Handbook of air conditioning and refrigeration / Shan K

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calculated as Edif � (1 � wrsw)0.06Emax Therefore, the total evaporative heat loss from the skin surface is E sk � E rsw � E dif � w rswE max � (1 � w rsw)0.06E max � (0.06 � 0.94w rsw)E max � w skE max In Eq. (4.20), w sk is called the total skin wetness; it is dimensionless, and it can be calculated as 4.5 MEAN RADIANT TEMPERATURE AND EFFECTIVE TEMPERATURE Mean Radiant Temperature (4.19) (4.20) (4.21) Mean radiant temperature T Rad is defined as the temperature of a uniform black enclosure in which an occupant would have the same amount of radiative heat exchange as in an actual indoor environment. Mean radiant temperature T Rad, °R(K), can be calculated by the expression T 4 Rad � T 4 R1 F 0 – 1 � T 4 R2 F 0 –2 ��T 4 RnF 0 – n where T R1, T R2, ��, T Rn � absolute temperature of surrounding surfaces of indoor environment, °R(K) F 0 – 1 � shape factor denoting fraction of total radiant energy leaving surface of occupant’s clothing 0 and arriving on the surface 1 F 0 – 2 � fraction of total radiant energy leaving surface 0 and arriving on surface 2, etc. (4.22) Shape factors F 0 – n depend on the position and orientation of the occupant as well as the dimensions of the enclosure. One can use Figs. 4.2 and 4.3 to estimate the mean value of the shape factor between a seated person and rectangular surfaces. The sum of the shape factors of all the surfaces with respect to the seated occupant in an enclosure is unity. The temperature measured by a globe thermometer, called the globe temperature, is often used to estimate the mean radiant temperature. The globe thermometer consists of a copper hollow sphere of 6-in. (152-mm) diameter that is coated with black paint on the outer surface. A precision thermometer or thermocouple is inserted inside the globe with the sensing bulb or the thermojunction located at the center of the sphere. Because the net radiant heat received at the globe surface is balanced by the convective heat transfer from the globe surface in reaching a thermal equilibrium, according to Bedford and Warmer (1935), such a relationship gives T 4 Rad � T 4 Rg � 0.247 � 10 9 v 0.5 (T Rg � T Ra) (4.22a) where T Rad � absolute mean radiant temperature, °R (K) T Rg � absolute globe temperature, °R (K) v � ambient air velocity, fpm (m/s) T Ra � absolute air temperature, °R (K) INDOOR AND OUTDOOR DESIGN CONDITIONS 4.9 w sk � E sk E max After T Rg, v, and T Ra are measured, the mean radiant temperature T Rad can be calculated from Eq. (4.22). The mean radiant temperature indicates the effect, due to the radiant energy from the
4.10 CHAPTER FOUR FIGURE 4.2 Mean value of shape factor between a sedentary person and a horizontal plane. (Source: P. O. Fanger, Thermal Comfort Analysis and Applications in Environmental Engineering, 1972. Reprinted with permission.)
Page 1 and 2:
HANDBOOK OF AIR CONDITIONING AND RE
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This book is dedicated to my dear w
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PREFACE TO SECOND EDITION Air condi
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ACKNOWLEDGMENTS PREFACE TO THE FIRS
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I.2 INDEX Air conditioning systems,
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I.4 INDEX Bernoulli equation, 17.2
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I.6 INDEX Chilled-water storage sys
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I.8 INDEX Constant-volume single-zo
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I.10 INDEX Discharge air temperatur
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I.12 INDEX Evaporative cooling syst
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I.14 INDEX Fault detection and diag
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I.16 INDEX Ice storage systems: com
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I.18 INDEX Packaged systems, fan-po
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I.20 INDEX Refrigerant flow control
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I.22 INDEX Silencers (Cont.) dissip
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I.24 INDEX Space pressurization or
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I.26 INDEX VAV systems, VAV cooling
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Preface to Second Edition xi Prefac
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Chapter 27. Air Conditioning System
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1.2 CHAPTER ONE limits for the comf
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1.4 CHAPTER ONE Individual Room Air
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1.6 CHAPTER ONE Unitary Packaged Ai
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1.8 CHAPTER ONE Water System Centra
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1.10 CHAPTER ONE fire protection sy
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1.12 CHAPTER ONE Unitary Packaged S
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1.14 CHAPTER ONE in the residential
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1.16 CHAPTER ONE shipments were 750
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1.18 CHAPTER ONE properly equipped
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1.20 CHAPTER ONE Engineer’s Quali
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1.22 CHAPTER ONE Drawings Specifica
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1.24 CHAPTER ONE criteria or system
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1.26 CHAPTER ONE ● Equipment sele
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1.28 CHAPTER ONE Rowland, F. S., Th
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2.2 CHAPTER TWO The amount of water
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2.4 CHAPTER TWO Dalton’s law is b
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2.6 CHAPTER TWO Temperature Measure
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2.8 CHAPTER TWO Degree of Saturatio
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2.10 CHAPTER TWO Density where pat
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2.12 CHAPTER TWO Thermodynamic Wet-
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2.14 CHAPTER TWO The term T � T
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2.16 CHAPTER TWO 2.8 HUMIDITY MEASU
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2.18 CHAPTER TWO FIGURE 2.7 Ion-exc
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2.20 CHAPTER TWO The last digit for
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2.22 CHAPTER TWO Cooling and Dehumi
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2.24 CHAPTER TWO p ws � From Eq.
