CN117910276B - Method for controlling radiation noise of long floating plate - Google Patents
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Abstract
The invention discloses a method for controlling radiation noise of a long floating plate, which relates to the technical field of radiation noise control of the long floating plate and comprises the following steps: s1, testing to obtain the main frequency of long floating plate noise; s2, analyzing the mode of the long floating plate, and finding out a vibration mode diagram and a vibration-reference mode quality corresponding to the main frequency of the noise of the long floating plate; s3, setting TMD at the positions of the wave crest and the wave trough of the vibration mode through a vibration mode diagram; s4, repeatedly iterating the parameters of the TMD through the vehicle-track-TMD coupling dynamics analysis model until the vibration reduction and noise reduction effects are met. According to the invention, a TMD-containing vehicle-track-TMD coupling dynamics analysis model is established, so that the control effect of the TMD on vibration noise is verified, and the arrangement form and the product parameters of the TMD are determined; the TMD structure of the tuned mass damper of the invention uses the damping sleeve to replace a spring structure in the prior art, uses vulcanized rubber, polyurethane and the like to replace damping fluid, and has simpler structure.
Description
Technical Field
The invention relates to the technical field of long floating plate radiation noise control, in particular to a method for controlling long floating plate radiation noise.
Background
Tuned Mass Dampers (TMDs) can better control vibration noise in rail transit, such as chinese patent application No. 2004800197071, a patent entitled rail tuned damper can better control rail vibration noise. The vibration and noise reduction principle of the TMD is shown in fig. 1, and a set of mass, spring and damping system is added on a main system (a general object to be subjected to vibration and noise reduction), so that the maximum resonance point of the original system at the resonance frequency (the position with the tuning ratio of 1) is changed into two smaller resonance points, and the vibration and noise reduction effect is achieved.
Conventional TMD is used for track slab vibration control, and no control method for forming a system is limited to application. In addition, conventional TMD product parameters and frequencies are often in the form of multiple attempts, and do not form a complete set of theoretical methods. The mass selection of the main system in the conventional TMD design is usually the mass of the track slab, and the mass should actually be the modal mass of the corresponding mode in the long floating slab modal analysis. The conventional TMD is arranged randomly, and further researches show that a long floating slab track (usually 25 meters in length) has vibration noise with low frequency of 63Hz ("long-long") when a metro vehicle passes, and the measured sound pressure spectrum characteristics are shown in fig. 2, so that a method for reducing noise of the vibration noise is not available at present.
Disclosure of Invention
The invention aims to provide a long floating plate radiation noise control method, which designs the arrangement position of a tuned mass damper and the tuned mass damper by actually measuring the noise characteristics of the long floating plate, the modal analysis of a track plate and the coupling dynamics analysis of a vehicle-track-tuned mass damper.
In order to achieve the above purpose, the present invention provides the following technical solutions:
A long floating plate radiation noise control method comprises the following steps:
S1, obtaining the main frequency of long floating plate noise through a long floating plate noise characteristic test;
S2, analyzing the mode of the long floating plate, and finding out a vibration mode diagram and a vibration-reference mode quality corresponding to the main frequency of the noise of the long floating plate;
S3, setting the TMD of the tuning mass damper at the positions of the wave crest and the wave trough of the vibration mode through a vibration mode diagram;
s4, repeatedly and iteratively tuning parameters of the TMD through the vehicle-track-TMD coupling dynamics analysis model until vibration reduction and noise reduction effects are met.
Preferably, the parameters of the tuned mass damper TMD include the mass, spring rate and damping coefficient of the tuned mass damper TMD.
Preferably, the parameter setting of the tuned mass damper TMD includes the following calculation expression:
tuning mass damper TMD mass ratio:
（1）；
Tuning mass damper TMD best natural frequency:
（2）；
Tuning mass damper TMD optimal damping ratio:
（3）；
In the method, in the process of the invention, The mass ratio of TMD to the main system; /(I)Is the mass of the TMD mass block; /(I)The quality of the main system; /(I)The best natural frequency for TMD; /(I)Is the resonant frequency of the main system; /(I)Is the TMD optimal damping ratio.
