extra edge damping as a way to improve sound insulation of

Extra Edge Damping as a Way to Improve SoundInsulation of Window StructuresAleksey Nikolaevich Puzankov, Dmitry Lvovich Shchegolev, Vladimir AleksandrovichTishkov and Vladimir Nikolaevich BobylevNizhny Novgorod State University of Architecture and Civil Engineering, Nizhny Novgorod, Russia.

(Received 26 September 2016; accepted 9 June 2017)

The article presents the experimental data of research of sound insulation of window structures using supple-mentary damping along the perimeter of the translucent portion of the protection with a strip of non-transparentvibration-damping material (edge damping). The authors considered a method for calculating double translucentprotective structures with edge damping. They gave versions of possible design solutions for these protectivestructures.

NOMENCLATURE

IGU — insulating glass unitISO — International Organization for StandardizationNNGASU — Nizhegorodsky Gosudarstvenny Arkhitekturno-stroitelny Universitet (Nizhny Novgorod State University ofArchitecture and Civil Engineering)

1. INTRODUCTION

Nowadays the increasing sound pollution of urban areasmakes it critical to improve sound insulation of outer protectivestructures of residential and public buildings, particularly thoseof windows. There are several ways to increase the sound insu-lation of windows without significantly increasing the materialconsumption and complexity of the design. Let us considerone of them.

2. WAYS TO INCREASE SOUNDINSULATION USINGTHE ADDITIONAL DAMPING

Extra damping of glasses of protection is widely used inmodern window structures, and specifically to improve theirsound insulation. There are several methods to use extra damp-ing to improve the sound insulation properties of translucentprotection:

• method No.1 — damping with a transparent film on theouter surface of the pane;

• method No.2 — damping with a transparent material con-necting two layers of the pane (triplex);

• method No.3 — use of non-transparent damping materialin certain areas of glazing (e.g., along the perimeter of thestructure).

The impact of damping methods No.1 and No.2 has beendiscussed by many researchers, in particular, by D.V. Mury-gin,1 A.A. Kochkin,2 J.G. Lilly,3 N. Garg,4 U. Keller,5J. Schimmelpenningh6 and others. In these and other re-searches, the results proving the efficiency of these ways ofdamping for improving sound insulation of various types oftranslucent enclosing structures are presented.

The third method is now scarcely studied, despite the factthat its application may allow to significantly improve thesound insulation due to the slight reduction of translucent area

of the structure. In his paper I.I. Bogolepov7 discussed thedouble polymethylacrylic structure in which a special elasticmaterial applied on the perimeter of the glazing, served for theacoustic separation of protection plates and prevention of oc-currence of sound bridges; however, the effect of this materialas a damping one has not been discussed.7

Currently, there are effective self-adhesive damping materi-als based on different types of polymer mastics having a lossfactor η = 0.3–0.4. It is proposed to use such materials for past-ing the perimeter of the transparent portion of the protection.These materials are relatively inexpensive and their costs arelow, since the glass area to be covered with these materials issmall. Such materials include, in particular, “BiMast Bomb”(η = 0.4), which is proposed to be used in subsequent experi-mental studies of the method.

3. THEORETICAL STUDIES OF POSSIBLEINCREASE OF SOUND INSULATIONUSING ADDITIONAL DAMPING

Consider the theoretical possibility of pasting the strip ofopaque vibration cushioning material around the perimeter oftranslucent walling (edge damping) to improve the design ofsound insulation.

Since the single-layer translucent structures are practicallynot used in modern construction practice, the studies on theeffect of regional damping on sound insulation of translucentwalling should be carried out for the double structure with anair gap.

Theoretical studies of sound insulation of walling of build-ings and structures in the NNGASU Laboratory of acousticsare carried out on the basis of the wave fields self-coupling the-ory (hereinafter — the WFSC theory) developed by a scientificschool of Professor M.S. Sedov.8 Since there aren’t many ma-terials on this subject in English sources, the following groundexpressions describing the sound insulation of double wallingwith an air gap are demonstrated here.

