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A previous study discussed a rectangular soundproofing ventilation unit having an inlet and an outlet located on the opposite face which results in a reduced outlet area. As a result, the ventilation function is decreased. To improve this problem, square one featuring an inlet and an outlet which are located on the crossed right angle face is proposed in this work. First, outlet sound pressure to the given inlet uniform velocity is obtained based on the wave equation and the boundary conditions. Next, the experimental results are shown to be in reasonable agreement with our theoretical predictions.
Along with the remarkable economic development, in recent years in developing countries environmental problems including road noise have been getting worse in countries belonging to tropical regions. Yano and others  measured road traffic noise on the main road of Vietnam for 24 hours and reported that a noise level of more than 75 dB occurred almost all day on the road with the highest noise level.On the other hand, ventilation holes are widely used in countries in tropical regions, which are installed in the middle of the window and the roof.
However, the noise of the road passes through the ventilation hole and propagates to the living space. As a result, there is virtually no difference in the noise level between the room and the outside, and people living in an environment are increasingly uncomfortable with noise increasing year by year even though there are considerable familiarity and patience. In recent houses, a glass plate is indicated on
the outside of the door ventilation hole to provide soundproofing measures. With this measures indoors only attenuation levels of only 10 dB – 15 dB can be obtained, but people are considerably reduced discomfort to noise. However, most residential houses in Southeast Asia do not have air-conditioning equipment,therefore by closing the glass plate during the day, the ventilate the room indoors cannot be done.A previous study  discussed a rectangular soundproofing ventilation unit having an inlet and an outlet located on the opposite face which results in a reduced outlet area. As a result, the ventilation function is decreased. To improve this problem, square one featuring an inlet and an outlet which are located on the crossed right angle confront is proposed in this work. There are for two sorts of waves inside the chamber, namely the standing wave that propagates in the axial direction and the traverse wave that propagates in the radial direction. The traverse wave occurs in the high frequency range. Regarding the circular cylindrical chamber, the noise will have a tendency to increase in this frequency range, far from decreasing depending on the resonance of the higher modes.
In this paper, at first the outletsound pressure to the given inlet uniform velocity is obtained based on the wave equation and the boundary conditions. Next, the experimental results are shown to be in reasonable agreement with our theoretical predictions.
Insertion loss IL defined by 
IL=10log W_r/W_0 =20log|U_1/U_2 | (1)
Here, W_r and W_0 are the radiated power at one point in space with or without the acoustic element inserted between that point and the source. The ratio of U_1/U_2 is equal to the D parameter of the four-pole parameters, as far as constant velocity source be concerned.
When three acoustic elements connected in series, as the sectional area of element 1 and 3 are sufficiently small to compare with those of element 2 of the D parameter of the whole system can be described by the following approximated equation
D=(coskl_1)(C_w)(jZ_3 sinkl_3) (2)
where C_w denoted the C parameter of element 2. In order to obtain a reliable IL effect, D parameter must be high enough. In other words, the design of element-2 to have a high enough parameter C_w is demanded.
Cw of square SVU
Model of the rectangular soundproofing ventilation unit which has a dimension of a×a×dis shown in Figure 1. Dimension of an input and output are(a_i2-a_i1)×(b_i2-b_i1) and(a_02-a_01)×(d_02-d_01) they located on the face which has a section area of S_ab=a×aand S_ad=a×d, respectively.
Figure1.Squaresoundproofing ventilation unit
Waveequation in terms ofvelocity potential is given by
(∂^2/(∂x^2 )+∂^2/(∂x^2 )+∂^2/(∂x^2 ))Φ=1/c^2 ∂^2/(∂t^2 ) Φ (3)
where c is the sound velocity. Let Φ=√2∅exp(jωt)(j^2=-1,ω=kc,k: wave number ) then the general solution of Eq.(3) can be given as
× ( Csinαx+Dcosαx)
× (Esin√(s^2-α^2 ) y+Fcos√(s^2-α^2 ) y )
where μ^2=s^2-k^2, A, B, C, D, E and F are arbitrary constants determinable from the boundary conditions, other symbols are constants.
