A tuned inertial mass eddy current damper and its design method

Abstract

This invention relates to the field of building vibration reduction technology, and provides a tuned inertial mass eddy current damper and its design method. The tuned inertial mass eddy current damper includes a movable block, an inertial flywheel, and a motion conversion mechanism. The movable block is connected to the controlled structure via an elastic element, and the inertial flywheel is rotatably connected to the controlled structure. One end of the motion conversion mechanism is connected to the inertial flywheel, and the other end is connected to the movable block. The motion conversion mechanism can convert the linear motion of the movable block into the rotational motion of the inertial flywheel. A magnet is fixed on the inertial flywheel, and a conductor is fixed on the controlled structure. This invention solves the problem that existing structural vibration control uses viscous dampers or TMDs, but viscous dampers are expensive and prone to performance degradation over long-term use, leading to high maintenance costs; while the vibration reduction effect of TMDs corresponds to the mass of the mass block, which can easily lead to an excessively large mass block.

Description

Technical Field

[0001] This invention relates to the field of building vibration reduction technology, and in particular to a tuned inertial mass eddy current damper and its design method. Background Technology

[0002] Building structures vibrate under external loads. For example, long-span cable-stayed bridges and suspension bridges experience significant longitudinal vibrations under external loads such as vehicle loads, wind loads, and earthquakes. Therefore, vibration control design is crucial for building structures. Currently, vibration control often directly employs viscous dampers or TMDs (Tuned Mass Dampers) for control.

[0003] Viscous dampers generally consist of a housing and a piston. The housing is fixed to the controlled structure, such as a house or bridge, and is filled with damping fluid. The piston is slidably disposed in the housing. When the housing vibrates with the controlled structure, the piston reciprocates inside the housing, thereby converting the mechanical energy of the controlled structure's vibration into the kinetic energy of the piston. This energy is then dissipated as heat through intense friction between the damping fluid and the piston, thus reducing the vibration of the main structure.

[0004] However, viscous dampers are expensive, and because they use hydraulic oil, their damping performance will significantly decline after 3-5 years due to various problems such as hydraulic oil aging and contamination, and seal failure, resulting in high maintenance costs in the later stages.

[0005] A TMD typically consists of a mass block, a spring system, and damping elements. The mass block is slidably connected to the controlled structure, while the spring system and damping elements are connected between the mass block and the controlled structure. When the controlled structure vibrates, the mass block reciprocates in the corresponding direction, thereby repeatedly compressing the spring system and damping elements, thus absorbing and dissipating the mechanical energy of the vibration of the controlled structure.

[0006] Traditional TMD (Transient Damping Device) systems for longitudinal vibration control suffer from the problem of requiring excessively large mass blocks. The damping effect of a TMD is directly proportional to the mass of the mass block; therefore, when applied to large controlled structures, the mass block often becomes too large. This leads to both high TMD costs and excessive loads on the controlled structure. Furthermore, TMDs often use hydraulic dampers containing damping fluid, which also suffer from high costs, performance degradation over long-term use, and high maintenance costs. Summary of the Invention

[0007] The purpose of this invention is to solve the problems arising from the use of viscous dampers or tuned mass dampers (TMDs) in existing structural vibration control, including the high cost of viscous dampers and their tendency to degrade in performance over long-term use, resulting in high maintenance costs; and the problem that the vibration reduction effect of TMDs corresponds to the mass of the mass block, which can easily lead to the problem of excessive mass of the mass block. The invention provides a tuned inertial mass eddy current damper and its design method.

[0008] To achieve the above objectives, the technical solution adopted by the present invention is as follows:

[0009] A tuned inertial mass eddy current damper includes a movable block, an inertial flywheel, and a motion conversion mechanism;

[0010] The movable block is connected to the controlled structure via an elastic element, and the extension or shortening of the elastic element can drive the movable block to move linearly.

