Tuned mass inerter damper and parameter design method thereof

Abstract

The invention relates to a tuned mass inerter damper and a parameter design method thereof. The tuned mass inerter damper comprises a balancing weight, a first guide rod, a first rigid spring, a first middle plate, a damper body and an inerter. The balancing weight is slidably connected to the floor, the first rigid spring sleeves the first guide rod, and the two ends of the first rigid spring abut against the balancing weight and the first middle plate correspondingly; one ends of the damper and the inerter are fixedly connected to the other side of the first middle plate, and the other ends of the damper and the inerter are fixedly connected to the floor main structure; the sliding direction of the balancing weight, the first guide rod, the damper and the inerter are parallel to one another. The invention relates to the technical field of building vibration reduction. Lightweight control over natural vibration of a building structure can be achieved.

Description

Technical Field

[0001] The present invention relates to the technical field of building vibration reduction, and particularly to a tuned mass inerter damper and a parameter design method thereof. Background Art

[0002] Modern buildings have a large aspect ratio, a more flexible structural system, and a longer natural vibration period. Under the action of external excitations that are sudden, random, and destructive, they are prone to cause property and personnel losses. Therefore, it is necessary to take measures for shock (vibration) reduction structural control to improve the seismic (vibration) resistance of the structure.

[0003] A tuned mass damper (TMD) is a shock (vibration) reduction sub-structure commonly used in the building field and attached to the structure. Its mass block is generally connected to the building structure through a spring and a damper. The weight of the tuned mass damper is determined by the mass ratio (the mass ratio is the mass of the mass block of the tuned mass damper / the mass of the structure). Generally speaking, the larger the mass ratio, the better the vibration absorption effect of the damper.

[0004] In the prior art, the application scenarios of TMD in the building field are mainly limited by the tuned mass. An overly large tuned mass will occupy too much installation space, causing difficulties in design and construction and increasing the building cost. In the current situation where building structures pursue large areas and large masses, traditional small-tonnage tuned mass dampers are difficult to meet the vibration reduction effect required by the main structure of the current structures. Summary of the Invention

[0005] Aiming at the problems existing in the prior art, the purpose of the present invention is to provide a tuned mass inerter damper and a parameter design method thereof, which can achieve lightweight control of the natural vibration of the building structure.

[0006] To achieve the above purpose, the present invention adopts the following technical solutions:

[0007] A tuned mass inerter damper includes a counterweight, a first guide rod, a first rigid spring, a first intermediate plate, a damper and an inerter; the counterweight is slidably connected to the floor slab; both ends of the first guide rod are respectively connected to the counterweight and one side of the first bottom plate; the first rigid spring is sleeved on the first guide rod and its two ends respectively abut against the counterweight and the first intermediate plate; one ends of the damper and the inerter are both fixedly connected to the other side of the first intermediate plate, and the other ends of the damper and the inerter are both fixedly connected to the floor slab; the sliding direction of the counterweight, the first guide rod, the damper and the inerter are parallel to each other. With this structure, the damper can provide a damping force for the sliding movement of the counterweight, and the mass coefficient of the inerter can significantly increase the equivalent mass of the system. Therefore, the setting of the inerter can amplify the mass of the counterweight, and the mass of the counterweight can be reduced under the same shock (vibration) damping effect, thus achieving the effect of lightweight control; the first rigid spring can make the movement of the counterweight more stable, so the response of the damper is more stable, and the shock (vibration) damping effect of the tuned mass inerter damper is more stable.

[0008] As a preference, the damper is a magnetorheological damping element. The push rod end of the magnetorheological damping element is fixedly connected to the first intermediate plate, the cylinder body of the magnetorheological damping element is fixedly connected to the main structure of the floor slab, and the damping of the magnetorheological damping element is adjustable. With this structure, the magnetorheological damper has the characteristics of simple structure, small volume, fast response speed and wide dynamic range, which is beneficial to improving the shock (vibration) damping effect of the tuned mass inerter damper and expanding the application scenarios.

