This document outlines the design of a HVAC system for a new building in New Orleans. It discusses zoning the building into 13 zones and performing thermodynamic calculations for each zone. Psychrometric analyses are presented for each zone showing the air conditions. The building is also analyzed as a single zone to determine overall air conditions entering and leaving the building. Duct design and component sizing will be covered in subsequent sections.

1. UNIVERSITY OF NEW ORLEANS
Department of Mechanical Engineering
Dr. Martin Guillot
ENME 4777 Design of Thermal Fluid Systems
Fall 2016
Project 2
Cooling System Design for a Facility in
New Orleans, LA
Group I
Team Leader: Luis Molina
Jason Gleason
Michael Hebert
Benjamin Leblanc
Jeremy Peacock

2. Table of Contents Page #
I. SUMMARY ...............................................................................................................................................................................1
II. PROBLEM...............................................................................................................................................................................2
III. ZONING....................................................................................................................................................................................4
III. DUCT DESIGN AND HVAC COMPONENTS ...............................................................................................................20
IV. AHU/COOLING COIL.........................................................................................................................................................30
V. HYDRONICS..........................................................................................................................................................................46
VI. CHILLER PLANT ................................................................................................................................................................57
VII. COOLING TOWER ............................................................................................................................................................69
VIII. AIR COOLED CONDENSER...........................................................................................................................................73
X. CONCLUSIONS......................................................................................................................................................................77
XI. REFERENCES.......................................................................................................................................................................78
XII: APPENDIX..........................................................................................................................................................................79
APPENDIX II CHILLER BROCHURE...............................................................................................................................................80
APPENDIX:III REVIT FILES................................................................................................................................................................87

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I. Summary
The purpose of a HVAC system is to provide a healthy and comfortable environment by
means of controlling humidity and temperature. Also, HVAC systems are responsible for
distributing this conditioned air to multiple locations at efficient rates. The majority of the
conditioned air can be recirculated into the desired locations, but a portion of the supply
air must be mixed with outside air to provide an ample supply of oxygen in this indoor
environment.
The main determinant of a HVAC system requirement is the total load for a given space.
These loads are not constant, but change with the amount of occupants, and with the
weather. Since temperature and humidity differ with seasonal changes, the HVAC system
must also be capable to adapt.

4. G r o u p I | 2
II. Problem
A new building is being added to a campus in New Orleans, LA. The building layout
information is given in the drawings provided, and the building spaces are shown in the
figures below. The set point temperature of each zone is 74 °F, 50% relative humidity, with
the assumption that required ventilation air for each zone is 25% of the total for that zone.
Even though it is not possible to maintain humidity at exactly 50% within each zone, it
should be in the comfort range.
The given loads in Table 1 are based on 95oF DB and 82oF WB conditions. The central
chiller plant must be capable of providing a maximum of 1000 tons of refrigeration, but will
be designed to be able to handle loads between 25% and 100% of maximum loads with
redundancy built in.
Table 1: Space Cooling Loads
Space Sensible Load (Btu/hr) Latent Load (Btu/hr)
Classroom 1 16940 9648
Classroom 2 16940 9648
Classroom 3 16940 9648
Classroom 4 17497 9814
Classroom 5 17497 9814
Classroom 6 17497 9814
Classroom 7 19662 10786
Lobby 39177 19979
Lavatory L 6082 1915
Lavatory M 6082 1915
Main Hallway 10851 3902
Mechanical Hallway 2515 683
Mechanical Room Not Conditioned Not Conditioned
Office 1 10984 1324
Office 2 9030 1045
Plenum Not Conditioned Not Conditioned
Conference A 6346 1940
Conference B 6346 1940
Figure 1 on the following page shows the floor plan layout of the spaces in Table 1 above.

5. G r o u p I | 3
Mechanical
Room
8
Mechanical
Hallway
17
Classroom
3
Classroom
2
Classroom
1
Lavatory M
10
Lavatory L
9
Classroom
7
Classroom
6
Classroom
5
Classroom
4
Conference B
12
Conference A
11
Lobby
15
Office 2
14
Office 1
13
Main Hallway
16
20.00' 10.99' 30.00' 30.00' 30.00' 15.00' 15.00' 29.00' 29.00'
30.99' 30.00' 30.00' 30.00' 15.00' 15.00' 58.00'
69.50' 10.00'
208.99'
27.15'
42.35'
29.75'
29.75'
150.99'
922.0 ft2
892.5 ft2
892.5 ft2
892.5 ft2
446.3 ft2
446.3 ft2
2456.3 ft2
446.3 ft2
446.3 ft2
892.5 ft2
892.5 ft2
892.5 ft2
327.0 ft2
595.0 ft2
787.4 ft2
787.4 ft2
1509.9 ft2
(Not Conditioned)
Total Heated/Cooled Space: 14525 ft2
Figure1: Floor Plan of Spaces to be Conditioned

6. G r o u p I | 4
III. Zoning
For our design, we have completed the zoning and the thermodynamic analysis of the air
entering the AHU unit and going through the zones. We have decided to split up the
building into 13 different zones, as shown in the next pages. We have performed
calculations for these zones already, using an excel spreadsheet, as well as psychometric
analysis using psychometric tables. We have calculated mass flow rates necessary for the
next part of the project, which is to size, and layout the ducts. Additionally, we found the
total mass flow rate of the system, which is necessary to select an AHU. When splitting the
classrooms into each individual zone with its own VAV unit, we took into consideration
their sensible and latent loads. We decided to maintain every single classroom as its own
Zone, with its own VAV unit to ensure that the rooms were maintained at the right
temperature when occupied. Since classrooms are sometimes occupied at different times, it
didn’t make sense to group them in sets. Although adding an independent VAV unit for each
classroom makes the design and layout of the duct work more expensive, it benefits the
overall design by ensuring that one room is not freezing while the other is really hot. The
conference rooms were designed to be a single zone, since there are rarely used. Each office
was made into an independent zone, as they might be occupied at different times. Lavatory
M and Lavatory L are a single zone. The mechanical hallway, and the main hallway were
set to be a single zone.

7. G r o u p I | 5
Table 2: Specifications for each Zone
Zones Area
Sensible
Load
(Btu/hr)
Latent
Load
(Btu/hr)
Total Load
(Btu/hr)
SHR
Mass Flow
Rate
(lbm/hr)
Supply
Volumetric
Flow Rate
(ft³/min)
Exhaust
Volumetric
Flow Rate
(ft³/min)
Return Air
Volumetric
Flow Rate
(Ft³/min)
Zone 1 Classroom 1 16940.0 9648.0 26588.0 0.6371 3529.2 784.3 196.1 588.2
Zone 2 Classroom 2 16940.0 9648.0 26588.0 0.6371 3529.2 784.3 196.1 588.2
Zone 3 Classroom 3 16940.0 9648.0 26588.0 0.6371 3529.2 784.3 196.1 588.2
Zone 4 Classroom 4 17497.0 9814.0 27311.0 0.6407 3645.2 810.0 202.5 607.5
Zone 5 Classroom 5 17497.0 9814.0 27311.0 0.6407 3645.2 810.0 202.5 607.5
Zone 6 Classroom 6 17497.0 9814.0 27311.0 0.6407 3645.2 810.0 202.5 607.5
Zone 7 Classroom 7 19662.0 10786.0 30448.0 0.6458 4096.3 910.3 227.6 682.7
Zone 8 Lobby 39177.0 19979.0 59156.0 0.6623 8161.9 1813.8 453.4 1360.3
Zone 9
Lavatory L 6082.0 1915.0 7997.0 0.7605 1267.1 281.6 70.4 211.2
Lavatory M 6082.0 1915.0 7997.0 0.7605 1267.1 281.6 70.4 211.2
Zone 10
Main
Hallway
10851.0 3902.0 14753.0 0.7355 2260.6 502.4 125.6 376.8
Mechanical
Hallway
2515.0 683.0 3198.0 0.7864
523.958 116.4 29.1 87.3
Zone 11 Office 1 10984.0 1324.0 12308.0 0.8924 2288.3 508.5 127.1 381.4
Zone 12 Office 2 9030.0 1045.0 10075.0 0.8963 1881.3 418.1 104.5 313.5
Zone 13
Conference
A
6346.0 1940.0 8286.0 0.7659 1322.1 293.8 73.4 220.3
Conference
B
6346.0 1940.0 8286.0 0.7659 1322.1 293.8 73.4 220.3

8. G r o u p I | 6
Figure2: Floor Plan of different zones

9. G r o u p I | 7
Psychrometrics for each Space
The following section includes psychometric analysis for each space using the psychometric chart.
Figure 3: Psychrometric Chart for Classrooms 1-3
Classrooms 1-3 all have the same sensible load and latent load; therefore, the figure above represents all of them.

10. G r o u p I | 8
Figure4: Psychrometric Chart for Classrooms 4-6

11. G r o u p I | 9
Figure 5: Psychrometric Chart for Classrooms 7

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Figure 6: Psychrometric chart for Conference Rooms

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Figure 7: Psychrometric chart for Lavatories

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Figure 8: Psychrometric chart for Lobby

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Figure 9: Psychrometric chart for Main Hallway

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Figure 10: Psychrometric chart for Mech Hallway

17. G r o u p I | 15
Figure 11: Psychrometric chart for office 1

18. G r o u p I | 16
Figure 12: Psychrometric chart for office 2

19. G r o u p I | 17
Table 3: Psychrometrics Analysis for each Area
Psychrometric Analysis
Area Tdb Twb Relative Humidity (%) Humidity Ratio Enthalpy (Btu/lb)
Classroom 1 74.0 61.8 50.0 0.01120 30.01
Classroom 2 74.0 61.8 50.0 0.01120 30.01
Classroom 3 74.0 61.8 50.0 0.01120 30.01
Classroom 4 74.0 61.8 50.0 0.01120 30.01
Classroom 5 74.0 61.8 50.0 0.01120 30.01
Classroom 6 74.0 61.8 50.0 0.01120 30.01
Classroom 7 74.0 61.8 50.0 0.01120 30.01
Lobby 74.0 61.8 50.0 0.01099 29.78
Lavatory L 74.0 61.8 50.0 0.01057 29.32
Lavatory M 74.0 61.8 50.0 0.01057 29.32
Main Hallway 74.0 61.8 50.0 0.01043 29.17
Mechanical Hallway 74.0 61.8 50.0 0.00996 28.66
Office 1 74.0 61.8 50.0 0.00930 27.93
Office 2 74.0 61.8 50.0 0.00930 27.93
Conference A 74.0 61.8 50.0 0.00943 28.07
Conference B 74.0 61.8 50.0 0.00943 28.07
2 73.8 65.0 60.7 0.01080 29.57
3 73.8 65.0 60.7 0.01080 29.57
4 95.0 82.0 58.0 0.02070 45.63
5 79.1 70.0 62.4 0.01328 33.59
1&6 55.0 54.0 94.0 0.00863 22.57

20. G r o u p I | 18
Psychrometrics
The following psychrometrics treat the whole building as a single zone
Table 4: Psychrometrics for the whole building
Figure 13: Psychrometric Analysis Diagram
For the psychrometrics we proceeded by getting all the values for state 0 (Supply air). For
state 0, the values were obtained by using 95 F and 82 F and the psych app. State 3/4/5 all
have the same temperature as no thermodynamic process occurs between these states.
Additionally, the problem statement tells us that there is 50% Relative humidity after going
through each zone. State 1/0/5 undergoes a mixing process. We proceeded, by finding the
enthalpy, and relative humidity at state 1.
STATE: T(db) T(wb)
Relative
humidity i W v
0 95 82 58 45.63 0.0207 14.44
1 79.1 67.7 55.9 32.05 0.01187 13.83
2 55.5 51.2 74.6 20.88 0.00696 13.12
3,4,5 74 61.8 50 27.52 0.00893 13.64

21. G r o u p I | 19
For state 1
For calculating Enthalpy at State 1
𝑖1 = .75𝑖5 + .25𝑖0
𝑖1 = .75(27.52) + .25(45.63)
𝑖1 = 32.05 𝑏𝑡𝑢/𝑙𝑏
For calculating Humidity Ratio at state 1
𝑤1 = .75𝑤5 + .25𝑤0
𝑤1 = .75(0.00893) + .25(0.0201)
𝑤1 = 0.01187
For state 2
𝐶𝑝 = 𝐶𝑝 𝑎 + 𝑊𝐶𝑝 𝑣
𝐶𝑝 = 0.24 + (0.00893) (0.444)
𝐶𝑝 = 0.244
Finding the heat transfer rate from state 2 to state 3 allows us to find the
temperature
𝑞 𝑠 = 𝑚̇ 𝑎 𝐶𝑝(𝑇3 − 𝑇2)
220386 = 487916 𝑙𝑏𝑚/ℎ𝑟 + 0.244(𝑇4 − 𝑇2)
𝑇2 = 55 ℉
𝑞𝑡𝑜𝑡𝑎𝑙 = 𝑚̇ 𝑎(𝑖3 − 𝑖2)
324201 = 487916
𝑖2 = 20.58 𝑏𝑡𝑢/𝑙𝑏
Using Enthalpy of state 2 and Tdb= 55F, gives the rest of the states' properties.

22. G r o u p I | 20
III. Duct Design and HVAC Components
The design for this entire system is based on how much energy is required for each room
or zone to be maintained at a specific temperature. Various environmental factors
influence this energy requirement such as the amount of people, building materials, and
outside weather conditions. The environmental factors add or remove heat to the system,
and therefore the HVAC system must compensate for these ever-changing conditions.
Ideally, each room would have its own unit and be able to maintain a specific desired
condition. Realistically, this scenario is not feasible, so the next alternative must be
considered. This consideration is a single air handler unit which supplied all the rooms
with conditioned air. Each room has a device to control the flow rate of air and effectively
is able to maintain specific conditions.
The total load seen below in Table 1 was found to be 324,000 Btu/hr, which equates to a
capacity of 27 tons. This load is based on key factors such as room size and the amount of
people in each room.
Table 5: Zone Loads
Area
Sensible Load
(Btu/hr)
Latent Load
(Btu/hr)
Total Load
(Btu/hr)
SHR
Classroom 1 16940.0 9648.0 26588.0 0.6371
Classroom 2 16940.0 9648.0 26588.0 0.6371
Classroom 3 16940.0 9648.0 26588.0 0.6371
Classroom 4 17497.0 9814.0 27311.0 0.6407
Classroom 5 17497.0 9814.0 27311.0 0.6407
Classroom 6 17497.0 9814.0 27311.0 0.6407
Classroom 7 19662.0 10786.0 30448.0 0.6458
Lobby 39177.0 19979.0 59156.0 0.6623
Lavatory L 6082.0 1915.0 7997.0 0.7605
Lavatory M 6082.0 1915.0 7997.0 0.7605
Main Hallway 10851.0 3902.0 14753.0 0.7355
Mechanical
Hallway
2515.0 683.0 3198.0 0.7864
Office 1 10984.0 1324.0 12308.0 0.8924
Office 2 9030.0 1045.0 10075.0 0.8963
Conference A 6346.0 1940.0 8286.0 0.7659
Conference B 6346.0 1940.0 8286.0 0.7659
Total 220386.0 103815.0 324201.0
The mass flow rates for each room was calculated by dividing the sensible load by the
specific heat capacity for air, which is 0.24 Btu/lb°F, times a temperature difference of 20
°F. This 20°F temperature variant is the different in the inside and outside temperature.
Next we were able to calculate the volumetric flow rates by dividing the mass flow rate by
the density of air at 70 °F multiplied by 60.

23. G r o u p I | 21
Now that the volumetric flow rate is known, we can start designing the ductwork using
Revit. The key component to consider in the design of this duct system is noise from high
velocity flow rates. Large volumetric rates through small area ducts create this high
velocity noise-producing condition. Table 2 shows these calculated flow rates for each
room in the building.
Table 6: Zoning Flow Rates
Area Mass Flow
Rate
(lbm/hr)
Supply
Volumetric
Flow Rate
(ft³/min)
Exhaust/Fresh
Volumetric
Flow Rate
(ft³/min)
Return
Volumetric
Flow Rate
(Ft³/min)
Classroom 1 3529.2 784.3 196.1 588.2
Classroom 2 3529.2 784.3 196.1 588.2
Classroom 3 3529.2 784.3 196.1 588.2
Classroom 4 3645.2 810.0 202.5 607.5
Classroom 5 3645.2 810.0 202.5 607.5
Classroom 6 3645.2 810.0 202.5 607.5
Classroom 7 4096.3 910.3 227.6 682.7
Lobby 8161.9 1813.8 453.4 1360.3
Lavatory L 1267.1 281.6 70.4 211.2
Lavatory M 1267.1 281.6 70.4 211.2
Main Hallway 2260.6 502.4 125.6 376.8
Mechanical Hallway 524.0 116.4 29.1 87.3
Office 1 2288.3 508.5 127.1 381.4
Office 2 1881.3 418.1 104.5 313.5
Conference A 1322.1 293.8 73.4 220.3
Conference B 1322.1 293.8 73.4 220.3
Total 45913.8 10203.1 2550.8 7652.3
The supply flow rates are what actually feed each zone, and the air handler must produce
this total amount of airflow, which is 10,203 cubic feet per minute. The unit must also be
able to carry a load of 27 tons or 324,000 Btu/hr. In addition, the air hander must
incorporate water for a transfer medium that is supplied by a chiller. This water circulates
in order to remove heat from the system.
The return volumetric flow rates are what the system recirculates or pulls from each zone.
This rate of flow is determined by the amount of fresh air to be applied to the system. The
fresh air to be added to the system is a percentage of the supply volumetric flow rate, and
in this case was 25% of that amount. The return flow rate is then calculated by subtracting
the fresh from the supply. Higher flow rates in the plenum above the hall area are
acceptable because the noise produced will be less noticeable due to movement in the hall.

