-
On the noise reduction mechanism of a flat plate
serrated trailing edge
Danielle J. Moreau1 and Con J. Doolan2
The University of Adelaide, South Australia, Australia 5005
This paper presents the results of an experimental investigation
exploring the noise re-
duction potential of sawtooth trailing edge serrations on a flat
plate at low-to-moderate
Reynolds number (1.6× 105 < Rec < 4.2× 105). Acoustic
measurements have been taken
using a flat plate with both sharp and serrated trailing edges
in an anechoic wind
tunnel. Trailing edge serrations are found to achieve reductions
of up to 13 dB in the
narrowband noise levels and this is mainly due to attenuation of
vortex shedding at
the trailing edge. Velocity data have also been measured in the
very near trailing edge
wake using hot-wire anemometry and these data are related to the
far-field noise mea-
surements to give insight into the trailing edge serration noise
reduction mechanism.
The results show that for this particular configuration, the
noise reduction mechanism
of trailing edge serrations is dominated by their influence on
the hydrodynamic field at
the source location. Therefore the assumption that the turbulent
field is unaffected by
the serrations is not valid and explains why theory is not able
to explain experimental
observations.
I. Introduction
Trailing edge noise is considered to be a major noise source in
many aerodynamic applications
for which sound production is problematic, such as fans, rotors,
propellers, wind turbines and
1 Postdoctoral Research Associate, School of Mechanical
Engineering, [email protected], AIAA mem-ber
2 Associate Professor, School of Mechanical Engineering,
[email protected], AIAA Senior member
1
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underwater vehicles [1–3]. Brooks et al. [4] classified airfoil
self-noise mechanisms into five categories
and showed that four of the five noise generation mechanisms are
due to the interaction of flow
disturbances with the trailing edge. Other studies [5, 6] have
shown that trailing edge noise levels
can be reduced by modifying the trailing edge geometry so that
flow disturbances are scattered
into sound with reduced efficiency. In [5] it is also noted that
other studies [7–9] have shown a
reduction in the radiated noise can be achieved with mechanisms
that reduce the correlation length
of turbulence near the trailing edge. Modifying the trailing
edge with the application of serrations
has been shown theoretically [5, 6], numerically [10, 11] and
experimentally [3, 12–21] to reduce the
trailing edge noise radiated into the far-field.
Howe [5, 6] derived an analytical noise radiation model for a
flat plate serrated trailing edge in
low Mach number flow. According to Howe’s [5, 6] theory,
trailing edge noise can be significantly
reduced with the addition of trailing edge serrations due to a
reduction in the effective spanwise
length of the trailing edge that contributes to noise
generation. Howe’s [5, 6] theory states that
the magnitude of this noise reduction is dependent on the height
and geometrical wavelength of the
serrations and on the frequency of sound. The sound generated by
large eddies whose length scales
are greater than the amplitude of the serrations (low frequency
sound) is unaffected by the presence
of the serrations and hence significant noise reductions are
only expected in the high frequency
region.
A number of experimental studies on trailing edge serrations
have examined their effect on full
scale wind turbine blades or wind tunnel scale airfoil models at
high Reynolds numbers (Rec >
5 × 105, based on chord) [3, 12–17]. Oerlemans et al. [3, 15]
investigated the reduction of trailing
edge noise from a NACA 64418 airfoil and the blades of a full
scale 2.3 MW wind turbine by
shape optimisation and the application of trailing edge
serrations. At high Reynolds numbers
(Rec ≈ 1.6 × 106), optimising the airfoil shape for low noise
emission and adding trailing edge
serrations achieved an average reduction of ∼ 6 dB in the
radiated noise levels over a variety of
flow conditions. Trailing edge serrations applied to a
full-scale wind turbine blade were found to
decrease noise levels by ∼ 3 dB at frequencies below 1 kHz and
increase the noise levels above this
frequency without any adverse effect on aerodynamic performance.
Gruber et al. [17] examined the
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noise reduction achieved with sawtooth serrations on a NACA
651-210 airfoil at Reynolds numbers
of 2.0× 105 < Rec < 8.3× 105 and found that noise
reductions of up to 7 dB were achieved at low
frequencies (< 2 kHz) and an increase in noise level was
observed at high frequencies. The frequency
delimiting a noise reduction and a noise increase was found to
correspond to a constant Strouhal
number of Stδ = 1, where Stδ is Strouhal number based on
boundary layer thickness.
Previous investigations on trailing edge serrations suggest they
are a valid means of airfoil self-
noise reduction. The mechanism responsible for this noise
reduction is, however, still unclear. Howe’s
model [6] provides some insight into the serration noise
reduction mechanism but all experimental
studies conducted on trailing edge serrations in the past have
reported some discrepancy between
their measurements and Howe’s theory. In all cases, the
predicted noise reduction levels far exceeded
those measured. In addition, contrary to Howe’s [6] theory,
trailing edge serrations on airfoils have
been found to produce a noise reduction at low frequencies and a
noise increase at high frequencies
[3, 13–17]. In deriving the serration noise reduction model,
Howe [6] made a number of assumptions
and approximations. One such assumption is that the surface
pressure frequency spectrum close
to the trailing edge is unchanged by the presence of trailing
edge serrations; however, a number
of experimental studies have speculated that this assumption is
inaccurate [14, 16]. This suggests
that there is a need to further investigate the physical
mechanisms by which trailing edge serrations
reduce airfoil self-noise.