[0009] As a preference, the inerter is a ball screw. The screw rod end of the ball screw is fixedly connected to the first intermediate plate, and the rotating nut of the ball screw is fixedly connected to the main structure of the floor slab. With this structure, the ball screw has the advantages of stable structure, high transmission efficiency and easy control, and its parameter adjustment is convenient.

[0010] As a preference, the damper and the inerter are symmetrically arranged on both sides of the first guide rod. With this structure, the balance and stability of the tuned mass inerter damper can be further improved.

[0011] As a preference, the first guide rod passes through the first intermediate plate and a first bottom plate is provided at the end. The first intermediate plate is located between the counterweight and the first bottom plate, and first rigid springs are provided between the first intermediate plate and the counterweight and between the first intermediate plate and the first bottom plate. With this structure, the forces at both ends of the first intermediate plate are more balanced, the movement amplitude of the first intermediate plate can be controlled, so that it can more stably transfer the movement of the counterweight to the damper and the inerter, and further make the damper more stably respond to the vibration of the main structure. On the one hand, the impact of the counterweight on the damper and the inerter can be reduced, and on the other hand, the shock (vibration) damping effect can be improved.

[0012] As a preference, a linear circular guide rail is penetrated through the middle of the first intermediate plate. The linear circular guide rail is sleeved on the first guide rod and is slidably connected to the first guide rod. With this structure, the movement of the first intermediate plate is smoother and more stable, which is beneficial to improving the response speed of the tuned mass inertial damper.

[0013] As a preference, a second guide rod is provided on one side of the first guide rod. The second guide rod is sleeved with a second rigid spring. The second rigid spring is parallel to the first rigid spring. The two ends of the second rigid spring respectively abut against the counterweight and the floor slab. With this structure, the movement of the counterweight is more stable, which can improve the movement stability of the tuned mass inertial damper. Therefore, this design can improve the control ability of the tuned mass inertial damper on the vibration of the main structure.

[0014] As a preference, a second intermediate plate is penetrated through the second guide rod. A second bottom plate is provided at the end of the second guide rod. Second rigid springs are provided between the second intermediate plate and the counterweight and between the second intermediate plate and the second bottom plate respectively. With this structure, the stability of the movement of the counterweight is further improved.

[0015] As a preference, the total stiffness, length, and deformation amount of the first rigid springs between the first intermediate plate and the counterweight and between the first intermediate plate and the first bottom plate are the same respectively; the total stiffness, length, and deformation amount of the second rigid springs between the second intermediate plate and the counterweight and between the second intermediate plate and the second bottom plate are the same respectively. The first rigid springs mainly cooperate with the inertial container and the parallel part of the damper to move and form a resonance effect. At this time, the movement phase of the parallel part will be nearly opposite to that of the first rigid spring, so that the displacement amplitude of the parallel part is greater than that of the counterweight, that is, it is beneficial for the damper to generate greater damping under small displacements; the total stiffness, length, and deformation amount of the second rigid springs between the second intermediate plate and the counterweight and between the second intermediate plate and the second bottom plate are the same respectively. The second rigid springs mainly play a tuning role to make the natural vibration period of the counterweight close to that of the main structure. With the structure of setting rigid springs on both sides, it can better achieve that the corresponding stiffness magnitudes remain unchanged under the tensile and compression states, making the actual structure closer to the mechanical principle. At the same time, the movement stability of the first intermediate plate and the counterweight will also be strengthened, and the vibration control ability of the tuned mass inertial damper on the main structure is stronger.

[0016] A parameter design method for a tuned mass inertial damper includes the following steps:

[0017] Step 1: Pre-analyze the main structure of the floor slab to obtain the modal and vibration mode results, and determine the installation position of the tuned mass inertial damper;

[0018] Step 2: After determining the installation position, establish a kinematic equation, thereby deriving the displacement response transfer function of the main structure, and then establish an optimization equation with the H2 norm l of the displacement response transfer function of the main structure as the optimization target;

[0019] Kinematics equation: MX″ + CX′ + KX = -M R X g ″;

[0020] Displacement response transfer function: H(ω) = C s (iωI - A) -1 E;

[0021]

[0022] C s =[I N+2n 0 N+2n ;