24. G r o u p I | 22
With this in mind, flow velocities were kept below 1100 feet per minute in this main supply
line. For this desired quality to be met, the ducting was stepped down to smaller cross
sectional areas in order to keep velocities up as the supply line progressed to the opposite
end of the building. At the far end of the main supply line, the duct size was 28”x28” with a
flow velocity of 1100 feet per minute.
Variable air velocity equipment was used for each room in order to be able to maintain a
specific temperature, and offer efficiency. These pieces of equipment control the rate of
conditioned air entering each space by a thermostat controlling the fan speed inside of the
unit. The variable air velocity units in the hallways further reduce noise inside of each
conditioned zone. Flow velocity was also taken into consideration for the supply ducts
leaving the variable air velocity units, with the velocity goal to be under 650 feet per
minute. Table 3 shows gives the area verses velocity.
Table 7 shows each area’s ductwork with its specific size. As well as the velocity and area.
Table 7 Area and Velocity for Each Room
Supply Line Trunk Line Diffuser Line
Area Size Velocity
(ft/min)
Size Velocity
(ft/min)
Size Velocity
(ft/min)
Total Pressure
Loss (in wg)
Classroom 1 14"x14" 576 12" Φ 499 8" Φ 562 0.11
Classroom 2 14"x14" 576 12" Φ 499 8" Φ 562 0.11
Classroom 3 14"x14" 576 12" Φ 499 8" Φ 562 0.11
Classroom 4 14"x14" 600 12" Φ 519 8" Φ 462 0.09
Classroom 5 14"x14" 600 12" Φ 519 8" Φ 462 0.13
Classroom 6 14"x14" 600 12" Φ 519 8" Φ 462 0.11
Classroom 7 15"x15" 584 12" Φ 581 9" Φ 516 0.12
Lobby 20"x20" 670 19" Φ 614 10" Φ 554 0.19
Lavatories 14"x14" 564 12" Φ 517 8" Φ 404 0.03
Hallways 14" Φ 579 12" Φ 579 8" Φ 646 0.28
Office 1 14"x14" 605 12" Φ 466 8" Φ 364 0.02
Office 2 14"x14" 605 12" Φ 385 8" Φ 301 0.02
Conference Rooms 14"x14" 588 12" Φ 539 8" Φ 421 0.03

25. G r o u p I | 23
Table 8 shows each area with the diffuser flow velocity for the supply and the return.
Additionally, it specifies the number of diffusers for each area
Table 8: Duct Size per Ductwork Line
Supply Line Trunk Line Diffuser Line
Area
Size
Area
(in²)
Velocity
(ft/min)
Size
Area
(in²)
Velocity
(ft/min)
Size
Area
(in²)
Velocity
(ft/min)
Classroom1 14"x14" 196 576 12" Φ 113 499 8" Φ 50 562
Classroom2 14"x14" 196 576 12" Φ 113 499 8" Φ 50 562
Classroom 3 14"x14" 196 576 12" Φ 113 499 8" Φ 50 562
Classroom 4 14"x14" 196 600 12" Φ 113 519 8" Φ 64 462
Classroom 5 14"x14" 196 600 12" Φ 113 519 8" Φ 64 462
Classroom 6 14"x14" 196 600 12" Φ 113 519 8" Φ 64 462
Classroom 7 15"x15" 225 584 12" Φ 113 581 9" Φ 64 516
Lobby 20"x20" 400 670 19" Φ 284 614 10" Φ 79 554
Lavatories 14"x14" 144 564 12" Φ 79 517 8" Φ 50 404
Hallways 14" Φ 154 579 12" Φ 154 579 8" Φ 64 646
Office 1 14"x14" 121 605 12" Φ 79 466 8" Φ 50 364
Office 2 14"x14" 100 605 12" Φ 79 385 8" Φ 50 301
Conf. Rooms 14"x14" 144 588 12" Φ 79 539 8" Φ 50 421
Table 9 includes the face sizes and connections sizes for both the supply diffusers and
return diffusers.
Table 9: Duct Size per Ductwork Line
Diffuser Flow Velocity (ft/min)
Area Supply Return Number of Diffusers
Classroom 1 562 420 4 supply 2 return
Classroom 2 562 420 4 supply 2 return
Classroom 3 562 420 4 supply 2 return
Classroom 4 582 440 4 supply 2 return
Classroom 5 582 440 4 supply 2 return
Classroom 6 582 440 4 supply 2 return
Classroom 7 654 490 4 supply 2 return
Lobby 554 370 6 supply 3 return
Lavatories 404 390 1 supply 1 return (each)
Hallways 462 330 4 supply 1 return
Office 1 364 360 4 supply 2 return
Office 2 301 340 4 supply 2 return
Conference Rooms 421 400 1 supply 1 return (each)

26. G r o u p I | 24
Table 10: Face Size and Connection Size for Diffusers
All of the dimensions were found through the use of the software “Revit”. Data for the
ductwork is included in the Appendix section of this report.
The following pages contains figures designed in Revit. The blue ducts are the supply lines,
and the pink ducts are the return lines. The main supply line running down the middle was
32”x36” at a maximum flow velocity of 1300 feet per minute just as the air leaves the air
handler.
Supply
Diffuser
Return
Diffuser
Face Size 12"x12" 24"x24"
Connection
Size
8" Φ
12"x12"
Lobby Uses 10" Φ Connect for Supply

27. G r o u p I | 25
Figure 14 : Duct/HVAC Equipment Arrangment Front View

28. G r o u p I | 26
Figure 15 : Duct/HVAC Equipment Arrangment Rear View

29. G r o u p I | 27
Figure 16: Diffuser Arrangment

30. G r o u p I | 28
Figure 17: Duct/HVAC Equipment Arrangment Top View

31. G r o u p I | 29
Some other special pieces of HAVAC equipment can be seen in the above figures. The
bottom right corner of Figure 15 shows a mixing unit connected to the system. The mixing
unit is responsible for allowing fresh air into the system, while removing the same amount
of return air from the system. This aspect of the HVAC is critical for healthy indoor air
because with a source of fresh air, air quality would become toxic. This scenario is not seen
in our homes because of small indoor space in conjunction with the opening and closing of
doors on a daily basis.
Another interesting aspect for the duct arrangement is what to do with the return air from
the lavatories. Obviously, bathroom air recirculated throughout the building is
unacceptable for health and comfort reasons. This issue is addressed by making the
returns for both lavatories exhaust outlets, which means the pressure created inside the
lavatory from the supply line is forced to the outside. This exhaust flow rate for the
laborites is small enough to dismiss for the fresh/exhaust calculations.
Return lines also had to be taken into consideration for sizing because of noise concerns
just like the supply lines. The diffusers for the return side were 24”x24” with 12”x12”
connections and are twice as large as the supply side diffusers. This obviously allowed for
the return side to use half of the amount of diffusers as compared to the supply side. The
flow rate for the return side was kept under 400 feet per minute by using 14”x14” duct
coming off the diffusers. The main return line is 30”x30” at the end, and 12”x12” at the
farthest run.

32. G r o u p I | 30
IV. AHU/Cooling Coil
Air Handling Unit
Cooling Coil
The design of the AHU (Air Handling Unit) cooling coil was the first step in selecting a unit
for this project. In order to select the unit, it was essential that the cooling coil’s dimensions
were known so that minimum physical requirements were set. There are two main cooling
coil configurations that are typically seen in the industry: direct expansion and chilled
water. The main difference between the two is that for a direct expansion configuration,
refrigerant is used in the cooling coil tubes as compared to water in the chilled water
system. For our project, it is specified that chilled water is supplied to the AHU from an
outside source, therefore, a chilled water cooling coil configuration is used. Figure 18,
below, shows a typical setup for a counter- flow cooling coil. It is common for coil systems
of three or more rows of tubes for counter-flow to be assumed (Page 505, “Enter book
reference).
Figure 18: Counter-flow Cooling Coil Setup
Before the calculation process could be carried out, a few design parameters had to be
chosen based upon typical industry standards. The table to follow shows the parameters
that were assumed at the beginning of the coil design process.
Table 11: Cooling Coil Design Parameters
Property: Value: Units:
Air Face Velocity 500 fpm
Water Velocity 4 fps
Water Pressure
Drop 17 ft
Tube OD 0.625 in
Tube ID 0.545 in
Tube Thickness 0.04 in
Xa 1.25 in
Xb 1.083 in
fin thickness (y) 0.006 in
fins/inch 10 in^-1

33. G r o u p I | 31
Air face velocities are usually within the range of 200-550 feet per minute (fpm). Velocities
over 500 can cause water droplets to leave outer edge of fin causing moisture carry over
which is when water droplets leave the outer edges of the fins. 500 fpm was chosen for this
design as this is the most commonly seen in chilled water systems [5].
The water velocity was chosen as 4 feet per second (fps) as these values are typically seen
in between 3-6 fps but do not exceed 8 fps. [5]
The max water pressure drop in the coil is about 25’ according to [5]. Typically, for chilled
water coils the WPD is between 15-20’. 17’ was arbitrarily chosen for the WPD in this
design.
Type L Copper was the material chosen in this design as it is the most common type of pipe
seen in chilled water systems. The size of this pipe is ½ inch. This size was not only just
common within most cooling coils but Figure 14-12 in textbook provides useful j-factor
and fin information that could not be located in other sources.
Using https://sizes.com/materials/pipeCopper.htms, the actual diameter for ½ type L
copper tubing is 0.625” with an inner diameter of 0.545” which leads to a thickness of
0.04”. The rest of the coil properties that were pre-determined in Table 11 were found
using the Figure below.
Figure 19: Fin and Heat Transfer Data for Cooling Coil
As it can be seen from the previous figure, the dimensions Xa and Xb, which represent the
vertical and horizontal distance between coil pipes, respectively, are provided. The
remaining fin and heat transfer can be found according to which fin pitch was chosen and
can be found in Table 12, below. Typical values for this range from 8 to 16 fins per inch. A
value of 10 was arbitrarily chosen and its corresponding values were interpolated
appropriately. A fin thickness of 0.006” is also found from Figure 19.

34. G r o u p I | 32
Table 12: Properties of Cooling Coil
Property Value: Units:
σ 0.555 N/A
Dh 0.0133 ft
α 170.624 ft^-1
Af/A 0.9193 N/A
With all of the appropriate design assumptions made, the cooling coil calculations could
now be carried out. The first step in this process is to calculate the Reynolds number for the
water flowing through the coils. The equation to determine the Reynolds number is as
follows:
𝑅𝑒 𝐷 =
𝜌𝑉̅ 𝐷
𝜇
(1)
In equation 1, 𝜌 is the water density at 45 ᵒF, 𝑉̅ is the average water velocity, D is the inner
diameter, and 𝜇 is the dynamic viscosity of the water. With the Reynolds number
determined, the next property to calculate is the Prandtl number, which can be calculated
using equation 2.
𝑃𝑟 =
𝜇𝑐 𝑝
𝑘
(2)
Using both the Reynolds number and Prandtl number, the convective heat transfer
coefficient can be determined. This is achieved using the following equation:
ℎ̅ 𝑖 = 0.023
𝑘
𝐷
(𝑅𝑒 𝐷)0.8(𝑃𝑟)0.3
(3)
where ℎ̅ 𝑖is the convective heat transfer coefficient. The thermal conductivity (k) is based
off the same value used in the previous equations at 45 ᵒF.
𝑚̇ 𝑎 = 𝐺𝑐 𝐴 𝑐 (4)
Where Gc can be calculated by:
𝐺𝑐 =
𝐺 𝑓𝑟
𝜎
(5)
And, Gfr is found by the following equation,
𝐺𝑓𝑟 = 𝜌 𝑓𝑟 𝑉̅𝑓𝑟 (6)
Note: the subscript “fr” refers to face of the coil and “c” refers to the coil itself.
In the previous equations, 𝑚̇ 𝑎 is the mass flow rate of the air, 𝐺𝑐 is the mass velocity of the
minimum flow area, and 𝜎 is the ratio of minimum flow area to frontal area. As previously
mentioned, this value was obtained from Figure 19, where it was interpolated according to
the fin pitch assumed.
With the inner tube diameter accounted for, the outside tube diameter is focused on which
will allow working towards calculated the air side heat transfer coefficient.

35. G r o u p I | 33
The first step in this process is to find the Reynolds number for the incoming airflow. The
equation is as follows:
𝑅𝑒 𝐷 =
𝐺 𝑐 𝐷
𝜇
(7)
In the previous equation, the diameter used is the OD and the dynamic viscosity value is
that of air at a temperature of 45 ᵒF.
Equation 8, calculates the ratio of the total heat transfer area to the area of the bare, finless tubes.
𝐴
𝐴 𝑡
=
4
𝜋
𝑥 𝑏
𝐷ℎ
𝑥 𝑎
𝐷
𝜎 (8)
Where Xa and Xb are the row height and width spacing found in Figure 19, respectively, and Dh
is the hydraulic diameter which can be found in Table 12. Remember, the hydraulic diameter
was determined using Figure 19. The value for this variable was determined according to the fin
pitch that was assumed.
In calculating the outside air heat transfer coefficient, the j-factor must be calculated. The j-factor
is read from Figure 20, but first the JP parameter must be calculated. The JP parameter is found
by:
𝐽𝑃 = 𝑅𝑒 𝐷
−0.4
(
𝐴
𝐴 𝑡
)
−0.15
(9)
Once the JP parameter was calculated, the j-factor could be evaluated using the figure below.
Using this value and fin pitch the j-factor determined was 0.007 (dimensionless).
Figure 20 Heat Transfer correlation for smooth plate-fin-tube coils
With the j-factor now found, the heat transfer coefficient of the air can now be solved for using
the following equation:

36. G r o u p I | 34
ℎ̅ 𝑜 = 𝑗𝐺𝑐 𝑐 𝑝 (
𝜇𝑐 𝑝
𝑘
)
−
2
3
(10)
where Cp, is the specific heat of air and ℎ̅ 𝑜 is the air heat transfer coefficient.
The next objective is to calculate the overall heat transfer coefficient. The first step in reaching
this value is to calculate the two dimensions: L and M. The equations for these two values
involve referring to the previously obtained Xa and Xb dimensions. L and M can be computed by:
𝐷𝑖𝑚 𝐿 =
𝑥 𝑎
2
(11)
𝐷𝑖𝑚 𝑀 =
[(
𝑥 𝑎
2
)
2
+𝑥 𝑏
2
]
1/2
2
(12)
Using the previously obtained dimensions L and M, the 𝜓 and 𝛽 parameters can be found. The
equations for these two parameters are as followed:
𝜓 =
𝑀
𝑟
(13)
𝛽 =
𝐿
𝑀
(14)
The variable “r” is the outer radius of the copper tubes.
Using the two previous found values, we can now calculate the ratio of the equivalent fin radius
to outer tube radius by the following equation:
𝑅 𝑒
𝑟
= 1.27𝜓(𝛽 − 0.3)
1
2 (15)
where 𝑅 𝑒 is the equivalent fin radius.
The next parameter to be calculated is ∅, which is used in the calculation of fin efficiency. The
parameter can be calculated by:
∅ = (
𝑅 𝑒
𝑟
− 1) [1 + 0.35ln (
𝑅 𝑒
𝑟⁄ )] (16)
Following this calculation, the final parameter, m, for the fin efficiency calculation can be found
using the following equation:
𝑚 = (
2ℎ̅ 𝑜
𝑘𝑦
)
1/2
(17)
where y is the fin thickness which is found from Figure 19, and k is the thermal conductivity of
aluminum.
With the previous parameters calculated, the fin efficiency can now be found by:
ɳ =
tanh[𝑚𝑟∅]
𝑚𝑟∅
(18)

37. G r o u p I | 35
The surface effectiveness can be calculated using the fin efficiency and the ratio,
𝐴 𝑓
𝐴
, which can
be found in the graph. It is dependent on the fin pitch chosen in Figure 19. The equation for
surface effectiveness is as follows:
ɳ 𝑠𝑜 = 1 −
𝐴 𝑓
𝐴
(1 − ɳ) (19)
Before the overall heat transfer coefficient can be calculated, the ratio of the water-side to air-
side heat-transfer areas must be computed, which can be achieved by the following equation:
𝐴 𝑖
𝐴 𝑜
=
𝜋𝐷 𝑖
𝑥 𝑎 𝑥 𝑏 𝛼
(20)
where Di is the inner tube diameter and 𝛼 is a parameter found using Figure 19.
With all the necessary information needed to determine the overall heat transfer coefficient, the
following equation can now be completed:
1
𝑈 𝑜
=
1
ℎ̅ 𝑜ɳ 𝑠𝑜
+
1
ℎ̅𝑖(𝐴 𝑖 𝐴 𝑜⁄ )
(21)
Obtaining the overall heat transfer coefficient concludes the water to air cooling coil continuous
plate-fin-tube. The next step in the design process is to determine the geometric configuration of
the coil which requires the computation of the NTU and fluid capacity rates of the cooling coil.
The first step in the process of designing the geometric configuration of the coil is to determine
the mass flow rate of the air which can be determined by the equation to follow:
𝑚̇ 𝑎 = 𝜌𝑄̇ (22)
where 𝜌 is the density of air and 𝑄̇ is the volumetric flow rate of the incoming air. The next
equation calculates the corrected, total heat transfer rate of the AHU. The equation for this is:
𝑞̇ 𝑡𝑜𝑡 = 𝑚̇ 𝑡𝑜𝑡(𝑖5 − 𝑖6) (23)
where 𝑚̇ 𝑡𝑜𝑡 is the total mass flowrate of all zones and i represents the enthalpy at states 5 and 6.
Using the corrected total load, both the heat capacity rate of air and water can be calculated using
the following equations:
𝑞̇ 𝑡 𝑜𝑡 = 𝐶 𝑎𝑖𝑟(𝑇6 − 𝑇5) (24)
𝑞̇ 𝑡 𝑜𝑡 = 𝐶 𝑤(𝑇𝑖𝑛 − 𝑇𝑜𝑢𝑡) (25)
where T represents the temperatures at state 5, state 6, entering the coil, and leaving the coil, Cair
is the heat capacity rate of the air and is also equivalent to Cmin, and Cw is the heat capacity rate
of the water which is equal to Cmax.

