CC BY
107Electronic Journal «Technical Acoustics» http://www.ejta.org
2011, 8 Liu Zhihong, Yi Chuijie
Institution of Mechanical Engineering of Qing Dao Technological University,
11, Fushun Road, Qingdao, 266033, China. e-mail: Lzhqingdao@163.com
Acoustic analytical solution of rotating compact sources in frequency domain
Received 05.05.2011, published 01.09.2011
The paper describes a frequency-domain numerical predicting method for sound radiation of rotating compact sound sources. The analytical Green functions of rotating monopole and dipole sources in free space are presented. Sound radiation models are established and characteristics of sound field are studied by numerical simulation. The relationship between radiated sound frequencies and acoustic nature frequency of source, angular frequency and its harmonics can be revealed by the mathematical solution. Results show that radiated sound field has a strong directivity, fundamental frequency transmitting in the rotary shaft direction and harmonics spreading along radial direction and frequency shift phenomena appearing clearly in higher rotating speed of source. The method has theoretical significance for exploring the low-noise rotating machinery.
Keywords: rotating compact sound source, sound radiation, analytical Green function, numerical simulation
INTRODUCTION
For a helicopter or centrifugal fans, the noise generated from moving sources is usually very important. They are many kinds of aerodynamic noise including turbine jet noise, impulsive noise due to unsteady flow around wings and rotors. Accurate prediction of noise mechanisms is essential in order to be able to control or modify them to comply with noise regulations and achieve noise reductions. Both theoretical and experimental studies are being conducted to understand the basic noise mechanisms. The first integral approach for acoustic propagation is the acoustic analogy [1]. In the acoustic analogy, the governing Navier-Stokes equations are rearranged to be in wave-type form. The far-field sound pressure is then given in terms of a volume integral over the domain containing the sound source. However the major difficulty with the acoustic analogy is that the sound source is not compact in supersonic flows. The Ffowcs Williams and Hawkings (FW-H) equation [2] is introduced to extend acoustic analogy in the case of surfaces. However, when acoustic sources are presented in the flowfield, volume integration is needed. This volume integration of the quadrupole source term is difficult to compute and is usually neglected in most acoustic analogy codes. Errors can be encountered in calculating the sound field. Recently, there have been some successful attempts in evaluating this term.
Another alternative is the Kirchhoff method [3] which assumes that the sound transmission is governed by the simple wave equation. Kirchhoffs method consists in the calculation of the nonlinear near- and mid-field, usually numerically, with the far-field solutions found from a linear Kirchhoff formulation evaluated on a control surface surrounding the nonlinear-field. The control surface is assumed to enclose all the nonlinear flow effects and noise sources. The sound pressure can be obtained in terms of a surface integral of the surface pressure and its normal and time derivatives. This approach has the potential to overcome some of the difficulties associated with the traditional acoustic analogy approach. The method is simple and accurate and accounts for the nonlinear quadrupole noise in the far-field. Full diffraction and focusing effects are included while eliminating the propagation of the reactive near-field.
More experimental studies to the complexity of sound generation of moving sound sources have been presented. In 1965, M. V. Lowson [5] derives firstly acoustic field equations produced from rotating point force. The equations are applied successful to predict the sound radiation of rotors. The sound field mechanism of the linear motion point source with the moving coordinate system is first proposed by P. M. Morse [4] in 1968. The sound radiation equations are only available for simple moving point sources and the method of coordinate transform is difficult for the complex motion sources. The equations are only used to predict the moving sources in free field. However, in most applications only a few locations are needed to study directivity and compare with measurements. Also, for many numerical solution of field equations dissipation and dispersion errors and an accurate description of propagating far-field waves is compromised. Sound field equations of rotating point force with cylindrical boundary using direct boundary element method have been deduced by K. D. Ih and D. J. Lee [6]. Helmholtz equation and its normal derivative of moving surface are given. The equations are applied to discuss the sound source’s types and are extended to explore acoustic radiation of centrifugal fans by W. H. Jeon and D. J. Lee [7-10]. These methods have established the foundation for sound radiation of moving source but there are some problems needed to overcome further. First the simplification of the fact with the assumption of point source and plane wave will bring more inaccurate for the prediction. Second, the sound pressure equations are often given in time domain. The time models are difficult to calculate and obtain the numerical solution.