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2.26 CHAPTER TWO Aslam, S., Charmch
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3.2 CHAPTER THREE 3.1 BUILDING ENVE
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3.4 CHAPTER THREE Convective Heat T
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3.6 CHAPTER THREE Overall Heat Tran
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3.8 CHAPTER THREE Heat Capacity The
Page 101 and 102: 3.10 CHAPTER THREE Coefficients for
Page 103 and 104: 3.12 CHAPTER THREE Temperature also
Page 105 and 106: 3.14 CHAPTER THREE FIGURE 3.3 Mass
Page 107 and 108: 3.16 CHAPTER THREE Moisture Transfe
Page 109 and 110: 3.18 CHAPTER THREE During summer, t
Page 111 and 112: 3.20 CHAPTER THREE TABLE 3.3 Therma
Page 113 and 114: 3.22 CHAPTER THREE 3.7 SOLAR ANGLES
Page 115 and 116: 3.24 CHAPTER THREE ● Solar altitu
Page 117 and 118: 3.26 CHAPTER THREE In Table 3.5, th
Page 119 and 120: 3.28 CHAPTER THREE National Climati
Page 121 and 122: 3.30 CHAPTER THREE silver coatings
Page 123 and 124: 3.32 CHAPTER THREE 3.10 HEAT ADMITT
Page 125 and 126: 3.34 CHAPTER THREE design condition
Page 127 and 128: 3.36 CHAPTER THREE Shading Coeffici
Page 129 and 130: 3.38 CHAPTER THREE 40° north latit
Page 131 and 132: 3.40 CHAPTER THREE and fire protect
Page 133 and 134: 3.42 CHAPTER THREE External Shading
Page 135 and 136: 3.44 CHAPTER THREE FIGURE 3.16 Shad
Page 137 and 138: 3.46 CHAPTER THREE 3.12 HEAT EXCHAN
Page 139 and 140: 3.48 CHAPTER THREE Example 3.2. At
Page 141 and 142: 3.50 CHAPTER THREE Fenestration, in
Page 143 and 144: 3.52 CHAPTER THREE Donnelly, R. G.,
Page 145 and 146: 4.2 CHAPTER FOUR 2. Indoor air qual
Page 147 and 148: 4.4 CHAPTER FOUR 4.3 METABOLIC RATE
Page 149 and 150: 4.6 CHAPTER FOUR When the air veloc
Page 151: 4.8 CHAPTER FOUR calculated as TABL
Page 155 and 156: 4.12 CHAPTER FOUR FIGURE 4.4 Dimens
Page 157 and 158: 4.14 CHAPTER FOUR Effective Tempera
Page 159 and 160: FIGURE 4.5 Fanger’s comfort chart
Page 161 and 162: 4.18 CHAPTER FOUR Dew-point tempera
Page 163 and 164: 4.20 CHAPTER FOUR lower boundary in
Page 165 and 166: 4.22 CHAPTER FOUR FIGURE 4.9 Relati
Page 167 and 168: 4.24 CHAPTER FOUR levels are as fol
Page 169 and 170: 4.26 CHAPTER FOUR In Eq. (4.24), 0.
Page 171 and 172: 4.28 CHAPTER FOUR 1. Total particul
Page 173 and 174: 4.30 CHAPTER FOUR Outdoor Air Requi
Page 175 and 176: 4.32 CHAPTER FOUR 4.12 SOUND LEVEL
Page 177 and 178: 4.34 CHAPTER FOUR Human Response an
Page 179 and 180: 4.36 CHAPTER FOUR FIGURE 4.11 Room
Page 181 and 182: 4.38 CHAPTER FOUR hazardous, contam
Page 183 and 184: 4.40 TABLE 4.10 Climatic Conditions
Page 185 and 186: 4.42 CHAPTER FOUR 3. Outdoor weathe
Page 187 and 188: CHAPTER 5 ENERGY MANAGEMENT AND CON
Page 189 and 190: The 1973 energy crisis greatly boos
Page 191 and 192: The later the building is construct
Page 193 and 194: Control Methods ENERGY MANAGEMENT A
Page 195 and 196: 5.3 CONTROL MODES Two-Position Cont
Page 197 and 198: Floating Control Proportional Contr
Page 199 and 200: The set point is the desired value
Page 201 and 202: where K is the derivative gain. The
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ENERGY MANAGEMENT AND CONTROL SYSTE
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Pressure Sensors Flow Sensors ENERG
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An infrared occupancy sensor senses
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For a direct-acting pneumatic tempe
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attery backup. However, EEPROM cann
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Types of Control Valves to the elec
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Valve Selection ENERGY MANAGEMENT A
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design water flow rate V˙ , gpm (L
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The movement of the split damper fr
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damper is then fully opened. If the
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Damper Selection Damper Sizing wher
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BAC net SC BAC net UC UC UC UC SC A
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Future Development The development
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Network Layer Conformance Class, Fu
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5.10 CONTROL LOGIC AND ARTIFICIAL I
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Fuzzy Logic Controller. An FLC cons
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give a printout. A friendly dialog
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Artificial Neural Networks ENERGY M
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3. Evaluate the error � between t
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Graphical Programming for Mechanica
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System Capacity changes during off-
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Generic Controls ENERGY MANAGEMENT
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● Central plant control Multiple-
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The diagnostician used color coding
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Discharge air temperature T dis,
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REFERENCES ENERGY MANAGEMENT AND CO
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ENERGY MANAGEMENT AND CONTROL SYSTE
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6.2 CHAPTER SIX 6.1 SPACE LOAD CHAR
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6.4 CHAPTER SIX FIGURE 6.2 Solar he
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6.6 CHAPTER SIX Influence of Stored
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6.8 CHAPTER SIX leaving the coil, s
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6.10 CHAPTER SIX the maximum sum of
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6.12 CHAPTER SIX adoption of person
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6.14 CHAPTER SIX Characteristics of
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6.16 CHAPTER SIX where T sol, a �
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6.18 CHAPTER SIX Space latent heat
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6.20 CHAPTER SIX FIGURE 6.7 Relatio
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6.22 TABLE 6.2 CLTD for Calculating
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6.24 CHAPTER SIX Infiltration Infil
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6.26 CHAPTER SIX nighttime in summe
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6.28 CHAPTER SIX ● Outer surface
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6.30 TABLE 6.6 July Solar Cooling L
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6.32 CHAPTER SIX From Eqs. (6.19a)
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6.34 CHAPTER SIX thickness of the d
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6.36 CHAPTER SIX Simplifying Assump
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6.38 CHAPTER SIX where hci � conv
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6.40 CHAPTER SIX Adjacent Unheated
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6.42 CHAPTER SIX the next morning b
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6.44 CHAPTER SIX Trace 600 Input—
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6.46 CHAPTER SIX ● For the calcul
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6.48 CHAPTER SIX Area of perimeter
