Bridge vibration exciting and damping integrated device, bridge and laying method

Abstract

The application relates to the technical field of bridge vibration control, in particular to a bridge excitation and damping integrated device, a bridge and a laying method. The bridge excitation and damping integrated device comprises a mass block, a spring assembly, an actuator and two groups of lever assemblies. The middle part of the mass block is provided with a mounting hole, and a flywheel is arranged on the mass block. The spring assembly is arranged below the mass block and connected with the mass block, and the other end is connected with a structure to be damped. The actuator is arranged in the range of the mounting hole. The two groups of lever assemblies are respectively connected with the mass blocks on the two sides of the mounting hole through power arm ends, and the resistance arm ends are connected with the end parts of the telescopic rods of the actuator. When the telescopic rods of the actuator are telescopically extended or retracted, the mass blocks are driven to move up and down through the lever assemblies. The problem that the damping effect is only predicted through numerical simulation or simplified model test in the prior art and it is difficult to adjust parameters after installation can be solved. In addition, the nesting layout of the actuator and the mass block can reduce the requirement for the installation space by using the lever displacement amplification principle.

Description

Technical Field

[0001] This invention relates to the field of bridge vibration control technology, specifically to an integrated bridge excitation and vibration reduction device, a bridge, and a deployment method. Background Technology

[0002] Engineering structures, especially flexible structures such as long-span bridges, high-rise buildings, and towering masts, are prone to significant vibrations under environmental loads such as wind, traffic, crowds, and earthquakes. Long-term vibrations not only affect the normal performance and comfort of the structure but may also cause fatigue damage and even threaten its safety and stability. Therefore, effectively suppressing harmful structural vibrations has always been one of the core challenges in research and practice in the field of civil engineering.

[0003] Among various structural vibration control technologies, passive vibration control devices are widely used due to their relatively simple construction, lack of external power requirements, and high reliability. The tuned mass damper (TMD) is one of the most classic passive control devices. Its basic principle is to add a substructure system consisting of a mass block, springs, and damping elements to the main structure. By precisely designing the mass, stiffness, and damping parameters of this subsystem, its vibration frequency is made close to the target modal frequency of the main structure (i.e., "tuning"). When the main structure resonates, the mass block in the TMD system generates an inertial force opposite to the vibration direction of the main structure, and dissipates energy through the damping elements, thereby effectively suppressing the vibration response of the main structure.

[0004] However, traditional TMD systems also exhibit some inherent limitations in practical applications: poor parameter fixation and environmental adaptability. Once a traditional TMD is designed, manufactured, and installed, its mass, stiffness, and damping parameters are fixed. However, during the service life of an engineering structure, its dynamic characteristics (such as frequency and damping ratio) may slowly change due to material aging, changes in load conditions, or damage accumulation; simultaneously, the characteristic frequencies of environmental excitations (such as different wind speeds and traffic flows) are not constant. This means that a TMD pre-tuned to a fixed frequency may experience "detuning" in complex and variable environments, leading to a significant decrease in vibration reduction efficiency.

[0005] The vibration reduction effect of traditional TMD (Transformer Motion Detector) is highly dependent on the degree of matching between its parameters and the actual dynamic characteristics of the structure. Before the device is installed on the actual structure, its theoretical vibration reduction effect can usually only be predicted through numerical simulation or simplified model tests. Due to the simplification error of the numerical model and the existence of factors such as actual structural boundary conditions, material nonlinearity, and manufacturing and installation deviations, there are often differences between this theoretical prediction and the actual field effect. This leads to a certain degree of blindness in the design, and once the effect is not good after installation, adjusting the parameters or location is costly or even impossible. Summary of the Invention

[0006] In view of the shortcomings of the existing technology, the purpose of this invention is to provide an integrated bridge vibration excitation and damping device, a bridge and a deployment method, which can solve the problem that the vibration reduction effect of traditional TMD in the existing technology is usually predicted only by numerical simulation or simplified model test, resulting in a certain degree of blindness in the design, poor effect after installation, and high cost or even difficulty in adjusting parameters or positions.

[0007] To achieve the above objectives, the technical solution adopted by the present invention is as follows:

[0008] On one hand, the present invention provides an integrated device for bridge vibration excitation and damping, characterized in that it comprises:

[0009] A mass block has a mounting hole in its middle and a flywheel on the mass block. The flywheel rotates when the mass block moves to provide inertial mass.

[0010] A spring assembly is located below and connected to the mass block, with its other end used to connect to the structure to be damped.

[0011] An actuator is disposed within the range of the mounting hole;

[0012] Two sets of lever assemblies are provided. The power arm ends of the two sets of lever assemblies are respectively connected to the mass blocks on both sides of the mounting hole, and the resistance arm ends are connected to the end of the telescopic rod of the actuator. When the telescopic rod of the actuator extends or retracts, it drives the mass blocks to move up and down through the lever assemblies.

