HVAC Applications
The Challenge
Building design and construction must
include engineering controls for HVAC
equipment to limit objectionable noise and
vibration levels. Meeting the acoustical
expectations of building owners and occupants
has become increasingly difficult
with today's lightweight construction methods
and with HVAC systems that are located
in close proximity to occupied spaces
and listener critical environments.
BProper design and effective use of noise
and vibration control materials are required
to avoid system problems. QWYATT has the
practical experience using proven and tested
materials to quiet mechanical systems in
new design and remedial construction
projects. There is no cost or obligation to
consult with us on your next project.
HVAC System Problems
Noise and vibration problems in HVAC
applications are rarely caused solely by the
ventilation equipment. Most such
complaints are system problems relating to
the lack of integration of all system components.
Improper selection, design or installation
can result in system problems despite
the use of duct silencers, sound absorptive
duct liners and other common noise and
vibration treatments.
Correction Vs. Prevention
Correcting a noise or vibration problem
after start-up of the HVAC system costs much
more than addressing the potential problems
at the design stage. Short cuts to save on
construction costs may result in real costs far
exceeding the monetary cost in direct
payments to the retrofitting contractors. The
opportunity costs of time lost in the investigation,
analysis and implementation of a solution
and the loss of goodwill from the building
owner and/or tenants are also part of the real
costs. The cost of prevention to incorporate
sufficient noise controls and integrate all of the
system components into a quiet design has
been estimated at as little as 1% of total HVAC
system costs. The benefits of prevention more
than justify this small incremental increase in
project costs.
Typical "System" Problems For A Common Air Handling Application
Are Shown Above And Described In More Detail Below
- AHU panel vibration "couples" to the
lightweight, flexible gypsum wall just a
few inches away. This coupling lets low
frequency noise pass easily through the
wall.
- The counterclockwise rotation of the fan's
discharge air is forced to change direction
at the downstream elbow. The change in
the direction at the elbow causes turbulence
resulting in excessive low frequency
noise, duct rumble and pressure drop.
- Problem 2 is aggravated if the elbow's
turning vanes do not have long trailing
edges to straighten the air flow and control
the turbulence.
- The sound trap is too close to the elbow.
This compounds the turbulence problem.
- Rectangular ductwork and sound traps do
not control the rumble produced by turbulent
air flow.
- The AHU's air inlet is too close to the wall.
This causes two acoustical problems:
unstable fan operation leading to surge
and rumble, and direct exposure of the
inlet noise to the mechanical room wall.
- The lack of a sound trap in a mechanical
room return air opening allows fan noise
to travel into the ceiling cavity, then
through the lightweight acoustical ceiling
into the occupied space.
- The unit is resting on thin cork/neoprene
isolation pads that are too stiff to adequately
isolate the fan vibration.
- The poorly isolated unit is resting on a
relatively flexible floor slab without sufficient
structural support. This arrangement
allows unit vibration to enter the slab.
- The chilled water piping is rigidly attached
to the slab above, thereby letting unit
vibration enter the slab.
- Ductwall vibration in the sound trap (or
any other part of the trunk duct system)
touching the drywall partition can cause
the partition to act as a sounding board
and radiate low frequency noise into the
occupied space.
- Suspending the ceiling from the supply
duct causes it to be a sound radiator.
Acoustical Rating Systems And Criteria
Many single number rating systems and
criteria have been developed to quantify and
describe HVAC system noise in buildings and
occupied spaces. Examples of these rating
systems include A-weighted decibels (dBA),
loudness levels (Sones), room criteria (RC) and
noise criteria (NC). Most commonly, engineers
and consultants today are using the NC rating
system in specifications and when evaluating
noise situations. The NC curves and rating
system are described in more detail below.
They were derived from equal loudness curves
consistent with human hearing frequency
response. The NC system, like any rating criteria,
has its own set of assumptions and limiting
conditions. Building occupants agree that the
NC curves have a spectrum shape that sounds
too rumbly and hissy. Momentum is gathering
in the engineering community to adopt the
NCB (Noise Criteria Balanced) system, but
standard NC methods remain the single most
widely accepted rating system.
Noise Criteria
(NC) Curves
Standardized NC curves are
plotted at left along with frequency
spectrum data for a particular room
application. The NC-45 rating for
the example, at left, is determined
by comparing the plotted data to
the standardized curves and finding
the highest penetration which in
this case is the tangent point on the
NC-45 curve at 125 Hz (60 dB).
The A curve represents the approximate
threshold of hearing for
continuous noise. The NC rating
system should be used with caution
in evaluating environments with
dominant low frequency levels as
the standardized curves do not
extend down into the 16 Hz and
31.5 Hz octave bands.
Another caution/limitation of
this system is the inability to differentiate
the subjective quality of the
noise for equivalent rating values.