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6.50 CHAPTER SIX Komor, P., Space C
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7.2 CHAPTER SEVEN 7.1 FUNDAMENTALS
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7.4 CHAPTER SEVEN Open systems need
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7.6 CHAPTER SEVEN FIGURE 7.2 Fricti
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7.8 TABLE 7.1 Dimensions of Commonl
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TABLE 7.2 Dimensions of Copper Tube
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7.12 CHAPTER SEVEN Pipe Joints Copp
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7.14 CHAPTER SEVEN also be consider
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7.16 CHAPTER SEVEN Insulation expos
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7.18 CHAPTER SEVEN Valve Materials
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7.20 CHAPTER SEVEN Open Expansion T
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7.22 CHAPTER SEVEN FIGURE 7.8 Close
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7.24 CHAPTER SEVEN Penalties due to
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7.26 CHAPTER SEVEN TABLE 7.7 Analys
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7.28 CHAPTER SEVEN Changeover Two P
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7.30 CHAPTER SEVEN a semiautomatic
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7.32 CHAPTER SEVEN Performance Curv
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7.34 CHAPTER SEVEN remove. In most
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7.36 CHAPTER SEVEN FIGURE 7.15 Comb
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7.38 CHAPTER SEVEN The wire-to-wate
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7.40 CHAPTER SEVEN Variable Flow fo
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7.42 CHAPTER SEVEN Chiller VSD 2 VS
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7.44 5 2 6 Plant hot water pump Boi
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7.46 CHAPTER SEVEN Sequence of Oper
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7.48 CHAPTER SEVEN FIGURE 7.20 (Con
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7.50 CHAPTER SEVEN Use of Balancing
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7.52 CHAPTER SEVEN 2. For Qcs/Qcs,d
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7.54 CHAPTER SEVEN The following ar
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7.56 CHAPTER SEVEN loops. However,
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7.58 CHAPTER SEVEN DDC system contr
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7.60 CHAPTER SEVEN REFERENCES Input
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CHAPTER 8 HEATING SYSTEMS, FURNACES
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8.2 WARM AIR FURNACES Types of Warm
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Heat exchanger Warm air supply plen
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Saving Energy ● Annual fuel utili
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Nighttime Setback. ASHRAE research
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HEATING SYSTEMS, FURNACES, AND BOIL
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Gas and Oil Burners When natural ga
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Modern packaged boilers often inclu
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Electric Hot Water Boilers elements
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where volume flow rate of supply ai
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Thermal Stratification divided into
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15°F (8.3°C) is usually used. The
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Design Considerations FIGURE 8.8 Ba
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finned tube is 1190 Btu/h (350 W).
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Heating flux q u, Btu/h•ft 2 Floo
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● Pulse-width-modulated zone cont
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Design and Layout HEATING SYSTEMS,
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REFERENCES HEATING SYSTEMS, FURNACE
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CHAPTER 9 REFRIGERANTS, REFRIGERATI
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9.2 REFRIGERANTS Refrigerants, Cool
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9.3 PROPERTIES AND CHARACTERISTICS
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● Halide torch. This method is si
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9.9 Specific volume of Power Critic
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Action and Measures REFRIGERANTS, R
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Because of the worldwide effort to
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Zeotropic HFC HFC-410A is a blend o
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Refrigeration Cycles Unit of Refrig
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the diagram and temperature T, °R,
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The heat extracted from the source
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REFRIGERANTS, REFRIGERATION CYCLES,
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With subcooling, Savings in electri
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calculated as where p con � conde
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Coefficient of Performance REFRIGER
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Then, from Eq. (9.33), the total wo
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x 1 at interstage pressure p i1 can
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From Eq. (9.22), the enthalpy diffe
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FIGURE 9.13 (Continued) where p 1,
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If �c, �t, TR1� , TR3, and pr
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Recent Developments ASHRAE Standard
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The only type of non-positive displ
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Energy Use Index In Eq. (9.71), m˙
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For institutional or health care oc
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Storage of Refrigerants REFERENCES
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CHAPTER 10 REFRIGERATION SYSTEMS: C
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● Shell-and-tube liquid cooler wi
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at an oil concentration of 3 percen
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or h al � h ae � �(h ae � h
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FIGURE 10.3 Control of DX coils at
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Example 10.1. A DX coil in a packag
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REFRIGERATION SYSTEMS: COMPONENTS 1
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where U dirty, U clean � overall
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Temperature difference T ee � T e
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FIGURE 10.7 (Continued) (b) Schemat
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Total Heat Rejection Compared with
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FIGURE 10.9 Double-tube condenser.
