Broadband inertia-enhanced vibration isolator and vibration-damping track

Abstract

The application provides a broadband inertia enhanced vibration isolator and a novel damping track, wherein the broadband inertia enhanced vibration isolator comprises an outer cylinder, a spring, a granular damping inertia container and an inner cylinder, the spring is arranged in the inner cylinder, and the granular damping inertia container is sleeved in the spring; the granular damping inertia container comprises a ball screw pair, a flywheel containing granular substances and a base, the flywheel is coaxially fixedly connected with the ball screw pair at a nut of the ball screw pair; a first end of the ball screw pair is fixedly connected on the outer cylinder, and a second end is connected in the base and can rotate around an axis. The broadband inertia enhanced vibration isolator provided by the application is composed of an outer cylinder, a spring, an inner cylinder and other components, the granular damping inertia container in the broadband inertia enhanced vibration isolator is both an inertia container and a granular damper, and is applied to a track, so that the comprehensive damping capacity of a spring floating slab track in a full frequency band can be effectively improved.

Description

Technical Field

[0001] This invention relates to the field of engineering vibration reduction equipment, and in particular to a broadband inertial enhancement vibration isolator and a novel vibration reduction track. Background Technology

[0002] Urban rail transit operates in cities of all sizes, with trams and subways being common types. These are high-capacity, fast, convenient, and environmentally friendly public transportation options, providing residents with a good choice for travel. However, as lines become increasingly dense and urban buildings gradually cluster around rail lines, the environmental vibration problems caused by urban rail transit are becoming more prominent. This affects the work and lives of residents along the lines, jeopardizes the functionality of ancient buildings, concert halls, and other special structures, and may even interfere with the normal use of precision instruments in hospitals, universities, and research institutes along the lines.

[0003] Steel spring floating slab track is a vibration reduction measure with good vibration reduction effect that can be applied to urban rail transit, with a maximum vibration reduction effect of up to 25dB. Steel spring floating slab track consists of rails, fasteners, sleepers, floating slabs, vibration isolators, and other foundation structures. The track slab is supported and suspended by vibration isolators (referred to as "floating slabs"). The mass of the floating slabs and the elasticity and damping of the vibration isolators form a "mass-elasticity-damping" system. Through tuning filtering and damping energy dissipation, this system isolates wheel-rail vibration from being transmitted to the lower foundation, reducing the impact of vibration on the track environment.

[0004] However, theoretical research and engineering applications have shown that steel spring floating slab track structures based on vibration isolation principles suffer from problems such as resonance amplification near the natural frequency, insufficient damping energy dissipation and low-frequency vibration reduction, and large rail displacement amplitude. In particular, with the accelerated construction of urban rail transit lines (speeds of 100km / h-160km / h) in my country (for example, the Guangzhou Metro Line 22 currently under construction, which will connect Guangzhou Nansha Science City, Dongguan Binhai Bay New Area, and Shenzhen Guangming Science City, designed for a speed of 160 km / h), higher requirements are placed on the vibration reduction performance of track structures, the safety of high-speed train operation, and stability. Therefore, in response to the new characteristics of accelerated urban rail transit operation, it is necessary to develop new track structures based on new technologies and methods.

[0005] In existing vibration reduction technologies, a novel type of inertial mechanical element with two ends was summarized and refined by British scholar Simth in the early 21st century. The axial force at each end point is proportional to the relative acceleration at both ends; this ratio is called the "inertial capacitance coefficient" or "apparent mass." The apparent mass of the flywheel can reach hundreds of times its actual physical mass, exhibiting a significant inertial amplification effect. Based on this principle, its inertial amplification effect allows for the generation of a large inertial force with a relatively small physical mass, solving the problems of insufficient effectiveness with small masses and inconvenient installation and additional dynamic effects with large masses faced by traditional inertial elements. Furthermore, inertial capacitance also has advantages such as widening the low-frequency vibration reduction band, providing anti-resonance capability, suppressing resonance peaks, and suppressing low-frequency resonance amplification of floating slabs. Based on these advantages, inertial capacitance has been widely applied in the theoretical research of vibration reduction in mechanical and civil engineering structures, and has achieved excellent vibration reduction results in practical projects such as Formula 1 racing cars and the vibration reduction project of the NTT building in Japan.

[0006] Furthermore, particle damping technology originated in the fields of aerospace and mechanical vibration control, dating back to the 1930s. In 1937, Pagat invented the impact damper while studying turbine blade vibration reduction. Subsequently, in 1945, Lieber et al. applied the impact damper to control aircraft flutter. However, this impact damper contained only a single particle, resulting in significant impact force and noise during collisions, and was highly sensitive to changes in influencing parameters (such as excitation amplitude, particle movement gaps, and coefficient of restitution). To overcome the shortcomings of the impact damper and to increase the number of collisions between the particle and the cavity, researchers replaced the single particle with multiple particles of equal mass, thus creating the particle damper. In summary, in the fields of aerospace and mechanical vibration control, particle dampers offer numerous advantages, including good vibration reduction effect, wide operating frequency range, minimal modification to the original structure, flexible arrangement, low cost, maintenance-free operation, and long service life. Therefore, particle damping technology holds promise for widespread research and application in vibration reduction and isolation of civil engineering structures.

