SIST EN ISO 14163:1999
(Main)Acoustics - Guidelines for noise control by silencers (ISO 14163:1998)
Acoustics - Guidelines for noise control by silencers (ISO 14163:1998)
Akustik - Leitlinien für den Schallschutz durch Schalldämpfer (ISO 14163:1998)
Diese Internationale Norm befaßt sich mit der praktischen Auswahl von Schalldämpfern zur Lärmminderung in gasförmigen Medien. Sie legt die akustischen und betriebstechnischen Anforderungen fest, die zwischen dem Lieferanten oder Hersteller und dem Anwender eines Schalldämpfers zu vereinbaren sind. Diese Internationale Norm beschreibt die grundlegenden Wirkprinzipien, ist jedoch keine Anleitung für die Auslegung von Schalldämpfern.
Acoustique - Lignes directrices pour la réduction du bruit au moyen de silencieux (ISO 14163:1998)
Akustika - Smernice za varstvo pred hrupom z dušilniki (ISO 14163:1998)
General Information
Related Packages
Standards Content (Sample)
SLOVENSKI STANDARD
SIST EN ISO 14163:1999
01-november-1999
Akustika - Smernice za varstvo pred hrupom z dušilniki (ISO 14163:1998)
Acoustics - Guidelines for noise control by silencers (ISO 14163:1998)
Akustik - Leitlinien für den Schallschutz durch Schalldämpfer (ISO 14163:1998)
Acoustique - Lignes directrices pour la réduction du bruit au moyen de silencieux (ISO
14163:1998)
Ta slovenski standard je istoveten z: EN ISO 14163:1998
ICS:
17.140.01 $NXVWLþQDPHUMHQMDLQ Acoustic measurements and
EODåHQMHKUXSDQDVSORãQR noise abatement in general
SIST EN ISO 14163:1999 en
2003-01.Slovenski inštitut za standardizacijo. Razmnoževanje celote ali delov tega standarda ni dovoljeno.
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SIST EN ISO 14163:1999
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SIST EN ISO 14163:1999
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SIST EN ISO 14163:1999
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SIST EN ISO 14163:1999
INTERNATIONAL ISO
STANDARD 14163
First edition
1998-10-15
Acoustics — Guidelines for noise control
by silencers
Acoustique — Lignes directrices pour la réduction du bruit au moyen
de silencieux
A
Reference number
ISO 14163:1998(E)
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SIST EN ISO 14163:1999
ISO 14163:1998(E)
Contents
1 Scope .1
2 Normative references .1
3 Terms and definitions .2
4 Specification, selection and design considerations .4
4.1 Requirements to be specified .4
4.2 Selection and layout of silencers.4
4.3 Design of special silencers.5
5 Types of silencers, general principles and operational considerations .5
5.1 Overview.5
5.2 Acoustic and aerodynamic performance of silencers .7
5.3 Sound propagation paths .7
5.4 Acoustic installation effect .8
5.5 Abrasion resistance and protection of absorbent surfaces.9
5.6 Fire hazards and protection against explosion .9
5.7 Starting-up and closing-down of plants.9
5.8 Corrosion.9
5.9 Hygienic requirements and risk of contamination .9
5.10 Inspection and cleaning, decontamination.10
6 Performance characteristics of types of silencers.10
6.1 Dissipative silencers .10
6.2 Reactive silencers .22
6.3 Blow-off silencers .29
© ISO 1998
All rights reserved. Unless otherwise specified, no part of this publication may be reproduced or utilized in any form or by any means, electronic
or mechanical, including photocopying and microfilm, without permission in writing from the publisher.
International Organization for Standardization
Case postale 56 • CH-1211 Genève 20 • Switzerland
Internet iso@iso.ch
Printed in Switzerland
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SIST EN ISO 14163:1999
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ISO 14163:1998(E)
7 Measurement techniques . 30
7.1 Laboratory measurements . 30
7.2 Measurements in situ. 31
7.3 Measurements on vehicles. 31
8 Information on silencers. 31
8.1 Information to be provided by the user. 31
8.2 Information to be provided by the manufacturer . 32
Annex A (informative) Applications . 33
Annex B (informative) Effect of spectral distribution of sound on the declaration of attenuation
in one-third-octave or octave bands. 40
Annex C (informative) Operating temperatures of sound sources and temperature limits of
sound-absorbent materials. 42
Bibliography. 43
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SIST EN ISO 14163:1999
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ISO 14163:1998(E)
Foreword
ISO (the International Organization for Standardization) is a worldwide federation of national standards bodies (ISO
member bodies). The work of preparing International Standards is normally carried out through ISO technical
committees. Each member body interested in a subject for which a technical committee has been established has
the right to be represented on that committee. International organizations, governmental and non-governmental, in
liaison with ISO, also take part in the work. ISO collaborates closely with the International Electrotechnical
Commission (IEC) on all matters of electrotechnical standardization.
