Mass-tuned damping particle composite type built-in vibration reduction device

Abstract

The invention discloses a damping particle composite type built-in vibration reduction device with tuned mass. The device is pre-buried and installed in a force bearing structure below a steel rail. The device comprises a box body shell, a spring and a mass tuning container are arranged in the box body shell, a plurality of baffles are arranged in the mass tuning container, the mass tuning container is divided into a plurality of independent cavities by the baffles, and the cavities are closed containers and are filled with damping particles; vibration energy is consumed through collision and friction between the damping particles and the inner wall of the cavity and mutual collision and friction between the damping particles. The spring is arranged between the mass tuning container and the box body shell, so that the energy consumption efficiency is improved, and the mass tuning container can be protected; according to the device, the movement distance and the kinetic energy of the particle units are increased by utilizing the displacement and the acceleration of the mass tuning container, the energy consumption is increased, the vibration and noise reduction means are enriched and increased, and a good economic effect can be achieved.

Description

Technical Field

[0001] The invention belongs to the field of vibration and noise control of rail transit, and in particular is a mass-tuned damping particle composite built-in vibration reduction device. Background Art

[0002] Rail transit refers to a type of transportation tool or transportation system in which vehicles need to travel on specific tracks, including subways, light rails, railway systems, etc. However, in the actual operation of vehicles, different degrees of vibration and noise will be generated, among which vertical vibration has the greatest damage effect on the railway system and poses the greatest threat.

[0003] Most of the existing vibration reduction measures in rail transit use the theory of mass-spring system to convert vibration energy into vibration of track plates, sleepers, ballasts, etc., so as to achieve the purpose of vibration reduction. More and more theories and experiments show that the vibration of tracks equipped with medium, high and special vibration reduction measures is concentrated in the track superstructure, which is more likely to cause mechanical diseases of rails, wheels and their components. Secondly, the vibration of track plates and rails is transmitted to the vehicle body through the vehicle suspension system and then radiates noise into the vehicle. Thirdly, among the existing track vibration reduction and noise reduction measures, the main means is to reduce (lose) the stiffness of the track structure. This method will increase the vibration displacement of the track structure, induce rail corrugation, make the vehicle run unevenly, and reduce the comfort level. At the same time, it will also be accompanied by diseases such as broken fastener spring bars and cracked track plates.

[0004] The fundamental reason for the above problems is that the main means is to reduce (lose) the stiffness of the track structure. Although the system energy can be effectively redistributed, it cannot be consumed. These measures are accompanied by a significant increase in in-vehicle noise, corrugation, uneven operation, etc. Therefore, it is very necessary and urgent to explore the use of technical means such as increasing component damping and maintaining uniform and unchanged track structure stiffness to ensure the smoothness and comfort of vehicle operation and reduce related diseases.

[0005] The damping particle collector consumes vibration energy by collision and friction between particles or between particles and containers, and has excellent vibration control performance. It has the characteristics of simple structure, low cost, easy installation, excellent fatigue resistance, obvious vibration and noise reduction effect, and simple operation and maintenance.

[0006] According to the survey, the high-frequency vibration from the track structure has a short propagation distance due to the attenuation effect of the surrounding geology, and has little impact on the surrounding sensitive point buildings. The natural frequency of structural components such as concrete is low-frequency, and it is easy to resonate under the excitation of train loads and propagate to a distance through the surrounding geology. Therefore, by setting the mass tuning function, the low-frequency vibration of the concrete component can be partially offset by the opposite movement of the mass tuning block, which can achieve a good vibration reduction effect. However, the vibration frequency range adapted by the damping particles is small, which is smaller than the vibration frequency range that can be generated when the train passes, resulting in unsatisfactory vibration reduction effect in some cases.

[0007] Based on this, the inventor has conducted in-depth research on the vibration reduction device in the hope of designing a new vibration reduction device that can solve the above-mentioned problems. Summary of the invention

[0008] In order to overcome the above problems, the inventors have conducted intensive research and designed a mass-tuned damping particle composite built-in vibration reduction device, which is pre-buried and installed in the load-bearing structure under the rail, and the load-bearing structure is a sleeper, a ballast, a track plate or a base; the device includes a box shell, a spring and a mass tuning container are arranged inside the box shell, and a plurality of baffles are arranged inside the mass tuning container, and the baffles divide the mass tuning container into a plurality of independent cavities, and the cavities are closed containers filled with damping particles; through the collision and friction between the damping particles and the inner wall of the cavity, the damping particles The particles collide and rub against each other to consume vibration energy; the spring is arranged between the mass tuning container and the box shell to amplify the displacement and rate of vibration of the mass tuning container, improve energy consumption efficiency, and avoid direct contact between the mass tuning container and the box shell; the device utilizes the displacement of the mass tuning container and its acceleration to increase the movement distance and kinetic energy of the particle unit, increase the energy consumed by particle friction and collision, overcome the many defects of currently relying solely on adjusting the stiffness of the track structure to reduce vibration and noise, enrich and increase the means of reducing vibration and noise, and achieve good economic effects, thereby completing the present invention.

