Curved surface base tuned mass damping device capable of adaptively adjusting mass and rigidity

Abstract

The invention discloses a curved-surface base tuned mass damping device capable of adaptively adjusting mass and rigidity, and belongs to the technical field of civil engineering damping. The defects that an existing TMD device is tedious in quality adjustment, high in shear damage risk, narrow in rigidity adjustment and control range and low in energy dissipation efficiency are overcome. The device comprises a curved-surface base, a tuning solid mass part, a tuning liquid damping device, an independent water tank, a water pump, an industrial personal computer and a connecting device. The variable curve design of the curved surface base improves energy dissipation, and the vibration period of the rigidity adaptive structure is flexibly adjusted through the warping effect. The tuning solid mass part is arranged in the curved-surface base and can move freely, the tuning liquid damping device is fixed to the top of the tuning solid mass part, and the mass of tuning liquid is adjusted between the tuning liquid damping device and the independent water tank through the water pump. The acceleration sensor can provide the vibration acceleration of the device in real time, and the industrial personal computer can monitor the acceleration in real time to reflect the vibration change of the device. The connecting devices are symmetrically arranged on the periphery of the tuning solid-state mass component, and each connecting device is composed of a universal hinge for connection, a long straight rod, a nitrogen spring, a sleeve and a buckling induction band gap double-layer rod system mechanism. The universal hinge eliminates the shearing effect, the long straight rod can provide effective positive stiffness, the sleeve ensures that the nitrogen spring and the long straight rod are coordinated and matched without interference, and the nitrogen spring and the buckling induction band gap double-layer rod system mechanism are combined to flexibly adjust the stiffness. The method can be used for seismic resistance and shock absorption of large building structures such as ultrahigh buildings.

Description

Technical Field

[0001] This invention belongs to the field of seismic resistance and vibration reduction and disaster prevention and mitigation in civil engineering. Specifically, it relates to a curved base tuned mass vibration reduction device with adaptive adjustable mass and stiffness, suitable for seismic resistance and vibration reduction of high-rise building structures and industrial infrastructure. Background Technology

[0002] Tuned mass dampers (TMDs), as a passive vibration reduction device, have been widely used in the field of civil engineering. Their mechanism is to tune the device to the same frequency as the basic frequency or specified frequency of the main structure in a specified direction. Under external excitations such as strong winds or earthquakes, the tuning vibration of the mass block fully consumes the kinetic energy of the main structure, thereby reducing the dynamic response of the structure, improving the dynamic reliability of the structure, and ensuring its safety.

[0003] Traditional passive TMDs are the most classic and widely used tuned dampers, typically consisting of a mass block, spring, and viscous damper. Their mechanism is well-defined, the technology is mature, reliability is high, they require no external power source, and maintenance costs are relatively low. However, traditional TMDs are sensitive to frequency tuning accuracy. Once installed, the frequency and damping ratio are fixed, making them unable to adapt to changes in structural characteristics or loads. This can easily lead to "detuning" in actual use, and they usually occupy a significant amount of space and mass.

[0004] Multi-directional pendulum TMDs are designed to control multi-directional vibrations of structures (such as two horizontal directions and torsion). They include simple pendulum TMDs and spherical pendulum / compound pendulum TMDs. Simple pendulum TMDs are suspended by cables, and their oscillation period depends on the pendulum length. They can be used for horizontal vibration control, but due to limitations in practical period requirements, the pendulum length is often too short, making them difficult to implement in actual engineering. Long-term use also leads to wear on the pendulum cables. Spherical pendulum / compound pendulum TMDs can oscillate in any horizontal direction, and some TMDs can also provide torsional control. However, their actual vibration reduction rate is often lower than ideal, and their engineering practicality urgently needs improvement.

[0005] Tuned liquid dampers (TLDs) utilize the sloshing of liquid within a container to provide damping mass and resistance. Tuned liquid column dampers utilize liquid oscillation within a rectangular container, generating damping through perforated baffles. Tuned liquid (sloshing) dampers are often rectangular shallow water tanks where the liquid sloshes freely. The liquid acts as both the mass and damping element, resulting in a relatively simple construction. They are often integrated into functional components such as building water tanks, saving on additional mass. The damping efficiency of TLDs is generally lower than that of solid mass TMDs. They are sensitive to liquid depth (frequency) and may exhibit wave breaking, strong nonlinear effects, and require consideration of waterproofing, spill prevention, and corrosion protection.

[0006] A multi-tuned mass damper (TMD) replaces a large TMD with multiple small TMDs at slightly different frequencies. It is constructed as multiple small mass blocks, each tuned to a frequency near but slightly different from the main structure frequency, forming a wider control band. It is more robust to changes in the main structure frequency and load frequency components; the failure of a single mass block does not affect the overall function, and its layout is more flexible. The disadvantages are higher engineering costs, more complex design, manufacturing, and tuning, and a total mass that may be slightly larger than an equivalent single TMD.

[0007] Semi-active and hybrid TMDs introduce controllable elements to enhance adaptability based on passive TMDs. Semi-active TMDs maintain traditional mechanical structures but use adjustable dampers (such as magnetorheological or electrorheological dampers) or adjustable stiffness devices. Parameters are adjusted in real-time based on the structural response using sensors and control algorithms. This structure exhibits superior vibration reduction performance compared to passive TMDs, is insensitive to detuning, and has extremely low energy consumption (only required for control valves or circuits), making it a current research and application hotspot. Hybrid TMDs add an active actuator to the passive TMD. The active force and the passive inertial force of the TMD work together. Theoretically, this can achieve optimal control performance, but it requires significant external energy, is complex, and has high cost and maintenance requirements.

[0008] In summary, existing TMD devices have the following shortcomings: 1) During normal use, the main cycle or frequency of a structure will inevitably change due to factors such as temperature, humidity, changes and degradation of material properties, and adjustments to some components and functions. In some cases, the rate of change can even reach ±15% or more. The frequency of a traditional TMD (Transformer Motion Detector) is adjusted through its inherent mass and springs, and is consistent with the initially set structural frequency. However, it cannot guarantee consistency with the real-time frequency of the structure, nor can it be flexibly adjusted. It is impossible to quickly rematch the structural frequency by adjusting the mass or spring stiffness of the TMD. Replacing the mass is cumbersome and costly. Therefore, its vibration reduction efficiency and effect may not meet the expected results, and its performance may not meet the actual vibration reduction requirements in some cases.

[0009] 2) If the structure is damaged under strong wind or strong earthquake, its equivalent stiffness will decrease, the main period will increase and the frequency will decrease. At this time, the frequency of TMD is still consistent with the initial setting value or is difficult to adjust in time, so its actual performance will also decrease, making it difficult to guarantee its vibration reduction effect, and may even lead to further damage or aggravation of the structure.