[0007] In summary, combining the advantages of inertial capacitance, such as providing anti-resonance capabilities, suppressing resonance peaks, reducing response amplitude, and widening the low-frequency vibration reduction range, with the advantages of granular dampers, such as damping energy dissipation and wide-frequency vibration reduction, the design of a wide-frequency inertial-enhanced vibration isolator is expected to improve problems such as resonance amplification near the natural frequency of floating slab tracks, insufficient damping energy dissipation and low-frequency vibration reduction capabilities, and large rail displacement amplitude. Furthermore, it will provide effective vibration reduction tailored to the operational characteristics of urban express lines, ensuring the green, healthy, and sustainable development of urban rail transit. Summary of the Invention

[0008] Therefore, it is necessary to provide a wide-band inertial capacitance enhanced vibration isolator and a new type of vibration-damping track to address at least one of the problems mentioned above.

[0009] In the first aspect, this application provides a broadband inertial capacitance enhanced vibration isolator, including an outer cylinder, a spring, a particle damping inertial container, and an inner cylinder, wherein the inner cylinder is sleeved inside the outer cylinder, the spring and the particle damping inertial container are disposed in the inner cylinder, and the particle damping inertial container is sleeved inside the spring;

[0010] The particle damping inertial container includes a ball screw assembly, a base, and a flywheel containing particles. The flywheel is coaxially and fixedly connected to the ball screw assembly. The first end of the ball screw assembly is fixedly connected to the outer cylinder, and the second end is connected to the base and can rotate around the axis.

[0011] In some implementations of the first aspect, the flywheel includes a turntable, a counterweight, a vibrator, and a plurality of particles. The counterweight is disposed on the outer circumferential surface of the turntable, and the turntable has at least one annular chamber arranged radially therein. The particles are disposed within the annular chamber, and the vibrator is disposed on the inner sidewall of the annular chamber.

[0012] In combination with the first aspect and the above implementation, in some implementations of the first aspect, the turntable is provided with three annular chambers in the radial direction, and the particles include a first particle, a second particle and a third particle, which are respectively disposed in the annular chambers.

[0013] In combination with the first aspect and the above-described implementations, in some implementations of the first aspect, the ball screw assembly includes an inner support rod, an outer support rod, and balls. At least a portion of the inner support rod is provided with a threaded groove, and the outer support rod is provided with a receiving hole along its central axis. The receiving hole is provided with a threaded groove, and the balls are disposed in the matching threaded grooves of the inner support rod and the outer support rod.

[0014] In combination with the first aspect and the above implementation, in some implementations of the first aspect, the outer support rod includes a first rod body and a second rod body, and the receiving hole of the second rod body is provided with the threaded groove on the hole wall, and the two ends of the threaded groove are connected through a channel.

[0015] In combination with the first aspect and the above implementation methods, in some implementation methods of the first aspect, the outer cylinder includes an outer cylinder body and an ear clip, the ear clip being disposed on the outer periphery of the outer cylinder body; a spring fixing assembly is provided on the top surface of the inner cavity of the outer cylinder body, the spring fixing assembly being used to fix the spring.

[0016] In combination with the first aspect and the above implementation methods, in some implementation methods of the first aspect, the spring fixing assembly includes a first limiting plate and a second limiting plate. The first limiting plate is provided with a hollow portion, and the second limiting plate is provided with a protruding edge that can pass through the hollow portion in the circumferential direction. A spring stop and a screw stop are provided on one end face of the second limiting plate. One end of the spring is disposed in the spring stop, and the first end of the ball screw assembly is disposed in the screw stop.

[0017] Secondly, this application provides a novel vibration-damping track, mounted on a foundation component, comprising rails, fasteners, sleepers, a floating slab, and a broadband inertial-capacitance-enhanced vibration isolator as described in the first aspect of this application; the rails, fasteners, and sleepers are mounted on the floating slab, and the broadband inertial-capacitance-enhanced vibration isolator is mounted between the floating slab and the foundation component, wherein the floating slab is supported by the broadband inertial-capacitance-enhanced vibration isolator and thus suspended above the foundation component.

[0018] In some implementations of the second aspect, the floating plate is provided with mounting holes, the outer cylinder is embedded in the mounting holes, and the bottom of the inner cylinder is connected to the base component.

[0019] In combination with the second aspect and the above implementation methods, in some implementation methods of the second aspect, both the floating slab and the foundation component are reinforced concrete components.

