阅读说明：本技术 一种可调准周期阻尼钢轨 (Adjustable quasi-periodic damping steel rail ) 是由 冯青松 周涛 张凌 杨立新 毛建红 于 2021-01-13 设计创作，主要内容包括：本发明的目的在于提供一种可调准周期阻尼钢轨,其特征在于：包括钢轨本体、层状声子晶体结构体、一维声子晶体减振层、横向振动传递杆、带孔螺栓杆、紧固螺帽、竖向振动传递杆、颗粒阻尼器、曲柄连杆腔体、矩形截面腔体。本发明的方案增加了钢轨的垂向静刚度和阻尼,提高了轮轨振动顺轨向的衰减率,同时阻隔了轮轨辐射的一次噪声,有效控制轨道结构低中频域内的振动与噪声,可在0～2000Hz的较宽频段内耗散振动能量,且整体结构拆卸方便,易于更换零部件。(The invention aims to provide an adjustable quasi-periodic damping steel rail, which is characterized in that: the steel rail comprises a steel rail body, a layered phononic crystal structure body, a one-dimensional phononic crystal vibration reduction layer, a transverse vibration transmission rod, a bolt rod with holes, a fastening nut, a vertical vibration transmission rod, a particle damper, a crank connecting rod cavity and a rectangular section cavity. According to the scheme provided by the invention, the vertical static stiffness and damping of the steel rail are increased, the attenuation rate of the wheel rail vibration along the rail direction is improved, the primary noise radiated by the wheel rail is blocked, the vibration and noise in a low-medium frequency region of a track structure are effectively controlled, the vibration energy can be dissipated in a wider frequency band of 0-2000Hz, the whole structure is convenient to disassemble, and parts are easy to replace.)

1. An adjustable quasi-periodic damping steel rail is characterized in that: the steel rail comprises a steel rail body, a layered phononic crystal structure body, a one-dimensional phononic crystal vibration reduction layer, a transverse vibration transmission rod, a bolt rod with holes, a fastening nut, a vertical vibration transmission rod, a particle damper, a crank connecting rod cavity and a rectangular section cavity.

2. The adjustable quasi-periodic damping rail according to claim 1, wherein: the layered phononic crystal structure is attached to the rail waist position of the steel rail body.

3. The adjustable quasi-periodic damping rail according to claim 2, wherein: the phononic crystal structure 2 is a novel structural layer formed by periodically arranging a material A and a material B.

4. The adjustable quasi-periodic damping rail according to claim 1, wherein: the matrix of the one-dimensional phononic crystal vibration reduction layer is a rectangular structure formed by periodically arranging two materials of a material C and a material D along the thickness direction, one end of the rectangular structure is attached to the layered phononic crystal structure, and the other end of the rectangular structure is fixedly connected with the transverse vibration transmission rod.

5. An adjustable quasi-periodic damping rail according to claim 4, wherein: and the other end of the one-dimensional phononic crystal vibration reduction layer is provided with a threaded hole and is rotationally connected with the cylindrical thread of the transverse vibration transmission rod.

6. An adjustable quasi-periodic damping rail according to any one of claims 1 to 5, wherein: the vertical vibration transmission rod is connected with the transverse vibration transmission rod through the bolt rod with the hole.

7. An adjustable quasi-periodic damping rail according to claim 6, wherein: one end of the perforated bolt rod is coaxially connected with the transverse vibration transmission rod through a threaded structure, and the vertical vibration transmission rod penetrates through a threaded hole of the perforated bolt rod and is fixed through a fastener.

8. An adjustable quasi-periodic damping rail according to claim 7, wherein: the threaded hole at the upper end part of the crank connecting rod cavity is rotationally connected with the cylindrical thread of the vertical vibration transmission rod, and the cylindrical thread at the lower end part of the crank connecting rod cavity is rotationally connected with the threaded hole at the side surface of the rectangular cross-section cavity.

9. The adjustable quasi-periodic damping rail according to claim 8, wherein: the particle dampers are of spherical structures and are uniformly distributed in the cavity units of the crank connecting rod cavity and the cavity with the rectangular cross section.

