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Basics of Sound and Noise David Herrin, Ph.D., P.E. University of Kentucky
Department of Mechanical Engineering
Introductions
Noise and Vibration Short Course
Dept. of Mech. Engineering University of Kentucky
2
University of Kentucky
Ø Public University Ø 16 Colleges Ø 93 Undergraduate Programs Ø 99 M.S. Programs Ø 66 Ph.D. Programs Ø 28,000 Students
Introductions
Noise and Vibration Short Course
Faculty Ø D. W. Herrin, Ph.D., P.E. Ø T. W. Wu, Ph.D. Students Ø Yitian Zhang (Ph.D.) Ø Gong Cheng (Ph.D.) Ø Kangping Ruan (Ph.D.) Ø Peng Wang (Ph.D.) Ø Keyu Chen (Ph.D.) Ø Weiyun Liu (Ph.D.) Ø Wanlu Li (M.S.) Ø Shishuo Sun (M.S.) Ø Huangxing Chen (M.S.)
Vibro-Acoustics Group
3 Dept. of Mech. Engineering University of Kentucky
Small Engines / Generator Sets Ø BASCO Ø Kohler Corp. Sound Absorbing Materials Ø 3M Company Ø American Acoustical Products Ø Blachford Inc. Ø Commercial Vehicle Group Ø Federal Foam Technologies Ø Insul-Coustic Corp. Ø Technicon Acoustics Inc. Others Ø Bechtel Marine Propulsion Corporation Ø Ebco Inc. Ø General Electric Appliances Ø Lexmark International
HVAC and Refrigeration Industry Ø Emerson Climate Ø Ingersoll Rand Trane Ø JCI York Ø Transicold Carrier Heavy Equipment Industry Diesel Engines Ø Caterpillar Inc. Ø Cummins Inc. Ø Deere and Company Ø Southwest Research Institute Ø Universal Silencers Automotive Supplier / Motorcycle Ø Dana Corp. Ø Eaton Corp. Ø Harley-Davidson Motor Co. Ø Mann+Hummel Group
Vibro-Acoustics Consortium
Introductions
Noise and Vibration Short Course
Dept. of Mech. Engineering University of Kentucky
5
Structural Dynamics Lab
Introductions
Noise and Vibration Short Course
Dept. of Mech. Engineering University of Kentucky
6
Hemi-Anechoic Chamber
Introductions
Noise and Vibration Short Course
Dept. of Mech. Engineering University of Kentucky
7
Acoustic Materials Characterization
ABSORPTION COEFFICIENT FOR SINGLE AND DOUBLE LAYER ABSORBING MATERIALS
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1.00
0 200 400 600 800 1000 1200 1400 1600 1800 2000FREQUENCY (Hz)
ALP
HA
Double layerSingle layer
Introductions
Noise and Vibration Short Course
8
Sound and Vibration Fields
Sound and vibration waves are mechanical elastic waves, and thus the conditions for their existence are that the medium possess mass and elasticity (i.e., stiffness). If a mass particle is displaced from its equilibrium position, the elastic forces will seek to return it to its original position. The particle influences the surrounding particles and in this way, a disturbance (i.e., wave) propagates through the medium.
Wallin et al. Longitudinal Transverse
Dept. of Mech. Engineering University of Kentucky
Wallin, Carlsson, Åbom, Bodén, and Glav, Sound and Vibration, 2nd Edition, Marcus Wallenberg Laboratoriet, Stockholm, 2011.
Introductions
Noise and Vibration Short Course
Dept. of Mech. Engineering University of Kentucky
9
Wave Motion – Some Basics
Sound waves are pressure disturbances in fluids, such as air, caused by vibration, turbulence, explosions, etc.
These disturbances propagate at the speed of sound c (c = 343 m/s or 1125 ft/s in air at room temperature)
The wavelength λ = c/f. For f = 1 kHz, the wavelength is approximately 0.34 m or 1.13 ft.
As a sound wave passes a point, the fluid particles are displaced but return to their original position until the next wave passes.
Wave animation
Introductions
Noise and Vibration Short Course
10
Sound and Vibration Fields
An acoustic field implies a small disturbance. Sound pressure disturbances are only on the order of 1 Pa for 94 dB.
Dept. of Mech. Engineering University of Kentucky
Wallin, Carlsson, Åbom, Bodén, and Glav, Sound and Vibration, 2nd Edition, Marcus Wallenberg Laboratoriet, Stockholm, 2011.
