Sudan University of Science and Technology

Collage of Engineering
Mechanical Engineering

Design of Air Conditioning System for Sport Hall for

1000 Occupant
‫ متفرج‬1000 ‫تصميم نظام تكييف لصالة رياضية سعة‬
A Project Submitted in Partial Fulfillment for the
Requirement of the Degree of B.Eng. (HONOR) In
Mechanical Engineering
Prepaid By:
1- ALameen Awad Alameen Ahmed
2- Altayeb Ahmed Altayeb Mohammed
3- Mohamed Ameir Huseen Elnoor

Supervisor:
Dr. Eihab Abdelraouf Mustafa Omer

October 2017
‫االية‬

‫‪i‬‬
 DEDICATION
For their countless sleepless nights filled with prayer and hopes for
our Success in life, the least we could do is to dedicate the fruit of
our Efforts to the two most influential people in our life mother and
father.
…This is for you.
For providing us with constant encouragement to complete this
journey, And for believing in our ability to always do our best, we
would like to Dedication this project to our teachers who have been
with us all the Step of the way.
We are truly blessed to have them by our side.
Experience also, we predict the effort to the kindness person, who
provides us with his knowledge Experience studies tell this see the
light. And the respectful college teachers who take our hands since
our
Entrance to the college till this step.

ii
 ACKNOWLEDGMENTS

The greatest thanks always to Allah for complete this project .

Our most grateful and appreciation to or supervisor Dr. Eihab
Abdelraouf Mustafa Omer for his expertise, support and endless
valuable advices .which guided us to throughout this work and our
engineering career life .
We also would like to thanks all of our teachers in mechanical
engineering school for all the help and knowledge that they gave to
us .
We also would like to thanks Eng. Abd Alhameed for his all efforts,
knowledge and experience which give to us.

iii
 Abstract

The aim of this study is calculate cooling load for sport hall (1000
occupant) by mathematical relation, software program and select proper air
conditioning devices and equipment.

Cooling load have been calculated by relation by using cooling load

temperature difference (CLTD) and it founded 116TR, and software program
by Hourly Analysis Program (HAP) and it founded 103TR then air duct
dimension have been calculated by using McQuay duct sizer design tools by
using constant head loss method.

Five air conditioning unit package (50Z030) 30TR capacity have been
selected from CARRIER product CatLog.

iv
 ‫المستخلص‬

‫الهدف من هذا المشروع هو حساب االحمال الحرارية لصالة رياضية سعة الف متفرج باستخدام‬
‫العالقات الرياضية وباستخدام برنامج حاسوب‪ ،‬ومن ثم اختيار اجهزة التكييف المناسبة على ضوء‬
‫االحمال الحرارية‪.‬‬

‫تم حساب االحمال الحرارية باستخدام العالقات الرياضية بطريقة فرق درجة الحرارة لحمل‬
‫التبريد ووجد انه يساوي ‪ 116‬طن تبريدي وباستخدام برنامج الحاسوب ‪ 103‬طن تبريدي ومن ثم تم‬
‫حساب ابعاد مجاري الهواء باستخدام برنامج ‪ McQuay Duct Sizer‬بطريقة ثبات فرق الضغط‪.‬‬

‫تم اختيار خمس وحدات تكييف ‪ Package‬سعة ‪ 30‬طن تبريدي من نوع ‪(50Z030‬‬
‫‪ .(CARRIER‬من منتجات شركة كاريير االمريكية‪.‬‬

‫‪v‬‬
 Table of Content
TOPICS NO

‫األية‬ i

DEDICATION ii

ACKNOWLEDGEMENT iii

ABSTRACT iv

‫المستخلص‬ v

TABLE OF CONTENTS vi

LIST OF FIGURES x

LIST OF TABLES xi

Table of Abbreviations xii

LIST OF APPENDIX xiv

CHAPTER ONE :INTRODUCTION

1.1 Introduction 2

1.2 Problem statement 2

1.3 Objective 3

1.4 Significant of study 3

1.5 Scope of study 3

CHAPTER TWO LITERATURE REVIEW

2.1 Introduction 5

2.2 Classification of air conditioning systems 6

2.2.1 All air systems 7

2.2.2 All water systems 7

2.2.3 Air-water systems 8

vi
 2.3 Unitary refrigerant based systems 8

2.3.1 Window Type 9

2.3.2 Split Type 10

2.3.3 Packaged Air Conditioner 11

2.3.4 Central Type 12

2.3.5 Evaporative Type 14

2.4 Thermal Load 16

2.4.1 Thermal Load Calculation 16

2.4.2 Outdoor and Indoor Thermal Load 16

2.5 External Loads 17

2.5.1 Heat Transfer through Fenestration 17

2.5.2 Heat Transfer Due to Infiltration 17

2.5.3 Solar Heat Gain through Glazing 18

2.6 Internal Load 19

2.6.1 People 19

2.6.2 Light 19

2.6.3 Appliance 20

2.6.4 Ventilation Load 20

2.6.5 Infiltration Load 20

2.7 Thermal Comfort 21

CHAPTER THREE METHODOLOGY

3.1 24
Methodology
3.2 24
Calculation of thermal load by Relation

vii
3.3 External Cooling Load 24

3.3.1 Roofs, walls, and conduction through glass 24

3.3.2 Solar load through glass 24

3.3.3 Cooling load from partitions, ceilings, floors 25

3.4 Internal Cooling Load 25

3.4.1 People 25

3.4.2 Light 25

3.4.3 Power 26

3.4.4 Appliances 26

3.4.5 Ventilation and Infiltration Air 26

3.5 Calculation by software Hourly Analysis 27

Program (HAP)
3.5.1 28
Data input in Hourly analysis software
3.6 Working with HAP Input Windows 30

3.6.1 Weather properties window 31

3.6.2 Space Properties window 31

3.6.3 Air System Properties window 37

3.6.4 System Design Report 41

3.7 Duct Design 42

3.7.1 Duct System Component 43

3.7.2 Duct Design Criteria 43

3.7.3 Type of Duct 43

3.7.4 Static pressure 43

viii
3.7.5 Duct Aspect Ratio 44

3.8 Conditioning Space 45

3.8.1 Construction Data 45

CHAPTER FOUR CALCULATIONS

4.1 Introduction 48

4.2 Calculate cooling load By Relation 48

4.2.1 External Cooling Load 48

4.2.2 Internal Cooling Load 51

4.3 Calculation by software Hourly Analysis 54

Program (HAP)
4.4 Duct Design 55

CHAPTER FIVE EQUIPMENT SELECTION

5.1 Introduction 59

5.2 Packaged Units 59

5.2.1 Unit Selection 59

5.3 Diffusers Selection 60

5.4 Conclusion 61

5.5 Recommendations 62

5.6 References 63

APPENDIX

ix
 LIST OF FIGURES
Fig 2-1 : Window type _______________________________________ 10
Fig 2-2: Spilt type ___________________________________________ 11
Fig 2-3: Package type ________________________________________ 12
Fig 2-4: Central type ________________________________________ 13
Fig 2-5: Evaporator type ____________ Error! Bookmark not defined.4
Fig 3-1: The user interface of hourly analysis software _____________ 28
Fig 3-2: Weather properties ___________________________________ 30
Fig 3-3: Space properties-general ______ Error! Bookmark not defined.
Fig 3-4: Space properties-internal load __ Error! Bookmark not defined.
Fig 3-5: Space properties-wall, window and door Error! Bookmark not
defined.
Fig 3-6: Roof Data ___________________ Error! Bookmark not defined.
Fig 3-7: Infiltration __________________ Error! Bookmark not defined.
Fig 3-8: Floor _______________________ Error! Bookmark not defined.
Fig 3-9: Air system general data _______ Error! Bookmark not defined.
Fig 3-10: System component data ______ Error! Bookmark not defined.
Fig 3-11: Zone component ____________ Error! Bookmark not defined.
Fig 3-12: Sizing Data_________________ Error! Bookmark not defined.
Fig 3-13: System design report ________ Error! Bookmark not defined.
Fig 3-14: MCQUAY duct sizer layout ___ Error! Bookmark not defined.
Fig 3-15: Sport Hall _________________ Error! Bookmark not defined.
Fig 5-1: 250, 250-AA Titus diffuser _____ Error! Bookmark not defined.

