Greenheck Fan Corporation certifies
that the backward inclined and airfoil
centrifugal fans shown herein are
SOUND
R
AIR
MOVEMENT
AND CONTROL
ASSOCIATION
INTERNATIONAL, INC.
and
AIR
PERFORMANCE
licensed to bear the AMCA Seal. The
ratings shown are based on tests and
procedures performed in accordance with
AMCA Publication 211 and Publication
311 and comply with the requirements of
the AMCA Certified Ratings Program.
®
Our Warranty
Greenheck warrants this equipment to be free from defects
in material and workmanship for a period of one year from
the shipment date. Any units or parts which prove defective
during the warranty period will be replaced at our option
when returned to our factory, transportation prepaid. Motors
are warranted by the motor manufacturer for a period of one
year. Should motors furnished by Greenheck prove defective
during this period, they should be returned to the nearest
authorized motor service station. Greenheck will not be
responsible for any removal or installation costs.
As a result of our commitment to continuous improvement, Greenheck
reserves the right to change specifications without notice.
Aided Product Selection program, CAPS. Online, you can
also find electronic copies of our product literature as
well as storage, installation and maintenance information
in our Installation and Operation Manuals.
And, of course, you can always count on the personal
service and expertise of our national and international
representative organization. To locate your nearest
Greenheck representative call 715-359-6171 or visit our
Web site at www.greenheck.com
To-Scale Drawings and Fan Specifications
To-scale CAD drawings along with detailed centrifugal
specifications can be found online at greenheck.com or
within our Computer Aided Product Selection program
(CAPS).
Computer Aided
Product Selection
Program — CAPS
All Greenheck products
are supported by the
industry’s best product
literature, electronic
media, and Computer
®
2
Engineering Data
The model number codes on this page are a complete guide to ordering or specifying Greenheck Class IV centrifugal fan models.
Motor Selection
Greenheck centrifugal fans can be supplied with any motor that is commercially available, and appropriate for the fan size
and performance required. The tables show motor frame sizes corresponding to those motors readily available.
Notes: 1. Fractional horsepower motor frame sizes shown may change due to variations in voltage, special features and
2. Motors shown are ball bearing, continuous duty. Two speed motors are two winding, 1/3 reduction in RPM.
Discharge Position
TH = Top Horizontal TAU = Top Angular Up
BH = Bottom Horizontal BAU = Bottom Angular Up
UB = Upblast TAD = Top Angular Down
DB = Downblast BAD = Bottom Angular Down
3
®
Engineering Data
Motor Starting Torque
When selecting a motor for an industrial process fan, the motor
must be capable of driving the fan at operating speed and also
capable of accelerating the fan wheel, shaft and drive to the
operating speed.
The fan performance tables and curves in this catalog show the
brake horsepower required to operate the fan once it is brought to
operating speed. For applications requiring a large air volume at a
low static pressure, the BHP required at the fan’s operating RPM
may not be sufficient to initially start the fan. If the time required to
bring the fan to speed is excessive, the motor winding insulation
can be damaged due to excessive temperature rise and the life of
the motor seriously affected.
For a belt drive industrial process fan, the required motor starting
torque capability can be expressed by the following formula:
2
WR
M
2
WR
M
2
WR
F
FRPM =
MRPM =
2
F
x
(
FRPM
MRPM
= WR
The moment of inertia that the motor must be
=
capable of turning at the motor shaft, lb-ft
The moment of inertia of the fan wheel, lb-ft
=
Fan RPM
Motor RPM
)
2
x (1.1)
2
2
V-Belt Drives
Constant Speed Drives
Advantages of constant speed drives include low vibration levels,
ease of assembly and low cost. Fan speed changes can be
accomplished in most cases simply by changing the motor pulley.
Constant speed drives are recommended over variable speed
drives for applications that require motors 15 HP and larger, and all
applications requiring 3600 RPM motors.
Variable Speed Drives
Variable speed drives allow the fan speed to be changed by
adjusting the pitch diameter of the motor pulley. The power to the
fan must be off and locked out, and the belts must be removed
before manually adjusting the variable pitch pulley.
Moments of Inertia (lb-ft2)
Moments of inertia are shown for steel wheels. Aluminum wheels
are one-third of the value shown.
