CN210668062U - Constraint damping composite noise reduction structure applied to inner wall of transformer oil tank - Google Patents

Constraint damping composite noise reduction structure applied to inner wall of transformer oil tank Download PDF

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CN210668062U
CN210668062U CN201921797196.6U CN201921797196U CN210668062U CN 210668062 U CN210668062 U CN 210668062U CN 201921797196 U CN201921797196 U CN 201921797196U CN 210668062 U CN210668062 U CN 210668062U
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surface course
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incident surface
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杨晓丰
莫国华
胡恩德
闵鹤群
曹枚根
王博
沈翀
徐建锋
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Shaoxing Jianyuan Electric Power Group Co Ltd Daxing Electric Power Loading Branch
Shaoxing Power Supply Co of State Grid Zhejiang Electric Power Co Ltd
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Shaoxing Jianyuan Electric Power Group Co Ltd Daxing Electric Power Loading Branch
Shaoxing Power Supply Co of State Grid Zhejiang Electric Power Co Ltd
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Abstract

The utility model discloses a be applied to compound structure of making an uproar of falling of restraint damping of transformer tank inner wall, its structure includes incident surface course, transmission surface course and is located the damping layer between incident surface course and the transmission surface course, incident surface course and transmission surface course adopt not magnetic conductive metal material to make, the damping layer is viscoelastic material, incident surface course and transmission surface course and damping layer bonding together form the compound sound insulation structure of restraint damping. The utility model discloses a metal decking and the adhesive mode of elastic damping layer have good sound insulation effect in the wide frequency range of well low frequency, and this composite sheet structure steadiness is better, and can adapt to grease proofing , antimagnetic interference's transformer damping noise reduction environment, simple to operate, the durability is good.

Description

Constraint damping composite noise reduction structure applied to inner wall of transformer oil tank
Technical Field
The utility model belongs to the power transformer field, concretely relates to be applied to compound sound insulation structure of restraint damping of power transformer oil tank inner wall and performance prediction method, structural design method thereof.
Background
The noise source of the transformer is the iron core vibration caused by magnetostriction of the silicon steel sheets of the iron core caused by internal electromagnetic force, and the vibration is transmitted to the wall body of the oil tank through insulating oil and then radiated to the surrounding air environment through the wall surface of the tank body. At present, measures for controlling noise radiation of a transformer oil tank can be divided into two aspects of oil tank structure optimization and propagation path control, for example, the strength of the oil tank is increased by adding densely distributed ribs on the wall surface of the oil tank, and the amplitude of the wall surface of the tank body is reduced; and a sound insulation plate is added outside the oil tank, and measures such as a sound insulation cover are arranged to control the transmission path of the noise. The radiation noise of the transformer oil tank is mainly low-frequency noise and harmonic waves thereof, and most of the existing noise reduction measures have the problems of poor adaptability and insignificant control effect when the existing noise reduction measures are used for different actual working conditions.
The constrained damping composite sound insulation structure has the characteristics of small thickness, high damping ratio, large insertion loss and the like, has better sound insulation performance on low-frequency noise compared with other single-layer sound insulation structures, is one of the front development directions of sound insulation material optimization, and has wide application prospect. The multilayer composite damping plate is researched by LanliFang (LanliFang. multilayer damping composite structure vibration and acoustic radiation analysis [ D ]. Hunan university, 2012.) and the acoustic radiation rule of the multilayer composite damping plate is analyzed, and the result shows that the outer layer damping material has great influence on the structural vibration, and when the elastic modulus of the outer layer damping material is improved or the damping material with the large elastic modulus is arranged on the outer layer, the structural rigidity and the energy consumption capacity of the system are obviously improved. The method is characterized in that a bending vibration and boundary conditions of the viscoelastic composite plate are simplified by using an equivalent stiffness, an equivalent mass and an equivalent Poisson's ratio method aiming at the rectangular elastic-viscoelastic composite plate under the action of underwater sound, and the influence of material parameters in the composite plate on the vibration is analyzed based on the method. However, the existing research is less related to the research of an acoustic model of the viscoelastic material in the constrained damping composite structure, and the influence of the viscoelastic material on the sound insulation performance of the constrained damping composite structure and a performance prediction method of the structure are not clear.