[0011] The inertial flywheel is rotatably connected to the controlled structure; one end of the motion conversion mechanism is connected to the inertial flywheel, and the other end is connected to the movable block. The motion conversion mechanism can convert the linear motion of the movable block into the rotational motion of the inertial flywheel.

[0012] A magnet is fixed on the inertial flywheel, and a conductor is fixed on the controlled structure. The rotation of the inertial flywheel enables the conductor to cut the magnetic field lines of the magnet.

[0013] The specific arrangement of the elastic elements depends on the actual vibration reduction requirements. For example, if it is necessary to control the vibration of the controlled structure in the horizontal direction, the extension and contraction direction of the elastic elements can be made in the horizontal direction; if it is necessary to control the vibration of the controlled structure in the vertical direction, the extension and contraction direction of the elastic elements can be made in the vertical direction. The elastic elements include, but are not limited to, rubber blocks, gas disc springs, disc springs, and wave springs.

[0014] Motion conversion mechanisms can employ various mechanisms that can convert linear motion into rotary motion, such as crank-slider mechanisms, rolling screw mechanisms, and cable-pulley mechanisms.

[0015] Referring to existing technologies, inertial flywheels can use either a homogeneous disk structure or a heterogeneous disk structure that concentrates mass at the edge of the inertial flywheel. The conductor material includes, but is not limited to, iron, aluminum, and tungsten, as long as it can interact with the magnet and generate eddy currents during rotation, thus functioning as an eddy current damper.

[0016] The working principle of the tuned inertial mass eddy current damper in this scheme is as follows: when the controlled structure vibrates in a certain direction, the elastic element will repeatedly extend and contract in the corresponding direction, thereby driving the movable block to perform linear reciprocating motion. This linear reciprocating motion will be converted into the reciprocating rotational motion of the inertial flywheel through the motion conversion mechanism, thereby converting the mechanical energy of the controlled structure vibration into the angular momentum of the inertial flywheel rotation. Since the inertial flywheel generates inertial mass during rotation, compared with the mass block in the existing TMD, this scheme has a larger equivalent mass when the mass of the inertial flywheel and the mass block are the same, thus having a better vibration reduction effect. Conversely, if the required vibration reduction effect is the same, the mass of the inertial flywheel in this scheme can be made smaller.

[0017] Meanwhile, during its reciprocating rotation, the inertial flywheel drives the magnet to move relative to the conductor, enabling the conductor to cut the magnetic field lines generated by the magnet. This generates eddy currents within the conductor and creates resistance to the magnet. This resistance is transmitted to the inertial flywheel. On one hand, this resistance increases the damping force of this solution, thereby improving its vibration reduction effect. On the other hand, it gradually slows down the rotational speed of the inertial flywheel, converting the angular momentum of the inertial flywheel into its internal energy, thus dissipating the mechanical energy of the vibration. Compared to existing viscous dampers, this solution does not require the conductor to be in direct contact with the magnet during operation, nor does it require a working fluid similar to damping fluid. Therefore, it has the advantages of low mechanical friction, long service life, and low maintenance costs.

[0018] In summary, the tuned inertial mass eddy current damper of this scheme generates inertial mass through an inertial flywheel and combines a magnet and the inertial flywheel to form an eddy current damper. Compared with existing TMDs, this scheme has a larger equivalent mass and damping force when the masses of the inertial flywheel and the mass block are the same, thus achieving better vibration reduction effect. Conversely, when the vibration reduction requirements are the same, the mass of the inertial flywheel in this scheme can be made smaller, thereby reducing material consumption and manufacturing costs. At the same time, compared with existing viscous dampers, this scheme has the advantages of low mechanical friction, long service life, and low maintenance costs.

[0019] As a preferred embodiment of the present invention, the motion conversion mechanism includes a gear and a rack; the gear is coaxially and fixedly connected to the inertial flywheel, one end of the rack is fixed to the movable block, and the other end meshes with the gear.