10. The adjustable quasi-periodic damping rail according to claim 8, wherein: the layered phononic crystal structure A material and the layered phononic crystal structure B material are polyurethane rubber, smoked sheet natural rubber or ethylene propylene rubber; the material C and the material D of the one-dimensional phononic crystal damping layer are resin materials, silicon rubber or chloroprene rubber.

Technical Field

The invention belongs to the field of vibration and noise reduction of rail transit, and particularly relates to an adjustable quasi-periodic phononic crystal damping steel rail applied to urban rail transit and high-speed railways.

Background

In recent years, rail transit is developed vigorously due to the advantages of large transportation capacity, low energy consumption and the like, and with the increase of operation mileage and the improvement of operation speed, the problems of environmental vibration and noise caused by rail transit are increasingly highlighted, wherein the problems of severe vibration generated by friction between wheels and steel rails in the running process of a train and noise radiated to the outside are still main sources, so that the living environment of people is directly influenced, the fatigue damage of train components is caused, and the service life of key parts of a rail structure is shortened.

At present, the rail transit takes various vibration-damping and noise-reducing measures with various types in four aspects of vibration isolation, vibration absorption, vibration resistance and vibration elimination, and the measures mainly comprise labyrinth damping steel rails, broadband damping steel rails, vibration-damping fasteners, trapezoidal sleepers, steel spring floating plates, sound-absorbing plates and the like, but various vibration-damping and noise-reducing measures still have defects and shortcomings in the actual use process, for example, the vibration-damping and noise-reducing effect on wheel rail noise in a low-frequency range is not ideal, and the vibration-damping effect on a very wide frequency band cannot be realized.

The phononic crystal is a periodic composite material with elastic wave band gap and composed of two or more than two elastic media, and is periodically arranged in a specific direction by taking a unit cell as a minimum unit and taking a lattice constant as a basic size. When an elastic wave propagates in a phononic crystal, the elastic wave in some frequency ranges cannot propagate due to the internal periodic structure, the corresponding frequency ranges are called band gaps, and the elastic wave in other ranges can propagate and are called pass bands. At present, there are two types of bandgap formation mechanisms for phononic crystals that are often mentioned and are well established. According to the proportional relationship between the wavelength corresponding to the band gap frequency and the lattice constant, the band gap can be divided into a bragg scattering type and a local resonance type.

Although the track structure has obvious periodic characteristics and band gap characteristics, the band gap range is small, and the attenuation capacity of elastic waves in the band gap is weak. According to the Bloch wave vector obtained by solving, the elastic wave propagating in the structure can be divided into three regions: (1) the attenuated region, abbreviated a. At the moment, the elastic wave propagation in the structure is in an attenuation characteristic, and the phase changes by 0 or +/-pi after passing through one lattice length; (2) the propagation region, abbreviated as P. At the moment, the phase of the elastic wave in the structure changes Re (ql) after passing through one lattice length, and the amplitude is kept unchanged; (3) the complex solution area is abbreviated as C. Representing elastic wave propagation as well as evanescent waves, the phase changes re (ql) after one lattice length. Therefore, by utilizing the band gap characteristic of the phononic crystal and introducing a local resonance mechanism, the adjustable quasi-periodic damping steel rail based on the phononic crystal and the particle damper can be designed, the band gap of a low-intermediate frequency broadband is generated, and the propagation of elastic waves in the band gap frequency range is inhibited.

Disclosure of Invention

The invention aims to solve the problem that the effect of the existing vibration and noise reduction measures in a low-medium frequency domain is not obvious, and provides an adjustable quasi-periodic damping steel rail based on a phononic crystal and a particle damper.

Specifically, the invention aims to provide an adjustable quasi-periodic damping steel rail, which is characterized in that: the steel rail comprises a steel rail body, a layered phononic crystal structure body, a one-dimensional phononic crystal vibration reduction layer, a transverse vibration transmission rod, a bolt rod with holes, a fastening nut, a vertical vibration transmission rod, a particle damper, a crank connecting rod cavity and a rectangular section cavity.

Further, it is characterized in that: the layered phononic crystal structure is attached to the rail waist position of the steel rail body.