[0010] 3) The mass block motion trajectory of traditional TMD is linear or fixed curve, which is difficult to adapt to the multi-directional energy dissipation requirements under complex vibration scenarios. In addition, the connecting parts between the base and the mass block are prone to damage due to concentrated shear force, which shortens the service life of the device. 4) The vibration reduction direction of traditional TMD is fixed. Generally, a TMD can only achieve single-direction tuning vibration reduction. Vibration reduction in other directions requires additional TMD or other vibration reduction devices, resulting in excessive cost and low economic benefits.

[0011] To address the aforementioned issues, there is an urgent need for a TMD device that is mass-adjustable, reasonably constrained, has optimizable stiffness, and can continuously eliminate the risk of damage, in order to improve the adaptability and reliability of damping devices.

[0012] In recent years, novel materials, structures, or configurations from other fields have provided technical inspiration for addressing the shortcomings of traditional TMD devices. To achieve flexible period adjustment of the TMD device, this patent further innovates by proposing the following novel structures or materials: 1. Curved Base: The core of this component is a continuous, smooth parabolic bottom structure with a non-linearly varying radius of curvature along the direction of mass component movement, possessing both load-bearing and energy-dissipating core functions. In this patent, this novel structure is mainly used to increase the vibration period of the device. On the one hand, it can precisely guide the tuned solid mass component to complete multi-track horizontal movement, significantly widening the energy dissipation path of vibration, while further enhancing energy consumption during vibration through its own warping effect; on the other hand, as the basic load-bearing structure of the device, it provides stable installation support for all components, ensuring the overall stability of the device's movement from a structural perspective and avoiding problems such as offset and jamming during vibration. 2. Tuned Liquid Damping (TLD) Device: Using tuned liquid as the core mass adjustment component, a closed-loop injection and drainage circuit is formed by water pipes and flow control valves to achieve flexible control of the total mass of the device. In this patent, the main function of this component is to adjust the vibration period of the device by injecting or draining water. The core feature is continuous mass adjustment without disassembly. No replacement or disassembly of mass components is required; continuous, stepless adjustment of the device's mass is achieved solely through precise control of liquid injection and discharge via a flow control valve. Operation is convenient and the control precision is high, enabling rapid response to dynamic changes in the vibration characteristics of the main structure. Simultaneously, the liquid generates sloshing viscous energy during vibration, which assists in attenuating vibration energy during mass tuning, combining dynamic mass tuning and passive viscous energy dissipation functions. 3. Nitrogen Spring: An elastic component using high-pressure nitrogen as the working medium, its core advantages are small size, high elasticity, long stroke, stable force, and long lifespan. In this patent, it serves as the core component for stiffness adjustment, possessing variable positive stiffness output capability. Continuous, stepless stiffness adjustment is achieved through the extension and retraction of the piston rod, with a wide stiffness adjustment range and fast response speed. It can cooperate with other stiffness components within the device to form a composite stiffness system, providing stable and reliable positive stiffness support for the device's frequency tuning, ensuring the accuracy and stability of frequency tuning. 4. Buckling-Induced Bandgap Double-Layer Rod Mechanism: Utilizing a hyperbolic beam-type honeycomb unit cell integral molding structure, it consists of an upper pressure plate, hyperbolic beams, reinforcing walls, horizontal beams, and a lower pressure plate. The hyperbolic beams are uniformly arranged circumferentially along the unit cell, with rounded transitions at all connections, resulting in high structural strength and good deformation stability. In this patent, it effectively reduces stiffness while enabling multi-directional bandgap tuning for large deformation reconstruction. It combines reconfigurability with broadband vibration suppression capabilities, overcoming the limitations of traditional bandgap structures with fixed bandgap and narrow vibration suppression frequency ranges. Within a wide frequency range of 0.1Hz to 50Hz, it can change its geometric configuration through compression deformation, dynamically expanding the bandgap distribution and significantly reducing vibration transmittance. Furthermore, it can withstand significant compression deformation and maintain a stable configuration, providing crucial structural support and broadband vibration suppression assistance for device stiffness adjustment.

[0013] For vibration-damping structures, installing a tuned mass damper (TMD) with a period perfectly matched to its theoretical period can effectively reduce vibration and suppress structural vibration. However, the natural period of the structure will fluctuate due to factors such as temperature and humidity. Given the shortcomings or limitations of existing vibration-damping technologies, the innovative approach of this patent is as follows: considering that the square of the natural period is directly proportional to the mass and inversely proportional to the stiffness, the period can be dynamically matched to the structural period by flexibly increasing or decreasing the mass or stiffness of the TMD. To increase the TMD period, the mass can be increased by injecting water into the tuned liquid damper, or the stiffness can be reduced by using a buckling-induced bandgap double-layer rod mechanism. Conversely, to reduce the TMD period, the mass can be reduced by draining water from the tuned liquid damper, or the stiffness can be increased by using nitrogen springs and a variable-curve base.

[0014] The specific implementation path of frequency adjustment in this invention is as follows: In the initial stage, the mass of the tuning liquid is adjusted by a flow control valve according to the inherent frequency of the structure, while the initial stiffness of the nitrogen spring and the initial state of the negative buckling induced bandgap double-layer rod mechanism are set to complete frequency matching; when the structural frequency changes, the mass of the tuning liquid is increased or decreased in real time, which simultaneously triggers the extension and contraction of the nitrogen spring and the compression deformation of the buckling induced bandgap double-layer rod mechanism, dynamically adjusting the composite stiffness and bandgap distribution to ensure that the device frequency and the structural frequency are continuously matched, thereby achieving wide-frequency and efficient vibration reduction. Summary of the Invention

[0015] This invention relates to a tuned mass damping device for a curved base with adaptively adjustable mass and stiffness. Its purpose is to overcome the shortcomings of existing TMD devices, such as cumbersome mass adjustment, high risk of damage, narrow stiffness control range, and low energy dissipation efficiency, and to provide a tuned mass damping device for a curved base with adaptively adjustable mass and stiffness.