According to the WFSC theory, the walling structure makesa wave motion under the influence of incident sound waves,which involves its own (free) and forced (inertial) waves.

Resonant passage of sound is determined by the degree ofthe wave fields self-coupling in front of and behind the wallingand by the wave field made by own oscillations of the plate.The bigger the self-coupling of sound fields is, the more in-tense the sound will penetrate through the barrier. Inertial pas-

106 https://doi.org/10.20855/ijav.2018.23.11286 (pp. 106–112) International Journal of Acoustics and Vibration, Vol. 23, No. 1, 2018

A. N. Puzankov, et al.: EXTRA EDGE DAMPING AS A WAY TO IMPROVE SOUND INSULATION OF WINDOW STRUCTURES

sage of sound depends on the surface density of the fence andits geometrical dimensions (length and width).

Given the independence of inertial and free waves in accor-dance with the principle of superposition of sound transmis-sion, the coefficient for double walling with an air gap can bewritten as:

τ = τs.i. + τs.r. + τ1iτ2i + τ1rτ2r; (1)

here τs.i. is the coefficient of inertial transmission of soundthrough the structure as a system of plates with elastic connec-tion between them;τs.r. is the coefficient of resonant transmission of sound

through the structure as a system of plates with elastic con-nection between them;τ1i is the coefficient of inertial transmission of sound

through the first plate;τ2i is the coefficient of inertial transmission of sound

through the second plate;τ1r is the coefficient of resonant transmission of sound

through the first plate;τ2r is the coefficient of resonant transmission of sound

through the second plate.In this expression τs.i. coefficient is given by:

τs.i. =1

π2

ρ20c20

m′2f2

F 21i.av

( f2

f20− 1) + 1

; (2)

where m′ is the area density of the walling:

m′ = m′1 +m′2; (3)

wherein m′1 is the area density of the first walling plate,kg/m2;m′2 is the area density of the second walling plate, kg/m2;f is the frequency, Hz;ρ0c0 is the characteristic impedance;f0 is the resonant frequency of the walling, as a system of

“mass-elasticity-mass”, Hz.

f0 = 60

√m′1 +m′2dm1m2

. (4)

In this expression, d is the distance between the plates of thewalling (the width of the air gap), m.F1i is the response function of the first plate, on which the

sound impinges.

F1i =GmnQmn

. (5)

Herein:

Gmn =

{Qm −

sinmπ

π · (m2 +m21)· [m1 · sinmπ+

+m · e−m1π +m · βa · (1 + e−2·m1π)]}×

×{Qn −

sinnπ

π · (n2 + n21)·[n1 · sinnπ + n · e−n1π+

+n · βb · (1 + e−2·n1π)]}

;

βa =e−m1π − cosmπ

1− e−2·m1π;

βb =e−n1π − cosnπ

1− e−2·n1π;

m =k0 · aπ· cosαx;

n =k0 · bπ· cosαy;

cosαx =b · sin θav√a2 + b2

;

cosαy =a · sin θav√a2 + b2

;

m1 =k0 · aπ·√

1 + sin2αx;

n1 =k0 · bπ·√

1 + sin2αy;

cos2αx + cos2αy + cos2θ = 1;

Qmn = Qm ·Qn;

Qm =1

2· (1 +

sin2mπ

2mπ);

Qn =1

2· (1 +

sin2nπ

2nπ).

Here:a and b is the walling dimensions on the plan (length and

width), m;αx and αy — slip angles of the sound wave along the sides

of the plate a and b;k0 — the wave number of the medium, m−1;θav — the angle of incidence of the sound waves at the first

walling plate (in diffused falling θav = 51.7575◦).The coefficient τs.r. in the expression (1) is defined by:

τs.r. =1

π2

ρ20c20

m′2f2

A2 ( f2

f20−1

) + 1; (6)

where A is the characteristic of self-coupling.The value of characteristic of self-coupling depends on the

field frequency range. Boundary frequencies of the areas ofsimple spatial resonance (hereinafter — SSR), incomplete spa-tial resonance (hereinafter — the ISR) and the full spatial res-onance (hereinafter — FSR) is calculated by the following ex-pressions.