Introductions
Noise and Vibration Short Course
Dept. of Mech. Engineering University of Kentucky
11
Particle Motion
Particles oscillate (but no net flow) Waves move much faster than particles Surface displacement determines particle displacement and resulting sound pressure, as well as frequency
Particle displacement amplitude D
ftDtd π2sin)( =
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Noise and Vibration Short Course
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12
Particle Velocity
Particle displacement amplitude D
( ) ftfDtu ππ 2cos2)( =
Particle velocity amplitude (m/s)
u increases with frequency for a constant displacement
Particle velocity is like current, sound pressure like voltage
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13
Field Quantities
un = velocity of surface in normal direction – must be known
p, u = sound pressure and particle velocity in the field.
How do we determine
these?
Numerical Acoustics
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14
Sound Intensity and Power pu ,
Sound intensity is the sound power radiated per unit area
To get sound power, we integrate the normal component of the sound intensity over a closed surface
puI =
dSIWS n∫=
I
(watts)
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15
An Analogy
Like temperature, the sound pressure depends on the source power level AND the environment in which the source is placed.
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16
Another Analogy
A light bulb produces the same optical power (in watts) regardless of its environment – big or small room – but the intensity of light depends on the environment (reflectance of the walls) and the distance from the light bulb.
A sound source produces the same sound power (in watts) regardless of its environment* – big or small room – but the intensity of sound and the sound pressure depend on the environment (reflectance of the walls) and the distance from the source.
_____ * There are some notable exceptions to this (exhaust noise, close fitting enclosures)
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17
Plane waves in a duct
λ Oscillating Piston un
Special Cases 1. Plane Waves with no reflection
( ) uzucpuu
oo
n
==
+=
ρ
shift phase a zo = characteristic impedance
ISWcp
cpppuI
oo
=
=⎟⎟⎠
⎞⎜⎜⎝
⎛==
ρρ
2
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Noise and Vibration Short Course
Dept. of Mech. Engineering University of Kentucky
18
2. In the far field* of a source in a free field
p, u
Special Cases
* The far field is where the SPL decreases by 6 dB for a doubling of the distance to the source
cp
cppI
cup
oo
o
ρρ
ρ2
=⎟⎟⎠
⎞⎜⎜⎝
⎛=
=
(like plane waves in a duct except the sound pressure decreases with distance)
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Addition of Sound Sources
Combining Acoustic Sources
ptot t( ) = pn t( )n=1
N
∑
19
For Two Sources
ptot2 =
1T
ptot2 t( )dt
0
T
∫ =1T
p1 t( )+ p2 t( )( )2dt
0
T
∫ =
= p12 + p2
2 +2T
p1 t( ) p2 t( )dt0
T
∫
Dept. of Mech. Engineering University of Kentucky
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Noise and Vibration Short Course
Uncorrelated Sources
20
ptot2 = p1
2 + p22 ++ pn
2
Addition by Sound Pressure Level
p2 = pref2 10Lp /10
ptot2 = p1
2 + p22 = pref
2 10Lp1 /10 +10Lp2 /10( )Lptot
=10 log 10Lp1 /10 +10Lp2 /10( )In general
Lptot=10 log 10Lpn /10
n=1
N
∑
Dept. of Mech. Engineering University of Kentucky
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Example
21
A sound source causes a sound pressure level of Lp1 at a certain point. What increase in SPL is provided by a second source, equal in strength to, but uncorrelated to, the first?
Lptot=10 log 10Lp1/10 +10Lp1/10( ) =10 log 2 10Lp1 /10( )= Lp1 +10 log 2( ) = Lp1 +3 dB
Dept. of Mech. Engineering University of Kentucky
Introductions
Noise and Vibration Short Course
Example
22
A machine causes a SPL of 90 dB at a certain point while the background noise is 83 dB. What is the SPL of the machine with the background noise removed.
ptot2 = pM
2 + pB2
pM2 = ptot
2 − pB2
LpM=10 log 10Ltot /10 −10LpB /10( ) = 89 dB
Dept. of Mech. Engineering University of Kentucky
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Adding Frequency Components
23
ptot2 = pn
2
n=1
N
∑
Lptot=10 log 10Lpn /10
n=1
N
∑
The 1000 Hz octave band includes the 800, 1000, and 1250 Hz third-octave bands. Determine the octave band level if the third-octave band levels are 79, 86 and 84 dB, respectively.