38. G r o u p I | 36
The NTU can now be determined by using the ratio of the previously found heat transfer rates
and the effectiveness of the heat exchanger which is to be calculated. This involves using Figure
21, which provides the proper information needed to determine the NTU.
The effectiveness of the heat exchanger is the ratio of the actual heat transfer rate over the
maximum possible heat transfer rate. The equation for this is as follows:
𝜀 =
𝑇6−𝑇5
𝑇 𝑖𝑛−𝑇𝑜𝑢𝑡
(26)
Using this effectiveness value, the NTU can now be obtained using the following figure.
Figure 21: Effectiveness of Cross-flow Exchanger with Fluids Unmixed
Using the previously calculated values, the NTU was determined to be 0.48. This value is then
used to determine the overall heat transfer area. This is done by the following equation:
𝑁𝑇𝑈 =
𝑈 𝑜 𝐴 𝑜
𝐶 𝑚𝑖𝑛
(27)
Once the area is found, the volume can be evaluated using:
𝑉 =
𝐴 𝑜
𝛼
(28)
As mentioned in the beginning of this section, the air face velocity was assumed previous to the
design calculation process. Using this value, the area of the face of the coil can be solved for
using:
𝐴𝑓𝑟 =
𝑄̇
𝑉̅ 𝑓𝑟
(29)

39. G r o u p I | 37
With this value calculated the next geometric property to be determined is the depth of the coil
which is computed using the following equation:
𝐿 =
𝑉
𝐴 𝑓𝑟
(30)
The number of rows in the system can be determined as well using the length previously
determined and the horizontal distance between the tubes. The equation is as follows:
𝑁 𝑅 =
𝐿
𝑋 𝐵
(31)
The value of NR must be an integer and a multiple of two.
This concludes the design of the geometric configuration of the cooling coil. The next important
design parameter is to calculate the pressure loss that will occur for the air flow through the coil.
The first step is to calculate the following ratio:
𝐴
𝐴 𝑐
=
𝛼𝑉
𝜎𝐴 𝑓𝑟
(32)
The mean density is calculated next,
𝜌 𝑚 =
𝑃
2𝑅
(
1
𝑇5
+
1
𝑇6
) (33)
where P is the atmospheric pressure and R is the heat exchanger parameter constant.
In order to calculate the pressure drop, the friction factor must be found. To find the friction
factor the parameter FP must be calculated. This can be done by the following equation:
𝐹𝑃 = 𝑅𝑒 𝐷
−0.25
(
𝐷
𝐷∗
)
0.25
[
𝑥 𝑎−𝐷
4(𝑠−𝑦)
]
−0.4
[
𝑥 𝑎
𝐷∗
− 1]
−0.5
(34)
Using this value for FP along with the amount of fins per inch which was chosen before the
design calculations, the friction factor can be obtained from the following figure.

40. G r o u p I | 38
Figure 22: Heat Transfer Correlation for Smooth Plate-Fin-Tube Coils
From reading the graph, the friction factor for this design was chosen to be 0.025.
With the friction factor now known, the pressure drop can now be calculated. The equation for
the pressure drop is as follows:
∆𝑃𝑜 =
𝐺 𝑐
2
2𝑔 𝑐 𝜌1
[(1 + 𝜎2) (
𝜌1
𝜌2
− 1) + 𝑓 (
𝐴
𝐴 𝑐
) (
𝜌1
𝜌 𝑚
)] (36)
where 𝑔𝑐 is the gravitational constant, 𝜌1 is the density of the air at the inlet, and 𝜌2 is the air
density at the exit of the AHU.
This now completes the air side pressure loss calculations for the air handling unit. The next
series of calculations will determine the pressure loss in the tube side of the system. The first step
in this process is to determine the flow cross-sectional area of the water.
𝐴 =
𝐶 𝑚𝑎𝑥
𝑉̅ 𝜌𝑐 𝑝
(37)
The number of tubes can now be calculated for this AHU by using the following equation:
𝑁𝑡 =
4𝐴
𝜋𝐷𝑖
2 (38)
The value of this variable must be an integer. After the calculations were performed, this value
was determined to be 35.2 but rounded to 40. This effects the next equation which determines the
height of the cooling coil.
𝐻 = (𝑛𝑢𝑚𝑏𝑒𝑟 𝑜𝑓 𝑡𝑢𝑏𝑒𝑠)𝑥 𝑎 = 40𝑥 𝑎 (39)
The width of the coil is the next geometric property to be determined. This is done by the
following:
𝑊 =
𝐴 𝑓𝑟
𝐻
(40)

41. G r o u p I | 39
The length of the coil can now be determined,
𝐿 𝑤 = 𝐾𝑊 (41)
where K is the loss coefficient associated with each bend and was predetermined before design
calculations to be 2.
In order to determine the lost head within the tubes, the Moody friction factor must be
determined. This can be done by using the friction factor and Reynolds number and reading the
following figure.
Figure 23: Moody Diagram for Pipe Flow Friction Factor
Once the friction factor was determined from the previous figure, the tube side pressure loss can
be determined:
𝑙 𝑓𝑤 = 𝑓
𝐿 𝑤
𝐷 𝑖
𝑉̅2
2𝑔 𝑐
+ 𝐾𝑁𝑏
𝑉̅2
2𝑔 𝑐
(42)
where 𝑁𝑏 is the number of return bends in each circuit.
The final stage of the design calculations involves calculating the water flow rate and rate of heat
transfer of water flowing through the coils.
The following equation will calculate the mass flow rate of water through the tubes:
𝑚̇ 𝑤 = 𝜌 𝑤 𝐴𝑉̅ (43)
With this value now calculated, the rate of heat transfer of the tube water can now be found:

42. G r o u p I | 40
𝑞̇ 𝑤 = 𝑚̇ 𝑤∆𝑇 (44)
To convert this value into GPM involves finding a conversion factor which is accomplished by:
𝜌 𝑤 𝑐 𝑝=500 (45)
This conversion factor is now used in converting the heat transfer rate into GPM by the
following conversion:
𝐺𝑃𝑀 =
𝐵𝑡𝑢
ℎ𝑟⁄
500∗(𝑇 𝑖𝑛−𝑇𝑜𝑢𝑡)
(46)
This now concludes the series of design calculations used for this AHU design. A summary of
the calculated properties is to follow:
The following table presents the temperatures used through the calculation process:
Table 13: AHU Design Temperatures
Property Value Unit
State 1 79.1 F
State 2 55.5 F
Inlet H2O 45 F
Exit H2O 55 F
Delta T H20 10 F
The following table presents the geometric dimensions calculated during the design process:
Table 14: AHU/CC Dimensions
Property Value Unit
Volume of HT 7.11 Ft^3
Face Area 20.41 Ft^2
Depth of HT 4.18 in
Number of Rows 3.86 N/A
Actual Number of Rows 4.00 N/A
Number of Tubes 35.23
*USE
40
Number of Bends 9.00 N/A
Tubes per Row 10 N/A
H 50.00 in
H 4.17 ft
W 58.77 in
W 4.90 ft
Tube Length (Flow
Length) 39.18 ft

43. G r o u p I | 41
The following table presents the pressure losses calculated during the design process:
Table 15: Calculated Pressure Losses
Property Value Unit
Air Side Pressure Loss 2.602767252 lbf/ft^2
Air Side Pressure Loss 0.500532164 in*wg
Tube Side Pressure
Loss 9.144435757 ft
This last table presents the flowrates determined for the AHU/CC system:
Table 16: Determined System Flow Rates
Property Value Unit
Air Flow Rate 10203.1 cfm
Total Supply Mass
Flowrate 45913.8 lbm/hr
Total Load 512857.146 Btu/hr
water flowrate 51306.26176 lbm/hr
GPM 102.6125235 GPM
Air Handling Unit
After all design calculations were performed for the AHU and cooling coil, the data was
analyzed and an air handling unit was chosen accordingly. The unit itself was chosen based
upon the entering and exiting air mass flowrates. For this design, the incoming volumetric
flow rate was calculated to be 10203.1 cubic feet per minute, and the exiting air volumetric
flowrate was found to be 7652.3 cubic feet per minute. Using the flowrates, an appropriate
air handling unit was chosen from Dunham-Bush, model RT 26 This specific model is sized
for volumetric flow rates within the range of 7000-15600 cfm, and has a nominal face area
of 26 𝑓𝑡2
. The unit’s shell and inside design resembles the following two figures.

44. G r o u p I | 42
Figure 24: Model of RT 26 Dunham-Bush Rooftop AHU
Figure 25: Interior Design of RT 26 Dunham-Bush Rooftop AHU
Dunham-Bush prides themselves on the excellent standard at which the outer casing of the
AHU is constructed. The AHU is designed to be protected from any water entry due to
weather. Standing flanges raise the unit 1” from the ground which eliminate the possibility
of any water entry from the ground level into the unit. The top panels are pitched to the
cabinet sides with no pockets to collect rain, and an overhang is installed on the unit so no
rainwater will drip onto the door tops. All exposed panels are constructed of 18-gauge steel
and are finished with climate proof coatings. The unit is ensured to be sealed with absolute
air tightness through the use of a gasket, which is closed cell foam. The cell foam method is
far superior to caulking and further ensures no heat loss will be experienced by the unit.
The modular interior design of the AHU, as seen in Figure 25, minimizes the static
pressure resistance due to its straight thru design that allows low velocity airflow through
the unit. This design is very versatile as there are a total of 22 possible modular sections
that can be selected.

45. G r o u p I | 43
The water cooled coils come with the following options: (The bolded options represent the
values calculated for this design)
Material: Type 5 Copper
O.D.: 0.625”
Rows: 3, 4, 5, 6, 8, 10
Fins Per Inch: 6, 8, 10, 12, 14
A picture of the cooling coil for the chosen AHU is in the following figure.
Figure 26: Cooling Coil System for RT 26 AHU
With unit size chosen, the coil face area is given as 25.5 𝑓𝑡2
. This is a good size unit because
the calculated area needed for the designed coil from calculations was 20.4 𝑓𝑡2
.
The next component that was chosen based off of the previous design calculations was the
supply fan. The supply fan was designed to handle an incoming air flow rate of 10203.1
cubic feet per minute with a total static pressure loss of 0.5 inches of water. The fan was
chosen from the following table:

46. G r o u p I | 44
Table 17: Supply Fan Table Provided by Dunham-Bush
As seen in the above table, the chosen fan for this design is a 4.22 BHP, 575 RPM size 500
forward curved fan. The forward curved fans come with an adjustable fan/motor base. The
motor and drive are all built into a fan and motor sub-assembly. Only 1 supply fan is used
in the AHU which give the unit a very quiet performance with low energy consumption.
The figure below depicts a forward curved fan:
Figure 27: Model of a Forward Curved Fan
The last component chosen for the calculated design parameters is the return fan. The fan
was designed for a flow rate of 7652.3 cubic feet per minute and the same pressure loss.
The return fan was picked according to the smallest possible fan that could be found. The
fan was chosen from the table to follow.

47. G r o u p I | 45
Table 18: Return Fan Table Provided by Dunham-Bush
As seen above, the chosen fan has an rpm of 595 and brake horsepower of 3.04. The fan
type is a size 450 forward curved fan.
Overall, the components picked for the AHU closely match the values received during the
design calculation process. When assembled, the AHU system should provide good
performance and quality, cooled airflow to the school building.

48. G r o u p I | 46
V. Hydronics
The hydronic system is responsible for transporting chilled water from the condenser to
the air handling unit (AHU), returning heated water from the AHU back to the condenser,
and transporting heated water from the evaporator to the cooling tower, as well as
returning the cooled water from the tower back to the evaporator.
The piping chosen for the hydronic system is schedule 40 commercial steel pipe. The
calculated values for each of the piping systems is presented in Tables 1 through 3 below.
The tables present the flow rates, pipe size, and losses for pipe lengths, fittings and valves.
The resources used in the calculations came from McQuiston’s Heating, Ventilating and Air
Conditioning, 6th edition, and follow the tables.
Table 19: Chilled Water Primary Loop
Chilled Water Primary
Loop
Volumetric Flow Rate (gpm) 2400
Velocity (ft/s) 10
Diameter (in.) 10
Friction Factor ft
Head Loss/ 100 feet 2.6
Small Pipe Diameter
(in.) 3 0.017
Pipe Length (ft.) 71
Large Pipe Diameter
(in.) 10 0.013
Total Pipe Head Loss 1.988 Chiller Diameter (in.) 19 0.012
Valves Qty. K
K
(coeff.)
Equivalent
Length (ft.)
Total Head Loss
(ft.)
Ball 9 3 0.014 4 1.01
Check 2 2 0.014 3 0.17
Globe 2 340 0.014 520 14.56
Fittings
Elbow (90°) 2 30 0.014 32 1.79
Tee (Branch) 7 60 0.014 60 11.76
Head Loss through straight
pipe 1.99
Head Loss through chiller 28.00
Grand Total Head Loss (ft.) 59.28

49. G r o u p I | 47
Table 20 : Chiller to AHU
Chiller to AHU
Volumetric Flow Rate (gpm) 103
Velocity (ft/s) 4
Diameter (in.) 3
Friction Factor ft
Head Loss/ 100 feet 2.5
Small Pipe Diameter
(in.) 3 0.018
Pipe Length (ft.) 1853
Large Pipe Diameter
(in.) 10 0.014
Total Pipe Head Loss 46.33 Chiller Diameter (in.) 0.012
Valves Qty. K
K
(coeff.)
Equivalent
Length (ft.)
Total Head Loss
(ft.)
Ball 7 3 0.018 10.5 0.26
Check 2 2 0.018 1 0.05
Fittings
Elbow (90°) 17 30 0.018 8 3.40
Tee (Branch) 2 60 0.018 15 0.75
Head Loss through straight
pipe 46.33
Head Loss through vertical
pipe 14.00
Head Loss through AHU 10.00
Grand Total Head Loss (ft.) 74.79

50. G r o u p I | 48
Table 21 : Chiller to Cooling Tower
Chiller to Cooling Tower
Volumetric Flow Rate (gpm) 2900
Velocity (ft/s) 8.5
Diameter (in.) 12
Friction Factor ft
Head Loss/ 100 feet 1.5
Small Pipe Diameter
(in.) 3 0.017
Pipe Length (ft.) 165
Large Pipe Diameter
(in.) 12 0.013
Total Pipe Head Loss 2.475 Chiller Diameter (in.) 0.012
Valves Qty. K (ft.)
K
(coeff.)
Equivalent
Length
Total Head Loss
(ft.)
Ball 2 3 0.013 10 0.15
Check 1 2 0.013 4.5 0.07
Globe 2 340 0.013 350 10.50
Fittings
Elbow (90°) 6 30 0.39 210 3.15
Tee (Branch) 1 60 0.78 70 1.05
Head Loss through straight
pipe 2.48
Head Loss through vertical
pipe 17.00
Head Loss through chiller 28.00
Grand Total Head Loss (ft.) 62.39
Figure 28: Formulas, Definition of terms and Values of ft.

51. G r o u p I | 49
Figure 29: Resistance Coefficients K for Various Valves and Fittings.
Figure 30: Equivalent Lengths L and L/D and Resistance Coefficient K.

52. G r o u p I | 50
Figure 31: Friction Loss of Water in Commercial Steel Pipe (Schedule 40).
The chilled water supply traveling from the chiller plant to the AHU consists of two loops,
primary and secondary. The primary pumping system services the return water from the
AHU to the chillers. The secondary pumping system services the AHU of the new building
with the chilled water and returns it back to the chilled water return header. The primary
and secondary pumping systems will each have two pumps piped in such a fashion as to
allow either redundancy, maintenance or demand.
Table 22 : Chilled Water Loop Pumps
Pump Flowrate, Q (gpm) Head, h (Ft. of H2O) Motor Speed, w (rpm)
NPSHR
(ft.)
NPSHA
(ft.)
CHWP-1 2400 60 1760 14 42
CHWP-2 2400 60 1760 14 42
CHWS-1 103 75 1760 13 41
CHWS-2 103 75 1760 13 41
The primary pumps chosen were TACO Model SFI8013-1760-100 for 60 feet of head. The
pump curve is presented below.

53. G r o u p I | 51
Figure 32: Primary Pump Curve
The secondary pumps chosen were TACO Model SKS3011-1760-7.5 for 75 ft. of head.
Figure 33: Secondary Pump Curve

54. G r o u p I | 52
The chiller to cooling tower system consists of two redundant pumps. Each pump will have
the capacity to handle the full load.
Table 23 : Chiller to Cooling Tower Pumps
Pump Flowrate, Q (gpm) Head, h (Ft. of H2O) Motor Speed, w (rpm)
NPSHR
(ft.)
NPSHA
(ft.)
CHWR-1 2900 63 1760 14 40
CHWR-2 2900 63 1760 14 40
The pumps chosen for the chiller to cooling tower were TACO Model SKS1213B-1760-100.
Figure 34: Cooling Tower Pump Curve

55. G r o u p I | 53
The piping arrangements were modeled using the Applied Flow Technology (AFT) Fathom
software to make a comparison with the hand calculations. The following figures present
the model for the primary and secondary loop. They include the evaporator side of the
chillers and air handling unit (AHU), followed by a screenshot of the output after running
the software.
Figure 35: Fathom Model for Primary and Secondary to AHU Loop.

56. G r o u p I | 54
Figure 36: Fathom Output for Primary and Secondary to AHU Loop.

57. G r o u p I | 55
The following figures present the model for the chiller to cooling tower loop. They include
the condenser side of the chiller and the cooling tower, followed by a screenshot of the
output after running Fathom.
Figure 37: Fathom Model for Chiller to Cooling Tower Loop.