Boundary frequency of SSR:

frm0n0 =c0

4 · a; (7)

where c0 is the speed of sound in air, m/s.This area is characterized by a mismatch between the speed

vectors of sound waves in the plane of the plate and the ownelastic waves.

Boundary frequency of ISR:

frmn0 =c0

2 · a · sinαmn0

; (8)

where

sinαmn0=

b√a2

4 + b2. (9)

αmn0is the angle between the sound waves impinging on

the plate and waves of own oscillations of the plate.In the ISR area the characteristics of own elastic and acous-

tic waves are not fully coincide: the speed of the spread of

International Journal of Acoustics and Vibration, Vol. 23, No. 1, 2018 107


tracks of free and sound waves on one side of the plate areequal to each other, and on the other side they are in such aratio, in which the response of the plate is largest.

Boundary frequency of FSR:

frmn =c202π

√m′1D1

. (10)

In this frequency range the conditions of complete self-coupling of sound fields in front of and behind the wallingstructure and the wave field of the natural oscillations of thewalling are met.

In the SSR range at frequencies below the boundary fre-quency of the ISR (f < frmn0

) the expression for the self-coupling characteristic has the following form:

A20m0n0

= ∆NPm4cp

(m2av −m2

0av)4

; (11)

where ∆NP is the number of resonances in the frequencyband ∆f :

∆NP =∆fab

2√

D1

m′1

; (12)

here: ∆f = fu − fd, Hz;fd is the lower boundary frequency, Hz;fu is the upper boundary frequency, Hz.The values of fd and fu are calculated by the expressions:

fd =√fnfn−1; fu =

√fnfn+1; (13)

where fn is the center frequency of the current one-thirdoctave band, Hz; fn+1 is the center frequency of the followingone-third octave band, Hz; fn−1 is the center frequency of theprevious one-third octave band, Hz;D1 is bending stiffness of the first walling plate, defined by

the relation:

D1 =Eh3

12(1− σ2); (14)

where σ is the Poisson’s ratio;E is the elastic modulus, Pa;h is the thickness of the walling plates, m.

m2av =

2fb2

π√

D1

m′1(1 + b2

a2 ); (15)

m20av =

1

π8

fab√D1

m′1

2

. (16)

In the ISR range the frequency range the (frmn0 < f <frmn

2 ) expression for the self-coupling characteristic will be:

A20 = m0max

n2

(n2 − n20av)2+ n0max

m2

(m2 −m20av)

2. (17)

In this expression:

m0max = a

√4f2

c20− 1

b2;

n0max = b

√4f2

c20− 1

a2;

n20av =(n0max

2

)2;

m20av =

(m0max

2

)2;

n2 = b2

(2

π

√m′

Df − m2

0av

a2

);

m2 = a2

(2

π

√m′

Df − n20av

b2

).

In the frequency range ( frmn

2 < f < frmn), the self-coupling characteristic is given by:

A200 = A2

0 +A201; (18)

where the value A20 is defined by the expression (17), and

the additional value of A201 is:

A201 = m01max ·

n21(n21 − n201av)2

+

+ n01max ·m2

1

(m21 −m2

01av)2. (19)

Herein:

m21 = n21 =

2f

π

(1

a2+

1

b2

)√D

m′;

m01max = a

√4f2

c20− m2

1

b2;

n01max = b

√4f2

c20− n21a2

;

n201av =(n01max

2

)2;

m201av =

(m01max

2

)2.

The coefficients τ1i and τ2i (1) describe the sound wavepassing sequentially through the first plate, the air gap and thesecond plate. They are determined by the expressions:

τ1i =1

π2

ρ20c20

m′21 f

2cos2θav

F 21i.av

+ 1; (20)

τ2i =1

π2

ρ20c20

m′21 f

2cos2θ2F 2

2i.av+ 1

. (21)

Here θ2 is the angle of incidence of sound waves constitutingthe natural vibration shape of the air gap along the plane of thesecond plate:

cosθ2 =d√

a2+b2

2 + d2.