Preferably, the vehicle-track-TMD coupling dynamics analysis model is composed of a vehicle subsystem, a track subsystem and a wheel-track subsystem.
Preferably, the tuned mass damper TMD is disposed on a floating plate, the tuned mass damper TMD includes a mass block, and a spring and a damper are disposed in parallel between the floating plate and the mass block.
Preferably, the damper comprises a damping outer sleeve and a damping inner sleeve arranged in the damping outer sleeve, damping glue is filled between the damping inner sleeve and the damping outer sleeve, the damping inner sleeve is of a spline shaft structure, and the damping outer sleeve is of a spline sleeve structure.
Preferably, the damping rubber is one of vulcanized rubber, polyurethane or solid damping rubber, and the outer wall of the damping inner sleeve and the damping outer sleeve are glued through the damping rubber.
Compared with the prior art, the invention has the following beneficial effects:
according to the invention, a vehicle-track-TMD coupling dynamics analysis model containing the tuned mass damper TMD is established, the control effect of the TMD on vibration noise is verified, and then the arrangement form and the product parameters of the tuned mass damper TMD are determined.
The TMD structure of the tuned mass damper provided by the invention utilizes the damping sleeve to replace a spring structure in the prior art, and utilizes vulcanized rubber, polyurethane or solid damping rubber to replace damping liquid, so that the structure is simpler, the installation is convenient and quick, and the service life is longer.
Drawings
FIG. 1 is a schematic diagram of TMD vibration damping and noise reduction principles;
FIG. 2 is a diagram illustrating the spectrum of the low frequency vibration noise of the long floating plate according to the present invention;
FIG. 3 is a schematic diagram of a TMD structure of a tuned mass damper of the present invention;
FIG. 4 is a schematic illustration of a cross-sectional A-A configuration of a tuned mass damper TMD of the present invention;
FIG. 5 is a schematic flow chart of the embodiment of the present invention;
FIG. 6 is a schematic diagram of a long floating plate mode analysis 63.5Hz vibration mode according to the present invention;
FIG. 7 is a schematic diagram of the placement of a tuned mass damper TMD of the present invention on a long floating plate;
FIG. 8 is a graph of a vehicle-rail-TMD coupling dynamics analysis model in accordance with an embodiment of the present invention;
FIG. 9 is a schematic diagram showing the comparison of sound pressure levels obtained by coupling analysis according to an embodiment of the present invention;
fig. 10 is a schematic diagram of a TMD vibration spectrum of a tuned mass damper according to an embodiment of the present invention.
The figure shows:
1. the mass block, 2, the spring, 3, the damping inner sleeve, 4, the damping outer sleeve, 5, the floating plate;
11. secondary suspension, 12, framework, 13, primary suspension, 14, wheel set, 15, steel rail, 16, fastener, 18, spring vibration isolator, 19, TMD,20, shear hinge, 21, foundation, 22 and CA mortar layer.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention; all other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Example 1
Referring to fig. 1 and 5, the present invention provides a method for controlling radiation noise of a long floating plate, comprising the following steps:
s1, obtaining the main frequency of long floating plate noise through a long floating plate noise characteristic test; as shown in FIG. 2, the long floating plate with a length of 25 meters has a noise of 63Hz
S2, building a solid (or plate shell) model of the long floating plate by using finite element analysis software, setting material parameters, analysis frequency range and the like of the long floating plate, and carrying out modal analysis on the long floating plate, as shown in FIG. 6, finding a vibration pattern diagram and a vibration-reference modal mass corresponding to the noise main frequency (63 Hz) of the long floating plate; the obtained vibration pattern diagram is used as a reference diagram of the TMD arrangement of the tuned mass damper, and the reference vibration mode mass is used as a reference mass of the TMD mass of the tuned mass damper. The mass, stiffness and damping parameters of the tuned mass damper TMD are obtained by the following calculation expression:
tuning mass damper TMD mass ratio:
（1）；
Tuning mass damper TMD best natural frequency:
（2）；
Tuning mass damper TMD optimal damping ratio:
（3）；
In the method, in the process of the invention, The mass ratio of TMD to the main system; /(I)Is the mass of the TMD mass block; /(I)The quality of the main system; /(I)The best natural frequency for TMD; /(I)Is the resonant frequency of the main system; /(I)Is the TMD optimal damping ratio.
