Self-adaptive tuning inerter damping device and method for suppressing vertical micro-vibration of structure

Abstract

The invention relates to a self-adaptive tuning inerter damping device and method for suppressing vertical micro-vibration of a structure. The self-adaptive tuning inerter damping device comprises a bearing base, a tuning mass block, a vibration system connecting the bearing base and the tuning mass block, a pneumatic control system and an intelligent measurement and control system. The vibration system is formed by connecting an outer side air spring set and a central air spring in series with a hydraulic inerter unit, an adjustable damping branch and a fixed inerter branch which are connected in parallel are integrated in the hydraulic unit and are respectively provided with an electro-hydraulic proportional valve and a spiral pipe type hydraulic inerter, so that adjustable damping and mass amplification are realized. The pneumatic system adjusts the air pressure of each air spring through an independent air path and a proportional valve so as to change the rigidity. An intelligent system monitors vibration through a sensor, a central controller identifies excitation frequency and optimizes parameters based on a kinetic model, and rigidity and damping are synchronously adjusted. According to the invention, the problem that a mechanical inerter is insufficient in response to micro-vibration is solved, the defects that a traditional passive device is narrow in frequency band and easy to detune are overcome, and broadband, self-adaptive and high-performance suppression of vertical micro-vibration of a structure is realized.

Description

Technical Field

[0001] This invention relates to the field of structural vibration control technology, and in particular to an adaptive tuned inertial capacitance vibration reduction device and method for suppressing vertical micro-vibrations in structures. Background Technology

[0002] In civil engineering, horizontal structures such as floor slabs and pedestrian bridges are prone to continuous vertical micro-vibrations under dynamic loads from pedestrians and vehicles. While these vibrations typically do not directly threaten structural safety, they significantly reduce user comfort, interfere with the operation of precision instruments, and may accelerate structural fatigue damage. Tuned mass dampers (TMDs) are a widely used passive control method to suppress these vibrations. Traditional TMDs are tuned to a specific natural frequency of the main structure via a spring-mass-damping system, thereby absorbing and dissipating vibrational energy. However, this device has inherent drawbacks: firstly, it relies on a large physical mass to achieve the necessary tuning mass, resulting in a bulky and heavy device that is difficult to apply in space-constrained environments; secondly, its stiffness and damping parameters are fixed after installation, resulting in an extremely narrow frequency bandwidth for vibration reduction, effective only for a single frequency or narrow frequency band targeted in the design. In practical engineering, the frequency components of the excitations on the structure (such as pedestrian and vehicle loads of different frequencies) are often complex and time-varying, which makes the passive TMD with fixed parameters very prone to "detuning", resulting in a significant decrease in vibration reduction effect or even failure.

[0003] To overcome the shortcomings of traditional TMDs, inertial containers have been introduced to construct tuned inertial mass damping systems (such as Tuned Viscous Mass Damper, TVMD). As an acceleration-dependent element at both ends, the inertial container can generate a force proportional to the relative acceleration, achieving a "mass amplification" effect. Theoretically, it can reduce physical mass while maintaining vibration reduction performance and broaden the vibration reduction frequency band. However, such systems still face significant technical bottlenecks. On the one hand, common mechanical inertial containers (such as ball screw type) usually require a certain starting stroke or driving force. For the small amplitude vibrations unique to structures such as floor slabs, their response is sluggish and their sensitivity is low, making it difficult to effectively activate and exert the mass amplification effect under small amplitude conditions. On the other hand, the more fundamental problem with existing solutions is the lack of an efficient, reliable, and internally integrated mechanical design that can organically and synergistically integrate a high-sensitivity inertial capacitance mechanism suitable for micro-amplitude vibrations, a damping mechanism that can be quickly and accurately adjusted, and a stiffness mechanism that can be continuously adjusted over a wide frequency range into a compact system. This would allow the system to simultaneously address the inherent high-frequency micro-vibration characteristics of the structure and the wide-frequency time-varying characteristics of external excitations, thereby achieving truly wideband, adaptive, and high-performance vibration control. Summary of the Invention

[0004] Therefore, it is necessary to provide an adaptive tuned inertial capacitance vibration reduction device and method for suppressing vertical micro-vibrations in structures, addressing the aforementioned technical problems.

