Tuned mass inerter damper and parameter design method thereof

Abstract

The present application relates to a kind of tuned mass inertial damper and its parameter design method, tuned mass inertial damper includes counterweight, first guide rod, first rigid spring, first intermediate plate, damper and inertial container;Counterweight is slidably connected to floor, first rigid spring is sleeved in first guide rod and two ends are respectively abutted on counterweight and first intermediate plate;Damper and inertial container one end are both fixed to the other side of first intermediate plate, and the other end of damper and inertial container is all fixed to floor main structure;The sliding direction of counterweight, first guide rod, damper and inertial container are mutually parallel between each other.The present application relates to the field of building vibration reduction technology, and lightweight control of building structure self-vibration can be realized.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of building vibration reduction, in particular to a tuned mass inertia damper and a parameter design method thereof. BACKGROUND

[0002] Modern buildings have a large height-width ratio, and the structural system is more flexible, with a long natural period. Under the action of external excitation with suddenness, randomness and destructiveness, it is easy to cause property and personnel loss, so it is necessary to take measures to control the vibration of the structure to improve the structural seismic capacity.

[0003] The tuned mass damper (TMD) is a common vibration reduction substructure in the field of building, which is usually connected to the building structure through a spring and a damper. The weight of the tuned mass damper is determined by the mass ratio (mass ratio is the mass of the tuned mass damper mass / structure mass), generally speaking, the larger the mass ratio, the better the vibration absorption effect of the damper.

[0004] In the prior art, the use of TMD in the field of building is mainly limited by the tuned mass. A large tuned mass occupies too much installation space, causing difficulties in design and construction, and increasing the cost of the building. In the current situation of pursuing large area and large mass of building structures, traditional small tonnage tuned mass dampers cannot meet the vibration reduction effect required by the main structure of the current structure. SUMMARY

[0005] In view of the problems existing in the prior art, the purpose of the present application is to provide a tuned mass inertia damper and a parameter design method thereof, which can realize lightweight control of the natural vibration of the building structure.

[0006] In order to achieve the above purpose, the technical scheme adopted by the present application is as follows:

[0007] A tuned mass inertial damper comprises a counterweight, a first guide rod, a first rigid spring, a first intermediate plate, a damper, and an inertial container. The counterweight is slidably connected to a floor. The first guide rod has two ends connected to the counterweight and one side of the first bottom plate, respectively. The first rigid spring is sleeved on the first guide rod and has two ends abutting the counterweight and the first intermediate plate, respectively. One end of the damper and the inertial container are both fixed to the other side of the first intermediate plate, and the other ends of the damper and the inertial container are both fixed to the floor. The sliding direction of the counterweight, the first guide rod, the damper, and the inertial container are parallel to each other. With this structure, the damper can provide damping force for the sliding motion of the counterweight, and the mass coefficient of the inertial container can significantly increase the equivalent mass of the system. Therefore, the provision of the inertial container can amplify the mass of the counterweight, reducing the mass of the counterweight while maintaining the same vibration reduction effect, thereby achieving a lightweight control effect. The first rigid spring can make the motion of the counterweight more stable, thereby making the response of the damper more stable, and the vibration reduction effect of the tuned mass inertial damper more stable.

[0008] Preferably, the damper is a magnetorheological damping element, with its push rod end fixed to the first intermediate plate and its cylinder fixed to the main floor structure. The damping capacity of the magnetorheological damping element is adjustable. This structure offers a simple structure, compact size, fast response, and a wide dynamic range, enhancing the shock (vibration) reduction performance of the tuned mass inertia damper and expanding its application scenarios.

[0009] Preferably, the inertia chamber is a ball screw, with its screw end fixed to the first intermediate plate and its rotating nut fixed to the main floor structure. This structure offers the advantages of structural stability, high transmission efficiency, and ease of control, with convenient parameter adjustment.

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

[0011] Preferably, the first guide rod passes through the first intermediate plate and is provided with a first base plate at its end. The first intermediate plate is positioned between the counterweight and the first base plate. First rigid springs are provided between the first intermediate plate and the counterweight, and between the first intermediate plate and the first base plate. This structure provides a more balanced force distribution at both ends of the first intermediate plate, controlling the range of motion of the first intermediate plate and enabling more stable transmission of the counterweight's motion to the damper and inertia vessel. This, in turn, allows the damper to more stably respond to vibrations of the main structure, thereby reducing the impact of the counterweight on the damper and inertia vessel and improving shock (vibration) absorption.

