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Special thanks to the Bonneville Power Adminstration for permitting us to distribute this tool to energy professionals worldwide,as well as Christopher B. Milan, PE, CEM Mechanical & Civil Engineer, B.P.A. for developing these calculators.
See the complete line of energy saving drives from Cerus by clicking on the photo below:
If you have any questions regarding these tools, please click to email Chris Milan at bpa.govThis, and other handy calculators can be found at http://www.cerusind.com/calculators.aspClick here for extensive analysis tools at DOE web site
VFD CALCULATORSfor Fan & Pump Applications
VFD CALCULATORSfor Fan & Pump Applications
Comparison of Inlet and Outlet Dampers
Page 2 of 14 Bonneville Power Administration Revision No. 1
These three (3) graphs can be useful in estimating
airflow based upon damper position. Note: These
curves are representative, not precise.
These three (3) graphs can be useful in estimating
airflow based upon damper position. Note: These
curves are representative, not precise.
Comparison of Inlet and Outlet Dampers
Page 3 of 14 Bonneville Power Administration Revision No. 1
Fan Drives Power Graphs
Page 4 of 14 Bonneville Power Administration Revision No. 1
The power curves above are used in the energy savings analysis. Curves developed from data obtained by measuring the operating characteristics of various fan systems and from information provided in "Flow Control", a Westinghouse publication, Bulletin B-851, F/86/Rev-CMS 8121. Curves are representative, not precise,final economic analysis should be based on actual power (kW) measurements of the fan system.
0 20 40 60 80 100 1200.0
20.0
40.0
60.0
80.0
100.0
120.0
16.4 17.020.0
25.0
32.0
40.7
51.1
62.8
75.7
89.6
104.4
Eddy Current Drive Fan Flow Control
% of Design CFM
% o
f D
esig
n I
np
ut
Pow
er (
kW
)
0 20 40 60 80 100 1200.00
20.00
40.00
60.00
80.00
100.00
120.00
4.75 5.378.00
12.89
20.27
30.38
43.46
59.75
79.50
102.93
Adjustable Speed Drive Fan Flow Control
% of Design CFM or % of Full Speed RPM
% o
f D
esig
n I
np
ut
Po
wer
(k
W)
ADJUSTABLE SPEED DRIVE ENERGY SAVINGS CALCULATOR~ Fan Applications ~
Page 5 of 14 Bonneville Power Administration Revision No. 1
Fan Motor Information
100.00 hp85.00 %80.00 % 1-800-3543787
Power(kW) at Fan Design CFM: 70.21 KW
Facility Information
80 hrs/yr0.05 $/kwh
Existing Flow Control Method and Fan Type
1 Inlet Guide Vane, FC Fans 4 Outlet Damper, FC Fans 71 2 Inlet Guide Vane, BI & Airfoil Fans 5 Outlet Damper, BI & Airfoil Fans
3 Inlet Damper Box 6 Eddy Current Drives
Duty Cycle Power Analysis Savings Analysis
Existing System ASD System
ASD System Power (kW)
0.0% 5.0% 20.00 14.04 5.90 4.14 39.60 $ 1.98 10.0% 5.0% 20.64 14.49 4.75 3.33 44.64 $ 2.23 20.0% 10.0% 21.57 15.14 5.37 3.77 90.99 $ 4.55 30.0% 10.0% 23.32 16.37 8.00 5.62 86.03 $ 4.30 40.0% 10.0% 26.44 18.56 12.89 9.05 76.09 $ 3.80 50.0% 10.0% 31.45 22.08 20.27 14.23 62.84 $ 3.14 60.0% 10.0% 38.92 27.32 30.38 21.33 47.97 $ 2.40 70.0% 10.0% 49.36 34.66 43.46 30.51 33.18 $ 1.66 80.0% 10.0% 63.33 44.47 59.75 41.95 20.13 $ 1.01 90.0% 10.0% 81.37 57.13 79.50 55.82 10.52 $ 0.53 100.0% 10.0% 104.01 73.03 102.93 72.27 6.04 $ 0.30
Totals: 100.0% 2,584.31 2,066.29 518.03 $ 25.90
Sample Duty Cycles (these can be used as a guide if the duty cycle is not known)Sample Duty Cycle - HIGH FAN LOADING Sample Duty Cycle - LOW FAN LOADING
Summary
Energy Savings: 518.03 KWH/yr Enter Labor Cost:Cost Savings: $ 25.90 Total Cost: $ -
Enter Materials Cost: $ - Simple Payback: years
If you have any questions or comments, please email Chris Milan at the following:
More extensive analysis tools are available at the following DOE web site:
* This is an Excel 2000 file and is approximately 2.5 MB in size.