[0020] This solution uses a rack and pinion mechanism as the motion conversion mechanism. By adjusting the size of the gear, the ratio of the number of gear rotations to the rack travel length can be adjusted. For example, by reducing the size of the gear, the gear can rotate more times with the same rack travel length, thereby amplifying the vibration of the controlled structure. This ensures that the gear and flywheel have sufficient speed even when the amplitude of the controlled structure is small, thus ensuring the vibration reduction effect of this solution under such conditions. At the same time, compared with other mechanisms, such as linkage mechanisms, the rack and pinion mechanism has no dead points, and therefore can more stably and reliably convert between linear and rotary motion.

[0021] As a preferred embodiment of the present invention, a roller assembly is provided between the movable block and the controlled structure.

[0022] The roller assembly can be fixed to the movable block, facing the controlled structure, or fixed to the controlled structure, facing the movable block.

[0023] This design incorporates a roller assembly between the moving block and the controlled structure, which prevents direct sliding friction between the moving block and the controlled structure. This reduces wear caused by relative motion between the moving block and the controlled structure, thereby extending the service life of the tuned inertial mass eddy current damper and the controlled structure.

[0024] As a preferred embodiment of the present invention, the side of the conductor facing away from the inertial flywheel is further provided with a back iron.

[0025] The back iron can adopt existing mature structures and be made of materials with good magnetic permeability, such as pure iron.

[0026] This design places a back iron on the side of the conductor facing away from the inertial flywheel, which prevents the magnetic field lines of the magnets on the inertial flywheel from spreading into the air, thereby ensuring that more magnetic field lines can cut the conductor.

[0027] As a preferred embodiment of the present invention, the number of magnets is greater than one; the magnets are distributed at intervals along the circumference of the inertial flywheel.

[0028] This design arranges multiple magnets at intervals along the circumference of the inertial flywheel. When the flywheel rotates, eddy currents can be generated at various points along the circumference of the conductor, thereby generating resistance at various points of the flywheel and improving the efficiency of this design in consuming the rotational angular momentum of the flywheel, thus improving the vibration reduction efficiency of this design.

[0029] As a preferred embodiment of the present invention, the magnet is a permanent magnet.

[0030] This solution uses permanent magnets as the magnets, which eliminates the need for excitation equipment and corresponding power supply equipment compared to solutions using electromagnets. This reduces the manufacturing and maintenance costs of this solution, while also reducing potential failure points and improving the reliability of its operation.

[0031] In a preferred embodiment of the present invention, the conductor is a copper component.

[0032] The conductor material used in this design is copper, which has good electrical and thermal conductivity. On the one hand, this enables the conductor to more efficiently sense and conduct eddy currents, thereby improving the efficiency of dissipating the rotational angular momentum of the flywheel. On the other hand, it also helps the conductor to quickly transfer heat to the surrounding environment.

[0033] A design method for a tuned inertial mass eddy current damper, applicable to a tuned inertial mass eddy current damper of this invention, includes the following steps:

[0034] Determine the mass ratio μ of the tuned inertial mass eddy current damper based on vibration reduction requirements; calculate the optimal frequency ratio v based on μ. opt According to v opt Calculate the frequency ω of the tuned inertial mass eddy current damper. T ;

[0035] The moment of inertia I of the inertial flywheel is determined by μ; and the moment of inertia I of the inertial flywheel is determined by ω. T Determine the stiffness K of the elastic element T .

[0036] It is important to note the determination of the moment of inertia I and the stiffness K of the elastic element. T The order in which these are determined is not fixed. For example, I can be determined first based on μ, and then based on v. opt Calculate the frequency ω of the tuned inertial mass eddy current damper. T Or first complete the stiffness K. T The calculation is then performed to determine I.