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It is important to recognize that t
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A refrigeration system with a lower
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Selection and Installation REFRIGER
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Counterflow Forced-Draft Cooling To
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air film that surrounds the condens
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By using the numerical integration
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Tower Coefficient and Water-Air Rat
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Construction Materials cellular fil
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(T w2 � T w1)/(h s � h a), or t
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Blowdown Legionnaires’ Disease va
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The rated conditions of air-cooled
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The corresponding saturated tempera
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Electric Expansion Valves slugs may
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Capillary Tube FIGURE 10.21 Float v
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11.2 CHAPTER ELEVEN 11.1 RECIPROCAT
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11.4 CHAPTER ELEVEN refrigerants. A
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11.6 FIGURE 11.5 Schematic reciproc
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11.8 CHAPTER ELEVEN Accessories sys
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11.10 CHAPTER ELEVEN into the inner
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11.12 CHAPTER ELEVEN FIGURE 11.8 Se
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11.14 CHAPTER ELEVEN Size of Copper
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11.16 CHAPTER ELEVEN TABLE 11.3 Fit
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11.18 CHAPTER ELEVEN FIGURE 11.10 S
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11.20 CHAPTER ELEVEN 5. The minimum
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11.22 CHAPTER ELEVEN If a receiver
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11.24 CHAPTER ELEVEN 11.5 CAPACITY
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11.26 CHAPTER ELEVEN Safety Control
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11.28 CHAPTER ELEVEN FIGURE 11.16 L
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11.30 CHAPTER ELEVEN Refrigeration
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11.32 CHAPTER ELEVEN Performance of
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11.34 CHAPTER ELEVEN 11.7 SYSTEM BA
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11.36 CHAPTER ELEVEN compression ra
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11.38 CHAPTER ELEVEN is superheated
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11.40 CHAPTER ELEVEN in Fig. 11.22,
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11.42 CHAPTER ELEVEN (2048 kPa abs.
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11.44 CHAPTER ELEVEN Scroll Compres
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11.46 CHAPTER ELEVEN Compressor Per
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11.48 CHAPTER ELEVEN System Charact
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11.50 CHAPTER ELEVEN are specified
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11.52 CHAPTER ELEVEN FIGURE 11.29 T
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11.54 CHAPTER ELEVEN Variable Volum
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11.56 CHAPTER ELEVEN REFERENCES ASH
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CHAPTER 12 HEAT PUMPS, HEAT RECOVER
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where h 2� � enthalpy of hot ga
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climates, cold supply air may be re
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FIGURE 12.3 (Continued) HEAT PUMPS,
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Operating Modes System Performance
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load. When the outdoor temperature
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Controls Capacity and Selection HEA
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FIGURE 12.5 A typical groundwater h
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HEAT PUMPS, HEAT RECOVERY, GAS COOL
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A vertical ground coil is buried fr
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Exhaust airstream Runaround Coil Lo
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HEAT PUMPS, HEAT RECOVERY, GAS COOL
Page 603 and 604:
Comparison between Various Air-to-A
Page 605 and 606:
Gas-Engine Chiller Gas Engines HEAT
Page 607 and 608:
When the engine jacket water is rou
Page 609 and 610:
CHAPTER 13 REFRIGERATION SYSTEMS: C
Page 611 and 612:
Compressor REFRIGERATION SYSTEMS: C
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Purge Unit FIGURE 13.3 Orifice plat
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Types of Centrifugal Chiller match
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For water-cooled centrifugal chille
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FIGURE 13.5 (Continued ) REFRIGERAT
Page 621 and 622:
(5.6 to 6.7°C) in temperature diff
Page 623 and 624:
● The maintenance cost can be red
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FIGURE 13.10 (Continued ) where Q r
Page 627 and 628:
13.6 CAPACITY CONTROL OF CENTRIFUGA
Page 629 and 630:
Comparison between Inlet Vanes and
Page 631 and 632:
Condenser Water Temperature Control
Page 633 and 634:
7. After the oil pressure has been
Page 635 and 636:
The log-mean temperature difference
Page 637 and 638:
Therefore, from Eq. (13.12) the eva
Page 639 and 640:
The actual percentage of design pow
Page 641 and 642:
water enters the condenser T en, c
Page 643 and 644:
Chiller Minimum Performance Design
Page 645 and 646:
REFRIGERATION SYSTEMS: CENTRIFUGAL
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14.2 CHAPTER FOURTEEN Historical De
Page 649 and 650:
14.4 CHAPTER FOURTEEN Equilibrium C
Page 651 and 652:
14.6 CHAPTER FOURTEEN If an aqueous
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14.8 CHAPTER FOURTEEN Air Purge Uni
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14.10 CHAPTER FOURTEEN 10 5 20 40 1
Page 657 and 658:
14.12 CHAPTER FOURTEEN Also, Therma
Page 659 and 660:
14.14 CHAPTER FOURTEEN Coefficient
Page 661 and 662:
14.16 CHAPTER FOURTEEN From the psy
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14.18 CHAPTER FOURTEEN bypass recir
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14.20 CHAPTER FOURTEEN Corrosion Co
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14.22 CHAPTER FOURTEEN Actual Perfo
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14.24 CHAPTER FOURTEEN absorber and
Page 671 and 672:
14.26 CHAPTER FOURTEEN Coefficient
Page 673 and 674:
CHAPTER 15 AIR SYSTEMS: COMPONENTS
Page 675 and 676:
FIGURE 15.1 Types of fans: (a) cent
Page 677 and 678:
The fan power input on the fan shaf
Page 679 and 680:
where �p t,s � fan total pressu
Page 681 and 682:
The total pressure developed is AIR
Page 683 and 684:
Forward-Curved Fans AIR SYSTEMS: CO
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AIR SYSTEMS: COMPONENTS—FANS, COI
Page 687 and 688:
Page 689 and 690:
Page 691 and 692:
Page 693 and 694:
Inlet Vanes Modulation AIR SYSTEMS:
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Inlet Cone Modulation AIR SYSTEMS:
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the smooth airflow suddenly breaks
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High-Temperature Fans AIR SYSTEMS:
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FIGURE 15.24 Direction of rotation