58. G r o u p I | 56
Figure 38: Fathom Output for Chiller to Cooling tower Loop.

59. G r o u p I | 57
VI. Chiller Plant
The chiller system works as refrigeration cycle. Figure 1 is a diagram of the refrigeration
cycle for fluid 134-A. From Process 1-2 Isentropic compression takes place. The fluid leaves
the evaporator at state 1 in a low pressure state, and flows through the compressor and
becomes super-heated fluid. During Process 2-4, the refrigerant flows at constant pressure
from the compressor into the condenser where heat is rejected from the system. The
refrigerant fluid then exits the condenser during state 3, and enters the throttling valve at
state 4. During this process, Process 3-4, the refrigerant ends in a two-phase liquid vapor
mixture. Process 4-1 is the final process of the cycle where the refrigerant flows at
constant pressure through the evaporator.
For this project we proceeded to select a Chiller that would meet the requirements of 1000
Tonnage specified by the problem statement, and provide the 45 oF required for the AHU
unit. Additionally, we designed a chiller system that would meet the requirements. For the
design we ignored the losses caused by entropy. The chiller system was analyzed as an
ideal-vapor compression cycle.
Figure 39: T-S Diagram for Refrigerant 134-A

60. G r o u p I | 58
Figure 40: Direct Expansion Chiller Schematic
The figure above, shows the layout of the chiller system used in this project. The Primary
supply loop refers to the water going to the hydronic system.
Hand calculations were performed to determine the required refrigerant temperatures, the
mass flow rate of water, and the mass flow rate of the refrigerant, needed to meet the
requirements set by the AHU to satisfy the sensible and latent loads of each room in the
building. The 1000 Tonnage requirement set by the problem statement was also
considered. The process of finding the specified values is shown below:
1000 𝑇𝑜𝑛𝑠 ∗ 12,000 = 12,000,000 𝐵𝑡𝑢/ℎ𝑟
We assumed the temperature of the refrigerant to be 30oF.
For state 1:
From R-134a Tables
𝑃1 = 40. 788 𝐿𝑏𝑓/𝑖𝑛2
ℎ1 = ℎ 𝑔 = 106.01 𝑏𝑡𝑢/𝑙𝑏
𝑆1 = 𝑆 𝑔 = 0.2196
For state 2:
We assumed isentropic process, so sg1=sg2

61. G r o u p I | 59
Since, The Temperature has to be above 95 oF, from the Table A-12E from Moran’s
Thermodynamics book, we selected pressure table p=140 lbf/in2 , Tsat= 100.56, S2=0.2161.
120℉ − 𝑇2
120 − 100.56℉
=
0.2254 − 0.2196
0.2254 − 0.2161
𝑇2 = 107.87℉
120.25 − ℎ2
120.25 − 114.95
=
0.2254 − 0.2196
0.2254 − 0.2161
ℎ2 = 116.94 𝑏𝑡𝑢/𝑙𝑏
ℎ 𝑉𝑎𝑝𝑠𝑎𝑡 = 114.95 𝑏𝑡𝑢/𝑙𝑏
For State 3
𝑇3 = 100.56℉
𝑃3 = 140 𝑙𝑏/𝑖𝑛2
(Same Pressure Line)
105℉ − 100.56℉
105℉ − 100℉
=
0.0930 − 𝑠𝑓3
0.0930 − 0.0898
𝑠3 = 0.0901584 𝑏𝑡𝑢/𝑙𝑏 𝑅
105℉ − 100.56℉
105℉ − 100℉
=
46.01 − ℎ𝑓3
46.01 − 44.23
ℎ3 = 44.42936 𝐵𝑡𝑢/𝑙𝑏𝑚
For State 4
For throttling process h4=h3
𝑇4 = 30℉
𝑃4 = 40.788℉
ℎ4 = 44.429℉

62. G r o u p I | 60
Flow Rate of Refrigerant
𝑄 𝐿
̇ = 𝑚̇ 𝑅134𝑎(ℎ1 − ℎ4)
𝑚̇ 𝑅134𝑎 =
12,000,000 𝑏𝑡𝑢/ℎ𝑟
(106.01 − 44.42936)
Work of Compressor
𝑊𝑐
̇ = 𝑚̇ 𝑅134𝑎(ℎ2 − ℎ1) (47)
𝑊𝑐
̇ = 19,504,936(116.944 − 106.01)
𝑊𝑐
̇ = 2,132,114.363 𝑏𝑡𝑢/ℎ𝑟
Heat Transfer of Condenser
𝑄 𝐻
̇ = 𝑚̇ 𝑅134𝑎(ℎ2 − ℎ1) (48)
𝑄 𝐻
̇ = 195,069.9326(116.944 − 106.01)
𝑄 𝐻
̇ = 14,145,425.94 𝑏𝑡𝑢/ℎ𝑟
Flow Rate of water for Condenser
𝑄 𝐻
̇ = 𝑚̇ 𝑐𝑤 𝑐𝑝𝑐𝑤∆𝑇 (49)
𝑚̇ 𝑐𝑤 =
14,145,425.94
(0.999)(10)
𝑚̇ 𝑐𝑤 = 1,415,958.522 lbm/hr
Flow Rate of water for Evaporator
𝑚̇ 𝑐𝑤 =
12,000,000
(1)(10)
𝑚̇ 𝑐𝑤 = 1,200,000 𝑙𝑏𝑚/ℎ𝑟

63. G r o u p I | 61
The chiller we have selected is from Trane can provide the 1000 Tonnage needed to fulfill
the system requirements. We have decided to go with two units of CVHF-080L-142L/IECU,
so that there is redundancy in case one of them shuts off the HVAC system won’t stop
working. This specific water chiller we picked meets the requirements for the AHU water
flow rate, with a minimum flow rate of 1135 GPM Additionally, it has the required
temperatures towards the AHU unit of 45 F, and it meets the requirements for the cooling
tower. For purpose of redundancy we have decided to use to Chiller Plants working at
34.58% percent each. The selected Chillers work with a tonnage range of 1000-1300.
Figure 41: Chiller System CVHF-080L-142L/IECU

64. G r o u p I | 62
Table 24: Selected Chiller Specifications
Chiller Specs
Model Series CVHF
Tonnage Range for Model 350-2000 Ton
Model Number CVHF-080L-142L/IECU
Evaporator Size 080L
Condenser Size 142L
Tonnage 1300
Capacity Running For Each 38.46 %
Evaporator Pipe Connection Size 10-inch
Condenser Pipe Connection Size 10-inch
Number of Passes 1 Pass
Evaporator Maximum Flow Rate 8394 GPM
Evaporator Minimum Flow Rate 1135 GPM
Condenser Maximum Flow Rate 6407 GPM
Condenser Minimum Flow Rate 1747 GPM
Length 180.3 in.
Height 121.6 in.
Width 121.7 in.
Total Volume Occupied 2,668,209.216 in3
Evaporator Temperature Water Outlet 45oF
Evaporator Temperature Water Inlet 55oF
Condenser Temperature Water Inlet 95oF
Condenser Temperature Water Exit 85oF
Additionally, from selecting a chiller, we have decided to design one. For the design chiller
we used a similar approach to the first project.
The first calculation is the tube clearance. This is the clearance between adjacent tubes. The
equation to calculate this value is as followed:
𝐶 = 𝑃𝑡 − 𝑂𝐷𝑡 (50)
Where Pt is the tube pitch and ODt is the outer diameter of the tube. The tube pitch for our
design was chosen as a square pitch. This means that if you were to look at a cross sectional
view of the tubes, they would be arranged in square patterns.
The next parameter to calculate is the baffle spacing, which can be calculated as followed:
𝐵 =
𝐿
𝑁 𝐵+1
(51)
Where L is the length of the tubes and NB is the number of baffles within the heat exchanger
which is user defined. The more baffles within a heat exchanger increases the effectiveness
because it improves heat transfer. The improved heat transfer is due to the more resistance
the incoming water encounters as it passes through the heat exchanger. This gives the
water a more directed path and allows it to better transfer heat between the tubes.
With the baffle spacing and clearance calculated, the flow area within the shell can be
calculated as:

65. G r o u p I | 63
𝐴 𝑠 =
𝐷𝑠 𝐶𝐵
𝑃𝑡
(52)
Where Ds is the user defined shell diameter, C is the clearance previously calculated, B is the
baffle spacing also previously calculated, and Pt is the user defined tube pitch.
The tube flow area can be calculated as followed:
𝐴 𝑡 =
𝑁𝑡 𝜋(𝐼𝐷𝑡
2)
4𝑁 𝑝
(53)
Nt is the number of tubes within the exchanger which is reliant upon the shell diameter and the
number of passes. IDt is the inner tube diameter which is user defined along with Np which is
the number of passes.
With the flow areas calculated, the shell and tube velocities can now be found:
𝑉𝑠 =
𝑚̇ 𝑠
𝜌𝐴 𝑠
(54)
Where ms is the water flow rate into the shell, 𝜌 is the density of the water, As is the flow area of
the water into the shell.
The flow velocity can also be calculated for the tube fluid as followed:
𝑉𝑡 =
𝑚̇ 𝑡
𝜌𝐴 𝑡
(55)
Where mt is the mass flow rate of the refrigerant passing through the tubes, 𝜌 is the density of the
vapor within the two phase flow of refrigerant, and At, as previously defined, is the tube flow
area.
The next value to calculate is the equivalent diameter. The calculation of this value depends on
the pitch chosen, triangular or square. For our design, as previously mentioned, a square pitch
was chosen. Therefore, the calculation is as followed:
𝐷𝑒 =
4𝑃𝑡2−𝑝𝑖(𝑂𝐷𝑡2)
𝑝𝑖(𝑂𝐷𝑡)
(56)
Where Pt is the tube pitch and ODt is the outer diameter of the tubes.
The next value to calculate are the Reynolds number for the shell and tube. These are calculated
using the following formulas:
𝑅𝑒𝑡 =
𝑉𝑡 𝐼𝐷𝑡 𝜌
𝜇
(57)
And,
𝑅𝑒𝑠 =
𝑉𝑠 𝐷 𝑒 𝜌
𝜇
(58)
Where Ret is the Reynolds number for the tube and Res is the Reynolds number for the shell. For
the tube, Vt is the tube fluid velocity, IDt is the inner tube diameter, 𝜌 is the density of the
refrigerant vapor, and 𝜇 is the dynamic viscosity of the vapor. For the shell Reynolds number, Vs
is the fluid in the shell, De is the equivalent diameter, 𝜌 is the density of the water, and 𝜇 is the
dynamic viscosity of the water within the shell.
The Nusselt number is then calculated after the Reynolds number. The shell side is the easier
calculation and is found using the following equation:
𝑁𝑢 𝑠 =
ℎ 𝑜 𝐷 𝑒
𝑘 𝑓
= 0.36𝑅𝑒𝑠
0.55
𝑃𝑟
1
3 (59)
Where ho is the heat transfer coefficient in the tube, De is the equivalent diameter, and kf is the
thermal conductivity.

66. G r o u p I | 64
𝑁𝑢 𝑡 = 𝐶1 [(
𝐺 𝑣 𝐼𝐷𝑡
𝜇 𝑙
)
2
(
𝐽∆𝑥𝑖 𝑓𝑔 𝑔 𝑐
𝐿𝑔
)]
𝑛
(60)
Where:
 J = Joule equivalent
 Δx = change in quality of R134a
 ifg = enthalpy of vaporization
 n = constant = 0.4 (0.3 if the fluid was being cooled)
 𝜇 = dynamic viscosity of R-134a (Liquid)
 𝐺𝑣 =mass flux
 C1 = 8.2*10-3
 L = length of tube
 g = gravity
The Nusselt Number for the condenser is calculated differently than for the evaporator. This
equation depends on the value for the Reynolds number. The parameters for choosing the
equation can be seen in the problem statement. Since our Reynolds number was greater than
10,000, the equation used was:
𝑁𝑢 𝑡 =
ℎ 𝑖 𝐷 𝑖
𝑘 𝑙
= 0.1 (
𝑐 𝑝,𝑙 𝜇 𝑙
𝑘 𝑙
) (𝑃𝑟𝑙)
1
3 (
𝑖 𝑓𝑔
𝑐 𝑝,𝑙∆𝑡
)
1
6
(
𝐺 𝑣 𝐼𝐷𝑡
𝜇 𝑙
(
𝜌 𝑙
𝜌 𝑣
)
1
2
)
2
3
(61)
Where:
 ifg = enthalpy of vaporization
 𝑐 𝑝 = specific heat of R-134a
 𝛥𝑇 = difference in the refrigerant temperature and the average water temperature.
 𝑃𝑟 = Pandlt number
 𝐺𝑣 = mass flux
 𝜇 = dynamic viscosity of R-134a (Liquid)
 𝜌 𝑣 = density of vapor
 𝜌𝑙 = density of liquid
 𝑘𝑙 = thermal conductivity in liquid phase
The heat transfer coefficients can be calculated by the following three equations:
ℎ𝑖 =
𝑁𝑢 𝑡 𝑘 𝑡
𝐼𝐷𝑡
(62)
ℎ 𝑡 =
ℎ 𝑖 𝐼𝐷𝑡
𝑂𝐷𝑡
(63)
ℎ 𝑜 =
𝑁𝑢 𝑠 𝑘 𝑠
𝐷 𝑒
(64)
Where hi is the heat transfer coefficient for the tube, ht is the heat transfer coefficient for the
evaporator, and ho is the heat transfer coefficient for the condenser.

67. G r o u p I | 65
Nu is the Nusselt number for the appropriate component, tube or shell. K is the thermal
conductivity of either the fluid in the tube or shell, De is the equivalent diameter, ODt is the
outside tube diameter, and IDt is the inside tube diameter.
With the individual heat transfer coefficients solved for, the overall heat transfer coefficient can
now be calculated.
𝑈 𝑜 =
1
1
ℎ 𝑡
+
1
ℎ 𝑜
(65)
Where ht and ho are the individual coefficients for the tube and shell.
The heat transfer area is the next variable to calculate and is done by the following equation:
𝐴 𝑜 = 𝑁𝑡 𝜋𝑂𝐷𝑡 𝐿 (66)
Where Nt is the number of tubes, ODt is the outer tube diameter, and L is the length of the pipes.
The NTU (number of transfer units) can now be solved for. This involves the minimum heat
capacitance rate, Cmin, the heat transfer area, Ao, and the overall heat transfer coefficient, Uo.
𝑁𝑇𝑈 =
𝑈0 𝐴0
𝐶 𝑚𝑖𝑛
(67)
Now, we start to calculate our goal design values: effectiveness, outlet temperature, and pressure
drop.
The effectiveness can be calculated using the following equation:
𝜀 = 2 {1 + 𝐶 +
1+𝑒
(−𝑁𝑇𝑈(1+𝐶2)
1/2
)
1−𝑒
(−𝑁𝑇𝑈(1+𝐶2)
1/2
)
(1 + 𝐶2)1/2
}
−1
(68)
Where C is a constant that is set to zero because of the presence of two phase flow.
The exit temperature of the water leaving both the evaporator and condenser can be
calculated by:
𝑡 𝑤,𝑜𝑢𝑡 = 𝜀(𝑡 𝑅134𝑎 − 𝑡 𝑤,𝑖𝑛) + 𝑡 𝑤,𝑖𝑛 (69)
Where tw is the temperature of the water. TR134a is the temperature of the refrigerant, and e
is the effectiveness.
Lastly, the pressure drop can be calculated. First the friction factor must be calculated
which can be done using the chen equation:
𝑓 = (
1
−2.0log(
𝑒
3.7056𝐷
−
5.0452
𝑅𝑒
∗log(
1
2.8257
∗(
𝑒
𝐷
)
1.1098
+
5.8506
𝑅𝑒0.8981))
)
2
(70)

68. G r o u p I | 66
Where e in this case is the roughness of the material. Since we specified that the tube
material was carbon steel, the roughness was selected to be 0.00015. This allowed the
relative roughness (e/D) to be calculated using the specified absolute roughness value and
the value of the shell diameter. By using this method, the use of the Moody diagram is
eliminated and a more accurate friction factor can be used. The only other variable in this
equation is Re which is the Reynolds number in the tube.
With the friction factor calculated, the pressure drop within the tube can now be found
using the following equation:
∆𝑃𝑡 =
𝜌(𝑉𝑡2)
2𝑔
(
𝑓∗𝐿∗𝑁𝑝
𝐼𝐷𝑡
+ 4𝑁𝑝) (71)
Where 𝜌 is the vapor refrigerant density, Vt is the tube fluid velocity, f is the friction factor,
L is the length of the tubes, Np is the number of passes, and IDt is the inside diameter of the
tubes
Table 25: Chiller Designed Specifications for Condenser
Shell Diameter 15.25 in.
Inner Tube Diameter 0.56 in.
Outer Tube Diameter 0.75 in.
# of Tubes 137
Length of tubes 9’
Number of Passes 1
Number of Baffles 5
Pitch 1
Water Exit Temperature 95.251oF
Effectiveness 0.6588
Table 25. Shows the dimensions calculated using the spreadsheet from project 1. This
condenser can fulfill the requirements.