CN201510137073 discloses a composite damping plate based on a reclaimed rubber matrix and a manufacturing method thereof, comprising a bottom layer and a damping layer. The damping layer adopts the modified regenerated rubber, comprehensively utilizes the high sound insulation effect of the steel plate, and utilizes the modified regenerated rubber material to form a large damping constraint structure layer to inhibit the performance of the steel plate easy to resonate, so that the noise energy penetrating through the sound insulation plate is reduced by more than 90%. CN201510595697 discloses a compound sound insulation board of viscoelasticity, including damping layer, sound insulating layer and the acoustic absorption layer that sets gradually, one side on damping layer is laminated mutually with the casing surface of the underwater motion body, and the damping layer adopts isotropic polyurethane or polymer resin preparation, and the sound insulating layer adopts polyolefin elastomer or glass fiber preparation, and the acoustic absorption layer adopts photosensitive resin preparation, the inside array of acoustic absorption layer is provided with closed cavity, and whole compound sound insulation board wholly has certain mechanical strength and adjusts multilayer structure's sound insulating ability at low-intermediate frequency range simultaneously. CN201710907565 discloses a low-noise power capacitor based on damping steel plates, wherein damping materials are arranged between an outer steel plate and an inner steel plate to form a three-layer closed cavity structure, and the closed cavity formed by welding the damping steel plates is utilized to insulate a frequency band mainly contributing to noise.
SUMMERY OF THE UTILITY MODEL
The utility model aims to solve the technical problem that a restraint damping composite noise reduction structure applied to the inner wall of a transformer oil tank is provided, a good sound insulation effect is achieved in a wide frequency range of middle and low frequency, and a difficult problem of poor low-frequency sound insulation performance of a light and thin structure is solved.
In order to solve the technical problem, the utility model adopts the following technical scheme: the utility model provides a be applied to compound structure of making an uproar of falling of restraint damping of transformer tank inner wall, installs in transformer tank inner wall, includes incident surface course, transmission surface course and is located the damping layer between incident surface course and the transmission surface course, incident surface course and transmission surface course adopt not magnetic conductive metal material to make, the damping layer is viscoelastic material, incident surface course and transmission surface course and damping layer bonding are in the same place, form the compound sound insulation structure of restraint damping.
Optionally, the incident surface layer and the transmission surface layer are aluminum plates.
Optionally, the damping layer is a butyl rubber viscoelastic tape.
Optionally, the thickness of the incident surface layer is 1.0mm, the thickness of the transmission surface layer is 1.5mm, and the thickness of the damping layer is 0.8 mm.
Optionally, a sandwich surface layer is arranged between the incident surface layer and the transmission surface layer, the sandwich surface layer is an aluminum plate, and damping layers are arranged between the sandwich surface layer and the incident surface layer as well as between the sandwich surface layer and the transmission surface layer.
Optionally, the incident surface layer is a 3mm thick aluminum plate, the transmission surface layer is a 6mm thick aluminum plate, the sandwich surface layer is a 1mm thick aluminum plate, and the damping layer is a 1mm thick butyl rubber viscoelastic adhesive tape.
The utility model discloses a metal decking and the adhesive mode of elastic damping layer have good sound insulation effect in the wide frequency range of well low frequency, specifically solved following three point problem:
(1) compared with a single-layer sound insulation plate structure, the viscoelastic constraint damping layer is added, the damping layer is similar to glue to closely adhere the sound incidence plate and the transmission plate, the sound insulation valley caused by the mass law is effectively avoided, and the problem of poor low-frequency sound insulation performance of a light and thin structure is solved;
(2) the rationality of the physical performance and the price of the damping layer material is fully considered when the damping layer material is selected, and the feasibility of large-scale popularization and application is better;
(3) the composite board has good structural stability, can adapt to the transformer vibration reduction and noise reduction environment with oil resistance and anti-magnetic interference, is convenient to mount, and has good durability.
The specific technical solution and the advantages of the present invention will be described in detail in the following embodiments.