Fan
Size
Steel Backward Inclined
Centrifugal Wheels
Class IClass IIClass IIIClass IClass IIClass III
122.22.73.8––—
133.14.35.6––—
155.46.17.8––—
167.98.910.5––—
1812.513.818.916.923.914.6
2017.319.135.223.438.121.6
2232.032.052.338.857.231.6
2444.249.471.354.178.244.1
2766.279.196.985.512972.9
30105136144139178113
33152198210234261165
36260303399362428273
40435505628582665426
44642863927842955612
499711310138013001450935
54176021202130210024301570
60285034803700318035302390
66465050705350455052903400
73695075707950686078605070
Steel Airfoil
Centrifugal Wheels
Fan RPM Limitations
The maximum allowable wheel RPM shown on the fan performance
pages are for fans of standard steel operating at 70°F. Since the
strength of the fan wheel, shaft and bearings decreases with an
increase in temperature, maximum allowable speeds must be
reduced by the correction factors shown below.
Maximum RPM Correction Factors For High Temperatures
Temperature
(°F)
701.001.001.00
2001.00.97.92
AluminumSteel316 SS
Wheel Material
High Temperature Operating Limits
TemperatureMaterialArrangementOptions Included
-20
to
180°F
®
Steel
Aluminum
Stainless Steel
3None
4
Engineering Data
Inlet Vane Performance
As inlet vanes are closed, they impart a spin to the airflow in the direction of wheel rotation and reduce airflow, static pressure and brake
horsepower as shown in the graphs below. The graphs show how CFM, static pressure and brake horsepower are affected as inlet vanes
are modulated from 100% open to 0% open in a typical variable air volume system. Graph 3 provides RPM and BHP correction factors for
fans equipped with inlet vanes.
100
90
80
70
60
0% Open
50
40
30
% Peak Static Pressure
20
10
0
0 10 20 30 40 50 60 70 80 90 100
25% Open
50% Open
% Wide Open Volume
100% Open
75% Open
Without Vanes
100
% Peak Brake Horsepower
Graph 1Graph 2
RPM & BHP Corrections
To compensate for pressure drop through inlet vanes, a
percentage increase in fan RPM and BHP at full-load design
conditions must be applied.
Enter graph 3 with “% wide open volume” (see page 9 for
calculation of % WOV) and the appropriate fan size.
Move horizontally left to the “% increase” scale. Record the
% increase.
Increase the selected fan RPM by the % increase shown.
Also increase the BHP by the % increase shown.
20
18
16
14
12
10
8
% Increase
6
4
2
0
50 60 70 80 90 100
Graph 3
90
80
70
60
50
40
30
20
10
0
0 10 20 30 40 50 60 70 80 90 100
25% Open
RPM and BHP Correction Factors for Fans with Inlet Vanes
% Wide Open Volume (without vanes)
50% Open
% Wide Open Volume
BHP Fan Sizes 12-22
BHP Fan Sizes 24-73
RPM Fan Sizes 12-22
RPM Fan Sizes 24-73
75% Open
Without Vanes
100% Open
Minimum Recommended Actuator Torque For Inlet Vanes (inch-lbs.) for Double-Width Fans
Use the table below to determine minimum torque required for an inlet vane actuator.
Ratings in the fan performance tables and curves of this catalog are based on standard air (clean, dry air with a density of 0.075 pounds per
cubic foot, barometric pressure at sea level of 406.75 inches wg, temperature of 70°F). Selecting a fan to operate at conditions other than
standard air requires an adjustment to both static pressure and brake horsepower.
One cubic foot of air has a constant volume regardless of temperature or elevation. However, air density changes with non-standard
temperature or elevation. Therefore, when selecting a fan to operate at a non-standard air density using standard air density tables and
curves, corrections must be made to parameters affected by air density. These parameters are static pressure and brake horsepower.
For example, a size 30 BIDW
centrifugal fan is to deliver
35,000 CFM at 4.5 inches
wg static pressure. Elevation
is 4000 feet, temperature is
100°F.
The 4.5 inches wg static
pressure refers to the static
pressure at the operating air
Barometric Pressure
Multiply Standard Air Density, 0.075 lbm / ft3 by the Factor to obtain Density at Condition p
Altitude, (Z)ft.-1000
)
( p
b
density, in this case at 4000
feet, 100°F. Intuitively, we
realize that at higher than
standard elevations and
temperatures, air density
will be lower than standard.
Therefore, we must determine
what static pressure at
standard air density will
equate to 4.5inches wg static
pressure at our operating
density. Since standard
Temperature °F, (t)
air density is greater than
operating air density in this
case, we would expect the
corrected static pressure to
be greater than the operating
static pressure.
The accompanying table
gives air density correction
factors for non-standard
temperatures and elevations.