[0009] Specifically, the object of the present invention is to provide a mass-tuned damping particle composite built-in vibration reduction device, which is pre-buried and installed in a load-bearing structure under the rail, and the load-bearing structure is a trapezoidal sleeper, a ballast, a track slab or a base;

[0010] The device comprises a box shell 1, inside which a spring 2 and a mass tuning container 3 are arranged, the mass tuning container 3 is a closed container filled with damping particles 6, and the damping particles are selected from one or more of iron sand, lead particles, steel balls, and sand;

[0011] The vibration energy is consumed by the collision and friction between the damping particles 6 and the wall surface, and the collision and friction between the damping particles.

[0012] The spring 2 is arranged between the mass tuning container 3 and the box shell 1. The spring 2 amplifies the displacement and rate of vibration of the mass tuning container 3, thereby improving the energy consumption efficiency of the damping particles 6 in the mass tuning container 3. The spring 2 also avoids direct contact between the mass tuning container 3 and the box shell 1.

[0013] A mass tuning container 3 is arranged in the box shell 1, and a plurality of baffles 4 are arranged in each mass tuning container 3, and the baffles 4 divide the mass tuning container 3 into a plurality of cavities 5 independent of each other;

[0014] The wall surface is the inner wall surface of the cavity 5 formed by the inner wall of the mass tuning container 3 and the baffle 4 .

[0015] Wherein, in the cavity 5, the volume proportion of the damping particles 6 material is 80-90%.

[0016] The spatial volumes inside the various cavities 5 are consistent, that is, the baffles 4 evenly divide the mass tuning container 3 into a plurality of cavities 5 .

[0017] In each mass tuning container 3 , the number of cavities 5 is 20 to 30.

[0018] In the process of pouring the load-bearing structure, the box shell 1 is buried inside the box shell 1; the length direction of the box shell 1 is consistent with the length direction of the load-bearing structure;

[0019] When the box shell 1 is provided with one, the box shell 1 is buried in the middle of the load-bearing structure;

[0020] When there are multiple box shells 1, the horizontal heights of the multiple box shells 1 are consistent; in the vertical direction, the distances between each box shell 1 and the top and bottom of the load-bearing structure are basically consistent; in the horizontal direction, the multiple box shells 1 are symmetrically and evenly distributed in the load-bearing structure;

[0021] Preferably, the box shell 1 is completely buried inside the load-bearing structure, that is, the box shell 1 is not visible from outside the load-bearing structure.

[0022] Among them, when the load-bearing structure is a trapezoidal sleeper 7, 1 to 3 box shells 1 are pre-embedded in the trapezoidal sleeper with a sleeper length of 6 meters, and the total effective volume of the mass tuning container 3 in each box shell 1 is 100×100×5600mm, and the effective volume of a single cavity 5 is 100×100×200mm, and the effective volume is the spatial volume that can be used to accommodate damping particles.

[0023] Among them, when the load-bearing structure is a ballast bed, at most 10 to 12 box shells 1 are pre-buried in any ballast bed section, the length of the box shell 1 is 3 meters, and a plurality of cavities 5 are arranged in the mass tuning container 3 of each box shell 1. The effective volume of a single cavity 5 is 100×100×200mm, and the effective volume is the spatial volume that can be used to accommodate damping particles.

[0024] Among them, when the load-bearing structure is a track plate, 8 to 10 box shells 1 are pre-embedded in the track plate with a length of 6 meters and a width of 2.5 meters. The total effective volume of the mass tuning container 3 in each box shell 1 is 100×100×5600mm, and the effective volume of the single cavity 5 is 100×100×200mm. The effective volume is the spatial volume that can be used to accommodate damping particles.

[0025] Among them, when the load-bearing structure is a base, at most 3 to 4 box shells 1 are embedded in any base section, the total effective volume of the mass tuning container 3 in each box shell 1 is 100×100×5600mm, and the effective volume of a single cavity 5 is 100×100×200mm, and the effective volume is the spatial volume that can be used to accommodate damping particles.