[0037] The relationship between the mass ratio and the optimal frequency ratio can be found in existing TMD optimal design formulas:

[0038]

[0039]

[0040] In the formula, υ opt For the optimal frequency ratio, ζ opt The optimal damping ratio is μ, which is the mass ratio of the tuned inertial mass eddy current damper. The specific value of the mass ratio depends on the actual vibration reduction requirements. The larger the mass ratio, the better the vibration reduction effect. However, it should not be too large, otherwise it will increase the manufacturing cost and manufacturing difficulty of this scheme, and also generate excessive load on the controlled structure.

[0041] The specific method for determining the moment of inertia I of the inertial flywheel based on μ depends on the actual situation. For example, an initial value of I may be determined first, and then the actual mass ratio of the system to μ may be determined through simulation calculations or experimental analysis.r Comparison of μ and μ r If μ and μ r If the difference between μ and μ satisfies the design requirements, then the value of I can be determined as the design value; if μ and μ r If the difference does not meet the design requirements, then the I value and μ and μ can be repeatedly selected and verified. r The difference is calculated until the design requirements are met; according to ω T Determine the stiffness K of the elastic element T Similarly, K can also be selected through preliminary selection. T The value is then calculated or measured to determine the actual frequency ratio, and compared with v. opt Compare the results until they meet the design requirements.

[0042] The specific formula for the moment of inertia I of an inertial flywheel depends on the shape of the flywheel. For example, if the inertial flywheel is a homogeneous disk, then I can be expressed as:

[0043]

[0044] In the formula, I is the moment of inertia of the inertial flywheel; M T M is the mass of the inertial flywheel; T The diameter of the inertial flywheel.

[0045] The tuning inertial mass eddy current damper design method of this scheme is used in the tuning inertial mass eddy current damper of this invention. The rotational inertia of the inertial flywheel and the stiffness of the elastic element are selected according to the mass ratio and the optimal frequency ratio, respectively. This allows the actual damping and frequency of this scheme to be as close as possible to the optimal design value, thereby maximizing the vibration reduction effect.

[0046] In a preferred embodiment of the present invention, when the tuned inertial mass eddy current damper further comprises a gear and a rack, the moment of inertia I of the inertial flywheel and the radius r of the gear are determined according to the following formula:

[0047]

[0048] In the formula, μ is the mass ratio of the tuned inertial mass eddy current damper; m s The mass of the controlled structure; m T Let I be the mass of the rack; I be the moment of inertia of the flywheel; and r be the radius of the gear.

[0049] This scheme provides the specific basis for determining the rotational inertia of the inertial flywheel and the radius of the gears when the tuned inertial mass eddy current damper includes gears and racks.

[0050] In a preferred embodiment of the present invention, when the tuned inertial mass eddy current damper further includes gears and racks, the stiffness K of the elastic element is determined according to the following formula. T :

[0051]

[0052] In the formula, K T The stiffness of the elastic element; m T Let I be the mass of the rack; I be the moment of inertia of the flywheel; r be the radius of the gear; ω be the radius of the gear. s v is the frequency of the controlled structure; opt This is the optimal frequency ratio.

[0053] This scheme provides the specific basis for determining the stiffness value of the elastic element when the tuned inertial mass eddy current damper includes gears and racks.

[0054] In summary, due to the adoption of the above technical solution, the beneficial effects of the present invention are:

[0055] 1. The tuned inertial mass eddy current damper in this solution generates inertial mass through an inertial flywheel and combines a magnet and the inertial flywheel to form an eddy current damper. Compared to existing TMDs, with the same mass of the inertial flywheel and the mass block, this solution has a larger equivalent mass and damping force, resulting in better vibration reduction. Conversely, with the same vibration reduction requirements, the mass of the inertial flywheel in this solution can be made smaller, thereby reducing material consumption and manufacturing costs. Furthermore, compared to existing viscous dampers, this solution has advantages such as lower mechanical friction, longer service life, and lower maintenance costs.