Enter Nameplate Horsepower:Enter Nameplate Efficiency: www.cerusind.com
Enter Motor Load at Fan Design CFM:
Enter Hours per year fan operates:Enter Energy Charge:
Select Flow Control andFan Type Below Click to go to the Fan Types worksheet for more information
Selection 7 allows Measured Power (kW) readings to be used in the analysis
Enter Percent of Design Capacity (CFM)
Enter Percent of
Time at this Capacity
Annual Energy Savings (Kwh/yr)
Annual Energy Cost Savings ($/yr)Existing System
Percent of Design (KW)
Do Not Enter Data
Below
Existing System Power (kW)
Percent of Design (kW)
for ASD System
Kwh/yrexisting Kwh/yrasd
This calculator was developed by Chris Milan at the Bonneville Power Administration (BPA) and is intended to be used as an estimation of potential energy savings and simple payback for ASD installations. Final economic decisions should be based upon more extensive analysis tools than what is provided here.
[email protected]://www.eere.energy.gov/industry
50 75 900
10
20
30
40
50
60
70
20
60
20
Percent of Design Capacity (cfm)
Percen
t of
Tim
e a
t th
is C
ap
acit
y
30 50 70 900
10
20
30
40
50
60
15
55
25
5
Percent of Design Capacity (cfm)
Percen
t o
f T
ime a
t t
his
Ca
pa
cit
y
Common Fan Types
Page 6 of 14 Bonneville Power Administration Revision No. 1
(FC) Forward-Curved Fans (BI) Backward-Inclined Fans Radial-Blade Fans Axial FansD
escr
ipti
on
s an
d F
an E
ffic
ien
cies
Per
form
ance
Ch
arac
teri
stic
sA
pp
licat
ion
s
Reference: "Improving Fan System Performance" Industrial Technologies and Best Practices Web Site at: http://www.oit.doe.gov
The fan blades curve in the direction of rotation. These fans are typically not as large as other fan types and structurally are not very rugged. Fan efficiencies are in the range of 55 to 65%.
The fan blades tilt back, away from the direction of rotation. The main difference between fans in this category is the shape and construction of the blades. The Backward-Inclined Flat blades tend to be more rugged and allow some particulate to pass through but these blades are not very aerodynamic and therefore are the least efficient. The Backward-Inclined Curved blades are more efficient but their orientation with the air stream can allow moisture and particulate to collect on the blades which reduces fan performance and may cause excessive vibrations. The efficiency ranges from 75 to 85%. The Backward-Inclined Airfoil blade resembles the wing of an aircraft and is the most efficient fan type with efficiencies over 90%.
These fans are typically the most rugged of all types and can range from Paddle-Wheel design to Flat Blades with corrosion resistance coatings. These fans usually operate at lower volumes but higher pressures than other fan types. The wide openings between the blades allow larger material to pass through and also minimizes vibrations when operating during conditions when the flow and pressure drops. The construction of these fans allows them to be modified to meet specific applications and to be repaired at minimum costs. Typical ranges of fan efficiencies for Flat Blades is 55 to 65% and 60 to 75% for the Radial Tip.
This fan group includes Propeller, Tubeaxial, and Vaneaxial fans. The fan blades are installed perpendicular to the air stream. The majority of these fans can be operated in reverse which allow them to supply or exhaust the air. Propeller fans generate high airflows but minimum pressure and are the least expensive and least efficient. To increase the pressure and efficiency these fans are placed inside a hollow tube to form the Tubeaxial fan. To further increase the efficiency and develop a more unified air stream, outlet vanes are installed to form the Vaneaxial fan.
The typical performance curve for a Forward Curved fan contains a dip in the static pressure curve to the left of the point of maximum static pressure. This region of the performance curve indicates that the characteristics of the air flow through the fan was not consistent. As the flow increases, the static pressure increases and decreases within this region. It is not recommended to operate the fan within this unstable region of the fan curve due to the unpredictable flow characteristics. This area is sometimes referred to as the "stall" region.