x
 LIST OF TABLES
Table 4-1: load summary for zone1 .......................................................... 53
Table 4-2: load summary for zone 2 ......................................................... 54
Table 4-3: Main Duct .................................................................................. 55
Table 4-4: Branch Duct .............................................................................. 55
Table 4-5: Diffuser Supply Duct................................................................ 56

xi
 Table of Abbreviations
HVAC Heating and ventilating air conditioning

TOR Ton of refrigeration

American Society of Heating and Refrigeration and Air

ASHRAE
Conditioning Engineers.

TFM Transfer Function Method

DBT Dry bulb temperature

WBT Wet bulb temperature

Φ Relative humidity

w Humidity ratio

H Enthalpy

CLF Cooling Load Factor

CLTD Cooling Load Temperature Differential

U Heat transfer coefficient

A Area

𝑆𝐶 Shading coefficient

𝑆𝐶𝐿 Solar cooling load factor with no interior shade or with shade

𝑊 Watts input from electrical plans or lighting fixture data

𝑃 Horsepower rating from electrical plans or manufacturer’s data

𝐹𝑢𝑙 Special allowance factor, as appropriate

𝐸𝐹 Efficiency factors and arrangements to suit circumstance

𝐹𝑈 Usage factors,

𝐹𝑅 Radiation factors

𝐹𝐿 Load factor

𝑄 Ventilation from ASHRAE Standard 62

HAP Hourly Analysis Program

xii
cfm Cubic feet per minute

FPM Feet per minute

xiii
 List of Appendix
Appendix A: Heat Gain from Occupant…………………………...65

Appendix B: Resistance of Air ……………………………………66

Appendix C: Lighting Power Densities…………………………...67

Appendix D: Cooling Load Temperature Difference for Roof….68

Appendix E: Wall Construction Grop…………………………….69

Appendix F: Cooling Load Temperature Difference for Wall…..70

Appendix G: CLTD Correction for Wall and Roof……………...71

Appendix H: Ventilation Rates……………………………………72

Appendix I: Psychrometric Chart…………………………....73

xiv
Chapter One

Introduction

1
1.1 Introduction

The American Society of Heating& Refrigerating and Air-Conditioning

engineers ASHRAE defines air conditioning as: "The process of heating air so as
to control simultaneously its temperature, humidity, cleanliness, and distribution to
meet the requirements of the conditioned space." as the definition indicates, the
important actions involved in the operation of an air conditioning system (1)

 Temperature control.
 Humidity control.
 Air filtering & cleaning and purification.
 Air movement and circulation.

The purpose of air conditioning is to provide a comfortable temperature for

human beings and machines and equipment to be protected. Air conditioning can
either be for cooling or heating. This project is dealing with conditioning the air
within certain areas to keep it in the range of Human comfort. The human beings
will feel more comfortable when he is in an atmosphere of a reasonable temperature
and humidity.

1.2 Problem Statement

Estimate Cooling load for sport hall and select proper air conditioning
devices and equipment.

1.3 Objective
 Calculate the thermal load manually.
 Calculate the thermal load by HAP application.
 Select suitable air conditioning equipment.

2
1.4 Significant of Study
The importance of this research and its essence in preserving both the two
methods (manual and software) of calculating Air Conditioning cooling load for
sizing cooling equipment and a general procedure for calculating cooling load, for
nonresidential applications.

1.5 Scope of Study

Estimate the cooling load calculation for nonresidential building
according to The American Society of Heating& Refrigerating and Air-
Conditioning engineers ASHRAE Stander.

3
 CHAPTER TWO

LITERATURE REVIEW

4
2.1 Introduction

Air-conditioning is a process that simultaneously conditions air; distributes

it combined with the outdoor air to the conditioned space, and at the same time
controls and maintains the required space’s, temperature, humidity, air movement,
air cleanliness, sound level, and pressure differential within predetermined
limits for the health and comfort of the occupants, for product processing, or
both(2)

As mentioned earlier, the term “air conditioning,” when properly used, now
means the total control of temperature, moisture in the air (humidity), supply of
outside air for ventilation, filtration of airborne particles, and air movement in the
occupied space. There are seven main processes required to achieve full air
conditioning and they are listed and explained below:

This processes are:

1- Heating: the process of adding thermal energy (heat) to the conditioned

space for the purposes of raising or maintaining the temperature of the space

2- Cooling: the process of removing thermal energy (heat) from the conditioned
space for the purposes of lowering or maintaining the temperature

of the space.

3- Cleaning: the process of removing particulates, (dust etc.,) and biological

contaminants, (insects, pollen etc.,) from the air delivered to the conditioned space
for the purposes of improving or maintaining the air quality.

4- Humidification

5
 This as its name implies, means that the moisture content of the air is
increased. This may be accomplished by either water or steam in air conditioning
system Humidification can be obtained by direct injection of water drops of
aerosol size into the room being conditioned.(A variant of this last technique is to
inject aerosol-sized droplets into an airstream moving through a duct.)

5- Dehumidification

There principal methods whereby moist air can be dehumidified in

application of air conditioning system cooling to a temperature below the dew
point, Cooling to a temperature below the dew point is done by passing the moist
air over a cooler coil or through an air washer provided with chilled water(3)

6- Ventilating:

The process of exchanging air between the outdoors and the conditioned
space for the purposes of diluting the gaseous contaminants in the air and
improving or maintaining air quality, composition and freshness. Ventilation can
be achieved either through natural ventilation or mechanical ventilation. Natural
ventilation is driven by natural draft, like when you open a window. Mechanical
ventilation can be achieved by using fans to draw air in from outside or by fans that
exhaust air from the space to outside

7- Air Movement: the process of circulating and mixing air through conditioned
spaces in the building for the purposes of achieving the proper ventilation and
facilitating the thermal energy transfer. (4)

2.2 Classification of air conditioning systems

6
 Based on the fluid media used in the thermal distribution system, air
conditioning systems can be classified as (5)

2.2.1 All air systems

As the name implies, in an all air system air is used as the media that
transports energy from the conditioned space to the A/C plant. In these systems air
is processed in the A/C plant and this processed air is then conveyed to the
conditioned space through insulated ducts using blowers and fans. This air extracts
(or supplies in case of winter) the required amount of sensible and latent heat from
the conditioned space. The return air from the conditioned space is conveyed back
to the plant, where it again undergoes the required processing thus completing the
cycle. No additional processing of air is required in the conditioned space. All air
systems can be further classified into:

2.2.2 All water systems

In all water systems the fluid used in the thermal distribution system is water,
i.e., water transports energy between the conditioned space and the air conditioning
plant. When cooling is required in the conditioned space then cold water is
circulated between the conditioned space and the plant, while hot water is
circulated through the distribution system when heating is required. Since only
water is transported to the conditioned space, provision must be there for supplying
required amount of treated, outdoor air to the conditioned space for ventilation
purposes. Depending upon the number of pipes used, the all water systems can be
classified into a 2-pipe system or a 4-pipe system

2.2.3 Air-water systems

7
 In air-water systems both air and water are used for providing required
conditions in the conditioned space. The air and water are cooled or heated in a
central plant. The air supplied to the conditioned space from the central plant is
called as primary air, while the water supplied from the plant is called as secondary
water. The complete system consists of a central plant for cooling or heating of
water and air, ducting system with fans for conveying air, water pipelines and
pumps for conveying water and a room terminal. The room terminal may be in the
form of a fan coil unit, an induction unit or a radiation panel.