This paper presents the results of an experimental study that
explores the noise reduction
potential of sawtooth trailing edge serrations on a flat plate
at low-to-moderate Reynolds number
(1.6 × 105 < Rec < 4.2 × 105). This experimental study has
relevance to applications employing
small sized airfoils such as small scale wind turbines, unmanned
air vehicles (UAVs) and computer
and automotive fans, all of which operate at lower Reynolds
numbers. Acoustic test data have been
measured for a flat plate with both sharp and serrated trailing
edges in an anechoic wind tunnel.
In addition, velocity data about the flat plate trailing edge
have been measured using hot-wire
anemometry, providing information on the turbulent noise
sources. The overall aims of this paper
are: (1) to present acoustic and flow data for two different
serration geometries at a variety of flow
speeds; (2) to compare experimental measurements with
theoretical noise reductions predicted using
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the theory of Howe [5, 6]; and (3) to investigate how serrations
affect noise production at the trailing
edge.
This paper is structured as follows: Section II presents the
theoretical background; the exper-
imental method is described in Section III; Section IV presents
the experimental results including
far-field acoustic data, comparison with the theoretical
predictions of Howe [6] and velocity spectra
in the wake; and the conclusion is given in Section V.
II. Theoretical background
Howe [6] derived an analytical model to predict the effect on
noise radiation of sawtooth serra-
tions at the trailing edge of a flat plate in low Mach number
flow. The acoustic pressure frequency
spectrum, Φ(x, ω), of a flat plate with a serrated trailing edge
at an observer location a distance |x|
from the trailing edge is given by [6]
Φ(x, ω)
(ρv2∗)2(l/c0)(δ/|x|)2
=
(
Cmπ
)
sin2(
θ
2
)
sin(α)Ψ(ω), (1)
where ρ is the fluid density, v∗ ≈ 0.03U∞, l is the plate span,
c0 is the speed of sound, δ is
the boundary layer thickness, Cm ≈ 0.1553, θ and α are the polar
and azimuthal observer angles
respectively, Ψ(ω) is the non-dimensional edge noise spectrum
and ω = 2πf , where f is the frequency.
The polar and azimuthal observer angles, θ and α, are defined
according to the co-ordinate system
of Fig. 1.
The serrated trailing edge investigated here has a root-to-tip
amplitude of 2h and wavelength of
λ, as shown in Fig. 2. The non-dimensional edge spectrum for the
serrated trailing edge is defined
as
Ψ(ω) =
(
1 +1
2ǫ∂
∂ǫ
)
f
(
ωδ
Uc,h
λ,h
δ; ǫ
)
, (2)
where
f
(
ωδ
Uc,h
λ,h
δ; ǫ
)
=1
AB + ǫ2
(
1 +64(h/λ)3(δ/h)
(
cosh(C√A+ ǫ2)− cos(2ωh/Uc)
)
(√A+ ǫ2)(AB + ǫ2) sinh(C
√A+ ǫ2)
)
, (3)
A = (ωδ/Uc)2, B = 1+ (4h/λ)2, C = λ/2δ and ǫ = 1.33. For the
case when h → 0, Eqs. (2) and (3)
reduce to the following non-dimensional edge spectrum for an
unserrated trailing edge
Ψ(ω) =A
(A+ ǫ2)2. (4)
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According to Howe’s [6] theory, when the acoustic frequency is
high such that ωh/U∞ >> 1,
the theoretical maximum reduction in radiated mean square
pressure is proportional to 10 log10[1+
(4h/λ)2] for serrations with a sawtooth profile. The largest
noise reductions occur when the dimen-
sions of the serrations are of the order of the turbulent
boundary layer thickness and when the angle
between the mean flow and the local tangent to the wetted
surface is less than 45◦. This suggests
that sharper serrations with a smaller wavelength to amplitude
ratio, λ/h, will result in greater
noise reduction.
x
z
y
Trailing edge
Plate
Observer x
Fig. 1 Flat plate co-ordinate system.
Flow
2h
Tip of sawtooth
Root of sawtooth
Plate
Fig. 2 Sawtooth serrations at the trailing edge of a flat plate
with root-to-tip amplitude of 2h
and wavelength of λ.
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III. Experimental method
A. Anechoic wind tunnel facility
Experiments were performed in the anechoic wind tunnel at the
University of Adelaide. The
anechoic wind tunnel test chamber is 1.4 m × 1.4 m × 1.6 m
(internal dimensions) and has walls
that are acoustically treated with foam wedges to approximate a
free environment at frequencies
above 250 Hz. The facility contains a contraction outlet that is
rectangular in cross-section with
dimensions of 75 mm x 275 mm. The maximum flow velocity of the
free jet is ∼ 40 m/s and the
free-stream turbulence intensity is 0.33% [22].