[0023] Step 3: Determine the optimization objective l according to the requirements. By giving the tuning mass ratio μ t and the damping ratio ζ in value intervals, use step-by-step parameter scanning to realize the parameter optimization of RIDTMD; where I represents the identity matrix; M is the mass matrix of the additional tuned mass and inertance, K is the stiffness matrix; C is the damping matrix, M R is the mass matrix of only the additional tuned mass; A is the state matrix, describing the dynamic characteristics of the system, E is the input matrix, describing the influence of the input on the state, C S is the output matrix describing the contribution of the state to the output;

[0024] Optimization equation: l = ||H||2 = ||C s (iω - A) -1 E||2;

[0025] μ min ≤ μ t ≤ μ max ;

[0026] ζ min ≤ ζ in ≤ ζ max ;

[0027] where H is the frequency response function; i is the imaginary unit; ω represents the frequency of the external excitation; μ t is the tuning mass ratio; ζ in is the damping ratio;

[0028] Step 4: Solve the optimization design equation to obtain the design parameter values of the tuning mass ratio μ t and the damping ratio ζ in , and use these two parameters to deduce and determine the tuning mass, damping coefficient, inertance coefficient, first rigid spring stiffness and second rigid spring stiffness;

[0029] Step 5: Verify the obtained design parameters by time history analysis. If the control effect meets the requirements, the parameter design is completed; otherwise, adjust the tuning mass ratio μ t and the damping ratio ζ in in the value range, and repeat steps 3 - 4 until the control effect is satisfied.

[0030] Using this method, based on the improved fixed - point theory method, the optimization design problem of multiple parameters of RIDTMD is simplified to the optimization problem of two parameters, mass and damping. The relevant design parameters of RIDTMD can be determined more accurately and quickly, achieving the best effect of vibration control of the low - order modes of high - rise structures by the tuned mass inertia - damping damper.

[0031] Generally speaking, the present invention has the following advantages:

[0032] When the main structure is subjected to an external excitation and has a dynamic response, and the external excitation frequency is close to the natural frequency of the structure, the structure resonates and has a large displacement at the position of the natural vibration mode. During the vibration of the floor slab following the main structure, the counterweight in the device will deviate from the static position and slide on the floor slab. At this time, the counterweight drives the first rigid spring to deform under the constraint of the first guide rod parallel to the sliding direction of the counterweight. The resultant force of the first rigid spring is transmitted to the damper and the inertor arranged in parallel through the first guide rod and then to the floor slab. The damper and the inertor perform linear reciprocating motions parallel to the sliding direction of the counterweight. The inertor generates an inertial force that can amplify the tuned mass, and the damper generates a damping force to play an energy - dissipation role, achieving the effect of shock (vibration) reduction. When the weight of the counterweight, the elastic force and the damping force reach the optimal control parameters, the natural frequency of the damper is consistent with the first - order vibration frequency of the high - rise building, and the vibration control of the low - order modes of the high - rise structure can be realized. Brief Description of the Drawings

[0033] Figure 1 It is a schematic diagram of the overall structure of the tuned mass inertia - damping damper.

[0034] Figure 2 It is a schematic diagram of the connection structure of the T - shaped plate, the first guide rod and the second guide rod in the embodiment.

[0035] Figure 3 It is a schematic diagram of the structure at the second rigid spring of the tuned mass inertia - damping damper.

[0036] Figure 4 It is a schematic diagram of the connection structure of the first rigid spring, the damper and the inertor.

[0037] Figure 5 It is a schematic diagram of the structure of the counterweight box in the embodiment.

[0038] Figure 6 It is a schematic diagram of the connection structure of the baffle part.

[0039] Figure 7 It is a flow chart of the parameter design method for a tuned mass inertial damper.

[0040] In the figure: 1 is a baffle, 2 is an angle steel, 3 is a circular tube, 4 is a clamp, 5 is a ball screw, 6 is a flange, 7 is a magnetorheological damping element, 8 is a second intermediate plate, 9 is a first intermediate plate, 10-1 is a first bottom plate, 10-2 is a second bottom plate, 11 is a linear circular guide rail, 12 is a second rigid spring, 13 is a first rigid spring, 14-1 is a first guide rod, 14-2 is a second guide rod, 15 is a T-shaped plate, 16 is a counterweight box, 17 is a lifting lug, 18 is a counterweight guide rail slider mechanism, 19 is a guide rail embedded part, 20 is a bolt. Specific implementation mode

[0041] The present invention will be further described in detail below.