International Standards are drafted in accordance with the rules given in the ISO/IEC Directives, Part 3.
Draft International Standards adopted by the technical committees are circulated to the member bodies for voting.
Publication as an International Standard requires approval by at least 75 % of the member bodies casting a vote.
International Standard ISO 14163 was prepared by Technical Committee ISO/TC 43, Acoustics, Subcommittee
SC 1, Noise.
Annexes A to C of this International Standard are for information only.
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Introduction
Whenever airborne sound cannot be controlled at the source, silencers provide a powerful means of sound
reduction in the propagation path. Silencers have numerous applications and different designs based on various
combinations of absorption and reflection of sound, as well as on reaction on the sound source. This International
Standard offers a systematic description of principles, performance data and applications of silencers.
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SIST EN ISO 14163:1999
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SIST EN ISO 14163:1999
INTERNATIONAL STANDARD © ISO ISO 14163:1998(E)
Acoustics — Guidelines for noise control by silencers
1 Scope
This International Standard deals with the practical selection of silencers for noise control in gaseous media. It
specifies the acoustical and operational requirements which are to be agreed upon between the supplier or
manufacturer and the user of a silencer. The basic principles of operation are described in this International
Standard, but it is not a silencer design guide.
The silencers described are suitable, among others,
for attenuating system noise and preventing crosstalk in heating, ventilation and air-conditioning (HVAC)
equipment;
for preventing or reducing sound transmission through ventilation openings from rooms with high inside sound
levels;
for attenuating blow-off noise generated by high-pressure lines;
for attenuating intake and exhaust noise generated by internal combustion engines; and
for attenuating intake and outlet noise from fans, compressors and turbines.
They are classified according to their types, performance characteristics and applications. Active and adaptive
passive noise-control systems are not covered in detail in this International Standard.
2 Normative references
The following normative documents contain provisions which, through reference in this text, constitute provisions of
this International Standard. For dated references, subsequent amendments to, or revisions of, any of these
publications do not apply. However, parties to agreements based on this International Standard are encouraged to
investigate the possibility of applying the most recent editions of the normative documents indicated below. For
undated references, the latest edition of the normative document referred to applies. Members of ISO and IEC
maintain registers of currently valid International Standards.
ISO 3741, Acoustics — Determination of sound power levels of noise sources using sound pressures — Precision
methods for reverberation rooms.
ISO 3744, Acoustics — Determination of sound power levels of noise sources — Engineering methods for free-field
conditions over a reflecting plane.
ISO 7235, Acoustics — Measurement procedures for ducted silencers — Insertion loss, flow noise and total
pressure loss.
ISO 11691, Acoustics — Measurement of insertion loss of ducted silencers without flow — Laboratory survey
method.
ISO 11820, Acoustics — Testing of silencers in situ.
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3 Terms and definitions
For the purposes of this International Standard, the following terms and definitions apply.
3.1
silencer
device reducing sound transmission through a duct, a pipe or an opening without preventing the transport of the
medium
3.2
dissipative silencer
absorptive silencer
silencer providing for broad-band sound attenuation with relatively little pressure loss by partially converting sound
energy to heat through friction in porous or fibrous duct linings
3.3
reactive silencer
general term for reflective and resonator silencers where the majority of the attenuation does not involve sound
energy dissipation
3.4
reflective silencer
silencer providing for single or multiple reflections of sound by changes in the cross-section of the duct, duct linings
with resonators, or branchings to duct sections with different lengths
3.5
resonator silencer
silencer providing for sound attenuation at weakly damped resonances of elements
NOTE The elements may or may not contain absorbent material.
3.6
blow-off silencer
silencer used in steam blow-off and pressure release lines throttling the gas flow by a considerable pressure loss in
porous material and providing sound attenuation by lowering the flow velocity at the exit and reacting on the source
of the sound (such as a valve)
3.7
active silencer
silencer providing for the reduction of sound through interference effects by means of sound generated by
controlled auxiliary sound sources
NOTE Mostly low-order modes of sound in ducts are affected.