[0026] The beneficial effects of the present invention include:

[0027] (1) The mass-tuned damping particle composite built-in vibration reduction device provided by the present invention is embedded in the load-bearing structure and processed as one piece, so that the construction plan of rail transit is basically the same as the original plan, without adding any additional difficulty. At the same time, due to the addition of the device, the requirements for traditional vibration reduction devices are greatly reduced;

[0028] (2) The mass-tuned damping particle composite built-in vibration reduction device provided by the present invention can be buried in different load-bearing structures, and different burying positions and burying methods can be selected according to the characteristics of the road section, thereby maximizing the vibration reduction effect;

[0029] (3) The built-in damping particle vibration reduction device provided by the present invention comprises a mass tuning container, a plurality of mutually independent cavities are arranged in the mass tuning container, and damping particles are filled in the cavities, so that vibration energy is consumed by collision and friction between the damping particles and the wall surface, and collision and friction between the damping particles.

[0030] (4) The mass-tuned damping particle composite built-in vibration reduction device provided by the present invention has a spring disposed outside the mass tuning container in the box shell. By selecting appropriate spring stiffness, vibration frequency, weight of the mass tuning container, etc., the natural frequency of the entire vibration reduction device is made close to the natural frequency of the load-bearing structure, so as to increase the effective vibration reduction frequency range of the vibration reduction device and improve the vibration reduction effect of the vibration reduction device as a whole.

[0031] (5) The mass-tuned damping particle composite built-in vibration reduction device provided by the present invention has damping particles with a particle size of 0.1 to 1 mm filled in the cavity, which has the best "energy dissipation" and "vibration reduction" effects; the preferred order of materials is: lead, steel, iron, sand, etc.; the particle shape of the damping particles is mainly spherical, which is most conducive to vibration, collision, and energy dissipation;

[0032] (6) The mass-tuned damping particle composite built-in vibration reduction device provided by the present invention uses damping particles whose filling volume accounts for about 80-90% of the cavity. Multiple experiments and theoretical studies have proved that the volume ratio within this range has the best vibration reduction effect; too large a volume ratio is not conducive to particle movement and collision; too small a volume ratio has a poor effect due to a small probability of collision;

[0033] (7) The mass-tuned damping particle composite built-in vibration reduction device provided by the present invention is provided with a spring; since the particles need to move to collide with each other, too small displacement of the surrounding environment is not enough to stimulate the "movement" of the particles; the spring provided in the present application has a dual effect, one is that it can amplify the movement effect, thereby stimulating the movement of the particles; the other is that it provides a mass-tuned elastic basic function, thereby providing the necessary movement means for the entire vibration-reducing mass-tuning container; when a vehicle passes by, due to its small vibration displacement, the vibration displacement of the track plate, rail, roadbed, etc. needs to rely on the spring to stimulate the movement of the damping particles and the mass-tuning container, so as to achieve a better vibration reduction effect;

[0034] (8) The mass-tuned damping particle composite built-in vibration reduction device provided by the present invention can be integrated with the load-bearing structure in which it is located, that is, a part of the load-bearing structure is regarded as the box shell, thereby achieving the effect of reducing costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 A schematic diagram showing the structure of the mass-tuned damping particle composite built-in vibration reduction device provided by the present invention when it is pre-buried in a trapezoidal sleeper;

[0036] Figure 2 A cross-sectional view of a mass-tuned damping particle composite built-in vibration reduction device provided by the present invention is shown;

[0037] Figure 3A three-dimensional perspective view of a mass-tuned damping particle composite built-in vibration reduction device provided by the present invention is shown;

[0038] Figure 4 An exploded view of the mass-tuned damping particle composite built-in vibration reduction device provided by the present invention is shown.

[0039] Reference numerals

[0040] 1-Box shell

[0041] 2- Spring

[0042] 3-Mass Tuning Container

[0043] 4-Baffle

[0044] 5- Cavity

[0045] 6- Damping particles

[0046] 7-Track slabs or sleepers

[0047] 8-Container sealing plate DETAILED DESCRIPTION

[0048] The present invention will be further described in detail below through the accompanying drawings and embodiments. Through these descriptions, the characteristics and advantages of the present invention will become more clear and distinct.

