups... Value and The electromagnetic damping anti-vibration hammer is manufactured in value; Otherwise, return to step 2.

[0009] Optionally, the dynamic equation of the electromagnetic energy dissipation unit is: ; in, This is the displacement vector matrix of the four sets of electromagnetic energy dissipation units relative to the hammer cylinder; The first derivative is the axial velocity of the four sets of electromagnetic energy-consuming units relative to the hammer cylinder. The second derivative is the axial acceleration of the four sets of electromagnetic energy-consuming units relative to the hammer cylinder; The displacement of the sleeve in the vertical direction. The second derivative is the axial acceleration of the sleeve as it vibrates with the overhead power transmission conductor; in, This is the load vector matrix of four sets of electromagnetic energy dissipation units.

[0010] Optionally, in step 2, the stiffness coefficient matrix of the spring... Satisfy the following formula: ; in, Let be the natural angular frequency of the electromagnetic energy dissipation unit, and satisfy the following formula: 2 .

[0011] Optionally, in step 3, the damping ratio of the electromagnetic energy dissipation unit... .

[0012] Optionally, in step 4, the electromagnetic damping energy dissipation W of the electromagnetic energy dissipation unit c Satisfy the following formula: ; And the axial displacement of the permanent magnet hammer head relative to the sleeve Satisfy the following formula: ; in, It is the single amplitude of the conductor's vibration; Let be the angular frequency of the vibration of the overhead transmission line, and 2 ; t is a time variable, The phase difference between the equivalent harmonic excitation force applied to the electromagnetic energy dissipation unit by the sleeve as it vibrates with the overhead power transmission line and the axial displacement of the permanent magnet hammer relative to the sleeve; in, .

[0013] Optionally, the buffer cavity contains a carrier component made of magnetically conductive metal. Both ends of the carrier component are fixedly connected to the two springs respectively. The permanent magnet hammer head is annular and is sleeved on the outer wall of the carrier component and fixedly connected to the carrier component.

[0014] Optionally, the permanent magnet hammerhead is magnetized from the center of the permanent magnet hammerhead along the radial direction of the permanent magnet hammerhead.

[0015] Optionally, the buffer cavity has a built-in sliding shaft, which is coaxially arranged with the central axis of the buffer cavity. The sliding shaft passes through the carrier component, and the carrier component is slidably connected to the sliding shaft through a bearing. The spring is sleeved outside the sliding shaft.

[0016] Optionally, the working gap is between 0.2mm and 3mm. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the specific embodiments of this application or the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the overall structure of the electromagnetic damping vibration damper in some embodiments of this application; Figure 2 This is a cross-sectional schematic diagram of an electromagnetic damping vibration damper in some embodiments of this application; Figure 3 This is a schematic diagram of the magnetization of the permanent magnet hammer head of the electromagnetic damping anti-vibration hammer in some embodiments of this application.

[0019] [Explanation of Labels in the Attached Image] 1. Overhead power transmission lines; 100. Wire clamp; 200. Sleeve; 210. Buffer chamber; 211. Working clearance; 212. Sliding shaft; 220. Eddy current copper plate; 300. Permanent magnet hammerhead; 310. Carrier component; 400. Spring; 2. Electromagnetic energy-consuming unit; Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0021] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used in the description of this application is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms "comprising" and "having," and any variations thereof, in the description, claims, and accompanying drawings of this application are intended to cover non-exclusive inclusion. The terms "first," "second," etc., in the description, claims, or accompanying drawings of this application are used to distinguish different objects, not to describe a specific order or hierarchy.

[0022] In this application, the reference to "embodiment" means that a specific feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a mutually exclusive, independent, or alternative embodiment. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described in this application can be combined with other embodiments.

[0023] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "attachment" 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 direct connection or an indirect 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 application according to the specific circumstances.

[0024] In this application, the term "and / or" merely describes the relationship between related objects, indicating that three relationships can exist. For example, "electromagnetic damping vibration damper and / or vehicle" can represent: the existence of an electromagnetic damping vibration damper alone, the existence of both an electromagnetic damping vibration damper and a vehicle, or the existence of a vehicle alone. Additionally, in this application, the character " / " generally indicates that the preceding and following related objects have an "or" relationship.