[0020] The technical solutions provided in the embodiments of this application bring the following beneficial technical effects:

[0021] The broadband inertial enhancement vibration isolator provided in this application consists of components such as an outer cylinder, a spring, and an inner cylinder. The particle damping inertial container is both an inertial container and has the characteristics of a particle damper. Thus, the broadband inertial enhancement vibration isolator is actually a new type of vibration isolator that combines the advantages of an inertial container and a particle damper. When applied to rails, it can effectively improve the full-frequency vibration reduction capability of steel spring floating slab rails.

[0022] Additional aspects and advantages of this application will be set forth in the following sections and will be understood in detail from the following description, or may be learned by specific practice of the invention. Attached Figure Description

[0023] Figure 1 This is a schematic cross-sectional view of a broadband inertial-enhanced vibration isolator according to an embodiment of the present invention;

[0024] Figure 2 This is a schematic cross-sectional view of a particle-damped inertial container in one embodiment of the present invention.

[0025] Figure 3This is a schematic cross-sectional view of the particle-damped inertial container in one embodiment of the present invention.

[0026] Figure 4 This is a schematic cross-sectional view of a broadband inertial-enhanced vibration isolator according to another embodiment of the present invention;

[0027] Figure 5 This is a schematic diagram of the planar structure of the first limiting piece in one embodiment of the present invention;

[0028] Figure 6 This is a schematic diagram of the planar structure of the second limiting piece in one embodiment of the present invention;

[0029] Figure 7 This is a three-dimensional structural diagram of a novel vibration-damping track according to an embodiment of the present invention;

[0030] Figure 8 This is a schematic cross-sectional view of a novel vibration-damping track in one embodiment of the present invention.

[0031] Explanation of reference numerals in the attached figures:

[0032] 100-Rail, 200-Fasteners, 300-Sleepers, 400-Broadband Inertial Reinforced Vibration Isolators, 500-Floating Slabs, 600-Foundation Components;

[0033] 410 - Particle-damped inertial container, 420 - Spring, 430 - Outer cylinder, 440 - Inner cylinder;

[0034] 411 - Ball screw assembly, 412 - Flywheel, 413 - Base;

[0035] 431-Outer cylinder body, 432-Ear buckle, 433-Spring fixing assembly;

[0036] 4111-Inner support rod, 4112-Outer support rod, 4113-Ball bearing;

[0037] 4121-Turntable, 4122-Counterweight, 4123-Vibrator, 4124-Particles;

[0038] 4331 - First limiting piece, 4332 - Second limiting piece, 4333 - Hollowed-out part, 4334 - Raised edge, 4335 - Spring stop, 4336 - Screw stop. Detailed Implementation

[0039] To facilitate understanding of the present invention, a more complete description will be given below with reference to the accompanying drawings. The drawings illustrate possible embodiments of the invention. However, the invention can be implemented in many different forms and is not limited to the embodiments described herein with reference to the drawings. The embodiments described with reference to the drawings are exemplary and intended to provide a more thorough and complete understanding of the disclosure of the invention, and should not be construed as limiting the invention. Furthermore, detailed descriptions of known techniques may be omitted where such details are not essential to the features of the illustrated invention.

[0040] Those skilled in the art will understand that, unless otherwise defined, all terms used herein (including technical and scientific terms) have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. It should also be understood that terms such as those defined in general dictionaries should be understood to have the same meaning as in the prior art and should not be interpreted in an idealized or overly formal sense unless specifically defined as herein.

[0041] Those skilled in the art will understand that, unless specifically stated otherwise, the singular forms “a,” “an,” “the,” and “the” used herein may also include the plural forms. It should be further understood that the term “comprising” as used in the specification of this application means the presence of the stated features, integers, steps, operations, elements, and / or components, but does not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof. It should be understood that the term “and / or” as used herein includes all or any units and all combinations of one or more associated listed items.

[0042] In existing technologies, inertial capacity was proposed in the early 21st century by Japanese scholars Inoue and Ikago, and further refined by British scholar Simth. It is a novel type of inertial mechanical unit with two endpoints. Its inertial characteristics are mainly achieved through mechanisms such as "translational-rotational conversion" and "flow velocity change," with the most classic mechanism being the ball screw's "translational-rotational conversion." Taking the ball screw inertial container as an example, it converts the linear motion of the two endpoints (i.e., the axial translation of the flywheel) into the high-speed rotational motion of the flywheel, and converts the flywheel's rotational inertia into axial inertia through the ball screw mechanism. The inertial force... P Relative acceleration with respect to the two endpoints They are directly proportional, and the ratio is called the "capacity coefficient" or "apparent mass", denoted as . As shown in equations (1) to (3), equation (1) is the output force expression of the inertia container, equation (2) is the output force expression of the ball screw inertia container, and equation (3) is the inertia capacity coefficient expression of the ball screw inertia container. I is the screw lead, and I is the flywheel moment of inertia. The outer diameter of the flywheel. This is the inner diameter of the flywheel.