[0013] In some alternative solutions, a vertical guide rail is provided in the mounting hole, and a slider is provided on the vertical guide rail. The slider is located at the end of the telescopic rod of the actuator and is connected to the end of the resistance arm of the lever assembly.

[0014] In some alternative solutions, the mass block is provided with a guide hole, and a vertically fixed lead screw is provided in the guide hole. A flywheel is provided on one side of the mass block, and the flywheel is rotatably connected to the mass block and is sleeved on the lead screw through a threaded groove provided in the middle.

[0015] In some alternative solutions, four guide holes are provided, circumferentially spaced outside the mounting hole. Each guide hole is equipped with a lead screw and a flywheel. The mass block is connected to the flywheel via a bidirectional thrust bearing.

[0016] In some alternative solutions, the flywheel is provided with multiple circumferentially spaced slide rails, which are arranged along the radial direction of the flywheel and have sliding mass blocks on them, and the sliding mass blocks are adjustable in position on the slide rails.

[0017] In some alternative solutions, the spring assembly includes a first spring group and a second spring group, which are located on both sides of the mounting hole, respectively. Both the first spring group and the second spring group include multiple springs, each of which is divided into an upper spring section and a lower spring section, and a spring partition is provided between the upper spring section and the lower spring section.

[0018] On the other hand, the present invention also provides a bridge equipped with the vibration excitation and damping integrated device described in any of the above claims.

[0019] In another aspect, the present invention also provides a method for deploying an integrated bridge vibration excitation and damping device, which is implemented using any of the aforementioned integrated bridge vibration excitation and damping devices, including:

[0020] The extension frequency of the actuator is set according to the modal frequency of the structure to be vibration-damped;

[0021] The actuator is activated, and when the structure to be vibration-damped reaches the set test amplitude, the actuator is stopped.

[0022] A damper is connected to the outside of the mass block to disconnect the power arm end of the lever assembly from the mass block and retract the telescopic rod of the actuator.

[0023] Record the time it takes for the structure to be vibrated to decrease to the set amplitude, adjust the inertial mass provided by the flywheel, repeat the excitation and damping process, and select the configuration with the shortest damping time as the flywheel parameter by recording the structure vibration decay time under different flywheel parameters.

[0024] In some alternative solutions, the flywheel is provided with a position-adjustable sliding mass block, and the mass block is adjusted by adjusting the position of the sliding mass block.

[0025] In some alternative solutions, before the step of setting the extension frequency of the actuator according to the modal frequency of the structure to be vibration-damped, the following method is further included:

[0026] Test the tuning frequency of the vibration damping device corresponding to the inertial mass of different flywheels;

[0027] The initial parameters of the flywheel are set based on the modal frequency and tuning frequency.

[0028] Compared with existing technologies, the advantages of this invention are as follows: Controllable excitation of the structure is achieved by using an actuator telescopic rod to move a mass block up and down via a lever assembly; excitation stops when the structure reaches a set amplitude, and then a damper is connected to the outside of the mass block and disconnected from the lever assembly, switching the device to vibration reduction mode; by recording the vibration decay time of the structure under different flywheel parameters, the configuration with the shortest decay time is selected as the optimal parameter. This device ingeniously integrates excitation and vibration reduction functions into the same system. During the excitation phase, the lever assembly converts the linear motion of the actuator into the up and down movement of the mass block, applying controllable excitation to the structure; the flywheel parameters are adjusted to achieve optimal matching with the dynamic characteristics of the structure. This effectively solves the problems of fixed TMD parameters, difficulty in adapting to actual structural dynamic characteristics, and the high dependence of the vibration reduction effect on the degree of matching between its parameters and the actual dynamic characteristics of the structure; before the device is installed on the actual structure, its theoretical vibration reduction effect can usually only be predicted through numerical simulation or simplified model tests, and there is often a difference between theoretical predictions and actual field effects; leading to problems such as poor performance after installation, high costs for adjusting parameters or positions, and even difficulty in implementation.

[0029] Based on the lever displacement amplification principle, the mass block displacement = actuator stroke × resistance arm length / power arm length, achieving the effect of small stroke input and large displacement output, significantly reducing the requirements for actuator stroke specifications. Simultaneously, the nested three-dimensional layout of the actuator and mass block fully utilizes the internal space of the mass block, effectively solving the technical challenge of installing traditional TMD devices in space-constrained structures. Attached Figure Description

[0030] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0031] Figure 1 This is a three-dimensional structural diagram of the integrated bridge vibration excitation and damping device in an embodiment of the present invention;

[0032] Figure 2 This is a schematic diagram showing the mass block at the bottom in an embodiment of the present invention;

[0033] Figure 3 This is a schematic diagram showing the mass block located in the middle position in an embodiment of the present invention;