The nature of the resonance passage through the first andsecond plates is different for the following frequency areas:

108 International Journal of Acoustics and Vibration, Vol. 23, No. 1, 2018


f <frmn

2;frmn

2< f < frmn; f > frmn.

In the frequency range, the (f < frmn

2 ) coefficients of reso-nant passage from the expression (1) have the form:

for the first walling plate:

τ1r =1

1.15π3

8ρ20c20A

401m

′22 f

2η1cos2θav + 1; (22)

for the second walling plate:

τ2r =1

1.15π3

8ρ20c20A

402m

′22 f

2η2cos2θ2 + 1. (23)

Here η1, η2 are the loss factor for the first and second plates,respectively.

For the frequency range ( frmn

2 < f < frmn) the expres-sions (22) and (23) take the form:

for the first walling plate:

τ1r =1

1.15π3

8ρ20c20A

4001m

′22 f

2η1cos2θav + 1; (24)

for the second walling plate:

τ2r =1

1.15π3

8ρ20c20A

4001m

′22 f

2η2cos2θ2 + 1; (25)

For the FSR area for the frequencies (f > frmn) the coef-ficients of the resonant sound passage for the first and secondplates are, respectively:

τ1r =1

8πρ20c

20m

′21

f3

frmnη1cos2θav

√1− frmn

f + 1; (26)

τ2r =1

8πρ20c

20m

′22

f3

frmnη2cos2θ2

√1− frmn

f + 1. (27)

In the above expressions the damping of the vibrations inthe walling plate is taken into account by the coefficient of thematerial losses η. Thus, it can be concluded that the additionaldamping affects the resonant oscillations of the walling platesto which it is applied.

To assess the impact of the edge damping on sound insula-tion of the structure it is proposed to introduce in the expres-sions (22)–(27) the value of the effective loss coefficient ofconstruction (ηef1, ηef2). The effective loss coefficient is therate of glass losses considering the damping with fragments ofvibration cushioning material. Changing the effective loss co-efficient will have an impact on the coefficients of the resonanttransmission of sound: τ1r and τ2r.

The values of ηef for glass with partial pasting with dampingmaterial can be measured experimentally by the Oberst method(standard method to measure the loss factor of the material).9The results of measurements for glass 4 mm thick with dif-ferent pasting area of vibration cushioning material “BiMastBomb” conducted at the Acoustics Laboratory of NNSUACEare presented in Table 1.

As can be seen from the data shown in the table, the ef-fective loss coefficient in case of the edge damping with the

Table 1. The results of measurements of the effective loss factor for a glass4 mm thick

Sample area The effective loss factor ηefcovered with vibration measured accordingcushioning material, % to the Oberst method9

0 0.00612.5 0.01925 0.02250 0.023

100 0.026

Figure 1. Comparison of values of coefficient τ1r when the loss factor: 1 —ηef = 0.006; 2 —- ηef = 0.019.

area 12.5 % of structure area exceeds the loss coefficient of theglass by 3 times. It is proposed to consider the damping areaof 12.5 % as the most effective value, since with this relativelysmall pasting area a significant increase in the effective lossrate is achieved, and with further increase in the area of vibra-tion cushioning material a significant increase in the values ofthe effective loss coefficient does not occur.

In order to estimate the expected increase in sound insula-tion due to the use of regional damping by the above proce-dure, there has been calculated the coefficients τ1r and τ2r andsoundproofing coefficient R, dB for the double walling of sil-ica glass of a size 1.3 × 1.1 m with a glazing formula 4 + 24 +4 mm (two sheets of silicate glass 4 mm thick each, separatedby an air gap of 24 mm width). The calculation was made fortwo values of the effective loss factor:

1. ηef = 0.006 (glass without additional damping);2. ηef = 0.019 (glass with an additional damping).The calculation results are shown in Figures 1, 2, 3.As seen from frequency characteristics in Fig. 1 and Fig. 2,

with an increase in the loss factor from 0.006 to 0.019 the val-ues of coefficients τ1r and τ2r significantly increase over theentire frequency range.