[0042] As Figures 1-6 shown, a tuned mass inertial damper includes an installation support part, a first rigid spring 13 part, a second rigid spring 12 part for transmitting the axial movement of the structure, an inertial damper parallel part for energy dissipation and amplifying the tuned mass, a counterweight box 16 part, and a T-shaped plate part for connecting the installation support part and the counterweight box 16 part.

[0043] The counterweight box 16 is used to accommodate counterweight blocks. A number of square sliders are installed at the center position of the lower steel plate of the counterweight box 16. A guide rail embedded part 19 cooperating with the counterweight guide rail slider mechanism 18 is provided on the floor slab. The counterweight box 16 is horizontally slidably connected to the floor slab through the counterweight guide rail slider mechanism 18; the first rigid spring 13 and the second rigid spring 12 provide elastic forces for the reciprocating movement of the counterweight box 16. The counterweight box 16 is provided with a lifting lug 17 for convenient hoisting.

[0044] The installation support part is connected to the building structure floor slab; the installation support part includes an angle steel 2, a baffle 1 and a circular tube 3. The angle steel 2 is connected to the baffle 1 by welding or bolts 20, and the angle steel 2 is connected to the main building structure by anchor bolts; the circular tube 3 is welded to the baffle 1.

[0045] The T-shaped plate 15 is provided with holes, and the hole positions correspond to the counterweight box 16. The T-shaped plate 15 connects two counterweight boxes 16, and the first guide rod 14-1 and the second guide rod 14-2 are connected to the corresponding center position on the other side of the T-shaped plate 15. The first guide rod 14-1 is used to place the first rigid spring 13, and the second guide rod 14-2 is used to place the second rigid spring 12.

[0046] At the first rigid spring 13, there are a first guide rod 14-1, a first intermediate plate 9, and a first bottom plate 10-1. First rigid springs 13 are provided between the first intermediate plate 9 and the first bottom plate 10-1, and between the first intermediate plate 9 and the counterweight box 16. The first intermediate plate 9 is fixed on the installation support part. The first guide rod 14-1 passes through the hole of the first intermediate plate 9, and the first bottom plate 10-1 is fixedly connected to the end of the first guide rod 14-1. The first guide rod 14-1 connected to the T-shaped plate 15 is used to limit the deformation direction of the first rigid spring 13.

[0047] The inertia of the inertia-damping parallel part is realized by the ball screw 5. One end of the ball screw 5 pair partially passes through the round tube 3. The end of the round tube 3 is welded with a flange 6, and the external rotating nut of the ball screw 5 element is fixed with the flange 6. The other end of the round tube 3 is connected to the installation support part. A flywheel is installed on the rotating nut. The rotating nut is in a stepped cylindrical shape, and a closed ball track containing balls is arranged inside the rotating nut. When the screw rod makes a translational motion, the balls will circulate in the screw thread teeth of the screw rod and in the bearing track, and drive the rotating nut and the flywheel to rotate; the flywheel is fixedly connected to the rotating nut and does not rotate relatively. The flywheel has a certain mass and radius and can be disassembled and replaced according to actual needs. The inertia of the counterweight box 16 is adjusted by changing the lead of the ball screw pair and the size of the flywheel of the ball screw 5 element.

[0048] The damping of the inertia-damping parallel part is realized by the magnetorheological damping element 7, and the damping fluid is an oil-based magnetorheological fluid with conductivity. The cylinder body of the magnetorheological damping element 7 is fixed by a clamp 4, and the other side of the clamp 4 is fixed on the round tube 3 connected to the installation support part. The damping of the magnetorheological damping element 7 can be adjusted according to the change of the current as needed, providing an appropriate adjustable damping force for the linear reciprocating motion of the counterweight box 16.