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octave bands for axial fans are far
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Types of Coils Fins AIR SYSTEMS: CO
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Contact Conductance AIR SYSTEMS: CO
Page 711 and 712:
Water Circuits Contact conductance
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If the thermal resistance of copper
Page 715 and 716:
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Coil Construction Parameters AIR SY
Page 719 and 720:
And from Eq. (15.34), Assume � f
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Dry Part airstream and water stream
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FIGURE 15.32 Psychrometric analysis
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cooling and dehumidifying capacity
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From Eq. (15.27), Then the outer su
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Coil Cleanliness Drain and Isolatin
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particles may range from � 1�m
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15.14 AIR FILTERS Filtration Mechan
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● Most low-efficiency filters hav
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15.15 ELECTRONIC AIR CLEANERS AIR S
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usually decreases the adsorption ca
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FIGURE 15.41 Humidifying load for a
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Heating Element Humidifiers AIR SYS
Page 749 and 750:
Ultrasonic Humidifiers An ultrasoni
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15.21 AIR WASHERS The air washer wa
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Bypass Control For a cooling and de
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industrial manufacturing processes
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REFERENCES AIR SYSTEMS: COMPONENTS
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CHAPTER 16 AIR SYSTEMS: EQUIPMENT
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FIGURE 16.1 Type of air-handling un
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Coils Filters Humidifiers AIR SYSTE
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AIR SYSTEMS: EQUIPMENT—AIR-HANDLI
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15.10, the cooling coil face veloci
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16.11 TABLE 16.2 Volume Flow and Fa
Page 771 and 772:
Page 773 and 774:
Indoor Packaged Units AIR SYSTEMS:
Page 775 and 776:
Reciprocating and scroll compressor
Page 777 and 778:
Minimum Performance 9. Compressor l
Page 779 and 780:
16.21 TABLE 16.4 Supply Fan Perform
Page 781 and 782:
There will be no carryover of conde
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FIGURE 16.9 Interior core fan room:
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CHAPTER 17 AIR SYSTEMS: AIR DUCT DE
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p� 1 � � 1v 1 2 (17.4) If bot
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Stack Effect where � � air dens
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Velocity Distribution Equation of C
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FIGURE 17.3 Pressure characteristic
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where Psy � each air system total
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Rectangular Ducts AIR SYSTEMS: AIR
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17.15 TABLE 17.2 Rectangular Ferrou
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TABLE 17.4 Round Ferrous Metal Duct
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17.4 DUCT HEAT GAIN, HEAT LOSS, AND
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Temperature Rise Curves If the temp
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In an ideal smooth tube or duct, th
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loss per unit length �p f, in in.
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Circular Equivalents Example 17.1.
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17.29 42 15.6 17.1 18.5 19.9 21.1 2
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For galvanized steel flat oval duct
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AIR SYSTEMS: AIR DUCT DESIGN 17.33
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FIGURE 17.12 Round and flat oval te
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FIGURE 17.14 Openings mounted on a
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FIGURE 17.16 Total pressure loss
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FIGURE 17.17 Combination of flow re
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Fig. 17.19a, are given as and (17.6
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● An optimal duct system layout w
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● From node 1, the total pressure
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TABLE 17.10 Duct Leakage Classifica
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each fire damper. Many regulatory a
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The designer then compares various
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T Method planes 1 and 2, and the vo
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h, or in I-P units For SI units, FI
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When the total pressure loss of the
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TABLE 17.11 Local Loss Coefficients
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Return or Exhaust Duct Systems AIR
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and the sized diameter 0.0147 � 2
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FIGURE 17.25 Rectangular supply duc
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If the height of the rectangular du
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FIGURE 17.28 A return duct system w
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Design Interface AIR SYSTEMS: AIR D
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vacuum used in duct cleaning is oft
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accurate measurement, an inclined m
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AIR SYSTEMS: AIR DUCT DESIGN 17.79
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18.2 CHAPTER EIGHTEEN Design Consid
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18.4 CHAPTER EIGHTEEN cooling load
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18.6 CHAPTER EIGHTEEN FIGURE 18.2 F
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18.8 CHAPTER EIGHTEEN Confined Air
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18.10 CHAPTER EIGHTEEN Free Nonisot
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18.12 CHAPTER EIGHTEEN Ceiling Diff
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18.14 CHAPTER EIGHTEEN Slot Diffuse
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18.16 CHAPTER EIGHTEEN TABLE 18.1 P
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18.18 CHAPTER EIGHTEEN FIGURE 18.12
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18.20 CHAPTER EIGHTEEN 18.4 MIXING
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18.28 CHAPTER EIGHTEEN ● The loca
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18.30 CHAPTER EIGHTEEN ● The aver
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18.32 CHAPTER EIGHTEEN ● Cost. In
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18.34 CHAPTER EIGHTEEN ● A termin
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18.38 CHAPTER EIGHTEEN The return s
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18.40 CHAPTER EIGHTEEN Ventilating
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18.42 CHAPTER EIGHTEEN 18.8 STRATIF
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18.44 CHAPTER EIGHTEEN 18.9 PROJECT