In order to deal with the problems, sound radiation in frequency domain is investigated in the paper. The analytical expressions of the pressure of rotating monopole and dipole based on numerical Green function are derived. Characteristics of sound field are explored by numerical simulation. The analytical method provides important theoretical value for the research of sound radiation and noise control of moving source.
1. ANALYTICAL FORMULAE
In this section, the analytical Green function and sound pressure model of rotating compact sources are derived in frequency domain. The Green formula is as a common starting point.
1.1. Free-field analytical Green function
1.1.1 Rotating point source
The Green function G (x, y, t ,t) is defined as the response of the flow to an impulsive
point source represented by delta functions of space and time. G (X, y, t ,t) is the acoustical
response measured in X at time t of a source placed in y fired at time t :
cn?-v2G=S(x-y)5(‘ t °)
where S(x - y) = S(x1 - y1 )S(x2 - y2 )S( x3 - y3), when t <t , then G = 0.
1
4n\x - JP|
, f \x - vl ^ 1 f r \
G(x,y,t,r)= hS t-t--=--S t-t—- , (2)
" 4nr„
cn
V 0 J ^/ws v '■'O J
where c0 is the sound speed.
Introducing G as shorthand notation for the Fourier transform of Green function, which is defined by
G = — I-;» G (x, y, t, r)e~iatdt.
2n v 7
Taking the Fourier transform on both sides of the formula (2) then Green function in frequency-domain can be deduced:
A/ — — \ 1 -iot iKr
G(y,a,T)= e e s, (3)
8n rs v '
where o is the frequency, k = o / c0 is wave number.
Rotating point source configuration is in figure 1. Location of initial point source is (r,6,p), observation location is (r0,60,p0), where ^ = Qt, 6 = nl2, Q are the rotating angular frequencies.
In the spherical coordinate, we expand the term elkrs/4nrs of formula (3) with Legendre and spherical harmonic functions:
eikrs » n T »
— = Tb, I C(O.VK= -T-IX2» + 1)i„P(cosP). (4)
4nr„ n=0 m=-n 4n n=0
Figure 1. Rotating point source
By the Euler's formula and addition theorem:
P„ (cos P) = £ Smam„ [ e""-"’ + [
e*"" e~i"^T + e i"" e^m^T
h b \jn (Kro)hn (Kr) r > ro (1/2 m = 0 (n - m)! nm ( n)nm ( n)
where bn =< , ; , sm = { , amn = ±-Pn (cos0)Pn (cos6'0),
n \jn (Kr)h, (Ko) r < ro m V m = 1... n mn (n+m)! ,n' 0>-
P is the angle between the vector r0 and r.
Green function of rotating point source in free space is given by
iK “ n
G ( y 0 T) = -n ££Sm (2n + 1) bnamn (" (
n=0 m=0
0+ mQ)r + e*m"o e* (-mQ)
(5)
1.1.2 Rotating dipole source
Rotating dipole source’s analytical Green function and sound field expressions in frequency domain are derived. They are two different types dipole, the horizontal (along the "orientation) and vertical directions (along the z axis), are discussed. They are shown in figure 2 and 3 respectively.
Figure 2. Horizontal rotating dipole source
Figure 3. Vertical rotating dipole source
We can get multipole Green function by the partial derivatives of source coordinates of rotating point source’s Green function. Vertical Green function of dipole source is defined by
the derivative of G along the source coordinate Z (6 = 0) :
Gz = -dG / dz = -(dG / dr) cos 6 ,
(6)
GZ (r / ro ) = ££ s„ (-K) (I cos
n=0 m=0
6b' a (
n mn \
(7)
where b: = \r >ro,
[ jn (Kr )hn (Kr0 ) r < r0.