Recommended NC Levels For Various Activities
Broadcast studios (distant microphone pickup used) | 10 |
Concert halls, opera houses, and recital halls
(listening to faint musical sounds) | 15-18 |
Small auditoriums | 25-30 |
Large auditoriums, large drama theatres, and large
churches (for very good speech articulation) | 20-25 |
TV and broadcast studios
(close microphone pickup only) | 15-20 |
Legitimate theatres | 20-25 |
Private residences: |
Bedrooms | 25-30 |
Apartments | 30-40 |
Family rooms and living rooms | 30-40 |
Schools: |
Lecture and classrooms |
with areas less than 70 sq. m. | 35-40 |
with areas greater than 70 sq. m. | 30-35 |
Open-plan classrooms | 35-40 |
Hotels/motels: |
Individual rooms or suites | 30-35 |
Meeting/banquet rooms | 25-35 |
Service support areas | 40-50 |
Churches, small | 30-35 |
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Office buildings: |
Offices |
executive | 25-35 |
small, private | 35-40 |
larger, with conference tables | 30-35 |
Conference rooms |
large | 25-30 |
small | 30-35 |
General secretarial areas | 40-45 |
Open-plan areas | 35-40 |
Business machines/computers | 40-45 |
Public circulation | 40-50 |
Hospitals and clinics: |
Private rooms | 25-30 |
Wards | 30-35 |
Operating rooms | 25-35 |
Laboratories | 35-45 |
Corridors | 35-45 |
Public areas | 40-45 |
Movie theatres | 30-40 |
Courtrooms | 30-35 |
Libraries | 35-40 |
Restaurants | 40-45 |
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Detailed procedures
for calculating HVAC
system noise levels to meet
a desired NC design goal
are outlined in various
trade reference guides and
technical publications.
Please refer to the chapters
entitled "Sound and
Vibration Fundamentals" in
the ASHRAE Fundamentals
Handbook and "Sound and
Vibration Control" in the
ASHRAE Systems and
Applications Handbook for
more details. The short
form at left is available in
full format upon request.
Operating conditions and
fan sound power levels
must be predetermined.
Simple form sample worksheet for system
design calculations.
Calculation | Source | Octave Band/Center Frequency (Hz) |
1/63 | 2/125 | 3/250 | 4/500 | 5/1K | 6/2K | 7/4K | 8/8K |
1. Room design goal NC. | | | | | | | | | |
2. Room attenuation. | | | | | | | | | |
3. Multiple outlet effect. | | | | | | | | | |
4. End reflection attenuation. | | | | | | | | | |
5. Branch power division. | | | | | | | | | |
6. Elbow attenuation, noise
source to outlet. | | | | | | | | | |
7. Duct attenuation, noise source to outlet. | | | | | | | | | |
8. Terminal unit correction. | | -3 | -3 | -3 | -3 | -3 | -3 | -3 | -3 |
9. Allowable PWL at fan discharge. | Total Lines 1-8 | | | | | | | | |
10. Actual PWL at fan discharge. | Fan Mfr's Data | | | | | | | | |
11. Dynamic insertion loss (DIL) required. | Subtract Line 9
from Line 10 | | | | | | | | |
12. DIL of selected silencer.
QWYATT DUCT MODEL______
Face velocity_____fpm. | QWYATT DUCT
Performance
Tables | | | | | | | | |
13. Silencer air flow generated
noise PWL at___fpm.
Include air flow generated noise
correction factor where required. | QWYATT DUCT
Performance
Tables | | | | | | | | |
14. Attenuated fan PWL at
silencer discharge. | Subtract Line 12
From Line 10 | | | | | | | | |
15. Resultant PWL at silencer discharge
(compare with Line 9). | Combine Lines
13 & 14. | | | | | | | | |
Regenerated Noise: HVAC Designer Enemy #1
Medium and high velocity air flow impinging
on any obstruction will cause disturbance
of the air flow. The resultant turbulence
produces regenerated noise. HVAC duct
design components such as elbows, turning
vanes, dampers, transitions, offsets, take-offs,
tees, etc. are examples of such obstructions.
The turbulence in most air flow systems is
characterized by sharp changes in the air flow
path, sharp bends, abrupt cross-sectional area
changes, etc. in contrast to aerodynamic fan
noise which manifests itself in a more tonal
frequency spectrum at the fan blade passage
frequency. Turbulence and regenerated noise
are generally characterized by a broad band
frequency spectrum. Turbulence increases
noise levels and system operating costs.
Regenerated noise can be minimized by
ensuring smooth air flow conditions.
SMACNA duct design and construction guidelines
should be incorporated in all job specifications
and drawings. The SMACNA guidelines
also outline optimal duct silencer locations
and guidelines for centrifugal fan installations
(distances for placement of duct
fittings).
The Design/Planning Phase
Postponing the acoustical design until
the end of the working drawings phase
does not allow for proper integration of all
components to ensure the system design
goals are met. The use of duct silencers,
acoustical lining and insulation and vibration
isolators if not integrated into the
system or if improperly implemented can
reduce the system performance (noise
reduction) and in some cases cause additional
noise or vibration problems. This
explains why today, despite the increased
use of acoustical equipment and materials,
noise and vibration problems persist. Noise
and vibration control design should start
during the schematic and design development
phases and continue throughout the
entire design process.