2.3 Unitary refrigerant based systems

Unitary refrigerant based systems consist of several separate air conditioning

units with individual refrigeration systems. These systems are factory assembled
and tested as per standard specifications, and are available in the form of package
units of varying capacity and type. Each package consists of refrigeration and/or
heating units with fans, filters, controls etc. Depending upon the requirement these
are available in the form of window air conditioners, split air conditioners, heat
pumps, ductable systems with air cooled or water cooled condensing units etc. The
capacities may range from fraction of TR to about 100 TR for cooling. Depending
upon the capacity, unitary refrigerant based systems are available as single units
which cater to a single conditioned space, or multiple units for several conditioned
spaces.

2.3.1 Window Type

Type of Window air conditioners are one of the most commonly used and
cheapest type of air conditioners. Window air conditioners are comprised of
components like the compressor, condenser, expansion valve or expansion coil,
and the evaporator or the cooling coil, all housed in a single box. There is also a

8
motor which has shafts on both sides. On one side of the shaft the blower is
connected, which sucks hot air from the room and blows it over the cooling coil,
thus cooling it and sending it to the room. On the other shaft the fan is connected,
which blows the air over Freon gas passing through the condenser.

One of the complaints that window air conditioners have had is that they
tend to make noise inside the room. But this problem has been greatly overcome
by the present day efficient and less noisy rotary compressors, which also consume
less electricity. Today a number of fancy and elegant looking models of window
air conditioners are available that enhance the beauty of your rooms

Figure (2 – 1) : Window Type

2.3.2 Split Type

Split air conditioners are used for small rooms and halls, usually in places
where window air conditioners cannot be installed. However, these days many

9
people prefer split air conditioner units even for places where window air
conditioners can be fitted.

The split air conditioner comprises of two parts: the outdoor unit and indoor
unit. The outdoor unit, fitted outside the room, houses components like the
compressor, condenser and expansion valve. The indoor unit comprises the
evaporator or cooling coil and the cooling fan. For this unit you don’t have to have
to make any slot in the wall of the room. A split air conditioner can be used to cool
one or two rooms.

Figure (2 – 2) : Split Type

2.3.3 Packaged Air Conditioner

Package air conditioner use when we want to cool more than two rooms or
large space at your home or office. There are two possible arrangements with
package unit.

10
 In the first one, all components namely the compressor, condenser,
expansion valve and evaporator are housed in single box. The cooled air is shown
by the high capacity blower and it flow through the duct laid through various rooms

Figure (2 – 3) : Package Type

In the second arrangement, the compressor and condenser are housed in one
casing. The compressed gas passes through individual units, comprised of the
expansion valve and cooling coil, located in various rooms.

2.3.4 Central Type

The central air conditioning plants or the systems are used when large
buildings, hotels, theaters, airports, shopping malls etc. are to be air conditioned
completely. The window and split air conditioners are used for single rooms or
small office spaces. If the whole building is to be cooled it is not economically
viable to put window or split air conditioner in each and every room. Further, these

11
small units cannot satisfactorily cool the large halls, auditoriums, receptions areas
etc.

The central air conditioning systems are highly sophisticated applications of

the air conditioning systems and many a times they tend to be complicated. It is
due to this reason that there are very few companies in the world that specialize in
these systems. In the modern era of computerization, a number of additional
electronic utilities have been added to the central conditioning systems

Figure (2 – 4) : Central Type

2.3.5 Evaporative Type

An evaporative cooler (also swamp cooler, desert cooler and wet air cooler)
is a device that cools air through the evaporation of water. Evaporative cooling

12
differs from typical air conditioning systems which use vapor-compression or
absorption refrigeration cycles. Evaporative cooling works by employing water's
large enthalpy of vaporization. The temperature of dry air can be dropped
significantly through the phase transition of liquid water to water vapor
(evaporation), which can cool air using much less energy than refrigeration. In
extremely dry climates, evaporative cooling of air has the added benefit of
conditioning the air with more moisture for the comfort of building occupants

Figure (1 – 5) : Evaporative Type

13
2.4 Thermal Load

Heating and cooling loads are the measure of energy needed to be added or
removed from a space by the HVAC system to provide the desired level of comfort
within a space. Right-sizing the HVAC system begins with an accurate
understanding of the heating and cooling loads on a space. Right-sizing is selecting
HVAC equipment and designing the air distribution system to meet the accurate
predicted heating and cooling loads of the house. The values determined by the
heating and cooling load calculation process will dictate the equipment selection
and duct design to deliver conditioned air to the rooms of the house, right-sizing
the HVAC system. The heating and cooling load calculation results will have a
direct impact on first construction costs along with the operating energy efficiency,
occupant comfort, indoor air quality, and building durability.
2.4.1 Thermal Load Calculation
Heating and cooling load calculations are carried out to estimate the required
capacity of heating and cooling systems, which can maintain the required
conditions in the conditioned space. To estimate the required cooling or heating
capacities, one has to have information regarding the design indoor and outdoor
conditions, specifications of the building, specifications of the conditioned space
(such as the occupancy, activity level, various appliances and equipment used etc.)
and any special requirements of the particular application.
2.4.2 Outdoor and Indoor Thermal Load

Indoor design conditions are governed either by thermal comfort conditions

or by special requirements for materials or processes housed in a space. In most
buildings, such as offices and residences, thermal comfort is the only requirement,
and small fluctuations in both temperature and humidity within the comfort zone

14
are not objectionable1. In other occupancies, however, more precise control of
temperature and humidity may be required; refer to the appropriate chapter in the
ASHRAE Handbook—HVAC Applications for recommendations. Standard 55
provides guidance on appropriate winter and summer indoor design conditions.
State or local energy codes and particular owner requirements may also affect the
establishment of criteria for indoor design conditions

2.5 External Loads

External loads are highly variable, both by season and by time of day. They
cause significant changes in the heating and cooling requirements over time, not
only in the perimeter building spaces, but for the total building heating/cooling
plant

2.5.1 Heat Transfer through Fenestration

Heat transfer through transparent surface such as a window, includes heat

transfer by conduction due to temperature difference across the window and heat
transfer due to solar radiation through the window. The heat transfer through the
window by convection is calculated using CLTD being equal to the temperature
difference across the window and A equal to the total area of the window.

2.5.2 Heat Transfer Due to Infiltration

Heat transfer due to infiltration consists of both sensible as well as latent

components.