Further, it is characterized in that: the phononic crystal structure 2 is a novel structural layer formed by periodically arranging a material A and a material B

Further, it is characterized in that: the matrix of the one-dimensional phononic crystal vibration reduction layer is a rectangular structure formed by periodically arranging two materials of a material C and a material D along the thickness direction, one end of the rectangular structure is attached to the layered phononic crystal structure, and the other end of the rectangular structure is fixedly connected with the transverse vibration transmission rod.

Further, it is characterized in that: and the other end of the one-dimensional phononic crystal vibration reduction layer is provided with a threaded hole and is rotationally connected with the cylindrical thread of the transverse vibration transmission rod.

Further, it is characterized in that: the vertical vibration transmission rod is connected with the transverse vibration transmission rod through the bolt rod with the hole.

Further, it is characterized in that: one end of the perforated bolt rod is coaxially connected with the transverse vibration transmission rod through a threaded structure, and the vertical vibration transmission rod penetrates through a threaded hole of the perforated bolt rod and is fixed through a fastener.

Further, it is characterized in that: the threaded hole at the upper end part of the crank connecting rod cavity is rotationally connected with the cylindrical thread of the vertical vibration transmission rod, and the cylindrical thread at the lower end part of the crank connecting rod cavity is rotationally connected with the threaded hole at the side surface of the rectangular cross-section cavity.

Further, it is characterized in that: the particle dampers are of spherical structures and are uniformly distributed in the cavity units of the crank connecting rod cavity and the cavity with the rectangular cross section.

Further, it is characterized in that: the layered phononic crystal structure A material and the layered phononic crystal structure B material are polyurethane rubber, smoked sheet natural rubber or ethylene propylene rubber; the material C and the material D of the one-dimensional phononic crystal damping layer are resin materials, silicon rubber or chloroprene rubber.

The invention has the advantages that:

1. according to the damping dynamic vibration absorption and vibration isolation principle, the layered photonic crystal structure body and the one-dimensional photonic crystal vibration absorption layer can increase the vertical static rigidity and damping of the steel rail, improve the attenuation rate of the wheel rail vibration along the rail direction, and simultaneously block primary noise radiated by the wheel rail.

2. A photonic crystal local resonance mechanism is introduced, the band gap range of the track structure is widened, elastic wave control in the track structure is realized, a resonance unit is periodically added at the rail waist position of the steel rail to form a local resonance type photonic crystal structure, and vibration and noise in a low-medium frequency domain of the track structure are effectively controlled.

3. The amplitude-frequency variation characteristic of the particle damper is considered, the particle damper is applied to a steel rail vibration environment, vibration energy can be dissipated in a wide frequency range of 0-2000Hz, and the vibration and noise reduction effect of the vibration and noise reduction device is further enhanced.

4. The invention can freely adjust the mounting position of the one-dimensional phononic crystal damping layer on the layered phononic crystal structure body through the transverse and vertical vibration transmission rods, flexibly use various rod pieces to fix the device, is convenient to disassemble and is easy to replace parts.

Drawings

FIG. 1 is a schematic view of the adjustable periodic photonic crystal damping rail of the present invention along the direction of the rail.

FIG. 2 is a schematic side view of an adjustable periodic photonic crystal damped rail of the present invention.

FIG. 3 is an enlarged view of the one-dimensional phononic crystal damping layer and the lateral vibration transfer rod assembly.

Fig. 4 is an enlarged schematic view of the lateral vibration transfer rod and the vertical vibration transfer rod assembly.

FIG. 5 is an enlarged schematic view of the crank link cavity and rectangular cross section cavity assembly.

Detailed Description

In order to make the technical solution and advantages of the present invention more clear, the present invention is described in detail below with reference to the accompanying drawings and specific embodiments.

The quasi-period-adjustable damping steel rail according to the present embodiment is described with reference to fig. 1 to 5, and includes a steel rail body 1, a layered phononic crystal structure 2, a one-dimensional phononic crystal damping layer 3, a transverse vibration transmission rod 4, a bolt rod with holes 5, a fastening nut 6, a vertical vibration transmission rod 7, a particle damper 8, a crank link cavity 9, and a rectangular cross-section cavity 10.