B. Test model
The flat plate model used in this study is composed of a main
steel body and a detachable
trailing edge plate made from brushed aluminum, as shown in Fig.
3. The main body has a span of
450 mm and a thickness of 6 mm. The leading edge (LE) of the
main body is elliptical with a semi-
major axis of 8 mm and a semi-minor axis of 3 mm while the
trailing edge (TE) is asymmetrically
bevelled at an angle of 12◦. Three 0.5 mm thick trailing edge
plates were used (one at a time):
one with a straight, unserrated configuration and two with
serrations. The flat plate model with
the straight unserrated trailing edge is used as the reference
configuration for all tests and so will
be referred to as the reference plate hereafter. Two different
serration geometries are compared
in this study, both with root-to-tip amplitude of 2h = 30 mm:
one with a wavelength of λ = 3
mm (λ/h = 0.2, termed narrow serrations) and the other with λ =
9 mm (λ/h = 0.6, termed wide
serrations). The root of the serrations is aligned with the
trailing edge of the main body so that only
the serrated component of the trailing edge plate is exposed to
the flow. The area of the reference
plate is equivalent to that of the flat plate with serrated
trailing edges giving the same effective
wetted surface area in all three test cases. The serrated and
reference plate models all have the
same mean chord of 165 mm.
The trailing edge plate is fastened to the main body with 24 M2
× 0.4 screws. These screws
protruded slightly (< 0.4 mm) into the flow below the lower
flat surface of the plate model; however,
this was consistent for all three plate configurations. Hot-wire
measurements within the boundary
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3 mm
8 mm
LE
TE
0.5 mm
12
Main body
Trailing edge plate
Fig. 3 Schematic diagram of the flat plate model.
layer on the lower flat surface of the plate downstream of the
screws confirmed that any flow
disturbances created at the screws dissipated well before the
trailing edge. The method of trailing
edge attachment used in this study avoids bluntness at the root
of the serrations that may produce
vortex shedding and a tonal noise component. The flat plate
model was held between two side plates
and attached to the contraction at zero angle of attack as shown
in Fig. 4. The span of the flat
plate models extends beyond the width of the contraction outlet
to eliminate the noise produced by
the interaction of the side plate boundary layers with the model
leading edge.
In a previous study by the authors [23], the noise produced by
two different reference plate
models (with straight trailing edge) were compared. One plate
had a span equal to the width of
the contraction outlet (275 mm) and was held between two side
plates that were aligned with the
contraction edges. The second plate had a span of 450 mm as
shown in Fig. 4. The noise radiated
by the two plates was found to be highly comparable over the
entire frequency range of interest
(250 Hz - 10 kHz) indicating that the dominant source of noise
is turbulent boundary layer trailing
edge noise. It is also worth mentioning that in another study
[22], the authors have experimentally
analyzed the cross-correlation of noise measured above the
leading and trailing edges of the reference
plate at U∞ = 15 − 38 m/s to show that trailing edge noise
significantly dominates the radiated
sound field over the noise produced at the leading edge.
C. Measurement techniques
Unless otherwise stated, acoustic measurements were recorded at
a single observer location using
a B&K 1/2" microphone (Model No. 4190) located 554 mm
directly below the trailing edge of the
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Fig. 4 The flat plate model with wide trailing edge serrations
held between the side plates
and attached to the contraction outlet.
reference plate. The accuracy in the microphone sound pressure
level is ±1 dB based on its free field
response (as stated in the transducer documentation). Hot-wire
anemometry was used to obtain
unsteady velocity data in the wake of the serrated and reference
plate models. A TSI 1210-T1.5
single wire probe with wire length of L = 1.27 mm and a wire
diameter of d = 3.81 µm was used in
experiments. The sensor was connected to a TSI IFA300 constant
temperature anemometer system
and positioned using a Dantec automatic traverse with 6.25 µm
positional accuracy. The traverse
allowed continuous movement in the streamwise (x), spanwise (y)
and vertical (z) directions. The
co-ordinate system used in this study is shown in Fig. 1. The
origin of the co-ordinate system is
located at the centre of the trailing edge of the reference
plate.
Experiments were conducted at zero angle of attack and at
free-stream velocities between
U∞ = 15 and 38 m/s corresponding to Reynolds numbers, Rec = 1.6
× 105 and 4.2 × 105, respec-
tively. Acoustic and flow data were recorded for each flat plate
model using a National Instruments
PCI-4472 board at a sampling frequency of 5 × 104 Hz for a
sample time of 8 s and 4 s, respec-
tively. Data are presented in either one-third-octave band or
narrowband format with a frequency
resolution of 8 Hz. Narrowband spectra have been calculated
using Welch’s averaged modified
periodogram method of spectral estimation with a Hamming window
function and 75% overlap.