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18.46 CHAPTER EIGHTEEN Target Veloc
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18.48 CHAPTER EIGHTEEN Application
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18.50 CHAPTER EIGHTEEN Heat Unneutr
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18.52 CHAPTER EIGHTEEN CFD Becomes
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18.54 CHAPTER EIGHTEEN Conducting C
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18.56 CHAPTER EIGHTEEN Wendes, H.,
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19.2 CHAPTER NINETEEN Sound Paths T
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19.4 CHAPTER NINETEEN 9. Check this
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19.6 CHAPTER NINETEEN Branch ducts
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19.8 CHAPTER NINETEEN TABLE 19.3 So
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19.10 CHAPTER NINETEEN End Reflecti
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19.12 CHAPTER NINETEEN 19.4 SILENCE
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19.14 CHAPTER NINETEEN facing. A so
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19.16 CHAPTER NINETEEN Active Silen
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19.18 CHAPTER NINETEEN Recommendati
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19.20 CHAPTER NINETEEN FIGURE 19.6
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19.22 CHAPTER NINETEEN TABLE 19.11
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19.24 CHAPTER NINETEEN Array of Cei
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19.26 CHAPTER NINETEEN Environmenta
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19.28 CHAPTER NINETEEN Octave band
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19.30 CHAPTER NINETEEN Sound Source
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19.32 CHAPTER NINETEEN Structure-Bo
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CHAPTER 20 AIR SYSTEMS: BASICS AND
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Air Distribution Systems Ventilatio
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20.2 BUILDING LEAKAGE AREA AND BUIL
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20.3 SPACE PRESSURIZATION Space Pre
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doors and windows are closed. When
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Wind speed from a meteorological st
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In Eq. (20.8), m˙ inf indicates th
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System Operating Point FIGURE 20.4
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20.6 SYSTEM EFFECT ● Condition 1.
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Inlet System Effect Loss fan inlet
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FIGURE 20.7 Outlet system effect: (
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For a SWSI centrifugal fan with A b
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Two Fan-Duct Systems Connected in S
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volume flow and fan total pressure.
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FIGURE 20.12 Two parallel fan-duct
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Similarly, the residual pressure of
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Modulation of Fan-Duct Systems AIR
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FIGURE 20.14 (Continued) AIR SYSTEM
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Plot the fan performance curve Ft a
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20.9 CLASSIFICATION OF AIR SYSTEMS
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To save energy, most AHU and PU man
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where ws,wr � humidity ratio at t
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exchanger is called the sensible co
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compressed air, or ultrasonic force
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AIR SYSTEMS: BASICS AND CONSTANT-VO
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FIGURE 20.21 Adiabatic mixing and b
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and the heating coil load is 20.16
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Cooling mode operation in summer co
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ecirculating air m is usually lower
Page 1013 and 1014:
● Outdoor damper activates with s
Page 1015 and 1016:
3. To provide a desirable air veloc
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Air Conditioning Rules Graphical Me
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FIGURE 20.25 Effect of sensible hea
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2. Because the air temperature at t
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At a temperature of 72°F (22.2°C)
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Because w m � w s, Therefore, Fro
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Part-Load Operation 7. Draw a verti
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Reheating is a simple and effective
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Operating Parameters and Calculatio
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REFERENCES AIR SYSTEMS: BASICS AND
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21.2 CHAPTER TWENTY-ONE 21.1 SYSTEM
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FIGURE 21.1 A single-zone VAV syste
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21.6 CHAPTER TWENTY-ONE FIGURE 21.2
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21.8 CHAPTER TWENTY-ONE Region IV:
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21.10 CHAPTER TWENTY-ONE dry-bulb e
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21.12 CHAPTER TWENTY-ONE Consider a
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21.14 CHAPTER TWENTY-ONE ● The ou
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21.16 CHAPTER TWENTY-ONE outdoor ve
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21.18 CHAPTER TWENTY-ONE 7. When T
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21.20 CHAPTER TWENTY-ONE VAV Reheat
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21.22 CHAPTER TWENTY-ONE FIGURE 21.
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21.24 CHAPTER TWENTY-ONE FIGURE 21.
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21.26 CHAPTER TWENTY-ONE In dead-ba
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21.28 CHAPTER TWENTY-ONE For the pe
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21.30 CHAPTER TWENTY-ONE calculated
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21.32 CHAPTER TWENTY-ONE For the wi
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21.34
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21.36 CHAPTER TWENTY-ONE Number of
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21.38 CHAPTER TWENTY-ONE Mixing Mod
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21.40 CHAPTER TWENTY-ONE ● Modula
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21.42 CHAPTER TWENTY-ONE where Q rs
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21.44 CHAPTER TWENTY-ONE From Eq. (
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FIGURE 21.13 (Continued) 21.46
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21.48 CHAPTER TWENTY-ONE Fan-Powere
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21.50 CHAPTER TWENTY-ONE The drawba
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21.52 CHAPTER TWENTY-ONE Zone Contr
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21.54 CHAPTER TWENTY-ONE Percentage
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21.56 CHAPTER TWENTY-ONE ● During
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21.58 CHAPTER TWENTY-ONE Wendes, H.