[0056] 2. The tuning inertial mass eddy current damper design method of this scheme is used in the tuning inertial mass eddy current damper of this invention. The rotational inertia of the inertial flywheel and the stiffness of the elastic element are selected according to the mass ratio and the optimal frequency ratio, respectively. This enables the actual damping and frequency of this scheme to be as close as possible to the optimal design value, thereby maximizing the vibration reduction effect. Attached Figure Description

[0057] Figure 1 This is a side view schematic diagram of a tuned inertial mass eddy current damper installed in a controlled structure according to the present invention. Figure 1 ;

[0058] Figure 2 This is a partial side view of the structure at the inertial flywheel. Figure 1 ;

[0059] Figure 3 yes Figure 1 Schematic diagram of partial cross-sectional structure of section AA Figure 1 ;

[0060] Figure 4 yes Figure 1 A magnified schematic diagram of the local structure at point I;

[0061] Figure 5 This is a side view schematic diagram of a tuned inertial mass eddy current damper installed in a controlled structure according to the present invention. Figure 2 ;

[0062] Figure 6 This is a partial side view of the structure at the inertial flywheel. Figure 2 ;

[0063] Figure 7 yes Figure 5 Schematic diagram of partial cross-sectional structure of section BB Figure 2 ;

[0064] Icons: 1-Active block; 2-Inertia flywheel; 3-Magnet; 41-Gear; 42-Rack; 5-Elastic element; 6-Roller assembly; 7-Controlled structure; 9-Rotating support; 10-Conductor; 11-Back iron. Detailed Implementation

[0065] The present invention will now be described in detail with reference to the accompanying drawings.

[0066] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0067] In the following description of specific embodiments, terms such as "up," "down," "left," "right," "center," "inner," and "outer," indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings, or the orientation or positional relationship in which the device / apparatus is typically placed during use. These terms are merely for ease of description or simplification of the description in the specific embodiments, to facilitate quick understanding of the solution by those skilled in the art, and do not indicate or imply that a particular device / component / element must have a specific orientation, or be constructed and operated in a specific positional relationship. Therefore, they should not be construed as limitations on the present invention.

[0068] The terms "horizontal," "vertical," etc., do not imply that the corresponding device / component / element must be absolutely horizontal, vertical, or suspended, but rather can be slightly tilted. For example, "horizontal" simply means that its direction is more horizontal relative to "vertical," not that the structure must be completely horizontal, but can be slightly tilted. Alternatively, it can be simplified to mean that the corresponding device / component / element, when set in a specific orientation such as "horizontal" or "vertical," can have an error / deviation of ±10% relative to that orientation, more preferably within ±8%, more preferably within ±6%, more preferably within ±5%, and more preferably within ±4%. As long as the corresponding device / component / element is within the error / deviation range, it can still achieve its function in the present invention.

[0069] The terms “first,” “second,” “third,” etc., are merely used to distinguish identical or similar components and should not be interpreted as emphasizing or implying the relative importance of a particular component.

[0070] The terms “set up,” “install,” “connect,” and “link” should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections. They can refer to common connection methods in the field, such as welding, riveting, bolting, and threaded connections. They can refer to direct connections or indirect connections through an intermediate medium. They can refer to the internal connection between two components.

[0071] Example 1

[0072] like Figures 1 to 7 As shown, the tuned inertial mass eddy current damper used in this embodiment includes a movable block 1, an inertial flywheel 2, and a motion conversion mechanism. The movable block 1 is connected to the controlled structure 7 via an elastic element 5. The extension or shortening of the elastic element 5 can drive the movable block 1 to move linearly. The inertial flywheel 2 is rotatably connected to the controlled structure 7. One end of the motion conversion mechanism is connected to the inertial flywheel 2, and the other end is connected to the movable block 1. The motion conversion mechanism can convert the linear motion of the movable block 1 into the rotational motion of the inertial flywheel 2. A magnet 3 is fixed on the inertial flywheel 2, and a conductor 10 is fixed on the controlled structure 7. The rotation of the inertial flywheel 2 can cause the conductor 10 to cut the magnetic field lines of the magnet 3.