[0025] In this application, "multiple" refers to two or more (including two), similarly, "multiple sets" refers to two or more (including two sets), and "multiple pieces" refers to two or more (including two pieces).

[0026] Reference Figures 1 to 2 This invention provides an electromagnetic damping vibration damper, comprising a clamp 100, a sleeve 200, a permanent magnet hammer head 300, and a spring 400. The clamp 100 is used for fixed connection with an overhead power transmission line 1. One end of the sleeve 200 is fixedly connected to the clamp 100. Along the axial direction of the sleeve 200, a buffer cavity 210 is provided inside the sleeve 200, and the inner wall of the buffer cavity 210 is fully covered with an eddy current copper plate 220. The permanent magnet hammer head 300 is arranged in the buffer cavity 210 along the axial direction of the sleeve 200. In this configuration, the permanent magnet hammer head 300 can slide along the axial direction of the sleeve 200, and a working gap 211 is provided between the permanent magnet hammer head 300 and the eddy current copper plate 220; one end of the spring 400 is fixedly connected to the permanent magnet hammer head 300, and the other end is fixedly connected to the end of the permanent magnet hammer head 300 or the buffer cavity 210; wherein, four permanent magnet hammer heads 300 cooperate with two adjacent springs 400 to form four sets of electromagnetic energy dissipation units 2, and the natural frequency of the four sets of electromagnetic energy dissipation units 2 is... F1, F2, F3, and F4 are the damping ratios of the four groups of electromagnetic energy dissipation units 2. Between 0 and 1.

[0027] In practical use, the electromagnetic damping vibration damper, through the rigid fixation of the clamp 100, ensures that the vibration energy of the overhead transmission line 1 is completely transmitted to the entire vibration damper interior. The sleeve 200 provides a closed protective space and rigid support for the internal electromagnetic energy dissipation structure, and at the same time serves as the transmission carrier of vibration excitation. Its inner wall is fully covered by eddy current copper plates 220, which, together with the moving permanent magnet hammer head 300, constitute an eddy current energy dissipation system. Based on the law of electromagnetic induction, the moving permanent magnet hammer head 300 generates an alternating magnetic field in the copper plate, thereby inducing eddy currents. The Joule heating effect of the eddy currents converts the mechanical energy of the vibration into heat energy for dissipation. At the same time, the reverse magnetic field generated by the eddy currents hinders the movement of the permanent magnet hammer head 300, forming a damping force. Specifically, when the sleeve 200... When the conductor vibrates, the permanent magnet hammer head 300, under the combined action of inertial force and spring force 400, reciprocates along the axial direction of sleeve 200 with a phase difference from the vibration of sleeve 200, causing continuous axial relative motion between the permanent magnet hammer head 300 and eddy current copper plate 220. The constant magnetic field generated by the permanent magnet hammer head 300 forms an alternating magnetic field with its motion, inducing closed eddy currents in the opposing eddy current copper plate 220. The eddy currents generate Joule heat under the resistance of the copper plate, converting the vibration mechanical energy into heat energy and dissipating it into the air. At the same time, the induced magnetic field generated by the eddy current is opposite in direction to the original magnetic field of the permanent magnet hammer head 300, forming an electromagnetic damping force that hinders the relative motion between the two, rapidly attenuating the vibration amplitude of the overhead transmission line 1.

[0028] Specifically, the four sets of electromagnetic energy dissipation units 2 constitute four relatively independent tuned mass damping systems. Each set of electromagnetic energy dissipation units 2 corresponds to an independent natural frequency, forming four discrete resonant frequency points, covering the core frequency band of 0-150Hz of the overhead transmission line 1 under wind vibration.

[0029] Furthermore, the natural frequency is determined by the mass and spring stiffness of the electromagnetic energy dissipation unit 2, while the damping ratio is jointly determined by the electromagnetic damping coefficient, mass, and natural frequency. The damping ratio determines the system's vibration decay rate, resonance peak height, and frequency coverage bandwidth. The range between 0 and 1 ensures that the electromagnetic energy dissipation unit 2 has sufficient bandwidth near the resonance point, while avoiding the problems of insufficient resonance amplitude and reduced energy dissipation efficiency caused by overdamping.