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22.2 CHAPTER TWENTY-TWO 22.1 RETURN
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22.4 CHAPTER TWENTY-TWO 22.2 FAN CO
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22.6 CHAPTER TWENTY-TWO Recirculati
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22.8 CHAPTER TWENTY-TWO flow rate o
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22.10 CHAPTER TWENTY-TWO FIGURE 22.
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22.12 CHAPTER TWENTY-TWO The system
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22.14 CHAPTER TWENTY-TWO to balance
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22.16 CHAPTER TWENTY-TWO The fixed
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22.18 CHAPTER TWENTY-TWO air is ext
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22.20 CHAPTER TWENTY-TWO Air Econom
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22.22 CHAPTER TWENTY-TWO (2) The re
Page 1115 and 1116:
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22.28 CHAPTER TWENTY-TWO ● The as
Page 1121 and 1122:
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22.32 CHAPTER TWENTY-TWO Design Con
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22.34 CHAPTER TWENTY-TWO �a � a
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22.36 CHAPTER TWENTY-TWO The pressu
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22.38 CHAPTER TWENTY-TWO REFERENCES
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CHAPTER 23 AIR SYSTEMS: MINIMUM VEN
Page 1133 and 1134:
ASHRAE Standard 62-1999 control, a
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The system outdoor air volume flow
Page 1137 and 1138:
CO 2 Sensor or Mixed-Gases Sensor L
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supplied to a control zone in a VAV
Page 1141 and 1142:
Economizer damper Exhaust damper Mi
Page 1143 and 1144:
AIR SYSTEMS: MINIMUM VENTILATION AN
Page 1145 and 1146:
● The maximum supply volume flow
Page 1147 and 1148:
where m˙ ex,r, m˙ eu � mass flo
Page 1149 and 1150:
System Description AIR SYSTEMS: MIN
Page 1151 and 1152:
Page 1153 and 1154:
● It lowers the duct heat gain or
Page 1155 and 1156:
Page 1157 and 1158:
Steam Humidifier Control Dew Point
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consumption than proportional contr
Page 1161 and 1162:
Page 1163 and 1164:
Page 1165 and 1166:
REFERENCES AIR SYSTEMS: MINIMUM VEN
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24.1 IAQ PROBLEMS CHAPTER 24 IMPROV
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air economizer cycle and mixed air
Page 1171 and 1172:
Sundell (1996) noted that many stud
Page 1173 and 1174:
Service Life of Air Filters Filter
Page 1175 and 1176:
● To eliminate or to reduce indoo
Page 1177 and 1178:
Chemisorption Fig. 24.1, the sharp
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and final filter in air systems wit
Page 1181 and 1182:
REFERENCES IMPROVING INDOOR AIR QUA
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25.2 CHAPTER TWENTY-FIVE energy res
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25.4 CHAPTER TWENTY-FIVE Mitigating
Page 1187 and 1188:
25.6 CHAPTER TWENTY-FIVE Energy Aud
Page 1189 and 1190:
25.8 CHAPTER TWENTY-FIVE Green Buil
Page 1191 and 1192:
25.10 CHAPTER TWENTY-FIVE Energy St
Page 1193 and 1194:
25.12 CHAPTER TWENTY-FIVE 25.5 CASE
Page 1195 and 1196:
25.14 CHAPTER TWENTY-FIVE For both
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25.16 CHAPTER TWENTY-FIVE Unit elec
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25.18 CHAPTER TWENTY-FIVE Physical
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25.20 CHAPTER TWENTY-FIVE condensin
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25.22 CHAPTER TWENTY-FIVE Condenser
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25.24 CHAPTER TWENTY-FIVE The polyn
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25.26 CHAPTER TWENTY-FIVE Loads Sys
Page 1209 and 1210:
25.28 CHAPTER TWENTY-FIVE ● Recip
Page 1211 and 1212:
25.30 CHAPTER TWENTY-FIVE Scientifi
Page 1213 and 1214:
26.2 CHAPTER TWENTY-SIX The purpose
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26.4 CHAPTER TWENTY-SIX requiring l
Page 1217 and 1218:
26.6 CHAPTER TWENTY-SIX the nutriti
Page 1219 and 1220:
26.8 CHAPTER TWENTY-SIX Space Limit
Page 1221 and 1222:
26.10 CHAPTER TWENTY-SIX and throug
Page 1223 and 1224:
26.12 CHAPTER TWENTY-SIX Controls F
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26.14 CHAPTER TWENTY-SIX Exterior l
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26.16 CHAPTER TWENTY-SIX Harold, R.
Page 1229 and 1230:
27.2 CHAPTER TWENTY-SEVEN condition
Page 1231 and 1232:
27.4 CHAPTER TWENTY-SEVEN 2. Water-
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27.6 CHAPTER TWENTY-SEVEN TABLE 27.