[0012] Preferably, a linear circular guide rail is provided through the middle of the first intermediate plate, which is sleeved and slidably connected to the first guide rod. This structure allows for smoother and more stable movement of the first intermediate plate, thereby improving the response speed of the tuned mass inertia damper.

[0013] Preferably, a second guide rod is provided on one side of the first guide rod. A second rigid spring is sleeved onto the second guide rod and is parallel to the first rigid spring. The second rigid spring's ends abut the counterweight and the floor slab, respectively. This structure stabilizes the counterweight's movement, improving the stability of the tuned mass inertia damper. Consequently, this design enhances the tuned mass inertia damper's ability to control the vibrations of the main structure.

[0014] Preferably, a second intermediate plate is provided through the second guide rod, a second bottom plate is provided at the end of the second guide rod, and second rigid springs are provided between the second intermediate plate and the counterweight and between the second intermediate plate and the second bottom plate. This structure further improves the stability of the counterweight movement.

[0015] Preferably, the first rigid springs between the first intermediate plate and the counterweight, and between the first intermediate plate and the first base plate, have the same total stiffness, length, and deformation. The second rigid springs between the second intermediate plate and the counterweight, and between the second intermediate plate and the second base plate, have the same total stiffness, length, and deformation. The first rigid spring primarily coordinates the motion of the parallel components of the inertia chamber and the damper, creating a resonant effect. At this point, the motion phase of the parallel components is nearly opposite to that of the first rigid spring, resulting in a larger displacement amplitude of the parallel components than the counterweight, which facilitates greater damping of the damper at small displacements. The second rigid springs between the second intermediate plate and the counterweight, and between the second intermediate plate and the second base plate, have the same total stiffness, length, and deformation. The second rigid springs primarily serve a tuning function, aligning the natural vibration periods of the counterweight and the main structure. Using a structure with rigid springs on both sides better ensures that the corresponding stiffness remains constant under tension and compression, bringing the actual structure closer to mechanical principles. This also enhances the stability of the motion of the first intermediate plate and the counterweight, and strengthens the vibration control capability of the tuned mass inertia chamber damper on the main structure.

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

[0017] Step 1: Perform a preliminary analysis of the main floor structure to obtain modal and vibration shape results and determine the installation location of the tuned mass inertia damper;

[0018] Step 2: After determining the installation position, establish the kinematic equation to derive the displacement response transfer function of the main structure. Then establish the optimization equation with the H2 norm l of the displacement response transfer function of the main structure as the optimization target.

[0019] Kinematic 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 target l according to the requirements, by giving the tuning mass ratio μ t and damping ratio ζ in The parameter optimization of RIDTMD is realized by stepwise parameter sweeping. Where I represents the identity matrix; M is the mass matrix of the additional tuning mass and inertia, K is the stiffness matrix; C is the damping matrix, M R is the mass matrix with only the tuning mass added; 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 Describe the contribution of the state to the output for the output matrix;

[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; in is the damping ratio;

[0028] Step 4: Solve the optimization design equation to obtain the tuning mass ratio μ t , damping ratio ζ in The design parameter values ​​of are taken, and the tuning mass, damping coefficient, inertia coefficient, first rigid spring stiffness and second rigid spring stiffness are determined by deriving these two parameters;

[0029] Step 5: Use time history analysis to verify the obtained design parameters. If the control effect meets the requirements, the parameter design is completed. Otherwise, adjust the tuning mass ratio μ t and damping ratio ζ in Repeat steps 3 and 4 in the value range until the control effect is satisfied.

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

[0031] In general, the present invention has the following advantages:

[0032] When the main structure responds to external excitation and the frequency of the external excitation approaches the natural frequency of the structure, the structure resonates and experiences significant displacement at the natural vibration mode. As the floor vibrates with the main structure, the counterweight in the device deviates from its static position and slides on the floor. At this point, the counterweight drives the first rigid spring to deform under the constraint of a first guide rod parallel to the counterweight's sliding direction. The combined force of the first rigid spring is transmitted through the first guide rod to the parallel-arranged damper and inertia vessel, and then to the floor. The damper and inertia vessel undergo linear reciprocating motion parallel to the counterweight's sliding direction. The inertia vessel generates an inertial force that amplifies the tuned mass, while the damper generates a damping force that dissipates energy, achieving a shock (or vibration) reduction effect. When the counterweight weight, the elastic force, and the damping force reach optimal control parameters, the damper's natural frequency aligns with the high-rise building's first-order vibration frequency, effectively controlling the high-rise structure's low-order modes. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 Schematic diagram of the overall structure of the tuned mass inertia damper.