[0016] The main design concepts of this invention are as follows: 1. Modular design concept: The device is divided into four functional modules: load-bearing base, core mass, connection adjustment, and damping auxiliary. Each module is independent yet works in concert. The curved base is the load-bearing module, the tuned solid mass component and tuned liquid damping device are the core mass module, the connection device is the stiffness adjustment module, and the water pipe and flow control valve are the damping auxiliary adjustment module. Modular design ensures the functional specificity of each component, facilitates installation, maintenance, and standardized adaptation of components, and reduces the overall structural design complexity. 2. Precise mechanical adaptation concept: With "real-time matching of the device's natural frequency with the vibration frequency of the main structure" as the core mechanical objective, the device's frequency is precisely tuned by continuously adjusting the mass and dynamically controlling the stiffness, utilizing the mechanical principle that "period is positively correlated with mass and negatively correlated with stiffness" through continuous adjustment of mass and dynamic control of stiffness. At the same time, the device is subjected to balanced forces by optimizing the component size ratio and arrangement, avoiding local stress concentration, and achieving dual adaptation of structural mechanics and vibration reduction mechanics. 3. Multi-mechanism collaborative energy dissipation concept: Breaking through the limitations of traditional TMD's single inertial energy dissipation, it integrates four energy dissipation mechanisms: inertial energy dissipation of mass components, viscous energy dissipation of tuned liquids, warping effect energy dissipation of curved bases, and bandgap attenuation energy dissipation of buckling-induced bandgap double-layer rod mechanism. This multi-path dissipation of the main structure's vibration energy significantly improves vibration reduction efficiency. 4. Full life-cycle stability concept: Ensuring the long-term service stability of the device from two dimensions: structural motion characteristics and material selection. Structural innovation eliminates adverse forces such as shear forces that can easily damage components. Simultaneously, high-strength, high-wear-resistant, and deformation-resistant materials are selected, and the fit of kinematic pairs is optimized to reduce the risk of component wear and deformation, extend the device's service life, and reduce maintenance costs.

[0017] The functions of other components in this invention are described as follows: 1. Tuned solid mass component: As the core basic mass carrier of the device, it combines mass stability and compatibility. Its own mass provides the basic inertial force for vibration reduction, and it can be seamlessly combined with the tuning liquid to form a continuously variable total mass system. It can achieve gradient adjustment of the device's mass without changing its own structure, adapting to the mass requirements of different vibration reduction conditions; 2. Accelerometer (dedicated to TLD frequency monitoring): In this patent, this component is specially designed for TLD frequency monitoring. The filtering algorithm matches the vibration characteristics of the TLD system, effectively eliminating environmental noise and vibration interference from other components of the device, capturing only the effective vibration frequency of the TLD system and the tuned solid mass component, making the monitoring highly targeted; it also has the function of acquiring multiple parameters such as frequency, acceleration, vibration amplitude, and motion trajectory, providing core frequency data for water volume control and auxiliary basis for the industrial control computer to judge the working status of the device; 3. Independent water tank: A dedicated water tank is installed independently next to the TMD device to provide an independent, sealed, and measurable dedicated water tank for the tuning liquid. Using storage and supply carriers, a stable supply and recovery of liquid is ensured during the injection and drainage process, eliminating the uncertainty of external water sources. At the same time, it provides a standardized liquid storage and transportation foundation for the precise water volume control of the industrial control computer, allowing the input and output of water volume to be accurately measured, controllable and adjustable; 4. Industrial control computer: A dedicated industrial control computer is installed next to the TMD device to receive the TLD measured frequency data from the acceleration sensor, the liquid level and volume data of the independent water tank, and combine it with the inherent frequency data of the main structure. Through the built-in algorithm, it performs real-time analysis and calculation to accurately determine the amount of water to be input or output to the TMD device, and sends precise control commands to the flow control valve and water pump to realize the automatic, precise and dynamic adjustment of water volume, so that the total mass of the TMD device and the vibration characteristics of the main structure are always optimally matched, maximizing the vibration reduction efficiency; 5. Water pump: In this patent, the water pump is used to drive, regulate and stabilize the damping fluid inside the vibration reduction device, realizing the active adjustment of the mass, damping and stiffness of the vibration reduction system, thereby improving the vibration reduction effect and self-adaptive capability of the device under complex working conditions. 6. Universal Joint for Connection: Develop a universal joint connection structure that enables multi-directional rotation, offsetting shear forces at the structural level and ensuring the structural integrity and movement flexibility of the connection points. This component features 360° free rotation without dead angles, low rotational damping, and high load-bearing capacity. It can adapt to and tune any movement direction of solid mass components in real time, eliminating shear forces at their source. Furthermore, the structure exhibits excellent wear resistance and fatigue resistance, allowing for long-term stable operation without frequent maintenance. 7. Sleeve: Develop a dedicated fixed guide sleeve employing a high-precision coaxial guide structure. Its smooth inner wall and excellent wear resistance provide strong fixing and high guiding accuracy for the nitrogen spring and long straight rod, without generating additional movement resistance. Simultaneously, its compact structure allows for seamless integration with other components without occupying additional installation space. It provides dual constraints on the nitrogen spring and long straight rod, ensuring their movement accuracy and structural stability, thereby guaranteeing the accuracy of overall stiffness adjustment and the smoothness of movement of the device.8. Long Straight Rod: Developed long straight rod components using high-rigidity, deformation-resistant materials, exhibiting excellent axial stiffness and strong bending resistance. The length can be customized as needed, effectively extending the travel of the mass component without increasing the device's volume. It serves both structural support and travel extension functions, cooperating seamlessly with sleeves and nitrogen springs. This enhances the overall structural strength and load-bearing capacity of the connecting device while extending the travel of the mass component, expanding the device's vibration damping adaptability from both structural and motion perspectives. 9. Water Pipe: Developed dedicated sealed water pipes integrating a high-precision flow control valve. Made with high-sealing, anti-aging materials, it is leak-free and has excellent vibration resistance. The flow control valve is a high-precision stepless adjustment type, offering high control accuracy and fast response speed, enabling real-time precise control of liquid flow. The valve body and water pipe are integrated, facilitating installation and maintenance. It is suitable for long-term operation in complex vibration environments, ensuring safe and efficient delivery and precise flow control of the tuned liquid, guaranteeing the accuracy and stability of mass adjustment, and allowing for precise adjustment of the combination ratio of the tuned liquid and solid mass component as needed.

