Side branch resonators modelling with Green's function...
Transcript of Side branch resonators modelling with Green's function...
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Side branch resonators modelling with Green’sfunction methods
E. Perrey-Debain, R. Marechal, J.-M. Ville
Laboratoire Roberval UMR 6253, Equipe Acoustique,Universite de Technologie de Compiegne, France
July 09-10, 2012
MATHmONDES 2012, Reading, U.-K.
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Outline
Introduction
Impedance matrix and Green’s function formalism
Simplified models
Low-frequency applications : Helmholtz and Herschel-Quinckeresonators
Medium-frequency applications : HQ-liner system for inlet fannoise reduction
Conclusions
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Introduction
Side branch resonators are commonly used for engine exhaust noisecontrol : (i) low-frequency applications with a single plane wavemode (automotive) (ii) medium-frequency applications and highlymultimodal context (aeronautics).
Pinc
Pref Ptr
Figure: Side branch resonator (cavity Ω) with two openings Γ.
Numerical predictions : (i) 1D approximations (with lengthcorrections) ; (ii) FEM, BEM -> computationally demanding (thisincludes mesh preparation etc...) especially in a highly multimodalcontext, lack of physical interpretation.
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Impedance matrix
In the frequency domain, the acoustic pressure must obey theHelmholtz equation
∆p + k2p = 0, k = ω/c ,
and q = ∂np = 0 everywhere except on Γ. The Green’s function forthe rigid-wall cavity is given by the infinite series
GΩ(r, r′) =
∞∑
n=0
φn(r)φn(r′)
λn − λ
where λ = ω2. Eigenfunctions φn are properly normalized so thatapplication of the Green’s theorem in the cavity yields
p(r) =
∫
ΓGΩ(r, r
′) q(r′)dΓ(r′)
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Impedance matrix
We need to precompute a finite set of eigenfunctions and estimatethe truncation error...Consider the eigenvector Φn, the FE discretization of ntheigenmode φn :
A(λn)Φn = 0 where A(λ) = K − λM
After reduction to the interfacial nodes, we obtain the impedancematrix
Z(λ) = ITΓ A−1(λ) IΓ
with
A−1(λ) =∞∑
n=0
ΦnΦTn
λn − λ= ΦD(λ)ΦT
Finally,
p = Z(λ) F q = GΩ q
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Truncation
Keeping the first N eigenmodes gives
Z(λ) = (ΦD(λ) ΦT)|N + R(λ).
The correction term R remains weakly dependent on the frequency,so we can take the first order Taylor expansion
R(λ) ≈ R(λ) + (λ− λ)∂R
∂λ+ . . .
The residual matrices are computed via
R = ITΓ A−1 IΓ − (ΦD(λ) ΦT)|N∂λR = ITΓ A−1MA−1IΓ − (Φ ∂λD ΦT)|N
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Scattering matrix
The theory starts by introducing the hard-walled duct Green’sfunction
G (r, r′) =∞∑
l=0
ψl(x , y)ψ∗l (x
′, y ′)
2iβleiβl |z−z ′|
The transverse eigenmodes ψl are solution of the boundary valueproblem
(∂2xx + ∂2yy)ψl + k2ψl = β2l ψl
with ∂nψl = 0 on the boundary line ∂S . These modes arenormalized as
∫
S|ψl |2 dS = 1
in particular ψ0 = 1/√Ad where Ad is the cross section area of the
main duct. For circular ducts :
ψl = Nm,nJm(αm,nr)eimθ, βl =
√
k2 − α2m,n
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Scattering matrix
The finite element discretization of the integral equation
p(r) =
∫
ΓG (r, r′) q(r′)dΓ(r′) + pI (r)
gives (ri is the FE node location)
pi =N∑
j=1
Gijqj + pIi with Gij =
∫
ΓG (ri , r
′) φj (r′)dΓ(r′)
The acoustic velocity is deduced from
q = (GΩ − G)−1 pI
Note :i. The computation is not trivial as ∂z′G is discontinuous at z′ = zi .
ii. The matrix GΩ − G is of small size.