[0030] Understandably, when the frequency of the conductor's wind vibration is close to any of the frequencies of 30Hz, 60Hz, 90Hz, and 120Hz, the electromagnetic energy dissipation unit 2 corresponding to the natural frequency resonates. The relative motion amplitude of the permanent magnet hammer head 300 of this unit is maximized, and the electromagnetic damping energy dissipation efficiency reaches its peak, specifically dissipating the conductor's vibration energy at that frequency. The frequency coverage bandwidth of each electromagnetic energy dissipation unit 2 is interconnected, achieving uniform coverage of the entire frequency band from 0 to 150Hz, avoiding the problem of a significant decrease in the vibration suppression effect of traditional anti-vibration hammers between resonance points.

[0031] Regarding the aforementioned electromagnetic damping vibration damper, the design method for the four sets of electromagnetic energy dissipation units 2 includes the following steps: Step 1: Predetermine the natural frequencies of the four sets of electromagnetic energy dissipation units 2 as F1, F2, F3, and F4, and determine the damping ratio of all the electromagnetic energy dissipation units 2. Between 0 and 1; Step 2: With each permanent magnet hammer head having a mass of 300... Given a fixed sum, the masses of each permanent magnet hammer are allocated to form a mass matrix. Combined with the natural frequency in step 1 Derive the stiffness coefficient matrix of the spring 400 of each electromagnetic energy dissipation unit 2. ; Step 3: Optimize based on electromagnetic simulation, according to the damping ratio of each electromagnetic energy-consuming unit. Mass matrix of permanent magnet hammerhead 300 Natural frequency Stiffness coefficient matrix of spring 400 To calculate the electromagnetic damping coefficient of each electromagnetic energy dissipation unit. ; Step 4: Select N specific points in the 0-150Hz range and assign them to the natural frequency of overhead transmission line 1. Based on the data from steps 1, 2, and 3, the total energy consumption of the four sets of electromagnetic energy-consuming units 2 at each specific point within one motion cycle T is calculated. Next, calculate the natural frequency of overhead transmission line 1. The total energy consumption corresponding to F1, F2, F3 and F4. Total energy consumption Total energy consumption Total energy consumption ; Step 5: Based on the total energy consumption of the four groups of electromagnetic energy-consuming units 2 described in Step 4. The average energy consumption of the four sets of electromagnetic energy-consuming units 2 in the 0-150Hz range was calculated. , If average energy consumption Greater than 1.5w, and , , and If all are greater than 20,000, then based on the current four groups... Value and The electromagnetic damping anti-vibration hammer is manufactured in value; Otherwise, return to step 2.

[0032] In this embodiment, the scheme is illustrated using F1=30Hz, F2=60Hz, F3=90Hz, and F4=120Hz as examples. Correspondingly, the total energy consumption is as follows: , , and .

[0033] In step 1, the typical frequency range of aerobatic vibration of overhead transmission line 1 is 0-150Hz, with 30Hz, 60Hz, 90Hz, and 120Hz being the main energy concentration frequencies within this band. By pre-locking these four natural frequencies, the frequency band with the highest proportion of wind vibration energy can be effectively suppressed, effectively avoiding the defects of traditional vibration dampers' "peak-type" vibration suppression; damping ratio The underdamped range, set between 0 and 1, is to balance the resonant peak value and the frequency coverage bandwidth, avoiding overdamping. ≥1) This prevents the system from resonating and causes a sharp drop in energy consumption efficiency. It also avoids the problem of a narrow frequency coverage bandwidth caused by an excessively small damping ratio, which can only effectively suppress vibration in a very narrow frequency band. In step 2, without changing the total weight of the vibration damper (generally between 6-8 kg), a corresponding 400 stiffness matrix of springs is matched. The stiffness coefficient matrix of the spring 400 Satisfy the following formula: ; in, Let be the natural angular frequency of the electromagnetic energy dissipation unit 2, and satisfy the following formula: 2 .