[0005] The present invention provides an adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations of a structure, comprising a support base, a tuned mass block, and a vibration system, a pneumatic active control system, and an intelligent measurement and control system connected between the support base and the tuned mass block; The vibration system includes an outer stiffness adjustment unit and an inertial-capacitive damping subsystem connected in parallel. The outer stiffness adjustment unit includes at least one set of outer air springs, the outer air springs comprising one or more air springs connected in parallel, the upper end of each air spring being connected to the tuning mass block, and the lower end being connected to the bearing base via a support. The inertial-capacitive damping subsystem consists of a central air spring and a parallel hydraulic inertial-capacitive damping unit connected in series. The lower end of the central air spring is connected to the bearing base via a support, and the upper end is connected to the lower end of the parallel hydraulic inertial-capacitive damping unit. The upper end of the parallel hydraulic inertial-capacitive damping unit is connected to the tuning mass block. The parallel hydraulic inertial-capacitive damping unit includes a hydraulic cylinder, a piston disposed within the hydraulic cylinder, and a piston rod connected to the piston. The piston divides the inner cavity of the hydraulic cylinder into a first chamber and a second chamber. The parallel hydraulic inertial-capacitive damping unit also includes an adjustable damping branch and a fixed inertial-capacitive branch, with their two ends respectively connected to the first chamber and the second chamber. The adjustable damping branch and the fixed inertial-capacitive branch are connected in parallel. The adjustable damping branch is equipped with an electro-hydraulic proportional valve for providing continuously adjustable damping force, and the fixed inertial-capacitive branch is equipped with a helical-tube hydraulic inertial container for providing mass amplification effect. The pneumatic active control system includes an air source and at least two independent control air paths. Each independent control air path is branched off from the main air path of the air source and is equipped with an electro-proportional valve to independently connect to and control the air pressure of the outer air spring assembly and the central air spring. The intelligent measurement and control system includes sensors for acquiring vibration response signals of the main structure and a central controller. The input terminal of the central controller is connected to the sensors, and the output terminal is connected to the electro-hydraulic proportional valve and each electro-hydraulic proportional valve in the pneumatic active control system. The central controller is configured to: identify the current dominant excitation frequency based on the sensor signals, solve for the optimal stiffness parameters and damping parameters based on the excitation frequency and a preset coupled dynamics model, and generate control commands to synchronously adjust the air pressure output of the electro-hydraulic proportional valve and the opening degree of the electro-hydraulic proportional valve.

[0006] In one embodiment, the outer air spring assembly includes a first outer air spring and a second outer air spring arranged in parallel; in the pneumatic active control system, an independent control air path connected to the outer air spring assembly supplies air to the first outer air spring and the second outer air spring simultaneously through a split tee.

[0007] In one embodiment, the central controller is configured to: solve for the optimal parameters using a fixed-point theory optimization strategy when the identified excitation frequency is close to the natural frequency of the main structure; and solve for the optimal parameters using a frequency tracking strategy when the identified excitation frequency is far from the natural frequency of the main structure.

[0008] In one embodiment, the sensor includes an accelerometer for measuring the acceleration of the main structure and / or a wire-type displacement sensor for measuring the relative displacement of the main structure and the tuned mass.

[0009] In one embodiment, the pneumatic active control system further includes an air source processing module and a pressure relief valve located downstream of the air source.

[0010] In one embodiment, the support base is connected to the main structure at a single point.

[0011] In one embodiment, the inertial capacity coefficient b of the fixed inertial capacity branch is determined by the formula b = ρL² / A, where ρ is the fluid density, L is the pipe length of the helical hydraulic inertial container, and A is the pipe cross-sectional area.