69. G r o u p I | 67
Table 26: Thermodynamic Properties for Condenser
Table 27: Chiller Designed Specifications for Evaporator
Shell Diameter 23.25 in.
Inner Tube Diameter 0.56 in.
Outer Tube Diameter 0.75 in.
# of Tubes 341
Length of tubes 9’
Number of Passes 1
Number of Baffles 5
Pitch 1
Water Exit Temperature 45.782oF
Effectiveness 0.307
Condenser Design
Quantity Magnitude Units
Condenser Heat Transfer Rate 7072712.97 Btu/hr
Refrigerant Flow Rate 97534.9663 lbm/hr
Condenser Water Flow Rate 70868.7964 lbm/hr
Temperature of R134 Condenser 100.56 oF
Inlet Temperature of Water 85 oF
Outlet Temperature of Water 95 oF
Average Temperature of Water 90 oF
Water Properties
Specific Heat 1 Btu/lbm*R
Density 62.12 lbm/ft ^3
Dynamic Viscosity 0.0005117 lbm/ft*s
Kinematic Viscosity 0.000008027 ft^2/s
Thermal Diffusivity 0.0059599 ft^2/hr
Prandtl Number 4.844 -
Refrigerant Properties
Liquid Specific Heat 0.3552424 BTU/lbm*R
Liquid Thermal Conductivity 0.0443048 BTU/h*ft*R
Liquid Dynamic Viscosity 0.000114446 lbm/ft*s
Vapor Dynamic Viscosity 9.25515E-06 lbm/ft*s
Liquid Density 72.08712 lbm/ft^3
Vapor Density 2.963 lbm/ft^3

70. G r o u p I | 68
Table 27 shows the specifications of an evaporator that can meet the requirements. It was
found through the process of using the excel spreadsheet from project 1.
Table 28: Thermodynamic Properties for Evaporator
Evaporator Design
Quantity Magnitude Units
Evaporator Heat Transfer Rate 6000000 Btu/hr
Evaporator Water Flow Rate 600000 lbm/hr
Temperature of R134 Evaporator 30 F
Inlet Temperature of Water 55 F
Outlet Temperature of Water 45 F
Average Temperature of Water 50 F
Water Properties
Specific Heat 0.97663 Btu/lbm*R
Density 62.403 lbm/ft ^3
Dynamic Viscosity 0.0000273 lbm/ft*s
Kinematic Viscosity 0.00001407 ft^2/s
Thermal Diffusivity 0.0055772 ft^2/hr
Prandtl Number 8.8027 -
Refrigerant Properties
Liquid Specific Heat 0.3185 BTU/lbm*R
Liquid Thermal Conductivity 0.05565 BTU/h*ft*R
Liquid Dynamic Viscosity 0.0001883 lbm/ft*s
Vapor Dynamic Viscosity 0.00000496 lbm/ft*s
Liquid Density 81.8 lbm/ft^3
Vapor Density 0.866 lbm/ft^3

71. G r o u p I | 69
VII. Cooling Tower
Cooling Tower Calculations
Temperature Hot H20= 95oF
Temperature Cold H20= 85oF
Wet Bulb Temperature of Air =82oF
Heat Load =Qhcond=14,145,425.94 Btu/hr
Mass Flow Rate of H20= 1,415,958.552 lbm/hr
Mass Flow Rate of H20= 2827.82 gpm
Rate of Evaporation
𝑅𝑎𝑡𝑒 𝑜𝑓 𝐸𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 = 𝑚̇ ℎ20(∆𝑇) ∗ 0.0008 (72)
2827.82 𝑔𝑝𝑚 ∗ 10 ∗ 0.0008= 22.62256 gpm
Rate of Drift Loss
𝑅𝑎𝑡𝑒 𝑜𝑓 𝐷𝑟𝑖𝑓𝑡 𝐿𝑜𝑠𝑠 = 𝑚̇ ℎ20 ∗ 0.0002 (73)
𝑅𝑎𝑡𝑒 𝑜𝑓 𝐷𝑟𝑖𝑓𝑡 𝐿𝑜𝑠𝑠 = 2827.82 ∗ 0.0002
𝑅𝑎𝑡𝑒 𝑜𝑓 𝐷𝑟𝑖𝑓𝑡 𝐿𝑜𝑠𝑠 = 0.565564 𝑔𝑝𝑚
Rate of Blowdown
We determined the contaminate concentration to be 4
𝑅𝑎𝑡𝑒 𝑜𝑓 𝑏𝑙𝑜𝑤𝑑𝑜𝑤𝑛 =
𝑅𝑎𝑡𝑒 𝑜𝑓 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛−(𝐶𝑜𝑛𝑡𝑎𝑚𝑖𝑛𝑎𝑡𝑒 𝑐𝑜𝑛𝑐𝑒𝑛𝑡𝑟𝑎𝑡𝑖𝑜𝑛−1)∗𝐷𝑟𝑖𝑓𝑡 𝑙𝑜𝑠𝑠
(𝐶𝑜𝑛𝑡𝑎𝑚𝑖𝑛𝑎𝑡𝑒 𝐶𝑜𝑛𝑐𝑒𝑛𝑡𝑟𝑎𝑡𝑖𝑜𝑛−1)
(74)
𝑅𝑎𝑡𝑒 𝑜𝑓 𝑏𝑙𝑜𝑤𝑑𝑜𝑤𝑛 =
22.623 − [(4 − 1) ∗ 0.565564]
(4 − 1)
𝑅𝑎𝑡𝑒 𝑜𝑓 𝑏𝑙𝑜𝑤𝑑𝑜𝑤𝑛 = 6.9754

72. G r o u p I | 70
Cooling tower Efficiency
𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦% =
(𝑇ℎ𝑜𝑡 𝑤𝑎𝑡𝑒𝑟−𝑇 𝑐𝑜𝑙𝑑𝑤𝑎𝑡𝑒𝑟
)∗100
𝑇ℎ𝑜𝑡 𝑤𝑎𝑡𝑒𝑟−𝑇 𝑤𝑒𝑡𝑏𝑢𝑙𝑏
(76)
𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦% =
(95℉ − 85℉) ∗ 100
95℉ − 82℉
𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑐𝑦% = 76.923
Make up water Requirement
𝑀𝑎𝑘𝑒 𝑢𝑝 𝑤𝑎𝑡𝑒𝑟 𝑅𝑒𝑞𝑢𝑖𝑟𝑒𝑚𝑒𝑛𝑡 = ∑ 𝐿𝑜𝑠𝑠𝑒𝑠 (77)
𝑀𝑎𝑘𝑒 𝑢𝑝 𝑤𝑎𝑡𝑒𝑟 𝑅𝑒𝑞𝑢𝑖𝑟𝑒𝑚𝑒𝑛𝑡 = 22.62256 + 0.565564 + 6.9754
For the cooling tower we used the mass flow rate of determined from the thermodynamic
analysis as previously shown in the report. By finding our mass flow rate and using the
temperatures determined by the chiller we selected. With the specifications of 85 F and 95
F and a mass flow rate of 1,415,958.522 lbm/hr. We were able to plug in those values into
Baltimore’s Air Coil Company’s software to select a cooling tower.

73. G r o u p I | 71
Figure 41: Cooling tower input data
The data plugged in gave us the following cooling tower with its specs displayed below.
Table 29: Cooling Tower Properties
Cooling tower Specifications Design Conditions
Model Information XESE-122-10o Flow Rate 2,827.82 USGPM
Number of Units 2 Hot water Temp 95
Fan Motor 30.00 HP/Unit Cold Water Temp 85
Unit Length 11'0.975" Wet Bulb Temp 82
Unit Width 21' 0.650 Tower Pumping Head 6.71 psi
Unit Height 16'05.00" Reserve Capability 0.45%
Air Flow 165,430
Operating Weight 33,370 lbs

74. G r o u p I | 72
Figure 42: Single Unit cooling tower

75. G r o u p I | 73
VIII. Air Cooled Condenser
The air cooled condenser will serve to reject the heat gained from the building into the
atmosphere. It is an alternative to using a regular water cooled chiller with a cooling tower.
Using an air cooled condenser will eliminate the need for a cooling tower entirely, therefore
saving space and water consumption. However, the lower heat transfer capabilities of air in
comparison to water mean that the system is less efficient than a cooling tower setup. Therefore,
the air cooled condenser setup will require more power than the cooling tower setup would to
remove the same amount of heat from the refrigerant.
The air cooled condenser operates by having the refrigerant’s temperature raised through the
compressor, similarly to the water cooled setup. It then enters the condenser at 125°F where it
runs through the condenser tubes and is cooled by a fan moving air over the tubes at 325000 cfm.
The refrigerant then exits the condenser at 115°F where it then moves through a throttling valve
to lower its temperature back to the required 45°F for the air handling unit.
The condenser uses ¾ in Type K copper tubing with copper fin attachments for increased heat
transfer area. The design values for the air cooled condenser are shown below in tables 30-32.
Table 30: Air Cooled Condenser Temperature, Heat Transfer, and Refrigerant Flow Rate
Air
Temperature
inlet, Tai [°F]
Air
Temperature
Outlet, Tao
[°F]
Refrigerant
Temperature
Inlet, Tri [°F]
Refrigerant
Temperature
Outlet, Tro
[°F]
Condenser
Heat
Transfer, Q
[BTU/hr]
Refrigerant
Mass Flow
Rate, 𝑚̇
[lbm/hr]
95 105 125 115 512860 160270
Table 31: Design Dimensions for Air Cooled Condenser
Tube
Length,
L [in]
Number
of
Tubes,
Nt
Number
of Tube
Passes,
Np
Tube
Outer
Diameter,
Do [in]
Tube
Inner
Diameter,
Di [in]
Surface
Area,
As [ft2
]
Tube
Pitch,
Pt [in]
Fin
Pitch,
Nf
[fin/in]
168 61 1 0.75 0.652 590.9 1 4
Table 32: Calculated Values for Air Cooled Condenser
Tube
Fluid
Velocity,
Vt [ft/s]
Air
Volumetric
flow rate,
𝑉𝑎̇ [cfm]
Overall
Heat
Transfer
Coefficient,
U [BTU/hr-
ft2
-°F]
Pressure
Drop, p
[ft H2O]
4.7 325000 103 11.74
The calculation procedure for the design of the air cooled condenser is shown below.
To begin, the inlet and outlet temperatures for both fluids were chosen. The air was chosen at
95°F inlet as that is the temperature for a typical summer day in southern Louisiana. The
refrigerant was chosen to be 125°F at the inlet so as to always be above the air temperature.

76. G r o u p I | 74
The temperature difference for both fluids was chosen to be 10°F as this is a typical design value
for a cross flow heat exchanger.
The required heat transfer for the condenser was already known before the design, so the mass
flow rate for the refrigerant could be calculated using equation 78 below.
𝑚̇ 𝑟 = 𝑄̇/𝐶 𝑝𝑟∆𝑇𝑟 (78)
Where 𝑚̇ 𝑟is the mass flow rate of the refrigerant, 𝑄̇ is the heat transfer of the condenser, 𝐶 𝑝𝑟 is
the specific heat of the refrigerant, and ∆𝑇𝑟 is the temperature difference of the refrigerant
between he inlet and outlet of the condenser.
Next the log mean temperature difference is calculated using equation 79 below.
𝐿𝑀𝑇𝐷 =
∆𝑇 𝑖−∆𝑇𝑜
ln(∆𝑇 𝑖−∆𝑇𝑜)
(79)
After this a value for U, the overall heat transfer coefficient, is assumed in order to calculate the
total heat transfer area that is required. The value of U will be iterated to produce a valid result.
The calculation for the heat transfer area is shown below in equation 80.
𝐴 𝑠 =
𝑄̇
𝐿𝑀𝑇𝐷∗𝑈 𝑎𝑠𝑠𝑢𝑚𝑒𝑑
(80)
Next the tube dimensions are chosen in order to calculate the single tube and fin surface area,
which is used to calculate the required number of tubes. This is all shown below in equations 81
and 82.
𝐴 𝑠𝑡 = (𝜋𝐷𝑜 𝐿) + (2𝐻𝐿) (81)
Where 𝐴 𝑠𝑡 is the surface area of a single tube, 𝐷𝑜 is the tube outer diameter, 𝐿 is the tube length,
and 𝐻 is the fin height.
𝑁𝑡 = 𝐴 𝑠/𝐴 𝑠𝑡 (82)
Next, the Tube velocity must be found as it needs to be within the typical design value of 2-5
ft/s. This was done by first choosing the inner tube diameter so as to find the tube’s flow area,
which is then used to find the velocity. This is shown below in equations 83 and 84.
𝐴 𝑐 = 𝑁𝑡 𝐷𝑖
2 𝜋
4
(83)
Where 𝐴 𝑐 is the flow area of the tubes and 𝐷𝑖 is the inner tube diameter.
𝑉𝑡 = 𝑚 𝑟/̇ 𝑁𝑡
𝑁 𝑝
/
𝜋
4
𝜌𝑟 𝐷𝑖
2
(84)
Where 𝑁𝑝 is the number of tube passes and 𝜌𝑟 is the density of the refrigerant.
Next the mass flow rate of the air must be calculated. This was done using equation 85 below.
𝑚 𝑎̇ =
𝑉̇
𝜌 𝑎
(85)
Where 𝑚 𝑎 is the mass flow rate of the air, 𝑉̇ is the volumetric flow rate of the air, and 𝜌 𝑎 is the
density of the air.
Next the flow area for the air must be calculated.
𝐴 𝑓 = 𝑁𝑡(𝐷𝑓(𝐿 − 𝐿𝑁𝑓 𝑡 𝑏) + 2(𝑁𝑓 − 1)𝐻 (
𝑡 𝑏
2
+
𝑡 𝑡
2
)) (86)
Where 𝐷𝑓 is the fin diameter, 𝑁𝑓 is the number of fins per inch, 𝑡 𝑏 is the fin width at the base,
and 𝑡𝑡 is the fin width at the tip.
Next, the Reynolds number for the air side must be calculated. This is shown in equation 87

77. G r o u p I | 75
𝑅𝑒 𝑑𝑜 =
𝐷 𝑜 𝑚 𝑎̇
𝜇 𝑎 𝐴 𝑓
(87)
Where 𝑅𝑒 𝑑𝑜 is the Reynold’s number for the flow of air outside the tubes, and 𝜇 𝑎 is the viscosity
of the air.
The Reynolds number is then used in conjunction with a tabulated Prandtl number to calculate
the Nusselt number for the flow outside the tubes. This is shown in equation 88.
𝑁𝑢 𝑜 = 0.027𝑅𝑒 𝑑𝑜
0.805
𝑃𝑟𝑎
1/3
(88)
Where 𝑁𝑢 𝑜 is the Nusselt number for the flow of air outside the tubes and 𝑃𝑟𝑎 is the Prandtl
number of the air.
The definition of the Nusselt number shown below in equation 89 is then used to calculate the
outside heat transfer coefficient.
𝑁𝑢 =
ℎ𝐷
𝑘
(89)
Where h is the heat transfer coefficient and k is the thermal conductivity.
Next, the inside heat transfer coefficient was found through an empirical relation shown below in
equation 90.
𝑁𝑢𝑖 = 0.1(
𝐶 𝑝𝑟 𝜇 𝑟
𝑘 𝑟
)(𝑃𝑟𝑟
1
3)(
𝑖 𝑓𝑔𝑟
𝐶 𝑝𝑟(𝑇 𝑟𝑖−𝑇𝑟𝑜)
)
1
6(
𝐷 𝑖 𝑚̇
𝐴 𝑐 𝑁𝑡
∗
𝜌 𝑙
𝜌 𝑣
1
2
)
2
3 (90)
Where 𝑁𝑢𝑖 is the Nusselt number for the flow inside of the tubes, 𝜇 𝑟 is the viscosity of the
refrigerant, 𝑘 𝑟 is the thermal conductivity of the refrigerant, 𝑃𝑟𝑟 is the Prandtl number for the
refrigerant, 𝑖 𝑓𝑔𝑟 is the enthalpy of vaporization for the refrigerant, 𝐶 𝑝𝑟 is the specific heat of the
refrigerant, 𝑇𝑟𝑖 − 𝑇𝑟𝑜 is the temperature difference between the inlet and outlet for the
refrigerant, 𝜌𝑙 is the liquid density of the refrigerant, and 𝜌 𝑣 is the vapor density of the
refrigerant.
This Nusselt number is then used to calculate the inside heat transfer coefficient
Next we need to calculate the fin efficiency using equation 91 below
𝜂 =
√ℎ 𝑜 𝑃𝑘 𝑓 𝐴 𝑠𝑓(𝑇 𝑤−𝑇𝑎)tanh(√
ℎ 𝑜 𝑃
𝑘 𝑓 𝐴 𝑐𝑓
)
ℎ 𝑜 𝐴 𝑠𝑓(𝑇 𝑤−𝑇𝑎)
(91)
Where 𝑃 is the perimeter of the fin, 𝑘 𝑓 is the thermal conductivity of the fin, 𝐴 𝑠𝑓 is the fin
surface area, 𝑇 𝑤 is the wall temperature of the tube, 𝑇𝑎 is the temperature of the air, and 𝐴 𝑐𝑓 is
the cross sectional area of the fin.
Lastly, the overall heat transfer coefficient is calculated using equation 92 below.
𝑈 =
1
1
ℎ 𝑜 𝜂
+
1
ℎ 𝑖 𝜂
+
ln(
𝐷 𝑜
𝐷 𝑖
)𝐷 𝑖 𝜋𝐿
2𝑘 𝑓 𝐿
(92)
Where 𝑈 is the overall heat transfer coefficient.
The pressure drop for the tubes was also calculated using equation 93 below
𝑝 = (
𝜌 𝑟 𝑉𝑡
2
2∗32.2
) (
𝐿𝑓𝑁 𝑝
𝐷 𝑖
) + 4𝑁𝑝 (93)
Where 𝜌𝑟 is the refrigerant density and 𝑓 is the friction factor for the tubing obtained from a
moody chart.

78. G r o u p I | 76
The design values in the previous tables were found by iterating the dimensions for the fins and
tubes, the assumed overall heat transfer coefficient which is used to determine a surface area, as
well as the flow rate for the air.
In order to meet the building’s required load, the following air cooled condenser was selected. It
is a CAUJC60G20002 Trane 60-ton Air Cooled Condenser. A picture of it is shown below in
Figure 1.
Figure 43: Trane CAUJC60G20002 Air cooled Condenser.
It is able to provide the 512860 BTU/hr needed to keep the refrigerant temperature where it
needs to be. It also uses less air and is about 3 feet less in length than the design specifications. It
is also capable of operating within any ambient temperature ranges that would present
themselves within southern Louisiana, with ambient entering air temperatures up to 115 °F. It
also has similar head losses to the design specifications, with head losses of 5 to 10.9 ft of head
depending on the flow rate. It also comes with variable air volume controls as an option, for
when it doesn’t need to operate at full capacity.