[0073] It should be noted that, due to Figure 1 and Figure 5 The middle rack 42 and the flywheel will obstruct the structure behind them, therefore... Figure 1 and Figure 5 The rack 42 and flywheel were made transparent to reveal the hidden structures. Figure 7 The inertial flywheel 2 and gear 41 are not cut apart to show the magnet 3 on their circumference.

[0074] Specifically, in this embodiment, the controlled structure 7 is a bridge, and this embodiment is used to control the vibration of the controlled structure 7 along the longitudinal direction of the bridge. Therefore, the elastic element 5 is arranged in a relationship where the extension and contraction direction is parallel to the longitudinal direction of the bridge. Thus, when the controlled structure 7 vibrates along the longitudinal direction of the bridge, the elastic element 5 will repeatedly extend and contract, driving the movable block 1 to reciprocate in a straight line along the longitudinal direction of the bridge.

[0075] Furthermore, the motion conversion mechanism includes a gear 41 and a rack 42; the gear 41 is coaxially and fixedly connected to the inertia flywheel 2, and one end of the rack 42 is fixed to the movable block 1, while the other end meshes with the gear 41; as shown... Figure 1 and Figure 5 As shown, since this embodiment is used to control the vibration of the controlled structure 7 along the longitudinal bridge direction, the length direction of the rack 42 is set along the longitudinal bridge direction; and in this embodiment, the gear 41 is placed below the rack 42, so that the end of the rack 42 away from the movable block 1 can be supported by the gear 41.

[0076] Furthermore, a roller assembly 6 is provided between the movable block 1 and the controlled structure 7. For example... Figure 4 As shown, in this embodiment, the roller assembly 6 is connected to the movable block 1.

[0077] Furthermore, the number of magnets 3 is greater than one; the magnets 3 are distributed at intervals along the circumference of the inertial flywheel 2. Specifically, this embodiment includes multiple strip magnets 3 evenly spaced along the circumference of the inertial flywheel 2, and the N poles and S poles of two adjacent magnets 3 face opposite directions, thereby forming a loop of magnetic field lines; the length direction of each strip magnet 3 is along the tangent of the inertial flywheel 2. The magnets 3 can be disposed on the side of the inertial flywheel 2 facing the conductor 10, for example... Figures 1 to 3 Alternatively, it can be positioned on the circumference of the inertia flywheel 2 to increase the distance between the magnet 3 and the axis of the inertia flywheel 2, for example... Figures 5 to 7 Correspondingly, if the magnet 3 is placed on the circumference of the inertial flywheel 2, the conductor 10 is changed to a shape that surrounds the inertial flywheel 2 along the circumference of the inertial flywheel 2, such as a circular ring or a rectangular ring, and the back iron 11 is placed on the side of the conductor 10 away from the center of the inertial flywheel 2.

[0078] Furthermore, magnet 3 is a permanent magnet.

[0079] Furthermore, conductor 10 is a copper component.

[0080] Furthermore, the back iron 11 is a pure iron component.

[0081] Furthermore, the inertial flywheel 2 is a steel component.

[0082] Furthermore, the elastic element 5 is a helical spring. And as... Figure 1 and Figure 5As shown, this embodiment includes multiple elastic elements 5 spaced apart along the height direction.

[0083] Furthermore, such as Figure 3 and Figure 7 As shown, inertial flywheels 2, corresponding conductors 10 and back irons 11 are provided on both sides of gear 41 along its axial direction, so that the load on both sides of gear 41 is balanced.