[0034] Figure 4 This is a schematic diagram showing the mass block at the top in an embodiment of the present invention;

[0035] Figure 5This is a top view of the flywheel structure in an embodiment of the present invention;

[0036] Figure 6 This is a front view schematic diagram of the flywheel structure in an embodiment of the present invention;

[0037] In the diagram: 1. Spring assembly; 11. Upper half of the spring; 12. Lower half of the spring; 13. Spring partition; 2. Mass block; 21. Connecting lug; 22. Pin; 3. Lever assembly; 31. First transmission rod; 32. Second transmission rod; 4. Actuator; 5. Vertical guide rail; 51. Sliding component; 511. Sliding block; 512. Mounting support; 52. Rotating support; 61. Lead screw; 62. Flywheel; 621. Slide rail; 622. Sliding mass block; 7. Support frame; 71. Column; 72. Crossbeam; 8. Base. Detailed Implementation

[0038] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0039] The embodiments of the present invention will be further described in detail below with reference to the accompanying drawings.

[0040] like Figures 1 to 4 As shown, the present invention provides an integrated device for bridge vibration excitation and damping, comprising: a mass block 2, a spring assembly 1, an actuator 4, and two sets of lever assemblies 3. The mass block 2 has a mounting hole in the middle and a flywheel 62 on it. The flywheel 62 rotates as the mass block 2 moves to provide inertial mass. The spring assembly 1 is located below the mass block 2 and connected to it, with its other end connected to the structure to be damped. The actuator 4 is located within the mounting hole. The two sets of lever assemblies 3 have their power arm ends connected to the mass blocks 2 on both sides of the mounting hole, and their resistance arm ends connected to the telescopic rod ends of the actuator 4. When the telescopic rod of the actuator 4 extends or retracts, it drives the mass block 2 to move up and down through the lever assemblies 3.

[0041] When using this device, the actuator 4 parameters are first set according to the modal frequency of the structure to be vibration-damped. The actuator 4's telescopic rod drives the mass block to move up and down via the lever assembly, achieving controlled excitation of the structure. When the structure reaches the set amplitude, the excitation stops. Then, a damper is connected to the outside of the mass block 2 and disconnected from the lever assembly 3, switching the device to vibration reduction mode. By recording the vibration decay time of the structure under different flywheel 62 parameters, the configuration with the shortest decay time is selected as the optimal parameter. This device cleverly integrates excitation and vibration reduction functions into the same system. During the excitation phase, the lever assembly converts the linear motion of the actuator 4 into the up and down movement of the mass block 2, applying controllable excitation to the structure. The optimal match between the flywheel 62 parameters and the structure's dynamic characteristics is achieved by adjusting the flywheel 62 parameters.

[0042] This solution effectively addresses the parameter mistuning problem of traditional tuned mass dampers (TMDs). Traditional TMDs have fixed parameters, making it difficult to adapt to the actual dynamic characteristics of the structure. This results in the vibration reduction effect being highly dependent on the degree of matching between the parameters and the actual dynamic characteristics of the structure. Before the device is installed on the actual structure, its theoretical vibration reduction effect can usually only be predicted through numerical simulation or simplified model tests. However, due to the simplification error of the numerical model, as well as the existence of factors such as the boundary conditions of the actual structure, material nonlinearity, and manufacturing and installation deviations, there are often differences between the theoretical prediction and the actual field effect. Once the effect is unsatisfactory after installation, adjusting the parameters or position is costly or even impossible.

[0043] This solution can directly assess the vibration reduction effect by recording the time it takes for the structure to be reduced to a set amplitude, thereby setting the flywheel 62 parameters and avoiding the blindness of traditional methods. Parameter optimization is completed before formal installation, significantly reducing the cost of adjusting parameters or positions after installation. In terms of engineering reliability, the vibration reduction effect is verified through actual testing to ensure that the vibration reduction system achieves optimal performance under actual working conditions, providing a more reliable guarantee for structural safety.

[0044] Furthermore, by using two sets of lever assemblies 3 and placing the actuator 4 in the mounting hole, the drive end of the actuator 4 and the mass block 2 are connected through the lever assemblies 3. The power arm end is connected to the mass blocks 2 on both sides of the mounting hole, and the resistance arm end is connected to the end of the telescopic rod of the actuator 4. The length of the resistance arm is less than the length of the power arm. By using two sets of symmetrical lever assemblies 3 and embedding the actuator into the mounting hole of the mass block 2, based on the lever displacement amplification principle, the mass block displacement = actuator stroke × resistance arm length / power arm length, the effect of small stroke input and large displacement output is achieved, significantly reducing the requirements for actuator stroke specifications. At the same time, through the nested three-dimensional layout of the actuator 4 and the mass block 2, the internal space of the mass block 2 is fully utilized, which can effectively solve the technical problem of traditional TMD devices being difficult to install in space-constrained structures.