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According to Bendat and Piersol [24], the 95% confidence
interval on the narrowband autospectral
density is therefore -0.74/+0.81 dB/Hz for the acoustic
measurements and 10−0.1/100.1 m2/s for
the velocity measurements. One-third-octave band spectra have
been calculated using a filter bank
from time series data. Mean velocity profiles at the flat plate
trailing edge are also presented and
the uncertainty in the mean velocity is less than 7% for a 95%
confidence interval [24].
IV. Experimental results
A. Acoustic data
1. Reference plate acoustic spectra
The far-field acoustic spectra for the reference plate with a
straight trailing edge at free-stream
velocities between U∞ = 15 and 38 m/s are shown in Fig. 5. This
figure shows a clear trend with
broadband noise levels decreasing for a reduction in flow
velocity. This is particularly evident at
lower frequencies (< 1 kHz) where high noise levels are
measured. In addition, a broad peak is
observed in the noise spectra at high frequencies (at 8.5 kHz
for U∞ = 38 m/s) and this peak
reduces in frequency and amplitude with decreasing flow
speed.
Frequency, kHz
Spe
ctra
l den
sity
, dB
re
(20
µPa)
2 /H
z
0.3 1 100
20
40
60
8038 m/s35 m/s30 m/s25 m/s20 m/s15 m/s
Fig. 5 Far-field acoustic spectra for the reference plate with a
straight trailing edge at flow
speeds of U∞ = 15− 38 m/s.
The high frequency peak observed in the reference plate noise
spectra in Fig. 5 is attributed
to vortex shedding from the trailing edge. According to Blake
[1], narrowband blunt trailing edge
vortex shedding noise is negligible if the trailing edge is
sufficiently sharp such that the bluntness
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parameter t/δ∗ < 0.3 where t is the thickness of the trailing
edge and δ∗ is the boundary layer
displacement thickness. While the boundary layer properties have
not been directly measured at all
flow speeds in this study, they can be approximated using the
expressions for a turbulent boundary
layer at zero pressure gradient on a flat plate as follows
[25]
δ = 8δ∗, (5)
and
δ
c=
0.37
Re1/5c
, (6)
where δ is the boundary layer thickness and c is the plate
chord. Table 1 shows the flat plate
boundary layer properties and bluntness parameter calculated
using Eqns. (5) and (6) at flow speeds
between U∞ = 15 and 38 m/s. The mean velocity profile for the
reference plate at U∞ = 38 m/s is
presented later in Section IV B 2 and shows good agreement with
the estimated boundary properties
given in this table. As stated in Table 1, the bluntness
parameter t/δ∗ > 0.3 for all free-stream
velocities between U∞ = 15 and 38 m/s indicating that narrowband
noise contributions due to blunt
trailing edge vortex shedding can be expected.
The centre frequency, fc, of the vortex shedding peak in the
noise spectra (see Fig. 5) and the
associated Strouhal number based on trailing edge thickness, Stt
= fct/U∞, are also given in Table
1. Between U∞ = 15 and 38 m/s, the vortex shedding peak occurs
at a Strouhal number of between
0.08 and 0.11. This is in agreement with the findings of Herr
and Dobrzynski [26] who also reported
flat plate blunt trailing edge vortex shedding noise to occur at
Stt ≈ 0.1.
2. Noise reduction achieved with trailing edge serrations
Figure 6 shows the narrowband far-field acoustic spectra for the
reference plate and the two
plates with trailing edge serrations at free stream velocities
of U∞ = 15 and 38 m/s. The background
noise spectra are also shown in these figures for comparison.
Figure 6 shows that both serration
geometries reduce the high frequency trailing edge vortex
shedding noise component. Reductions of
up to 13 dB are achieved at frequencies where trailing edge
vortex shedding noise is dominant.
For clearer comparison, Figs. 7 and 8 show one-third-octave band
spectra for the reference plate
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Table 1 Flat plate boundary layer properties and centre
frequency, fc, and Strouhal number,
Stt, of the trailing edge vortex shedding noise peak for U∞ =
15− 38 m/s.
U∞, m/s δ, mm δ∗, mm t/δ∗ fc, Hz Stt = fct/U∞
38 4.7 0.53 0.84 8540 0.11
35 4.8 0.60 0.82 7750 0.11
30 5.0 0.62 0.80 6680 0.11
25 5.2 0.64 0.77 4900 0.10
20 5.4 0.67 0.74 3980 0.10
15 5.7 0.71 0.70 2530 0.08
Frequency, kHz
Spe
ctra
l den
sity
, dB
re
(20
µPa)
2 /H
z
0.3 1 100
20
40
60
80ReferenceNarrow serrationsWide serrationsBackground
(a)
Frequency, kHz
Spe
ctra
l den
sity
, dB
re
(20
µPa)
2 /H
z
0.3 1 100
20
40
60
80ReferenceNarrow serrationsWide serrationsBackground
(b)
Fig. 6 Far field acoustic spectra for the reference plate and
the plates with trailing edge
serrations compared to background noise levels at U∞ of (a) 38
and (b) 15 m/s.
and the flat plate with trailing edge serrations at flow speeds
between U∞ = 15 and 38 m/s. In
Figs. 7 and 8, the one-third-octave band spectra have been
normalised according to
Lp1/3norm = Lp1/3 − 50 log10(M)− 10 log10(δb/r2), (7)
where Lp1/3 is the far-field acoustic spectra in
one-third-octave bands, M is free-stream Mach
number, δ is the boundary layer thickness given in Table 1, b is
the length of the wetted span and r
is the radial distance from the reference plate trailing edge to
the observer location. The normalised
one-third-octave band spectra in Figs. 7 and 8 are plotted
against Strouhal number based on trailing
edge boundary layer thickness, Stδ = fδ/U∞.