[0049] The other end of the ball screw 5 pair and the push rod end of the magnetorheological damping element 7 are both fixed on the first intermediate plate 9 on the linear circular guide rail 11. The first intermediate plate 9 is connected to the linear circular guide rail 11 through the flange 6 to achieve the parallel effect of the inertia-damping parallel part.

[0050] The first guide rod 14-1 passes through the middle of the linear circular guide rail 11 of the inertia-damping parallel part. The linear circular guide rail 11 can move horizontally along the first guide rod 14-1. The first rigid spring 13 is sleeved on the first guide rod 14-1. One end of the first guide rod 14-1 is fixed on the T-shaped plate, and the other end is fixed to the first bottom plate 10-1, forming the first rigid spring 13 part.

[0051] A series part is formed between the inertia-damping parallel part and the first rigid spring 13 part, and the series part is then connected in parallel with the second rigid spring 12.

[0052] On one side of the first guide rod 14-1, there is a second guide rod 14-2. The second rigid spring 12 is sleeved on the second guide rod 14-2. A second intermediate plate 8 is sleeved on the second guide rod 14-2. The second guide rod 14-2 passes through the second intermediate plate 8 and a second bottom plate 10-2 is provided at its end. Second rigid springs 12 are provided both between the second intermediate plate 8 and the second bottom plate 10-2 and between the second intermediate plate 8 and the counterweight box 16.

[0053] The sliding direction of the counterweight, the first guide rod 14-1, the second guide rod 14-2, the first rigid spring 13, the second rigid spring 12, the damper and the inertor are parallel to each other.

[0054] In use, the tuned mass inertance damper is installed inside the high-rise structure to control, but not limited to, the first-order structural vibration of the structure. When the high-rise structure is subjected to an external excitation and undergoes a dynamic response, when the external excitation frequency is close to the natural frequency of the structure, the structure resonates and a large displacement occurs at the position of the natural vibration mode. During the vibration of the high-rise structure, the counterweight box 16 in the device will deviate from the static position and slide within the track. At this time, the counterweight box 16 drives the two rigid springs to deform under the constraint of the guide rod in the direction parallel to the track. The resultant force of the rigid springs is transmitted to the installation support part through the guide rod. The first rigid spring 13 drives the magnetorheological damping element 7 and the ball screw 5 element to perform a linear reciprocating motion parallel to the track, causing the balls to move within the screw and the ball bearings and driving the ball bearings and the flywheel to rotate, generating an inertial force. After the magnetorheological damping element 7 is energized, it can generate an appropriate damping force. When the weight of the mass block, the elastic force received, and the damping force reach the optimal control parameters, the natural frequency of the damper is consistent with the first-order vibration frequency of the high-rise building, and the vibration control of the low-order mode of the high-rise structure can be achieved.

[0055] As Figure 7 shown, a parameter design method for a tuned mass inertance damper includes the following steps:

[0056] Step 1: Pre-analyze the main structure of the floor slab to obtain the modal and vibration mode results, and determine the installation position of the tuned mass inertance damper;

[0057] Step 2: After determining the installation position, establish a kinematic equation, derive the displacement response transfer function of the main structure from this, and then establish an optimization equation with the H2 norm l of the displacement response transfer function of the main structure as the optimization objective;

[0058] Kinematic equation: MX″ + CX′ + KX = -M R X g ″

[0059] Displacement response transfer function: H(ω) = C s (iωI - A) -1 E

[0060]

[0061] C s = [I N+2n 0 N+2n ;

[0062] Step 3: Determine the optimization objective l according to the requirements. By given tuning mass ratio μ t and damping ratio ζ in value intervals, use step-by-step parameter scanning to achieve parameter optimization of RIDTMD; where I represents the identity matrix; M is the mass matrix of the additional tuned mass and inertance, K is the stiffness matrix; C is the damping matrix, M R is the mass matrix with only the additional tuned mass; A is the state matrix, describing the dynamic characteristics of the system, E is the input matrix, describing the influence of the input on the state, C S is the output matrix describing the contribution of the state to the output;

[0063] Optimization equation: l = ||H||2 = ||C s (iω - A) -1 E||2;

[0064] μ min ≤ μ t ≤ μ max ;

[0065] ζ min ≤ ζ in ≤ ζ max ;