[0043] (1)

[0044] (2)

[0045] (3)

[0046] Based on mechanisms such as "translational-rotational conversion," a relatively small physical mass can generate a large inertial force, achieving an inertial amplification effect. This solves the problems of insufficient effect with small masses and inconvenient installation and additional dynamic effects with large masses faced by traditional mass components. The inertial amplification effect is manifested in the inertial capacitance coefficient. Much greater than its actual physical mass , and The ratio can be hundreds of times.

[0047] Another advantage of inertial capacitance is its ability to broaden the low-frequency vibration reduction band, thereby improving the low-frequency vibration reduction range. Since the principle of a floating plate isolator involves supporting and suspending the plate to isolate wheel-rail vibrations from transmission to the lower foundation and surrounding areas, it is mechanically a multi-point supported plate model. Simplifying it as a single-degree-of-freedom system facilitates the explanation of the advantages of inertial capacitance. The following analysis examines the influence of inertial capacitance isolators on the low-frequency vibration reduction range and effect of a single-degree-of-freedom system. Assume that the mass of the single-degree-of-freedom system is... Subject to simple harmonic load The inertial compression vibration isolator is a spring. Damping and habitual tolerance It is composed of parallel components. Its dynamic equations satisfy: Define a dimensionless parameter. That is, the ratio of the system excitation frequency to the system natural frequency is taken as the dimensionless system excitation frequency. That is, the ratio of inertial mass to physical mass is taken as the dimensionless inertial mass or inertial-mass ratio. For this system, the force transmissibility is chosen. As an indicator of vibration reduction effect, when force transmission rate It has a vibration reduction effect, and thus the vibration reduction frequency range can be obtained. For traditional floating slab tracks, the vibration isolators lack inertial capacitance, and their mechanical model consists of a spring and a damper connected in parallel. This simplifies the traditional floating slab track into a single-degree-of-freedom system, corresponding to a specific vibration reduction frequency range. .because And when the inertia ratio Increase the initial damping frequency Gradually decrease, force transmission rate The single peak of the curve continuously shifts towards lower frequencies, indicating that adding inertial capacitance to the vibration isolator widens the low-frequency vibration reduction range. The inertial-to-mass ratio of the inertial capacitance... The larger the value, the more obvious the widening of the low-frequency vibration reduction range, and the more it can suppress vibrations at even lower frequencies, demonstrating better low-frequency vibration reduction capability.

[0048] Another advantage of inertial capacitance is that it provides anti-resonance capability, suppressing resonance peaks and low-frequency resonance amplification of the floating plate. Combined with the single-degree-of-freedom system described above, the aforementioned force transmissibility... The curve has only one trough, which is the force transmissibility at that point. The minimum, known as the anti-resonance phenomenon, corresponds to the frequency. .

[0049] When inertia-mass ratio At that time, force transmission rate exist The system reaches a trough when its excitation frequency equals its natural frequency, resulting in anti-resonance. This is because, under normal circumstances, when the system excitation frequency equals its natural frequency, the force transmissibility of the system without inertial capacitance is low. The maximum value occurs at the wave crest, resulting in resonance. When the vibration isolator contains inertial capacitance, the system's force transmissibility... The minimum value occurs at the trough of the wave, indicating anti-resonance. This suggests that inertial capacitance has been added to the vibration reduction system and the inertia-to-mass ratio has been adjusted. Reaching appropriate values ​​can provide anti-resonance capability and suppress resonance peaks. For floating slab track systems, since the frequency components of wheel-rail excitation cover a wide range from 0 to thousands of hertz, the excitation component around 10 Hz is the same as the natural frequency of the floating slab track, which will cause low-frequency vibration amplification of the floating slab. Adding inertial capacitance and adjusting the inertia-to-mass ratio are necessary. It can provide low-frequency anti-resonance capability for the floating slab track and suppress the low-frequency resonance amplification of the floating slab.

[0050] However, the application of inertial containers in this field also has its shortcomings. First, inertial containers can only play a good role in vibration reduction and isolation near the resonant frequency of the main structure, and the vibration reduction frequency band is relatively narrow. Second, inertial capacitive elements reduce vibration based on the principle of tuned energy absorption. By adding the phase difference between the inertial container substructure and the main structure, a force opposite to the direction of motion of the main structure is generated, thereby suppressing vibration and absorbing the dynamic potential energy of the main structure to form the dynamic potential energy of the flywheel rotation, but it does not have the function of energy dissipation itself.