[0049] The word "exemplary" is used exclusively herein to mean "serving as an example, embodiment, or illustration." Any embodiment described herein as "exemplary" is not necessarily to be construed as preferred or advantageous over other embodiments. Although various aspects of the embodiments are shown in the drawings, the drawings are not necessarily drawn to scale unless otherwise noted.

[0050] The present invention provides a mass-tuned damping particle composite built-in vibration reduction device, such as Figure 1 and Figure 4 As shown in , the device is pre-embedded in the load-bearing structure under the rail, and the load-bearing structure is a trapezoidal sleeper, a ballast, a track plate or a base; in this application, the pre-embedded means that during the process of manufacturing the load-bearing structure, the device is buried therein, and the load-bearing structure obtained is basically consistent with the appearance of the traditional structure to facilitate subsequent construction;

[0051] The device includes a box shell 1, which can be made of steel plate, or other materials with sufficient physical properties, such as cement consistent with the material of the load-bearing structure. The box shell 1 can be omitted in combination with the internal structural design of the track plate, sleeper, etc., and only the fixing and installation of the spring 2 is required.

[0052] like Figure 2 and Figure 3As shown in the figure, a spring 2 and a mass tuning container 3 are arranged inside the box shell 1, the mass tuning container 3 is a closed container, which is sealed by a container sealing plate 8, and the container sealing plate 8 can be sealed and connected to other wall surfaces of the mass tuning container 3 by welding, and the mass tuning container 3 is filled with damping particles 6, and the damping particles are selected from one or more of iron sand, lead particles, steel balls, and sand; the inventors found that the preferred order of the damping particle material is: lead, steel, iron, sand, etc.; suitable damping particles can be selected according to the vibration reduction performance requirements and economy.

[0053] In the present application, preferably, the damping particles are approximately spherical in shape. The spherical shape can make the collision vibration between each other more irregular, and the overall vibration reduction effect is the best. More preferably, the particle size of the damping particles is 0.1-1 mm, preferably 0.2-0.8 mm; the multiple damping particles filled in a mass tuning container 3 may not have completely consistent particle sizes with each other, as long as they are all within the specified range. The inventors found that when the particle size is controlled within the above-mentioned 0.2-0.8 mm, the overall vibration reduction effect is best.

[0054] The vibration energy is consumed by the collision and friction between the damping particles 6 and the wall surface, and the collision and friction between the damping particles.

[0055] Preferably, the spring 2 is arranged between the mass tuning container 3 and the box shell 1 to avoid direct contact between the mass tuning container 3 and the box shell 1 .

[0056] At least two springs are arranged on the inner wall of each box shell 1, and the size and elastic modulus of each spring are basically the same. The spring at the bottom can be appropriately lengthened or thickened to cope with the influence of the weight of the mass tuning container 3. In this application, the spring 2 is extremely necessary, and its stiffness needs to be determined by calculation, so as to maximize the "movement" of the tuning container 3 when it resonates, and to maintain an appropriate degree of displacement, recovery, speed, etc., and ultimately make the frequency of the mass tuning container of the vibration reduction device as close to or consistent with the natural frequency of the structure to be damped, that is, the load-bearing structure.

[0057] Preferably, the spring can be replaced by an elastic material with damping. If only a spring is provided, a liquid or solid damping should be provided in the housing 1 accordingly, so as to adapt the damping characteristics required outside the mass tuning container. The use of a spring component in the present invention is only considered to be intuitive and convenient for explaining the mechanical model of the present invention, and is not a specific recommended engineering practice during implementation.

[0058] Preferably, a plurality of baffles 4 are provided in the mass tuning container 3, and the baffles 4 divide the mass tuning container 3 into a plurality of independent cavities 5, that is, each baffle 4 is sealedly connected to the baffle and the mass tuning container 3, and when the mass tuning container 3 and the baffles 4 are both made of steel, they are connected to each other by welding.

[0059] The wall surface is the inner wall surface of the cavity 5 formed by the inner wall of the mass tuning container 3 and the baffle 4 .

[0060] In a preferred embodiment, the damping particles 6 are filled in the cavity 5; that is, each cavity 5 is filled with the damping particles 6, and the volume proportion of the damping particles 6 in each cavity 5 is consistent, so that the vibration damping performance at various locations in the mass tuning container 3 is consistent, and the vibration damping performance of the vibration damping device is uniform and reliable.

[0061] In a preferred embodiment, in the cavity 5, the volume proportion of the damping particles 6 is 80-90%, preferably about 85%. The applicant has found that according to the vibration characteristics of the railway system, the vibration reduction performance of about 85% volume proportion is the best, which can maximize the vibration reduction effect.