The example below shows
the relationship of fan
performance at sea level
and at 4000 ft. elevation
Adapted from AMCA Standard 99-09, section 0200, Charts and Tables, with written permission from Air Movement and
Control Association International, Inc.
and 100°F.
Example:
The following example shows how to properly select the fan described above:
1. Since the air volume delivered by the fan is not affected by density, airflow remains 35,000 CFM.
2. Determine correction factor from chart for an elevation of 4000 feet and air temperature of 100°F. The correction factor is 0.817.
3. Divide the specified operating static pressure by the
correction factor to determine the standard air density
equivalent static pressure.
Corrected static pressure = 4.5 inches wg ÷ 0.817 =
5.5inches wg static pressure.
4. Refer to the fan performance table for a 30 BIDW. At
35,000 CFM and 5.5 inches wg static pressure:
Fan RPM = 1571, BHP = 51.5
5. 1571 Fan RPM is required to produce the desired
performance.
6. Since the horsepower selected refers to standard air
density, this must be corrected to reflect actual BHP at
the lighter operating air.
Operating BHP = Standard BHP x 0.817, or 51.5 x 0.817 =
42.1BHP.
If a fan is selected to operate at high temperatures, the motor
must be of sufficient horsepower to handle the increased
load at any lower operating temperature where the air is more
dense. Assume the air entering the 30 BIDW fan at start-up is
0°F. For 0°F and 4000 feet elevation, the air density correction
factor is 0.995
BHP at 0°F = 51.5 x 0.995 = 51.2, therefore, a 60 HP motor is
required.
Ratings presented in the performance tables and curves of this
catalog were derived from tests made in accordance with AMCA
Standard 210 — “Laboratory Methods of Testing Fans for Ratings.”
The AMCA test procedure utilizes an open inlet and a straight
outlet duct to assure maximum static regain.
Any installation with inlet or discharge configurations that deviate
from this standard may result in reduced fan performance.
Restricted or unstable flow at the fan inlet can cause pre-rotation
of incoming air or uneven loading of the fan wheel yielding large
system losses and increased sound levels. Free discharge or
turbulent flow in the discharge ductwork will also result in system
effect losses.
Static pressure losses due to inlet and discharge conditions can
be expressed in terms of system effect factors. The static pressure
for selection of the fans equals the system static pressure plus the
system effect factor.
Some common inlet and discharge conditions which affect fan
performance are:
Non-Ducted Inlet Clearance
One
fan
wheel
Installation of a fan with an open inlet too close to a wall or
bulkhead will cause reduced fan performance. It is desirable to
have one fan wheel diameter between the fan inlet and the wall.
System effect Curve #2 depicts the pressure loss for one-half
wheel diameter clearance.
Free Discharge
diameter
Discharge Duct Turns
n
o
i
t
a
t
o
R
POOR
n
o
i
t
a
t
o
R
Length of Straight Duct
GOOD
Duct turns located near the fan discharge should always be in the
direction of the fan rotation.
Fan performance is reduced when duct turns are made immediately
off the fan discharge. To achieve cataloged fan performance there
should be at least three equivalent duct diameters of straight
ductwork between the fan discharge and any duct turns. Curve#3
shows the system effect factor for two diameters of straight
ductwork and Curve #1 for one diameter.
System Effect Factor Curves
Additional information on system effect factors can be found
in AMCA Publication 201 — “Fans and Systems” and ASHRAE
Handbooks.
Free or abrupt discharge into a plenum results in a reduction in fan
performance. The effect of static regain in discharge is not realized.
System effect Curve #1 depicts the pressure loss for free or abrupt
discharge.
7
®
Sound Performance Testing
Fan
Reverberant
Room
ReferenceSoundSource
Microphone
Path
AMCA Licensed Ratings
Sound tests of Model BIDW and AFDW were conducted in Greenheck Fan Corporation’s AMCA Accredited sound laboratory in accordance
with AMCA Standard 300. Inlet and outlet sound ratings comply with AMCA Publication 311, qualifying these models to bear the AMCA Seal
for Sound and Air Performance. The sound power levels published here can be compared directly with those of other similarly rated fans, or
used as a baseline to determine sound levels in occupied spaces.
The sound data in this brochure is the result of extensive testing, which included both inlet and outlet sound tests on double-width
centrifugal fans. Typically, fan manufacturers publish only inlet sound for double-width fans. The assumption they make is that outlet sound
is identical to inlet sound. Sound data based on this assumption is simply not accurate enough for today’s sound sensitive installations. This
assumption also ignores duct end corrections for outlet sound.