The fan performance curve for Backward Inclined fans is similar to the forward curve but typically has a smaller dip in the static pressure curve. The major difference of the backward inclined fans is the characteristics of the BHP curve. The horsepower curve does not increase to a maximum amount at maximum flow rate but instead will reach a peak and then drop off as the flow rate continues to increase to it's maximum amount. This characteristic allows the designer to select a motor size for the worst case(design) conditions and if any errors or changes occur that would increase the flow requirements, the fan will not be overloaded. This is typically referred to as a "non-overloading" power curve.
The performance curve for fans with Radial Blade wheels is typically a smooth curve showing the pressure steadily dropping from a maximum at zero flow to a minimum pressure at full flow. This characteristic allows stable operation of the fan throughout a wide range of flow(cfm) by adjusting the pressure. The corresponding BHP curve increases at a linear rate as the fan flow rate increases. The Radial Tip fan performance curve is a blend of the Backward- Inclined and Radial Blade curves. The BHP curve increases to a maximum amount at maximum flow. The Radial Tip is more efficient than the Radial Blade and therefore requires less horsepower to produce the same output.
The fan performance curve for this group of fans indicates that they are capable of providing high flow rates at lower pressures than other fan types. These fans will typically have a unique BHP curve that requires maximum power at zero flow rate. The horsepower and static pressure will increase and decrease as flow increases until finally reaching a minimum value at maximum flow rate. These variations in flow and pressure result in different flow rates at the same operating pressure, causing instability and control problems. Operating within this region should be avoided.
Due to the narrow openings between fan blades, these fans are not suited for airstreams containing particulate. These fans usually operate at low volumes and low speeds such as in residential HVAC units.
As stated above, these fans are typically "non-overloading" and this characteristic makes them a popular choice for applications were the system performance is uncertain at maximum flow rates. The inside of these blades are usually hollow to reduce their weight but the build up of moisture and particulate can lead to cavities which reduces their efficiency. The narrow openings can limit the size of particulate in the air stream they can tolerate. These fans are a good choice for installations on the clean side of the process air stream for material and dust handling systems and for forced-draft fans in boilers.
These fans are the fans of choice for moving material or air in harsh operating environments. They are used to convey everything from air filled with particulate to wood chips, rock or metal scrap
Propeller fans are common on cooling towers and inexpensive exhaust systems. Tubeaxial and Vaneaxial fans are used in HVAC exhaust applications were higher pressures and flow rates are required. All of these fans produce significant airflow noise when compared to other fans.
Inlet Vane Graphs
Page 7 of 14 Bonneville Power Administration Revision No. 1
power curve is over loading….go 105%
6
These power curves are used in the energy savings analysis. Curves developed from data obtained by measuring the operating characteristics of various fan systems and from information provided in "Flow Control", a Westinghouse publication, Bulletin B-851, F/86/Rev-CMS 8121. Curves are representative, not precise. Final economic analysis should be based on actual power(kW) measurements of the fan system.
0 20 40 60 80 100 1200.0
20.0
40.0
60.0
80.0
100.0
120.0
50.3
56.159.8
62.2 64.0 66.069.1
73.9
81.2
91.9
106.7
Inlet Damper Box, General Curve
% of Design CFM
% o
f D
esig
n I
np
ut
Po
wer
(k
W)
0 20 40 60 80 100 1200.0
20.0
40.0
60.0
80.0
100.0
120.0
20.0 20.6 21.623.3
26.4
31.5
38.9
49.4
63.3
81.4
104.0
Inlet Guide Vane Control, Forward Curve Fans
% of Design CFM
% o
f D
esig
n I
np
ut
Po
wer
(k
W)
0 20 40 60 80 100 1200.0
20.0
40.0
60.0
80.0
100.0
120.0
47.3
52.655.8 57.4 58.5 59.9
62.366.7
73.8
84.6
99.8
Inlet Guide Vane Control, BI & Airfoil Fans
% of Design CFM
% o
f D
esig
n I
np
ut
Po
wer
(k
W)
Outlet Damper Graphs
Page 8 of 14 Bonneville Power Administration Revision No. 1
The power curves above are used in the energy savings analysis. Curves developed from data obtained by measuring the operating characteristics of various fan systems and from information provided in "Flow Control", a Westinghouse publication, Bulletin B-851, F/86/Rev-CMS 8121. Curves are representative, not precise, final economic analysis should be based on actual power(kW) measurements of the fan system.