[0034] The natural frequency determined in step 1 Through Formula 2 Convert to natural angular frequency Then The mass matrix of the permanent magnet hammer 300 assigned in step 2 Substitute into the formula The required spring stiffness coefficient for the corresponding electromagnetic energy dissipation unit 2 is calculated, and then the stiffness coefficient matrix of spring 400 is completed. The construction of the formula can realize the design of the natural frequency. After determining the target natural frequency and mass distribution, the spring stiffness of the required spring 400 can be directly calculated to ensure that the natural frequency of the four electromagnetic energy dissipation units 2 is completely matched with the target value. In step 3, the electromagnetic damping coefficient matrix Mass matrix of permanent magnet hammerhead 300 Natural angular frequency With damping ratio The core formula is satisfied between them. This formula establishes a mapping relationship between electromagnetic parameters and dynamic parameters. It should be mentioned that, as a conventional technique in this field, electromagnetic simulation software can be used to simulate the electromagnetic coupling process between the permanent magnet hammer 300 and the eddy current copper plate 220, optimizing parameters such as the permanent magnet size, working gap 211, and copper plate thickness to obtain the desired result. The electromagnetic energy dissipation unit 2 involves a specific solution; it is important to emphasize that this formula allows for the preset and adjustment of the damping ratio, solving problems such as the inability to accurately design damping characteristics and the significant influence of environment and wear in traditional vibration damping hammers; by adjusting the electromagnetic damping coefficient matrix... The damping ratio can be flexibly adjusted. By balancing resonance energy dissipation efficiency and frequency coverage bandwidth, the electromagnetic damping vibration damper of this invention can be adapted to different wind vibration environment requirements (0-150Hz). The core performance indicator of a vibration damper is its vibration energy dissipation capacity. In step 4, this refers to the total energy dissipation within one motion cycle. It is a quantitative indicator for measuring the vibration suppression effect. Frequency sweep calculations are performed at N frequency points within the 0-150Hz full-band to comprehensively verify the energy dissipation performance of the vibration damper across the entire frequency band. Energy dissipation calculations at the core frequency points of 30Hz, 60Hz, 90Hz, and 120Hz can specifically verify the suppression effect of the vibration damper on the main wind vibration frequencies. Specifically, in step 4, the electromagnetic damping energy dissipation of the electromagnetic energy dissipation unit 2... Satisfy the following formula: ; in The speed of movement of the permanent magnet hammer head 300 relative to the sleeve 200; Furthermore, the axial displacement of the permanent magnet hammer head 300 relative to the sleeve 200 Satisfy the following formula: ; in, It is the single amplitude of the conductor's vibration; Let be the angular frequency of the vibration of overhead transmission line 1, and 2 ; t For time variables, The phase difference between the equivalent harmonic excitation force applied to the electromagnetic energy dissipation unit 2 by the sleeve 200 as it vibrates with the overhead power transmission line 1 and the axial displacement of the permanent magnet hammer head 300 relative to the sleeve 200; in, .

[0035] Based on the above calculation formula, as a specific implementation method, in the entire step 4, 151 frequency points (0, 1, 2, 3, 4...150) are selected at equal intervals within the full frequency band of aerodynamic vibration from 0 to 150 Hz as the vibration frequency of the overhead transmission line 1. Assigning values, and assigning each The value is converted to the vibration angular frequency of the overhead transmission line 1. Combined with the results obtained in steps 1-3 , , and Specific parameters were used to calculate the axial displacement matrix of the permanent magnet hammer head 300 relative to the sleeve 200 at each frequency point. With speed of movement Then, the total energy consumption within one cycle corresponding to each frequency point is calculated using the above formula. Furthermore, extract separately. The calculation results at 30Hz, 60Hz, 90Hz, and 120Hz are used to obtain the total power consumption at the corresponding core frequency points. , , and .

[0036] Following the calculations in step 4 above, step 5 is performed, setting an average energy consumption threshold of 1.5W and a core frequency point energy consumption threshold of 2W. This is to ensure that the electromagnetic damping vibration damper in this embodiment has both full-band foundation vibration suppression capability and effective protection against wind-induced vibration energy in the core frequency band. It has a highly efficient suppression effect; if the threshold is not met, return to step 2 to iterate again, ensuring that the final solution meets the performance requirements.