Drawings
The invention will be further described with reference to the accompanying drawings and specific embodiments:
fig. 1 is a schematic view of a constrained damping composite sound insulation structure in a first embodiment of the present invention;
FIG. 2 is a graph showing the change of storage modulus and loss modulus with frequency of a damping layer of a type-selected damping structure of the present invention, which is a 3M-830 type adhesive tape;
FIG. 3 is a graph showing the storage modulus, loss modulus and loss factor of a butyl rubber viscoelastic adhesive tape used as a damping layer for a type selection of a constrained damping composite sound insulation structure according to the present invention;
FIG. 4 is a schematic diagram of a two-dimensional model of a constrained damping composite sound insulation structure for finite element simulation based on an impedance tube method;
FIG. 5 is a comparison graph of TL curve, incident plate RDA curve and transmission plate RDA curve of the constrained damping composite sound insulation structure type I of the present invention;
FIG. 6 is a comparison diagram of the displacement phase of the incident plate and the transmission plate of the type I of the constrained damping composite sound insulation structure of the present invention;
FIG. 7 is a comparison graph of TL curve, incident plate RDA curve and transmission plate RDA curve of the constrained damping composite sound insulation structure type II of the present invention;
FIG. 8 is a comparison diagram of the displacement phase of the incident plate and the transmission plate of the type II of the constrained damping composite sound insulation structure of the present invention;
fig. 9 is a schematic view of a constrained damping composite sound insulation structure in a first embodiment of the present invention;
FIG. 10 is a comparison graph of experimental measurement and numerical simulation of the sound insulation amount of the type II of the constrained damping composite sound insulation structure of the present invention;
FIG. 11 is a TL curve diagram of a design example of the constrained damping composite sound insulation structure at 0-1000 Hz.
Detailed Description
The technical solutions of the embodiments of the present invention are explained and illustrated below, but the following embodiments are only preferred embodiments of the present invention, and not all embodiments. Based on the embodiments in the embodiment, other embodiments obtained by those skilled in the art without any creative work belong to the protection scope of the present invention.
The prior art and design of vibration reduction and noise reduction of the transformer oil tank do not find reports that a constraint damping sound insulation composite structure based on the constitutive relation and the sound insulation characteristic of a viscoelastic material is applied to the inner wall of the transformer oil tank.
Therefore, referring to fig. 1, the utility model provides a restraint damping sound insulation composite construction based on viscoelastic material's constitutive relation and sound insulation characteristic installs in transformer tank inner wall, include incident surface course 1, transmission surface course 3 and be located incident surface course and transmission surface course between damping layer 2, incident surface course and transmission surface course adopt not magnetic conductive metal material to make, the damping layer is viscoelastic material, incident surface course and transmission surface course and damping layer and bonding are in the same place, form the compound sound insulation construction of restraint damping.
The utility model also provides a performance prediction method of the constrained damping composite sound insulation structure, the performance is represented by the sound transmission loss TL, which is characterized in that the sound transmission loss TL is obtained by the formula 1,
Figure DEST_PATH_GDA0002460850170000051
in the formula: τ denotes an acoustic energy transmission coefficient of the composite panel (τ ═ Λ +2) (ii) a Λ represents the ratio of the transmitted sound pressure coefficient C to the incident sound pressure coefficient a, i.e., a ═ C/a;