Horizontal Green function of dipole source is the derivative of G along the " orientation:
G =- - G
" r0
G"(r / ro ) = £ (-K/ro)[<2n^]b„»
8n
n=o
f n (n - m)! r (-)
P (o)P (6)-£^5tPm (o)Pnm (6H
(n + m )!
m=1
e~im" e-i(+ mQ) e^-m" e-i(-mQ)
1.2 Sound pressure model and directivity
1.2.1 Sound pressure of rotating dipole source
We assume that the acoustic field is from a given time-harmonic source distribution Qs (T) = Q (Te '0T, then the sound pressure is given by
p (F-t)=E Q (T)GdT=E Q-(T n s(t - T- R)dT. (9)
Taking the Fourier transform on both sides of the formula (9) then we can get sound pressure in frequency-domain:
p(r,0) = -1 f f Qs (r)Ge~,mdzdt = -^ f Q(r)e~,C0TGdT, (1o)
2nJ-<”J-<” 2n-“
Q (t) is point source strength. We define the dipole strength Ds = Qsd and assume that d is vanishingly small and the Ao (0) is the Fourier transform of Q(t) , then
A (0)=2n£ Q (r)e-0TdT. (11)
For a given time-harmonic source, formula (11) is rewritten as
Ao (0) = Qs(0-0t) (12)
where 0t is the source vibration frequency (nature frequency). The sound pressure of rotating dipole source is presented P.
P, = Ds ££ &m (-iK) f ^+^) cos6o * Pm (o)Pnm (cos6o )*[( (0 + mfi-0,))
n=o"=o f 8n ) (n + m)! L\ '! (13)
+ ( ( - mQ - )t )] ,
pr= D, ]C-,K(82:2+ m- \ Pn (o)P: (cos6„ )-±,m ("j Pm (o )p: (cos6„).
n=o 8n ro \ m=1 (n +m)! (14)
(e (-""s (0 + mQ -at) + e~'m(""s (0 - mQ - at)} .
1.2.2 Directivity of rotating dipole source
The far-field directivity pattern is defined by removing the e~'Kr/r factor so that the directivity pattern D(6,") is defined by
limn[p (r,6") = (e^/r)D (6,". (15)
Far-field directivity of rotating dipole source:
D, (6") = re-"p, Dr(6," = k'"P,. (16)
2 NUMERICAL ANALYSIS OF SOUND FIELD
Acoustic field characteristics are given in the condition of time-harmonic source. Simulation parameters: azimuth of observation point "o = n/4, source nature frequencies 0t are 23oo and 68oo Hz, rotating angular frequencies Q are 112 and 56o rad/s, acoustic field frequencies are shown by 0=0t + kQ. k is harmonic orders and is for integer k = -5, • • • ,5. Observation angle 6o are given o, n/18, n/6, n/3, n/2 . For far-field r = 2m and ro = o.3m. Simulation results are demonstrated from figure 4 to figure 7.
(c) 0t =23oo Hz, 0o =56o rad/s
(b) 0t =68oo Hz, 0o =112 rad/s
(d) 0t =23oo Hz, 0o =112 rad/s
Figure 4. Sound pressure amplitude distribution of vertical dipole with observation angle at
different nature and angular frequencies
With the increasing of nature frequencies, the far-field sound pressure amplitude of vertical dipole increases, the scope of harmonic distribution expand and fundamental frequency component reduce with the observation angle augmentation. Harmonic distribution is the most abundant in the observation angle ofn/2. There is only fundamental frequency in the rotating axis direction. With the increasing of angular frequencies, the distribution of harmonics and sound pressure amplitude increase. Doppler frequency shift phenomena are appear clearly with higher angular frequency shown in figure 5.
(a) Low Frequencies
(b) High Frequencies
Figure 5. Sound pressure amplitude distribution of vertical dipole with different angular
frequencies at 6o° observation angle
(a) 0t =68oo Hz, 0o =56o rad/s
(b) 0t =68oo Hz, 0o =112 rad/s
(c) 0t =23oo Hz, 0o =56o rad/s
(d) 0t =23oo Hz, 0o =112 rad/s
Figure 6. Sound pressure amplitude distribution of horizontal dipole with observation angle at
different nature and angular frequencies
Sound pressure amplitude is impacted greatly by the nature frequencies. The scope of harmonic distribution expands with the increasing of view angle in figure 6. Fundamental frequency is evidence in the small observation angle as o andn/18. There are no harmonic orders in the observation angle n / 2. The nature and angular frequencies changing have great effect on the harmonic distribution.