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The one-third-octave band spectra at all flow speeds in Fig. 7
show that the narrow serrations
slightly reduce broadband noise levels by up to 2.5 dB at low
frequencies (R1). In the mid-frequency
range, a minor noise increase of up to 3 dB is observed with
narrow serrations (R2). In the high
frequency region, narrow serrations produce a significant noise
reduction of up to 10 dB in the
trailing edge vortex shedding noise component (R3).
The one-third-octave band spectra for the reference plate and
the flat plate with wide serrations
are shown in Fig. 8. This figure shows that at all flow speeds
between U∞ = 15 and 38 m/s, the
wide serrations attenuate broadband noise levels by up to 3 dB
at low frequencies (R1). In the
mid frequency range, wide serrations have little affect on the
radiated noise with the noise levels
of the reference plate and the flat plate with wide serrations
being approximately equal (R4). At
high frequencies, the wide serrations significantly attenuate
the trailing edge vortex shedding noise
component by up to 10 dB (R3).
For both serration geometries in Figs. 7 and 8, the regions of
noise attenuation (R1 and R3)
reduce in frequency and amplitude with decreasing flow speed.
Comparing Figs. 7 and 8 shows that
wide serrations outperform the narrow ones by achieving higher
levels of low frequency attenuation
over a larger frequency range and no noise increase in the mid
frequency region.
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R1 R2 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceNarrow serrations
(a)
R1 R2 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceNarrow serrations
(b)
R1 R2 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceNarrow serrations
(c)
R1 R2 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceNarrow serrations
(d)
R1 R2 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceNarrow serrations
(e)
R1 R2 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceNarrow serrations
(f)
Fig. 7 Normalised one-third-octave band spectra for the
reference plate and the plate with
narrow serrations at U∞ of (a) 38, (b) 35, (c) 30, (d) 25, (e)
20 and (f) 15 m/s. R1: region
of noise reduction, R2: region of noise increase, R3: region of
noise reduction in the blunt
trailing edge vortex shedding component and R4: region of
equivalent noise levels.
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R1 R4 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceWide serrations
(a)
R1 R4 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceWide serrations
(b)
R1 R4 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceWide serrations
(c)
R1 R4 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceWide serrations
(d)
R1 R4 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceWide serrations
(e)
R1 R4 R3
Stδ
Lp1/
3 no
rm, d
B r
e 20
µP
a
0.1 1110
120
130
140
150ReferenceWide serrations
(f)
Fig. 8 Normalised one-third-octave band spectra for the
reference plate and the plate with
wide serrations at U∞ of (a) 38, (b) 35, (c) 30, (d) 25, (e) 20
and (f) 15 m/s. R1: region
of noise reduction, R2: region of noise increase, R3: region of
noise reduction in the blunt
trailing edge vortex shedding component and R4: region of
equivalent noise levels.
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3. Variation in noise reduction with Strouhal number
Figure 9 shows 2D surface plots of the measured attenuation
achieved with the trailing edge
serrations at flow speeds between U∞ = 15 and 38 m/s. The
attenuation in these figures has been
calculated by dividing the power spectral density of the
serrated plates by that of the reference plate.
Three separate regions of noise reduction are identifiable in
the attenuation maps in Fig. 9 and each
of these regions is bounded by a constant Strouhal number based
on boundary layer thickness at
the trailing edge, δ. For narrow serrations in Fig. 9 (a):
• Stδ < 0.13 : Region of noise attenuation (R1).
• 0.13 < Stδ < 0.7 : Region of noise increase (R2).
• 0.7 < Stδ < 1.4 : Region of attenuation in the blunt
trailing edge vortex shedding noise
component (R3).
For wide serrations in Fig. 9 (b):
• Stδ < 0.2 : Region of noise attenuation (R1).
• 0.2 < Stδ < 0.7 : Region of equivalent noise levels
(R4).
• 0.7 < Stδ < 1.4 : Region of attenuation in the blunt
trailing edge vortex shedding noise
component (R3).
In their experiments on a NACA 651-210 airfoil with trailing
edge serrations, Gruber et al.
[17] found that for a range of serration geometries (λ/h = 0.1 −
0.6) the frequency delimiting a
noise reduction and a noise increase followed a constant
Strouhal number dependency of Stδ = 1.
This Strouhal number scaling does not describe the trends
observed in the flat plate data in Fig. 9.