The infiltration rate depends upon several factors such as the tightness of the
building that includes the walls, windows, doors etc and the prevailing wind speed

15
and direction. As mentioned before, the infiltration rate is obtained by using either
the air change method or the crack method.

Difference due to wind and stack effects as functions of prevailing wind

velocity and direction, inside and outside temperatures, building dimensions and
geometry etc. Representative values of infiltration rate.

2.5.3 Solar Heat Gain through Glazing

Solar radiation often represents a major cooling load and is highly variable
with time and orientation. Careful analysis of heat gains through windows,
skylights, and glazed doors is imperative.

Facade self-shadowing, adjacent building shadowing, and reflections from

the ground, water, snow, and parking areas must be considered in the loads
analysis. Spaces with extensively glazed areas must be analyzed for occupant
comfort relative to radiant conditions.

2.6 Internal Load

While external loads can be heat gains or heat losses, internal loads are
always heat gains.

2.6.1 People
The internal cooling load due to occupants consists of both sensible and
latent heat components. The rate at which the sensible and latent heat transfer take
place depends mainly on the population and activity level of the occupants. Since
a portion of the heat transferred by the occupants is in the form of radiation, a
Cooling Load Factor (CLF) should be used similar to that used for radiation heat
transfer through fenestration.

16
 Table (1) shows typical values of total heat gain from the occupants and also
the sensible heat gain fraction as a function of activity in an air conditioned space (6).

The value of Cooling Load Factor (CLF) for occupants depends on the hours
after the entry of the occupants into the conditioned space, the total hours spent in
the conditioned space and type of the building.

2.6.2 Lighting
Lighting adds sensible heat to the conditioned space. Since the heat
transferred from the lighting system consists of both radiation and convection, a
Cooling Load Factor is used to account for the time lag.
The primary source of heat from lighting comes from light-emitting elements, or
lamps, although significant additional heat may be generated from associated
appurtenances in the light fixtures that house such lamps, TABLE (3) showing
Lighting Power Densities Using the Building Area Method(7).

2.6.3 Appliances
In a cooling load estimate, heat gain from all appliances electrical, gas, or
steam should be taken into account. Because of the variety of appliances,
applications, schedules, use, and installations, estimates can be very subjective.
Often, the only information available about heat gain from equipment is that on its
nameplate

2.6.4 Ventilation Load

The outdoor air ventilation load does not have a direct impact on the
conditioned space (except when provided via open windows), but it does impose a
load on the HVAC&R equipment. Outdoor air is normally introduced through the
HVAC system and adds a load (sensible and latent) to the heating and cooling coils,
thus affecting their sizing and selection. The amount of ventilation depends upon
17
the occupancy and function of each space. Refer to Standards 62.1 and 62.2 for
recommended ventilation rates; see also the requirements of the local building,
mechanical, and energy codes Table (3) minimum ventilation rates in breathing
zone(8).

2.6.5 Infiltration Load

Infiltration is the uncontrolled flow of outdoor air into a building through
cracks and other unintentional openings and through the normal use of exterior
doors for entrance and egress. Infiltration is also known as air leakage into a
building. In commercial and institutional buildings, uncontrolled natural
ventilation, such as through operable windows, may not be desirable from the point
of view of energy conservation and comfort. In commercial and institutional
buildings with mechanical cooling and forced ventilation, an air- or water-side
economizer cycle may be preferable to operable windows for taking advantage of
cool outdoor conditions when interior cooling is required. Infiltration may be
significant in commercial and institutional buildings, especially in tall, leaky, or
under pressurized buildings

2.7 Thermal Comfort

Comfort describes a delicate balance of pleasant feeling in the body. A

comfortable atmosphere describes our surroundings when we are not aware of
discomfort. Providing a comfortable atmosphere for people is the job of the heating
and air-conditioning profession. Parameter that affect thermal coffort:-

1- Dry bulb temperature (DBT)

18
 is the temperature of the moist air as measured by a standard thermometer or
other temperature measuring instruments.

2- Wet bulb temperature (WBT)

The wet-bulb temperature is a value indicated on an ordinary

thermometer, the bulb of which has been wrapped round with a wick,
moistened in water.

3- Relative humidity (Φ)

Is defined as the ratio of the mole fraction of water vapour in moist air to
mole fraction of water vapour in saturated air at the same temperature and pressure

4- Humidity ratio (W)

The humidity ratio (or specific humidity) W is the mass of water associated
with each kilogram of dry air

5- Enthalpy

The enthalpy of moist air is the sum of the enthalpy of the dry air and the
enthalpy of the water vapor

19
CHAPTER THREE

METHODOLOGY

20
3.1 Methodology
The variables affecting cooling load calculating are numerous, often difficult
precisely, and always interrelated. Many cooling load components vary in
magnitude over a wide range during 24-h period. Since these cyclic changes in load
components are often not in phase with each other, analysis is required to establish
are resultant maximum cooling load for a building or zone.

3.2 Calculation of thermal load by Relation

The CLTD method is a one-step, hand calculation procedure, based on the
transfer function method (TFM), and uses table, It may be used to approximate the
cooling load corresponding to the first three modes of heat gain (conductive heat
gain through surfaces such as windows, walls, and roofs; solar heat gain through
fenestrations; and internal heat gain from lights, people, and equipment) and the
cooling load from infiltration and ventilation(9).

3.3 External Cooling Load

3.3.1 Roofs, walls, and conduction through glass
𝑞 = 𝑈𝐴(𝐶𝐿𝑇𝐷) (3-1)
𝑈 ≡ Heat transfer coefficient for roof or wall

𝐴 ≡ Area of roof, wall, or glass

𝐶𝐿𝑇𝐷 ≡ Cooling load temperature difference, roof, wall, or glass

3.3.2 Solar load through glass
𝑞 = 𝐴(𝑆𝐶)(𝑆𝐶𝐿) (3-2)
𝑆𝐶 ≡ Shading coefficient
𝑆𝐶𝐿 ≡ Solar cooling load factor with no interior shade or with shade
3.3.3 Cooling load from partitions, ceilings, floors

21
 𝑞 = 𝑈𝐴(𝑡0 − 𝑡𝑟𝑐 ) (3-3)
𝑈 ≡ Design heat transfer coefficient for partition, ceiling, or floor

𝐴 ≡ Area of partition, ceiling, or floor

𝑡0 ≡ Temperature in adjacent space

𝑡𝑟𝑐 ≡ Inside design temperature (constant) in conditioned space

3.4 Internal Cooling Load

3.4.1 People

𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 𝑁(𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 ℎ𝑒𝑎𝑡 𝑔𝑎𝑖𝑛)𝐶𝐿𝐹 (3-4)

𝑞𝑙𝑎𝑡𝑒𝑛𝑡 = 𝑁(𝐿𝑎𝑡𝑒𝑛𝑡 ℎ𝑒𝑎𝑡 𝑔𝑎𝑖𝑛) (3-5)

𝑁 ≡ Number of people in space

𝐶𝐿𝐹 ≡ Cooling load factor, by hour of occupancy

CLF 1.0 with high density or 24-h occupancy and/or if cooling off at

night or during weekends.