[0012] The present invention also provides an adaptive tuned inertial capacitance vibration reduction method for suppressing vertical micro-vibrations in structures, employing an adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in structures as described above, the method comprising: S1. Real-time acquisition of vibration response signals of the main structure through sensors; S2. The central controller performs frequency domain analysis on the vibration response signal to identify the currently dominant excitation frequency; S3. Based on the identified excitation frequency and the pre-established two-degree-of-freedom coupled dynamic model of the main structure-vibration damping device, the current optimal target stiffness of the outer air spring group, the target stiffness of the central air spring, and the target damping coefficient of the system are calculated online through an adaptive tuning algorithm. S4. The central controller generates coordinated control commands and executes them synchronously: S4a. Send a command to the corresponding electro-proportional valve in the pneumatic active control system to adjust its output air pressure so that the stiffness of the outer air spring assembly and the central air spring approaches their corresponding target stiffness. S4b: Send a command to the electro-hydraulic proportional valve in the parallel hydraulic inertial-capacitive damping unit to adjust its opening degree so that the system damping coefficient approaches the target damping coefficient.

[0013] In one embodiment, in S3, the two-degree-of-freedom coupled dynamic model includes at least the main structure displacement, the tuned mass block displacement, the equivalent stiffness of the outer air spring group, the equivalent stiffness of the central air spring, the damping coefficient of the adjustable damping branch, and the inertial capacity coefficient of the spiral tube hydraulic inertial container as parameters.

[0014] In one embodiment, in step S3, different parameter optimization strategies are dynamically selected for solving based on the relative relationship between the excitation frequency and the natural frequency of the main structure.

[0015] The aforementioned adaptive tuned inertial capacitance damping device and method for suppressing vertical micro-vibrations in structures employs a hydraulic inertial capacitance damping unit consisting of an adjustable damping branch and a fixed inertial capacitance branch connected in parallel. This unit is highly sensitive to minute displacements, solving the problem that mechanical inertial containers suffer from delayed response and difficulty in effective activation due to insufficient starting stroke or driving force in micro-vibration scenarios, thus achieving a high-sensitivity mass amplification effect for micro-vibrations. By setting up a pneumatic active control system containing at least two independent control air paths, the air pressure of the outer air spring group and the central air spring can be adjusted independently and continuously, thereby achieving rapid and precise adjustment of the overall system stiffness over a wide frequency range, overcoming the shortcomings of fixed parameters and narrow frequency band of traditional passive devices. By setting up an intelligent measurement and control system and its central controller, the external excitation frequency can be sensed in real time and the optimal parameters can be dynamically solved based on the coupled dynamic model. The stiffness of the pneumatic system and the damping of the hydraulic system can be adjusted synchronously and collaboratively, so that the dynamic characteristics of the device can adaptively track the time-varying external excitation. Thus, the highly sensitive micro-amplitude vibration inertial capacity mechanism, the rapidly adjustable damping mechanism, and the wide-frequency adjustable stiffness mechanism are organically unified in a compact device, realizing wide-frequency, adaptive, and high-performance suppression of vertical micro-amplitude vibrations of the structure. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of an adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in a structure, according to one embodiment. Figure 2 for Figure 1 Schematic diagram of a parallel hydraulic inertial-capacitive damping unit; Figure 3 for Figure 2 A sectional view; Figure 4 This is a schematic diagram of an adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in a structure, according to one embodiment.