According to the damping dynamic vibration absorption and vibration isolation principle, the layered photonic crystal structure body and the one-dimensional photonic crystal vibration absorption layer can increase the vertical static rigidity and damping of the steel rail, improve the attenuation rate of the wheel rail vibration along the rail direction, and simultaneously block primary noise radiated by the wheel rail.

The layered phononic crystal structure body 2 and the one-dimensional phononic crystal vibration reduction layer 3 are matched to form a band gap with wider frequency range, and the band gap is complementary with the range of the particle damper with insufficient vibration reduction frequency band, so that the propagation of vibration in the frequency range of 0-2000Hz is inhibited, and the low-medium frequency vibration reduction effect is realized

The steel rail body 1 is provided with a rail web, a top rail positioned at the upper end of the rail web and a rail seat positioned at the lower end of the rail web.

In one scheme, the layered phononic crystal structure 2 is attached to the rail waist position of the steel rail body 1. The phononic crystal structure 2 is a novel structural layer formed by periodically arranging a material A and a material B. Specifically, the structural layer can be cut according to the shape of the rail web of the steel rail, so that the layered phononic crystal structural body 2 is tightly attached to two sides of the rail web of the steel rail body 1 and is bonded together by using a high-strength adhesive.

In one scheme, the base body of the one-dimensional phononic crystal damping layer 3 is a rectangular structure formed by periodically arranging two materials of a material C and a material D along the thickness direction, one end of the rectangular structure is attached to the layered phononic crystal structure 2, and the other end of the rectangular structure is fixedly connected with the transverse vibration transmission rod 4. Preferably, the other end of the one-dimensional phononic crystal vibration attenuation layer 3 is provided with a threaded hole which is rotatably connected with a cylindrical thread of the transverse vibration transmission rod 4.

In one embodiment, the vertical vibration transmission rod 7 is connected to the lateral vibration transmission rod 4 by a bolt-equipped rod 5. Wherein, one end of the perforated bolt rod 5 is coaxially connected with the transverse vibration transmission rod 4 through a thread structure. The vertical vibration transmission rod 7 passes through the threaded hole of the holed bolt rod 5 and is fixed by a fastener, for example, a hexagonal fastening nut 6 is rotated to a cylindrical thread of the vertical vibration transmission rod 7, and the whole is fixed.

In one scheme, a threaded hole in the upper end of the crank connecting rod cavity 9 is rotationally connected with a cylindrical thread of the vertical vibration transmission rod 7, and a cylindrical thread in the lower end of the crank connecting rod cavity is rotationally connected with threaded holes in two sides of the rectangular-section cavity 10.

In one scheme, the particle dampers 8 are spherical structures and are uniformly distributed in a cavity unit of a crank connecting rod cavity 9 and a rectangular section cavity 10, wherein a threaded hole is processed at the upper end part of the crank connecting rod cavity 9, a cylindrical thread is processed at the lower end part of the crank connecting rod cavity 9, and threaded holes matched with the threads processed on the crank connecting rod cavity 9 are formed in the center positions of two sides of the rectangular section cavity 10.

In one scheme, the whole steel rail is a bilaterally-symmetrical stable structure, namely, layered phononic crystal structures 2, a one-dimensional phononic crystal vibration damping layer 3, a transverse vibration transmission rod 4, a perforated bolt rod 5, a fastening nut 6, a vertical vibration transmission rod 7, a particle damper 8 and a crank connecting rod cavity 9 are arranged on two sides of a steel rail body 1, the crank connecting rod cavities 9 on two sides are connected with a rectangular section cavity 10, and the installation, connection modes and sequential connection of components on two sides of the steel rail body 1 are kept consistent.

In one aspect, preferably, an elastic dynamics formula is introduced and a transmission matrix method is used to derive the dispersion relation of the layered phononic crystal structure, and each parameter can satisfy the following relation through calculation:

wherein the thickness of the material A is a₁The thickness of the material B is B₁The combined thickness (lattice constant) c ═ a of the two materials₁+b₁And a is a₁＝b₁K is the wavevector, h is the cross-sectional height of the material, α₁、α₂Is the material parameter of material A, B, and F is the force vector of the discrete node.