[0018] Further integrating the above innovative ideas and component functions, this patent proposes a curved base tuned mass damping device with adaptively adjustable mass and stiffness: The adaptively adjustable mass and stiffness curved base tuned mass damping device has a core structure comprising multiple components, specifically: curved base (1), tuned solid mass component (2), tuned liquid damping device inner wall (3), tuned liquid (4), universal joint for connection (5), buckling-induced bandgap double-layer rod mechanism (6), sleeve (7), nitrogen spring (8), long straight rod (9), water pipe (10), water pump (11), acceleration sensor (12), independent water tank (13), and industrial control computer (14). The curved base (1) is a cavity structure with an open top. The tuned solid mass component (2) serves as the core mass carrier and is horizontally installed at the bottom of the cavity. Its bottom is in contact with the variable curve inner wall of the curved base (1) and can move horizontally along the inner wall in multiple trajectories. The tuned liquid damping device consists of the inner wall (3) of the tuned liquid damping device and the tuned liquid (4). The inner wall (3) of the tuned liquid damping device is fixedly installed on the top of the tuned solid mass component (2) to form a closed liquid containment space. The tuned liquid (4) fills the space. One end of the water pipe (10) is inserted into the tuned liquid damping device from above, and the other end of the water pipe (10) extends to the outside of the curved base (1) and is connected to a connection port of the water pump (11). Another water pipe (10) is connected to the other connection port of the water pump (11) and the independent water tank (13). An accelerometer (12) is arranged on the side wall of the tuned solid mass component (2), and an independent water tank (13) and an industrial control computer (14) are installed near the overall device. At least four sets of connecting devices are required, symmetrically arranged between the inner wall of the curved base (1) and the side wall of the tuned solid mass component (2), with the installation height consistent with the center of gravity height of the tuned solid mass component (2). Each set of connecting devices adopts a series connection method of "universal hinge (5) for connection - buckling-induced bandgap double-layer rod mechanism (6) - nitrogen spring (8) - long straight rod (9) - universal hinge (5) for connection". The specific connections are as follows: one end of a universal joint (5) is fixedly connected to the side wall of the curved base (1), and the other end is fixedly connected to one side of the buckling-inducing bandgap double-layer rod mechanism (6). The other side of the buckling-inducing bandgap double-layer rod mechanism (6) is fixedly connected to the cylinder of the nitrogen spring (8). One end of the long straight rod (9) is fixedly connected to the piston rod of the nitrogen spring (8), and the other end is connected to another universal joint (5). The other universal joint (5) is fixedly connected to the inner wall of the curved base (1). The sleeve (7) is fitted on the outside of the nitrogen spring (8) and the long straight rod (9). The inner wall of the sleeve (7) is fitted and fixed to the outer wall of the cylinder of the nitrogen spring (8), while forming a guiding constraint on the long straight rod (9), realizing the relative fixation and motion guidance of the nitrogen spring (8) and the long straight rod (9).

[0019] The bottom of the curved base (1) is a continuous smooth parabola, and the radius of curvature changes nonlinearly along the direction of motion of the tuned solid mass component (2) (gradual change rate ≤ 1 / 5). The ratio of its radius of curvature to the equivalent diameter of the mass component is 1.2~2.0, which can guide the mass component to perform multi-track motion and ensure motion and structural stability. Both the curved base (1) and the tuned solid mass component (2) are made of high-strength ductile iron or low-alloy high-strength steel. The ratio of the yield strength to the elastic modulus of the material is not greater than 1 / 800, and the elongation is not less than 15%, ensuring load-bearing strength and impact resistance. The ratio of the height to the equivalent diameter of the tuned solid mass component (2) is 0.4~0.8. The inner diameter of the water pipe (10) used in the tuned liquid damping device is 1 / 30 to 1 / 20 of the equivalent diameter of the damping device, which can ensure smooth liquid flow and avoid impact disturbance; the water pipe (10) is equipped with a high-precision electromagnetic flow control valve to achieve precise control of liquid quality; the mass ratio of the tuned liquid (4) to the unloaded mass of the tuned solid mass component (2) is 0.2 to 0.3, and the total mass of the device can be continuously adjusted within the range of 1.2 to 1.3 times the unloaded mass. The height ratio of the inner wall (3) of the tuned liquid damping device to the height of the tuned solid mass component (2) is 0.5 to 0.7, and the wall thickness ratio of the inner wall (3) to the wall thickness of the tuned solid mass component (2) is 0.6 to 0.9; The length of the nitrogen spring (8) cylinder used in the connecting device is 1.5~2.5 to the length of the buckling-induced gap double-layer rod mechanism (6), and the inner diameter of the sleeve (7) is 1.05~1.15 to the outer diameter of the nitrogen spring (8) cylinder, ensuring that the components work together without interference; the connecting component adopts a ball joint universal joint, the ratio of the pin diameter to the hinge seat hole diameter is 0.95~0.98, and the ratio of the radial clearance of the rotating pair to the pin diameter is 1 / 500~1 / 300, which can realize 360° free rotation and effectively eliminate shear force; the universal joint pin is made of bearing steel with a hardness of not less than HRC58, and the hinge seat is made of wear-resistant bronze alloy with a friction coefficient of less than 0.15, which reduces rotational wear and extends service life; The buckling-induced bandgap double-layer rod system (6) adopts a hyperbolic beam honeycomb unit cell structure, which is integrally formed by an upper pressure plate, hyperbolic beams, reinforcing walls, horizontal beams and lower pressure plate; the number of hyperbolic beams is 4 to 6 and they are evenly arranged along the circumference of the unit cell, the included angle between adjacent hyperbolic beams is 60° to 90°, the ratio of the thickness of the reinforcing wall to the thickness of the hyperbolic beam is 1.2 to 1.5, and the connection adopts a rounded transition to ensure the structural strength and deformation stability; the structure is made of beryllium bronze or titanium alloy, with an elastic modulus of 100 to 150 GPa and a yield strength greater than 800 MPa, which is suitable for large deformation and bandgap tuning requirements; The cylinder body of the nitrogen spring (8) is made of ultra-high strength alloy steel with a yield strength ≥1200MPa and an elastic modulus ≥200GPa, and the piston rod is made of nitrided alloy structural steel with a surface hardness ≥HV600; the ratio of the length of the long straight rod (9) to the length of the cylinder body of the nitrogen spring (8) is 1.0~1.5, and the ratio of the axial stiffness to the positive stiffness value of the nitrogen spring (8) is less than 0.2; the stiffness ratio of the buckling-induced bandgap double-layer rod mechanism (6) to the nitrogen spring (8) is 0.6~0.9, and the combined stiffness adjustment range formed by the two is at least -30~50kN / m; The acceleration sensor (12) is used to collect the vibration response signal of the shock absorber; the independent water tank (13) has a volume of about 1 / 5 of the overall volume of the shock absorber and is connected to the fluid circuit of the TLD device to replenish or adjust the liquid capacity in the TLD device; the industrial control computer (14) has a volume of about 1 / 100 to 1 / 200 of the overall volume of the shock absorber and is electrically connected to the control unit of the acceleration sensor (12) and the TLD device to receive the signal from the acceleration sensor (12) and control the damping parameters of the TLD device according to the preset algorithm.