[0018] Reference numerals: 01, Support base; 02, Tuning mass block; 11, First outer air spring; 12, First outer air spring support; 13, Second outer air spring; 14, Second outer air spring support; 21, Central air spring; 22, Central air spring support; 31, Parallel hydraulic inertial-capacitive damping unit; 41, Accelerometer; 42, Wire-type displacement sensor; 51, Central controller; 52, Monitor; 61, Air source; 62, Air source processing module; 63, Pressure relief valve; 64, Ratio Example: 65. Outer air spring electro-proportional valve; 66. Center air spring electro-proportional valve; 67. Air spring assembly tee; 3101. Piston rod; 3102. Piston; 3103. First chamber; 3104. Second chamber; 3105. First oil port; 3106. Second oil port; 311. Adjustable damping branch; 311a. Electro-hydraulic proportional valve; 3111. First tee connector; 3112. Second tee connector; 312. Fixed inertial capacity branch; 511. Adaptive tuning algorithm module. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0020] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on the other component or there may be an intermediate component. When a component is considered to be "connected to" another component, it can be directly connected to the other component or there may be an intermediate component present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used in this specification are for illustrative purposes only and do not represent the only possible implementation.

[0021] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0022] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature and the second feature are in indirect contact through an intermediate medium. Furthermore, "above," "over," and "on top" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0023] Unless otherwise defined, all technical and scientific terms used in this specification have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0024] The following is combined Figures 1-3 The present invention describes an adaptive tuned inertial capacitance vibration reduction device and method for suppressing vertical micro-vibrations in structures.

[0025] like Figures 1 to 3 As shown, in one embodiment, an adaptive tuned inertial-capacitive vibration damping device for suppressing vertical micro-vibrations of a structure includes a support base 01, a tuned mass block 02, and a vibration system, a pneumatic active control system, and an intelligent measurement and control system connected between the support base 01 and the tuned mass block 02. The vibration system includes an outer stiffness adjustment unit and an inertial-capacitive damping subsystem arranged in parallel. The outer stiffness adjustment unit consists of at least one set of outer air springs, which includes one or more air springs connected in parallel. The upper end of each air spring is connected to the tuned mass block 02, and the lower end is connected to the support base via a support. The inertial-capacitive damping subsystem consists of a central air spring 21 connected in series with a parallel hydraulic inertial-capacitive damping unit 31. The lower end of the central air spring 21 is connected to the support base 01 via a support, and the upper end is connected to the lower end of the parallel hydraulic inertial-capacitive damping unit 31. The upper end of the parallel hydraulic inertial-capacitive damping unit 31 is connected to the tuned mass block 02. (Refer to...) Figure 1The device is installed on the main structure via a single-point connection through a support base 01. The tuning mass block 02 is coupled to the support base 01 through a vibration system. The outer air spring group includes a first outer air spring 11 and a second outer air spring 13, which are connected in parallel and fixed by a first outer air spring support 12 and a second outer air spring support 14. The central air spring 21 is connected through a central air spring support 22 and is connected in series with the parallel hydraulic inertial-capacitive damping unit 31 to form an inertial-capacitive subsystem. The whole structure is symmetrical to ensure balanced output.

[0026] The parallel hydraulic inertial-capacitance damping unit 31 includes a hydraulic cylinder, a piston 3102, and a piston rod 3101. The piston 3102 divides the inner cavity of the hydraulic cylinder into a first chamber 3103 and a second chamber 3104, and is provided with an adjustable damping branch 311 and a fixed inertial-capacitance branch 312. The two are connected in parallel between the chambers through a first tee connector 3111 and a second tee connector 3112. When external vibration drives the piston rod 3101 and the piston 3102 to move, it will squeeze the hydraulic oil in the first chamber 3103 or the second chamber 3104. The squeezed oil flows out through the first oil port 3105 or the second oil port 3106, and first reaches the first tee connector 3111, which is a diversion node. At this node, the oil is divided into two and flows into the two parallel branches in parallel.

[0027] The adjustable damping branch 311 is equipped with an electro-hydraulic proportional valve 311a to provide continuously adjustable damping force, while the fixed inertia branch 312 is equipped with a spiral tube type hydraulic inertia container, which realizes mass amplification through fluid inertia effect. Its inertia coefficient b is determined by the formula b = ρL² / A, where ρ is the fluid density, L is the pipe length, and A is the cross-sectional area.