[0037] By performing full-band frequency sweep calculations, the vibration suppression performance of the vibration damping hammer can be comprehensively verified across the entire light wind vibration frequency band, avoiding the problem of insufficient energy dissipation in local frequency bands. Individual energy dissipation calculations at the core frequency point can verify the electromagnetic damping vibration damping hammer's ability to dissipate the main wind vibration energy in this embodiment. This ensures that the final electromagnetic damping vibration damping hammer avoids both the problem of poor broadband vibration suppression caused by insufficient average energy dissipation across the entire frequency band, and the problem of ineffective dissipation of the main wind vibration energy due to insufficient energy dissipation at the core frequency point.

[0038] In the specific embodiment described above, during the numerical verification of the electromagnetic energy dissipation unit 2, the dynamic equation of the electromagnetic energy dissipation unit 2 is as follows: ; in, This is the displacement vector matrix of the four sets of electromagnetic energy dissipation units relative to the hammer cylinder; The first derivative is the axial velocity of the four sets of electromagnetic energy-consuming units relative to the hammer cylinder. The second derivative is the axial acceleration of the four sets of electromagnetic energy-consuming units relative to the hammer cylinder; This refers to the vertical displacement of the sleeve 200. The second derivative is the axial acceleration of the sleeve 200 as it vibrates with the overhead power transmission conductor ground wire; in, This is the load vector matrix of four sets of electromagnetic energy dissipation units.

[0039] When the sleeve 200 generates an axial acceleration y'' along with the conductor, it produces an equivalent harmonic excitation load matrix on the permanent magnet hammer head 300. Under this excitation load, the permanent magnet hammer 300 generates an axial displacement matrix. During its movement, it is simultaneously subjected to the elastic force of spring 400. Electromagnetic damping force With its own inertial force The four forces form a force balance, satisfying the above dynamic equations. By solving these equations, the displacement, velocity, and acceleration responses of the permanent magnet hammer 300 under different excitation frequencies can be obtained. This allows for the calculation of the system's energy consumption performance and vibration suppression effect, effectively verifying the vibration suppression effect of the design scheme, avoiding the cost and time of physical testing, and providing a theoretical basis for the precise optimization of parameters.

[0040] As a further supplement to the above embodiments, wherein: Within a unit time T, the displacement vector matrix of the four hammers relative to the sleeve 200 is: ; Mass matrix of permanent magnet hammerhead 300 satisfy: , The mass of the first permanent magnet hammer head is 300. For the mass of the second permanent magnet hammer head 300, For the mass of the third permanent magnet hammer head 300, The mass of the fourth permanent magnet hammer is 300. Stiffness coefficient matrix of spring 400 satisfy: , The stiffness coefficient of the first spring is 400. The stiffness coefficient of the second spring is 400. The stiffness coefficient of the third spring is 400. The stiffness coefficient of the fourth spring is 400. The stiffness coefficient of the fifth spring is 400. Electromagnetic damping coefficient matrix satisfy: ; The electromagnetic damping coefficient of the first electromagnetic energy dissipation unit 2 is given. The electromagnetic damping coefficient of the second electromagnetic energy dissipation unit 2. The electromagnetic damping coefficient of the third electromagnetic energy dissipation unit 2. The electromagnetic damping coefficient of the fourth electromagnetic energy dissipation unit 2; Load vector matrix of electromagnetic energy dissipation unit satisfy: ; In some embodiments, refer to Figure 2 The buffer cavity 210 contains a carrier component 310. Both ends of the carrier component 310 are fixedly connected to two springs 400 respectively. The permanent magnet hammer head 300 is annular and is sleeved on the outer wall of the carrier component 310 and fixedly connected to the carrier component 310. The carrier component 310 provides a base for mounting and positioning the permanent magnet hammer head 300, and simultaneously realizes the force transmission between the permanent magnet hammer head 300 and the spring 400. The annular permanent magnet hammer head 300 can form a uniform radial magnetic field, forming a 360° full-circumferential electromagnetic coupling with the circumferentially covered eddy current copper plate 220, which greatly improves the magnetic field utilization rate and damping force output efficiency. During assembly, the annular permanent magnet hammer head 300 is coaxially sleeved on the outer wall of the carrier component 310 and fixedly connected to the carrier component 310 by interference fit, bonding, fastener locking, etc., to form an integral moving component. The two ends of the carrier component 310 are fixedly connected to the adjacent springs 400 respectively, so that the elastic force of the springs 400 can be completely transmitted to the permanent magnet hammer head 300 through the carrier component 310, driving the permanent magnet hammer head 300 to perform axial reciprocating motion with the extension and contraction of the springs 400.