79. G r o u p I | 77
X. Conclusions
The overall process of designing the HVAC System started with the zoning and
psychometrics of each room. The psychometrics were performed using the psych app, an
excel spreadsheet and the psychometric charts. The sensible, and latent loads were
provided for each space by the problem statement. The next step from the psychometrics
was to determine the velocities, and flow areas in order to create the ductwork. For the
ductwork, we used the software Revit. The Revit outputted the necessary diameters for the
return and supply ductwork. Thermodynamic analysis was for performed the whole
building to determine the required temperatures and specifications of the AHU. Before the
calculation process was carried out, a few design parameters had to be chosen based upon
typical industry standards.
After we determined the required temperatures needed for the Air Handling Unit, we were
able to determine the required mass flowrates needed from the chiller plant. After that we
were able to design hydronic system that connected the chiller plant with the Air handling
unit.
For the hydronic system we ended up selecting 2 pumps that will make the water flow from
the chiller to the AHU. The primary pump will cycle water through the chiller, while the
secondary pump will supply the AHU. There are two of each pump to allow redundancy in
case of failure or service. The primary pumps have a flow rate of 2400gpm and the
secondary has a 103 gpm flowrate. They both run with a motor speed of 1760 rpm. The
chiller to cooling tower loop also has redundancy with both pumps being able to handle the
full load independent of the other. The flow rate of the cooling tower loop pumps is 2900
gpm, with a motor speed of 1760 rpm..
For the chiller plant, we first started with a thermodynamic analysis to determine the
specifications for the chiller plant. Once we calculated, the mass flow rate of the refrigerant
134-A, along with the temperatures, we selected 2 chiller plant from TRANE. Each chiller
has a capacity of 1300 Tons. However, we will be running each one at 500 tons to meet the
1000 tonnage max requirement. Overall, each chiller plant will be running at 38.5% of
there full capacity. Alternatively, we designed a chiller plant using the spreadsheet from
After that, with the specifications of 85 °F and 95°F and a mass flow rate of 1,415,958.522
lbm/hr., we inputted those values into the Baltimore Air Coil Company software to
determine the specifications of the cooling tower. The efficiency of the cooling tower was
calculated to be 76.923%.
As an alternative we had selected to use air cooled condenser. The unit would rest on the
rooftop of the building and supply the 512860 BTU/hr needed to keep the refrigerant at the
required temperature

80. G r o u p I | 78
XI. References
1. McQuiston, Faye C.; Parker, Jerald D.; Spitler, Jeffery D. Heating, Ventilation, and Air
Conditioning. 6th Edition. New York: John Wiley & Sons, 2005
2. Cengel, Yunus. Heat and Mass Transfer: Fundamentals and Applications. 5th Edition.
New York: McGraw-Hill, 2015
3. Ingadóttir, Sigríður Bára. "Air Cooled Condensers." A-to-Z Guide to Thermodynamics,
Heat and Mass Transfer, and Fluids Engineering (2014): Web.
4. http://www.tacohvac.com/products/variable_speed_products/selfsensing_series/i
ndex.html
5. Posted October 25, 2012 by Jim Shiminski. "Custom Air Handling Units | Coil Selection
Guidelines." DAC SALES. N.p., n.d. Web. 07 Dec. 2016
6. Mitrovic, Jovan. Heat Exchangers: Basics Design Applications. Rijeka: InTech, 2012. Print

81. G r o u p I | 79
XII: APPENDIX

82. G r o u p I | 80
APPENDIX II CHILLER BROCHURE

83. G r o u p I | 81

84. G r o u p I | 82

85. G r o u p I | 83

86. G r o u p I | 84

87. G r o u p I | 85

88. G r o u p I | 86

89. G r o u p I | 87
APPENDIX:III REVIT FILES
Return Line
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure
Length
Loss
Coefficient
Friction
Total Pressure
Loss
Section
Pressure
Loss
1
Fittings 683 CFM - 0 FPM 0.00 in-wg - 0.50538 - 0.00 in-wg
0.06 in-wg
Air Terminal 683 CFM - - - - - - 0.06 in-wg
2
Duct 683 CFM - 490 FPM - 6' - 0 19/32" -
0.02 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 683 CFM - 490 FPM 0.01 in-wg - 0.687508 - 0.01 in-wg
3 Fittings 683 CFM - 0 FPM 0.00 in-wg - -29.315397 - -0.01 in-wg -0.01 in-wg
4
Duct 4309 CFM 36"x36" 480 FPM -
41' - 4
23/32"
-
0.01 in-
wg/100ft
0.00 in-wg
0.02 in-wg
Fittings 4309 CFM - 480 FPM 0.01 in-wg - 1.176644 - 0.02 in-wg
5 Fittings 4309 CFM - 0 FPM 0.02 in-wg - 4.094168 - 0.07 in-wg 0.07 in-wg
6 Fittings 7654 CFM - 0 FPM 0.06 in-wg - 0.026434 - 0.00 in-wg 0.00 in-wg
7
Duct 7654 CFM 24"x43" 1070 FPM - 6' - 2 3/4" -
0.04 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 7654 CFM - 1070 FPM 0.07 in-wg - 0.050769 - 0.00 in-wg
8
Duct 7654 CFM 43"x26" 990 FPM - 0' - 7 3/8" -
0.04 in-
wg/100ft
0.00 in-wg
0.08 in-wg
Fittings 7654 CFM - 990 FPM 0.06 in-wg - 1.339597 - 0.08 in-wg
9
Duct 10722 CFM 43"x26" 1380 FPM - 4' - 11 5/8" -
0.07 in-
wg/100ft
0.00 in-wg
0.16 in-wg
Fittings 10722 CFM - 1380 FPM 0.12 in-wg - 1.288439 - 0.15 in-wg
10
Fittings 10722 CFM - 0 FPM 0.24 in-wg - 0 - 0.00 in-wg
0.00 in-wg
Equipment 10722 CFM - - - - - - 0.00 in-wg
11
Fittings 220 CFM - 0 FPM 0.00 in-wg - 3.487262 - 0.00 in-wg
0.06 in-wg
Air Terminal 220 CFM - - - - - - 0.06 in-wg
12
Duct 220 CFM - 400 FPM - 9' - 4 3/32" -
0.03 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 220 CFM - 400 FPM 0.01 in-wg - 0.708799 - 0.01 in-wg
13 Fittings 220 CFM - 0 FPM 0.00 in-wg - -48.404552 - -0.01 in-wg -0.01 in-wg
14
Duct 1802 CFM 24"x24" 450 FPM -
15' - 1
25/32"
-
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 1802 CFM - 450 FPM 0.01 in-wg - 0.175102 - 0.00 in-wg

90. G r o u p I | 88
15 Fittings 1802 CFM - 0 FPM 0.01 in-wg - 0.433877 - 0.00 in-wg 0.00 in-wg
16
Duct 2410 CFM 28"x28" 440 FPM -
27' - 3
19/32"
-
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 2410 CFM - 440 FPM 0.01 in-wg - 0.085067 - 0.00 in-wg
17 Fittings 2410 CFM - 0 FPM 0.01 in-wg - 0.382478 - 0.00 in-wg 0.00 in-wg
18
Duct 3018 CFM 30"x30" 480 FPM -
27' - 0
19/32"
-
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 3018 CFM - 480 FPM 0.01 in-wg - 0.079922 - 0.00 in-wg
19 Fittings 3018 CFM - 0 FPM 0.01 in-wg - 0.328285 - 0.00 in-wg 0.00 in-wg
20
Duct 3626 CFM 32"x32" 510 FPM - 28' - 8 7/8" -
0.01 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 3626 CFM - 510 FPM 0.02 in-wg - 0.138519 - 0.00 in-wg
21 Fittings 3626 CFM - 0 FPM 0.01 in-wg - 0.313515 - 0.00 in-wg 0.00 in-wg
22
Fittings 220 CFM - 0 FPM 0.00 in-wg - 3.487262 - 0.00 in-wg
0.06 in-wg
Air Terminal 220 CFM - - - - - - 0.06 in-wg
23
Duct 220 CFM - 400 FPM - 9' - 7 7/8" -
0.03 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 220 CFM - 400 FPM 0.01 in-wg - 0.679425 - 0.01 in-wg
24 Fittings 220 CFM - 0 FPM 0.00 in-wg - -39.49115 - -0.01 in-wg -0.01 in-wg
25 Fittings 1582 CFM - 0 FPM 0.01 in-wg - 0.056144 - 0.00 in-wg 0.00 in-wg
26
Duct 1582 CFM 23"x23" 430 FPM -
20' - 8
19/32"
-
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 1582 CFM - 430 FPM 0.01 in-wg - 0.053854 - 0.00 in-wg
27 Fittings 1582 CFM - 0 FPM 0.01 in-wg - 0.255339 - 0.00 in-wg 0.00 in-wg
28
Fittings 588 CFM - 0 FPM 0.00 in-wg - 0.50538 - 0.00 in-wg
0.06 in-wg
Air Terminal 588 CFM - - - - - - 0.06 in-wg
29
Duct 588 CFM - 420 FPM - 7' - 0 3/32" -
0.02 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 588 CFM - 420 FPM 0.01 in-wg - 0.640804 - 0.01 in-wg
30 Fittings 588 CFM - 0 FPM 0.00 in-wg - -7.236559 - 0.00 in-wg 0.00 in-wg
31
Duct 2882 CFM 32"x32" 410 FPM - 18' - 1 1/4" -
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 2882 CFM - 410 FPM 0.01 in-wg - 0.281945 - 0.00 in-wg
32
Duct 3346 CFM 32"x32" 470 FPM - 31' - 7 1/2" -
0.01 in-
wg/100ft
0.00 in-wg
0.02 in-wg
Fittings 3346 CFM - 470 FPM 0.01 in-wg - 1.225363 - 0.02 in-wg
33 Fittings 3346 CFM - 0 FPM 0.01 in-wg - 6.88715 - 0.07 in-wg 0.07 in-wg
34
Fittings 588 CFM - 0 FPM 0.00 in-wg - 0.50538 - 0.00 in-wg
0.06 in-wg
Air Terminal 588 CFM - - - - - - 0.06 in-wg

91. G r o u p I | 89
35
Duct 588 CFM - 420 FPM - 7' - 7 1/32" -
0.02 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 588 CFM - 420 FPM 0.01 in-wg - 0.573543 - 0.01 in-wg
36 Fittings 588 CFM - 0 FPM 0.00 in-wg - -3.891242 - 0.00 in-wg 0.00 in-wg
37
Duct 2293 CFM 28"x28" 420 FPM -
26' - 11
5/32"
-
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 2293 CFM - 420 FPM 0.01 in-wg - 0.154688 - 0.00 in-wg
38 Fittings 2293 CFM - 0 FPM 0.01 in-wg - 0.387009 - 0.00 in-wg 0.00 in-wg
39
Fittings 588 CFM - 0 FPM 0.00 in-wg - 0.50538 - 0.00 in-wg
0.06 in-wg
Air Terminal 588 CFM - - - - - - 0.06 in-wg
40
Duct 588 CFM - 420 FPM - 8' - 1 31/32" -
0.02 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 588 CFM - 420 FPM 0.01 in-wg - 0.480934 - 0.01 in-wg
41 Fittings 588 CFM - 0 FPM 0.00 in-wg - -0.723474 - 0.00 in-wg 0.00 in-wg
42
Duct 1705 CFM 24"x24" 430 FPM -
27' - 1
25/32"
-
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 1705 CFM - 430 FPM 0.01 in-wg - 0.175102 - 0.00 in-wg
43 Fittings 1705 CFM - 0 FPM 0.01 in-wg - 0.476008 - 0.00 in-wg 0.00 in-wg
44
Fittings 314 CFM - 0 FPM 0.00 in-wg - 1.066759 - 0.00 in-wg
0.06 in-wg
Air Terminal 314 CFM - - - - - - 0.06 in-wg
45
Duct 314 CFM - 340 FPM - 8' - 10 9/16" -
0.02 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 314 CFM - 340 FPM 0.01 in-wg - 0.3178 - 0.00 in-wg
46 Fittings 314 CFM - 0 FPM 0.00 in-wg - 0.148849 - 0.00 in-wg 0.00 in-wg
47
Duct 695 CFM 16"x16" 390 FPM - 17' - 0 7/32" -
0.02 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 695 CFM - 390 FPM 0.01 in-wg - 0.138519 - 0.00 in-wg
48 Fittings 695 CFM - 0 FPM 0.01 in-wg - 0.435916 - 0.00 in-wg 0.00 in-wg
49
Duct 906 CFM 18"x18" 400 FPM -
20' - 6
19/32"
-
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 906 CFM - 400 FPM 0.01 in-wg - 0.1254 - 0.00 in-wg
50 Fittings 906 CFM - 0 FPM 0.01 in-wg - 0.362238 - 0.00 in-wg 0.00 in-wg
51
Duct 1117 CFM 20"x20" 400 FPM - 16' - 6 5/16" -
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 1117 CFM - 400 FPM 0.01 in-wg - 0.201667 - 0.00 in-wg
52 Fittings 1117 CFM - 0 FPM 0.00 in-wg - 0.626406 - 0.00 in-wg 0.00 in-wg
53
Fittings 381 CFM - 0 FPM 0.00 in-wg - 0.794783 - 0.00 in-wg
0.06 in-wg
Air Terminal 381 CFM - - - - - - 0.06 in-wg
54 Duct 381 CFM - 360 FPM - 11' - 10 - 0.02 in- 0.00 in-wg 0.00 in-wg

92. G r o u p I | 90
27/32" wg/100ft
Fittings 381 CFM - 360 FPM 0.01 in-wg - 0.015183 - 0.00 in-wg
55
Duct 381 CFM 12"x12" 380 FPM - 23' - 7 5/32" -
0.02 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 381 CFM - 380 FPM 0.01 in-wg - 0.28875 - 0.00 in-wg
56 Fittings 381 CFM - 0 FPM 0.00 in-wg - 0.823597 - 0.00 in-wg 0.00 in-wg
57
Fittings 211 CFM - 0 FPM 0.00 in-wg - 3.487262 - 0.00 in-wg
0.06 in-wg
Air Terminal 211 CFM - - - - - - 0.06 in-wg
58
Duct 211 CFM - 390 FPM - 9' - 8 23/32" -
0.03 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 211 CFM - 390 FPM 0.01 in-wg - 0.640804 - 0.01 in-wg
59 Fittings 211 CFM - 0 FPM 0.00 in-wg - -13.328115 - 0.00 in-wg 0.00 in-wg
60
Fittings 211 CFM - 0 FPM 0.00 in-wg - 3.487262 - 0.00 in-wg
0.06 in-wg
Air Terminal 211 CFM - - - - - - 0.06 in-wg
61
Duct 211 CFM - 390 FPM - 10' - 0 5/32" -
0.03 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 211 CFM - 390 FPM 0.01 in-wg - 0.588606 - 0.01 in-wg
62 Fittings 211 CFM - 0 FPM 0.00 in-wg - -5.398212 - 0.00 in-wg 0.00 in-wg
63
Fittings 608 CFM - 0 FPM 0.00 in-wg - 0.50538 - 0.00 in-wg
0.06 in-wg
Air Terminal 608 CFM - - - - - - 0.06 in-wg
64
Duct 608 CFM - 440 FPM - 6' - 9 1/16" -
0.02 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 608 CFM - 440 FPM 0.01 in-wg - 0.640804 - 0.01 in-wg
65 Fittings 608 CFM - 0 FPM 0.00 in-wg - -24.469114 - -0.01 in-wg -0.01 in-wg
66
Fittings 608 CFM - 0 FPM 0.00 in-wg - 0.50538 - 0.00 in-wg
0.06 in-wg
Air Terminal 608 CFM - - - - - - 0.06 in-wg
67
Duct 608 CFM - 440 FPM - 7' - 0 3/4" -
0.02 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 608 CFM - 440 FPM 0.01 in-wg - 0.610144 - 0.01 in-wg
68 Fittings 608 CFM - 0 FPM 0.00 in-wg - -7.406839 - 0.00 in-wg 0.00 in-wg
69
Fittings 608 CFM - 0 FPM 0.00 in-wg - 0.50538 - 0.00 in-wg
0.06 in-wg
Air Terminal 608 CFM - - - - - - 0.06 in-wg
70
Duct 608 CFM - 440 FPM - 7' - 4 15/32" -
0.02 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 608 CFM - 440 FPM 0.01 in-wg - 0.553816 - 0.01 in-wg
71 Fittings 608 CFM - 0 FPM 0.00 in-wg - -3.650213 - 0.00 in-wg 0.00 in-wg
72
Fittings 454 CFM - 0 FPM 0.00 in-wg - 0.635633 - 0.00 in-wg
0.06 in-wg
Air Terminal 454 CFM - - - - - - 0.06 in-wg

93. G r o u p I | 91
73
Duct 454 CFM - 370 FPM -
14' - 7
19/32"
-
0.02 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 454 CFM - 370 FPM 0.01 in-wg - 0.464887 - 0.00 in-wg
74 Fittings 454 CFM - 0 FPM 0.00 in-wg - -0.823333 - 0.00 in-wg 0.00 in-wg
75
Duct 1362 CFM 22"x22" 410 FPM - 21' - 1 3/8" -
0.01 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 1362 CFM - 410 FPM 0.01 in-wg - 0.282503 - 0.00 in-wg
76
Fittings 454 CFM - 0 FPM 0.00 in-wg - 0.635633 - 0.00 in-wg
0.06 in-wg
Air Terminal 454 CFM - - - - - - 0.06 in-wg
77
Duct 454 CFM - 370 FPM - 15' - 2 1/2" -
0.02 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 454 CFM - 370 FPM 0.01 in-wg - 0.300026 - 0.00 in-wg
78 Fittings 454 CFM - 0 FPM 0.00 in-wg - 0.52 - 0.00 in-wg 0.00 in-wg
79
Duct 908 CFM 18"x18" 400 FPM - 14' - 9 5/32" -
0.01 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 908 CFM - 400 FPM 0.01 in-wg - 0.218182 - 0.00 in-wg
80 Fittings 908 CFM - 0 FPM 0.00 in-wg - 0.606667 - 0.00 in-wg 0.00 in-wg
81
Fittings 454 CFM - 0 FPM 0.00 in-wg - 0.635633 - 0.00 in-wg
0.06 in-wg
Air Terminal 454 CFM - - - - - - 0.06 in-wg
82
Duct 454 CFM - 370 FPM - 8' - 0 3/4" -
0.02 in-
wg/100ft
0.00 in-wg
0.00 in-wg
Fittings 454 CFM - 370 FPM 0.01 in-wg - 0.010043 - 0.00 in-wg
83
Duct 454 CFM 13"x13" 390 FPM - 36' - 5 7/32" -
0.02 in-
wg/100ft
0.01 in-wg
0.02 in-wg
Fittings 454 CFM - 390 FPM 0.01 in-wg - 1.465741 - 0.01 in-wg
84 Fittings 454 CFM - 0 FPM 0.00 in-wg - 0.92 - 0.00 in-wg 0.00 in-wg
85
Fittings 464 CFM - 0 FPM 0.00 in-wg - 0.50538 - 0.00 in-wg
0.06 in-wg
Air Terminal 464 CFM - - - - - - 0.06 in-wg
86
Duct 464 CFM - 330 FPM - 7' - 0 13/16" -
0.01 in-
wg/100ft
0.00 in-wg
0.01 in-wg
Fittings 464 CFM - 330 FPM 0.01 in-wg - 0.640804 - 0.00 in-wg
87 Fittings 464 CFM - 0 FPM 0.00 in-wg - -39.674431 - -0.01 in-wg -0.01 in-wg
88
Duct 3068 CFM 24"x26" 710 FPM -
10' - 10
31/32"
-
0.03 in-
wg/100ft
0.00 in-wg
0.48 in-wg
Fittings 3068 CFM - 710 FPM 0.03 in-wg - 0.757713 - 0.02 in-wg
Air Terminal 3068 CFM - - - - - - 0.45 in-wg
Critical Path : 88-9-10 ; Total Pressure Loss : 0.63 in-wg