0 20 40 60 80 100 1200.0
20.0
40.0
60.0
80.0
100.0
120.0
20.422.3
25.6
30.4
36.7
44.5
53.8
64.6
76.9
90.6
105.9
Outlet Damper Control, Forward Curve Fans
% of Design CFM
% o
f D
esig
n I
np
ut
Pow
er (
kW
)
0 20 40 60 80 100 1200.0
10.0
20.0
30.0
40.0
50.0
60.0
70.0
80.0
90.0
100.0
110.0
120.0
52.6 53.3
57.2
63.6
71.5
80.2
88.7
96.3
102.1105.2
Outlet Damper Control, Radial Blade, Backward Inclined & Airfoil Fans
% of Design CFM
% o
f D
esig
n I
np
ut
Pow
er (
kW
)
ADJUSTABLE SPEED DRIVE ENERGY SAVINGS CALCULATOR~ Fan Applications ~
Page 9 of 14 Bonneville Power Administration [Revision No. 1]
Motor Information
50.00 hpEnter Nameplate Efficiency: 95.00 %
Enter Motor Load at Fan Design CFM: 90.00 %Power(KW) at Fan Design CFM: 35.34 KW
Facility Information
Enter Hours per year fan operates: 8760 hrs/yrEnter Energy Charge: 0.05 $/kwh
Flow Control Method and Fan Type
1 Inlet Guide Vane, FC Fans 4 Outlet Damper, FC Fans5 2 Inlet Guide Vane, BI & Airfoil Fans 5 Outlet Damper, BI & Airfoil Fans
3 Inlet Damper, General Curve 6 Eddy Current Drives 7 Measured kW
Duty Cycle Power Analysis Savings Analysis
Existing System ASD System
ASD System Power (KW)
25.0% 15.0% 54.90 19.40 6.42 2.27 22,511.26 $ 1,125.56 50.0% 55.0% 71.53 25.28 20.27 7.16 87,270.91 $ 4,363.55 70.0% 25.0% 88.71 31.35 43.46 15.36 35,022.55 $ 1,751.13 90.0% 5.0% 102.08 36.07 79.50 28.09 3,494.89 $ 174.74
0.00 0.00 0.00 0.00 0.00 0.00 0.00
Totals: 100.0% 231,719.64 83,420.05 148,299.60 $ 7,414.98
Sample Duty Cycles (use these as a guide if the duty cycle is not known)Sample Duty Cycle - HIGH FAN LOADING Sample Duty Cycle - LOW FAN LOADING
Summary
Energy Savings: (Note 1) 148,299.60 KWH/yr Enter Labor Cost: $ 100,000.00 Cost Savings: $ 7,414.98 Total Cost: $ 100,950.00
Enter Materials Cost: $ 950.00 Simple Payback: 13.61 years
Enter Nameplate Horsepower:
Select Flow Control andFan Type Below Click to go to the Fan Types worksheet for more information
Enter Percent of
Design Capacity
(CFM)
Enter Percent of Time at
this Capacity
Annual Energy Savings (Kwh/Yr)
Annual Energy Cost Savings ($/yr)Existing
System Percent of
Design (KW)
Do Not Enter Data
Below
Existing System Power
(KW)
Percent of Design (KW)
for ASD System
Kwh/yrexisting Kwh/yrasd
This calculator was developed by Chris Milan at the Bonneville Power Administration (BPA) and is intended to be used as an indication of the potential energy savings and simple payback for ASD installations. If you have any questions or suggestions for improvements, please contact Chris Milan at [email protected]. More extensive analysis tools are available at: http://www.eere.energy.gov/industry.
50 75 900
10
20
30
40
50
60
70
20
60
20
Percent of Design Capacity (cfm)
Percen
t of
Tim
e a
t th
is C
ap
acit
y
30 50 70 900
10
20
30
40
50
60
15
55
25
5
Percent of Design Capacity (cfm)
Percen
t o
f T
ime a
t th
is C
ap
acit
y
This Sample Input Sheet is for viewing purposes only. No values can be inputted or changed. It is included here to give the user
an idea of what types of values can be entered into either the Fan Calculator or
Pump Calculator worksheets.