[0028] The pneumatic active control system includes an air source 61, a main air path, and at least two independent control air paths. Each air path branches off from the main air path and is equipped with electro-proportional valves 65 and 66 to independently adjust the air pressure of the outer air spring assembly and the central air spring 21. The intelligent measurement and control system includes sensors 41 and 42 and a central controller 51. The sensors are used to collect vibration signals of the main structure. The input terminal of the central controller 51 is connected to the sensors, and the output terminal is connected to the electro-hydraulic proportional valve 311a and the electro-proportional valves 65 and 66. The central controller 51 is configured to identify the dominant excitation frequency based on the sensor signals, solve for the optimal stiffness and damping parameters based on a preset coupled dynamics model, and generate commands to synchronously adjust the air pressure and valve opening. In the working principle, when the external vibration drives the piston 3102 to move, the oil flows from the chamber through the first three-way connector 3111 to the adjustable damping branch 311 and the fixed inertial capacity branch 312. In the adjustable damping branch 311, the damping force is adjusted by the electro-hydraulic proportional valve 311a. c·v α ( c The damping coefficient is adjustable. αThe damping index is... v (For velocity), inertial force is generated in the fixed inertial volume branch 312 through the helical hydraulic inertial container. b·a ( b The inertia coefficient, a (For acceleration), the two oil streams converge at the second three-way connector 3112 and return to the hydraulic cylinder. The total hydraulic pressure is the sum of the damping force and the inertial force, thus efficiently dissipating energy. The pneumatic system is supplied with air from the air source 61. After being stabilized by the air source processing module 62 and the pressure relief valve 63, the air is divided into two paths by the diversion three-way valve 64 before the proportional valve. The air pressure is controlled by the electric proportional valves 65 and 66 respectively to continuously adjust the stiffness of the air spring. During the intelligent control process, the central controller 51 has a built-in adaptive tuning algorithm module 511. First, it collects vibration signals in real time through the accelerometer 41 and the wire-type displacement sensor 42, performs frequency domain analysis to identify the excitation frequency, and then optimizes the parameters online based on a two-degree-of-freedom coupled dynamic model. This model is described by the following equations:

[0029] in, and These represent the vertical displacements of the main structure and the tuning mass 02, respectively. The vertical acceleration of the main structure, To tune the vertical acceleration of the mass block, The vertical displacement at the connection point between the central air spring 21 and the parallel hydraulic inertial-capacitive damping unit 31 is [value missing]. and The equivalent stiffness provided by the outer air spring assembly and the central air spring 21, respectively. and These are the damping coefficients of the adjustable damping branch 311 and the inertial capacity coefficients of the helical hydraulic inertial container on the fixed inertial capacity branch 312, respectively. In this model, the mass of the tuned mass block 02 is... and inertia coefficient For fixed parameters, while stiffness , and damping These are time-varying adjustable parameters for real-time optimization of the algorithm. The algorithm selects a strategy based on the estimated excitation frequency and the known structural frequency: when the excitation frequency is close to the structural resonance region, Den Hartog's fixed-point theory is used for parameter optimization; when the excitation frequency is far from the structural frequency, a frequency tracking strategy is activated. After solving for the optimal frequency ratio and damping ratio using these strategies, the algorithm inversely calculates the theoretically optimal target stiffness of the outer air spring. k 1* Target stiffness of the central air spring k 2* and system target damping cSubsequently, the central controller 51 converts the target parameters into specific control commands, generating two coordinated signals: one is sent to the pneumatic system to drive the outer air spring electro-proportional valve 65 and the central air spring electro-proportional valve 66 to adjust the air pressure to change the stiffness; the other is sent directly to the electro-hydraulic proportional valve 311a driver in the adjustable damping branch 311 to adjust the valve core opening to change the system damping, so that the device's dynamic characteristics adaptively track external excitation and achieve wideband vibration suppression.