[0020] The pin of the universal joint (5) for connection is clearance-fitted with the hinge seat, the piston rod of the nitrogen spring (8) is sliding-fitted with the cylinder, and the long straight rod (9) is sliding-fitted with the inner wall of the sleeve (7). The angle between the adjacent central axes of the four sets of connection devices is 90°, and the central axis of each set of connection devices is in the same horizontal plane as the center of gravity of the tuned solid mass component (2). The nitrogen spring (8) and the buckling-induced bandgap double-layer rod system (6) in the connection devices of different horizontal directions adopt differentiated size design.

[0021] Compared with the prior art, the advantages of the present invention are as follows: 1. By using a tuned liquid damping system, the total mass of the device can be adaptively and continuously adjusted within a range of 1.2 to 1.3 times the unloaded mass through water pipe injection or discharge of tuned liquid. This allows for rapid adaptation to changes in the vibration characteristics of the main structure caused by changes in load and service life. There is no need to disassemble or replace the mass block, making the operation convenient and cost-effective. 2. The variable positive stiffness is provided by a nitrogen spring, and the adjustable negative stiffness is provided by a buckling-induced bandgap double-layer rod mechanism. The two form a composite stiffness component, and the ratio of the absolute value of the negative stiffness of the buckling-induced bandgap double-layer rod mechanism to the positive stiffness value of the nitrogen spring can be adjusted in the range of 0.6 to 0.9. Combined with the auxiliary stiffness of the long straight rod, the natural frequency of the device can be precisely tuned to ensure real-time matching with the vibration frequency of the main structure. 3. The curved base serves as the load-bearing base of the device, providing installation support for each component. The variable curve design at the bottom guides the tuned solid mass components to perform multi-track horizontal movements. Combined with the warping effect, it increases energy dissipation during vibration. At the same time, the nonlinear gradual change of the curve curvature alters the motion resistance, further enhancing the vibration reduction effect. 4. The buckling-induced bandgap double-layer rod system dynamically expands the bandgap range through compression deformation reconstruction, effectively attenuating vibrations over a wide frequency range and significantly reducing transmittance. At the same time, multiple symmetrically arranged connecting devices ensure precise tuning of bidirectional vibrations, maintaining excellent vibration reduction performance under different vibration scenarios such as earthquakes and wind loads. Attached Figure Description

[0022] Figure 1 This is an isometric view of the overall structure of the TMD device of the present invention; Figure 2 This is a top view of the overall structure of the TMD device of the present invention; Figure 3 It is an axonometric drawing of the curved base; Figure 4 This is a cross-sectional view of the curved base; Figure 5 This is a cross-sectional view of the tuned solid mass component and the tuned liquid damping device; Figure 6 This is an isometric view of the tuned solid mass component and the tuned liquid damping device; Figure 7 It is an isometric drawing of the connecting device; Figure 8 This is a sectional view of the connecting device; Figure 9 This is the front view of the universal joint; Figure 10 It is an isometric view of a universal joint; Figure 11 This is an isometric view of a nitrogen spring; Figure 12 This is a cross-sectional view of a nitrogen spring; Figure 13 This is a front view of a buckling-induced bandgap double-layer bar system. Figure 14 It is an isometric drawing of a buckling-induced bandgap double-layered rod mechanism.

[0023] In the figure: curved base (1), tuned solid mass component (2), tuned liquid damping device inner wall (3), tuned liquid (4), universal joint for connection (5), buckling-induced bandgap double-layer rod mechanism (6), sleeve (7), nitrogen spring (8), long straight rod (9), water pipe (10), water pump (11), accelerometer (12), independent water tank (13), industrial control computer (14). Detailed Implementation

[0024] The present invention will now be described in detail with reference to specific embodiments. These embodiments are based on the technical solution of the present invention and provide detailed implementation methods and specific operating procedures. However, the scope of protection of the present invention is not limited to the following embodiments.

[0025] The adaptively adjustable mass and stiffness curved base tuned mass damping device has a core structure comprising multiple components, specifically: a curved base, a tuned solid mass component, an inner wall of a tuned liquid damping device, a tuning liquid, a universal joint for connection, a buckling-induced bandgap double-layer rod mechanism, a sleeve, a nitrogen spring, a long straight rod, a water pipe, a water pump, an acceleration sensor, an independent water tank, and an industrial control computer. The curved base is a cavity structure with an open top. A tuned solid mass component serves as the core mass carrier, horizontally mounted at the bottom of the cavity. Its bottom conforms to the curved inner wall of the curved base, allowing for multi-path horizontal movement along the inner wall. A tuned liquid damping device consists of its inner wall and a tuned liquid. The inner wall of the tuned liquid damping device is fixedly mounted on top of the tuned solid mass component, forming a closed liquid-containing space filled with the tuned liquid. One end of a water pipe is inserted into the tuned liquid damping device from above, while the other end extends to the outside of the curved base and connects to one port of a water pump. Another water pipe connects to the other port of the water pump and an independent water tank. An accelerometer is positioned on the side wall of the tuned solid mass component. The independent water tank and industrial control computer are installed near the overall device. At least four sets of connection devices are required, symmetrically arranged between the inner wall of the curved base and the side wall of the tuned solid mass component, with the installation height matching the center of gravity height of the tuned solid mass component. Each connecting device employs a series connection method: "universal hinge for connection - buckling-inducing bandgap double-layer rod mechanism - nitrogen spring - long straight rod - universal hinge for connection". The specific connections are as follows: one end of a universal hinge for connection is fixedly connected to the side wall of the curved base, and the other end is fixedly connected to one side of the buckling-inducing bandgap double-layer rod mechanism. The other side of the buckling-inducing bandgap double-layer rod mechanism is fixedly connected to the cylinder of the nitrogen spring. One end of the long straight rod is fixedly connected to the piston rod of the nitrogen spring, and the other end is connected to another universal hinge for connection. The other universal hinge for connection is fixedly connected to the inner wall of the curved base. A sleeve is fitted onto the outside of the nitrogen spring and the long straight rod. The inner wall of the sleeve is fitted and fixed to the outer wall of the nitrogen spring cylinder, simultaneously providing a guiding constraint for the long straight rod, achieving relative fixation and motion guidance between the nitrogen spring and the long straight rod.