Discrepancies in the Strouhal number scaling are attributed to
significant differences in the geometry
of the airfoil used in the study of Gruber et al. [17] and the
flat plate studied here.
4. Noise directivity
Figure 10 shows the sound pressure level directivity pattern for
the reference plate and the
plates with trailing edge serrations at three selected one-third
octave band centre frequencies at
15
-
(a) (b)
Fig. 9 Noise reduction achieved with (a) narrow serrations and
(b) wide serrations at U∞ =
15 − 38 m/s. Dashed lines are lines of constant Strouhal number,
Stδ. R1: region of noise
reduction, R2: region of noise increase, R3: region of noise
reduction in the blunt trailing
edge vortex shedding component and R4: region of equivalent
noise levels.
U∞ = 38 m/s. To obtain these measurements, the microphone was
fastened to the traverse arm and
the traverse was then used to position the microphone at a
number of locations on an arc at a radial
distance of 300 mm from the trailing edge of the reference
plate. The measurements in Fig. 10 have
been corrected to account for shear layer refraction [27].
At the one-third-octave band centre frequency of 0.4 kHz, Fig.
10 (a) shows that both serration
geometries slightly reduce the noise levels of the reference
plate (region R1 in Figs. 7 (a) and 8 (a))
at all angular locations, with the wide serrations outperforming
the narrow ones. In Fig. 10 (b)
at 2 kHz, the wide serrations produce equivalent noise levels to
the reference plate (region R4 in
Fig. 8 (a)) while a noise increase is observed with the narrow
serrations (region R2 in Fig. 7 (a)) at
all angular locations. At 8 kHz in Fig. 10 (c), both serration
geometries significantly attenuate the
trailing edge vortex shedding noise component (region R3 in
Figs. 7 (a) and 8 (a)) at all angular
locations.
Figure 10 shows that the trailing edge serrations do not
significantly modify the directivity of
the radiated trailing edge noise and that their effect on the
radiated noise is independent of observer
position. This was found to be the case at all one-third-octave
band frequencies, whether a noise
reduction occurred or not.
16
-
180°
210°
240° 270°
300°
330°
0°
40
60
80
ReferenceNarrow serrationsWide serrations
(a)
180°
210°
240° 270°
300°
330°
0°
40
60
80
ReferenceNarrow serrationsWide serrations
(b)
180°
210°
240° 270°
300°
330°
0°
40
60
80
ReferenceNarrow serrationsWide serrations
(c)
Fig. 10 Trailing edge noise directivity pattern for the
reference plate and the plates with
trailing edge serrations for U∞ = 38 m/s at one-third-octave
band centre frequencies of (a)
0.4, (b) 2 and (c) 8 kHz. Dashed circular contours denote the
sound pressure level in dB.
Note that the origin is 20 dB. An angular position of 180◦
relates to a position upstream of
the trailing edge at x = −300 mm, y = 0, z = 0, 270◦ relates to
a position directly below the
trailing edge at x = 0, y = 0, z = −300 mm and 0◦ relates to a
position downstream of the
trailing edge at x = 300 mm, y = 0, z = 0.
5. Comparison with theory
Figure 11 shows 2D surface plots of the noise reduction
predicted with Howe’s [6] theory as
presented in Section II for the two different serration
geometries used in this study. The predicted
attenuation in Fig. 11 has been calculated by dividing the edge
spectra of the serrated plates (Eqs. (2)
and (3)) with that of the reference plate (Eq. (4)). The
oscillations in the theoretical noise reduction
map for narrow serrations in Fig. 11 (a) are due to interference
between acoustic radiation produced
at the root and the tip of the serrations.
17
-
(a) (b)
Fig. 11 Noise reduction for (a) the narrow serrations and (b)
the wide serrations predicted
with the theory of Howe [6] at U∞ = 15− 38 m/s. Note the
differing colorbar scales.
The experimental measurements in Fig. 9 do not agree with Howe’s
theory (Fig. 11) in terms of
absolute noise levels or in terms of the variation in noise
reduction with flow velocity and frequency.
Compared with measured attenuation levels, the theoretical noise
reduction predictions are much
higher and occur over a much larger frequency range at all flow
velocities considered in this study.
In addition, some attenuation is measured at low frequencies
contrary to Howe’s model that predicts
noise reductions to occur only at high frequencies (ωh/U∞
>> 1). This is however, in agreement
with a number of other experimental studies that have found
trailing edge serrations to attenuate
low frequency airfoil self-noise [13, 14, 16, 17].
According to Howe [6], the serration geometry determines the
magnitude of the noise reduction.