[0062] In a preferred embodiment, the spatial volumes inside the multiple mass tuning containers 3 installed in the same load-bearing structure are consistent, and the spatial volumes inside the multiple cavities 5 are consistent, that is, the baffle 4 evenly divides the mass tuning container 3 into multiple cavities 5; this setting can also ensure that the overall vibration reduction effect of the vibration reduction device is uniform and stable, thereby improving the service life of the load-bearing structure.

[0063] In a preferred embodiment, in each mass tuning container 3, the number of cavities 5 is 20-30.

[0064] Preferably, during the pouring process of the load-bearing structure, the box shell 1 is buried inside it;

[0065] When the box shell 1 is provided with one, the box shell 1 is buried in the middle of the load-bearing structure; the length direction of the box shell 1 is consistent with the length direction of the load-bearing structure;

[0066] When there are multiple box shells 1, the horizontal heights of the multiple box shells 1 are consistent; in the vertical direction, the distances between each box shell 1 and the top and bottom of the load-bearing structure are basically consistent; in the horizontal direction, the multiple box shells 1 are symmetrically and evenly distributed in the load-bearing structure;

[0067] Preferably, the box shell 1 is completely buried inside the load-bearing structure, that is, the box shell 1 is not visible from outside the load-bearing structure.

[0068] There are two common track laying schemes in the track system. One is that from top to bottom, there are rails, trapezoidal sleepers and bases; the other is that from top to bottom, there are rails, track plates and roadbeds. That is, the base in this application is used in conjunction with the trapezoidal sleepers, and the base is used to support the trapezoidal sleepers; the track plates in this application are used in conjunction with the roadbeds, and the roadbeds are used to support the track plates.

[0069] The trapezoidal sleeper in the present application comprises two longitudinal beams extending along the length direction of the rails, on which the rails are installed and fixed by rail supports, and between the two longitudinal beams there are arranged a varying number of transverse connecting mechanisms, and the box shell in the present application is pre-buried in the longitudinal beams, and the length direction of the box shell is consistent with the extension direction of the longitudinal beams and the rails; in actual engineering, the frame-type track plate also has a longitudinal beam structure similar to the above-mentioned trapezoidal sleepers, which can also be used to bury the box shell in the present application, so the trapezoidal sleepers in the present application include trapezoidal sleepers in the traditional sense, and also include sleeper structures with similar structural forms such as frame-type track plates, that is, sleeper structures with longitudinal beam structures that can be used to bury the box shell in the present application can be classified as the trapezoidal sleepers in the present application.

[0070] The track plate in the present application includes a whole, continuous track plate, which can carry two rails at the same time. There is no longitudinal beam on such a track plate, and more box shells can be buried in parallel in the track plate, which has a larger burying space. Therefore, for a track plate with such a structural form, more than 10 box shells in the present application can be buried while ensuring that its physical properties such as strength meet the requirements.

[0071] In a preferred embodiment, Figure 1 As shown in , when the load-bearing structure is a trapezoidal sleeper 7, 1 to 3 box shells 1 are evenly pre-buried in the trapezoidal sleeper with a sleeper length of 6 meters, the total effective volume of the mass tuning container 3 in each box shell 1 is 100×100×5600mm, and the effective volume of a single cavity 5 is 100×100×200mm, that is, the width dimension inside the mass tuning container 3 is 100mm, the height dimension is 100mm, and the length dimension is 5600mm, and a total of 28 cavities 5 are provided; the effective volume is the space volume that can be used to accommodate damping particles;

[0072] In the present application, since the length of the mass tuning container is too large, it is not conducive to increasing the chances of collision between the damping particles and between the damping particles and the container wall. By adding a baffle 4 to divide the container into several smaller containers, the collision effect can be greatly improved.

[0073] In a preferred embodiment, when the load-bearing structure is a ballast bed, at most 10 to 12 box shells 1 are embedded in any ballast bed section; the length of each box shell 1 can be arranged according to the requirements of the actual construction section length, and it is recommended that its length is slightly greater than 3000 mm, so that 15 cavities with an effective volume of 100×100×200 mm can be arranged in the mass tuning container, and the effective volume is the space volume that can be used to accommodate damping particles;

[0074] The cavity of "100×100×200mm" in the present application is the optimal volume size. The inventor has found through theoretical calculations and several experiments that too small or too large cavity size is not conducive to the collision and energy consumption of the damping particles 6, and will cause particle rolling, too small displacement, too small speed, accumulation, compaction and other phenomena that are not conducive to vibration reduction.