[0034] Figure 2 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 This is a schematic diagram of the structure of the second rigid spring of the tuned mass inertia damper.

[0036] Figure 4 Schematic diagram of the connection structure of the first rigid spring, damper and inertia container.

[0037] Figure 5 Schematic diagram of the structure of the counterweight box in the embodiment.

[0038] Figure 6 Schematic diagram of the connection structure of the baffle part.

[0039] Figure 7 Flowchart of the parameter design method for tuned mass inertial damper.

[0040] In the figure: 1 is a baffle, 2 is an angle steel, 3 is a round 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 ear, 18 is a counterweight guide rail slider mechanism, 19 is a guide rail embedded part, and 20 is a bolt. DETAILED DESCRIPTION

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

[0042] like Figures 1-6 As shown, a tuned mass inertia damper includes a mounting support portion, a first rigid spring 13 portion, a second rigid spring 12 portion for transmitting axial motion of the structure, an inertia damping parallel portion for consuming energy and amplifying the tuned mass, a counterweight box 16 portion, and a T-plate portion for connecting the mounting support portion and the counterweight box 16 portion.

[0043] The counterweight box 16 is used to accommodate the counterweight. Several square sliders are installed at the center of the steel plate below the counterweight box 16. The floor slab is equipped with embedded guide rails 19 that cooperate with the counterweight guide rail slider mechanism 18. The counterweight box 16 is 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 force for the reciprocating motion of the counterweight box 16. The counterweight box 16 is equipped with lifting lugs 17 to facilitate lifting.

[0044] The installation support part is connected to the building structure floor; the installation support part includes angle steel 2, baffle 1 and round 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 structure of the building through anchor bolts; the round tube 3 is welded to the baffle 1.

[0045] The T-shaped plate 15 has a hole, and the hole position corresponds to the counterweight box 16. The T-shaped plate 15 connects the 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] A first guide rod 14-1, a first intermediate plate 9, and a first bottom plate 10-1 are provided at the first rigid spring 13. A first rigid spring 13 is 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 mounting support part. The first guide rod 14-1 passes through the hole of the first intermediate plate 9. 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 parallel part of the inertia damping is realized by the ball screw 5. One end of the ball screw 5 pair partially passes through the circular tube 3. The flange 6 is welded to the end of the circular tube 3. The flange 6 is used to fix the outside of the rotating nut of the ball screw 5 element. The other end of the circular tube 3 is connected to the mounting support. A flywheel is installed on the rotating nut. The rotating nut is in the shape of a stepped cylinder. A closed ball track containing balls is set inside the rotating nut. When the screw moves horizontally, the balls will circulate within the screw thread and the bearing track, driving the rotating nut and flywheel to rotate. The flywheel is fixedly connected to the rotating nut and does not rotate relative to each other. The flywheel has a certain mass and radius and can be disassembled and replaced according to actual needs. The ball screw 5 element adjusts the inertia of the counterweight box 16 by changing the lead of the ball screw pair and the size of the flywheel.

[0048] The damping of the parallel inertial capacitance damping section is provided by a magnetorheological damping element 7, whose damping fluid is a conductive, oil-based magnetorheological fluid. The cylinder of the magnetorheological damping element 7 is secured by a clamp 4, the other end of which is fixed to a circular tube 3 connected to the mounting support. The damping capacity of the magnetorheological damping element 7 can be adjusted according to the required current flow, providing a suitable and 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 11. The first intermediate plate 9 is connected to the linear circular guide 11 through the flange 6 to achieve the parallel effect of the inertia damping parallel part.

[0050] The first guide rod 14-1 is passed through the middle of the linear circular guide rail 11 of the inertia-capacitance 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-plate, and the other end is fixed to the first base 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 further connected in parallel with the second rigid spring 12.

[0052] A second guide rod 14-2 is provided on one side of the first guide rod 14-1. A second rigid spring 12 is sleeved onto the second guide rod 14-2. A second intermediate plate 8 is sleeved onto the second guide rod 14-2. The second guide rod 14-2 passes through the second intermediate plate 8 and is provided with a second bottom plate 10-2 at its end. Second rigid springs 12 are provided between the second intermediate plate 8 and the second bottom plate 10-2, as well as 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 inertia container are parallel to each other.