3.8
adaptive passive silencer
silencer with passive sound-attenuating elements dynamically tuned to the sound field
3.9
insertion loss,
D
i
difference between the levels of the sound powers propagating through a duct or an opening with and without the
silencer
NOTE 1 The insertion loss is expressed in decibels, dB.
NOTE 2 Adapted from ISO 7235.
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3.10
insertion sound pressure level difference
D
ip
difference between the sound pressure levels occurring at an immission point, without a significant level of
extraneous sound, without and with the silencer installed
NOTE 1 The insertion sound pressure level difference is expressed in decibels, dB.
NOTE 2 Adapted from ISO 11820.
3.11
transmission loss
D
t
difference between the levels of the sound powers incident on and transmitted through the silencer
NOTE 1 The transmission loss is expressed in decibels, dB.
NOTE 2 For standard test laboratories D equals D , whereas results for D and D obtained from in situ measurements may
t i t i
often differ due to limited measurement possibilities.
NOTE 3 Adapted from ISO 11820.
3.12
discontinuity attenuation
D
s
that portion of the insertion loss of a silencer or silencer section due to discontinuities
NOTE The discontinuity attenuation is expressed in decibels, dB.
3.13
propagation loss
D
a
decrease in sound pressure level per unit length which occurs in the midsection of a silencer with constant cross-
section and uniform longitudinal design, characterizing the longitudinal attenuation of the fundamental mode
NOTE The propagation loss is expressed in decibels per metre, dB/m.
3.14
outlet reflection loss
D
m
difference between the levels of the sound power incident on and transmitted through the open end of a duct
NOTE The outlet reflection loss is expressed in decibels, dB.
3.15
modes
spatial distributions (or transverse standing wave patterns) of the sound field in a duct that occur independently from
one another and suffer a different attenuation
NOTE The fundamental mode is least attenuated. In narrow and in lined ducts, higher-order modes suffer substantially
higher attenuation.
3.16
cut-on frequency
lower frequency limit for propagation of a higher-order mode in a hard-walled duct
NOTE 1 The cut-on frequency is expressed in hertz, Hz.
NOTE 2 In a duct of circular cross-section, the cut-on frequency for the first higher-order mode is f = 0,57c/C where c is the
cC
speed of sound and C is the duct diameter. In a rectangular duct with larger dimension H, f = 0,5c/H.
cH
3
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3.17
pressure loss
Δp
t
difference between the mean total pressures upstream and downstream of the silencer
NOTE 1 The pressure loss is expressed in pascals, Pa.
NOTE 2 Adapted from ISO 7235.
3.18
regenerated sound
flow noise
flow noise caused by the flow conditions in the silencer.
NOTE Sound power levels of regenerated sound and pressure losses measured in laboratory tests are related to a
laterally uniform flow distribution at the inlet of the silencer. If this uniform flow distribution is not attainable under in situ
conditions, for example because of the upstream duct design, higher levels of regenerated sound and higher pressure losses
will occur.
4 Specification, selection and design considerations
4.1 Requirements to be specified
4.1.1 In general, the sound pressure level (A-weighted, one-third-octave or full-octave) shall not exceed a specified
value at a specified position (e.g. at a work station, in the neighbourhood, or in a recreation room). The permissible
contribution from a sound source can then be determined in terms of the sound power level and the directivity index
of that source using sound propagation laws and requirements concerning the allocation of contributions to several
partial sound sources. The required insertion loss of the silencer is given by the difference between the permissible
and the actual sound power level of the source.
In simple cases where the sound immission is determined solely by the sound source to be attenuated, the
necessary insertion sound pressure level difference of the silencer can be calculated directly from the difference
between the permissible and the actual sound pressure level at the immission point. When the difference in
directivity indices with and without the silencer is negligible, the insertion sound pressure level difference equals the
insertion loss of the silencer.
4.1.2 The permissible pressure loss shall not be exceeded.
NOTE This requirement should be specified as clearly as possible. Instead of the imprecise specification "as small as
possible", a sensible limit value has to be found. Even if the pressure loss is considered as "not critical", a limit value should be
determined from the maximum permissible flow velocity that may not be exceeded for reasons of mechanical stability,
regenerated sound or energy consumption costs.
4.1.3 The permissible size of the silencer shall be kept as small as possible (for reasons of cost and weight).
NOTE There is a minimum size which (given the state of the art) cannot be reduced. This size depends on the required
reduction in sound level, the permissible pressure loss and on other restrictions concerning materials to be used (or avoided),
resistance to different kinds of stress, etc.