However, according to the WFSC theory the impact of τ1rand τ2r on sound insulation is largely dependent on the fre-quency range. These coefficients have the greatest impact onthe structure sound insulation at frequencies f > frmn

2 . Atfrequencies below frmn

2 the effect of τ1r and τ2r is slightlyless (the inertial passage of sound has more influence in thiscase). At frequencies close to the resonance frequency of thestructure as a system of “mass-elasticity-mass” f0, the influ-ence of these coefficients is minimal. The sound insulationhere is mainly determined by coefficients, that considering theconstruction as a whole: τs.i. and τs.r..

Thus, for walling with glazing formula 4 + 24 + 4 mm, weshould expect a substantial increase of sound insulation at fre-quencies above 1600 Hz, and a slight increase in the range of315–1600 Hz, which is confirmed by calculating the insulation



Figure 2. Comparison of values of the coefficient τ2r when the loss factor: 1— ηef = 0.006; 2 — ηef = 0.019.

Figure 3. Comparison of the calculated values of the walling insulation withthe glazing formula 4 + 24 + 4 mm at: 1 — ηef = 0.006; 2 — ηef = 0.019.

shown in Fig. 3.To test the assumptions, an experimental study of the effect

of additional edge damping on sound insulation in the translu-cent double walling with an air gap in the NNGASU Labora-tory of acoustics was carried out.

4. DESCRIPTION OF EXPERIMENTALSTUDIES’ METHODS

The sound insulation of studied protection structures hasbeen studied in large reverberant chambers of the NNGASULaboratory of acoustics according to standard procedure ISO10140-2 «Acoustics — Laboratory measurement of sound in-sulation of building elements — Part 2: Measurement of air-borne sound insulation».10

The measurements were made using a precision acoustic in-strumentation “Larson & Davis” (2900V spectrum analyzer,1/2′′ measuring microphones, type 2559). Measuring micro-

phones were sequentially installed in eight points in high- andlow-level chambers.

In the high-level chamber of 150 m3 with the help of sound-amplifying equipment the sound pressure levels in the range of100–110 dB were created. In the low-level chamber of 66 m3

the exceedance of the valid signals over intrinsic noise wasmore than 15 dB. This condition is satisfied for all frequenciesof the test range (100–8000 Hz of the 1/3-octave RMS am-plitude spectrum). The lower limit of the frequency range isdue to boundary frequency of the diffuseness of reverberationchambers in NNGASU Laboratory of acoustics.

The average sound pressure levels (Lm, dB) in the measur-ing chambers were determined by the formula 10:

Lm = 10 · lg

(1

n

n∑i=1

100.1·Li

); (28)

where n is the number of measuring points in the measuringchambers (in this case n = 8 for each chamber);Li , dB is the sound pressure level in the ith point.Sound insulation of the enclosing structures (R, dB) when

exposed to air noise was calculated by the formula 10:

R = Lm1 − Lm2 + 10 · lg SA

; (29)

where Lm1 · Lm2 , dB — the average sound pressure levelsin a high level chamber and in the low level chamber, respec-tively;S,m2 — the area of the tested enclosure;A = 0,16·V

T ,m2 — the equivalent acoustic absorption areaof low-level camera;V,m3 — the volume of low level chamber;T , s — the average time of reverberation in the low level

chamber.For each tested type of the enclosing structures, the measure-

ment of sound insulation was carried out three times. Accuracyof measurements was ±1.0 dB.

5. THE DESCRIPTION OF STUDIEDTRANSLUCENT WALLING

The translucent structures based on insulated glass units arewidely used in construction practice, so to conduct a researchon the effect of the edge damping on the sound insulation ofdouble walling the insulated glass unit was manufactured withthe glazing formula 4 + 24 + 4 mm with plan dimensions of1.3× 1.1 m.

The specific material “BiMast Bomb” manufactured by“Standartplast” LLC (Russia) was used for additional edgedamping. This material has one of the highest damping charac-teristics (η = 0.4) among opaque self-adhesive damping ma-terials, that are common in the Russian market.