the utility model relates to a performance prediction method of a constrained damping composite sound insulation structure, which is characterized in that an incident sound pressure coefficient A, a reflected sound pressure coefficient B and a transmitted sound pressure coefficient C are obtained by a formula 2,
Figure DEST_PATH_GDA0002460850170000052
in the formula: k is a radical ofx、kzThe components of the acoustic wave vectors in the x direction and the z direction are respectively infinite based on that the composite plate is in the xy direction of a plane rectangular coordinate system, the spaces on two sides are air media, the incident acoustic wave is a plane simple harmonic wave, the wave front perpendicular line is on the xz plane, and the included angle between the wave front perpendicular line and the z axis is thetan+1An assumption of (1) having kx＝k0sinθn+1、kz＝k0cosθn+1(ii) a Omega is the circular frequency of the incident sound wave; c. C0Is the speed of sound in air; i is an imaginary unit; h is the total thickness of the composite board
Figure DEST_PATH_GDA0002460850170000053
hjRepresents the thickness of each layer;
Figure DEST_PATH_GDA0002460850170000054
is a velocity potential function of the sound field, satisfying the helmholtz equation in the air sound field:
Figure DEST_PATH_GDA0002460850170000055
if the air particle velocity is recorded as
Figure DEST_PATH_GDA0002460850170000061
The sound pressure is denoted p, then
Figure DEST_PATH_GDA0002460850170000062
And p and
Figure DEST_PATH_GDA0002460850170000063
the relationship of (1) is:
Figure DEST_PATH_GDA0002460850170000064
if the air particle velocity and the sound pressure of the incident tube and the transmission tube are respectively distinguished by subscripts in and tr, the incident sound pressure coefficient A, the reflected sound pressure coefficient B, the transmitted sound pressure coefficient C and the transmitted sound pressure coefficient C can be obtained by substituting the formula 2-1 into the formula 4
Figure DEST_PATH_GDA0002460850170000065
Equation 2-2 for the p relationship:
Figure DEST_PATH_GDA0002460850170000066
Figure DEST_PATH_GDA0002460850170000067
Figure DEST_PATH_GDA0002460850170000068
Figure DEST_PATH_GDA0002460850170000069
the performance prediction method of the constrained damping composite sound insulation structure is characterized in that the recursion relation of the stress and the displacement distribution of each layer of the composite board is obtained by a formula 5,
Figure DEST_PATH_GDA00024608501700000610
in the formula: [ T ]]jCoefficient matrices determined for the geometrical and physical parameters of the elastic or viscoelastic layer of the j-th layer, for the viscoelastic layer, TijIs a plurality;
Figure DEST_PATH_GDA00024608501700000611
respectively representing displacement components of the j layer of the composite plate along the x direction and the z direction;
Figure DEST_PATH_GDA00024608501700000612
respectively representing the positive stress of the j layer of the composite board and the shear stress of the xy plane;
meanwhile, the vibration displacement u of any elastic and viscoelastic layer of the composite board under the action of a sound fieldx、uzThe relationship between the expansion wave and the shear wave potential function can be described by Navier equation:
Figure DEST_PATH_GDA00024608501700000613
in the formula:
Figure DEST_PATH_GDA00024608501700000614
and ψ represents the dilatational wave and shear wave potential functions, respectively, which satisfy the wave equation:
Figure DEST_PATH_GDA00024608501700000615
in the formula: c. CLjIs the velocity of longitudinal wave of material, cLj 2＝2(1-vj)Gj/((1-2vj)ρj)；cTjIs the material shear wave velocity, cTj 2＝Gj/ρj；GjFor shear modulus, for a viscoelastic material layer, the shear modulus is the complex modulus Gf＝G′f+tG″f＝G′j(1+tηj) Wherein ηjIs a loss factor; v. ofjIs the poisson ratio; rhoj(j ═ 1, 2, 3, 4.., n) is mass density;
according to an expression (formula 4) of sound field sound pressure and particle velocity, a formula 5 is continuously applied, and meanwhile, a reflected sound pressure coefficient B of an incident sound field is eliminated, so that a relation between a transmitted sound pressure coefficient C and an incident sound pressure coefficient A can be obtained, and a formula 1, namely a physical quantity, namely, a sound transmission loss TL, representing the sound insulation performance of the constrained damping composite sound insulation structure can be obtained.