[0045] In this example, the ratio of the length of the resistance arm to the length of the power arm is 1 to 4. Since the rotation angle of the lever assembly 3 is small, the lever scheme can reduce the stroke of the actuator 4 by about 4 times.

[0046] In some optional embodiments, a vertical guide rail 5 is provided in the mounting hole, and a slider 51 is provided on the vertical guide rail 5. The slider 51 is located at the end of the telescopic rod of the actuator 4 and is connected to the end of the resistance arm of the lever assembly 3.

[0047] See Figure 2 As shown, in this example, by setting a vertical guide rail 5 and configuring a slider 51 in the mounting hole, the end of the telescopic rod of the actuator 4 is connected to the end of the resistance arm of the lever assembly 3. The vertical guide rail 5 provides precise motion trajectory constraints for the telescopic rod of the actuator 4, ensuring that it moves only in the vertical direction, thereby improving force transmission efficiency and system stability. In addition, each lever assembly 3 includes two spaced lever units. Through the cooperation of the slider 51 and the vertical guide rail 5, the resistance arms of the four lever units of the two sets of lever assemblies 3 can be connected to the telescopic rod of the actuator 4, so that all lever units can be driven by a single actuator 4.

[0048] Furthermore, in this example, two spaced-apart vertical guide rails 5 are provided in the mounting hole, and a sliding member 51 is disposed between the two spaced-apart vertical guide rails 5. The sliding member 51 includes sliders 511 respectively disposed on the two vertical guide rails 5, and mounting supports 512 connected to the two sliders 511. The fulcrum of each lever unit is disposed at the end of the vertical guide rail 5 and is rotatably connected to the upper end of the vertical guide rail 5. Specifically, a rotating support 52 is provided at the upper end of the vertical guide rail 5, and the fulcrum of the lever unit is rotatably connected to the support, dividing the lever unit into a power arm and a resistance arm, and the length of the resistance arm is less than that of the power arm. The resistance arm is rotatably connected to the mounting support 512 through the second transmission rod 32.

[0049] This solution converts rotational motion into equivalent linear inertial mass by setting a flywheel 62 on the mass block 2 that rotates with its movement. Based on the principle of rotational inertia, it effectively solves the technical problems of limited installation space and increased structural load caused by the excessive physical mass block in traditional tuned mass dampers. The rotational inertia generated by the flywheel 62 when the mass block 2 moves can significantly improve the equivalent mass of the system, enhance the vibration reduction effect without increasing the actual weight, and at the same time greatly reduce the size of the device and the load requirements on the spring assembly 1. This not only improves the control efficiency of the TMD system for structural vibration, but also improves its applicability in space-constrained or weight-sensitive engineering environments.

[0050] In some optional embodiments, the mass block 2 is provided with a guide hole, and a vertically fixed lead screw 61 is provided in the guide hole. A flywheel 62 is provided on one side of the mass block 2. The flywheel 62 is rotatably connected to the mass block 2 and is sleeved on the lead screw 61 through a threaded groove provided in the middle.

[0051] In this embodiment, by setting a guide hole on the mass block 2 and installing a vertical fixed lead screw 61, the flywheel 62 is sleeved on the lead screw 61 through the central threaded groove and rotatably connected to the mass block 2. The linear vibration of the mass block 2 is converted into the rotational motion of the flywheel, which can effectively solve the space limitation and structural load problems caused by excessive physical mass in traditional tuned mass dampers. When the mass block 2 moves up and down, the flywheel 62 moves and rotates along the fixed lead screw 61, generating a significant moment of inertia, which greatly increases the equivalent mass of the system. At the same time, the frictional resistance generated by the rotational motion provides an additional energy dissipation path, which can improve the vibration reduction efficiency.

[0052] In some optional embodiments, four guide holes are provided, circumferentially spaced outside the mounting hole. Each guide hole is provided with a lead screw 61 and a flywheel 62. The mass block 2 is connected to the flywheel 62 through a bidirectional thrust bearing.

[0053] In this example, four guide holes are circumferentially spaced on the outside of the mounting hole, with a lead screw 61 and a flywheel 62 installed in each hole. A two-way thrust bearing is used to connect the mass block 2 and the flywheel 62. The four-point symmetrical layout makes the load evenly distributed, which can improve the rigidity of the entire device and also limit the mass block 2, which can improve the accuracy of the motion trajectory of the mass block 2. The two-way thrust bearing design ensures that the flywheel 62 can reliably withstand the two-way axial force during the reciprocating motion of the mass block 2, driving the flywheel 62 to move up and down without restricting the rotation of the flywheel 62. The superimposed rotational inertia generated by the coordinated work of the four flywheels can improve the equivalent mass.