[0030] The outer air spring assembly includes a first outer air spring 11 and a second outer air spring 13 connected in parallel. In the pneumatic control system, an independent air path connecting this assembly supplies air to both the first outer air spring 11 and the second outer air spring 13 simultaneously via an air spring assembly tee 67, enhancing the uniformity and efficiency of stiffness adjustment. The central controller 51 employs fixed-point theory optimization when the excitation frequency is close to the natural frequency of the main structure, and a frequency tracking strategy when it is far away, improving the accuracy and adaptability of parameter optimization. Sensors include an acceleration sensor 41 for measuring the acceleration of the main structure and / or a wire-type displacement sensor 42 for measuring the relative displacement between the main structure and the tuned mass, improving the comprehensiveness and accuracy of vibration sensing. The pneumatic system also includes an air source processing module 62 and a pressure relief valve 63 to ensure stable and safe air supply. The support base 01 is connected to the main structure at a single point, simplifying installation and reducing structural interference.

[0031] This device solves the problem of insufficient response of traditional mechanical inertial containers in micro-vibration scenarios by using a hydraulic inertial unit to respond highly sensitively to micro-vibrations, combined with rapid stiffness adjustment of the pneumatic system and real-time optimization of intelligent algorithms. It achieves lightweight, adaptive wideband vibration suppression, and significantly improves the comfort and durability of structures such as floors and pedestrian bridges.

[0032] In addition, the present invention provides an adaptive tuned inertial capacitance vibration reduction method for suppressing vertical micro-vibrations in structures.

[0033] In one embodiment, an adaptive tuned inertial capacitance vibration reduction method for suppressing vertical micro-vibrations in a structure includes the following steps: Step S1: The vibration response signal of the main structure is collected in real time by the sensor.

[0034] In step S2, the central controller performs frequency domain analysis on the vibration response signal to identify the currently dominant excitation frequency.

[0035] Step S3: Based on the identified excitation frequency and the pre-established two-degree-of-freedom coupled dynamic model of the main structure and vibration damping device, the optimal target stiffness of the outer air spring assembly is calculated online using an adaptive tuning algorithm. k 1. Target stiffness of the central air spring k 2 and the system target damping coefficient cSpecifically, the two-degree-of-freedom coupled dynamic model includes at least the displacement of the main structure. x 1. Displacement of the tuned mass x 2. Equivalent stiffness of the outer air spring assembly k 1. Equivalent stiffness of the central air spring k 2. Adjustable damping branch damping coefficient c Inertial volume coefficient of spiral tube hydraulic inertial container b As a parameter; where, k 1. k 2 and c Adjustable parameters are provided for real-time optimization to ensure the model matches actual dynamics. Different parameter optimization strategies are dynamically selected based on the relative relationship between the excitation frequency and the natural frequency of the main structure, enhancing the flexibility and effectiveness of the method.

[0036] Step S4: The central controller generates coordinated control instructions and executes them synchronously. Step S4a: Send a command to the corresponding electro-proportional valve in the pneumatic active control system to adjust its output air pressure so that the stiffness of the outer air spring assembly and the central air spring approaches their respective target stiffness. k 1*, k 2*; Step S4b: Send a command to the electro-hydraulic proportional valve in the parallel hydraulic inertial-capacitive damping unit to adjust its opening degree so that the system damping coefficient approaches the target damping coefficient. c *