[0054] During use, the tuned mass inertia damper is installed within a high-rise structure to control, but not limited to, first-order structural vibrations. When the high-rise structure responds dynamically to external excitation, and the frequency of the external excitation approaches the structure's natural frequency, the structure resonates and experiences significant displacement at the natural vibration mode. During vibration, the counterweight box 16 in the device deviates from its stationary position and slides within the track. At this point, the counterweight box 16 drives two rigid springs to deform under the constraints of guide rods parallel to the track. The combined force of the rigid springs is transmitted to the mounting support via the guide rods. The first rigid spring 13 drives the magnetorheological damping element 7 and the ball screw 5 in linear reciprocating motion parallel to the track, causing the balls to move within the screw and ball bearings, driving the ball bearings and flywheel to rotate, generating inertial forces. When energized, the magnetorheological damping element 7 generates an appropriate damping force. When the mass, the elastic force, and the damping force reach optimal control parameters, the damper's natural frequency aligns with the high-rise building's first-order vibration frequency, effectively controlling the high-rise structure's low-order modes.

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

[0056] Step 1: Perform a preliminary analysis of the main floor structure to obtain modal and vibration shape results and determine the installation location of the tuned mass inertia damper;

[0057] Step 2: After determining the installation position, establish the kinematic equation to derive the displacement response transfer function of the main structure. Then establish the optimization equation with the H2 norm l of the displacement response transfer function of the main structure as the optimization target.

[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 target l according to the requirements, by giving the tuning mass ratio μ t and damping ratio ζ in The parameter optimization of RIDTMD is realized by stepwise parameter sweeping. Where I represents the identity matrix; M is the mass matrix of the additional tuning mass and inertia, K is the stiffness matrix; C is the damping matrix, M R is the mass matrix with only the tuning mass added; 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 Describe the contribution of the state to the output for the output matrix;

[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; in is the damping ratio;

[0067] Step 4: Solve the optimization design equation to obtain the tuning mass ratio μ t , damping ratio ζ in The design parameter values ​​of are taken, and the tuning mass, damping coefficient, inertia coefficient, first rigid spring stiffness and second rigid spring stiffness are determined by deriving these two parameters;

[0068] Step 5: Use time history analysis to verify the obtained design parameters. If the control effect meets the requirements, the parameter design is completed. Otherwise, adjust the tuning mass ratio μ t and damping ratio ζ in Repeat steps 3 and 4 in the value range until the control effect is satisfied.

[0069] The present invention has the following advantages:

[0070] 1. Extending the characteristic of increased apparent mass of the inertial container to the tuned shock (vibration) reduction device can achieve lightweight horizontal shock (vibration) reduction.

[0071] 2. Under external excitation, when the main structure induces the counterweight box 16 to undergo tuned vibration, the parallel component 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 component will be almost 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 displacement of the magnetorheological damper.

[0072] 3. The parallel components can better realize the energy efficiency of the magnetorheological damping element 7 and the role of the ball screw 5 in amplifying the tuning quality, thereby enhancing the control effect of the entire device.

[0073] 4. The movement of the counterweight box 16 is transmitted to the damper and inertia container through the first intermediate plate 9. The related design of the first intermediate plate 9 and the first rigid spring 13 can play a stabilizing and buffering role, making the movement of the first intermediate plate 9 more stable and reducing the impact of the counterweight box 16 on the damper and inertia container; 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 inertial damper is balanced, which can respond to external excitation more stably and reliably, thereby improving the shock (vibration) reduction effect and enhancing the vibration control of the tuned mass inertial damper on the building structure.

[0075] 6. The structure is simple, directly corresponds to the mechanical principle diagram, and is easy to adjust. The damper performance parameters 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 present invention employs a design method that uses the H2 norm l of the displacement response transfer function of the primary structure as the optimization target for the relevant parameters. This method, based on an improved fixed-point theory approach, simplifies the multiple parameter optimization design problem of RIDTMD into the optimization problem of two parameters: mass and damping. This allows for a relatively accurate and rapid determination of the relevant RIDTMD design parameters.

[0077] The above embodiments are preferred implementation modes of the present invention, but the implementation modes of the present invention are not limited to the above embodiments. Any other changes, modifications, substitutions, combinations, and simplifications that do not deviate from the spirit and principles of the present invention should be considered as equivalent replacement methods and are included in the scope of protection of the present invention.