S3, setting the tuning mass damper TMD at the positions of the peaks and the troughs of the vibration mode through the vibration mode diagram so as to achieve the maximum vibration and noise reduction effect, as shown in FIG. 7.
S4, repeatedly and iteratively tuning parameters of the mass damper TMD through a vehicle-track-TMD coupling dynamics analysis model, wherein the vehicle-track-TMD coupling dynamics analysis model is composed of a vehicle subsystem, a track subsystem and a wheel-track subsystem as shown in fig. 8.
The vehicle subsystem establishes a train space three-dimensional dynamics model by adopting a multi-rigid-body dynamics theory; the model considers the nonlinear characteristics of rigidity and damping of the primary suspension 13 and the secondary suspension 11 of the vehicle, and nonlinear characteristics of a transverse stop, an anti-rolling torsion bar, an anti-snake-shaped shock absorber and the like of the vehicle. The equation of motion for each degree of freedom of the vehicle is represented by a matrix:
；
In the method, in the process of the invention, A mass matrix of the vehicle; /(I)Damping matrix of vehicle; /(I)A stiffness matrix of the vehicle; /(I)Dynamic load matrix for use on a vehicle system,/>For displacement matrix of vehicle,/>Is the velocity matrix of the vehicle,/>Is an acceleration matrix of the vehicle.
The track subsystem consists of steel rails 15, WTMD, fasteners 16, floating plates 5, spring isolators 18, foundations 21, CA mortar layers 22 and the like. The floating plate 5 is considered to be a flexible body, and the elastic elements such as the fastener 16, the spring vibration isolator 18, the TMD19, etc. are replaced with spring damping units. Wherein the fastener 16 is simulated using a spring-damper unit. The spring vibration isolator 18 employs a nonlinear spring force element simulation. The CA mortar layer 22 is simulated by uniformly distributed spring-damper units. The TMD19 was modeled using a mass, spring-damped vibration system. The frame 12 is used to connect the vehicle body, the wheel set 14 and the suspension system. The wheel set 14 is used to support the entire frame 12, the weight of the vehicle body, and to transfer wheel rail forces from the vehicle body to the rail. The shear hinge 20 serves to connect two adjacent floating plates and transfer shear forces between the floating plates. The steel rail 15 adopts a 3D numerical iron-wood sinkoff beam model. The track slab system is established by finite elements, and according to a mode synthesis method, the undamped dynamic equation is as follows:
；
In the method, in the process of the invention, For node displacement inside the structure,/>Is the displacement of the node at the interface,/>Is an internal force array at the boundary,/>、/>Are all mass matrices of the track system,/>Are all the rigidity of the track system,/>Acceleration matrix for internal nodes of structure,/>Is an acceleration matrix of the node at the interface.
Wherein, the node displacement is:
；
wherein, Is a modal matrix,/>Is the modal coordinates,/>Is a main mode matrix of a fixed interface,/>To constrain the modal matrix,/>Is the modal coordinates of the node at the interface,/>Is the modal coordinates of the internal node.
Eigenvalue analysis is performed by the following formula:
；
In the method, in the process of the invention, ；/>，/>For structural frequency,/>Is a rigidity matrix,/>Is a quality matrix,/>For regularized matrix,/>Is a modal matrix.
Orthogonalization mode matrix is obtained through regularization and transformation matrix:
；
In the method, in the process of the invention, The mode matrix is T, and the transformation matrix is T;
the damping matrix is given by the modal damping ratio, and the same or different damping ratios are given to each order of modes, so that the damping matrix is introduced into a non-damping kinetic equation:
；
The kinetic equation for the flexible body is:
；
wherein,
；
；
F；
；
Damping ratio of nth order mode,/>Is the nth order frequency of the structure, F is a moment array,/>Is a modal matrix,/>Is a displacement matrix,/>Is a generalized force matrix,/>Is a generalized quality matrix,/>Is a generalized damping matrix,/>Is a generalized stiffness matrix,/>Is a generalized modal displacement matrix,/>Is a first order derivative matrix of generalized modeIs a generalized modal second derivative matrix.