4.1.4 Additional requirements (concerning materials, durability, leakages, etc.) result from the application of the
silencer in hot, dusty, humid or aggressive gases, in pressure lines or for high sound pressure levels and vibration
levels, and from the combination of silencers with devices for the control of exhaust gas, sparks and particles.
4.2 Selection and layout of silencers
Specific information on silencers can be drawn from
laboratory measurements made in accordance with ISO 7235;
silencer manufacturers' test data;
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theoretical models to calculate propagation loss and insertion loss for silencers with circular or rectangular
cross-section;
pressure loss and regenerated sound prediction methods.
The selection of a dissipative, a reactive or a blow-off silencer will be determined by its application or by reference
to the experience presented in this International Standard.
Results obtained from computer programs for the insertion loss of dissipative silencers depend on the assumptions
made concerning the magnitude and distribution of airflow resistance in the silencer and the acoustical effect of the
cover [18]. Certain geometrical features like off-setting of splitters or subdividing of absorbers are not easily accessible
for calculation. Calculations are most accurate for parameter variations concerning design as well as operating
conditions. Effects of flow on the performance of reactive silencers are taken into account by special highly
sophisticated computer software.
4.3 Design of special silencers
The design of a special silencer is usually an iterative process featuring the following stages:
a) rough specification of the dimensions of free ducts for the flow and of connected spaces for the distribution of
sound, for example using the manufacturers' declarations for similar silencers and taking into account the
essential requirements and restrictions;
b) construction of a model for predictive calculation or measurements;
c) use of the model and comparison of the results with requirements concerning sound level reduction and
pressure loss;
d) change of dimensions and sound-absorbent materials to fulfil requirements or to optimize the design;
e) constructional consideration of special requirements.
5 Types of silencers, general principles and operational considerations
5.1 Overview
Silencers are used to
prevent pulsations and oscillations of the gas at the source,
reduce conversion of the pulsations and oscillations into sound energy, and
provide conversion of sound energy into heat.
Table 1 — Typical advantages and shortcomings of different types of silencers
Type of silencer Advantages Shortcomings
Dissipative silencer Broad-band attenuation, little pressure Sensitive to contamination and
loss mechanical destruction
Reactive silencers:
Resonator type Tuned attenuation, insensitive to Narrow-band attenuation, sensitive to flow
contamination
Reflective type Robust element, application for large Greater pressure loss, acoustic pass
pressure pulsations, high sound levels, bands (frequency bands with little or no
contaminated flow, strong mechanical attenuation), flow sensitivity of acoustical
vibrations performance
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The resulting insertion loss for a silencer mounted in a duct will in general depend on all three of these mechanisms.
According to the dominant attenuation mechanisms involved, silencers may be classified as (see table 1):
dissipative silencers,
reactive silencers, including resonator and reflective silencers,
blow-off silencers, and
active silencers.
5.1.1 Dissipative silencers
These provide broad-band sound attenuation by conversion of sound energy into heat with relatively little pressure
loss. Precautions shall be taken to prevent coating or clogging of the surface of the absorbent material when
dissipative silencers are used in ducts carrying gases contaminated with dust or encrusting material. Porous
absorbers made of fine fibrous material or thin-walled structures may be mechanically destroyed by high amplitudes
of alternating pressure.
5.1.2 Resonator silencers (reactive)
These reduce the conversion of gas pulsations and oscillations into sound energy and absorb sound. Single
resonators are mounted as side branches in duct walls. Groups of resonators are used as duct linings or splitter
elements (baffles) in ducts, thus causing a limited pressure drop. Resonances are mostly tuned to low and
intermediate frequencies, where attenuation is needed. The performance is limited to a narrow frequency band, is
sensitive to grazing flow and may (under certain unfavourable conditions) be negative so that a tone is generated.
5.1.3 Reflective silencers (reactive)
These reduce the conversion of gas pulsations and oscillations into sound energy. They are usually chosen for their
robustness in applications where purely dissipative silencers are less suitable, and where greater pressure loss is
permissible. This is the case, for example, with gas flows carrying dust, or with higher flow velocities and pressure
pulsations, and for applications with strong mechanical vibrations. The maximum attenuation and the frequency
where it occurs will be affected by the flow. It is possible that in some frequency bands only little or even negative
attenuation is encountered.