[0041] In some embodiments, referring to FIG3, the permanent magnet hammer head 300 is magnetized from the center of the permanent magnet hammer head 300 along the radial direction of the permanent magnet hammer head 300. The permanent magnet hammer head 300 adopts an integral radial magnetic ring structure. Through the radial magnetization process, the inner ring of the magnetic ring is a magnetic pole, and the outer ring is an opposite magnetic pole. The magnetic field lines are evenly dispersed from the inner ring to the outer ring in the radial direction, forming a radial magnetic field that is evenly distributed throughout the circumference. When the permanent magnet hammer head 300 moves axially, the radial magnetic field moves axially with the permanent magnet hammer head 300, generating eddy currents perpendicular to the magnetic field lines and the direction of movement in the circumferential eddy current copper plate 220, forming efficient electromagnetic damping energy dissipation. The radial magnetization method makes the magnetic field distribution of the permanent magnet hammer head 300 more uniform, greatly improves the magnetic field utilization rate, and can generate a larger and more stable electromagnetic damping force, thereby improving the energy dissipation efficiency of the vibration damper.

[0042] In some embodiments, refer to Figure 2The buffer cavity 210 has a built-in sliding shaft 212, which is coaxially arranged with the central axis of the buffer cavity 210. The sliding shaft 212 passes through the carrier component 310, and the carrier component 310 is slidably connected to the sliding shaft 212 via a bearing. The spring 400 is sleeved outside the sliding shaft 212. The guiding structure of the sliding shaft 212 and the linear bearing ensures the coaxiality and stability of the axial movement of the permanent magnet hammer head 300, keeps the working gap 211 uniform and stable throughout the entire stroke, ensures stable damping force output, and avoids performance fluctuations caused by movement deviation.

[0043] In some embodiments, the working gap 211 is between 0.2 mm and 3 mm.

[0044] It should also be noted that the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0045] The various embodiments in this specification are described in a progressive manner. Similar or identical parts between embodiments can be referred to interchangeably. Each embodiment focuses on describing the differences from other embodiments. In particular, the system embodiments are basically similar to the method embodiments, so the description is relatively simple; relevant parts can be referred to the descriptions in the method embodiments.

[0046] The above description is merely an embodiment of this application and is not intended to limit the scope of this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of the claims of this application.

[0047] Although embodiments of this application have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of this application, and such modifications and variations all fall within the scope defined by the appended claims.

Claims

1. An electromagnetic damping vibration damper, characterized in that, include: Wire clamps are used for fixed connection with overhead power transmission lines; A sleeve, one end of which is fixedly connected to the wire clamp, and a buffer cavity is provided inside the sleeve along the axial direction of the sleeve, the inner wall of which is fully covered with an eddy current copper plate; A permanent magnet hammer head is arranged in the buffer cavity along the axial direction of the sleeve. The permanent magnet hammer head can slide along the axial direction of the sleeve. A working gap is provided between the permanent magnet hammer head and the eddy current copper plate. A spring, one end of which is fixedly connected to the permanent magnet hammer head, and the other end of which is fixedly connected to the end of the permanent magnet hammer head or the buffer cavity; The four permanent magnet hammers, in conjunction with their adjacent two springs, form four sets of electromagnetic energy-dissipating units, the natural frequency of which... F1, F2, F3, and F4 are the damping ratios of the four groups of electromagnetic energy dissipation units. Between 0 and 1.