[0051] A particle damper is an energy-dissipating device that uses cavities filled with particles within a vibrating body to convert vibrational energy into heat and sound energy through collisions and friction between particles and between particles and the cavity walls. Each cavity is considered a unit, and based on the unit and the particle filling ratio, they can be classified as single-unit single-particle impact dampers, multi-unit single-particle impact dampers, single-unit multi-particle dampers, and multi-unit multi-particle dampers. Although particle motion and collision are highly nonlinear processes, and their theoretical analysis is quite complex, current theoretical research on particle dampers is relatively scarce. However, experimental and simulation results show that particle dampers have a wide-frequency vibration reduction advantage. Furthermore, optimizing parameters such as the number and volume of chambers, particle material, particle size, shape, density, and particle filling ratio can adjust the vibration reduction frequency range and core frequency band of the particle damper, thus contributing to achieving a wide-band vibration reduction effect with an adjustable frequency range.

[0052] The advantages of particle dampers in vibration reduction and isolation applications in civil engineering structures include: 1) A wide operating frequency range can be achieved by setting multiple chamber units and various particle filling ratios, with a maximum vibration reduction frequency of 6000Hz through reasonable design; 2) Based on damping energy dissipation vibration reduction, the vibration energy of the main structure can be converted into heat and sound energy generated by collisions and friction between particles and chamber walls, and between particles, and then dissipated; 3) Good durability, high reliability, insensitivity to temperature, and suitable for harsh environments. Its disadvantages are: 1) Particle dampers have a limited start-up vibration. During the start-up phase, the main structure vibrates slowly, and the particles move synchronously with the main structure, which cannot demonstrate a vibration reduction effect and may even amplify vibration. A better vibration reduction effect is achieved only when the main structure vibrates more violently, and the particle displacement is asynchronous with the main structure, causing violent collisions and friction between particles and between particles and chamber walls; 2) Traditional particle dampers must have a large mass ratio (the ratio of particle mass to main structure mass, generally not less than 2%) to demonstrate a good vibration reduction effect. However, excessive additional mass will trigger additional dynamic effects on the main structure and increase the cost of the main structure design phase.

[0053] Therefore, ordinary inertial dampers or particle dampers still cannot solve the problems of insufficient low-frequency vibration reduction and comprehensive improvement of vibration reduction performance across the entire frequency band, and are therefore difficult to apply to urban rapid railway tracks with greater wheel-rail vibration.

[0054] The broadband inertial-enhanced vibration isolator and steel spring floating plate track provided by this invention aim to solve the above-mentioned technical problems of the prior art.

[0055] The technical solution of the present invention and how the technical solution solves the above-mentioned technical problems will be described in detail below with specific embodiments.

[0056] An embodiment of the first aspect of this application provides a broadband inertial-enhanced vibration isolator 400, such as... Figure 1 As shown, the device includes an outer cylinder 430, a spring 420, a particle-damped inertia container 410, and an inner cylinder 440. The spring 420 is disposed within the inner cylinder 440, which is fitted inside the outer cylinder 430. The particle-damped inertia container 410 is fitted inside the spring 420. The spring 420 is generally selected from springs of suitable specifications, such as springs made of spring steel.

[0057] like Figure 2 As shown, the particle damping inertial container 410 includes a ball screw assembly 411, a base 413, and a flywheel 412 containing particles. The flywheel 412 is coaxially fixedly connected to the ball screw assembly 411 and can rotate around the axis. The first end of the ball screw assembly 411 is fixedly connected to the outer cylinder 430, and the second end is connected to the base 413 and can rotate around the axis.

[0058] The two ends of the structure consisting of the outer cylinder 430 and the inner cylinder 440 are subjected to forces in opposite directions. If used on a rail transit track, this is equivalent to the vibration force between the track and the ground. Through the ball screw pair 411 and the base 413 in the particle damping inertial container 410, as well as the inner cylinder 440 and the outer cylinder 430, the linear reciprocating motion of the two ends of the vibration isolator (i.e., the two ends of the inner cylinder 440 and the outer cylinder 430 or the two ends of the ball screw pair 411) can be converted into the rotational motion of the flywheel 412.

[0059] The broadband inertial enhancement vibration isolator provided by this invention is composed of components such as an outer cylinder 430, a spring 420, and an inner cylinder 440. The particle damping inertial container 410 is both an inertial container and has the characteristics of a particle damper. Thus, this vibration isolator is actually a new type of broadband inertial enhancement vibration isolator that combines the advantages of an inertial container and a particle damper. When applied to rails, it can effectively improve the low-frequency vibration reduction capability of new vibration-damping rails.

[0060] Optionally, in one specific implementation of the first aspect embodiment of this application, such as Figure 2 As shown, the flywheel 412 includes a turntable 4121, a counterweight 4122, a vibrator 4123, and several particles 4124. The counterweight 4122 is disposed on the outer circumferential surface of the turntable 4121. The turntable 4121 has at least one annular chamber arranged radially. The particles 4124 are disposed within the annular chamber. The vibrator 4123 is a semi-cylindrical metal protrusion fixed to the inner wall of the large ring of the annular chamber, which can increase the collision degree of the particles 4124 within the chamber. The aforementioned particle 4124 structure has a damping energy dissipation function. During the high-speed rotation of the flywheel 412 in alternating forward and reverse directions, the particles 4124 are struck by the vibrator 4123, causing violent and irregular vibrations. This results in violent collisions between the particles 4124 and the chamber wall, as well as between the particles 4124 themselves, consuming system energy.