The constants used in the present prediction method are shown in table 1:
table 1 table of constants required for prediction method
Figure DEST_PATH_GDA0002460850170000071
The utility model also provides a design method of utilizing performance prediction method to carry out compound sound insulation structure of restraint damping, including following step:
step 1, determining and obtaining a value of target sound transmission loss TL in a sound insulation frequency spectrum based on a transformer near-field noise actual measurement frequency spectrum;
step 2, selecting the types and thicknesses of the materials of the panel and the damping layer based on the specific requirements of the transformer, and determining the thickness h of each layer of the selected materialsjShear modulus Gj(the shear modulus of the viscoelastic material layer is the complex modulus Gj＝G′j+iG″j＝G′j(1+iηj) P. p), poisson's ratio vjMass density ρj(j ═ 1, 2, 3, 4.., n) and values of relevant physical parameters such as storage modulus E', energy consumption modulus E ″, loss factor η and relaxation time tau;
step 3, designing the material, thickness and layer number combined type selection of each composite layer in the constrained damping composite sound insulation structure based on a principle method that the more the number of the viscoelastic interlayers is, the more the TL frequency spectrum valley position moves towards high frequency;
step 4, verifying the performance of the type selection of the constrained damping composite sound insulation structure proposed in the step 3 by combining finite element numerical simulation and laboratory experiments with evidence based on a method for measuring the sound transmission loss of the member in the impedance tube in GB/Z22764 plus 2011, specifically, measuring the sound transmission loss of the member in the impedance tube by a four-microphone transmission matrix method, measuring the storage modulus and the loss modulus of the sample at the normal temperature within the range of 10-8 kHz by a dynamic thermal mechanical analysis method (DMA for short), thereby obtaining the loss factor and the relaxation time of the material, determining the relation between the relaxation time and the loss factor (η τ/w, wherein η is the loss factor, τ is the relaxation time, and ω is the angular frequency) based on the definition of a time-temperature equivalence principle and an elastic material K-V model, establishing a finite element model of the constrained damping composite structure in finite element software Comphysics, and further obtaining the linear average value of the sound pressure of four positions under two terminal impedances;
and 5, establishing a TL frequency spectrum curve, a Relative Displacement Amplitude (RDA) curve and a phase curve of the incident plate and the transmission plate of the constrained damping composite sound insulation structure according to the finite element simulation and laboratory test results in the step 4, and carrying out comparative analysis. If the TL value of the corresponding effective sound insulation frequency range can meet the target requirement, entering step 6; otherwise, repeating the step 3;
step 6, finally determining the material, thickness and layer number combined type selection of the constrained damping composite sound insulation structure based on a performance prediction method of the constrained damping composite sound insulation structure and by combining the related requirements of the specific use environment; determination of the shear modulus G of a MaterialjPoisson's ratio vjMass density ρjAnd physical parameters such as storage modulus E ', energy consumption modulus E', loss factor η, relaxation time tau and the like are final parameters of the structure, and the structure enters an actual installation and application stage.
Example one
According to the utility model, the specific use environment of the structure is combined, the following 3-point requirements are firstly determined, wherein ① application environment is the vibration and noise reduction design of the inner wall of the transformer oil tank, the constrained damping composite sound insulation structure is provided with oil resistance , antimagnetic interference, compression resistance and the like, the ② target sound insulation range is mainly low-frequency noise smaller than 1000Hz, and ③ can be fixed on the inner wall of the transformer oil tank in a bolt connection mode and the like.
According to the requirements, the surface layer is primarily selected to be an aluminum plate, the damping layer is a 3M-830 type viscoelastic adhesive tape and a butyl rubber viscoelastic adhesive tape which are respectively expressed by a type I and a type II, and two types of constraint damping composite sound insulation structures with the incident surface layer being 1.0mm thick, the transmission surface layer being 1.5mm thick and the damping interlayer being 0.8mm thick are designed. According to specific performance parameters of the 830 type viscoelastic adhesive tape shown by a 3M official website, fitting to obtain a curve (shown in figure 2) of storage modulus, loss modulus and frequency at 20 ℃; according to the time-temperature equivalent principle, a rotational rheometer (DHR for short) is adopted to measure the performance parameters of the butyl rubber viscoelastic adhesive tape, and the curves of the storage modulus, the loss factor, the relaxation time and the frequency are obtained by fitting (figure 3).