[0084] Taking the inertial flywheel 2 as a homogeneous disk as an example, the equation of motion for the tuned inertial mass eddy current damper in this embodiment can be established as follows:

[0085]

[0086] In the formula, m s The mass of the controlled structure 7; m T M is the mass of rack 42; T x is the mass of the inertial flywheel 2; s Let x be the displacement of the controlled structure along the longitudinal direction of the bridge. s (t), x s The zeroth, first, and second derivatives with respect to time t; x T For the displacement of active block 1 along the longitudinal direction of the bridge, the corresponding value is x. T (t), x T The zeroth, first, and second derivatives with respect to time t; c s c is the damping coefficient of the controlled structure 7; c is the damping coefficient of the eddy current damper composed of the inertial flywheel 2 and the magnet 3; k s k represents the stiffness of the controlled structure 7 along the longitudinal direction of the bridge. T denoted as , where is the stiffness of the elastic element 5; is the radius of the inertial flywheel 2; is the distance from the magnet 3 to the center of the inertial flywheel 2; is the radius of the gear 41; is the external load, and correspondingly, F(t) is a function of F with respect to time t.

[0087] As can be seen from this formula, this embodiment can increase the mass of the inertial flywheel. This will increase the damping force by a factor of two. This doubles the mass of the flywheel, thus reducing its mass.

[0088] The working principle of the tuned inertial mass eddy current damper in this embodiment is as follows: when the controlled structure 7 vibrates in a certain direction, the elastic element 5 will repeatedly extend and contract in the corresponding direction, thereby driving the movable block 1 to make linear reciprocating motion. This linear reciprocating motion will be converted into the reciprocating rotational motion of the inertial flywheel 2 through the motion conversion mechanism, thereby converting the mechanical energy of the vibration of the controlled structure 7 into the angular momentum of the rotation of the inertial flywheel 2.

[0089] Meanwhile, during the reciprocating rotation of the inertial flywheel 2, it will drive the magnet 3 to move relative to the conductor 10, so that the conductor 10 can cut the magnetic field lines generated by the magnet 3, thereby generating eddy currents inside the conductor 10 and generating resistance to the magnet 3. This resistance will be transmitted to the inertial flywheel 2 and gradually slow down the rotational speed of the inertial flywheel 2, and convert the angular momentum of the rotation of the inertial flywheel 2 into the internal energy of the inertial flywheel 2, thereby achieving the effect of dissipating vibration mechanical energy.

[0090] Example 2

[0091] The tuned inertial mass eddy current damper used in this embodiment, applied to the tuned inertial mass eddy current damper in Embodiment 1, includes the following steps:

[0092] Determine the mass ratio μ of the tuned inertial mass eddy current damper based on vibration reduction requirements; calculate the optimal frequency ratio v based on μ. opt According to v opt Calculate the frequency ω of the tuned inertial mass eddy current damper. T ;

[0093] The moment of inertia I of the inertial flywheel 2 is determined based on μ; based on ω T Determine the stiffness K of elastic element 5. T .

[0094] Specifically, the relationship between the mass ratio and the optimal frequency ratio can be found in existing TMD optimal design formulas:

[0095]

[0096]

[0097] In the formula, υ opt For the optimal frequency ratio, ζ opt For the optimal damping ratio, μ is the mass ratio of the tuned inertial mass eddy current damper.

[0098] The specific formula for the moment of inertia I of the inertial flywheel 2 depends on the shape of the inertial flywheel 2. For example, if the inertial flywheel 2 is a homogeneous disk, then I can be expressed as:

[0099]

[0100] In the formula, I is the moment of inertia of the inertial flywheel 2; M T M is the mass of the inertial flywheel 2; T The diameter of the inertial flywheel 2.

[0101] Furthermore, the tuned inertial mass eddy current damper in Embodiment 1 also includes a gear 41 and a rack 42. Therefore, the moment of inertia I of the inertial flywheel 2 and the radius r of the gear 41 are determined according to the following formula:

[0102]

[0103] In the formula, μ is the mass ratio of the tuned inertial mass eddy current damper; m S The mass of the controlled structure 7; m T I is the mass of rack 42; I is the moment of inertia of flywheel 2; r is the radius of gear 41.