The theoretical maximum attenuation in the radiated mean square
pressure (in dB) is 10 log10(1 +
(4h/λ)2) for serrations with a sawtooth profile. The noise
reduction is therefore expected to increase
as λ/h decreases. For the narrow serrations with λ = 3 mm, the
maximum attenuation is predicted
to be 26 dB while for the wide serrations with λ = 9 mm, the
maximum theoretical attenuation is
17 dB. As shown in Fig. 11, narrow serrations are predicted to
clearly outperform wide serrations in
terms of the level of attenuation achieved at all frequencies
and flow speeds. In this study however,
wide serrations were found to achieve higher attenuation levels
than narrow serrations which actually
cause a slight noise increase in the mid frequency range (see
Figs. 7 - 9). While contrary to Howe’s
[6] theory, this does agree with the experimental findings of
Chong et al. [18, 19] who found wider
18
-
serrations to be the more effective in reducing tonal
instability noise at low Reynolds numbers.
B. Velocity data
As the turbulent flow field about the trailing edge is the
source of trailing edge noise, velocity
measurements in the near wake of the straight and serrated
trailing edges are examined in this
section to gain insight into the mechanism by which serrations
affect noise production. While
velocity measurements are presented at the selected flow speed
of U∞ = 38 m/s only, measurements
at all other flow speeds follow the same trend.
1. Mean velocity profiles
Figure 12 shows the variation in mean velocity (U/U∞) measured
in the vertical (z) direction
with downstream (x) distance for the reference plate and the two
plates with trailing edge serrations
at U∞ = 38 m/s. As shown in this figure, the mean velocity
profiles for the three trailing edge
geometries differ significantly indicating that trailing edge
serrations alter the flow structure in the
near wake. Greater wake flow deflection is observed for the
serrated trailing edges compared to the
reference plate and this deflection increases with decreasing
serration wavelength.
According to Michel’s criteria [25], transition from laminar to
turbulent flow occurs when the
Reynolds number based on momentum thickness, Reθ, exceeds a
value of
Reθtr = 1.174
(
1 +22400
Rec
)
Re0.46c , (8)
where Rec is Reynolds number evaluated at distance c. For all
three plates, the profiles measured
1 mm downstream of the trailing edge (at x/c = 0.006 for the
reference plate and x/c = 0.1 for
the plates with trailing edge serrations) satisfy Michel’s
criteria of Reθ > Reθtr. Additionally, the
profiles all have a shape factor of H = 1.2 - 1.4 above and
below the trailing edge indicating that
the trailing edge flow is well developed and turbulent on both
surfaces of all three plates.
2. Velocity spectra
Figures 13 and 14 show spectral maps of the fluctuating velocity
(u′2/Hz) measured in the
spanwise (y) and vertical (z) directions in the near wake of the
plate with straight and serrated
19
-
−0.04 −0.02 0 0.02 0.04
0.4
0.5
0.6
0.7
0.8
0.9
1
z/cU
/U∞
0.0060.100.120.150.21
(a)
−0.04 −0.02 0 0.02 0.040.5
0.6
0.7
0.8
0.9
1
z/c
U/U
∞
0.100.120.150.21
(b)
−0.04 −0.02 0 0.02 0.04
0.5
0.6
0.7
0.8
0.9
1
z/c
U/U
∞
0.100.120.150.21
(c)
Fig. 12 Normalised mean velocity profiles in the wake measured
in the vertical (z) direction
at various downstream (x/c) locations at U∞ = 38 m/s for (a) the
reference plate, (b) the plate
with narrow serrations and (c) the plate with wide serrations.
The profiles in (b) and (c)
have been measured in line with the peak of a serrated
tooth.
trailing edges at U∞ = 38 m/s. In these figures, the velocity
spectral maps are plotted against
Strouhal number based on width of the wake, Stlw, where the
width of the wake, lw, for each
plate has been calculated from the velocity profiles in Fig. 12.
A small ridge can be seen in all
velocity spectral maps at approximately Stlw ≈ 2. This is due to
a slight dip or “notch” in the hot-
wire anemometer frequency response which does not affect the
conclusions drawn from the velocity
measurements.
The spectra for all three plates in Figs. 13 and 14 show high
energy levels at low frequencies.
20
-
This corresponds to the high levels of low frequency trailing
edge noise measured in the far-field at
U∞ = 38 m/s (see Fig. 6 (a)). The high levels of low frequency
energy are likely due to eddies or
convected flow perturbations in the boundary layer as it
negotiates the adverse pressure gradient on
the top beveled surface of the plate. This is evidenced by the
spectral maps in Fig. 14 which shows
slightly higher energy levels on the top surface of the plates
near the trailing edge than in the region
below the trailing edge.
(a)
(b) (c)
Fig. 13 Velocity spectral maps in the wake measured in the
spanwise (y) direction from
centre span at z/c = 0 at U∞ = 38 m/s for (a) the reference
plate, (b) the plate with narrow
serrations and (c) the plate with wide serrations. The spectral
map in (a) has been measured
at a position of x/c = 0.006 which corresponds to 1 mm
downstream from the trailing edge of
the reference plate. The spectral maps in (b) and (c) have been
measured at x/c = 0.1 which
corresponds to 1 mm downstream from the serrated trailing edge
and a position of y/c = 0
corresponds to the peak of a serrated tooth.