Claims

1. A tuned mass inertia damper, characterized in that: It includes a mounting support portion, a first rigid spring portion, a second rigid spring portion for transmitting axial motion of the structure, an inertia damping parallel portion for absorbing energy and amplifying the tuning mass, a counterweight box portion, and a T-plate portion for connecting the mounting support portion and the counterweight box portion. The counterweight box is used to accommodate the counterweight block, and the first rigid spring and the second rigid spring provide elastic force for the reciprocating motion of the counterweight box; The installation support part is connected to the floor slab; the installation support part includes angle steel, baffle and round tube, the angle steel is connected to the baffle, and the angle steel is connected to the main structure of the building; the round tube is welded to the baffle; The T-shaped plate is opened with a hole, the hole position corresponds to the counterweight box, the T-shaped plate is connected to the counterweight box, and the first guide rod and the second guide rod are connected to the corresponding center position on the other side of the T-shaped plate, the first guide rod is used to place the first rigid spring, and the second guide rod is used to place the second rigid spring; A first guide rod, a first intermediate plate, and a first bottom plate are provided at the first rigid spring. A first rigid spring is provided between the first intermediate plate and the first bottom plate, and between the first intermediate plate and the counterweight box. The first intermediate plate is fixed to the mounting support portion. The first guide rod passes through the hole of the first intermediate plate. The first bottom plate is fixedly connected to the end of the first guide rod. The inertia of the parallel part of the inertia damping is realized by a ball screw. One end of the ball screw pair partially passes through a round tube. A flange is welded to the end of the round tube. The flange is used to fix the outside of the rotating nut of the ball screw element. The other end of the round tube is connected to the mounting support part. A flywheel is installed on the rotating nut. The ball screw element adjusts the inertia of the counterweight box by changing the lead of the ball screw pair and the size of the flywheel. The damping of the parallel part of the inertial capacitance damping is achieved by a magnetorheological damping element. The damping fluid is a conductive oil-based magnetorheological fluid. The cylinder of the magnetorheological damping element is fixed by a clamp, and the other side of the clamp is fixed to the round tube connected to the mounting support part. The other end of the ball screw pair and the push rod end of the magnetorheological damping element are both fixed to the first intermediate plate on the linear circular guide rail. The first intermediate plate is connected to the linear circular guide rail through a flange to achieve the parallel effect of the inertia damping parallel part. The linear circular guide rail of the inertia-capacitance damping parallel part passes through the first guide rod, and the linear circular guide rail moves horizontally along the first guide rod. The first rigid spring is sleeved on the first guide rod. One end of the first guide rod is fixed to the T-plate, and the other end is fixed to the first base plate, forming a first rigid spring part. A series part is formed between the inertia damping parallel part and the first rigid spring part, and the series part is further connected in parallel with the second rigid spring; A second guide rod is provided on one side of the first guide rod, a second rigid spring is sleeved on the second guide rod, a second intermediate plate is sleeved on the second guide rod, the second guide rod passes through the second intermediate plate and a second bottom plate is provided at the end thereof; a second rigid spring is provided between the second intermediate plate and the second bottom plate and between the second intermediate plate and the counterweight box; The sliding direction of the counterweight, the first guide rod, the second guide rod, the first rigid spring, the second rigid spring, the damper and the inertia container are parallel to each other.

2. The tuned mass inertia damper according to claim 1, characterized in that: The total stiffness, length and deformation of the first rigid springs between the first intermediate plate and the counterweight box 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 box and between the second intermediate plate and the second bottom plate are respectively the same.

3. The parameter design method of a tuned mass inertia damper according to claim 1 or 2, characterized in that: The following steps are included: Step 1: Perform a preliminary analysis of the main floor structure to obtain modal and vibration shape results and determine the installation location of the tuned mass inertia damper; Step 2: After determining the installation position, establish the kinematic equation to derive the displacement response transfer function of the main structure, and then establish the displacement response transfer function of the main structure. H 2-norm l The optimization equation as the optimization objective; Kinematic equations: ; Displacement response transfer function: ; ； ； ； Step 3: Determine optimization goals based on needs l , by giving the tuning mass ratio μ t and damping ratio ζ in The parameter optimization of RIDTMD is realized by using step-by-step parameter scanning; I represents the identity matrix; M is the mass matrix of the additional tuning mass and inertia, K is the stiffness matrix; C is the damping matrix, M R is the mass matrix with only the tuning mass attached; A is the state matrix, describing the dynamic characteristics of the system, E is the input matrix, describing the impact of the input on the state, C S Describe the contribution of the state to the output for the output matrix; Optimization equation: ; ； ； in H is the frequency response function; i is the imaginary unit; ω represents the frequency of 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 , damping ratio ζ in The design parameter values ​​of are taken, and the tuning mass, damping coefficient, inertia coefficient, first rigid spring stiffness and second rigid spring stiffness are determined by deriving these two parameters; Step 5: Use time history analysis to verify the obtained design parameters. If the control effect meets the requirements, the parameter design is completed. Otherwise, adjust the tuning quality ratio. μ t and damping ratio ζ in Repeat steps 3 and 4 in the value range until the control effect is satisfied.

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