[0104] Furthermore, the tuned inertial mass eddy current damper in Embodiment 1 also includes a gear 41 and a rack 42, therefore the stiffness K of the elastic element 5 is determined according to the following formula. T :

[0105]

[0106] In the formula, K T The stiffness of elastic element 5; m T Let I be the mass of rack 42; let I be the moment of inertia of flywheel 2; let r be the radius of gear 41; ω be the radius of gear 41. s The frequency of the controlled structure 7; v opt This is the optimal frequency ratio.

[0107] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A design method for a tuned inertial mass eddy current damper, applied to a tuned inertial mass eddy current damper, characterized in that: The tuned inertial mass eddy current damper includes a movable block (1), an inertial flywheel (2), and a motion conversion mechanism; the movable block (1) is connected to the controlled structure (7) via an elastic element (5), and the extension or shortening of the elastic element (5) can drive the movable block (1) to move linearly; the inertial flywheel (2) is rotatably connected to the controlled structure (7); one end of the motion conversion mechanism is connected to the inertial flywheel (2), and the other end is connected to the movable block (1), and the motion conversion mechanism can convert the linear motion of the movable block (1) into the rotational motion of the inertial flywheel (2); a magnet is fixed on the inertial flywheel (2). The body (3) has a conductor (10) fixed on the controlled structure (7). The rotation of the inertial flywheel (2) enables the conductor (10) to cut the magnetic field lines of the magnet (3). The number of magnets (3) is greater than one. The magnets (3) are distributed at intervals along the circumference of the inertial flywheel (2). The N pole and S pole of two adjacent magnets (3) face opposite directions. The magnets (3) are arranged on the circumference of the inertial flywheel (2). The conductor (10) surrounds the inertial flywheel (2) along the circumference of the inertial flywheel (2). A back iron (11) is provided on the side of the conductor (10) away from the inertial flywheel (2). The design method for the tuned inertial mass eddy current damper includes the following steps: Determine the mass ratio of the tuned inertial mass eddy current damper based on vibration reduction requirements. ;according to Calculate the optimal frequency ratio ,according to Calculate the frequency of a tuned inertial mass eddy current damper ;according to Determine the moment of inertia of the inertial flywheel (2) ;according to Determine the stiffness of the elastic element (5) Stiffness of elastic element (5) Determined according to the following formula: In the formula, The stiffness of the elastic element (5); The mass of the rack (42); Let be the moment of inertia of the inertial flywheel (2); Let be the radius of the gear (41); The frequency of the controlled structure (7); This is the optimal frequency ratio.

2. The design method for a tuned inertial mass eddy current damper according to claim 1, characterized in that, The motion conversion mechanism includes a gear (41) and a rack (42); the gear (41) is coaxially and fixedly connected to the inertial flywheel (2), and one end of the rack (42) is fixed to the movable block (1), while the other end meshes with the gear (41).

3. A method for designing a tuned inertial mass eddy current damper according to any one of claims 1 to 2, characterized in that, A roller assembly (6) is provided between the movable block (1) and the controlled structure (7).

4. A method for designing a tuned inertial mass eddy current damper according to any one of claims 1 to 2, characterized in that, The magnet (3) is a permanent magnet.

5. A method for designing a tuned inertial mass eddy current damper according to any one of claims 1 to 2, characterized in that, The conductor (10) is a copper component.

6. The design method for a tuned inertial mass eddy current damper according to claim 1, characterized in that, When the tuned inertial mass eddy current damper also includes a gear (41) and a rack (42), the moment of inertia I of the inertial flywheel (2) and the radius of the gear (41) are determined according to the following formula. : In the formula, To adjust the mass ratio of the inertial mass eddy current damper; The mass of the controlled structure (7); The mass of the rack (42); Let be the moment of inertia of the inertial flywheel (2); Let be the radius of the gear (41).

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