[0075] In a preferred embodiment, when the load-bearing structure is a track plate, 8 to 10 box shells 1 are evenly pre-embedded in the track plate with a length of about 6 meters and a width of about 2.5 meters, and the total effective volume of the mass tuning container 3 in each box shell 1 is 100×100×5600mm, and the effective volume of a single cavity 5 is 100×100×200mm, and the effective volume is the spatial volume that can be used to accommodate damping particles; that is, 28 cavities 5 are opened in each mass tuning container 3.

[0076] In a preferred embodiment, when the load-bearing structure is a base, at most 3 to 4 box shells 1 are embedded in any section of the base, the total effective volume of the mass tuning container 3 in each box shell 1 is 100×100×3000mm, and the effective volume of a single cavity 5 is 100×100×200mm, and the effective volume is the spatial volume that can be used to accommodate damping particles; that is, 15 cavities 5 are opened in the mass tuning container 3.

[0077] Example

[0078] Three mass-tuned particle damping composite built-in vibration reduction devices are evenly embedded in the 6-meter-long trapezoidal sleeper. Each vibration reduction device includes a box shell, and each box shell is provided with multiple springs and a mass tuning container, such as Figure 1 As shown in , each mass tuning container is separated by a partition to form 28 cavities, and the effective volume of each cavity is 100×100×200mm, and the effective volume is the space volume that can be used to accommodate damping particles; the external volume of each vibration reduction device accounts for 10% of the total volume of the trapezoidal sleeper, and the external volume of three vibration reduction devices accounts for 30% of the total volume of the trapezoidal sleeper. The damping ratio of the spring is 0.05, and its stiffness makes the natural frequency of the vibration reduction device basically equal to the natural frequency of the load-bearing structure, and the natural frequency is 18 to 35HZ.

[0079] Each cavity is filled with iron sand particles, the particle size of which is 0.2-0.4 mm; in each mass tuning container, the volume of the iron sand particles accounts for 85%;

[0080] The trapezoidal sleeper was laid in a complete standard railway track. A 6-car B-type subway train with an axle weight of 14 tons was used. The vehicle pitch and wheelbase were 12.6m and 2.25m respectively. When the vertical vibration level of the tunnel wall at the mileage section was measured to be 73.6dB, the vertical vibration level of the tunnel wall at the mileage section was 73.6dB.

[0081] The subway train was then driven at a speed of 69 km / h through other sections of the standard track, i.e. sections with the same geology, fasteners, and sleeper positions, and with ordinary trapezoidal sleepers laid. The vertical vibration magnitude of the tunnel wall at this mileage section was measured to be 79.3 dB.

[0082] This shows that the trapezoidal sleeper equipped with the mass-tuned particle damping composite built-in vibration reduction device can significantly reduce the vibration generated when a train passes by.

[0083] Comparative Example 1

[0084] Two mass-tuned particle damping composite built-in vibration-damping devices are evenly embedded in the 6-meter-long trapezoidal sleeper. Each vibration-damping device includes a box shell, each box shell is provided with multiple springs and a mass-tuning container, and each mass-tuning container is separated by a partition to form 28 cavities. The effective volume of each cavity is 100×100×200mm, and the effective volume is the space volume that can be used to accommodate damping particles; the external volume of each vibration-damping device accounts for 10% of the total volume of the trapezoidal sleeper, and the external volume of the two vibration-damping devices accounts for 20% of the total volume of the trapezoidal sleeper. The damping ratio of the spring is 0.05, and its stiffness makes the natural frequency of the vibration-damping device basically equal to the natural frequency of the load-bearing structure, and the natural frequency is 18 to 35HZ.

[0085] Each cavity is filled with iron sand particles, the particle size of which is 0.2-0.4 mm; in each mass tuning container, the volume of the iron sand particles accounts for 85%;

[0086] The trapezoidal sleeper was laid in a complete standard railway track. A 6-car B-type subway train with an axle weight of 14 tons was used. The vehicle pitch and wheelbase were 12.6m and 2.25m respectively. When the vertical vibration level of the tunnel wall at the mileage section was measured to be 77.2dB, the vertical vibration level of the tunnel wall at the mileage section was 77.2dB.

[0087] The subway train was then driven at a speed of 69 km / h through other sections of the standard track, i.e. sections with the same geology, fasteners, and sleeper positions, and with ordinary trapezoidal sleepers laid. The vertical vibration magnitude of the tunnel wall at this mileage section was measured to be 79.3 dB.