94. G r o u p I | 92
Main Supply Line
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
1
Duct 823 CFM 16"ø 590 FPM - 0' - 1 13/32" -
0.03 in-
wg/100ft 0.00 in-wg
0.10 in-wg
Fittings 823 CFM - 590 FPM 0.02 in-wg - 4.309251 - 0.09 in-wg
Equipment 823 CFM - - - - - - 0.01 in-wg
2
Duct 9114 CFM 32"x36" 1140 FPM - 28' - 9 1/32" -
0.04 in-
wg/100ft 0.01 in-wg
0.02 in-wgFittings 9114 CFM - 1140 FPM 0.08 in-wg - 0.058524 - 0.00 in-wg
3
Duct 10072 CFM 32"x36" 1260 FPM - 9' - 7 3/8" -
0.05 in-
wg/100ft 0.01 in-wg
0.12 in-wgFittings 10072 CFM - 1260 FPM 0.10 in-wg - 1.187797 - 0.12 in-wg
4
Duct 10723 CFM 32"x36" 1340 FPM - 18' - 8 1/32" -
0.06 in-
wg/100ft 0.01 in-wg
2.14 in-wg
Fittings 10723 CFM - 1340 FPM 0.11 in-wg - 1.163333 - 0.13 in-wg
Equipment 10723 CFM - - - - - - 2.00 in-wg
5
Duct 823 CFM 16"ø 590 FPM - 0' - 1 13/32" -
0.03 in-
wg/100ft 0.00 in-wg
0.08 in-wg
Fittings 823 CFM - 590 FPM 0.02 in-wg - 3.306971 - 0.07 in-wg
Equipment 823 CFM - - - - - - 0.01 in-wg
6
Duct 7438 CFM 32"x36" 930 FPM -
26' - 7
11/32" -
0.03 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 7438 CFM - 930 FPM 0.05 in-wg - 0.061702 - 0.00 in-wg
7
Duct 8291 CFM 32"x36" 1040 FPM - 3' - 4 21/32" -
0.04 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 8291 CFM - 1040 FPM 0.07 in-wg - 0.057097 - 0.00 in-wg
8
Duct 823 CFM 16"ø 590 FPM - 0' - 4 11/32" -
0.03 in-
wg/100ft 0.00 in-wg
0.11 in-wg
Fittings 823 CFM - 590 FPM 0.02 in-wg - 4.770032 - 0.10 in-wg
Equipment 823 CFM - - - - - - 0.01 in-wg
9
Duct 5762 CFM 28"x28" 1060 FPM - 22' - 6 9/32" -
0.05 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 5762 CFM - 1060 FPM 0.07 in-wg - 0.038333 - 0.00 in-wg
10
Duct 5762 CFM 32"x36" 720 FPM - 3' - 2 1/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 5762 CFM - 720 FPM 0.03 in-wg - 0.077333 - 0.00 in-wg

95. G r o u p I | 93
11
Duct 6615 CFM 32"x36" 830 FPM - 3' - 4 21/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 6615 CFM - 830 FPM 0.04 in-wg - 0.066403 - 0.00 in-wg
12
Duct 592 CFM 16"ø 420 FPM - 0' - 4 11/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.06 in-wg
Fittings 592 CFM - 420 FPM 0.01 in-wg - 4.677419 - 0.05 in-wg
Equipment 592 CFM - - - - - - 0.01 in-wg
13
Duct 4087 CFM 28"x28" 750 FPM -
27' - 0
23/32" -
0.03 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 4087 CFM - 750 FPM 0.04 in-wg - 0.103571 - 0.00 in-wg
14
Duct 4939 CFM 28"x28" 910 FPM - 3' - 6 1/32" -
0.04 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 4939 CFM - 910 FPM 0.05 in-wg - 0.085714 - 0.00 in-wg
15
Duct 441 CFM 16"ø 320 FPM - 0' - 1 1/2" -
0.01 in-
wg/100ft 0.00 in-wg
0.02 in-wg
Fittings 441 CFM - 320 FPM 0.01 in-wg - 2.095675 - 0.01 in-wg
Equipment 441 CFM - - - - - - 0.01 in-wg
16
Duct 974 CFM 18"x20" 390 FPM -
19' - 5
11/32" -
0.01 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 974 CFM - 390 FPM 0.01 in-wg - 1.152741 - 0.01 in-wg
17
Duct 974 CFM 20"x20" 350 FPM - 0' - 0 3/4" -
0.01 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 974 CFM - 350 FPM 0.01 in-wg - 0.02 - 0.00 in-wg
18 Fittings 974 CFM - 0 FPM 0.01 in-wg - 2.992628 - 0.02 in-wg 0.02 in-wg
19 Fittings 2877 CFM - 0 FPM 0.03 in-wg - 0.031837 - 0.00 in-wg 0.00 in-wg
20
Duct 2877 CFM 28"x28" 530 FPM - 3' - 8 9/16" -
0.01 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 2877 CFM - 530 FPM 0.02 in-wg - 0.10601 - 0.00 in-wg
21
Duct 3494 CFM 28"x28" 640 FPM - 2' - 11 9/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 3494 CFM - 640 FPM 0.03 in-wg - 0.086948 - 0.00 in-wg
22
Duct 533 CFM 16"ø 380 FPM - 0' - 2 9/16" -
0.01 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 533 CFM - 380 FPM 0.01 in-wg - 0.043333 - 0.00 in-wg
Equipment 533 CFM - - - - - - 0.01 in-wg
23
Duct 533 CFM 16"x16" 300 FPM - 21' - 1" -
0.01 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 533 CFM - 300 FPM 0.01 in-wg - 0.034667 - 0.00 in-wg
24 Duct 533 CFM 18"x20" 210 FPM - 5' - 3 21/32" - 0.00 in- 0.00 in-wg 0.00 in-wg

96. G r o u p I | 94
wg/100ft
Fittings 533 CFM - 210 FPM 0.00 in-wg - 0.74819 - 0.00 in-wg
25
Duct 958 CFM 16"ø 690 FPM - 0' - 1 1/32" -
0.04 in-
wg/100ft 0.00 in-wg
0.13 in-wg
Fittings 958 CFM - 690 FPM 0.03 in-wg - 3.92759 - 0.12 in-wg
Equipment 958 CFM - - - - - - 0.01 in-wg
26
Duct 853 CFM 16"ø 610 FPM - 0' - 1 1/32" -
0.03 in-
wg/100ft 0.00 in-wg
0.09 in-wg
Fittings 853 CFM - 610 FPM 0.02 in-wg - 3.472741 - 0.08 in-wg
Equipment 853 CFM - - - - - - 0.01 in-wg
27
Duct 853 CFM 16"ø 610 FPM - 0' - 1 1/32" -
0.03 in-
wg/100ft 0.00 in-wg
0.08 in-wg
Fittings 853 CFM - 610 FPM 0.02 in-wg - 2.921545 - 0.07 in-wg
Equipment 853 CFM - - - - - - 0.01 in-wg
28
Duct 853 CFM 16"ø 610 FPM - 0' - 3 1/32" -
0.03 in-
wg/100ft 0.00 in-wg
0.09 in-wg
Fittings 853 CFM - 610 FPM 0.02 in-wg - 3.429066 - 0.08 in-wg
Equipment 853 CFM - - - - - - 0.01 in-wg
29
Duct 617 CFM 16"ø 440 FPM - 0' - 3 1/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.05 in-wg
Fittings 617 CFM - 440 FPM 0.01 in-wg - 3.245972 - 0.04 in-wg
Equipment 617 CFM - - - - - - 0.01 in-wg
30
Duct 1903 CFM 20"ø 870 FPM - 2' - 0 1/4" -
0.05 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 1903 CFM - 870 FPM 0.05 in-wg - 0.05455 - 0.00 in-wg
Equipment 1903 CFM - - - - - - 0.01 in-wg
31 Fittings 1903 CFM - 0 FPM 0.01 in-wg - -0.01292 - 0.00 in-wg 0.00 in-wg
32
Duct 651 CFM 16"ø 470 FPM - 1' - 4 3/4" -
0.02 in-
wg/100ft 0.00 in-wg
0.10 in-wg
Fittings 651 CFM - 470 FPM 0.01 in-wg - 6.685049 - 0.09 in-wg
Equipment 651 CFM - - - - - - 0.01 in-wg
Critical Path : 4-3-2-7-6-11-10-9-8 ; Total Pressure Loss : 2.43 in-wg

97. G r o u p I | 95
Classroom 1
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
4
Duct 392 CFM 12"ø 500 FPM - 5' - 7 1/4" -
0.03 in-
wg/100ft 0.00 in-wg
0.03 in-wgFittings 392 CFM - 500 FPM 0.02 in-wg - 1.644898 - 0.03 in-wg
5 Fittings 784 CFM - 0 FPM 0.03 in-wg - 0 - 0.00 in-wg 0.00 in-wg
6
Duct 784 CFM 14"x14" 580 FPM - 14' - 0 3/32" -
0.04 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 784 CFM - 580 FPM 0.02 in-wg - 0.381818 - 0.01 in-wg
7
Fittings 784 CFM - 0 FPM 0.03 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 784 CFM - - - - - - 0.00 in-wg
10 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
11
Duct 392 CFM 12"ø 500 FPM - 5' - 8 3/4" -
0.03 in-
wg/100ft 0.00 in-wg
0.03 in-wgFittings 392 CFM - 500 FPM 0.02 in-wg - 1.644898 - 0.03 in-wg
12
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
15
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
16
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
18
Duct 0 CFM 12"ø 0 FPM - 0' - 3 3/4" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg
19
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
Critical Path : 7-6-5-11-16 ; Total Pressure Loss : 0.05 in-wg

98. G r o u p I | 96
Classroom 2
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
3
Duct 0 CFM 12"ø 0 FPM - 0' - 5 5/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg
4
Duct 392 CFM 12"ø 500 FPM - 5' - 7 1/4" -
0.03 in-
wg/100ft 0.00 in-wg
0.03 in-wgFittings 392 CFM - 500 FPM 0.02 in-wg - 1.644898 - 0.03 in-wg
5 Fittings 784 CFM - 0 FPM 0.03 in-wg - 0 - 0.00 in-wg 0.00 in-wg
6
Duct 784 CFM 14"x14" 580 FPM - 14' - 0 3/32" -
0.04 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 784 CFM - 580 FPM 0.02 in-wg - 0.381818 - 0.01 in-wg
7
Fittings 784 CFM - 0 FPM 0.03 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 784 CFM - - - - - - 0.00 in-wg
10
Duct 0 CFM 12"ø 0 FPM - 0' - 3 21/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg
11
Duct 392 CFM 12"ø 500 FPM - 5' - 8 3/4" -
0.03 in-
wg/100ft 0.00 in-wg
0.03 in-wgFittings 392 CFM - 500 FPM 0.02 in-wg - 1.644898 - 0.03 in-wg
12
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
15
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
18
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
19
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
Critical Path : 7-6-5-11-18 ; Total Pressure Loss : 0.05 in-wg

99. G r o u p I | 97
Classroom 3
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
3 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
4
Duct 392 CFM 12"ø 500 FPM - 5' - 8 7/8" -
0.03 in-
wg/100ft 0.00 in-wg
0.03 in-wgFittings 392 CFM - 500 FPM 0.02 in-wg - 1.644898 - 0.03 in-wg
5 Fittings 784 CFM - 0 FPM 0.03 in-wg - 0 - 0.00 in-wg 0.00 in-wg
6
Duct 784 CFM 14"x14" 580 FPM -
13' - 11
5/32" -
0.04 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 784 CFM - 580 FPM 0.02 in-wg - 0.381818 - 0.01 in-wg
7
Fittings 784 CFM - 0 FPM 0.03 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 784 CFM - - - - - - 0.00 in-wg
10 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
11
Duct 392 CFM 12"ø 500 FPM - 5' - 7 1/8" -
0.03 in-
wg/100ft 0.00 in-wg
0.03 in-wgFittings 392 CFM - 500 FPM 0.02 in-wg - 1.644898 - 0.03 in-wg
12
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
15
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
18
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
19
Duct 196 CFM 8"ø 560 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 196 CFM - 560 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 196 CFM - - - - - - 0.00 in-wg
Critical Path : 7-6-5-4-19 ; Total Pressure Loss : 0.05 in-wg

100. G r o u p I | 98
Classroom 4
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
4 Fittings 812 CFM - 0 FPM 0.02 in-wg - 0.034091 - 0.00 in-wg 0.00 in-wg
7
Duct 203 CFM 8"ø 580 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
8 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
9
Duct 203 CFM 8"ø 580 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
15
Duct 203 CFM 8"ø 580 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
16
Duct 406 CFM 12"ø 520 FPM - 4' - 7 25/32" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 406 CFM - 520 FPM 0.02 in-wg - 0.0525 - 0.00 in-wg
17 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
20 Fittings 406 CFM - 0 FPM 0.01 in-wg - 2.9 - 0.02 in-wg 0.02 in-wg
21 Fittings 406 CFM - 0 FPM 0.01 in-wg - 2.9 - 0.02 in-wg 0.02 in-wg
23
Duct 406 CFM 12"ø 520 FPM - 6' - 0 9/16" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 406 CFM - 520 FPM 0.02 in-wg - 0.0525 - 0.00 in-wg
24
Fittings 812 CFM - 0 FPM 0.04 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 812 CFM - - - - - - 0.00 in-wg
25
Duct 812 CFM 14"x14" 600 FPM -
13' - 5
17/32" -
0.04 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 812 CFM - 600 FPM 0.02 in-wg - 0.381818 - 0.01 in-wg
26
Duct 203 CFM 8"ø 580 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
Critical Path : 24-25-4-21-23-26 ; Total Pressure Loss : 0.04 in-wg

101. G r o u p I | 99
Classroom 5
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
3
Duct 0 CFM 12"ø 0 FPM - 0' - 6 19/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 8500 - 0.00 in-wg
4 Fittings 812 CFM - 0 FPM 0.04 in-wg - 0 - 0.00 in-wg 0.00 in-wg
9
Duct 203 CFM 8"ø 580 FPM - 6' - 0 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.02 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.637778 - 0.01 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
13
Duct 0 CFM 12"ø 0 FPM - 0' - 7 13/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 8500 - 0.00 in-wg
14
Duct 203 CFM 8"ø 580 FPM - 6' - 0 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.02 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.637778 - 0.01 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
15 Fittings 406 CFM - 0 FPM 0.01 in-wg - 2.9 - 0.03 in-wg 0.03 in-wg
16
Duct 203 CFM 8"ø 580 FPM - 6' - 0 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.316667 - 0.01 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
21 Fittings 406 CFM - 0 FPM 0.01 in-wg - 2.9 - 0.03 in-wg 0.03 in-wg
25
Fittings 812 CFM - 0 FPM 0.04 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 812 CFM - - - - - - 0.00 in-wg
26
Duct 812 CFM 14"x14" 600 FPM - 13' - 5 7/16" -
0.04 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 812 CFM - 600 FPM 0.02 in-wg - 0.381818 - 0.01 in-wg
27
Duct 406 CFM 12"ø 520 FPM - 6' - 9" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 406 CFM - 520 FPM 0.02 in-wg - 0.031837 - 0.00 in-wg
28
Duct 406 CFM 12"ø 520 FPM - 5' - 4 3/16" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 406 CFM - 520 FPM 0.02 in-wg - 0.031837 - 0.00 in-wg
29
Duct 203 CFM 8"ø 580 FPM - 6' - 0 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 203 CFM - 580 FPM 0.02 in-wg - 0.316667 - 0.01 in-wg

102. G r o u p I | 100
Air Terminal 203 CFM - - - - - - 0.00 in-wg
Critical Path : 25-26-4-21-27-9 ; Total Pressure Loss : 0.06 in-wg
Classroom 6
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
3 Fittings 406 CFM - 0 FPM 0.01 in-wg - 2.9 - 0.03 in-wg 0.03 in-wg
4 Fittings 812 CFM - 0 FPM 0.04 in-wg - 0 - 0.00 in-wg 0.00 in-wg
8
Duct 0 CFM 10"ø 0 FPM - 0' - 2" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 0.036667 - 0.00 in-wg
10
Duct 203 CFM 8"ø 580 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
12
Duct 203 CFM 8"ø 580 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
14
Duct 0 CFM 10"ø 0 FPM - 0' - 0 3/16" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 0.036667 - 0.00 in-wg
15
Duct 203 CFM 8"ø 580 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
16
Duct 406 CFM 12"ø 520 FPM - 4' - 9 3/16" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 406 CFM - 520 FPM 0.02 in-wg - 0.031837 - 0.00 in-wg
19
Fittings 812 CFM - 0 FPM 0.04 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 812 CFM - - - - - - 0.00 in-wg
20
Duct 812 CFM 14"x14" 600 FPM - 13' - 5 7/16" -
0.04 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 812 CFM - 600 FPM 0.02 in-wg - 0.381818 - 0.01 in-wg
21 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg

103. G r o u p I | 101
22
Duct 406 CFM 12"ø 520 FPM - 6' - 2" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 406 CFM - 520 FPM 0.02 in-wg - 0.031837 - 0.00 in-wg
23 Fittings 406 CFM - 0 FPM 0.01 in-wg - 2.9 - 0.03 in-wg 0.03 in-wg
24 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
25
Duct 203 CFM 8"ø 580 FPM - 6' - 1 1/2" -
0.07 in-
wg/100ft 0.00 in-wg
0.01 in-wg
Fittings 203 CFM - 580 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
Air Terminal 203 CFM - - - - - - 0.00 in-wg
Critical Path : 19-20-4-3-22-25 ; Total Pressure Loss : 0.05 in-wg
Classroom 7
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
3
Duct 0 CFM 12"ø 0 FPM - 0' - 9 19/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 8500 - 0.00 in-wg
4 Fittings 912 CFM - 0 FPM 0.03 in-wg - 0 - 0.00 in-wg 0.00 in-wg
6
Duct 228 CFM 8"ø 650 FPM - 0' - 10 1/2" -
0.09 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 228 CFM - 650 FPM 0.03 in-wg - 0.135185 - 0.00 in-wg
Air Terminal 228 CFM - - - - - - 0.00 in-wg
8
Duct 0 CFM 12"ø 0 FPM -
0' - 11
13/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 8500 - 0.00 in-wg
9
Duct 228 CFM 8"ø 650 FPM - 0' - 10 1/2" -
0.09 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 228 CFM - 650 FPM 0.03 in-wg - 0.135185 - 0.00 in-wg
Air Terminal 228 CFM - - - - - - 0.00 in-wg
11
Duct 228 CFM 8"ø 650 FPM - 0' - 10 1/2" -
0.09 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 228 CFM - 650 FPM 0.03 in-wg - 0.135185 - 0.00 in-wg
Air Terminal 228 CFM - - - - - - 0.00 in-wg
18
Duct 456 CFM 12"ø 580 FPM - 6' - 7 9/32" -
0.05 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 456 CFM - 580 FPM 0.02 in-wg - 0.0432 - 0.00 in-wg
22 Duct 456 CFM 12"ø 580 FPM - 7' - 2 15/32" - 0.05 in- 0.00 in-wg 0.00 in-wg

104. G r o u p I | 102
wg/100ft
Fittings 456 CFM - 580 FPM 0.02 in-wg - 0.0432 - 0.00 in-wg
26
Fittings 912 CFM - 0 FPM 0.05 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 912 CFM - - - - - - 0.00 in-wg
29
Duct 912 CFM 15"x15" 580 FPM -
13' - 3
15/32" -
0.03 in-
wg/100ft 0.00 in-wg
0.02 in-wgFittings 912 CFM - 580 FPM 0.02 in-wg - 0.608571 - 0.01 in-wg
30 Fittings 456 CFM - 0 FPM 0.01 in-wg - 2.9 - 0.02 in-wg 0.02 in-wg
31 Fittings 456 CFM - 0 FPM 0.01 in-wg - 2.9 - 0.02 in-wg 0.02 in-wg
36
Duct 228 CFM 9"ø 520 FPM - 5' - 0 25/32" -
0.05 in-
wg/100ft 0.00 in-wg
0.02 in-wgFittings 228 CFM - 520 FPM 0.02 in-wg - 0.84375 - 0.01 in-wg
37
Duct 228 CFM 9"ø 520 FPM - 5' - 0 25/32" -
0.05 in-
wg/100ft 0.00 in-wg
0.02 in-wgFittings 228 CFM - 520 FPM 0.02 in-wg - 0.84375 - 0.01 in-wg
38
Duct 228 CFM 9"ø 520 FPM - 5' - 0 25/32" -
0.05 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 228 CFM - 520 FPM 0.02 in-wg - 0.27125 - 0.00 in-wg
39
Duct 228 CFM 9"ø 520 FPM - 5' - 0 25/32" -
0.05 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 228 CFM - 520 FPM 0.02 in-wg - 0.27125 - 0.00 in-wg
40
Duct 228 CFM 8"ø 650 FPM - 0' - 10 1/2" -
0.09 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 228 CFM - 650 FPM 0.03 in-wg - 0.135185 - 0.00 in-wg
Air Terminal 228 CFM - - - - - - 0.00 in-wg
Critical Path : 26-29-4-30-22-37-11 ; Total Pressure Loss : 0.07 in-wg

105. G r o u p I | 103
Lavatories
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
3 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
4
Duct 282 CFM 12"ø 360 FPM - 6' - 0 5/8" -
0.02 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 282 CFM - 360 FPM 0.01 in-wg - 1.644898 - 0.01 in-wg
5 Fittings 564 CFM - 0 FPM 0.02 in-wg - 0 - 0.00 in-wg 0.00 in-wg
6
Duct 564 CFM 14"x14" 410 FPM -
13' - 11
5/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 564 CFM - 410 FPM 0.01 in-wg - 0.381818 - 0.00 in-wg
7
Fittings 564 CFM - 0 FPM 0.02 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 564 CFM - - - - - - 0.00 in-wg
10 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
11
Duct 282 CFM 12"ø 360 FPM - 5' - 3 3/8" -
0.02 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 282 CFM - 360 FPM 0.01 in-wg - 1.644898 - 0.01 in-wg
12
Duct 141 CFM 8"ø 400 FPM - 6' - 1 1/2" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 141 CFM - 400 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 141 CFM - - - - - - 0.00 in-wg
15
Duct 141 CFM 8"ø 400 FPM - 6' - 1 1/2" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 141 CFM - 400 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 141 CFM - - - - - - 0.00 in-wg
18
Duct 141 CFM 8"ø 400 FPM - 6' - 1 1/2" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 141 CFM - 400 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 141 CFM - - - - - - 0.00 in-wg
19
Duct 141 CFM 8"ø 400 FPM - 6' - 1 1/2" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 141 CFM - 400 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 141 CFM - - - - - - 0.00 in-wg
Critical Path : 7-6-5-4-19 ; Total Pressure Loss : 0.02 in-wg

106. G r o u p I | 104
Office 1
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
4
Duct 254 CFM 12"ø 320 FPM - 6' - 1 27/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 254 CFM - 320 FPM 0.01 in-wg - 1.644898 - 0.01 in-wg
5 Fittings 508 CFM - 0 FPM 0.01 in-wg - 0 - 0.00 in-wg 0.00 in-wg
6
Duct 508 CFM 14"x14" 370 FPM - 9' - 6 29/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 508 CFM - 370 FPM 0.01 in-wg - 0.381818 - 0.00 in-wg
7
Fittings 508 CFM - 0 FPM 0.01 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 508 CFM - - - - - - 0.00 in-wg
10
Duct 0 CFM 12"ø 0 FPM - 0' - 4 9/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg
11
Duct 254 CFM 12"ø 320 FPM - 5' - 2 5/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 254 CFM - 320 FPM 0.01 in-wg - 1.644898 - 0.01 in-wg
12
Duct 127 CFM 8"ø 360 FPM - 6' - 1 1/2" -
0.03 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 127 CFM - 360 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 127 CFM - - - - - - 0.00 in-wg
15
Duct 127 CFM 8"ø 360 FPM - 6' - 1 1/2" -
0.03 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 127 CFM - 360 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 127 CFM - - - - - - 0.00 in-wg
16
Duct 127 CFM 8"ø 360 FPM - 6' - 1 1/2" -
0.03 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 127 CFM - 360 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 127 CFM - - - - - - 0.00 in-wg
18
Duct 0 CFM 12"ø 0 FPM - 0' - 8 5/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg
19
Duct 127 CFM 8"ø 360 FPM - 6' - 1 1/2" -
0.03 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 127 CFM - 360 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 127 CFM - - - - - - 0.00 in-wg

107. G r o u p I | 105
Critical Path : 7-6-5-4-19 ; Total Pressure Loss : 0.02 in-wg
Office 2
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
3
Duct 0 CFM 12"ø 0 FPM - 0' - 4 9/16" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg
4
Duct 210 CFM 12"ø 270 FPM - 6' - 1 27/32" -
0.01 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 210 CFM - 270 FPM 0.00 in-wg - 1.644898 - 0.01 in-wg
5 Fittings 420 CFM - 0 FPM 0.01 in-wg - 0 - 0.00 in-wg 0.00 in-wg
6
Duct 420 CFM 14"x14" 310 FPM -
10' - 6
31/32" -
0.01 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 420 CFM - 310 FPM 0.01 in-wg - 0.381818 - 0.00 in-wg
7
Fittings 420 CFM - 0 FPM 0.01 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 420 CFM - - - - - - 0.00 in-wg
10
Duct 0 CFM 12"ø 0 FPM - 0' - 4 9/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg
11
Duct 210 CFM 12"ø 270 FPM - 5' - 2 5/32" -
0.01 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 210 CFM - 270 FPM 0.00 in-wg - 1.644898 - 0.01 in-wg
12
Duct 105 CFM 8"ø 300 FPM - 6' - 1 1/2" -
0.02 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 105 CFM - 300 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 105 CFM - - - - - - 0.00 in-wg
15
Duct 105 CFM 8"ø 300 FPM - 6' - 1 1/2" -
0.02 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 105 CFM - 300 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 105 CFM - - - - - - 0.00 in-wg
18 Duct 105 CFM 8"ø 300 FPM - 6' - 1 1/2" -
0.02 in-
wg/100ft 0.00 in-wg 0.00 in-wg

108. G r o u p I | 106
Fittings 105 CFM - 300 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 105 CFM - - - - - - 0.00 in-wg
19
Duct 105 CFM 8"ø 300 FPM - 6' - 1 1/2" -
0.02 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 105 CFM - 300 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 105 CFM - - - - - - 0.00 in-wg
Critical Path : 7-6-5-4-19 ; Total Pressure Loss : 0.01 in-wg
Conference Rooms
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
3
Duct 294 CFM 12"ø 370 FPM - 6' - 0 9/16" -
0.02 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 294 CFM - 370 FPM 0.01 in-wg - 0.0525 - 0.00 in-wg
4 Fittings 588 CFM - 0 FPM 0.01 in-wg - 0.034091 - 0.00 in-wg 0.00 in-wg
7
Duct 147 CFM 8"ø 420 FPM - 6' - 1 1/2" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 147 CFM - 420 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 147 CFM - - - - - - 0.00 in-wg
8 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
9
Duct 147 CFM 8"ø 420 FPM - 6' - 1 1/2" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 147 CFM - 420 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 147 CFM - - - - - - 0.00 in-wg
13
Duct 147 CFM 8"ø 420 FPM - 6' - 1 1/2" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 147 CFM - 420 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 147 CFM - - - - - - 0.00 in-wg
16 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
17
Duct 294 CFM 12"ø 370 FPM - 4' - 7 25/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 294 CFM - 370 FPM 0.01 in-wg - 0.0525 - 0.00 in-wg

109. G r o u p I | 107
22 Fittings 294 CFM - 0 FPM 0.00 in-wg - 2.9 - 0.01 in-wg 0.01 in-wg
23 Fittings 294 CFM - 0 FPM 0.00 in-wg - 2.9 - 0.01 in-wg 0.01 in-wg
24
Fittings 588 CFM - 0 FPM 0.02 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 588 CFM - - - - - - 0.00 in-wg
25
Duct 588 CFM 14"x14" 430 FPM -
13' - 5
17/32" -
0.02 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 588 CFM - 430 FPM 0.01 in-wg - 0.381818 - 0.00 in-wg
26
Duct 147 CFM 8"ø 420 FPM - 6' - 1 1/2" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wg
Fittings 147 CFM - 420 FPM 0.01 in-wg - 0.11 - 0.00 in-wg
Air Terminal 147 CFM - - - - - - 0.00 in-wg
Critical Path : 24-25-4-23-3-26 ; Total Pressure Loss : 0.02 in-wg
Lobby
Total Pressure Loss Calculations by Sections
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
3
Duct 604 CFM 14"ø 570 FPM - 7' - 1 1/16" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 604 CFM - 570 FPM 0.02 in-wg - 0.06 - 0.00 in-wg
4 Fittings 1812 CFM - 0 FPM 0.04 in-wg - 0 - 0.00 in-wg 0.00 in-wg
7
Duct 302 CFM 10"ø 550 FPM - 8' - 4 3/16" -
0.05 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 302 CFM - 550 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
10
Duct 0 CFM 19"ø 0 FPM - 0' - 11 1/2" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 0 CFM - 0 FPM 0.00 in-wg - 8500 - 0.00 in-wg
13
Fittings 302 CFM - 0 FPM 0.05 in-wg - 0.0432 - 0.00 in-wg
0.00 in-wgAir Terminal 302 CFM - - - - - - 0.00 in-wg
14
Duct 302 CFM 10"ø 550 FPM - 8' - 0 11/16" -
0.05 in-
wg/100ft 0.00 in-wg
0.02 in-wgFittings 302 CFM - 550 FPM 0.02 in-wg - 0.612789 - 0.01 in-wg
15
Fittings 302 CFM - 0 FPM 0.05 in-wg - 0.0432 - 0.00 in-wg
0.00 in-wgAir Terminal 302 CFM - - - - - - 0.00 in-wg
16
Duct 302 CFM 10"ø 550 FPM - 8' - 0 11/16" -
0.05 in-
wg/100ft 0.00 in-wg
0.02 in-wgFittings 302 CFM - 550 FPM 0.02 in-wg - 1.073601 - 0.02 in-wg

110. G r o u p I | 108
17
Fittings 302 CFM - 0 FPM 0.05 in-wg - 0.0432 - 0.00 in-wg
0.00 in-wgAir Terminal 302 CFM - - - - - - 0.00 in-wg
21
Duct 302 CFM 10"ø 550 FPM - 8' - 0 11/16" -
0.05 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 302 CFM - 550 FPM 0.02 in-wg - 0.374709 - 0.01 in-wg
23
Fittings 302 CFM - 0 FPM 0.05 in-wg - 0.0432 - 0.00 in-wg
0.00 in-wgAir Terminal 302 CFM - - - - - - 0.00 in-wg
25
Duct 302 CFM 10"ø 550 FPM - 8' - 0 11/16" -
0.05 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 302 CFM - 550 FPM 0.02 in-wg - 0.230803 - 0.00 in-wg
28
Duct 302 CFM 10"ø 550 FPM - 8' - 4 3/16" -
0.05 in-
wg/100ft 0.00 in-wg
0.01 in-wgFittings 302 CFM - 550 FPM 0.02 in-wg - 0.11 - 0.00 in-wg
29 Fittings 0 CFM - 0 FPM 0.00 in-wg - 0 - 0.00 in-wg 0.00 in-wg
33 Fittings 604 CFM - 0 FPM 0.00 in-wg - 7.763333 - 0.04 in-wg 0.04 in-wg
36 Fittings 1208 CFM - 0 FPM 0.02 in-wg - 1.713333 - 0.03 in-wg 0.03 in-wg
38
Duct 1812 CFM 20"x20" 650 FPM - 27' - 1 3/16" -
0.03 in-
wg/100ft 0.01 in-wg
0.04 in-wg
Fittings 1812 CFM - 650 FPM 0.03 in-wg - 1.15 - 0.03 in-wg
Equipment 1812 CFM - - - - - - 0.00 in-wg
40
Fittings 302 CFM - 0 FPM 0.05 in-wg - 0.0432 - 0.00 in-wg
0.00 in-wgAir Terminal 302 CFM - - - - - - 0.00 in-wg
41
Fittings 302 CFM - 0 FPM 0.05 in-wg - 0.0432 - 0.00 in-wg
0.00 in-wgAir Terminal 302 CFM - - - - - - 0.00 in-wg
45
Duct 1208 CFM 19"ø 610 FPM - 7' - 6 1/2" -
0.03 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 1208 CFM - 610 FPM 0.02 in-wg - 0.0117 - 0.00 in-wg
47
Duct 604 CFM 19"ø 310 FPM - 18' - 0" -
0.01 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 604 CFM - 310 FPM 0.01 in-wg - 0.136667 - 0.00 in-wg
Critical Path : 38-4-36-45-16-15 ; Total Pressure Loss : 0.10 in-wg
Hallways
Total Pressure Loss Calculations by Sections

111. G r o u p I | 109
Section Element Flow Size Velocity
Velocity
Pressure Length
Loss
Coefficient Friction
Total Pressure
Loss
Section
Pressure
Loss
1
Fittings 620 CFM - 0 FPM 0.02 in-wg - 0 - 0.00 in-wg
0.00 in-wgEquipment 620 CFM - - - - - - 0.00 in-wg
2
Duct 620 CFM 14"ø 580 FPM - 5' - 3 9/32" -
0.04 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 620 CFM - 580 FPM 0.02 in-wg - 0.046715 - 0.00 in-wg
3
Duct 155 CFM 12"x12" 160 FPM - 0' - 8" -
0.00 in-
wg/100ft 0.00 in-wg
0.06 in-wg
Fittings 155 CFM - 160 FPM 0.00 in-wg - 0 - 0.00 in-wg
Air Terminal 155 CFM - - - - - - 0.06 in-wg
4 Fittings 155 CFM - 0 FPM 0.00 in-wg - 8.11847 - 0.02 in-wg 0.02 in-wg
5
Duct 155 CFM 12"x12" 160 FPM - 0' - 8" -
0.00 in-
wg/100ft 0.00 in-wg
0.06 in-wg
Fittings 155 CFM - 160 FPM 0.00 in-wg - 0 - 0.00 in-wg
Air Terminal 155 CFM - - - - - - 0.06 in-wg
6 Fittings 155 CFM - 0 FPM 0.00 in-wg - 3.970068 - 0.01 in-wg 0.01 in-wg
7
Duct 465 CFM 14"ø 430 FPM -
33' - 0
23/32" -
0.02 in-
wg/100ft 0.01 in-wg
0.01 in-wgFittings 465 CFM - 430 FPM 0.01 in-wg - 0.171667 - 0.00 in-wg
8
Duct 155 CFM 12"x12" 160 FPM - 0' - 8" -
0.00 in-
wg/100ft 0.00 in-wg
0.06 in-wg
Fittings 155 CFM - 160 FPM 0.00 in-wg - 0 - 0.00 in-wg
Air Terminal 155 CFM - - - - - - 0.06 in-wg
9 Fittings 155 CFM - 0 FPM 0.00 in-wg - 1.499592 - 0.00 in-wg 0.00 in-wg
10
Duct 310 CFM 14"ø 290 FPM - 29' - 8 9/16" -
0.01 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 310 CFM - 290 FPM 0.01 in-wg - 0.136667 - 0.00 in-wg
11
Fittings 155 CFM - 0 FPM 0.00 in-wg - 0.007747 - 0.00 in-wg
0.06 in-wgAir Terminal 155 CFM - - - - - - 0.06 in-wg
12
Duct 155 CFM 14"ø 140 FPM -
30' - 10
29/32" -
0.00 in-
wg/100ft 0.00 in-wg
0.00 in-wgFittings 155 CFM - 140 FPM 0.00 in-wg - 0.2 - 0.00 in-wg
Critical Path : 1-2-4-3 ; Total Pressure Loss : 0.08 in-wg

112. G r o u p I | 110