The vehicle subsystem and the floating slab track subsystem can be linked by the interaction relationship of the wheel track, and the wheel track effect can be replaced by the tangential force and the normal force of the wheel track. The wheel-rail contact adopts a multipoint non-Hertz contact model, and the calculation expression of the resultant force of the normal contact force is as follows:
；
Wherein N is the resultant force of normal force, p (x, y) is the distribution function of normal contact pressure, E is the elastic modulus, Is Poisson's ratio,/>For virtual penetration, x l is the contact patch area edge coordinates, and y l、yr is the contact patch left and right edge distances, respectively.
The multipoint non-hertz contact model calculates the Kalker linear coefficient of each contact patch by using the equivalent ellipse of each contact patch to obtain the compliance coefficient on each contact patch:
，/>，/>；
In the method, in the process of the invention, 、/>、/>Compliance coefficients in longitudinal, transverse, spin directions respectively,/>、/>、/>Kalker coefficients in longitudinal, transverse, spin directions, G is shear modulus,/>For the contact area of the ith contact spot, x li (y) is the ith contact spot area edge coordinate, and y li、yri is the ith contact spot left and right edge distances, respectively.
And then FASTSIM, solving the tangential force of the wheel track, iterating the parameters of TMD in the model for a plurality of times until the designed vibration reduction and noise reduction effect requirements can be met, wherein the sound pressure level example obtained by coupling analysis is shown in fig. 9, and the total sound pressure level of the radiation noise of the floating plate with TMD is reduced by about 3.83dB.
Example 2
As shown in fig. 3-4, the tuned mass damper TMD is placed on the floating plate 5, the tuned mass damper TMD includes the mass 1, and the spring 2 and the damper are arranged in parallel between the floating plate 5 and the mass 1. The mass block 1 is provided with an inner blind hole mounting seat, one end of the spring 2 is placed on the upper surface of the floating plate 5, the other end of the spring is fixed in the inner blind hole mounting seat of the mass block 1, one end of the damper is placed on the upper surface of the floating plate 5, and the other end of the damper is fixed in the inner blind hole mounting seat of the mass block 1.
The damper comprises a damping outer sleeve 4 and a damping inner sleeve 3 arranged in the damping outer sleeve 4, damping glue is filled between the damping inner sleeve 3 and the damping outer sleeve 4, the damping inner sleeve 3 is of a spline shaft structure, the damping outer sleeve 4 is of a spline sleeve structure, and the damping inner sleeve 3 can vertically displace in the damping outer sleeve 4. One end of the damping inner sleeve 3 is fixedly arranged in an inner blind hole mounting seat of the mass block 1, the lower end of the damping outer sleeve 4 is placed on the upper end face of the floating plate 5, and the outer wall of the damping inner sleeve 3 and the damping outer sleeve 4 are glued through damping glue.
The damping rubber is one of vulcanized rubber, polyurethane or solid damping rubber, and aims to increase the attachment area between the damping rubber and the damping inner sleeve 3 and the damping outer sleeve 4, exert the shearing energy consumption function of the damping rubber to the maximum extent, absorb the vibration energy of the floating plate 5 and play a role in vibration reduction to the maximum extent. The TMD of the tuned mass damper is simple in structure, convenient to install and use, capable of being directly placed on the floating plate 5, free of installation, convenient to replace and low in maintenance cost.
By tapping the tuned mass damper TMD, the spectrum of the tapping test is shown in FIG. 10. As can be seen from FIG. 10, the tuned mass damper TMD of the present invention has a resonance peak value of about 63Hz, which indicates that the tuned mass damper TMD of the present invention can reduce 63Hz noise, and the noise test is performed after the TMD is installed on site, so that the TMD meets the engineering design requirements.