[0088] Comparative Example 2

[0089] Three mass-tuned particle damping composite built-in vibration-damping devices are evenly embedded in a 6-meter-long trapezoidal sleeper. Each vibration-damping device includes a box shell, each box shell is provided with a plurality of springs and a mass-tuning container, and each mass-tuning container is separated by a partition to form 28 cavities. The effective volume of each cavity is 100×100×200mm, and the effective volume is the space volume that can be used to accommodate damping particles; the external volume of each vibration-damping device accounts for 10% of the total volume of the trapezoidal sleeper, and the external volume of the three vibration-damping devices accounts for 30% of the total volume of the trapezoidal sleeper. The damping ratio of the spring is 0.05, and its stiffness makes the natural frequency of the vibration-damping device basically equal to the natural frequency of the load-bearing structure, and the natural frequency is 18 to 35HZ.

[0090] Each cavity is filled with iron sand particles, the particle size of which is 0.2-0.4 mm; in each mass tuning container, the volume of the iron sand particles accounts for 50%;

[0091] The trapezoidal sleeper was laid in a complete standard railway track. A 6-car B-type subway train with an axle weight of 14 tons was used. The vehicle pitch and wheelbase were 12.6m and 2.25m respectively. When the vertical vibration level of the tunnel wall at the mileage section was measured to be 76.8dB, the vertical vibration level of the tunnel wall at the mileage section was 76.8dB.

[0092] The subway train was then driven at a speed of 69 km / h through other sections of the standard track, i.e. sections with the same geology, fasteners, and sleeper positions, and with ordinary trapezoidal sleepers laid. The vertical vibration magnitude of the tunnel wall at this mileage section was measured to be 79.3 dB.

[0093] Comparative Example 3

[0094] Three mass-tuned particle damping composite built-in vibration-damping devices are evenly embedded in a 6-meter-long trapezoidal sleeper. Each vibration-damping device includes a box shell, each box shell is provided with multiple springs and a mass-tuning container, and each mass-tuning container is separated by a partition to form 14 cavities. The effective volume of each cavity is 100×100×400mm, and the effective volume is the space volume that can be used to accommodate damping particles; the external volume of each vibration-damping device accounts for 10% of the total volume of the trapezoidal sleeper, and the external volume of the three vibration-damping devices accounts for 30% of the total volume of the trapezoidal sleeper. The damping ratio of the spring is 0.05, and its stiffness makes the natural frequency of the vibration-damping device basically equal to the natural frequency of the load-bearing structure, and the natural frequency is 18 to 35HZ.

[0095] Each cavity is filled with iron sand particles, the particle size of which is 0.2-0.4 mm; in each mass tuning container, the volume of the iron sand particles accounts for 85%;

[0096] The trapezoidal sleeper was laid in a complete standard railway track. A 6-car B-type subway train with an axle weight of 14 tons was used. The vehicle pitch and wheelbase were 12.6m and 2.25m respectively. When the vertical vibration level of the tunnel wall at the mileage section was measured to be 76.1dB, the vertical vibration level of the tunnel wall at the mileage section was 76.1dB.

[0097] The subway train was then driven at a speed of 69 km / h through other sections of the standard track, i.e. sections with the same geology, fasteners, and sleeper positions, and with ordinary trapezoidal sleepers laid. The vertical vibration magnitude of the tunnel wall at this mileage section was measured to be 79.3 dB.

[0098] By comparing the embodiment with comparative examples 1, 2 and 3, it is shown that the relatively optimal parameters of the mass-tuned damping particle composite built-in vibration reduction device in the embodiment are:

[0099] Total volume of vibration reduction device / volume of load-bearing structure: 30%;

[0100] The size of a single cavity: 100×100×200mm;

[0101] Volume proportion of damping particles in the cavity: 0.85.

[0102] It can be seen from the above embodiments that the damping particle composite built-in vibration reduction device with mass tuning provided in the present application can significantly reduce the vibration generated when a train passes by.

[0103] The present invention has been described above in conjunction with preferred embodiments, but these embodiments are only exemplary and serve only as an illustration. On this basis, the present invention may be subjected to a variety of substitutions and improvements, all of which fall within the scope of protection of the present invention.