[0066] where H is the frequency response function; i is the imaginary unit; ω represents the frequency of the external excitation; μ t is the tuning mass ratio; ζ in is the damping ratio;

[0067] Step 4: Solve the optimization design equation to obtain the design parameter values of the tuning mass ratio μ t and damping ratio ζ in . Use these two parameters to deduce and determine the tuning mass, damping coefficient, inertance coefficient, the stiffness of the first rigid spring and the stiffness of the second rigid spring;

[0068] Step 5: Verify the obtained design parameters by time history analysis. If the control effect meets the requirements, complete the parameter design. Otherwise, adjust the value intervals of the tuning mass ratio μ t and damping ratio ζ in and repeat steps 3 - 4 until the control effect is satisfied.

[0069] The present invention has the following advantages:

[0070] 1. The characteristic of increasing the apparent mass of the inerter can be extended to the tuned vibration damping device to achieve lightweight horizontal vibration damping.

[0071] 2. Under external excitation, when the main structure causes the counterweight box 16 to undergo tuned vibration, the parallel combination of the magnetorheological damper and the ball screw moves along with the movement of the first rigid spring 13 and forms a resonance effect. At this time, the movement phase of the parallel combination will be nearly opposite to that of the first rigid spring 13, so that the displacement amplitude of the parallel part is greater than that of the counterweight box 16, which is conducive to generating greater damping under small displacements of the magnetorheological damper.

[0072] 3. The parallel combination can better realize the energy dissipation and efficiency enhancement of the magnetorheological damping element 7 and the role of the ball screw in amplifying the tuned mass, and enhance the control effect of the entire device.

[0073] 4. The movement of the counterweight box 16 is transmitted to the damper and the inerter through the first intermediate plate 9. The relevant designs of the first intermediate plate 9 and the first rigid spring 13 can play a role in stabilizing and buffering, enabling the movement of the first intermediate plate 9 to be more stable and reducing the impact of the counterweight box 16 on the damper and the inerter; the role of the second intermediate plate 8 and the second rigid spring 12 can make the movement of the counterweight box 16 more stable.

[0074] 5. The internal structure of the tuned mass inerter damper is balanced, which can more stably and reliably respond to external excitation, thereby improving the vibration damping effect and enhancing the vibration control of the tuned mass inerter damper on the building structure.

[0075] 6. The structure is simple, directly corresponding to the mechanical principle sketch, easy to adjust, and the performance parameters of the damper can be quickly adjusted by adjusting the overall stiffness of the two rigid springs, the lead of the ball screw pair, the size of the flywheel, the mass of the counterweight block, and the current of the magnetorheological damping element 7.

[0076] 7. The relevant parameters of the present invention adopt a design method with the H2 norm l of the displacement response transfer function of the main structure as the optimization goal. Based on the improved fixed-point theory method, this method simplifies the multi-parameter optimization design problem of RIDTMD into an optimization problem of two parameters, mass and damping, and can determine the relevant design parameters of RIDTMD more accurately and quickly.

[0077] The above embodiments are the preferred embodiments of the present invention, but the embodiments of the present invention are not limited to the above embodiments. Any other changes, modifications, substitutions, combinations, and simplifications made without departing from the spirit and principle of the present invention shall be equivalent replacement methods and are all included in the protection scope of the present invention.

Claims

1. A tuned mass inertia-damper, characterized in that: It includes a counterweight, a first guide rod, a first rigid spring, a first intermediate plate, a damper and an inertor; The counterweight is slidably connected to the floor slab; Both ends of the first guide rod are respectively connected to the counterweight and one side of the first intermediate plate; The first rigid spring is sleeved on the first guide rod and its two ends respectively abut against the counterweight and the first intermediate plate; One ends of the damper and the inertor are both fixedly connected to the other side of the first intermediate plate, and the other ends of the damper and the inertor are both fixedly connected to the main structure of the floor slab; The sliding direction of the counterweight, the first guide rod, the damper and the inertor are parallel to each other.

2. The tuned mass inerter damper according to claim 1, wherein: The damper is a magnetorheological damping element. The push rod end of the magnetorheological damping element is fixedly connected to the first intermediate plate, and the cylinder body of the magnetorheological damping element is fixedly connected to the main structure of the floor slab. The damping of the magnetorheological damping element is adjustable.