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27.8 CHAPTER TWENTY-SEVEN FIGURE 27
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27.10 CHAPTER TWENTY-SEVEN Effectiv
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27.12 CHAPTER TWENTY-SEVEN consumpt
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50 50 13.0 27.14 40 40 60 60 50 50
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27.16 CHAPTER TWENTY-SEVEN Assume t
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27.18 CHAPTER TWENTY-SEVEN System C
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27.20 CHAPTER TWENTY-SEVEN If the e
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27.22 CHAPTER TWENTY-SEVEN coil and
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27.24 CHAPTER TWENTY-SEVEN warm and
Page 1253 and 1254:
27.26 CHAPTER TWENTY-SEVEN REFERENC
Page 1255 and 1256:
CHAPTER 28 AIR CONDITIONING SYSTEMS
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Induction Systems annoying. A recei
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Fan-Coil Units AIR CONDITIONING SYS
Page 1261 and 1262:
Volume Flow Rate Fan Motor. Permane
Page 1263 and 1264:
Heating Capacity If the sensible he
Page 1265 and 1266:
where � ps � air density of out
Page 1267 and 1268:
Part-Load Operation At cooling mode
Page 1269 and 1270:
TABLE 28.1 System Characteristics o
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AIR CONDITIONING SYSTEMS: SPACE CON
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where w s � humidity ratio of fan
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In a typical nonchangeover two-pipe
Page 1277 and 1278:
For all the rooms in the perimeter
Page 1279 and 1280:
Loop Temperatures AIR CONDITIONING
Page 1281 and 1282:
leaving condition of 60°F (15.6°C
Page 1283 and 1284:
Water Heater Storage Tanks heat pum
Page 1285 and 1286:
System Characteristics starts the f
Page 1287 and 1288:
● If ceiling units are used, good
Page 1289 and 1290:
Page 1291 and 1292:
Applications AC SYSTEMS: PACKAGED A
Page 1293 and 1294:
Controls Energy Use Intensities Sys
Page 1295 and 1296:
29.3 SINGLE-ZONE VAV PACKAGED SYSTE
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d. That is capable of being set bac
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volume flow rate when the total pre
Page 1301 and 1302:
FIGURE 29.2 A VAV reheat packaged s
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liquid slugging. Liquid slugging ma
Page 1305 and 1306:
A VAV packaged system is shut off d
Page 1307 and 1308:
more widely used. Fan-powered VAV p
Page 1309 and 1310:
AC SYSTEMS: PACKAGED AND DESICCANT-
Page 1311 and 1312:
AC SYSTEMS: PACKAGED AND DESICCANT-
Page 1313 and 1314:
FIGURE 29.4 A desiccant-based air c
Page 1315 and 1316:
As defined in Sec. 3.4, a sorption
Page 1317 and 1318:
flow rate of the mixture of the pro
Page 1319 and 1320:
Part-Load Operation and Controls Wh
Page 1321 and 1322:
System Description AC SYSTEMS: PACK
Page 1323 and 1324:
System Characteristics REFERENCES A
Page 1325 and 1326:
Page 1327 and 1328:
● Special process temperature and
Page 1329 and 1330:
Air and Water Temperature Different
Page 1331 and 1332:
of a VAV system using inlet vane mo
Page 1333 and 1334:
System Characterisics System charac
Page 1335 and 1336:
System Characteristics the supply a
Page 1337 and 1338:
System Characteristics AC SYSTEMS:
Page 1339 and 1340:
FIGURE 30.1 A clean-room system for
Page 1341 and 1342:
Manufacturing an integrated circuit
Page 1343 and 1344:
Summer Mode Operation Room temperat
Page 1345 and 1346:
System Pressure AC SYSTEMS: CENTRAL
Page 1347 and 1348:
FIGURE 30.2 (Continued) Effect of F
Page 1349 and 1350:
AC SYSTEMS: CENTRAL SYSTEMS AND CLE
Page 1351 and 1352:
31.2 CHAPTER THIRTY-ONE mechanical
Page 1353 and 1354:
31.4 CHAPTER THIRTY-ONE Refrigerati
Page 1355 and 1356:
31.6 CHAPTER THIRTY-ONE 31.2 ICE-ON
Page 1357 and 1358:
31.8 CHAPTER THIRTY-ONE FIGURE 31.3
Page 1359 and 1360:
31.10 CHAPTER THIRTY-ONE TABLE 31.1
Page 1361 and 1362:
31.12 CHAPTER THIRTY-ONE Water leve
Page 1363 and 1364:
31.14 CHAPTER THIRTY-ONE Location o
Page 1365 and 1366:
31.16 CHAPTER THIRTY-ONE FIGURE 31.
Page 1367 and 1368:
31.18 CHAPTER THIRTY-ONE In additio
Page 1369 and 1370:
31.20 CHAPTER THIRTY-ONE Temperatur
Page 1371 and 1372:
31.22 CHAPTER THIRTY-ONE volume flo
Page 1373 and 1374:
31.24 CHAPTER THIRTY-ONE Storage co
Page 1375 and 1376:
31.26 CHAPTER THIRTY-ONE Charging P
Page 1377 and 1378:
31.28 CHAPTER THIRTY-ONE System Per
Page 1379 and 1380:
CHAPTER 32 COMMISSIONING AND MAINTE
Page 1381 and 1382:
● Clarifly owner priorities and d
Page 1383 and 1384:
intent. The CC also makes sure that
Page 1385 and 1386:
APPENDIX A NOMENCLATURE AND ABBREVI
Page 1387 and 1388:
I DN i m I a I rad I ref I t solar
Page 1389 and 1390:
SC shadding coefficient Sc Schmidt
Page 1391 and 1392:
2g second-stage generator go satura
Page 1393 and 1394:
� relative humidity, percent; sol
Page 1395 and 1396:
APPENDIX B PSYCHROMETRIC CHART, TAB
Page 1397 and 1398:
B.3 TABLE B.1 Thermodynamic Propert
Page 1399 and 1400:
TABLE B.2 Physical Properties of Ai
Page 1401:
PSYCHROMETRIC CHART, TABLES OF PROP
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Handbook of air conditioning and refrigeration / Shan K

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