This Sample Input Sheet is for viewing purposes only. No values can be inputted or changed. It is included here to give the user
an idea of what types of values can be entered into either the Fan Calculator or
Pump Calculator worksheets.
TYPES OF AIRFLOW CONTROL
Page 10 of 14 Bonneville Power Administration Revision No. 1
Inlet Guide Vanes andInlet Dampers
OutletDampers
Adjustable Speed-Drives
Op
era
tin
gC
ha
ract
eri
sti
cs
Inlet Guide Vanes are installed across the opening of the fan inlet. By opening and closing, they vary the amount of air entering the fan and change the profile of the entering airstream. As the air passes through the vanes it begins to swirl in the same rotation as the fan impeller, this pre-spinning of the air reduces the momentum that the fan blades can impact on the entering air and therefore reduces the velocity and pressure of the discharged air. As the vanes continue to close, this swirling action increases and continues to decrease the pressure and flow the fan delivers to the system. The fan horsepower is proportional to the flow and pressure, therefore the horsepower requirement also decreases. Because the inlet vane opening affects all three of these fan characteristics, a new fan performance curve is created whenever the vane position is changed. Inlet control does not affect the system curve, as vane positions change the fan performance curve rides up and down the system curve.
Outlet dampers do not change the characteristics of the entering airstream. Outlet dampers control flowrate by restricting the amount of air being discharged. This restriction allows the air flow rate to be varied the same way a discharge throttle valve adjusts the volume of flow out of a pump. The resistance of flow through the system increases as the flow(cfm) of air increases. This relationship is shown graphically by plotting the flow and corresponding resistance(pressure) to generate the system resistance curve. When the system curve and fan performance curve are shown on the same graph, the intersection of these two curves defines a unique point of operation. When the fan is installed in this particular system and operates at this flow rate, it will produce this pressure. The fan can only operate as shown by it's performance curve, for a given pressure it will provide a unique flow or vice versa.
Adjustable Speed Drives(ASDs) control the flowrate by electronically adjusting the speed of the motor driving the fan or pump. Similar to Inlet Guide Vanes, as the speed is reduced, the flowrate, pressure and horsepower requirement is reduced which results in a new performance curve for each speed setting. With ASDs, as speed is reduced the horsepower requirement is decreased according to the affinity laws within a squared to cubic relationship depending upon the amount of static pressure and how the system responds to changes in flow and pressure. A system containing static head and in which small increases in flow result in large pressure drops will have a system curve that rises steeply. By plotting this system curve and a system curve that does not rise steeply onto the same fan or pump performance curves at various speeds, one can see the following relationship. That for the same reduction in flow rate, the system curve that rises steeply will require more speed reductions to obtain this reduced flow and therefore the greater the opportunity for energy savings.
Inlet dampers can be oriented to provide the same affect as inlet guide vanes but usually are not as effective at inducing the appropriate swirl. The blades typically operate in parallel with each other. If the inlet dampers are installed too far from the fan inlet or are not oriented properly, they only serve to restrict the entering airflow.
With outlet damper control, any new operating point is achieved by adjusting the characteristics of the system curve, not the fan performance curve. For example, in order to reduce the fan flow rate, as the outlet dampers begin to close, the system's resistance(pressure) increases and shifts the system curve upward until it intersects the fan performance curve to define a new operating point of increased pressure and reduced flow.
In determining the appropriate application of an ASD, the entire system should be evaluated. For example, if the fan or pump and electric motor is oversized, further reductions in operating speed could result in significant reductions in motor efficiency as well as the efficiencies of the fan, pump. In some cases the motor can be re-sheaved to confirm energy savings and system response to reduced speeds prior to purchasing the drive.
Ad
van
tag
es
/D
isa
dv
an
tag
es
Inlet Dampers are usually a better choice of flow control than Outlet Dampers because when properly installed, they allow the fan horsepower to be reduced as the flow is reduced. Inlet Guide Vanes usually provide more accurate control of fan performance than Inlet Dampers. Inlet Guide Vanes are an efficient method for controlling flow rates down to approximately 70% of capacity. This would correspond to a vane position of approximately 50% closed. If the desired fan flow rate requires that the vanes be closed more than 50%, adjustable speed drives usually provide more efficient controllability by reducing the fan speed rather than continuing to restrict the fan inlet with the guide vanes.