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Simplified models : one opening
Starting with one opening only, the impedance matrix relation canbe averaged to give
p = Z (λ)q where Z(λ) =1
N
N∑
i=1
N∑
j=1
(Z(λ) F)ij
By the same token,
p =1
Wq + pI , where W =
2ikAd
A
and A denotes the area of the interface. An incident plane wavepI = e
ikz produces a transmitted pressure field
p = T eikz with T = 1 +
1
WZ(λ) − 1
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Helmholtz resonators
Figure: Classical (left) ; with extended neck (right).
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Helmholtz resonator, classical
60 70 80 90 100 110 1200
10
20
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40
50
60
TL modèle mixteTL simplifiéTL Ingard
Frequency (Hz)
TL(dB)
60 70 80 90 100 110 120−0.1
−0.05
0
0.05
0.1
0.15
0.2
0.25
0.3
Zero100 modes1 mode2 modes10 modes50 modes
ZFrequency (Hz)
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Helmholtz resonator, with extended neck
60 70 80 90 100 110 1200
5
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15
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30
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TL modèle mixteTL simplifié
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Simplified models : two openings
We consider a symmetric resonator connected to the main duct viatwo openings located at z = z1 and z = z2.
(
p1p2
)
=
(
Z11 Z12
Z12 Z11
)(
q1q2
)
Moreover,(
p1p2
)
=1
W
(
1 eikL
eikL 1
)(
q1q2
)
+
(
pI1pI2
)
where L = |z2 − z1|. This gives
T = 1 +2WZ11 − 2WZ12 cos(kL) + (e2ikL − 1)
(WZ11 − 1)2 − (WZ12 − eikL)2
Thus, no acoustic energy is transmitted if
Z 212 − Z 2
11 − A sin(kL)
kAdZ12 = 0
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Herschel-Quincke resonator
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Herschel-Quincke resonator
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30
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50
60
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80
TL simplifiéTL tube droitTL modèle mixte
Frequency (Hz)
TL(dB)
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Fan noise
Perforate sheet
The fan noise is one of the dominant components at take-offand landing for aircraft with modern high bypass ratioturbofan engines : broadband noise + Blade PassingFrequency (BPF) tones
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Fan noise
Actual configuration...
Soufflante
Redresseurs
Collecteur
Tube HQ
Model...
A+
A−
B+
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Validation on a small size configuration
0
0.1
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0.4−0.05 0 0.05 0.1
−0.1
−0.05
0
0.05
0.1
x (m) y (m)
z(m
)
0 500 1000 1500 2000 2500 30000
5
10
15
20
25
30
35
40
Frequency (Hz)
TL(dB)
Matrix size CPU time (Matlab)
Our model 500 1 h 50 min
FEM 82 000 31 h 15 min
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Optimal configuration (36 HQ tubes)
0 5 10 15 20 25 30 35 40 4586
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100
ka
SPL(dB)
0 5 10 15 20 25 30 35 40 450
2
4
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10
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ka
TL(dB)
Incident Liner-HQ system
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What does the liner do ?
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0
2
4
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Re(β0,n)
Im(β
0,n)
0 5 10 15 20 25 30 35 400
5
10
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35
40
45
Re(β20,n)
Im(β
20,n)
Surface wave modes at 1530 Hz :
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Influence of the number of tubes on the first BPF
(iso-surface)
Number of tubes
Modes
Modal
pow
er(dB)
72675545403736300 (Liner)0 (Incident)
(7,1)(4,2)
(8,1)(2,3)
(-5,2)(-9,1)
(-3,3)
30
50
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90
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Conclusions and prospects
The proposed Green’s function based method allows to reduce thecomputational effort as only the acoustic velocity at the interfaceneeds to be calculated.A very high number of propagative modes (few hundreds) can behandled easily on a single PC.Gives access to physical interpretation in the low-frequency regime.
In prospect : - could be used for designing taylor-made resonatorsusing optimization procedures. - viscosity effects should be included