Claims

1. A mass-tuned damping particle composite built-in vibration reduction device, characterized in that: The device is pre-buried and installed in the load-bearing structure below the rail, and the load-bearing structure is a trapezoidal sleeper, a ballast bed, a track plate or a base; The device comprises a box shell (1), a spring (2) and a mass tuning container (3) are arranged inside the box shell (1), the mass tuning container (3) is a closed container filled with damping particles (6), and the damping particles are selected from one or more of iron sand, lead particles, steel balls, and sand; The vibration energy is consumed by the collision and friction between the damping particles (6) and the wall surface, and the collision and friction between the damping particles. The spring (2) is arranged between the mass tuning container (3) and the housing (1). The spring (2) amplifies the displacement and velocity of the vibration of the mass tuning container (3), thereby improving the energy consumption efficiency of the damping particles (6) in the mass tuning container (3). The spring (2) also prevents the mass tuning container (3) from directly contacting the housing (1).

2. The mass-tuned damping particle composite built-in vibration reduction device according to claim 1, characterized in that: A mass tuning container (3) is arranged in the box shell (1), and a plurality of baffles (4) are arranged in each mass tuning container (3), and the baffles (4) divide the mass tuning container (3) into a plurality of cavities (5) that are independent of each other; The wall surface is the inner wall surface of the cavity (5) formed by the inner wall of the mass tuning container (3) and the baffle (4).

3. The mass-tuned damping particle composite built-in vibration reduction device according to claim 2, characterized in that: In the cavity (5), the volume proportion of the damping particles (6) material is 80-90%.

4. The mass-tuned damping particle composite built-in vibration reduction device according to claim 2, characterized in that: The spatial volumes inside the various cavities (5) are consistent, that is, the baffles (4) evenly divide the mass tuning container (3) into a plurality of cavities (5).

5. The mass-tuned damping particle composite built-in vibration reduction device according to claim 4, characterized in that: In each mass tuning container (3), the number of cavities (5) is 20 to 30.

6. The mass-tuned damping particle composite built-in vibration reduction device according to claim 4, characterized in that: During the pouring process of the load-bearing structure, the box shell (1) is buried inside the box shell; the length direction of the box shell (1) is consistent with the length direction of the load-bearing structure; When the box shell (1) is provided with one, the box shell (1) is buried in the middle of the load-bearing structure; When a plurality of the box shells (1) are provided, the horizontal heights of the plurality of box shells (1) are consistent; In the vertical direction, the distances between each box shell (1) and the top and bottom of the load-bearing structure are substantially the same; in the horizontal direction, the multiple box shells (1) are symmetrically and evenly distributed in the load-bearing structure; Preferably, the box shell (1) is completely embedded in the load-bearing structure, that is, the box shell (1) is not visible from the outside of the load-bearing structure.

7. The mass-tuned damping particle composite built-in vibration reduction device according to claim 6, characterized in that: When the load-bearing structure is a trapezoidal sleeper (7), one to three box shells (1) are pre-buried in the trapezoidal sleeper with a sleeper length of 6 meters, the total effective volume of the mass tuning container (3) in each box shell (1) is 100×100×5600 mm, and the effective volume of a single cavity (5) is 100×100×200 mm, wherein the effective volume is the spatial volume that can be used to accommodate damping particles.

8. The mass-tuned damping particle composite built-in vibration reduction device according to claim 6, characterized in that: When the load-bearing structure is a ballast bed, at most 10 to 12 box shells (1) are pre-buried in any ballast bed section, the length of the box shells (1) is 3 meters, and a plurality of cavities (5) are arranged in the mass tuning container (3) of each box shell (1), the effective volume of a single cavity (5) is 100×100×200 mm, and the effective volume is the spatial volume that can be used to accommodate damping particles.

9. The mass-tuned damping particle composite built-in vibration reduction device according to claim 6, characterized in that: When the load-bearing structure is a track plate, 8 to 10 box shells (1) are pre-buried in the track plate with a length of 6 meters and a width of 2.5 meters. The total effective volume of the mass tuning container (3) in each box shell (1) is 100×100×5600 mm, and the effective volume of a single cavity (5) is 100×100×200 mm. The effective volume is the spatial volume that can be used to accommodate damping particles.

10. The mass-tuned damping particle composite built-in vibration reduction device according to claim 6, characterized in that: When the load-bearing structure is a base, at most 3 to 4 box shells (1) are embedded in any section of the base, the total effective volume of the mass tuning container (3) in each box shell (1) is 100×100×5600 mm, and the effective volume of a single cavity (5) is 100×100×200 mm, wherein the effective volume is the spatial volume that can be used to accommodate damping particles.

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