[0037] Furthermore, in specific implementation, the bearing base 01 is installed on the upper or lower surface of the main structure via a single-point connection, such as using a rigid support or hanging device, to ensure overall stability. The intelligent measurement and control system also includes a monitor 52 for human-machine interaction. The adaptive tuning algorithm module 511 in the central controller 51 specifically executes the following steps: real-time acquisition of signals from the accelerometer 41 and the wire-type displacement sensor 42, performing frequency domain analysis such as fast Fourier transform to accurately identify the dominant excitation frequency; based on known parameters such as the main structure mass m and the fundamental frequency f0, dynamically selecting an optimization strategy—when the excitation frequency is close to the resonance zone, applying Den Hartog's fixed-point theory to minimize the transmissibility, and when it is far away, using a frequency tracking strategy to broaden the bandwidth; after solving the optimal frequency ratio and damping ratio online, inversely calculating the target stiffness of the outer air spring group. k 1* Target stiffness of the central air spring k 2* and system target damping c * A coordinated command is generated and output to the pneumatic system, driving the outer air spring electro-proportional valve 65 and the central air spring electro-proportional valve 66 to adjust the output air pressure, thereby changing the air spring stiffness. Another output is sent to the electro-hydraulic proportional valve 311a of the hydraulic unit to adjust the valve core opening, thereby achieving the damping coefficient adjustment. cContinuous control is achieved. In the floor slab application embodiment, when the pedestrian excitation frequency is 2.5Hz, the system can complete frequency identification and parameter optimization within seconds, tuning the vibration damping device to its optimal state. For pedestrian bridge applications, a larger tuning mass block 02 is adapted, and the signal from the wire-type displacement sensor 42 is integrated, employing a multi-fixed-point optimization strategy to handle low-frequency broadband excitation. In the pneumatic active control system, the air source processing module 62 filters and stabilizes the compressed air, the pressure relief valve 63 provides overpressure protection, and the proportional valve pre-splitting tee 64 divides the main air path into two independent air paths, which are controlled by electric proportional valves 65 and 66 respectively, and then distributed to the outer air spring via the air spring assembly tee 67, ensuring the accuracy and reliability of air pressure regulation. The overall design of the device, through symmetrical layout and component integration, achieves high sensitivity response to micro-amplitude vibrations. At the same time, combined with adaptive algorithms, it effectively overcomes the detuning problem of traditional TMDs, improving vibration damping efficiency and applicability.

[0038] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0039] The above-described embodiments are merely illustrative of several implementations of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements all fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the appended claims.

Claims

1. An adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in structures, characterized in that, The device includes a support base, a tuned mass block, and a vibration system, a pneumatic active control system, and an intelligent measurement and control system connected between the support base and the tuned mass block. The vibration system includes an outer stiffness adjustment unit and an inertial-capacitive damping subsystem connected in parallel. The outer stiffness adjustment unit includes at least one set of outer air springs, the outer air springs comprising one or more air springs connected in parallel, the upper end of each air spring being connected to the tuning mass block, and the lower end being connected to the bearing base via a support. The inertial-capacitive damping subsystem consists of a central air spring and a parallel hydraulic inertial-capacitive damping unit connected in series. The lower end of the central air spring is connected to the bearing base via a support, and the upper end is connected to the lower end of the parallel hydraulic inertial-capacitive damping unit. The upper end of the parallel hydraulic inertial-capacitive damping unit is connected to the tuning mass block. The parallel hydraulic inertial-capacitive damping unit includes a hydraulic cylinder, a piston disposed within the hydraulic cylinder, and a piston rod connected to the piston. The piston divides the inner cavity of the hydraulic cylinder into a first chamber and a second chamber. The parallel hydraulic inertial-capacitive damping unit also includes an adjustable damping branch and a fixed inertial-capacitive branch, with their two ends respectively connected to the first chamber and the second chamber. The adjustable damping branch and the fixed inertial-capacitive branch are connected in parallel. The adjustable damping branch is equipped with an electro-hydraulic proportional valve for providing continuously adjustable damping force, and the fixed inertial-capacitive branch is equipped with a helical-tube hydraulic inertial container for providing mass amplification effect. The pneumatic active control system includes an air source and at least two independent control air paths. Each independent control air path is branched off from the main air path of the air source and is equipped with an electro-proportional valve to independently connect to and control the air pressure of the outer air spring assembly and the central air spring. The intelligent measurement and control system includes sensors for acquiring vibration response signals of the main structure and a central controller. The input terminal of the central controller is connected to the sensors, and the output terminal is connected to the electro-hydraulic proportional valve and each electro-hydraulic proportional valve in the pneumatic active control system. The central controller is configured to: identify the current dominant excitation frequency based on the sensor signals, solve for the optimal stiffness parameters and damping parameters based on the excitation frequency and a preset coupled dynamics model, and generate control commands to synchronously adjust the air pressure output of the electro-hydraulic proportional valve and the opening degree of the electro-hydraulic proportional valve.