The lattice constant c, the parameters of the material A, B, etc. are substituted into the formula, the energy band structure between the wave vector k and the characteristic frequency is solved, and the lattice constant c is adjusted to control the band gap frequency range. For example, taking the lattice constant c as 0.20m, two band gaps of 4KHz to 13.7KHz and 18.30KHz to 24.2KHz are generated in the frequency range of 0 to 35 KHz; the lattice constant c is 0.04m, and two band gaps of 53.8 KHz-86.4 KHz and 91.2 KHz-112.3 KHz can be generated in the frequency range of 0-180 KHz. According to the actual vibration reduction requirement, the vibration reduction effect of different frequency bands can be realized by adjusting the size of the lattice constant c.

In one aspect, it is more preferable that the substrate of the one-dimensional phononic crystal vibration-damping layer 3 is a phononic crystal structure layer, wherein the thickness of the material C in the phononic crystal structure layer exhibits periodic variation, the thickness of the material D is constant, and the periodic variation of the thickness of the material C is at an initial thickness D_cPlus a variable thickness of sinusoidal variation. Introducing a periodic function d_c(x)＝d_c+d_c×(α²sin 2 π β/n) to adjust the thickness of the material C, wherein x is expressed as the xth (C + D) cell unit for calculating the thickness D of the xth cell unit_c(x) Alpha is a transmission coefficient used for adjusting the width of a band gap, and the variable beta is a medium elastic constant which is the characteristic of the materialThe performance is independent of the lattice constant, and n is the number of unit cells used for controlling the number of unit cells of the phononic crystal structure layer. By the arrangement, the thickness value range of the material C in each unit cell can be accurately calculated through the periodic function, and the use amount of the material C, D is saved to the maximum extent on the basis of meeting the requirements of structural periodicity and vibration reduction frequency range.

In one embodiment, the rod end of the crank link cavity 9 is threaded and mates with a threaded hole machined in the rectangular cross section cavity 10. By such arrangement, the components can be stably connected.

In one scheme, threaded holes matched with threads of the vertical vibration transmission rod 7 and the transverse vibration transmission rod 4 are respectively processed in the crank connecting rod cavity 9 and the one-dimensional phononic crystal vibration damping layer 5 and are connected through transverse and vertical rod pieces, so that the transmission of vibration can be guaranteed, the stability of the whole structure can be fully guaranteed, and the installation, the disassembly, the maintenance and the repair are convenient.

In one embodiment, the materials a and B of the layered phononic crystal structure 2 are polyurethane rubber, flake natural rubber, or ethylene propylene rubber. The material C and the material D of the one-dimensional phononic crystal damping layer 3 are resin materials, silicon rubber or chloroprene rubber. The selection principle of the materials of the layered phononic crystal structural body 2 and the one-dimensional phononic crystal damping layer 3 is determined according to the material strength, the fatigue performance, the climate environment and the region position. Polyurethane rubber can be selected for high requirements on wear resistance and buffering and vibration damping performance; the high temperature resistance can be selected from natural rubber and silicon rubber of tobacco flakes; ethylene propylene rubber and chloroprene rubber can be selected for high corrosion resistance.

In one embodiment, the transverse vibration transmission rod 4, the perforated bolt rod 5, the vertical vibration transmission rod 7 and the crank link cavity 9 are made of alloy material, and the fastening nut is made of steel material.

In one embodiment, the rectangular-section cavity 10 is made of a low-carbon steel with a good shape. Preferably, particle dampers 8 are uniformly distributed in the chambers of the crank connecting rod cavity 9 and the rectangular section cavity 10 in advance, and the filling rate of the particle dampers in the chambers of the crank connecting rod cavity and the rectangular section cavity is 45-75%. The granular damping material is made of one of stainless steel, carbon steel, brass, cupronickel or lead, and a layer of wear-resistant paint is sprayed on the surface of the granular damping material.

In one scheme, threaded holes are processed at the center positions of the left side and the right side of a rectangular section cavity 10 and fixedly connected with cylindrical threads at the rod end part of a crank connecting rod cavity 9

In one scheme, the adopted particle damper 8 is a solid stainless steel sphere with the diameter of 1-4 mm and is in a sphere shape. A layer of wear-resistant polyurethane coating with the thickness of 0.2mm is sprayed on the surface of the sphere, when train wheels move on the steel rail at a high speed, the particle damper can be separated from the bottom of the container by violent vibration generated by the steel rail, and the particle damper and the adjacent particle damper and the wall of the cavity are subjected to relative collision and friction, so that vibration energy is greatly dissipated.