[0026] The curved base has a continuous, smooth parabola at its bottom, with the radius of curvature gradually changing non-linearly along the direction of motion of the tuned solid mass component (gradual change rate ≤ 1 / 5). The ratio of its radius of curvature to the equivalent diameter of the mass component is 1.2~2.0, which can guide the mass component to perform multi-path motion, ensuring motion and structural stability. Both the curved base and the tuned solid mass component are made of high-strength ductile iron or low-alloy high-strength steel, with a yield strength to elastic modulus ratio not exceeding 1 / 800 and an elongation not less than 15%, ensuring load-bearing strength and impact resistance. The ratio of the height to the equivalent diameter of the tuned solid mass component is 0.4~0.8. The tuned liquid damping device uses a water pipe with an inner diameter that is 1 / 30 to 1 / 20 of the equivalent diameter of the damping device, ensuring smooth liquid flow and avoiding impact disturbances. The water pipe is equipped with a high-precision electromagnetic flow control valve for precise liquid quality control. The ratio of the tuned liquid mass to the unloaded mass of the tuned solid mass component is 0.2 to 0.3, and the total mass of the device can be continuously adjusted within a range of 1.2 to 1.3 times the unloaded mass. The ratio of the height of the inner wall of the tuned liquid damping device to the height of the tuned solid mass component is 0.5 to 0.7, and the ratio of the wall thickness to the wall thickness of the tuned solid mass component is 0.6 to 0.9. The connecting device employs a nitrogen spring cylinder length to buckling-induced gap double-layer rod mechanism with a length ratio of 1.5~2.5 and a sleeve inner diameter to nitrogen spring cylinder outer diameter ratio of 1.05~1.15, ensuring seamless coordination among components. The connecting component uses a ball-joint universal joint with a pin diameter to hinge seat hole diameter ratio of 0.95~0.98 and a rotary joint radial clearance to pin diameter ratio of 1 / 500~1 / 300, enabling 360° free rotation and effectively eliminating shear force. The universal joint pin is made of bearing steel with a hardness of not less than HRC58, and the hinge seat is made of wear-resistant bronze alloy with a friction coefficient of less than 0.15, reducing rotational wear and extending service life. The buckling-induced bandgap double-layer rod system adopts a hyperbolic beam honeycomb unit cell structure, which is integrally formed by an upper pressure plate, hyperbolic beams, reinforcing walls, horizontal beams, and a lower pressure plate. The number of hyperbolic beams is 4 to 6 and they are evenly arranged along the circumference of the unit cell. The included angle between adjacent hyperbolic beams is 60° to 90°. The ratio of the thickness of the reinforcing wall to the thickness of the hyperbolic beam is 1.2 to 1.5. The connection is made of rounded transition to ensure structural strength and deformation stability. The structure is made of beryllium bronze or titanium alloy, with an elastic modulus of 100 to 150 GPa and a yield strength greater than 800 MPa, which is suitable for large deformation and bandgap tuning requirements. The nitrogen spring cylinder body is made of ultra-high strength alloy steel with a yield strength ≥1200MPa and an elastic modulus ≥200GPa, and the piston rod is made of nitrided alloy structural steel with a surface hardness ≥HV600; the ratio of the length of the long straight rod to the length of the nitrogen spring cylinder body is 1.0~1.5, and the ratio of the axial stiffness to the positive stiffness value of the nitrogen spring is less than 0.2; the stiffness ratio of the buckling-induced bandgap double-layer rod mechanism to the nitrogen spring is 0.6~0.9, and the combined stiffness adjustment range formed by the two is at least -30~50kN / m; The accelerometer is used to collect the vibration response signal of the shock absorber; the independent water tank, whose volume is about 1 / 5 of the overall volume of the shock absorber, is connected to the fluid circuit of the TLD device and is used to replenish or adjust the liquid volume in the TLD device; the industrial control computer, whose volume is about 1 / 100 to 1 / 200 of the overall volume of the shock absorber, is electrically connected to the control unit of the accelerometer and the TLD device and is used to receive the signal from the accelerometer and control the damping parameters of the TLD device according to a preset algorithm.

[0027] The universal joint connecting the components has a clearance fit between the pin and the hinge seat, a sliding fit between the piston rod of the nitrogen spring and the cylinder, and a sliding fit between the long straight rod and the inner wall of the sleeve. The angle between the adjacent central axes of the four sets of connecting devices is 90°, and the central axis of each set of connecting devices is in the same horizontal plane as the center of gravity of the tuned solid mass component. The nitrogen springs and buckling-induced gap double-layer rod mechanisms in the connecting devices of different horizontal directions adopt differentiated size designs.

[0028] A super high-rise office building located in Shanghai, with a building height of 200m, a steel frame-core tube structure, and a top floor area of ​​800㎡. The building's height-to-width ratio is 4.2. Under strong wind loads, the horizontal vibration acceleration of the top floor is 0.15g, which affects office comfort. The area is a 7-degree seismic fortification zone with a seismic intensity of 0.15g. Furthermore, during its service life, the vibration characteristics may change due to the addition or removal of equipment on the top floor and renovations to the facade, making it difficult for traditional TMD (Transformer Mechanism for Damping) systems to adapt.

[0029] Device parameter selection: Based on the natural frequency of the building structure (0.23~0.26Hz), the device of this invention is selected and installed on the top floor of the building. The device parameters are as follows: The ratio of the radius of curvature of the bottom curved surface of the curved base to the equivalent diameter of the tuned solid mass component is 1.6; the ratio of the side wall thickness to the equivalent side length of the base is 1 / 15; the ratio of the bottom curved surface thickness to the side wall thickness is 1.5; there are 6 pre-embedded bolt holes (Φ28mm) symmetrically distributed along the center.

[0030] The tuned solid mass component has a height of 0.8m and an equivalent diameter of 1.0m (the ratio of height to equivalent diameter is 0.8); it is made of low-alloy high-strength steel with a yield strength to elastic modulus ratio of 1 / 800 and an elongation of 18%.

[0031] The ratio of the height of the inner wall of the tuned liquid damping device to the height of the tuned solid mass component is 0.7, and the ratio of the wall thickness to the wall thickness of the tuned solid mass component is 0.8; the water pipe (the ratio of the inner diameter to the equivalent diameter of the inner wall is 1 / 25, equipped with a flow control valve); the ratio of the maximum mass of the tuned liquid to the unloaded mass of the tuned solid mass component is 0.25, and the total mass adjustment range of the device is 1.2~1.3 times the unloaded mass.

[0032] The ratio of the diameter of the universal joint pin to the diameter of the hinge seat hole is 0.96, the ratio of the radial clearance of the rotating pair to the diameter of the pin is 1 / 400, and the rotation angle is ±18°; the pin hardness is HRC60, and the friction coefficient of the hinge seat is 0.12.