Based on a finite element numerical simulation method, a two-dimensional model of an impedance tube test is established for a 100mm x 100mm model I test sample (an x axis is set to be parallel to a tube direction, a y axis is perpendicular to the tube direction, structural boundary conditions are set as x axial freedom and y axial statically determinate, a sound field radiation condition is plane wave radiation, tube walls are all rigid surfaces, sound pressure is set to be 1Pa), and the relation between a TL curve and an RDA curve of the constrained damping composite sound insulation structure model I is contrastively analyzed (figure 4). The simulation results are shown in fig. 5 and 6, and show that: within the range of 0-1000Hz, the amplitude difference between the incident surface layer and the transmission surface layer is small, simultaneously, the RDA is increased along with the increase of the frequency, the RDA is increased from 15dB to 45dB, and the TL is increased from 1dB to 32 dB. The viscoelastic interlayer is similar to the adhesive of the incident plate and the transmission plate, so that the incident plate and the transmission plate of the selected type I are consistent in phase, and the incident plate and the transmission plate vibrate in phase. Finite element numerical simulation was also performed on type ii, with the same boundary conditions set as for type i above. The simulation results are shown in fig. 7 and 8, and show that: the whole DJD TL curve is smooth, a large sound insulation valley is formed at 360Hz, the TL curve of the DJD curve after 360Hz has the same trend with the mass law curve, TL increases along with the increase of frequency, the TL value of the type II before 360Hz is far larger than that of the mass law, and the sound insulation performance of the type II is better than that of the traditional method for improving the surface density or the thickness of the component; in a low frequency range less than 500Hz, the loss factor of the viscoelastic interlayer of the type II is very large, a good damping effect is achieved, and the sound insulation quantity of the type II is far larger than that under the mass law.
Based on GB/Z22764 and 2011' impedance tube method, the laboratory verification is carried out on 100mm × 100mm type II test samples, and compared with the numerical simulation result, the result shows that: a low valley exists between the numerical simulation result and the experimental measurement result between 300Hz and 400Hz, the positions of the two valleys have slight difference, the numerical simulation valley is at 360Hz, the experimental result valley is at 380Hz, and the deviation of the two is within a reasonable range. The numerically simulated sound insulation valley is about 26dB, the experimentally measured sound insulation valley is about 20dB, and the sound insulation quantity under the numerically simulated sound insulation valley is 6dB higher. But under 300Hz, namely a frequency band away from the sound insulation valley, the sound insulation quantity measured in the experiment is larger than the sound insulation quantity simulated by numerical value; whereas above 700Hz, the amount of sound insulation for numerical simulation is larger than that for experimental measurement (fig. 10).
By carrying out finite element numerical simulation and interactive verification of experimental measurement results on two types of constrained damping composite sound insulation structures, the results show that: the butyl rubber viscoelastic damping composite sound insulation structure has excellent sound insulation performance in a low-frequency range of 0-1000Hz, can meet a target effective sound insulation frequency spectrum range, and can be subjected to actual installation test and application.
Example two
The foundation the utility model provides a prediction method and design method of compound sound insulation structure of restraint damping provides one kind by 3 layers of aluminum plates, 2 layers of butyl rubber viscoelastic damping layer adhesive composite sheet lectotypes.
Referring to fig. 10, a sandwich surface layer 4 is disposed between the incident surface layer and the transmission surface layer, and a damping layer is disposed between the sandwich surface layer and the incident surface layer and the transmission surface layer.
The incident surface layer is an aluminum plate with the thickness of 3mm, the transmission surface layer is an aluminum plate with the thickness of 6mm, the sandwich surface layer is an aluminum plate with the thickness of 1mm, and the damping layer is a butyl rubber viscoelastic adhesive tape with the thickness of 1 mm.
Based on a numerical simulation method of acoustic finite element-boundary element (FEM-BEM) coupling, establishing a simulation model of the constraint viscoelastic damping structure, wherein the simulation model is fixedly connected to the peripheral wall surface of the transformer oil tank shell in a selected mode, comparing sound pressure level measurement requirements provided in GB/T1094.10-2003 'power transformer part 10 sound level measurement' and GB/T1094.101-2008 'power transformer part 10.1 sound level measurement application guide rules', and fitting results in a frequency range of 0-1000Hz according to a sound pressure level mean value which is 0.3m away from the middle part of the periphery of the transformer oil tank shell before and after the structure is applied and a result cloud chart of simulation at 400Hz (shown in figure 11): in a low-frequency range, before and after the constrained damping composite sound insulation structure is applied, the sound insulation performance TL of a transformer oil tank is improved by about 20dB averagely in a main noise frequency band (50-1000Hz) of a power transformer, and the constrained damping composite sound insulation structure has great practical application value.