Lptot=10 log 107.9 +108.6 +108.4( )
n=1
N
∑
Dept. of Mech. Engineering University of Kentucky
Introductions
Noise and Vibration Short Course
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24
Sound Power Level: watts101 log10)dB( 1210
−×== refref
w WWWL
Sound Pressure Level:
Those Amazing dB’s
The main thing to remember is that 100 dB sound pressure level and 100 dB sound power level are completely different!
To avoid confusion, use the reference values:
100 dB (re 20 µPa) sound pressure level 100 dB (re 1x10-12 W) sound power level
Pa 20 log10)dB( ref
2
ref
rms10 µ=⎟⎟
⎠
⎞⎜⎜⎝
⎛= p
ppLp
Introductions
Noise and Vibration Short Course
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25
r
r
But they are related…
I
(no reflections)
SLL Wp 10log10−= S in m2
24 rS π= (Spherical source) 22 rS π= (Hemi-spherical source)
S = cross-sectional area (duct)
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26
A source has a sound power level of 90 dB (re 10-12 W). What is the sound pressure level at a distance of 10 m in (a) a free field, (b) in a hemispherical free field, and (c) in a duct of cross-sectional area 1 m2?
An Example
( ) Pa)20(redB59104log90 210 µπ =−=pL
The image cannot be displayed. Your computer may not have enough memory to open the image, or the image may have been corrupted. Restart your computer, and then open the file again. If the red x still appears, you may have to delete the image and then insert it again.
The image cannot be displayed. Your computer may not have enough memory to open the image, or the image may have been corrupted. Restart your computer, and then open the file again. If the red x still appears, you may have to delete the image and then insert it again.
a.
b.
c.
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Two Vacuums
Shopvac Bosch
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Bosch Vacuum
Exhaust flows through foam
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Shopvac Vacuum
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Sound Power
(Watts) SIW Σ=)(W/mIntensity Sound Avg 2=I
)(m Area Surface 2=S
Exhaust Deflected Upward
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Time and Frequency Domains
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Sound Power Comparison – Bosch, All Sides
10
20
30
40
50
60
70
80
0 1000 2000 3000 4000 5000
Frequency (Hz)
Sou
nd P
ower
(dB
)
Front LeftBack RightTop Total
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Noise and Vibration Short Course
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33
Sound Power Comparison – Narrow Band
10
20
30
40
50
60
70
80
0 1000 2000 3000 4000 5000Frequency (Hz)
A-W
eigh
ted
Soun
d Po
wer
(dB)
Bosch w/ Foam (77.6 dBA)
Bosch w/o Foam (81.2 dBA)
Shopvac (85.0 dBA)
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Sound Power Comparison at Low Frequency
Low Frequency Tone
10
20
30
40
50
60
70
80
100 200 300 400 500
Frequency (Hz)
A-W
eigh
ted
Sou
nd P
ower
(dB
)
Bosch w/ Foam
Bosch w/o Foam
Shopvac
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35
Sound Power Comparison – 1/3 Octave
40
45
50
55
60
65
70
75
80
100 1000 10000
Frequency (Hz)
A-W
eigh
ted
Soun
d Po
wer
(dB)
Bosch w/ Foam (77.6 dBA)
Bosch w/o Foam (81.2 dBA)
Shopvac (85.0 dBA)
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Sound Quality
Bosch (original) Bosch (w/o foam)
Shopvac Bosch (w/o 1st peak)
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Sound Quality: Jury Test
Note: Rate each vacuum on a scale from 1 to 10 where 1 is “very quiet” and 10 is “very loud.”
5.74
7.70 8.00
4.61
0123456789
10
BOSCH Foam BOSCH NoFoam
Other Vacuum BOSCH No 1stPeak
Ave
rage
Rat
ing
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Foam Inside Bosch Vacuum
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Sound Absorption Coefficient
20 1
incidentenergy soundabsorbedenergy sound R−==α
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Sound Absorption Coefficient of Foam
0
0.2
0.4
0.6
0.8
1
0 1000 2000 3000 4000Frequency (Hz)
Abso
rptio
n C
oeffi
cien
t
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Sound Intensity (Shopvac)
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Sound Intensity (Bosch)
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Sound Intensity (Bosch)
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Summary
q Absorption of foam in BOSCH significantly reduces sound power
q Sound exhaust is better directed on BOSCH
q Recommend altering design to reduce/shift first peak