[0033] The buckling-induced gap double-layer rod mechanism has 5 hyperbolic beams with an adjacent included angle of 72°; the ratio of the reinforcing wall thickness to the hyperbolic beam thickness is 1.3, the ratio of the horizontal beam length to the unit cell length is 0.8, and the ratio of the transition radius to the hyperbolic beam thickness is 0.4; it is made of beryllium bronze with an elastic modulus of 120 GPa and a yield strength of 850 MPa; the ratio of the absolute value of the negative stiffness to the positive stiffness of the nitrogen spring is 0.75.

[0034] The ratio of the length of the nitrogen spring cylinder to the length of the buckling-induced bandgap double-layer rod mechanism is 2.0. The cylinder yield strength is 1300MPa and the elastic modulus is 210GPa. The surface hardness of the piston rod is HV650.

[0035] The ratio of the length of the long straight rod to the length of the nitrogen spring cylinder is 1.2, and the ratio of its axial stiffness to the positive stiffness of the nitrogen spring is 0.15. The ratio of the inner diameter of the sleeve to the outer diameter of the nitrogen spring cylinder is 1.1.

[0036] The accelerometer is a triaxial MEMS accelerometer. The independent water tank is a stainless steel tank with a volume approximately 1 / 5 that of the overall device. The industrial control computer is an embedded industrial computer with a volume only 1 / 15 that of the overall device, serving as the control core.

[0037] Specific construction steps: Pre-embedded steel plates are reserved in the structural beams of the equipment layer, and the curved base is fixed by 6 sets of high-strength bolts (M28×120mm), with a horizontality error ≤0.5mm / m.

[0038] Install the accelerometer on the side wall of the tuned solid mass component, hoist the tuned solid mass component into the curved base, and evenly apply mechanical lubricant to the inner wall of the base to ensure a seamless fit.

[0039] The four sets of devices are connected in series in sequence using a universal joint, a buckling-induced double-layer rod system with a gap, a nitrogen spring, a sleeve, and a long straight rod. They are then fixed by welding (weld height 8mm, flaw detection qualified). The two ends of the connecting device are then welded to the side wall of the tuned solid mass component and the inner wall of the base, respectively, to ensure that the four sets of devices are subjected to uniform force.

[0040] The tuning liquid damping device is hoisted to the top of the tuning solid mass component and secured with a flange (8 sets of M16 bolts). The sealing gasket is tightened for waterproofing. An independent stainless steel water tank and an embedded industrial control computer are installed next to the overall unit. A water pump is used to circulate the tuning liquid between the independent water tank and the tuning liquid damping device.

[0041] Check the firmness of each component connection, test the flexibility of the universal joint rotation, and verify that the nitrogen spring has no leakage and the buckling-induced gap double-layer rod mechanism has no deformation.

[0042] Debugging and effect verification: Inject tuning liquid until the total mass of the device reaches 1.25 times the unloaded mass, then close the flow control valve to lock the mass. At this point, the device's natural frequency precisely matches the initial natural frequency of the main structure at 0.25Hz. By adjusting the working pressure of the nitrogen spring to 1.2MPa, combined with the bandgap tuning effect of the buckling-induced bandgap double-layer rod mechanism, the composite stiffness reaches 10kN / m, achieving a frequency-accurate match between the device and the main structure.

[0043] The device can achieve a natural frequency adjustment range of 0.2-0.4Hz by adjusting the mass (1.2-1.3 times the unloaded mass range) and the composite stiffness adjustment (stiffness adjustment range -30~50kN / m), which completely covers the frequency variation range of the main structure.

[0044] In strong winds (wind speed 25m / s), the measured horizontal vibration acceleration of the top floor of the building was 0.15g without the device installed. After installation and commissioning, the horizontal vibration acceleration of the top floor was reduced to 0.09g, and the vibration acceleration reduction rate reached 40%, which meets the comfort requirements (≤0.1g) in the "Technical Specification for Steel Structures of High-Rise Civil Buildings".

[0045] A shaking table test was used to simulate a rare earthquake of magnitude 7. Without this device, the measured inter-story displacement of the top floor was 52 mm. After installing this device, the inter-story displacement of the top floor was reduced to 28.6 mm, and the inter-story displacement reduction rate reached 45%, which can effectively suppress the deformation of the structure under seismic action.

[0046] After removing some equipment from the top of the building, the natural frequency of the main structure changed from 0.25Hz to 0.24Hz. By draining some of the tuning liquid, the total mass of the device was adjusted to 1.2 times the unloaded mass, and the working pressure of the nitrogen spring was simultaneously fine-tuned to 1.3MPa. The natural frequency of the device was rematched to 0.24Hz within 15 minutes.

[0047] A second test under strong wind conditions showed that the horizontal vibration acceleration reduction rate of the top floor remained above 38%, and the vibration reduction effect did not decrease, verifying the device's efficient adaptability to frequency changes in the main structure.

Claims

1. A curved surface base tuned mass damping device with adaptively adjustable mass and stiffness, characterized in that: Includes curved base (1), tuned solid mass component (2), tuned liquid damping device inner wall (3), tuned liquid (4), universal joint for connection (5), buckling-induced bandgap double-layer rod mechanism (6), sleeve (7), nitrogen spring (8), long straight rod (9), water pipe (10), water pump (11), accelerometer (12), independent water tank (13) and industrial control computer (14); The curved base (1) is a cavity structure with an open top. The tuned solid mass component (2) serves as the core mass carrier and is horizontally installed at the bottom of the cavity. Its bottom is in contact with the variable curve inner wall of the curved base (1) and can move horizontally along the inner wall in multiple trajectories. The tuned liquid damping device consists of the inner wall (3) of the tuned liquid damping device and the tuned liquid (4). The inner wall (3) of the tuned liquid damping device is fixedly installed on the top of the tuned solid mass component (2) to form a closed liquid-containing space. Liquid (4) is filled in the space; one end of water pipe (10) is inserted into the tuned liquid damping device from above, and the other end of water pipe (10) extends to the outside of the curved base (1) and is connected to a connection port of water pump (11). Another water pipe (10) is connected to the other connection port of water pump (11) and independent water tank (13). Accelerometer (12) is arranged on the side wall of tuned solid mass component (2). Independent water tank (13) and industrial control computer (14) are installed near the overall device. At least four sets of connecting devices are required, symmetrically arranged between the inner wall of the curved base (1) and the side wall of the tuned solid mass component (2). The installation height is consistent with the center of gravity height of the tuned solid mass component (2). Each set of connecting devices adopts a series connection method of "connecting universal hinge (5) - buckling-induced bandgap double-layer rod mechanism (6) - nitrogen spring (8) - long straight rod (9) - connecting universal hinge (5)". The specific connection is as follows: one end of the connecting universal hinge (5) is fixedly connected to the side wall of the curved base (1), and the other end is fixedly connected to one side of the buckling-induced bandgap double-layer rod mechanism (6). The other side of the buckling-induced band gap double-layer rod mechanism (6) is fixedly connected to the cylinder of the nitrogen spring (8). One end of the long straight rod (9) is fixedly connected to the piston rod of the nitrogen spring (8), and the other end is connected to another connection by a universal joint (5). The other connection is fixedly connected to the inner wall of the curved base (1) by a universal joint (5). The sleeve (7) is fitted on the outside of the nitrogen spring (8) and the long straight rod (9). The inner wall of the sleeve (7) is fitted and fixed to the outer wall of the cylinder of the nitrogen spring (8), while forming a guiding constraint on the long straight rod (9), so as to realize the relative fixation and motion guidance of the nitrogen spring (8) and the long straight rod (9).