[0054] In addition, the device is also equipped with a support frame 7 and a base 8. The support frame 7 includes multiple spaced columns 71. The tops of the multiple spaced columns 71 are connected in sequence by a crossbeam 72. The bottom of the columns 71 is fixed on the base 8. The lower ends of the spring assembly 1, the lead screw 61 and the vertical guide rail 5 are also fixed on the base 8. The upper end of the lead screw 61 is connected to the crossbeam 72.

[0055] Preferably, the flywheel 62 is provided with multiple circumferentially spaced slide rails 621, which are arranged along the radial direction of the flywheel 62 and are provided with sliding mass blocks 622, and the position of the sliding mass blocks 622 on the slide rails 621 is adjustable.

[0056] According to the excitation and vibration reduction frequency formula ,in, Let the stiffness of spring assembly 1 be... The mass of mass block 2 is the mass of the device. Adjusting the mass of mass block 2 can adjust the excitation and damping frequency of the entire device.

[0057] Furthermore, according to the formula for moment of inertia: Where M is the mass of flywheel 62, R is the radius of flywheel, m is the mass of sliding mass block 622, and r is the distance between sliding mass block 622 and the shaft.

[0058] This solution, by setting circumferentially spaced radial slide rails 621 on the flywheel 62 and configuring an adjustable sliding mass block 622, allows for continuous and stepless change of the system's moment of inertia I by adjusting the distance r between the sliding mass block 622 and the rotating shaft. This enables fine adjustment of the equivalent mass and the device's control frequency f, achieving precise matching with the vibration frequency of the structure to be vibration-damped. This design eliminates the need to replace the entire mass block 2 when the control frequency needs adjustment; the equivalent mass can be adjusted simply by changing the position of the sliding mass block 622. This significantly improves the convenience and accuracy of parameter adjustment and also significantly expands the frequency adjustment range, allowing the device to adapt to a wider range of vibration control needs. Furthermore, combined with on-site testing methods, the optimal parameter configuration can be quickly found to improve vibration reduction efficiency.

[0059] In this embodiment, the power arm end of the lever assembly 3 is connected to the mass block 2 via the first transmission rod 31, and the first transmission rod 31 is detachably connected to the mass block 2. The resistance arm end of the lever assembly 3 is connected to the telescopic rod end of the actuator 4 via the second transmission rod 32.

[0060] This solution utilizes a detachable connection design between the lever assembly 3 and the mass block 2 via a first transmission rod 31. This allows for easy transmission of the vertical displacement of the actuator 4's telescopic rod end to the mass block 2, enabling the mass block 2 to move vertically and reducing concentrated stress. Furthermore, the detachable connection facilitates switching between vibration testing and vibration reduction modes, achieving seamless transition from active vibration mode to passive vibration reduction mode. This design not only supports on-site parameter optimization processes but also significantly improves testing efficiency.

[0061] In other embodiments, the power arm end and the mass block 2 can be designed to be slidably connected, but this would be more troublesome to disconnect. Similarly, the connection between the mass block 2 and the telescopic rod end of the actuator 4 can also be in other ways, such as a sliding connection, to reduce the concentrated stress of the mass block 2 and the telescopic rod of the actuator 4 when they make vertical movements.

[0062] In this example, the specific implementation is as follows: a connecting lug 21 is provided at the connection between the mass block 2 and the first transmission rod 31. The connecting lug 21 and the first transmission rod 31 are connected by a pin 22. In this example, when it is necessary to disconnect the mass block 2 from the first transmission rod 31, it is only necessary to remove the pin 22, which is convenient to operate.

[0063] In some alternative embodiments, the spring assembly 1 includes a first spring group and a second spring group, which are located on both sides of the mounting hole. Both the first spring group and the second spring group include multiple springs, each spring being divided into an upper half spring 11 and a lower half spring 12, with a spring partition 13 provided between the upper half spring 11 and the lower half spring 12.

[0064] In this embodiment, by designing the spring assembly 1 as a symmetrically distributed double spring group, the first spring group and the second spring group are located on both sides of the mounting hole and adopt a segmented structure. Each spring is divided into an upper half spring 11 and a lower half spring 12, with a spring partition 13 in the middle, which can improve the stability of the entire spring assembly 1. The symmetrical arrangement on both sides ensures the stability of the vertical movement of the mass block 2.

[0065] In addition, in the preferred embodiment, the spring partition 13 can be fixed. When the structural amplitude is small and the vibration frequency is high, the spring partition 13 can be fixed, allowing only the upper half of the spring 11 to participate in the work and provide higher stiffness. When a large amplitude is required, the upper and lower springs work together, enabling the system to maintain efficient vibration reduction over a wider range of vibration frequencies. At the same time, the parallel design of multiple springs greatly improves the reliability of the system. The spring partition 13 also plays a role in dispersing stress and extending fatigue life, which can significantly improve the stability and durability of the device under extreme vibration conditions.