2. The electromagnetic damping vibration damper according to claim 1, characterized in that, The design method for the electromagnetic energy dissipation unit includes the following steps: Step 1: Predetermine the natural frequencies of the four sets of electromagnetic energy dissipation units as F1, F2, F3, and F4, and determine the damping ratio of all the electromagnetic energy dissipation units. Between 0 and 1; Step 2: Based on the mass of each permanent magnet hammerhead Given a fixed sum, the masses of each permanent magnet hammer are allocated to form a mass matrix. Combined with the natural frequency in step 1 Derive the stiffness coefficient matrix of the springs in each of the electromagnetic energy dissipation units. ; Step 3: Optimize based on electromagnetic simulation, according to the damping ratio of each electromagnetic energy-consuming unit. Mass matrix of permanent magnet hammer Natural frequency And the stiffness coefficient matrix k of the spring d To calculate the electromagnetic damping coefficient of each electromagnetic energy dissipation unit. ; Step 4: Select N specific points in the 0-150Hz range and assign them to the vibration frequency of the overhead transmission line. Based on the data from steps 1, 2, and 3, the total energy consumption of the four sets of electromagnetic energy-consuming units at each specific point within one motion cycle T is calculated. Next, calculate the vibration frequency of the overhead transmission line. The total energy consumption corresponding to F1, F2, F3 and F4. Total energy consumption Total energy consumption Total energy consumption ; Step 5: Based on the total energy consumption of the four groups of electromagnetic energy-consuming units described in Step 4. The average energy consumption of the four sets of electromagnetic energy-consuming units was calculated in the 0-150Hz range. , If average energy consumption Greater than 1.5w, and , , and If all are greater than 20,000, then based on the current four groups... Value and The electromagnetic damping anti-vibration hammer is manufactured in value; Otherwise, return to step 2.

3. The electromagnetic damping vibration damper according to claim 2, characterized in that, The dynamic equation of the electromagnetic energy dissipation unit is: ； in, This is the displacement vector matrix of the four sets of electromagnetic energy dissipation units relative to the hammer cylinder; The first derivative is the axial velocity of the four sets of electromagnetic energy-consuming units relative to the hammer cylinder. The second derivative is the axial acceleration of the four sets of electromagnetic energy-consuming units relative to the hammer cylinder; The displacement of the sleeve in the vertical direction. The second derivative is the axial acceleration of the sleeve as it vibrates with the overhead power transmission conductor; in, This is the load vector matrix of four sets of electromagnetic energy dissipation units.

4. The electromagnetic damping vibration damper according to claim 3, characterized in that, In step 2, the stiffness coefficient matrix of the spring Satisfy the following formula: ； in, Let be the natural angular frequency of the electromagnetic energy dissipation unit, and satisfy the following formula: 2 。 5. The electromagnetic damping vibration damper according to claim 4, characterized in that, In step 3, the damping ratio of the electromagnetic energy dissipation unit 。 6. The electromagnetic damping vibration damper according to claim 5, characterized in that, In step 4, the electromagnetic damping energy dissipation W of the electromagnetic energy dissipation unit c Satisfy the following formula: ; And the axial displacement of the permanent magnet hammer head relative to the sleeve Satisfy the following formula: ； in, It is the single amplitude of the conductor's vibration; Let be the angular frequency of the vibration of the overhead transmission line, and 2 ; t is a time variable, The phase difference between the equivalent harmonic excitation force applied to the electromagnetic energy dissipation unit by the sleeve as it vibrates with the overhead power transmission line and the axial displacement of the permanent magnet hammer relative to the sleeve; in, .

7. The electromagnetic damping vibration damper according to any one of claims 1 to 6, characterized in that, The buffer cavity contains a carrier component made of magnetically conductive metal. Both ends of the carrier component are fixedly connected to the two springs respectively. The permanent magnet hammer head is ring-shaped and is sleeved on the outer wall of the carrier component and fixedly connected to the carrier component.

8. The electromagnetic damping vibration damper according to claim 7, characterized in that, The permanent magnet hammerhead is magnetized from its center along the radial direction.

9. The electromagnetic damping vibration damper according to claim 7, characterized in that, The buffer cavity has a built-in sliding shaft, which is coaxially arranged with the central axis of the buffer cavity. The sliding shaft passes through the carrier component, and the carrier component is slidably connected to the sliding shaft through a bearing. The spring is sleeved outside the sliding shaft.

10. The electromagnetic damping vibration damper according to claim 1, characterized in that, The working gap is between 0.2mm and 3mm.

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