The sound insulation of double glazed unit with varying de-grees of regional damping was measured in the course of theseexperimental studies.

The scheme of the studied structure is presented in Figure 4.

6. RESULTS OF THE PERFORMEDEXPERIMENTAL STUDIES

Frequency characteristics obtained during the experimentare presented in Figure 5. The experimental results confirmthe data of a theoretical calculation of the frequency range inwhich can be expected the increased sound insulation of thestructure when using edge damping.

The main gain in sound insulation when applying edgedamping occurs in the frequency range 315–3150 Hz. Themost effective way to improve sound insulation proved tobe damping both panes of glass with strip material “BiMastBomb” 40 mm wide around the perimeter (at that, area occu-pied by the vibration cushioning material is 13% of the totalarea of glazing structure), which roughly corresponds to the“effective” area of damping material 12.5% obtained by deter-mining the effective loss factor. The main gain in sound insu-lation is 2–8 dB when applying edge damping in the frequencyrange 315–3150 Hz. In the frequency range below 315 Hz the



Figure 4. The scheme of the studied structure, as set out in the opening oflarge reverberant chambers of Acoustics Laboratory of NNGASU: 1 — glassunit with glazing formula 4 + 24 + 4 mm; 2 — vibration cushioning material“BiMast Bomb”; 3 — silicone sealant; 4 — plaster rim.

Figure 5. Sound insulation of glass unit 4 + 24 + 4 mm with varying degrees ofedge damping material “BiMast Bomb” (experimental data): 1 — without theuse of edge damping; 2 — 20 mm damping along the perimeter (single glass);3 — 20 mm damping along perimeter (both glasses); 4 — 40 mm dampingalong the perimeter (both glasses).

visible gain in sound insulation is not observed. With a smallerarea of vibration damping material the gain in sound insulationis much less, but there it is observed in the same frequencyrange.

The lack of increase in sound insulation at frequencies be-low 315 Hz supports the conclusion that the additional damp-ing is inefficient at frequencies close to the resonance fre-quency of “mass-elasticity-mass”.

It is necessary to draw attention to the fact that the appli-cation of the regional damping leads to increase in weight ofthe structure. However, this mass change is very small anddoes not exert any significant influence on the sound insula-tion of enclosure. For the investigated structure with dampingusing 40 mm wide strip around the perimeter of both glasses,the weight is increased by 12% of the original weight of theglazing without damping.

It should also be noted that the design of double translu-cent enclosing structures based on glass units provides the ad-ditional damping element by applying a sealing material forinsulating glass perimeter. However, as follows from the re-sults of the experiment, the additional edge damping improvesthe sound insulation even in this case.

Also the additional damping arising during construction ofthe measuring aperture can influence the sound insulation ofthe structure. However, during these measurements the methodof installing glass in the structure did not change from mea-

Figure 6. Frequency characteristics of sound insulation of double-glazed unitof 4 + 24 + 4 mm without the edge damping: 1 — experimental data; 2 —theoretical calculation.

Figure 7. Frequency characteristics of sound insulation of double-glazed unitof 4 + 24 + 4 mm with edge damping of both glasses with use of material“BiMast Bomb” by a stripe of 20 mm along the perimeter: 1 — experimentaldata; 2 — theoretical calculation.

surement to measurement, so the effect of damping, which oc-curs during the installation of the structure, was always con-stant and was not reflected in the increase of sound insulationarising from the application of the edge damping.

The edge damping is only one factor affecting the sound in-sulation of translucent structures. When combined with othersimilar factors (including, for example, the number and thick-ness of glass, the width of the air gap, etc.) there can be ex-pected further increase of sound insulation of the structure.The aim of the study on the current stage is to study the pos-sibility of using the edge damping in particular to increase in-sulation, combine it with other factors to improve the resultachieved — the goal of the next phase of the work.

In Fig. 6 there is a comparison of the theoretical calculationdata in accordance with the above-mentioned method and ex-perimental results for the construction without edge damping.