[0061] Optionally, in conjunction with the embodiments of the first aspect and the above-described implementations, in other specific implementations, such as... Figure 3 As shown, the turntable 4121 has three annular chambers arranged radially, and the particles 4124 include a first particle, a second particle, and a third particle, which are respectively arranged in each annular chamber.

[0062] The flywheel 412 containing particles 4124 is a disc structure containing multiple annular chambers. Each annular chamber contains particles 4124, and the types of particles 4124 vary between chambers. The number of chambers can be one, two, three, or more. The volume and rotational velocity of each chamber differ significantly, and each chamber contains the same type of particles 4124. The particles 4124 have requirements regarding material, particle size, shape, density, and filling rate. For example, in terms of material, the three types of particles 4124 can be solid particles 4124 such as steel, aluminum, iron, lead, gravel, and sand; in terms of particle size, the particle sizes of the first, second, and third particles can be set in a certain ratio; in terms of shape, the first, second, and third particles can be spherical, cubic, conical, flake, or other shapes; in terms of density, the densities of the three types of particles 4124 can be set in a certain ratio; and in terms of filling rate, the filling rates of the three types of particles 4124 can be set in a certain ratio. Optionally, a removable chamber cover is provided on the annular chamber, which can be removed to adjust parameters such as the material, particle size, shape, density, and filling rate of the particles 4124 inside.

[0063] The vibration reduction effect of the particle damper is greatly affected by parameters such as the number and volume of the chambers, the material, particle size, shape, density and filling rate of the particles. By disassembling the chamber cover and adjusting the particle parameters, the vibration reduction frequency range and the core vibration reduction frequency band can be adjusted to achieve a wide-band particle damping vibration reduction effect with an adjustable vibration reduction frequency range.

[0064] Furthermore, in this implementation, each chamber has multiple vibrators 4123 mounted on its outer-facing inner wall. The number can be one, four, or more. During the alternating high-speed rotation of the flywheel 412 in both directions, the particles 4124 are struck by the vibrators 4123, resulting in violent and irregular vibrations. During this process, the collisions between the particles 4124 and the chamber walls, as well as among the particles themselves, also consume the system's energy, thus achieving vibration damping. The vibrators 4123 fully utilize the damping effect of the particles 4124, avoiding the poor vibration damping effect that occurs in traditional particle damper applications where the vibration or movement of the attached structure is not intense, preventing the particles 4124 from vibrating sufficiently.

[0065] Optionally, a damping layer is attached to the wall of the annular chamber to increase the resistance between the particles 4124 and the chamber wall, further enhancing the damping energy dissipation function of the particle-damped inertial container 410. Optionally, the counterweight 4122 is a high-density metal ring, fixed to the outer periphery of the flywheel 412 containing the particles 4124. The counterweight 4122 provides a large mass and a large moment of inertia, thereby improving the inertial amplification effect.

[0066] Optionally, in a specific implementation, such as Figure 1 and Figure 2 As shown, the base 413 in the particle damping inertial container 410 includes a base shell, base balls, and an inner base disk. The base shell includes an inner base stop, a first rolling groove, and an outer base stop. The upper and lower surfaces of the inner base disk have second rolling grooves. The base balls can roll within the cavity formed by the matching first and second rolling grooves, causing the inner base disk to rotate horizontally relative to the base shell. The base shell is fixed to the center of the bottom cover, and the inner base disk is fixedly connected to the outer support rod 4112 of the ball screw assembly. The base acts as a bearing structure, and the second end of the ball screw assembly 411 is connected to this bearing structure, enabling rotation around its own axis.

[0067] Optionally, in another embodiment of the first aspect, such as Figure 2 As shown, the ball screw assembly 411 includes an inner support rod 4111, an outer support rod 4112, and a ball 4113. At least a portion of the inner support rod 4111 is provided with a threaded groove. The outer support rod 4112 is provided with a receiving hole along its central axis, and a threaded groove is provided in the receiving hole. The ball 4113 is disposed in the matching threaded grooves of the inner support rod 4111 and the outer support rod.

[0068] Optionally, in conjunction with the above embodiments, in one specific implementation, such as Figure 2 As shown, the outer support rod 4112 includes a first rod body and a second rod body. The receiving hole of the second rod body has a threaded groove on its wall, and the two ends of the threaded groove are connected by a channel. The outer support rod can be a split-type structure, with the threaded groove only on the second rod body, eliminating the need to provide threaded grooves on the entire outer support rod 4112. The threaded grooves on the second rod body are all located internally, corresponding to the threaded grooves of the inner support rod, forming a moving channel for the ball 4113. The beginning and end of this moving channel are connected by a channel further provided on the second rod body, allowing the ball 4113 to circulate between the outer support rod 4112 and the inner support rod 4111. The ball screw pair 411 can directly adopt or draw upon common ball screw structures in the prior art.