5.1.4 Blow-off silencers
These are mounted on steam and pressurized air release lines and are effective by reaction on the source of
sound, such as a valve, and by lowering the exit flow velocity through an expanded surface area while conversion of
sound into heat is usually of little significance. Large pressure losses require the silencer to have a good mechanical
stability. Its performance can be affected by material carried by the gas. There is also a danger of icing.
5.1.5 Active silencers
These mainly consist of speaker sets driven by amplifiers with input from suitable microphones. Control is effected
by a high-performance computer, the controller. These are specialist devices not dealt with in this International
Standard. Active silencers are most effective at low frequencies where passive dissipative silencers offer little
attenuation [32].
NOTE Active systems are presently offered exclusively as individual solutions tailored for particular applications and are
thus not discussed in this International Standard.
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5.2 Acoustic and aerodynamic performance of silencers
The attenuation required from a silencer is described in terms of the insertion loss, D, if no particular immission
i
point is defined, or in terms of the insertion sound pressure level difference, D , at a particular position. It is
i
p
specified in one-third-octave bands or full-octave bands. According to the laboratory standard ISO 7235, the
attenuation shall be measured in one-third-octave bands. Full-octave-band values may be calculated using
equation (1):
D
13/,k
3
−
1
10dB
D =− 10 (1)
10lg dB
1/1 ∑
3
k=1
where D to D are the attenuation values in the three one-third octaves of a full-octave band, in decibels, and
1/3,1 1/3,3
D is the resulting full-octave-band value. Declaring attenuation values in full octaves will suffice for broad-band
1/1
noise and for silencers with broad-band effect. For tonal noise and for resonator silencers with narrow band effect,
the attenuation data should be given in one-third-octave bands.
NOTE 1 Octave-band attenuation data may strongly depend upon the spectrum of the sound (see annex B).
A necessary parameter for the selection of a silencer is the permissible pressure loss in the flow. It shall not exceed
the total pressure loss Δp which depends on the mean flow velocity and density of the gas and on the flow condition
t
as described by equation (2):
ρ
2
ΔΔpv=+ζζ (2)
()
t1
2
where
ζ is the total pressure loss coefficient as defined in ISO 7235 for uniform flow conditions at both ends of the
silencer;
Δζ is the additional pressure loss coefficient due to flow conditions in situ deviating from the laboratory
conditions (values are to be estimated empirically);
3
r is the density of the gas, in kilograms per cubic metre, kg/m ;
v is the mean flow velocity in the inlet cross-section, in metres per second, m/s.
1
NOTE 2 It is common for definitions of the total pressure loss coefficient to differ from the one given in ISO 7235. It is
therefore necessary to check the definitions before using any values. For example, a different definition is the one considering
the flow velocity in the narrowest cross-section of the silencer instead of v . This will result in much lower values for ζ.
1
Other parameters to be considered which affect the acoustic and aerodynamic performance are
the regenerated sound,
the maximum dimensions available for the silencer, and
the necessary durability of the silencer under exposure to flow, pressure pulsations and mechanical vibration.
5.3 Sound propagation paths
It is possible for sound propagating from a source to an immission point to follow several paths beside the direct one
through the silencer (Figure 1, path 1). The additional paths are:
a) radiation from the housing of the source (path 2);
b) radiation from duct walls before the silencer (path 3);
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c) radiation from the shell of the silencer (path 4); and
d) propagation of structure-borne sound along and past the silencer (path 5).
Sound propagation along these flanking paths shall be prevented by providing housings and duct walls with
sufficient sound insulation and by inserting vibration isolation devices for interrupting the propagation path for
structure-borne sound.
Figure 1 — Sound propagation paths (schematic)
5.4 Acoustic installation effect
For certain applications and silencer types, the sound attenuation provided by a silencer depends on the
characteristics of the source connected to the inlet side and the characteristics of the termination connected to the
outlet side. Such an installation effect occurs especially on reactive silencers or on all types of silencers for low
frequencies.
It is also important that either the source or the termination is reactive, i.e. non-absorbing. When these conditions
are fulfilled, unfavourable resonance effects can be expected in the system that will lead to strong coupling between
different parts of the system. Formally, this type of installation effect can be described via equation (3):
LL=−D−D+E (3)
(rad) (source)
WW tm
where
(rad) is the level of sound power radiated from duct end, in decibels, dB,
L
W
L (source)is the level of sound power radiated from source into duct with anechoic termination, in decibels,
W
dB;
D is the transmission loss (see 3.11), in decibels, dB;
t
is the reflection loss at the duct outlet (see 3.14 and 6.2.2.2), in decibels, dB;
D
...
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