In Fig. 7 there is a comparison of the theoretical calculationdata in accordance with the above-mentioned method and ex-perimental results for the construction with edge damping ofboth glasses with use of material “BiMast Bomb” by a stripeof 20 mm.

As can be seen from the comparison of frequency character-istics in Fig. 6 and Fig. 7, the theoretical calculation resultsquite accurately correspond to the experimental data within



Figure 8. Examples of possible design solutions of windows using edge damp-ing: 1 — the case of the window unit; 2 — rubber seal; 3 —- silicate glass; 4— vibration cushioning material; 5 — rubber sealing bead; 6 — spacer; 7 —sealing mastic.

the whole standardized frequency range of 100– 3150 Hz (i.e.within the areas of SSR (simple spatial resonance) and ISR(incomplete spatial resonances). Identification of the reasonsfor discrepancies between theoretical and experimental indicesof sound insulation that are observed at frequencies higher thanthe standardized range (above 3150 Hz, i.e. in the area of SSR)will be the goal of our further research.

7. DESIGN SOLUTIONS OF WINDOWS WITHEDGE DAMPING

Based on the above, as well as other experimental and theo-retical data obtained by the staff of the NNGASU Laboratoryof acoustics, design solutions of window units with IGUs withedge damping have been proposed in the course of studies ofthe capabilities of edge damping11, 12 (see. Fig. 8). At that, itcan be seen on the schemes that in this case it is possible to re-duce the area of the translucent part of enclosure occupied byedge damping by placing the glazing parts coated with damp-ing material inside the window unit housing.

An application for a patent for the invention was filed forthe described method to improve sound insulation, as well asdesign solutions of structures based on it.13

8. CONCLUSIONS

Based on the results of the study, it can be concluded thatthe edge damping with opaque materials is a promising wayto improve the sound insulation of windows and other glassstructures. The increase of sound insulation due to the edgedamping occurs in a wide range of frequencies of practicallysignificant range (at frequencies of 315–8000 Hz for construc-tions of 4 mm glass). In the field of a resonance of structureas a system “mass-elasticity-mass” the extra edge damping isineffective. This study established the most effective area ofpasting the vibration damping material (1/8 of the glass area).In the future we plan to study the possibility of using regionaldamping in combination with other structural measures, allow-ing to increase the sound insulation of the structure.

9. ACKNOWLEDGEMENTS

The Reported study was Funded by Government Program ofthe Russian Federation “Development of science and technol-ogy” (2013–2020) within Program of Fundamental Researchesof Ministry of Construction, Housing and Utilities of the Rus-sian Federation and Russian Academy of Architecture and

Construction Sciences, section of scientific research projectsNo.7.6, project title: “Investigation of the resonant and inertialmechanism of sound transmission through new types of multi-layer isotropic and orthotropic enclosing structures for uniquebuildings and development of theoretical methods for calculat-ing their sound insulation”.

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8 Sedov, M.S. et al., textitSound Insulation. EngineeringAcoustics of Vehicles: Handbook, N.I. Ivanov (ed.), Po-litekhnika, St. Petersburg, Ch. 1, 68–105, (1992).

9 ASTM E756-05(2010) «Standard Test Method for Measur-ing Vibration-Damping Properties of Materials»

10 ISO 10140-2 «Acoustics - Laboratory measurement ofsound insulation of building elements - Part 2: Measure-ment of airborne sound insulation»

11 Puzankov, A.N., Schegolev, D.L. Investigation of the effectof the edge damping of translucent walling on its acous-tic permeability, textitBuilding materials, textbf6, 36–37,(2012).

12 Puzankov, A.N. Study on effectiveness of usage of addi-tional vibration cushioning to improve the sound insulationof modern windows, textitTGASU Herald, textbf2, 119–129, (2015).

13 An application for a patent No. 2016102569 RussianFederation. A method for improving sound insulation oftranslucent structures / V.N. Bobylev, D.L. Schegolev,A.N. Puzankov; the applicant — Nizhny Novgorod StateUniversity of Architecture and Civil Engineering; appl.01/26/2016. - 2016. - 1 p.


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