[0066] In addition, this device also sets a damper connection point on the outside of mass block 2, and sets a damper on the outside of mass block 2. After the excitation is completed by using this bridge excitation and damping integrated device and the mass block 2 stops moving up and down, the damper set on the outside of mass block 2 is connected to the damper connection point set on the outside of mass block 2, thereby realizing the conversion from exciter to damper.

[0067] Secondly, the present invention also provides a bridge equipped with the integrated vibration excitation and damping device described in any of the above embodiments. The structure and function of this integrated vibration excitation and damping device are the same as those in the above embodiments, and will not be described in detail here.

[0068] like Figures 1 to 6 As shown, in a third aspect, the present invention also provides a method for deploying an integrated bridge vibration excitation and damping device, implemented using any of the aforementioned integrated bridge vibration excitation and damping devices, comprising:

[0069] S1: Set the extension frequency of actuator 4 according to the modal frequency of the structure to be vibration-damped.

[0070] Before formal parameter optimization, the modal frequencies of the structure are first determined by performing a frequency sweep test using the device's own excitation function. The specific process is as follows:

[0071] The damper is installed on the structure to be vibration-damped. The actuator 4 is set to a frequency that varies continuously within a preset frequency range. The lever assembly 3 drives the mass block 2 to apply excitation to the structure. Simultaneously, an accelerometer is used to monitor the vibration response of the structure. The preset frequency range is determined according to the structure type, such as 0.1-5Hz. When the excitation frequency approaches the natural frequency of the structure, the amplitude of the structural response will increase significantly, indicating resonance. By analyzing the vibration response amplitude-frequency curve, the main vibration modes of the structure and their corresponding frequencies can be determined; these frequencies are the modal frequencies. Compared to traditional TMD design that relies solely on theoretical calculations, this method directly obtains the actual dynamic characteristics of the structure under actual boundary conditions. This ensures the accuracy of the crucial step of setting the extension frequency of the actuator 4 based on the modal frequencies of the structure to be vibration-damped, laying the foundation for achieving the best vibration reduction effect.

[0072] S2: Start actuator 4. When the structure to be vibration-damped reaches the set test amplitude, stop actuator 4.

[0073] This step controls actuator 4 to operate according to a preset modal frequency, causing the structure to vibrate at the same modal frequency. When the structural response reaches the preset test amplitude, the excitation is stopped immediately. This establishes a uniform initial vibration condition, ensuring that the time it takes for the structure to be vibrated to decrease to the set amplitude is comparable and avoiding the influence of different initial amplitudes on the decay time during the vibration reduction stage.

[0074] In addition, the stop actuator 4 can forcibly constrain the mass block 2 to stop its vertical displacement, providing conditions for connecting a damper to the outside of the mass block 2 and disconnecting the power arm end of the lever assembly 3 from the mass block 2.

[0075] S3: Connect a damper to the outside of mass block 2, disconnect the power arm end of lever assembly 3 from mass block 2, and retract the telescopic rod of actuator 4.

[0076] In this scheme, by connecting a damper to the outside of mass block 2 and disconnecting the power arm end of lever assembly 3 from mass block 2, a seamless switch from excitation testing mode to vibration reduction working mode is achieved. Connecting a damper to the outside of mass block 2 transforms the device from a simple excitation device into a complete tuned mass damper. The introduction of the damper enables the system to effectively dissipate structural vibration energy. Disconnecting the power arm end of lever assembly 3 from mass block 2 eliminates the constraint of the excitation mechanism on the movement of the mass block and avoids interference with the free vibration of the mass block during the vibration reduction phase. Retracting the telescopic rod of actuator 4 ensures that the vibration of the mass block is not hindered. This scheme allows the same device to accurately test the dynamic characteristics of the structure and immediately convert it into a high-efficiency vibration reduction system, realizing an integrated process of testing-optimization-application, and significantly improving parameter matching accuracy and engineering implementation efficiency.

[0077] S4: Record the time it takes for the structure to be vibration-damped to decrease to the set amplitude, adjust the inertial mass provided by the flywheel 62, repeat the excitation and damping process, and select the configuration with the shortest damping time as the parameters of the flywheel 62 by recording the structural vibration decay time under different flywheel 62 parameters. Also, configure the flywheel 62 settings corresponding to the shortest time for the structure to be vibration-damped to decrease to the set amplitude into the integrated excitation and damping device for this bridge.

[0078] By adjusting the flywheel 62 parameters and repeating the excitation and damping processes, the vibration energy transfer is most effective and the structural vibration decays fastest when the natural frequency of the TMD system precisely matches the vibration frequency of the main structure. By recording the time it takes for the structure to reduce its vibration to the set amplitude, the damping effect under different flywheel 62 parameters is directly quantified and evaluated. Finally, the flywheel 62 parameters corresponding to the shortest time are selected as the optimal configuration. Compared to traditional methods, this step transforms theoretical prediction of parameter determination into practical verification, enabling the TMD system to truly adapt to the actual dynamic characteristics of a specific structure and significantly reducing the cost and risk of adjusting parameters after installation.