3.4.2 Lights

𝑞𝑒𝑙 = 𝑊𝐹𝑢𝑙 𝐹𝑠𝑎 (𝐶𝐿𝐹) (3-6)

𝑊 ≡ Watts input from electrical plans or lighting fixture data

𝐹𝑢𝑙 ≡ Lighting use factor, as appropriate

𝐹𝑠𝑎 ≡ Special allowance factor, as appropriate

𝐶𝐿𝐹 ≡ Cooling load factor, by hour of occupancy

22
CLF = 1.0 with 24-h light usage and/or if cooling off at night

or during weekends

3.4.3 Power

𝑞𝑝 = 𝑃𝐸𝐹 𝐶𝐿𝐹 (3-7)

𝑃 ≡ Horsepower rating from electrical plans or manufacturer’s data

𝐸𝐹 ≡ Efficiency factors and arrangements to suit circumstance

3.4.4 Appliances

𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 𝑞𝑖𝑛𝑝𝑢𝑡 𝐹𝑈 𝐹𝑅 (𝐶𝐿𝐹) (3-8)

OR

𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 𝑞𝑖𝑛𝑝𝑢𝑡 𝐹𝐿 (𝐶𝐿𝐹) (3-9)

𝑞𝑖𝑛𝑝𝑢𝑡 ≡ Rated energy input from appliances

𝐹𝑈 ≡ Usage factors,

𝐹𝑅 ≡ Radiation factors

𝐹𝐿 ≡ Load factor

3.4.5 Ventilation and Infiltration Air

𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 1.23𝑄(𝑡𝑜 − 𝑡𝑖 ) (3-10)

𝑞𝑙𝑎𝑡𝑒𝑛𝑡 = 3010𝑄(𝑊𝑜 − 𝑊𝑖 ) (3-11)

𝑞𝑡𝑜𝑡𝑎𝑙 = 1.20𝑄(ℎ𝑜 − ℎ𝑖 ) (3-12)

23
𝑄 ≡ Ventilation from ASHRAE Standard 62

𝑡𝑜 &𝑡𝑖 ≡ Outside, inside air temperature, °C

𝑊𝑜 &𝑊𝑖 ≡ Outside, inside air humidity ratio, kg (water)/kg (dry air)

ℎ𝑜 &ℎ𝑖 ≡ Outside, inside air enthalpy, kJ/kg (dry air)

3.5 Calculation by software Hourly Analysis Program

(HAP)
Carrier’s Hourly Analysis Program (HAP) is a computer tool which assists
engineers in designing HVAC systems for commercial buildings. HAP is two tools
in one. First it is a tool for estimating loads and designing systems. Second, it is a
tool for simulating building energy use and calculating energy costs. In this
capacity it is useful for LEED®, schematic design and detailed design energy cost
evaluations. HAP uses the ASHRAE transfer function method for load calculations
and detailed 8,760 hour-by-hour simulation techniques for the energy analysis.

This program is released as two separate, but similar products. The “HAP
System Design Load” program provides system design and load estimating
features. The full “HAP” program provides the same system design capabilities
plus energy analysis features. This Quick Reference Guide deals with both
programs

HAP System Design Features. HAP estimates design cooling and

heating loads for commercial buildings in order to determine required sizes for
HVAC system components. Ultimately, the program provides information needed
for selecting and specifying equipment. Specifically, the program performs the
following tasks(10):

24
 Calculates design cooling and heating loads for spaces, zones, and coils in the
HVAC system.
 Determines required airflow rates for spaces, zones and the system.
 Sizes cooling and heating coils.
 Sizes air circulation fans.

 Sizes chillers and boilers

3.5.1 Data input in Hourly analysis software

HAP’s main program window which appears when you start the program.
Much of the work you will perform entering data and generating reports is done
using features of the main program window The HAP main program window
consists of six components used to operate the program.

Title Bare Menu Bare Tool Bare

25
 Tree View Pane List View Plane Pane Status Bar

Figure (3 – 1) : User Interface

1- Title Bare

lists the program name and the name of the current project. If you are running
HAP System Design Load or are running the full HAP but in System Design mode,
the program name will be "HAP System Design Load". If you are running the full
HAP program with energy analysis features turned on, the program name will
simply be "HAP".

2- Menu Bar
lies immediately below the title bar. The menu bar contains seven pull-down
menus used to perform common program tasks.
3- Tool Bar

26
 lies immediately below the menu bar and contains a series of buttons used
to perform common program tasks. Each button contains an icon which represents
the task it performs. These tasks duplicate many of the options found on the pull-
down menus.
4- Tree View Pane
It’s the left-hand panel in the center of the main program window. It contains
a tree image of the major categories of data used by HAP. The tree view acts as the
“control panel” when working with program data.
5- List View Plane
It’s the right-hand panel in the center of the main program window. It
contains a list of data items in alphabetical order for one of the categories of data
in your project. The list view acts as the second part of the “control panel” when
working with program data.
6- Status Bar
It’s the final component of the main program window and appears at the
bottom of the window. The current date and time appear at the right-hand end of
the status bar. Pertinent messages appear at the left-hand end of the status bar

3.6 Working with HAP Input Windows

While using HAP you will need to create and manage project data All the
data you enter and calculate in HAP is stored together within a “project”.
Project is simply a container for your data. However, a project can hold data
for other programs as well as HAP.

3.6.1 Weather properties window:

This window is used to enter the weather conditions in the area which
include the latitude, longitude, elevation, summer design bulb temperature and
summer design wet bulb temperature.

27
 Figure (3– 2) : Weather properties

3.6.2 Space Properties window

General windows in space properties contains the name of the space, floor
area, average ceiling height and ventilation requirements, and also contain of :

28
 Figure (3 – 3) : Space properties-general

i. Internal load window:

It consists of the type of light and the thermal load for lighting,
equipment’s, sensible and latent load of people of people and electric equipment
and other devices load.

29
 Figure (3 – 4) : Space properties-internal load

ii. Wall, Window, doors window:

In this window we define the walls that transfer heat to the system it is
directions and number of doors and windows in each of these walls

30
 Figure (3 –5) : Space properties-wall, window and door

iii. Roof-Skylight window:

It contains the roof thickness and type of the roof materials and the roof area

31
 Figure (3 – 6) : Space properties- Roof Data

iv. Infiltration window

It contains the infiltration rate of cooling and heating load

32
 Figure (3 – 7) : Space Properties- Infiltration

v. Floor

It contains floor type, area and heat transfer coefficient for floor

33
 Figure (3 – 8) : Space Properties- Floor

3.6.3 Air System Properties window

General window in air system It contains the name, equipment type, air
system type and the number of zones, air system properties also contain of

34
 Figure (3 – 9) : Air system Properties- general data

1- System component:
It contains the value of relative humidity and leave other variables to it is default
values

35
 Figure (3– 10) : Air system Properties System component data

2- Zone component:
In thermostats menu to schedule the system operation time

36
 Figure (3 – 11) : Air system Properties Zone component

3- Sizing Data

It contains the information of internal require design data

37
 Figure (3 – 12) : Air system Properties Sizing Data

3.6.4 System design Reports:

System results detailed report of the sizing of individual components and
psychometrics.

38
 Figure (3 – 13) : System design report

3.7 Duct Design

The purpose of air conditioning ductwork is to deliver air from the fan to
the diffusers which distribute the air to the room. Air Moves through the Ductwork
in Response to a Pressure Difference created by the Fan the necessary pressure
difference will be a function of the way the ductwork is laid out and sized. The
objective of duct design is to size the duct so as to minimize the pressure drop
through the duct, while keeping the size (and cost) of the ductwork to a minimum.
Proper duct design requires knowledge of the factors that affect pressure drop and
velocity in the duct. A duct system is often called ductwork. Planning (‘laying
out’), sizing, optimizing, detailing, and finding the pressure losses through a duct
system is called duct design.