3. The tuned mass inerter damper according to claim 1, wherein: The inertor is a ball screw. The screw rod end of the ball screw is fixedly connected to the first intermediate plate, and the rotating nut of the ball screw is fixedly connected to the main structure of the floor slab.

4. A tuned mass inerter damper according to claim 1, wherein: The damper and the inertor are symmetrically arranged on both sides of the first guide rod.

5. The tuned mass inerter damper according to claim 1, wherein: The first guide rod passes through the first intermediate plate and a first bottom plate is provided at the end. The first intermediate plate is located between the counterweight and the first bottom plate. First rigid springs are provided between the first intermediate plate and the counterweight and between the first intermediate plate and the first bottom plate.

6. The tuned mass inerter damper according to claim 1, wherein: A linear circular guide rail is penetrated through the middle of the first intermediate plate. The linear circular guide rail is sleeved on the first guide rod and is slidably connected to the first guide rod.

7. A tuned mass inertial damper according to claim 1, characterized in that: A second guide rod is provided on one side of the first guide rod. The second guide rod is sleeved with a second rigid spring. The second rigid spring is parallel to the first rigid spring. The two ends of the second rigid spring respectively abut against the counterweight and the floor slab.

8. A tuned mass inerter damper according to claim 7, characterized in that: A second intermediate plate is penetrated through the second guide rod. A second bottom plate is provided at the end of the second guide rod. Second rigid springs are provided between the second intermediate plate and the counterweight and between the second intermediate plate and the second bottom plate.

9. The tuned mass inerter damper according to claim 8, wherein: The total stiffness, length and deformation of the first rigid springs between the first intermediate plate and the counterweight and between the first intermediate plate and the first bottom plate are respectively the same; the total stiffness, length and deformation of the second rigid springs between the second intermediate plate and the counterweight and between the second intermediate plate and the second bottom plate are respectively the same.

10. A parameter design method for a tuned mass inertia damper according to any one of claims 1-9, characterized in that: It includes the following steps; Step 1: Perform pre-analysis on the main structure of the floor slab to obtain modal and vibration mode results, and determine the installation position of the tuned mass inertance damper; Step 2: After determining the installation position, establish a kinematic equation, thereby deriving the displacement response transfer function of the main structure, and then establish an optimization equation with the H2 norm l of the displacement response transfer function of the main structure as the optimization objective; Kinematics equation: MX″ + CX′ + KX = -M R X g ″; Displacement response transfer function: H(ω) = C s (iωI - A) -1 E; C s = [I N+2n 0 N+2n ; Step 3: Determine the optimization objective l according to the requirements, and use the given tuning mass ratio μ t and damping ratio ζ in value range, and use step-by-step parameter scanning to realize the parameter optimization of RIDTMD; where I represents the identity matrix; $M$ is the mass matrix of the additional tuned mass and the inertance, $K$ is the stiffness matrix; $C$ is the damping matrix, and $M$ R is the mass matrix of only the additional tuned mass; A is the state matrix, which describes the dynamic characteristics of the system. E is the input matrix, which describes the influence of the input on the state. C S is the output matrix, which describes the contribution of the state to the output; Optimization equation: l = ||H||2 = ||C s (iω - A) -1 E||2; μ min ≤ μ t ≤ μ max ; ζ min ≤ζ in ≤ζ max ; where H is the frequency response function; i is the imaginary unit; ω represents the frequency of the external excitation; μ t is the tuning mass ratio; ζ in is the damping ratio; Step 4: Solve the optimization design equation to obtain the tuning mass ratio μ t , the damping ratio ζ in of the design parameter values, and use these two parameters to derive and determine the tuning mass, damping coefficient, inertance coefficient, first rigid spring stiffness, and second rigid spring stiffness; Step 5: Verify the obtained design parameters through time history analysis. If the control effect meets the requirements, the parameter design is completed; otherwise, adjust the tuning mass ratio μ t and the damping ratio ζ in Take the value range and repeat steps 3 to 4 until the control effect is satisfied.

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