The utility model discloses an useful part lies in providing a performance prediction method of compound sound insulation structure of restraint damping. The utility model provides a Helmholtz equation that the sound field satisfies in the combination air, the Navier equation that arbitrary elasticity and the viscoelastic layer of composite sheet vibration displacement u _ x, u _ z and its swell-shrink wave and the relation between the shear wave potential function satisfied under the sound field effect, with pass sound loss TL 10lg # (1/tau) ═ 20lg | delta | represent the sound insulation performance of the compound sound insulation structure of restraint damping. Based on the method for measuring the sound transmission loss of the component by the impedance tube in GB/Z22764 and 2011, the results are verified mutually by adopting finite element numerical simulation and laboratory experiments.
The utility model discloses a still another useful part lies in providing a design method for the compound sound insulation structure of restraint damping, this design method is from the actual problem that waits to solve, select panel, damping layer material type and thickness, and confirm the shear modulus G _ j, poisson ratio v _ j, mass density rho _ j and storage modulus E ^ of material, power consumption modulus E ^ of material, loss factor η, physical parameters such as relaxation time tau, then based on the performance prediction method of the compound sound insulation structure of restraint damping, with "the similar glue of viscoelastic material closely glue link sound incident plate and transmission plate, make incident plate and transmission plate vibrate in phase, avoided the sound insulation low valley that arouses by the vibration mode of every layer, the influence of viscoelastic material to restraint damping compound structure TL does not follow the mass law, the more the viscoelastic intermediate layer quantity, TL frequency spectrum valley position will move towards high frequency more" basic principle, confirm the thickness and the number of layers combination lectotype of surface course and damping layer, design the compound sound insulation structure of restraint damping that satisfies numerical value TL within the target frequency range of restraint damping.
The above description is only for the specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto, and those skilled in the art should understand that the present invention includes but is not limited to the contents described in the above specific embodiments. Any modification which does not depart from the functional and structural principles of the present invention is intended to be included within the scope of the claims.

Claims (6)

1. The utility model provides a be applied to compound structure of making an uproar of falling of restraint damping of transformer tank inner wall installs in transformer tank inner wall, its characterized in that: the damping composite sound insulation structure comprises an incident surface layer, a transmission surface layer and a damping layer located between the incident surface layer and the transmission surface layer, wherein the incident surface layer and the transmission surface layer are made of non-magnetic conductive metal materials, the damping layer is made of viscoelastic materials, and the incident surface layer, the transmission surface layer and the damping layer are bonded together to form a constrained damping composite sound insulation structure.
2. The structure of claim 1, wherein the structure is characterized in that: the incident surface layer and the transmission surface layer are aluminum plates.
3. The structure of claim 2, wherein the structure is characterized in that: the damping layer is a butyl rubber viscoelastic adhesive tape.
4. The structure of claim 3, wherein the structure is characterized in that: the thickness of the incident surface layer is 1.0mm, the thickness of the transmission surface layer is 1.5mm, and the thickness of the damping layer is 0.8 mm.
5. The structure of claim 3, wherein the structure is characterized in that: be equipped with the sandwich surface course between incident surface course and the transmission surface course, the sandwich surface course is aluminum plate, all be equipped with the damping layer between sandwich surface course and incident surface course and the transmission surface course.
6. The structure of claim 5, wherein the structure is characterized in that: the incident surface course is 3mm thick aluminum plate, the transmission surface course is 6mm thick aluminum plate, the sandwich surface course is 1mm thick aluminum plate, the damping layer is 1mm thick butyl rubber visco-elastic sticky tape.
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110676035A (en) * 2019-10-24 2020-01-10 绍兴建元电力集团有限公司大兴电力承装分公司 Transformer oil tank inner wall constrained damping composite sound insulation structure and design method
CN113066649A (en) * 2021-03-31 2021-07-02 国网湖南省电力有限公司 Low-noise oil-immersed transformer

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110676035A (en) * 2019-10-24 2020-01-10 绍兴建元电力集团有限公司大兴电力承装分公司 Transformer oil tank inner wall constrained damping composite sound insulation structure and design method
CN113066649A (en) * 2021-03-31 2021-07-02 国网湖南省电力有限公司 Low-noise oil-immersed transformer

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