Test Methods
AMCA Standard 300 clearly defines methods used to test fans in a reverberant sound test room. The reverberant room is specifically
designed to allow sound waves to be dispersed evenly throughout the room. The walls have a hard surface that reflects sound and are
positioned to prevent resonances which could result in quiet areas within the room.
Sound power cannot be directly measured. The test method is based on a Reference Sound Source (RSS) substitution for determining fan
sound power. The RSS is a laboratory calibrated device which has a known sound power output level. The test fan is installed as shown
below. The RSS is energized and the sound pressure levels in the reverberant room are recorded. The fan is then operated without the RSS
and the fan sound pressure levels are recorded for various points of operation. Since the sound power levels of the RSS are known, the
substitution method is used to determine the sound power levels of the fan. This method is illustrated in the following example.
Calculating Fan Sound Power
Octave Band12345678
Center Frequency (Hz)
Calibrated RSS Sound Power (Lwr)
Measured RSS Sound Pressure (Lpq)
Difference (Lwr-Lpq)
Measured Fan Sound Pressure (Lpm)
Substitution (Lwr-Lpq , from above)
Fan Sound Power (Lw)
631252505001000200040008000
8281818181817978
7074757675746961
12765671017
6872696968625746
+12+7+6+5+6+7+10+17
8079757474696763
Note: Sound level shown in dB
Test Setups
The illustrations show where the sound levels were measured with respect to the fan. Inlet sound was tested as in Figure 2 of AMCA
Standard 300 and outlet sound was tested as in Figure 3. Inlet and outlet sound were determined in the same inlet and outlet configurations
as the air tests. (Installation Type B - Free Inlet, Ducted Outlet).
Since double-width fans are more often ducted at the inlet, they are tested only for sound radiated from the fan inlet.
DOUBLE WIDTH
Airflow
Fan
Microphone
Reference
Sound
Source
Path
Reverberant
Room
Figure 2:
AMCA Standard 300 - Fan Inlet Sound Testing
Installation Type B: Free Inlet, Ducted Outlet
Fan
Figure 3:
AMCA Standard 300 - Fan Outlet Sound Testing
Installation Type B: Free Inlet, Ducted Outlet
DOUBLE WIDTH
Reference
Sound
Source
Airflow
Microphone
Path
Reverberant
Room
(Ratings include the effects of duct end correction)
Interpreting Sound Data
Sound power levels in this catalog are presented as dB (re 10
63 Hz to 8000 Hz. They are also presented as a single A-weighted sound power level, LwA. Charts are provided covering the full range of
fan speeds and percent wide open volume (% WOV) for each fan size. Outlet sound power data is based on a ducted outlet and therefore
includes duct end reflection corrections.
-12
watts) in each of the eight full octave bands with center frequencies from
®
8
Sound Performance Testing
Outlet Sound – Duct End Corrections
This correction accounts for sound that is reflected back into the
duct where there is an abrupt termination of the duct.
AMCA Standard 300 requires that outlet sound power for fans with
ducted outlets include Duct End Corrections. These corrections
account for any sound power that may be present in the duct but is
not measured in the reverberant room, because it is reflected back
into the duct at the discharge.
Duct end corrections are included in all outlet sound power ratings.
Size
Duct End Corrections (dB)
Double-Width Fans
63 Hz125 Hz250 Hz
18
20
22
24
27
30
33
36
40
44
49
54
60
66
73
952
941
841
73
63
62
52
52
41
41
3
3
2
2
2
Tolerance and Application
The certification process in AMCA Standard 311 call for a precertification test to verify original test results. Check tests are also required
every three (3) years for each model licensed. Test data must agree with the published sound power within the following tolerance levels:
Octave Band12345678
Center Frequency (Hz)
Tolerance
631252505001000200040008000
+6+3+3+3+3+3+3+3
These tolerance levels are a good indication of the variance that could occur from one fan or test setup to another. Once installed however,
there are many other factors that can affect the sound power generated by a fan.
The lower frequencies (below 125 Hz) are greatly affected by vibration. Fan wheel balance, motor balance, drive alignment, etc., all affect
the vibration level of the fan and can increase sound power in the 1st and 2nd octaves. When ducts are not properly isolated from the fan,
these vibrations can be transmitted into the ducts, which can generate additional low frequency sound.