Dampers are an efficient method of fully open/closed flow control such as exhaust air or outside air intakes. Outlet dampers are the least efficient method of variable flow control. In order for the fan to compensate for this increase in system pressure when the dampers begin to close, it has to move to the left up along the performance curve to the higher operating pressure. For the majority of fans, as you continue to restrict flow and increase pressure, the fan operates in the least efficient and unstable region of the fan performance curve. Operating at higher system pressures than necessary to reduce the flow rate not only wastes energy but increases the air leakage throughout the system. Depending upon the variation in flow rates required by the system, inlet guide vanes or adjustable speed drives may provide more energy efficient flow control.
ASDs are an excellent choice of flow control if the system allows the fan or pump to operate at reduced flow rates and loads for a significant portion of the operating time. The ASDs provide quick and accurate adjustments to flow rate and pressure as required to maintain set point. Another advantage of ASD control is their soft starting capabilities which reduces the high in-rush currents at start-up. Operating at reduced speeds can increase the equipment life, reduce vibrations and noise. For fan applications were the flow rate does not vary significantly, inlet guide vanes may be a better choice of control. ASDs are not 100% efficient, therefore operating the motor at full speed with the ASD will increase the input power due to the inefficiency of the drive. ASDs typically require that they be placed in a clean, conditioned environment which could result in high installation costs.
Reference: "Improving Fan System Performance" Industrial Technologies and Best Practices Web Site at: http://www.oit.doe.gov
Pump Drives Power Graphs
Page 11 of 14 Bonneville Power Administration Revision No. 1
Values used in spreadsheet
These power curves are used in the energy savings analysis. Curves developed from data obtained by measuring the operating characteristics of various pumps and from information provided in "Flow Control", a Westinghouse publication, Bulletin B-851, F/86/Rev-CMS 8121. Curves are representative, not precise, final economic analysis should be based on actual power(kW) measurements of the pumping system.
10 20 30 40 50 60 70 80 90 100 1100.00
20.00
40.00
60.00
80.00
100.00
120.00
14.32 13.05 15.3021.07
30.37
43.19
59.53
79.40
102.79
ASD Pump Flow Control
% of Design Flow (gpm) or % of Full Speed(rpm)
% o
f D
esi
gn
In
pu
t P
ow
er (k
W)
0 20 40 60 80 100 1200
20
40
60
80
100
120
13.5113718.15707
24.92077
33.38247
43.12217
53.71987
64.75557
75.80927
86.46097
96.29067
104.87837
Mechanical Speed Pump Flow Control
% of Design Flow (gpm)
% o
f D
esi
gn
In
pu
t P
ow
er
(kW
)
0 20 40 60 80 100 1200.00
20.00
40.00
60.00
80.00
100.00
120.00
16.40 17.0419.98
25.03
32.01
40.75
51.06
62.77
75.69
89.64
104.45
Eddy Current Drive Pump Flow Control
% of Design Flow (gpm)
% o
f D
esi
gn
In
pu
t P
ow
er (k
W)
ADJUSTABLE SPEED DRIVE ENERGY SAVINGS CALCULATOR~ Pump Applications ~
Page 12 of 14 Bonneville Power Administration Revision No. 1
100.00 hp95.00 %55.00 % 1-800-354378743.19 KW
Facility Information
4000 hrs/yr0.05 $/kwh
Existing Pump Flow Control Method
1 Throttling Valve 4 Bypass, Recirculation Valve
1 2 Eddy Current Clutch 5 Selection 5 allows Measured Power (kW) readings to be used in the analysis
3 Mechanical (Torque Converter)
Duty Cycle Power Analysis Savings Analysis
Existing System ASD System
0.0% 5.0% 55.21 23.85 27.45 11.85 2,398.3010.0% 5.0% 61.39 26.52 19.12 8.26 3,651.0820.0% 10.0% 67.19 29.02 14.32 6.19 9,133.2830.0% 10.0% 72.61 31.36 13.05 5.64 10,289.9440.0% 10.0% 77.65 33.54 15.30 6.61 10,772.1650.0% 10.0% 82.31 35.55 21.07 9.10 10,579.9360.0% 10.0% 86.59 37.40 30.37 13.12 9,713.2670.0% 10.0% 90.49 39.08 43.19 18.65 8,172.1480.0% 10.0% 94.01 40.60 59.53 25.71 5,956.5790.0% 10.0% 97.15 41.96 79.40 34.29 3,066.55
100.0% 10.0% 99.91 43.15 102.79 44.40 -497.91
Totals: 100.0% 142,738.45 69,503.14 73,235.31
Sample Duty Cycles (these can be used as a guide if the duty cycle is not known)Sample Duty Cycle - HIGH PUMP LOADING Sample Duty Cycle - LOW PUMP LOADING
Summary
Energy Savings: 73,235.31 KWH/yr Labor Cost: $ - Cost Savings: $ 3,661.77 Total Cost: $ -
Materials Cost: $ - Simple Payback:
If you have any questions or comments, please email Chris Milan at the following:
* This is an Excel 2000 file and is approximately 2.5 MB in size.