Claims (7)
1. A method for controlling radiation noise of a long floating plate, comprising the steps of:
S1, obtaining the main frequency of long floating plate noise through a long floating plate noise characteristic test;
S2, analyzing the mode of the long floating plate, and finding out a vibration mode diagram and a vibration-reference mode quality corresponding to the main frequency of the noise of the long floating plate;
S3, setting the TMD of the tuning mass damper at the positions of the wave crest and the wave trough of the vibration mode through a vibration mode diagram;
S4, repeatedly and iteratively tuning parameters of the TMD through a vehicle-track-TMD coupling dynamics analysis model until vibration reduction and noise reduction effects are met;
The vehicle-track-TMD coupling dynamics analysis model consists of a vehicle subsystem, a track subsystem and a wheel-track subsystem;
The vehicle subsystem establishes a train space three-dimensional dynamics model by adopting a multi-rigid-body dynamics theory; taking into account the nonlinear characteristics of the rigidity and damping of a primary suspension (13) and a secondary suspension (11) of the vehicle and the nonlinear characteristics of a transverse stop, an anti-rolling torsion bar and an anti-snake-shaped shock absorber of the vehicle in a model; the equation of motion for each degree of freedom of the vehicle is represented by a matrix:
；
In the method, in the process of the invention, Is a mass matrix of the vehicle; /(I)Is a damping matrix of the vehicle; /(I)Is a stiffness matrix of the vehicle; /(I)Dynamic load matrix for use on a vehicle system,/>For displacement matrix of vehicle,/>Is the velocity matrix of the vehicle,/>An acceleration matrix for the vehicle;
The track subsystem consists of steel rails (15), WTMD, fasteners (16), floating plates (5), spring vibration isolators (18), a foundation (21) and a CA mortar layer (22); the floating plate (5) is considered to be a flexible body, and the fastener (16), the spring vibration isolator (18) and the TMD (19) elastic element are replaced by a spring damping unit; wherein the fastener (16) is simulated using a spring-damper unit; the spring vibration isolator (18) adopts nonlinear spring force element simulation; the CA mortar layer (22) is simulated by uniformly distributed spring-damping units; the TMD (19) is simulated by adopting a mass, spring and damping vibration system; the framework (12) is used for connecting a vehicle body, a wheel set (14) and a suspension system; the wheel set (14) is used for supporting the whole framework (12), the weight of the vehicle body and transmitting wheel rail force from the vehicle body to the rail; the shear hinge (20) is used for connecting two adjacent floating plates and transmitting shear force between the floating plates; the steel rail (15) adopts a 3D numerical iron-wood sinkoff beam model; the track slab system is established by finite elements, and according to a mode synthesis method, the undamped dynamic equation is as follows:
；
In the method, in the process of the invention, For node displacement inside the structure,/>Is the displacement of the node at the interface,/>Is an internal force array at the boundary,、/>Are all mass matrices of the track system,/>Are all the rigidity of the track system,/>Acceleration matrix for internal nodes of structure,/>An acceleration matrix for the node at the interface;
Wherein, the node displacement is:
；
wherein, Is a modal matrix,/>Is the modal coordinates,/>Is a main mode matrix of a fixed interface,/>To constrain the modal matrix,/>Is the modal coordinates of the node at the interface,/>Modal coordinates for the internal node;
Eigenvalue analysis is performed by the following formula:
；
In the method, in the process of the invention, ；/>，/>For structural frequency,/>Is a rigidity matrix,/>Is a quality matrix,/>For regularized matrix,/>Is a modal matrix;
Orthogonalization mode matrix is obtained through regularization and transformation matrix:
；
In the method, in the process of the invention, The mode matrix is T, and the transformation matrix is T;
the damping matrix is given by the modal damping ratio, and the same or different damping ratios are given to each order of modes, so that the damping matrix is introduced into a non-damping kinetic equation:
；
The kinetic equation for the flexible body is:
；
wherein,
；
；
F；
；