Sound power generated by a fan can also be influenced by system effects. System effects are pressure losses caused by inlet or outlet
restrictions, or other conditions causing non-uniform airflow at the inlet or discharge of a fan (see AMCA Publication 201). Examples include
inlet or outlet elbows too close to a fan, restricted inlets and fan accessories. While system effects can prevent fans from reaching their
designed air performance, they can also result in increased sound power levels. Typically, system effects cause pressure fluctuations
which influence the lower frequencies. Poor inlet conditions can also greatly increase sound levels at the blade pass frequency (BPF). The
blade pass frequency refers to how often a blade or wheel fin passes a stationary location of the housing and can be calculated using the
following equation:
Per AMCA: Blade Pass Frequency
BPF (Hz)=
NOTE: All BISW and AFSW wheels have nine blades.
Sound is becoming increasingly critical for most fan installations. Greenheck employs extensive research and testing to provide sound data
that is as thorough and accurate as possible. However, sound pressure levels in occupied spaces are affected by the acoustical qualities
of the space, distance from source to receiver, etc. Therefore, published sound power data can be used only as a baseline for determining
the resulting sound pressure levels an occupant hears. While Greenheck provides products which meet published sound power levels,
no manufacturer can be responsible for poor installations or system designs beyond their control. For further information on installation
practices, see AMCA Publication 201, “Fans and Systems”.
Fan RPM x Number of Blades
(
60
2
)
Sound Power
Sound power data is charted for the full range of RPM and percent wide open volume (% WOV) for each unit size.
The % WOV is a convenient way to indicate the operating point (pressure and CFM) for a given fan RPM. To calculate the % WOV for a
given fan size, use the equation given on the performance page.
Use the following procedure to calculate sound data for a specific Fan RPM and % WOV:
% WOV =
CFM x 100
RPM x K
1. Determine the eight sound power levels for the specified % WOV using the higher Fan RPM shown.
2. Determine the eight sound power levels for the specified % WOV using the lower Fan RPM shown.
3. Interpolate between the higher and lower sound power levels using the specified RPM.
9
®
Sample Fan Selection
20-BIDW-41
Fan Size
Series 21 - Permalock™Series 41 - Welded
DW - Double-width, Double-inlet
WheelBI - Backward-InclinedAF-Airfoil
The purpose of these two pages is to demonstrate the
manual centrifugal fan selection process. These pages also
contain helpful tips to check your fan selection, as well as a
step-by-step set of instructions on how to use this manual
to properly select a centrifugal fan.
An important point to remember when manually selecting
a centrifugal fan is that more than one fan is available to
meet the desired performance (CFM and Ps). Selection
criteria such as unit size, efficiency, speed, outlet velocity,
horsepower, or construction material may also dictate which
fan is chosen.
20 BIDW
AThe Outlet Area
is used for the
Outlet Velocity (OV)
OV =
CFM
OA
calculation.
B The Maximum BHP
can be calculated for
a given fan RPM along
the fan curve.
C The minimum starting
HP is determined by
the inertia (WR
2
) of the
fan and motor. See
page 4 for a complete
motor starting torque
formula.
D The maximum fan
RPM for each fan
class is listed.
EConstant HP curves
are plotted for each
motor HP size.
F The % WOV is used
to identify the fan
operating point. The
lines in the fan curve
or the equation can be
used.
Sound and Air performance are identical for Greenheck
Series 21 and 41 centrifugal fans.
The following example explains the model number code for
both series of centrifugal fans.
Minimum Starting HP = 3⁄4
Maximum RPM Class I = 1960
Maximum RPM Class II = 2554
Maximum RPM Class III = 3219
STATIC PRESSURE (in. wg)
Step 1
STATIC PRESSURE (in. wg)
STATIC PRESSURE (in. wg)
®
Performance certified is for model BIDW Arrangement 3, Installation Type B: free inlet, ducted outlet.
Performance ratings do not include the effects of appurtenances (accessories).
Power rating (BHP) does not include transmission losses.
10
Fan Selection Procedure
The sound power level ratings shown are in decibels, referred to 10
-12
watts calculated per AMCA Standard 301. Values shown are for inlet L
w
i
, L
w
i
A and outlet
L
w
o
, L
w
o
A sound power levels for Installation Type B: free inlet, ducted outlet. Outlet ratings include the effects of duct end correction. The A-weighted sound
ratings shown have been calculated per AMCA International Standard 301.
Enter the performance table with the desired CFM
and Ps. Obtain the fan RPM, BHP and Class.
EXAMPLE
For this example, we will use 13,400 CFM at 2.0 Ps.