2. The adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in structures according to claim 1, characterized in that, The outer air spring assembly includes a first outer air spring and a second outer air spring connected in parallel; in the pneumatic active control system, an independent control air path connected to the outer air spring assembly supplies air to the first outer air spring and the second outer air spring simultaneously through a split tee.

3. The adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in structures according to claim 1, characterized in that, The central controller is configured to: when the identified excitation frequency is close to the natural frequency of the main structure, use a fixed-point theory optimization strategy to solve for the optimal parameters; when the identified excitation frequency is far from the natural frequency of the main structure, use a frequency tracking strategy to solve for the optimal parameters.

4. The adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in structures according to claim 1, characterized in that, The sensors include an accelerometer for measuring the acceleration of the main structure and / or a wire-type displacement sensor for measuring the relative displacement between the main structure and the tuned mass.

5. The adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in structures according to claim 1, characterized in that, The pneumatic active control system also includes an air source processing module and a pressure relief valve located downstream of the air source.

6. The adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in structures according to claim 1, characterized in that, The support base is connected to the main structure at a single point.

7. The adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations in structures according to claim 1, characterized in that, The inertial coefficient b of the fixed inertial capacity branch is determined by the formula b = ρL² / A, where ρ is the fluid density, L is the pipe length of the helical hydraulic inertial container, and A is the pipe cross-sectional area.

8. An adaptive tuned inertial capacitance vibration reduction method for suppressing vertical micro-vibrations in structures, characterized in that, The method employs an adaptive tuned inertial capacitance vibration reduction device for suppressing vertical micro-vibrations of a structure as described in any one of claims 1 to 7, the method comprising: S1. Real-time acquisition of vibration response signals of the main structure through sensors; S2. The central controller performs frequency domain analysis on the vibration response signal to identify the currently dominant excitation frequency; S3. Based on the identified excitation frequency and the pre-established two-degree-of-freedom coupled dynamic model of the main structure-vibration damping device, the current optimal target stiffness of the outer air spring group, the target stiffness of the central air spring, and the target damping coefficient of the system are calculated online through an adaptive tuning algorithm. S4. The central controller generates coordinated control commands and executes them synchronously: S4a. Send a command to the corresponding electro-proportional valve in the pneumatic active control system to adjust its output air pressure so that the stiffness of the outer air spring assembly and the central air spring approaches their corresponding target stiffness. S4b: Send a command to the electro-hydraulic proportional valve in the parallel hydraulic inertial-capacitive damping unit to adjust its opening degree so that the system damping coefficient approaches the target damping coefficient.

9. The adaptive tuned inertial capacitance vibration reduction method for suppressing vertical micro-vibrations in structures according to claim 8, characterized in that, In S3, the two-degree-of-freedom coupled dynamic model includes at least the main structure displacement, the tuned mass block displacement, the equivalent stiffness of the outer air spring group, the equivalent stiffness of the central air spring, the damping coefficient of the adjustable damping branch, and the inertial capacity coefficient of the spiral tube hydraulic inertial container as parameters.

10. The adaptive tuned inertial capacitance vibration reduction method for suppressing vertical micro-vibrations in structures according to claim 8 or 9, characterized in that, In step S3, different parameter optimization strategies are dynamically selected to solve the problem based on the relative relationship between the excitation frequency and the natural frequency of the main structure.

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