[0069] Optionally, in conjunction with the above embodiments, in another implementation, such as Figure 1As shown, the outer cylinder 430 includes an outer cylinder body 431 and an ear clip 432, with the ear clip 432 disposed on the outer periphery of the outer cylinder body 431. A spring fixing assembly 433 is provided on the top surface of the inner cavity of the outer cylinder body 431, used to fix the spring 420. Specifically, the ear clip 432 is a metal sheet bent at 90 degrees, welded to the outer wall of the outer cylinder body 431. The ear clip 432 and the outer cylinder body 431 are cast together inside a reinforced concrete floating plate 500, ensuring the secure installation of the broadband inertia-enhanced vibration isolator 400. The spring fixing assembly 433 can be directly disposed on the outer cylinder body 431, or it can be disposed as a separate structure. Optionally, in conjunction with the above embodiments, in another implementation, such as... Figure 4 As shown, the spring fixing assembly 433 includes a first limiting piece 4331 and a second limiting piece 4332. The first limiting piece 4331 has a hollow portion 4333, and the second limiting piece 4332 has a protruding edge 4334 that can pass through the hollow portion 4333 in the circumferential direction. A spring stop 4335 and a screw stop 4336 are provided on one end face of the second limiting piece 4332. One end of the spring 420 is disposed in the spring stop 4335, and the first end of the ball screw assembly 411 is disposed in the screw stop 4336. Figure 5 and Figure 6 As shown, the hollow portion 4333 consists of three crescent-shaped notches evenly distributed circumferentially, while the raised edge 4334 is the opposite. During installation, the raised edge 4334 of the second limiting piece 4332 abuts against the non-hollow portion 4333 of the first limiting piece 4331. The first limiting piece 4331 can be set with multiple parallel pieces. The raised edge 4334 of the second limiting piece 4332 enters the first limiting piece 4331 at different positions through the hollow portion 4333 of the corresponding shape and abuts against it, thereby adjusting the position of the second limiting piece 4332. Particle damping inertial containers 410 of different heights can be installed.

[0070] An embodiment of the second aspect of this application provides a novel vibration-damping track, which is applied in rail transit infrastructure and specifically installed on a foundation component 600, such as... Figure 7As shown, the novel vibration-damping track includes a sleeper 300, a floating plate 500, and a broadband inertial-enhanced vibration isolator 400 as described in the first aspect embodiment of this application. The sleeper 300 is disposed on the floating plate 500, and the broadband inertial-enhanced vibration isolator 400 is disposed between the floating plate 500 and the base member 600. The floating plate 500 is supported by the broadband inertial-enhanced vibration isolator 400 and thus suspended above the base member 600. Of course, in addition to the above-mentioned components, as a type of track, the novel vibration-damping track provided in this application also includes rails 100, generally a pair of parallel rails 100. The rails 100 are connected to the sleeper 300 by fasteners 200. The sleeper 300 and the rails 100 on the sleeper 300 are all disposed on the floating plate 500. Vibrations and pressures transmitted from the rails 100 are reduced by the broadband inertial-enhanced vibration isolator 400 before being transmitted to the base member 600. Wideband inertial vibration isolators 400 are generally installed between fasteners 200, and the spacing can be the length of one or more spans of fasteners 200. Optionally, the floating slab 500 and the foundation component 600 are both reinforced concrete components, while the fasteners 200 and the wideband inertial vibration isolators 400 are generally steel components.

[0071] Optionally, in conjunction with the embodiments of the first aspect described above, in some implementations of the embodiments of the second aspect, such as Figure 8 As shown, the floating plate 500 has mounting holes, the outer cylinder 430 is embedded in the mounting holes, and the bottom of the inner cylinder 440 is connected to the foundation component 600.

[0072] In practical applications, when a train passes over the novel vibration-damping track equipped with the aforementioned particle-damped inertial container, the inner support rod 4111 vibrates vertically (relative to the horizontal direction) along with the outer cylinder 430 and the floating plate 500. The rapid or high-speed vertical vibration is converted into alternating high-speed rotation around the axis by the outer support rod 4112 and the flywheel 412 containing particles 4124, with upward and downward vibrations corresponding to forward and reverse rotations, respectively. During this process, the vibration energy of the track is absorbed as the mechanical energy of the flywheel 412's rotation, and part of it is dissipated through particle damping.

[0073] Based on the foregoing, the broadband inertial-enhanced vibration isolator and novel vibration-damping track provided in this application have at least the following technical effects:

[0074] First, the inertial container is combined with a particle damper, and a cavity is set in the flywheel filled with particles to achieve a wider frequency band of particle damping vibration reduction, which makes up for the narrow vibration reduction frequency band of the inertial container.