This gives us a fan RPM of 1847, requiring 10.9 BHP,
with Class I construction.
NOTE: If your specific fan selection requires inlet
vanes or if the fan operating point is not at standard air
(70°F), refer to the inlet vane and air density correction
factor graphs and tables found on pages 5 and 6.
D
E
Step 2
F
STEP 2
Enter the Fan Curve with the desired CFM and Ps.
Obtain the fan operating point, % WOV, Motor HP
and verify fan class by curve shading.
EXAMPLE
For this example, the fan operating point is at
85%WOV using a 15 HP motor.
STEP 3
Enter the Fan Sound Table
with the Fan RPM from the
performance table and the %
WOV from the fan curve. Obtain
the eight octave ratings for inlet
) and Outlet (L
(L
i
w
Power.
) Sound
w
o
EXAMPLE
For this example, the eight octave
ratings are circled in the table
below.
NOTE: The exact % WOV for your
desired performance can be found
using the equation at the top of
the Sound Power Tables if it is
not published. The eight octave
ratings can then be found using the
interpolation instructions found in
the Sound Performance section on
pages 8 and 9.
Performance certified is for model BIDW Arrangement 3, Installation Type B: free inlet, ducted outlet.
Performance ratings do not include the effects of appurtenances (accessories).
Power rating (BHP) does not include transmission losses.
A sound power levels for Installation Type B: free inlet, ducted outlet. Outlet ratings include the effects of duct end correction. The A-weighted sound
w
o
o
Inlet Sound Power, L
w
i
A
RPM %WOV 12345678L
i
w
-12
watts calculated per AMCA Standard 301. Values shown are for inlet L
Performance certified is for model BIDW Arrangement 3, Installation Type B: free inlet, ducted outlet.
Performance ratings do not include the effects of appurtenances (accessories).
Power rating (BHP) does not include transmission losses.
A sound power levels for Installation Type B: free inlet, ducted outlet. Outlet ratings include the effects of duct end correction. The A-weighted sound
w
o
o
Inlet Sound Power, L
w
i
A
RPM %WOV 12345678L
i
w
-12
watts calculated per AMCA Standard 301. Values shown are for inlet L
Performance certified is for model BIDW Arrangement 3, Installation Type B: free inlet, ducted outlet.
Performance ratings do not include the effects of appurtenances (accessories).
Power rating (BHP) does not include transmission losses.
A sound power levels for Installation Type B: free inlet, ducted outlet. Outlet ratings include the effects of duct end correction. The A-weighted sound
w
o
o
Inlet Sound Power, L
w
i
A
RPM %WOV 12345678L
i
w
-12
watts calculated per AMCA Standard 301. Values shown are for inlet L
Performance certified is for model BIDW Arrangement 3, Installation Type B: free inlet, ducted outlet.
Performance ratings do not include the effects of appurtenances (accessories).
Power rating (BHP) does not include transmission losses.
A sound power levels for Installation Type B: free inlet, ducted outlet. Outlet ratings include the effects of duct end correction. The A-weighted sound
w
o
o
Inlet Sound Power, L
w
i
A
RPM %WOV 12345678L
i
w
-12
watts calculated per AMCA Standard 301. Values shown are for inlet L
Performance certified is for model BIDW Arrangement 3, Installation Type B: free inlet, ducted outlet.
Performance ratings do not include the effects of appurtenances (accessories).
Power rating (BHP) does not include transmission losses.
A sound power levels for Installation Type B: free inlet, ducted outlet. Outlet ratings include the effects of duct end correction. The A-weighted sound
w
o
o
Inlet Sound Power, L
w
i
A
RPM %WOV 12345678L
i
w
-12
watts calculated per AMCA Standard 301. Values shown are for inlet L
Performance certified is for model BIDW Arrangement 3, Installation Type B: free inlet, ducted outlet.
Performance ratings do not include the effects of appurtenances (accessories).
Power rating (BHP) does not include transmission losses.
A sound power levels for Installation Type B: free inlet, ducted outlet. Outlet ratings include the effects of duct end correction. The A-weighted sound
w
o
o
Inlet Sound Power, L
w
i
A
RPM %WOV 12345678L
i
w
-12
watts calculated per AMCA Standard 301. Values shown are for inlet L
Performance certified is for model BIDW Arrangement 3, Installation Type B: free inlet, ducted outlet.
Performance ratings do not include the effects of appurtenances (accessories).
Power rating (BHP) does not include transmission losses.