[0079] In some optional embodiments, the mass block 2 is provided with a flywheel 62 that rotates as the mass block 2 moves, and the flywheel 62 is provided with a sliding mass block 622 whose position is adjustable. By adjusting the position of the sliding mass block 622, the mass of the mass block 2 is adjusted.

[0080] In this scheme, the equivalent mass of the system is infinitely adjusted by changing the radial distance from the sliding mass block 622 to the rotation axis, which solves the detuning problem caused by fixed mass parameters in traditional TMD systems. Specifically, based on the moment of inertia formula I=1 / 2MR²+mr², when the sliding mass block 622 moves outward, the system's moment of inertia I increases significantly, thus effectively increasing the mass of mass block 2; conversely, moving it inward decreases the equivalent mass. This design makes mass parameter adjustment simple and efficient, eliminating the need to replace the entire mass block 2, only requiring adjustment of the position of the sliding mass block 622. During vibration tests, the time it takes for the structure to be damped to decrease to the set amplitude is recorded, and the parameter optimization process of the excitation and damping processes is repeated, which also saves time.

[0081] Before step S1, the following is also included:

[0082] S01: Test the tuning frequency of the vibration damping device corresponding to the inertial mass of different flywheels 62.

[0083] A: Before installing the integrated bridge vibration excitation and damping device onto the structure to be damped, fix the integrated bridge vibration excitation and damping device in place and set the flywheel 62 parameters.

[0084] B: Load mass block 2, causing it to displace to its ultimate displacement Sd; release the constraint on mass block 2, allowing it to vibrate freely along the direction of motion. Collect displacement or acceleration time history data of mass block 2 during its free vibration using a dynamic testing system, and plot the time history curve of the vibration amplitude. The ultimate displacement Sd refers to the displacement of mass block 2 compressed by spring assembly 1.

[0085] C: Take the second peak (t2, a2) and the fifth peak (t5, a5) in the vibration time history curve of mass block 2 as the calculation points for frequency and damping. f d The initial damping ratio is 1 / 3(t5-t2). d The frequency is ln(a2 / a5) / 6π. Three experiments are conducted, and the average value of the experimental results is taken as the initial tuning frequency. f d0 And the initial damping ratio ζ d0 Where t2 is the time of the second peak, a2 is the displacement of the second peak, t5 is the time of the fifth peak, and a5 is the displacement of the fifth peak.

[0086] D: Loading is performed using a displacement method, the loading waveform is a sine wave, and the loading frequency is... f d0 The set amplitude and total number of load cycles are then applied. After the test, step C is followed to conduct damping ratio and tuning frequency tests on the specimen to obtain the tuning frequency of the specimen after the fatigue test. f d1Damping ratio ζ d1 Specifically, when the integrated bridge vibration excitation and damping device is used for vibration control of pedestrian bridges, the amplitude is set to ±1mm and the total number of cycles is not less than 400; when the damper is used for wind vibration control of bridges, the amplitude is set to ±limit displacement Sd and the total number of cycles is not less than 60,000.

[0087] The above steps can verify the durability of this integrated device as a vibration damping device. If the initial frequency is tuned... f d0 And the initial damping ratio ζ d0 Tuning frequency after corresponding experiment f d1 Damping ratio ζ after test d1 If the rate of change between the parameters is less than the set value, the durability of the integrated device is considered to meet the requirements. If the rate of change is less than the set value, the durability of the integrated device is considered to fail to meet the requirements, and the design parameters need to be readjusted.

[0088] In addition, the tuning frequency and damping ratio of the vibration damping device can be obtained.

[0089] In addition, the frequency and damping ratio of the TMD damper are obtained through experimental testing. If there is a deviation from the design parameters, it is necessary to adjust the frequency by adjusting the spring stiffness or the mass of the mass block, and adjust the damper parameters to adjust the damping ratio.

[0090] S02: Set the initial parameters of flywheel 62 according to the modal frequency and tuning frequency.

[0091] The tuning frequency of the vibration damping device is obtained through step S01. In order for the vibration damping device to better control the vibration of the structure to be damped, the tuning frequency of the vibration damping device needs to be the same as the modal frequency of the structure to be damped. Therefore, the initial parameters of the flywheel 62 are set to be the same as the tuning frequency of the vibration damping device and the modal frequency of the structure to be damped. In this way, the time to adjust the parameters of the flywheel 62 is shorter when the integrated device is used as a vibration damping device.