Damping ratio of nth order mode,/>Is the nth order frequency of the structure, F is a moment array,/>Is a modal matrix,/>Is a displacement matrix,/>Is a generalized force matrix,/>Is a generalized quality matrix,/>Is a generalized damping matrix,/>In the form of a generalized stiffness matrix,Is a generalized modal displacement matrix,/>Is a first order derivative matrix of generalized modeIs a generalized modal second derivative matrix;
The vehicle subsystem and the floating slab track subsystem can be connected through the interaction relation of the wheel track, and the wheel track effect can be replaced by the tangential force and the normal force of the wheel track; the wheel-rail contact adopts a multipoint non-Hertz contact model, and the calculation expression of the resultant force of the normal contact force is as follows:
；
Wherein N is the resultant force of normal force, p (x, y) is the distribution function of normal contact pressure, E is the elastic modulus, Is Poisson's ratio,/>Is virtual penetration quantity,/>For contact patch area edge coordinates,/>、/>The left and right edge distances of the contact spots are respectively;
the multipoint non-hertz contact model calculates the Kalker linear coefficient of each contact patch by using the equivalent ellipse of each contact patch to obtain the compliance coefficient on each contact patch:
，/>，/>；
In the method, in the process of the invention, 、/>、/>Compliance coefficients in longitudinal, transverse, spin directions respectively,/>、/>、/>Kalker coefficients in longitudinal, transverse, spin directions, G is shear modulus,/>For/>The contact area of each contact spot, x li (y) is the/>Edge coordinates of the individual contact patch areas,/>、/>Respectively is/>Left and right edge distances of the contact spots;
And then FASTSIM, solving the tangential force of the wheel track, and iterating the parameters of TMD in the model for a plurality of times until the designed vibration reduction and noise reduction effect requirements can be met.
2. A method of long floating plate radiated noise control according to claim 1, wherein the parameters of the tuned mass damper TMD include the mass, spring rate and damping coefficient of the tuned mass damper TMD.
3. The method of claim 1, wherein the parameter setting of the tuned mass damper TMD comprises the following calculation expression:
tuning mass damper TMD mass ratio:
（1）；
Tuning mass damper TMD best natural frequency:
（2）；
Tuning mass damper TMD optimal damping ratio:
（3）；
In the method, in the process of the invention, The mass ratio of TMD to the main system; /(I)Is the mass of the TMD mass block; /(I)The quality of the main system; the best natural frequency for TMD; /(I) Is the resonant frequency of the main system; /(I)Is the TMD optimal damping ratio.
4. The method of claim 1, wherein the vehicle-track-TMD coupling dynamics analysis model is comprised of a vehicle subsystem, a track subsystem, and a wheel-track subsystem.
5. A long floating plate radiation noise control method according to any one of claims 1-4, characterized in that the tuned mass damper TMD is arranged on the floating plate (5), the tuned mass damper TMD comprises a mass block (1), and a spring (2) and a damper are arranged in parallel between the floating plate (5) and the mass block (1).
6. The method for controlling radiation noise of the long floating plate according to claim 5, wherein the damper comprises a damping outer sleeve (4) and a damping inner sleeve (3) arranged in the damping outer sleeve (4), damping glue is filled between the damping inner sleeve (3) and the damping outer sleeve (4), the damping inner sleeve (3) is of a spline shaft structure, and the damping outer sleeve (4) is of a spline sleeve structure.
7. The method for controlling radiation noise of the long floating slab according to claim 6, wherein the damping rubber is one of vulcanized rubber, polyurethane or solid damping rubber, and the outer wall of the damping inner sleeve (3) and the damping outer sleeve (4) are glued through the damping rubber.
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| CN105887585A (en) * | 2016-04-11 | 2016-08-24 | 西南交通大学 | Vibration isolator in floating slab track system and method for determining operating parameters of vibration isolator |
| RU2016109829A (en) * | 2016-03-18 | 2017-09-21 | Мария Михайловна Стареева | SPRING EQUIPMENT VIBRATION ISOLATOR |
| CN113047092A (en) * | 2021-03-29 | 2021-06-29 | 中铁第一勘察设计院集团有限公司 | Electromagnetic variable-rigidity self-adjusting steel spring floating slab track system and vibration isolator |
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