39
3.7.1 Duct system components:

 Vibration isolators
 Take-offs
 Stacks, boots, and heads
 Dampers
 Terminal units
 Air terminals
3.7.2 Duct Design Criteria

Several factors must be considered when designing a duct system. Generally,

in order of importance they are as follows[11]:

 Space availability
 Installation cost
 Air friction loss
 Noise level
 Duct heat transfer and air flow leakage
3.7.3 Types of ducts:
1- Round duct.
2- Oval duct.
3- Rectangular duct.
3.7.4 Static pressure:

It is the pressure required to deliver quantity of air (cfm) at required velocity

(fpm) by overcoming the resistance offered to the flow of air in the air distribution
system.

40
3.7.5 Duct Aspect Ratio

Itis the ratio between long side and the short one (as it increases the air
friction in the duct increases).

Maximum AR=3

We will use the following standard conversion:

1TR=400 CFM

And from experiences velocity inside the ducts should equal to V=700 fpm.
Also we will use MCQUAY duct seizer to calculate ducts sizes.

Figure (3-14) MCQUAY duct sizer layout

41
3.8 Conditioning Space
Sport hall for multi [(50 ∗ 30)𝑚 dimension] sport ( football , basketball ,
volleyball….), 1000 occupancy

Figure (3-15) : conditioning spce

3.8.1 Construction Data

Wall : 101.6 common brick with 50.8 insulation and 101.6 face brick

Roof : steel sheet with 25.4 insulation and suspended ceiling

42
Floor : epoxy floor finishing with 10 cm plan concrete and 150 cm sand

Door : 2*2 Wooden Door

Light Density : 12 watt per meter square

43
CHAPTER FOUR
CALCULATIONS

44
4.1 Introduction

Functions at arenas and stadiums may be quite varied, so the air-

conditioning loads will vary. Arenas and stadiums are not only used for sporting
events such as basketball, ice hockey, boxing, and track meets but may also
house circuses; rodeos; convocations; social affairs; meetings; rock concerts;
car, cycle, and truck events; and special exhibitions such as home, industrial,
animal, or sports shows. For multipurpose operations, the designer must provide
highly flexible systems. High-volume ventilation may be satisfactory in many
instances, depending on load characteristics and outside air conditions(12).

4.2 Calculate cooling load By Relation

The CLTD method is a one-step simplification of the transfer

function method. The space cooling load is calculated directly by
multiplying the heat gain with CLTD, SCL, or CLF instead of first finding
the space heat gains and then converting into space cooling loads through
the room transfer function(2).

4.2.1 External Cooling Load

External cooling load contain every load affected by outside

condition which is:

1- Heat Transmission Through Wall

Wall construction by layer form inside to outside 101.6mm common

brick, 50.8 insulation and 101.6mm face brick. Wall construction group B

𝑞 = 𝑈𝐴(𝐶𝐿𝑇𝐷)

1 1 ∆𝑥1 ∆𝑥2 ∆𝑥3 1

= + + + +
𝑈 ℎ𝑖 𝑘1 𝑘2 𝑘3 ℎ𝑜
72
ℎ𝑖 , ℎ𝑜 value from Table (2) for vertical position surface , and 𝑘 value from Table
(5)

1 1 0.1016 0.0508 0.1016 1

= + + + + = 1.56
𝑈 8.29 0.727 0.043 1.333 22.7

𝑈 = 0.641𝑊/(𝑚2 . 𝐾)

𝐶𝐿𝑇𝐷𝑐𝑜𝑟𝑟 = (𝐶𝐿𝑇𝐷 + 𝐿𝑀) ∗ 𝐾 + (25.5 − 𝑇𝑖 ) + (𝑇𝑜 − 29.4)

K=0.83, 𝐶𝐿𝑇𝐷 from Table (6) and 𝐿𝑀 from Table (7)

𝐶𝐿𝑇𝐷𝑐𝑜𝑟𝑟 𝑁 = (5 + 0.5) ∗ 0.83 + (25.5 − 23) + (48 − 29.4) = 25.665

𝐶𝐿𝑇𝐷𝑐𝑜𝑟𝑟 𝐸 = (13 + 0. ) ∗ 0.83 + (25.5 − 23) + (48 − 29.4) = 31.89

𝐶𝐿𝑇𝐷𝑐𝑜𝑟𝑟 𝑆 = (8 − 1.6) ∗ 0.83 + (25.5 − 23) + (48 − 29.4) = 26.412

𝐶𝐿𝑇𝐷𝑐𝑜𝑟𝑟 𝑊 = (8 + 0) ∗ 0.83 + (25.5 − 23) + (48 − 29.4) = 27.740

𝑞𝑁 = 0.641 ∗ 413 ∗ 25.665 = 6.794𝐾𝑊

𝑞𝐸 = 0.641 ∗ 255 ∗ 31.89 = 5.212𝐾𝑊

𝑞𝑆 = 0.641 ∗ 413 ∗ 26.412 = 6.992𝐾𝑊

𝑞𝑊 = 6.41 ∗ 255 ∗ 27.740 = 4.534𝐾𝑊

𝑞𝑇 = 𝑞𝑁 + 𝑞𝐸 + 𝑞𝑆 + 𝑞𝑊

𝑞𝑇 = 7.323 + 5.593 + 7.522 + 4.861 = 23.532𝐾𝑊

2- Heat Transmission Through Roof And Floor

𝑞 = 𝑈𝐴(𝐶𝐿𝑇𝐷)

1 1 ∆𝑥1 ∆𝑥2 ∆𝑥3 1

= + + + +
𝑈 ℎ𝑖 𝑘1 𝑘2 𝑘3 ℎ𝑜

72
 ℎ𝑖 , ℎ𝑜 ,value from Table (2) for horizontal position surface, and 𝑘 value
from Table (5), Table (4) and 𝐶𝐿𝑇𝐷𝑐𝑜𝑟𝑟 from Table(7)

1 1 0.0508 0.0244 1
= + + + = 1.694
𝑈 5.17 0.035 5.08 22.7

𝑈 = 0.590𝑊/(𝑚2 . 𝐾)

𝐶𝐿𝑇𝐷𝑐𝑜𝑟𝑟 = [(𝐶𝐿𝑇𝐷 + 𝐿𝑀) ∗ 𝐾 + (25.5 − 𝑇𝑖 ) + (𝑇𝑜 − 29.4)] ∗ 𝑓

K=1 and 𝑓 = 0.75 [1], 𝐶𝐿𝑇𝐷 from Table () and 𝐿𝑀 from Table ()

𝐶𝐿𝑇𝐷𝑐𝑜𝑟𝑟 = [(43 + 0.5) ∗ 1 + (25.5 − 23) + (48 − 29.4)] ∗ 0.75 = 48.45

𝑞𝑅𝑜𝑜𝑓 = 0.590 ∗ 1500 ∗ 49.95 = 44.206𝐾𝑊

3- Floors

For floors directly in contact with the ground, or over an underground

basement that is neither ventilated nor conditioned, heat transfer may be
neglected for cooling load estimates

4- Heat Transmission Through Door

𝑈𝐷𝑜𝑜𝑟 = 1.703, Number of Door six Doors and gross area 4𝑚2 foe each Doors
therefore the total gross area is 24𝑚2