Enter Nameplate Horsepower:Enter Nameplate Efficiency: www.cerusind.com
Enter Motor Load at Pump Design GPM:Enter Power(KW) at Pump Design GPM:
Enter Hours per year pump operates:Enter Energy Charge:
Select Flow Control Method Below Click to go to Pump Power Graphs for additional information
Enter Percent of Design Capacity
(GPM)
Enter Percent of
Time at this Capacity
Annual Energy Savings (Kwh/yr)
Existing System
Percent of Design (KW)
Do Not Enter Data
Below
Existing System Power
(kW)
Percent of Design (kW)
for ASD System
ASD System Power (kW)
Kwh/yr existing Kwh/yr asd
This calculator was developed by Chris Milan at the Bonneville Power Administration (BPA) and is intended to be used as an estimation of potential energy savings and simple payback for ASD installations. Final economic decisions should be based upon more extensive analysis tools than what is provided here.
50 75 900
10
20
30
40
50
60
70
20
60
20
Percent of Design Capacity (gpm)
Perc
en
t o
f T
ime a
t th
is C
ap
acit
y
30 50 70 900
10
20
30
40
50
60
15
55
25
5
Percent of Design Capacity (gpm)
Per
cent of
Tim
e at
this
Cap
acity
ADJUSTABLE SPEED DRIVE ENERGY SAVINGS CALCULATOR~ Pump Applications ~
Page 13 of 14 Bonneville Power Administration Revision No. 1
Facility Information
Existing Pump Flow Control Method
Selection 5 allows Measured Power (kW) readings to be used in the analysis
Savings Analysis
119.92182.55456.66514.50538.61529.00485.66408.61297.83153.33-24.90
$ 3,661.77
Sample Duty Cycles (these can be used as a guide if the duty cycle is not known)Sample Duty Cycle - LOW PUMP LOADING
Summary
years
* This is an Excel 2000 file and is approximately 2.5 MB in size.
Click to go to Pump Power Graphs for additional information
Annual Energy Cost Savings ($/yr)
This calculator was developed by Chris Milan at the Bonneville Power Administration (BPA) and is intended to be used as an estimation of potential energy savings and simple payback for ASD installations. Final economic decisions should be based upon more extensive analysis tools than what is provided here.
30 50 70 900
10
20
30
40
50
60
15
55
25
5
Percent of Design Capacity (gpm)
Per
cent of
Tim
e at
this
Cap
acity
Throttle Valve Power Graphs
Page 14 of 14 Bonneville Power Administration Revision No. 1
The power curves above are used in the energy savings analysis. Curves developed from data obtained by measuring the operating characteristics of various pumps and from information provided in "Flow Control", a Westinghouse publication, Bulliten B-851, F/86/Rev-CMS 8121. Curves are representative, not precise, final economic analysis should be based on actual power (kW) measurements of the pumping system.
10 20 30 40 50 60 70 80 90 100 11080
85
90
95
100
105Constant Recirculation, Bypass Control
% of Design Flow (gpm)
% o
f D
esig
n (k
W)
10 20 30 40 50 60 70 80 90 100 1100
25
50
75
100
125
67.19
72.61
77.65
82.3186.59
90.4994.01
97.1599.91
Throttling Valve Flow Control
% of Design Flow (gpm)
% o
f D
esig
n (
kW
)