In one scheme, the energy consumption and vibration reduction performance of the rectangular-section cavity particle damping container are analyzed, and the following equation is obtained according to stress balance:

σ_zlw+ρ_alwδzg＝(σ_z+δσ_z)lw+2τ_z(l+w)δ_z

wherein sigma_zThe principal stress to which the particle damper infinitesimal body is subjected, i is the length of the rectangular section, w is the width of the rectangular section, and rho_aIs the density of the particle damper infinitesimal body, deltaz is the height of the particle damper infinitesimal body, g is the gravity acceleration, delta is the stress variation, tau_zIs the frictional stress of the wall surface to the micro-element.

Let m be the length-width ratio l/w of the rectangular cross section, and assuming the number Q of the particle dampers in the rectangular cross section and the number Q of the particles on the surface of the particle damper layer, the static stress applied to the particle damper micro element is approximately expressed as:

wherein theta is_aIs the friction angle, k, of damping particles with the wall of a chamber with a rectangular cross section_lIs the stress constant, epsilon is the filling rate of the particle damper in the cavity, and r is the radius of the particle damper. Approximation of static stress from infinitesimal bodiesIt can be seen that the larger the length-width ratio m of the rectangular cross section, the greater the static stress σ that the particle damper infinitesimal body is subjected to_zThe smaller the particle damper is, namely the particle damper can achieve free motion behavior when the vibration intensity is lower, more particle dampers participate in the energy consumption motion of the wheel rail, the vibration energy in a low-medium frequency domain is consumed, and therefore the vibration damping effect is better.

In one scheme, the steel rails used by urban rail transit and high-speed railways are mainly 60 steel rails, and the detailed dimensions of the 60 steel rails are as follows: the height of the steel rail is 176mm, the width of the rail bottom is 150mm, the height of the rail head is 48.5mm, the width of the rail head is 73mm, and the thickness of the rail web is 16.5 mm. Preferably, considering the practical installation condition and the relation that the length-width ratio m is about 2 times l/w, the experimental effect is optimal, and therefore the chamber size of the crank connecting rod cavity 9 is designed as follows: the transverse length is 160 mm-140 mm, the longitudinal width is 60 mm-80 mm, the vertical height is 100 mm-120 mm, and the radius of the connecting rod is 10 mm; the chamber size of the rectangular section cavity 10 is 90 mm-100 mm in transverse length, 40 mm-50 mm in longitudinal width, 40 mm-50 mm in longitudinal height, and 30 mm-40 mm in vertical height.

In one scheme, preferably, in order to better control the vibration in the low and medium frequency regions, the particle diameter matching ratio of the particle damper 8 in the cavity of the crank connecting rod cavity 9 and the cavity 10 with the rectangular cross section is further optimized, and the vibration damping effect of the frequency band of 0-2000Hz is further achieved by fully combining the vibration damping frequency band range with different diameter matching ratios. The experiment is carried out by using a controlled variable method, and the effect shows that when the diameter of the particle is 3mm, the vibration damping effect is best at 150 Hz-300 Hz and 450 Hz-2000 Hz; when the particle diameter is 2-3 mm, the particle diameter of the small particle is complementary with that of the large particle, the particle contact probability is further improved, and the vibration reduction effect is best within 100Hz and after 450 Hz. The crank connecting rod cavity 9 is connected with the steel rail through a vibration transmission rod, and mainly vibrates at medium and high frequencies, so that particle dampers 8 with the diameter of 3mm are uniformly distributed in a cavity of the crank connecting rod cavity 9; rectangular cross section cavity 10 laminating is on track structure upper surface to low intermediate frequency vibration is given first place to, therefore 2 ~ 3 mm's mixture ratio granule attenuator of equipartition in rectangular cross section cavity 10's the cavity.

The installation process of the adjustable quasi-period damping steel rail based on the phononic crystal and particle damper is described in the following with the accompanying drawings:

(1) the arc line type of the layered phononic crystal structure body 2 is matched with the line type of the rail web of the steel rail, and the curved periodic phononic crystal structure layer 2 is bonded and fixed on the two sides of the rail web of the steel rail body 1 by using a high-strength adhesive.