𝑞 = 𝑈𝐴(𝐶𝐿𝑇𝐷)

𝑞 = 1.703 ∗ 24 ∗ (48 − 23) = 1.022𝐾𝑊

4.2.2 Internal Cooling Load

Internal cooling load its contain every load optioned from internal
component

1- People
72
sensible heat gain and latent heat gain for people its obtained Form table (1)

𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 𝑁(𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 ℎ𝑒𝑎𝑡 𝑔𝑎𝑖𝑛)𝐶𝐿𝐹

𝑞𝑙𝑎𝑡𝑒𝑛𝑡 = 𝑁(𝐿𝑎𝑡𝑒𝑛𝑡 ℎ𝑒𝑎𝑡 𝑔𝑎𝑖𝑛)

𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝑝𝑙𝑎𝑦𝑒𝑟 = 25 ∗ 210 = 5.25𝐾𝑊

𝑞𝑙𝑎𝑡𝑒𝑛𝑡 𝑝𝑙𝑎𝑦𝑒𝑟 = 25 ∗ 325 = 8.125𝐾𝑊

𝑞𝑡𝑜𝑡𝑎𝑙 𝑝𝑙𝑎𝑦𝑒𝑟 = 𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 + 𝑞𝑙𝑎𝑡𝑒𝑛𝑡 = 5.25 + 8.125 = 13.375𝐾𝑊

𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝑓𝑎𝑛𝑠 = 1000 ∗ 65 = 65𝐾𝑊

𝑞𝑙𝑎𝑡𝑒𝑛𝑡 𝑓𝑎𝑛𝑠 = 1000 ∗ 30 = 30𝐾𝑊

𝑞𝑡𝑜𝑡𝑎𝑙 𝑓𝑎𝑛𝑠 = 𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 + 𝑞𝑙𝑎𝑡𝑒𝑛𝑡 = 65 + 30 = 95𝐾𝑊

𝑞𝑡𝑜𝑡𝑎𝑙 = 𝑞𝑝𝑙𝑎𝑦𝑒𝑟 + 𝑞𝑓𝑎𝑛𝑠 = 13.375 + 95 = 108.375𝐾𝑊

2- Light

From Table (3) Lighting Power Densities for sport hall is 12 𝑊/𝑚2 and since
the building area is 1500 𝑚2 therefore the total watts is given by

𝑊
12 ∗ 1500 𝑚2 = 18000𝑊
𝑚2

𝑞𝑒𝑙 = 𝑊𝐹𝑢𝑙 𝐹𝑠𝑎 (𝐶𝐿𝐹)

𝑞𝑒𝑙 = 18000 ∗ 1 ∗ 1.20 ∗ 1 = 21.600𝐾𝑊

3- Ventilation and Infiltration Air

From Table (8) the required quantity of air for ventilation is 3.8 liter per
second per person, since the occupancy of the hall is 1000 person and the floor
area is 1500 m2 with ceiling height 8.5 meter therefor

𝑄 = 3.8 ∗ 1000 = 3800

72
Air space volume = 8.5 ∗ 1500 = 12750𝑚3 corresponding to
(3800 3600 s/h 0.001 m3/L)/12750 = 1.073 air changes per hour
4- Ventilation

𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 1.23𝑄(𝑡𝑜 − 𝑡𝑖 )

𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 1.23 ∗ 3800 ∗ (48 − 23) = 116.850𝐾𝑊

𝑞𝑙𝑎𝑡𝑒𝑛𝑡 = 3010𝑄(𝑤𝑜 − 𝑤𝑖 )

𝑤𝑜 & 𝑤𝑖 from Psychrometric Chart

𝑞𝑙𝑎𝑡𝑒𝑛𝑡 = 3010 ∗ 3800 ∗ (0.0138 − 0.009) = 54.902𝐾𝑊

𝑞𝑡𝑜𝑡𝑎𝑙 = 𝑞𝑙𝑎𝑡𝑒𝑛𝑡 + 𝑞𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 54.902 + 116.850 = 171.752𝐾𝑊

5- Infiltration

Window infiltration is zero, since there is no windows. Infiltration

through wall surfaces is also neglected as insignificant, surfaces. Calculation of
door infiltration however, requires some judgement. The pressure of 1.073 air
changes/h in the form of positive ventilation could be sufficient to prevent door
infiltration, depending on the degree of simultaneous door openings and the
wind direction and velocity.

𝑄𝑇 = 𝑞𝑊𝑎𝑙𝑙 + 𝑞𝑅𝑜𝑜𝑓 + 𝑞𝐷𝑜𝑜𝑟 + 𝑞𝑃𝑒𝑜𝑝𝑙𝑒 + 𝑞𝐿𝑖𝑔ℎ𝑡 + 𝑞𝑉𝑒𝑛𝑡𝑜𝑙𝑎𝑡𝑖𝑜𝑛

𝑄𝑇 = 23.532 + 44.206 + 1.022 + 108.375 + 21.600 + 171.752

= 370.487𝐾𝑤

By using 1.1 as safety factor then total cooling load will be:-

𝑄𝑇 = 370.487 ∗ 1.1 = 407.536𝐾𝑤

407.536
𝑄𝑇 = = 116𝑇𝑅
3.5
72
4.3 Calculation by software Hourly Analysis Program (HAP)
Program load calculation result report

Table (4 – 1) : load summary for zone 1

Table (4 – 2) : load summary for zone 2

72
4.4 Duct Design
Calculation have been made at constant head loss equal 0.393 pa/m

Table (4 – 3) : Main Duct

Duct Size
Flow l/s Velocity m/s
No Width mm Depth mm

1 1300 1500 15200 8

2 1050 1500 11400 7.8

3 775 1500 7600 7

4 475 1500 3800 6

72
 Table (4 – 4) : Branch Duct

Duct Size
Flow l/s Velocity m/s
No Width mm Depth mm

1 1450 500 3800 6

2 1200 500 3040 5.7

3 950 500 2280 5.3

4 675 500 1520 4.7

5 400 500 760 4

Table (4 – 5) : Diffuser Supply Duct

Duct Size
Flow l/s Velocity m/s
No Width mm Depth mm

1 300 400 380 3.4

2 300 400 380 3.4

3 300 400 380 3.4

4 300 400 380 3.4

5 300 400 380 3.4

6 300 400 380 3.4

7 300 400 380 3.4

8 300 400 380 3.4

9 300 400 380 3.4

72
10 300 400 380 3.4

72
 CHAPTER
FIVE
EQUIPMENT SELECTION

72
5.1 Introduction

Selection of equipment's is an important factor in design process, where

a good Selection of equipment's makes the designer achieves the objective of
project. Selection of a suitable air conditioning system depends on:

1. Capacity, performance and spatial requirements

2. Initial and running costs

3. Required system reliability and flexibility

4. Maintainability

5. Architectural constraints

5.2 Packaged Units

A packaged unit (PU) is a self-contained air conditioner. It conditions the

air and provides it with motive force and is equipped with its own heating and
cooling sources. The packaged unit is the primary equipment in a packaged air-
conditioning system and is always equipped with a DX coil for cooling, unlike
an AHU. R-22, R-134a, and others are used as refrigerants in packaged units.

The portion that handles air in a packaged unit is called an air handler to
distinguish it from an AHU. Like an AHU, an indoor air handler has an indoor
fan, a DX coil (indoor coil), filters, dampers, and controls. Packaged units can
be classified according to their place of installation: rooftop, indoor, and split
packaged units.