[0075] Second, inertial containers reduce vibration based on the principle of tuned energy absorption, which can absorb the vibration energy of the main structure but does not have the function of energy dissipation. The broadband inertial enhancement vibration isolator of this application is an inertial container combined with a particle damper, which can both tune and absorb energy and damp dissipate energy, dissipating the vibration energy of the system and improving the vibration reduction effect.

[0076] Third, traditional particle dampers have a limitation on vibration initiation. When the main structure (such as a train running on a new type of vibration-damping track) vibrates gently, the vibration transmitted to the flywheel is difficult to excite the internal particle vibration. However, the inertial container based on the ball screw "translational-rotational conversion mechanism" of this application can convert the small relative linear velocity at both ends of the axial direction into the linear velocity of the high-speed rotation of the flywheel. By installing the particle damper on the flywheel of the inertial container in a certain way, the problem of the limitation on vibration initiation of particle dampers can be solved.

[0077] Fourth, setting a large mass ratio in a particle damper can cause additional dynamic effects on the main structure and increase costs. However, an inertial container has the characteristic of inertial amplification, and its apparent mass can reach hundreds of times its actual mass. Combining the two can provide a large mass ratio through the inertial amplification effect of the inertial container, and the particle damper can be made lighter.

[0078] Those skilled in the art will understand that the terms "first" and "second" discussed in this application are for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0079] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "joining" 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 direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0080] In the description of this specification, specific features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

[0081] The above description is only a partial embodiment of this application. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the principle of this application, and these improvements and modifications should also be considered within the scope of protection of this application.

Claims

1. A broadband inertial-enhanced vibration isolator, characterized in that, It includes an outer cylinder, a spring, a particle damping inertia container, and an inner cylinder. The inner cylinder is sleeved inside the outer cylinder, and the spring and the particle damping inertia container are disposed in the inner cylinder. The particle damping inertia container is sleeved inside the spring. The particle damping inertial container includes a ball screw assembly, a base, and a flywheel containing particles. The base is disposed on the inner cylinder. The ball screw assembly includes an inner support rod, an outer support rod, and balls. The flywheel is coaxially and fixedly connected to the outer support rod of the ball screw assembly. The inner support rod of the ball screw assembly is fixedly connected to the outer cylinder, and the outer support rod of the ball screw assembly is connected to the base and can rotate around its own axis. The flywheel includes a turntable, a counterweight, a vibrator, and several particles. The counterweight is disposed on the outer circumferential surface of the turntable. At least one annular chamber is disposed radially on the turntable. The particles are disposed within the annular chamber, and the vibrator is disposed on the inner wall of the annular chamber. At least a portion of the inner support rod is provided with a threaded groove, and the outer support rod is provided with a receiving hole along the central axis. The receiving hole is provided with a threaded groove, and the ball is disposed in the matching threaded groove of the inner support rod and the outer support rod.

2. The broadband inertial-enhanced vibration isolator according to claim 1, characterized in that, The turntable has three annular chambers arranged radially, and the particles include a first particle, a second particle, and a third particle, which are respectively disposed in the annular chambers.

3. The broadband inertial-enhanced vibration isolator according to claim 1, characterized in that, The outer support rod includes a first rod body and a second rod body. The receiving hole of the second rod body is provided with a threaded groove, and the two ends of the threaded groove are connected by a channel.

4. The broadband inertial-enhanced vibration isolator according to claim 1, characterized in that, The outer cylinder includes an outer cylinder body and an ear clip, the ear clip being disposed on the outer periphery of the outer cylinder body; a spring fixing assembly is provided on the top surface of the inner cavity of the outer cylinder body, the spring fixing assembly being used to fix the spring.

5. The broadband inertial-enhanced vibration isolator according to claim 4, characterized in that, The spring fixing assembly includes a first limiting plate and a second limiting plate. The first limiting plate has a hollow portion, and the second limiting plate has a protruding edge that can pass through the hollow portion in the circumferential direction. A spring stop and a screw stop are provided on one end face of the second limiting plate. One end of the spring is disposed in the spring stop, and the first end of the ball screw assembly is disposed in the screw stop.

6. A vibration-damping track, installed on a foundation component, characterized in that, It includes a sleeper, a floating slab, and a broadband inertial vibration isolator as described in any one of claims 1 to 5; the sleeper is disposed on the floating slab, the broadband inertial vibration isolator is disposed between the floating slab and the base component, and the floating slab is suspended above the base component.

7. The vibration-damping track according to claim 6, characterized in that, The floating plate is provided with mounting holes, the outer cylinder is embedded in the mounting holes, and the bottom of the inner cylinder is connected to the foundation component.

8. The vibration-damping track according to claim 6, characterized in that, Both the floating slab and the foundation components are reinforced concrete components.

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