2. The adaptively adjustable mass and stiffness curved base tuned mass damping device according to claim 1, characterized in that: The bottom of the curved base (1) is a continuous smooth parabola. The radius of curvature changes nonlinearly along the direction of motion of the tuned solid mass component (2) (gradual change rate ≤ 1 / 5). The ratio of its radius of curvature to the equivalent diameter of the mass component is 1.2~2.0, which can guide the mass component to perform multi-track motion and ensure the stability of motion and structure. The curved base (1) and the tuned solid mass component (2) are both made of high-strength ductile iron or low-alloy high-strength steel. The ratio of the yield strength to the elastic modulus of the material is not greater than 1 / 800, and the elongation is not less than 15%, to ensure load-bearing strength and impact resistance. The ratio of the height to the equivalent diameter of the tuned solid mass component (2) is 0.4~0.

8.

3. The adaptively adjustable mass and stiffness curved base tuned mass damping device according to claim 1, characterized in that: The inner diameter of the water pipe (10) used in the tuning liquid damping device is 1 / 30 to 1 / 20 of the equivalent diameter of the damping device, which can ensure smooth liquid flow and avoid impact disturbance; the water pipe (10) is equipped with a high-precision electromagnetic flow control valve to achieve precise control of liquid quality; the mass ratio of the tuning liquid (4) to the unloaded mass of the tuning solid mass component (2) is 0.2 to 0.3, and the total mass of the device can be continuously adjusted within the range of 1.2 to 1.3 times the unloaded mass; the height ratio of the inner wall (3) of the tuning liquid damping device to the height of the tuning solid mass component (2) is 0.5 to 0.7, and the wall thickness ratio of the wall thickness to the wall thickness of the tuning solid mass component (2) is 0.6 to 0.

9.

4. The adaptively adjustable mass and stiffness curved base tuned mass damping device according to claim 1, characterized in that: The length of the nitrogen spring (8) cylinder used in the connecting device is 1.5~2.5 to the length of the buckling-induced gap double-layer rod mechanism (6), and the inner diameter of the sleeve (7) is 1.05~1.15 to the outer diameter of the nitrogen spring (8) cylinder, ensuring that the components work together without interference; the universal joint (5) used for connection adopts a ball joint type universal joint, and the ratio of its pin diameter to the hinge seat hole diameter is 0.95~0.98, and the ratio of the radial clearance of the rotating pair to the pin diameter is 1 / 500~1 / 300, which can realize 360° free rotation and effectively eliminate shear force; the universal joint pin is made of bearing steel with a hardness of not less than HRC58, and the hinge seat is made of wear-resistant bronze alloy with a friction coefficient of less than 0.15, which reduces rotational wear and extends service life.

5. The adaptively adjustable mass and stiffness curved base tuned mass damping device according to claim 1, characterized in that: The buckling-induced bandgap double-layer rod system (6) adopts a hyperbolic beam honeycomb unit cell structure, which is integrally formed by the upper pressure plate, hyperbolic beam, reinforcing wall, horizontal beam and lower pressure plate; the number of hyperbolic beams is 4 to 6 and they are evenly arranged along the circumference of the unit cell, the included angle between adjacent hyperbolic beams is 60° to 90°, the ratio of the thickness of the reinforcing wall to the thickness of the hyperbolic beam is 1.2 to 1.5, and the connection adopts a rounded transition to ensure the structural strength and deformation stability; the structure is made of beryllium bronze or titanium alloy, with an elastic modulus of 100 to 150 GPa and a yield strength greater than 800 MPa, which is suitable for large deformation and bandgap tuning requirements.

6. The adaptively adjustable mass and stiffness curved base tuning mass damping device according to claim 1, characterized in that: The cylinder body of the nitrogen spring (8) is made of ultra-high strength alloy steel with yield strength ≥1200MPa and elastic modulus ≥200GPa, and the piston rod is made of nitrided alloy structural steel with surface hardness ≥HV600; the ratio of the length of the long straight rod (9) to the length of the cylinder body of the nitrogen spring (8) is 1.0~1.5, and the ratio of the axial stiffness to the positive stiffness value of the nitrogen spring (8) is less than 0.2; the stiffness ratio of the buckling-induced bandgap double-layer rod mechanism (6) to the nitrogen spring (8) is 0.6~0.9, and the combined stiffness adjustment range formed by the two is at least -30~50kN / m.

7. The adaptively adjustable mass and stiffness curved base tuning mass damping device according to claim 1, characterized in that: An accelerometer (12) is used to collect vibration response signals of the damping device; an independent water tank (13), whose volume is about 1 / 5 of the overall volume of the damping device, is connected to the fluid circuit of the TLD device and is used to replenish or adjust the liquid capacity in the TLD device; an industrial control computer (14), whose volume is about 1 / 100 to 1 / 200 of the overall volume of the damping device, is electrically connected to the control unit of the accelerometer (12) and the TLD device and is used to receive the signal from the accelerometer (12) and control the damping parameters of the TLD device according to a preset algorithm.

8. A curved surface base tuned mass damping device with adaptively adjustable mass and stiffness according to claim 1, characterized in that: The pin of the universal joint (5) and the hinge seat are clearance fit, the piston rod of the nitrogen spring (8) and the cylinder are sliding fit, and the long straight rod (9) and the inner wall of the sleeve (7) are sliding fit. The angle between the adjacent central axes of the four sets of connecting devices is 90°, and the central axis of each set of connecting devices is in the same horizontal plane as the center of gravity of the tuned solid mass component (2). The nitrogen spring (8) and the buckling-induced bandgap double-layer rod mechanism (6) in the connecting devices of different horizontal directions adopt differentiated size design.

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