Rotating dipole source have an intensive space directivity which is shown in figure 7 and figure 8.
(c) k=3 (d) k=5
Figure 7. The directivity of vertical dipole with different harmonic orders at the same and
nature frequency
(a) 0t =68oo Hz, 0o =112 rad/s (b) 0t =23oo Hz, 0o =56o rad/s
Figure 8. The directivity of vertical dipole with different nature and angular frequencies at
harmonic order k=5
With the increasing of harmonic orders, the directivity of vertical dipole becomes intensive. Especially, sound power focuses on the range from n/6 to n/3 in figure 7. The changes of nature and angular frequency have a small effect on the directivity of vertical dipole. It is shown in figure 8.
(c) k=3
(d) k=5
Figure 9. The directivity of horizontal dipole with different harmonic orders at same nature
and nature frequency
(a) 0t =68ooHz, 0o =112rad/s
(b) 0t =23ooHz, 0o =56orad/s
Figure 1o. The directivity of horizontal dipole with different nature and angular frequencies at
harmonic order k=5
With the increasing of harmonic orders, the directivity of horizontal dipole becomes intensive. Especially, sound power focuses on the range from n/3 to n/2 in figure 9. The change of nature and angular frequency has a small effect on the directivity of horizontal dipole. It is shown in figure 1o.
CONCLUSIONS
A frequency-domain method has been developed for prediction of sound field of rotating diople source. The method is based on the acoustic solution of rotating point source in freqency-domain with analytical Green function. Solutions are carried out employing an explicit sound pressure model and the characteristics of sound field of moving source. By numerical simulations we can get that the sound field frequency involves nature frequency, angular frequency and its harmonics. With the increasing of nature and angular frequency, sound field radiation frequency becomes complex. The free-space directivity of rotating source is intensive greatly. The method and results have important theoretical significance on the moving source sound field characteristics analysis and exploring the low-noise design of rotary machines.
REFERENCES
1. M. J. Lighthill. On sound generated aerodynamically. I. General Theroy. Proc. R. Soc. Lond., 1952, 211A, 11o7, 564-587..
2. J. E. Ffowcs Williams, D. L. Hawkings. Sound generation by turbulence and surface in arbitrary motion. Phil. Trans. Roy. Soc. of London, 1969, 264A, 321-342.
3. D. L. Hawkinqs. Noise Generation by Transonic Open Rotors. Westland Research Paper 599. 1979.
4. P. M. Morse, K. U. Ingard. Theoretical Acoustics. McGraw-Hill, New York, 1968.
5. M. V. Lowson. The sound field for singularities in motion. Proceeding of the Royal Society in London, Series A, 1965, 286, 559-572.
6. K. D. Ih, D. J. Lee. Development of the direct boundary element method for thin bodies with general boundary conditions. Journal of Sound and Vibration, 1997, 2o2, 361-373.
7. W. H. Jeon, D. J. Lee. An analysis of the flow and aerodynamic acoustic sources of a centrifugal impeller. Journal of Sound and Vibration, 2ooo, 222, 5o5-511.
8. W. H. Jeon, D. J. Lee. An analysis of generation and radiation of sound for a centrifugal fan. 7-th International Congress on Sound and Vibration, 2ooo, 121(3), 1235-1242.
9. W. H. Jeon, D. J. Lee. Anumerical study on the flow and sound fields of centrifugal impeller located near a wedge. Journal of Sound and Vibration, 2oo3, 266, 785-8o4.
10. H. L. Choi, D. J. Lee. Development of the numerical method for calculating sound radiation from a rotating dipole source in an opened thin duct. Journal of Sound and Vibration, 2oo6, 295, 739-752.