5.2.1 Unit Selection

The estimated total cooling load for the Sport Hall is found to be 103
T.O.R (by using the software) and 115 T.O.R (by using manual calculation) so

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we are going to select 50Z030 CARRIER fore rooftop unit package with 30
T.O.R and one units as stand by units [13]

Rooftop heating and cooling units are made by many manufacturers.

Some units are delivered with a full refrigerant charge. This means there are no
refrigerant lines to connect. This cuts labor costs and installation time. Since the
unit is on the rooftop, no inside room has to be allocated for the heating and
cooling equipment.

5.3 Diffusers Selection

A diffuser is the mechanical device that is designed to control the

characteristics of a fluid at the entrance to a thermodynamic open system. Flow
through nozzles and diffusers may or may not be assumed to be adiabatic.
Frictional effects may sometimes be important, but usually they are neglected

Since the requirement flow for one diffuser is 805𝑐𝑓𝑚 so we selected a

250, 250-AA diffuser from Titus diffuser Catalog with 805𝑐𝑓𝑚 4-way
Discharge Pattern and 4.3 & 6.4 𝑚 throw[14]

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 Figure (5 – 1): 250, 250-AA Titus diffuser

5.4 Conclusion

The objectives of this research have been achieved as follows :-

 The total cooling load for the sport hall has been calculated using HVAC
HAP software and it found to be 103 ton of refrigeration (T.O.R) and using
manual hand calculation and it found to be 116 ton of refrigeration (T.O.R)
and equipment have been selected according to the maximum cooling load.
 Duct distribution system have been made using MCQUAY duct sizer design
tool and constant head loss (𝑝𝑎/𝑚) method according to diffuser flow.
 Diffuser selection have been made according to diffuser flow which is
calculated by divided the total flow rate to the number of diffuser.
 Suitable equipment has been chosen According to the results above.

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 Recommendations
 Using HAP software or any other software to estimate cooling
load instead of manual method because its more accurate and take
less effort and time
 It’s very important to control and monitor building’s mechanical and
electrical equipment such as for ventilation, lighting, power systems, fire
systems, and security systems. Using buildings management systems (BMS)
or Buildings Automation Systems (BAS).

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5.5 References
1) ASHRAE standard 55.
2) Air Conditioning and Refrigeration Course Material – Promotion Exams.
3) Air Conditioning Engineering, Fifth Edition, W.P. Jones MSc, CEng,
FlnstE, FCIBSE, MASHRAE
4) Fundamentals of HVAC Systems, Robert McDowall, P.Eng., Engineering
Change Inc.
5) Refrigeration & air conditioning 40 lessons on refrigeration and air
conditioning EE IIT, Kharagpur, India 2008.
6) 1997 ASHRAE Fundamentals Handbook (SI).
7) ASHRAE/IESNA STANDARD 90.1-1999, Energy Standard for Buildings
Except Low-Rise Residential Buildings.
8) ANSIIASHRAE Standard 62.1 .2007, Ventilation for Acceptable Indoor
Air Quality.
9) 2005 ASHRAE Fundamentals Handbook (SI).
10) HAP Quick Reference Guide, 10th Edition…..( HAP v5.00) …..4/2016
11) 2009 ASHRAE Handbook—Fundamentals (SI).
12) 2003 ASHRAE Applications Handbook (SI).
13) Carrier Commercial Products Guide 2002.
14) Titus Diffuser Catalogue.

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APPENDIX

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 Appendix (A)
Table 1 Rates of Heat Gain from Occupants of Conditioned Spaces

Total Heat, W % Sensible Heat that is

b
Latent Sensible
Radiant

Degree of Activity Male M/Fa W W Low V High V

Seated at theater Theater, matinee 115 95 65 30

Seated at theater, night Theater, night 115 105 70 35 60 27

Seated, very light work Offices, hotels, apartments 130 115 70 45

Moderately active office work Offices, hotels, apartments 140 130 75 55

Standing, light work; walking Department store; retail store 160 130 75 55 58 38
Walking, standing Drug store, bank 160 145 75 70

Sedentary work Restaurantc 145 160 80 80

Light bench work Factory 235 220 80 140

Moderate dancing Dance hall 265 250 90 160 49 35

Walking 4.8 km/h; light machine work Factory 295 295 110 185

Bowlingd Bowling alley 440 425 170 255

Heavy work Factory 440 425 170 255 54 19

Heavy machine work; lifting Factory 470 470 185 285

Athletics Gymnasium 585 525 210 325

Heat, Heat, Adjusted, Adult

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 Appendix (B)
Table 2 Surface Conductances and Resistances for Air

Position of Direction Non- Reflective

Surface of Heat reflective ε = 0.05ε = 0.20
Flow ε = 0.90
hi R hi R hi R
STILL AIR Upward 9.26 0.11 5.17 0.19 4.32 0.23
Horizontal
Sloping— Upward 9.09 0.11 5.0 0.20 4.15 0.24
45° 0
Vertical Horizontal 8.29 0.12 4.20 0.24 3.35 0.30
Sloping— Downward 7.50 0.13 3.4 0.29 2.56 0.39
45° 1
Horizontal Downward 6.13 0.16 2.10 0.48 1.25 0.80
MOVING AIR (Any ho R
position)
34.0 0.030 — — — —
Any Wind (for winter)
6.7 m/s (24 km/h) 22.7 0.044 — — — —
Wind (for summer)
Any
3.4 m/s (12 km/h)

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 Appendix (C)
Table 3 Lighting Power Densities Using the Building Area Method

(W/m2) Lighting
Building Area Type Power Density

Automotive Facility 10
Convention Center 13
Court House 13
Dining: Bar Lounge/Leisure 14
Dining: Cafeteria/Fast Food 15
Dining: Family 17
Dormitory 11
Exercise Center 11
Gymnasium 12
Healthcare-Clinic 11
Hospital 13
Hotel 11
Library 14
Manufacturing Facility 14
Motel 11
Motion Picture Theater 13
Multi-Family 8
Museum 12
Office 11
Parking Garage 3
Penitentiary 11
Performing Arts Theater 17
Police/Fire Station 11
Post Office 12
Religious Building 14
Retail 16
School/University 13
Sports Arena 12
Town Hall 12
Transportation 11
Warehouse 9
Workshop 15

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 Appendix (D)
Table 4 Cooling Load Temperature Difference for Calculate Cooling
Load From Flat Roof

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 Appendix (E)
Table 5 Wall Construction Grop

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 Appendix (F)
Table 6 Cooling Load Temperature Difference for Calculate Cooling
Load from Sun Light Wall

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 Appendix (G)
Table 7 CLTD Correction for Latitude and Month Applied to Wall and
Roof

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 Appendix (H)
Table 8 Minimum Ventilation Rates in Breathing Zone

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 Appendix (I)
Psychrometric Chart

𝑀 ≡ 𝑀𝑖𝑥𝑖𝑛𝑔 𝑝𝑜𝑖𝑛𝑡

𝑅 ≡ 𝐼𝑛𝑑𝑜𝑟 𝑝𝑜𝑖𝑛𝑡

𝑆 ≡ 𝑆𝑢𝑝𝑝𝑙𝑦 𝑝𝑜𝑖𝑛𝑡

𝐼 ≡ 𝑂𝑢𝑡𝑑𝑜𝑜𝑟 𝑝𝑜𝑖𝑛𝑡

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