21
-
(a)
(b) (c)
Fig. 14 Velocity spectral maps in the wake measured in the
vertical (z) direction at centre
span at U∞ = 38 m/s for (a) the reference plate, (b) the plate
with narrow serrations and (c)
the plate with wide serrations. The spectral map in (a) has been
measured at a position of
x/c = 0.006 which corresponds to 1 mm downstream from the
trailing edge of the reference
plate. The spectral maps in (b) and (c) have been measured at
x/c = 0.1 which corresponds to
1 mm downstream from the serrated trailing edge, in line with
the peak of a serrated tooth.
The spectral maps measured in the spanwise direction in the near
wake of the two plates with
serrated trailing edges in Figs. 13 (b) and (c) show features
that occur due to flow interaction with
the serrations. Higher levels of turbulent energy are measured
at locations that correspond to the
tip of a serrated tooth. This is to be expected as the
measurement locations are physically closer
to the model at the tip of a serrated tooth, thus are closer to
an attached boundary layer and its
more energetic, small scale turbulence, compared with
measurements taken in the space between
two serrated teeth, where the probe is relatively far away from
the attached boundary layer and can
22
-
be considered to be in a wake. Figure 13 shows that the trailing
edge serrations affect the flow field
in the vicinity of the trailing edge which is the source of the
trailing edge noise in Fig. 6 (a).
The spectral maps for the reference plate in Figs. 13 (a) and 14
(a) support the theory that
vortex shedding at the trailing edge is the source of the broad
high frequency peak in the reference
plate noise spectra (see Fig. 5). High energy velocity
fluctuations at frequencies corresponding to
those of the broad peak in the reference plate noise
measurements are observed along the span and
close to the trailing edge of the reference plate in Figs. 13
(a) and 14 (a) respectively. These high
energy velocity fluctuations are however, not observed in the
spectral maps for the flat plate with
serrated trailing edges (see Figs. 13 (b) and (c) and 14 (b) and
(c)). This agrees with the noise
spectra in Fig. 6 (a) which shows that serrations attenuate the
vortex shedding noise component.
The vertical spectral map for the plate with narrow serrations
in Fig. 14 (b) shows higher energy
turbulent fluctuations at mid frequencies (Stlw = 0.16 − 1.6
corresponding to 600 Hz - 6 kHz) on
the top surface of the plate at the trailing edge compared to
the reference plate. This corresponds
to noise measurements in Fig. 7 (a) which shows the narrow
serrations increase noise in the mid
frequency region. The spectral map for the wide serrations does
not display these high energy
mid frequency fluctuations (see Fig. 14 (c)) and
correspondingly, no mid frequency noise increase is
observed for this trailing edge geometry (see Fig. 8 (a)).
The velocity measurements in Figs. 12 - 14 show that trailing
edge serrations alter the behaviour
of the flow field about the trailing edge and this directly
affects noise production. As stated earlier,
Howe’s [6] serration noise reduction model was derived assuming
that the surface pressure frequency
spectrum close to the trailing edge is unchanged by the presence
of trailing edge serrations. As the
surface pressure spectrum at the trailing edge is driven by the
velocity field, the near wake velocity
measurements in Figs. 13 and 14 indicate that the pressure
frequency spectrum close to the trailing
edge will be altered by the presence of trailing edge
serrations. This helps explain the considerable
theoretical over-prediction of noise reduction observed in this
and many other experimental studies
[13, 14, 16, 17]. The results suggest that for this particular
configuration (Reynolds number range
and serration and test model geometry), the effect of serrations
on noise production is dominated by
changes in the hydrodynamic field rather than changes in the
diffraction properties of the trailing
23
-
edge.
V. Conclusion
This paper has presented results of an experimental
investigation of the acoustic and aero-
dynamic effects of trailing edge serrations on a flat plate at
low-to-moderate Reynolds number.
Trailing edge serrations were found to minimise broadband noise
levels at low frequencies (by up
to 3 dB at the reference measurement location) and achieve
significant attenuation (of up to 13 dB
at the reference measurement location) of blunt vortex shedding
noise at high frequencies without
modifying the directivity of the radiated noise. The noise
reduction achieved with trailing edge
serrations was found to depend on Strouhal number, Stδ = fδ/U∞,
and serration wavelength.
Theoretical predictions of the noise reductions using the theory
of Howe [6] were in poor agree-
ment with experimental data. Contrary to theory, wide serrations
with larger wavelength to ampli-
tude ratio, λ/h, were found to outperform narrow ones by
achieving higher attenuation levels and
no noise increase in the mid frequency region.
Unsteady velocity data in the very near wake of the straight and
serrated trailing edges suggested
that for this particular configuration, the noise reduction
capability of trailing edge serrations is
related to their influence on the hydrodynamic field at the
source location rather than on a reduction
in sound radiation efficiency at the trailing edge. Hence the
assumption that serrations don’t affect
the turbulence field [6] appears to be invalid and explains the
considerable differences observed
between experimental measurements and theoretical
predictions.
Acknowledgments
This work has been supported by the Australian Research Council
under grant DP1094015 ‘The
mechanics of quiet airfoils’.
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26