Let-∂∅/∂x,-∂∅/∂y and -∂∅/∂zare the velocity component in the x, y and z directions, respectively. Assuming the walls of the cavity to be perfectly rigid and the loss at the wall can be neglected then boundary conditions are :
 at x=0 -(∂∅)/∂x=0 (5)
 at x=a -(∂∅)/∂x =0 (6)
 at y=0 -(∂∅)/∂y =0 (7)
 at y=a -(∂∅)/∂y=V_0 F_0 (x,z)(8)
 at z=0-(∂∅)/∂z=V_i F_i (x,z)(9)
 at z=d-(∂∅)/∂z=0(10)
where V_(i )is the driving velocity at the input, F_i (x,z)is defined as
Let ∅=∅_a+∅_bthen -∂∅/∂x=-∂∅_a/∂x+-∂∅_b/∂x, therefore we have the following boundary conditions
[1a] at x=0 -(∂∅)/∂x =0 (12)
[2a] at x=a -(∂∅)/∂x =0 (13)
[3a] at y=0 -(∂∅)/∂y =0 (14)
[4a] at y=a -(∂∅)/∂y=V_0 F_0 (x,z)(15)
[5a] at z=0-(∂∅)/∂z=0(16)
[1b] at x=0 -(∂∅)/∂x =0 (17)
[2b] at x=a -(∂∅)/∂x =0 (18)
[3b] at y=0 -(∂∅)/∂y =0 (19)
[4b] at y=a -(∂∅)/∂y=0(20)
[5b] at z=0-(∂∅)/∂z=V_i F_i (x,z)(21)
Based on the above boundary conditions ∅_abecomes
〖 ∅〗_a=4V_i/S_ab ∑_(m=0)^∞▒∑_(n=0)^∞▒(coshμ_(m,n) (z-d))/(μ_(m,n) sinhμ_(m,n) d)
I_(m,n) cos(mπx/a)cos(nπy/a) (22)
× ∫_(a_i1)^(a_i2)▒cos(mπy/a)dy (23)
Similarly, 〖 ∅〗_b becomes
〖 ∅〗_b=4V_0/S_ad ∑_(m=0)^∞▒∑_(n=0)^∞▒〖cosh nπ/d(z-d)〗
〖× O〗_(m,n) cos(mπx/a)cos(nπy/a) (24)
× ∫_(a_i1)^(a_i2)▒〖cos nπ/d (z-d)dy〗 (25)
The average sound pressure on the output is found as
(P_0 ) ̅=1/S_0 ∫_(a_02)^(a_02)▒∫_(d_01)^(d_02)▒〖P(x,b,z)dxdz〗
=jk ρc/S_0 ∑_(m=0)^∞▒∑_(n=0)^∞▒[4 V_i/S_ab (I_(m,n) cos(nπ))/(μ_(m,n) sinhμ_(m,n) d)┤
×∫_(a_02)^(a_02)▒∫_(d_01)^(d_02)▒〖cosμ_(m,n) (z-d) 〗 cos(mπx/a)dxdz
+4V_0/S_ad O_(m,n)/(β_(m,n) tanβ_(m,n) d)
×∫_(a_02)^(a_02)▒∫_(d_01)^(d_02)▒〖cos nπ/d (z-d) 〗 ├ cos(mπx/a)dxdz]
whereU_i=V_i S_i is the volume velocity supplied from the input.〖 Z〗_0=ρc/S_(0 )is the characteristic impedance of the output.
ExpandingEq.(26) with m=0 and n=0 the above equation becomes
(P_0 ) ̅=j4Z_0 [1/sinkd (〖-O〗_0,0 U_i+(S_0/S_ad coskd) U_0 ) ┤
+1/k ∑_*^∞▒∑_*^∞▒((I_(m,n) O_(m,n) cos(nπ))/(S_ad S_0 μ_(m,n) sinhμ_(m,n) d)┤ U_i
├ +├ U_0/(S_ad S_0 ) O_(m,n)/(β_(m,n) tanβ_(m,n) d)) ]
The Cw of SVU could be found from Eq. (27) as
RESULTS AND DISCUSSION
The average of outlet sound pressure is derived from Eq. (27) in which the first term in the bracket represents the plane wave and the second represents the higher order mode wave. First, with respect to the plane wave, the first term of Eq. (27), the sound pressure level is great at the frequencies where the denominator sin(kd) become zero.
kd=ηπ∴f=η c/2d (η=1,2,…) (29)
Similarly, with respect to higher order mode waves, the second term of Eq. (27), the sound pressure level becomes great at the frequencies given as follows:
∴f_(m,n)=c/2π √((mπ/a)^2+(nπ/a)^2+(ηπ/d)^2 )
=c/2a √(m^2+n^2+(ηa/d)^2 )
The spectrum of a plane wave and higher order mode are showed in Figure 2.
Note that, in the case of rectangular SVU, the resonance frequencies are
f_(m,n)=c/2π √((mπ/a)^2+(nπ/b)^2+(ηπ/d)^2 )
From Eq. (30) and Eq. (31), it is clear that the number of resonance frequencies generated inside the square SVU is less than those of rectangular SVU.
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