(2) The one-dimensional phononic crystal vibration reduction layer 3 is fixedly bonded on two sides of the layered phononic crystal structure 2 through a high-strength adhesive; meanwhile, a concave threaded hole is processed in the center of the outer surface of the one-dimensional phononic crystal vibration damping layer 3 and is fixedly connected with the transverse vibration transmission rod 4 which is processed with a convex thread through rotation.

(3) The bolt rod with the hole 5 has a screw hole processed on one side and a convex thread on the other side, wherein the convex thread end is fixedly connected with the screw hole end of the vibration transmission connecting rod 4 through rotation.

(4) Particle dampers 8 are placed in the crank connecting rod cavity 9 and the rectangular section cavity 10 in advance, and the number of the particle dampers 8 is half of the volume. Meanwhile, threaded holes are formed in the two ends of the rectangular section cavity 10 and are fixedly connected with threads formed in the rod end of the crank connecting rod cavity 9 in a rotating mode.

(5) Protruding type screw thread has all been processed at the pole both ends of vertical vibration transmission pole 7, and the bottom screw thread passes through rotatory fixed connection with the cavity screw hole of crank connecting rod cavity 9, and the top screw thread is rotatory to passing through fastening nut 6 fixed connection in the screw of foraminiferous shank of bolt 5. The whole structure is symmetrical left and right, and the installation and connection modes of the components at the two sides are consistent. And finishing the installation and application of the integral structure.

Further, in order to ensure that the layered phononic crystal structure 2 and the one-dimensional phononic crystal damping layer 3 are tightly adhered to the steel rail body, the external force applied to the rectangular periodic phononic crystal structure 3 can be adjusted by rotating the transverse vibration transmission rod 4 after the device is installed, so that the stability of the structure is ensured.

The working mechanism of the adjustable quasi-periodic damping steel rail based on the phononic crystal and particle damper is described as follows: when a train runs at a high speed, the contact of wheels and the steel rail body 1 can cause violent vibration and bring primary radiation noise, and when the vibration is transmitted to a lower track structure and the periphery from the steel rail body, because low and medium frequency band gaps exist in the layered phononic crystal structure body 2 and the one-dimensional phononic crystal vibration reduction layer 3, elastic waves with corresponding frequencies cannot be transmitted, and the vibration is attenuated; and then the transverse vibration connecting rod 4 and the vertical vibration transmission rod 7 transmit the vibration to the crank connecting rod cavity 9 and the rectangular section cavity 10, and the vibration can cause the particle damper 8 to enter an active jumping state, so that collision and friction occur between adjacent particles, the vibration energy is dissipated, and the transmission of elastic waves in a low-medium frequency domain is further reduced. Through introducing phononic crystal and particle damper to the rail transit vibration source vibration attenuation and noise reduction field, elastic wave control in the rail structure is realized, thereby achieving the effects of vibration isolation and noise reduction.

The invention considers the following factors according to the practical situation in the using process:

(1) the laying length of the layered phononic crystal structure. The invention is suitable for different types of track structures, and the layered phononic crystal structure bodies with corresponding lengths are arranged on the rail web of the steel rail body according to the requirement of the line vibration reduction distance.

(2) The number of the one-dimensional phonon crystal vibration reduction layer, the crank connecting rod cavity and the rectangular section cavity. In the required line vibration reduction length range, a one-dimensional phononic crystal vibration reduction layer, a crank connecting rod cavity and a rectangular section cavity can be installed at equal intervals according to the form and the size of the track structure, so that the continuous vibration reduction effect is realized.

(3) The number of cycles of the layered phononic crystal structure body and the one-dimensional phononic crystal damping layer and the thickness of the material layer. The periodicity of the two types of phononic crystal structures and the thickness of the ABCD material layer can be adjusted according to the vibration reduction frequency band range of engineering requirements.

The above-listed detailed description is only a specific description of a possible embodiment of the present invention, and they are not intended to limit the scope of the present invention, and equivalent embodiments or modifications made without departing from the technical spirit of the present invention should be included in the scope of the present invention.