[0092] In the description of this application, it should be noted that the terms "upper," "lower," etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. Unless otherwise expressly specified and limited, the terms "installed," "connected," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication between two elements. For those skilled in the art, the specific meaning of the above terms in this application can be understood according to the specific circumstances.

[0093] It should be noted that in this application, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0094] The above description is merely a specific embodiment of this application, enabling those skilled in the art to understand or implement this application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this application. Therefore, this application is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. A bridge vibration excitation and damping integrated device, characterized in that, include: A mass block (2) has a mounting hole in its middle and a flywheel (62) is provided on the mass block (2). The flywheel (62) rotates when the mass block (2) moves to provide inertial mass. A spring assembly (1) is located below the mass block (2) and connected to the mass block (2), with its other end used to connect to the structure to be damped; Actuator (4), which is located within the range of the mounting hole; Two sets of lever assemblies (3), the power arm ends of the two sets of lever assemblies (3) are respectively connected to the mass blocks (2) on both sides of the mounting hole, and the resistance arm ends are connected to the telescopic rod end of the actuator (4). When the telescopic rod of the actuator (4) extends or retracts, it drives the mass blocks (2) to move up and down through the lever assemblies (3). A damper connection point is provided on the outside of the mass block (2), and a damper is provided on the outside of the mass block (2) for disconnecting the power arm end of the lever assembly (3) from the mass block (2) after the excitation is completed and the mass block (2) stops moving up and down, and connecting the damper to the damper connection point provided on the outside of the mass block (2).

2. The integrated bridge vibration excitation and damping device as described in claim 1, characterized in that, The mounting hole is provided with a vertical guide rail (5), and a sliding member (51) is provided on the vertical guide rail (5). The sliding member (51) is located at the end of the telescopic rod of the actuator (4) and connected to the end of the resistance arm of the lever assembly (3).

3. The integrated bridge vibration excitation and damping device as described in claim 1, characterized in that, The mass block (2) is provided with a guide hole, and a vertically fixed lead screw (61) is provided in the guide hole. A flywheel (62) is provided on one side of the mass block (2). The flywheel (62) is rotatably connected to the mass block (2) and is sleeved on the lead screw (61) through a threaded groove provided in the middle.

4. The integrated bridge vibration excitation and damping device as described in claim 3, characterized in that, The guide hole is provided in four places, which are circumferentially spaced outside the mounting hole. Each guide hole is provided with a lead screw (61) and a flywheel (62). The mass block (2) and the flywheel (62) are connected by a bidirectional thrust bearing.

5. The integrated bridge vibration damping device as described in claim 3 or 4, characterized in that, The flywheel (62) is provided with multiple circumferentially spaced slide rails (621), the slide rails (621) are arranged along the radial direction of the flywheel (62), and a sliding mass block (622) is provided on it, and the position of the sliding mass block (622) on the slide rail (621) is adjustable.

6. The integrated bridge vibration excitation and damping device as described in claim 1, characterized in that, The spring assembly (1) includes a first spring group and a second spring group. The first spring group and the second spring group are located on both sides of the mounting hole. The first spring group and the second spring group each include multiple springs. Each spring is divided into an upper half spring (11) and a lower half spring (12). A spring partition (13) is provided between the upper half spring (11) and the lower half spring (12).

7. A bridge, characterized in that, It is equipped with an integrated bridge vibration reduction device as described in any one of claims 1-6.

8. A method for arranging an integrated bridge vibration excitation and damping device, characterized in that, This is achieved using the integrated bridge vibration damping device as described in any one of claims 1-6, comprising: The extension frequency of the actuator (4) is set according to the modal frequency of the structure to be vibration-damped; Start the actuator (4), and stop the actuator (4) when the structure to be vibration reduced reaches the set test amplitude. Connect a damper to the outside of the mass block (2), disconnect the power arm end of the lever assembly (3) from the mass block (2), and retract the telescopic rod of the actuator (4); Record the time it takes for the structure to be vibrated to decrease to the set amplitude, adjust the inertial mass provided by the flywheel (62), repeat the excitation and damping process, and select the configuration with the shortest damping time as the parameter of the flywheel (62) by recording the vibration decay time of the structure to be vibrated under different flywheel (62) parameters.

9. The method for arranging the integrated bridge vibration excitation and damping device as described in claim 8, characterized in that, The flywheel (62) is provided with a sliding mass block (622) with adjustable position. By adjusting the position of the sliding mass block (622), the mass of the mass block (2) can be adjusted.

10. The method for arranging the integrated bridge vibration excitation and damping device as described in claim 8, characterized in that, Before the step of setting the extension frequency of the actuator (4) according to the modal frequency of the structure to be vibration-damped, the method further includes: Test the tuning frequency of the vibration damping device corresponding to the inertial mass of different flywheels (62); The initial parameters of the flywheel (62) are set according to the modal frequency and the tuning frequency.

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