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TRG-TRC013-EN yvi8yveCDF8gr, gAc8hrf8yvi8yveCDF8DCPP8gr, EOCF8P8EOI, FLCC t e, o IGLCD8NIPP
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TRG-TRC013-EN
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Constant-VolumeSystem
Input Power
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Contents
Page
BUSINESS REPLY MAIL
BUSINESS REPLY MAIL
THE TRANE COMPANY Attn Applications Engineering
3600 Pammel Creek Road La Crosse WI
Response Card
Comment Card
Air Conditioning Fans
One of the Equipment Series
Worldwide Applied Systems Group
p e The Trane Company
A Trane Air Conditioning Clinic
Air Conditioning Fans
99999999999999999999999999999
caQ3caM6793O
axial centrifugal
Air Conditioning Fans
Measuring Pressure
period one
Air Conditioning Fans
atmospheric ductpressure pressure
fwt” p 2 p ”tvp rp S” r“- 4 jK 7683-- r-“4lcwt
Positive Duct Pressure
R-2 x”rwt
are “water gage” wg and “water column” wc
duct
Inclined Manometer
pressure
reservoir
Velocity Pressure vs. Static Pressure
Total Pressure
Velocity Pressure vs. Static Pressure
Velocity Pressure vs. Static Pressure
g DC
damper fully open
Velocity Pressure vs. Static Pressure
Measuring Static Pressure
g DD
g DE
Measuring Total Pressure
g DG
Fan Performance Test
Velocity Pressure Pv = Pt - P s
Determining Fan Airflow
Velocity V = Constant ⋅ √ Pρ
Airflow = Velocity ⋅ Fan Outlet Area
Plotting Fan Performance Points
Plotting Fan Performance Points
static pressure
2.0 in. H2O
static pressure
Fan Performance Curve
airflow
airflow
Fan Speed
Fan Surge
Input Power
Percent of Wide-OpenAirflow
Fan Surge Line
fan’s speed and input power requirement
Tabular Performance Data
Pp” -p”
g EG
System Resistance
System Resistance
Static Pressure
System Resistance Curve
Airflow
Static Pressure
Fan - System Interaction
Fan - System Interaction
System Resistance Curve
Lower System Resistance
Higher System Resistance
SE = Constant ⋅ Input Power
Power Out Static Efficiency SE = Power In
Static Efficiency
Airflow ⋅ Static Pressure
= 55%
3,500 cfm ⋅ 2.0 in. H2O
1.65 m3/s ⋅ 491 Pa
⋅ 1.5 kW
design system
Constant-VolumeSystem
resistance curve
pressure
variable-pitch blades
Variable-PitchVaneaxial Fan
g FH
surge region
total pressure
85% 80% 70%
airflow
surge region
total pressure
g FM
angl
Centrifugal Fan
period two
Air Conditioning Fans
g FN
Forward Curved Fan
Forward Curved Fan
cwt ux r2 - PM2 up” PM up” r-” -t
cwt r
static efficiency
Forward Curved Fan
50 to 65%
application
Backward Inclined Fan
forward curved
FC vs. BI Fans
backward inclined
Backward Inclined Fan
cwt p“xrp
Backward Inclined Fan
Airfoil Fan
Backward Curved Fan
backward inclined
backward curved
Airfoil Fan
Plug or Plenum Fan
static efficiency
80 to 86%
g HF
Vaneaxial Fan
straightening vanes fan wheel or impeller
Variable-PitchVaneaxial Fan
Vaneaxial Fan
application
static efficiency
pressure
surge region
airflow
g HI
Forward curved FC
Fan Selection
Backward inclined BI or airfoil AF
Vaneaxial
VAV System
period three
Air Conditioning Fans
K 9e“5
“Riding the Fan Curve”
Riding the Fan Curve
VAV System
S” p eKe
Forward Curved Centrifugal Fan
Fan Control Loop
VAV System Modulation Curve
Discharge Dampers
Methods of Fan Capacity Control
Discharge dampers Inlet vanes Fan-speedcontrol
Variable-pitchblade control
upward. The fan begins to “ride up” its constant-speedperformance curve toward f, from the design operating point e, trying to balance with this new system resistance curve. As a result, the fan delivers a lower airflow at a higher static pressure
Discharge Dampers
Inlet Vanes
Inlet Vanes
upward. The fan begins to “ride up” its current vane position curve toward f, from the design operating point e, trying to balance with this new system resistance curve. As a result, the fan delivers a lower airflow at a higher static pressure
Inlet Vanes
Fan-SpeedControl
Fan-SpeedControl
p“-”vKe
Variable-PitchBlade Control
g MF
variable-pitch blades
e eK/ up”
cwt t
power
Fan Control Comparison
discharge
design airflow
g MI
period four
Air Conditioning Fans
controller
System Static-PressureControl
sensor
VAV supplyterminal units fan
Optimized Static-PressureControl
System Effect
System Effect
Acoustics
Minimize system effects
Acoustical Guidelines
Avoid rectangular sound traps, if possible
Use adequate vibration isolation
5 Poweractual = Air Density Ratio ⋅ Powerstandard
Effect of Actual Conditions
1 Air Density Ratio =
Densityactual
Purpose
Equipment Certification Standards
Air Conditioning Fans
period five
Review-PeriodOne
Review-PeriodThree
Review-PeriodTwo
axial centrifugal
“Riding the fan curve” Discharge dampers
Application considerations
Review-PeriodFour
g NO
System static-pressurecontrol System effect
cp”t Kx
Page
DDList two possible causes of system effect
NLt -”trp” wp”s“t wxvwt PO up”4
E F 64 x”4 R8 j78 pl e F 82A98 u- j7
cbt L
bndb Kx
“riding the fan curve” K -tsx
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