About Vibration Isolation
The chart at right helps define amplification,
isolation and resonance. The vertical axis
shows transmissibility while the horizontal
axis shows the ratio of the disturbing frequency
(fd) to the natural frequency of the isolator
system (fn). Resonance results when sympathetic
vibrations reinforce each other because
the disturbing frequency is equal to the isolator
natural frequency (the fd/fn ratio equals
one). Below a ratio of one we are in the region
of amplification. Above a ratio of one we are
still in the region of amplification until the
ratio equals the square root of two. Above this
point we begin the region of isolation because
less energy is coming out of the isolator
compared to what is going in. As a rule of
thumb a ratio of ten to one is desirable for
effective vibration isolation. A ratio below
three to one is not generally recommended.
The chart at left graphically illustrates the static
deflection required of a vibration isolation
mounting to limit the transmission of vibration to
a given percentage of the total vibratory force of
the equipment. The chart also suggests the maximum
permissible transmissibility for various
conditions encountered in machinery/equipment
installations. To use the chart, determine the
lowest rotational speed of the equipment and
consider this as the disturbing frequency. Move
vertically to the slanted line corresponding to the
% of transmissibility which can be tolerated. Then
move horizontally to the left to determine the
natural frequency and static deflection required of
the isolators. Finally, refer to the QWYATT
MOUNTTM product section and select the isolator
type with the corresponding static defection. The
efficiency chart models a single degree of freedom
system. Other factors may affect the final selection.
QWYATT sales engineers are ready to review your
applications.
What Are Seismic Loads?
Seismic Loads are the forces exerted on a structure
during an earthquake. Every structure is designed
for vertical, or gravity loads. In the case of ducts or
pipes, gravity loads include the weight of the ducts or
pipes and their contents, and the direction of the
loading is downward. The ordinary supports designed
for gravity loads generally take care of the vertical
loads imposed during an earthquake. Therefore, the
primary emphasis in seismic design is on lateral, or
horizontal forces. However, since vertical loads
contribute to any overturning, they are included in
seismic analysis.
What Happens During An
Earthquake?
A fault is a fracture in the earth's crust, and an
earthquake results from slippage along the fault
plane. Any structure straddling the fault line will
probably suffer damage, no matter how well it has
been designed. However, most effects of earthquakes
are not directly on the fault line. This is because the
movement caused by the slippage creates waves in
the earth that travel away from the fault plane. These
waves change throughout the duration of the earthquake,
add to one another, and result in extremely
complex wave motions and vibrations. The direction
of forces on structures can be horizontal, vertical, or
rotational. In terms of the way they may affect a given
building, they are not only unpredictable in direction,
they are also unpredictable in strength and duration.
The structural load is proportional to the intensity of
shaking and to the weight of the supported elements.
How To Resist Seismic Loads
The general principle in resisting seismic loads
is that we want equipment, ducts, and piping to
resist seismic forces by the strength of their attachment
to the building's structure. Naturally, we must
assume that the building has been designed to
perform safely in response to earthquake motions.
So that they remain intact and functioning, we want
equipment, ducts and pipes to move with the building
during an earthquake and not break away from
their supports. Therefore, the restraints are sized to
insure the chances of keeping these systems
attached to the structure.
Kinds Of Bracing
Because we cannot predict the directionality of seismic
forces, it is important to restrain equipment and brace
piping and ductwork in several directions. Floor mounted
equipment is typically restrained by use of a seismic
isolator or restraint which keeps the equipment captive.
If the equipment does not require vibration isolators,
properly sized anchor bolts can be used to seismically
restrain the unit. In order to restrain ducts and pipes
against seismic forces, longitudinal (in the direction of
their run) and transverse (perpendicular to their run)
bracing together with their vertical support will resist
lateral loads from any direction. All in-line equipment
must be braced independently of the ducts or pipes.
Angle Bracing vs. Cable
Restraints
When suspended equipment, piping or duct is hung
using spring or rubber vibration isolators, cables are
required for seismic restraint so as not to short circuit or
bypass the isolators. Angle bracing can be used when
piping and duct is hard mounted to the structure.
General Requirements For
Seismically Restraining Ducts
Rectangular ducts with cross-sectional areas of 6
square feet and larger, and round ducts with diameters of
28 inches or larger generally require seismic restraint. No
bracing is required if the duct is suspended by hangers 12
inches or less in length. Bracing of ductwork shall be at
30 foot intervals, at each turn and at each end of a duct
run.
General Requirements For
Seismically Restraining Pipe
All piping of 2.5 inches nominal diameter and larger
requires seismic restraint. All piping located in boiler
rooms, mechanical equipment rooms, and refrigeration
mechanical rooms that have a nominal diameter of 1.25
inches and larger require restraints. Fuel oil piping and
gas piping (fuel gas, medical gas, compressed air) of 1
inch nominal diameter and larger require seismic
restraint. No bracing or restraint is required for piping
suspended by individual hangers 12 inches or less.
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