Handbook of air conditioning and refrigeration / Shan K

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FIGURE 21.3 Temperature economizer control: (a) outside weather regions; (b) temperature economizer. 21.11
21.12 CHAPTER TWENTY-ONE Consider a single-zone VAV system that serves a building located in Phoenix, Arizona. Assume that the outdoor temperature is 85°F (29.4°C), the humidity ratio is 0.006 lb/lb (kg/kg), and the conditioned air leaves the coil at a temperature of 55°F (12.8°C), with a relative humidity of 95 percent. The recirculating air enters the AHU or PU at a temperature of 78°F (25.5°C) and a humidity ratio of 0.0094 lb/lb (kg/kg). If a differential enthalpy economizer control is used, the state point of outdoor air o h falls in region III, and if a differential dry-bulb economizer control is used, the state point of outdoor air o T falls in region I. The properties of moist air are as follows: A differential dry-bulb economizer control is required to cool the mixture of outdoor and recirculating air down to an enthalpy difference of 6.2 Btu/lb (14.4 kJ/kg) instead of 7.2 Btu/lb (16.7 kJ/kg) using a differential enthalpy economizer control. Therefore, consider the following: 1. For locations having hot and humid climates where many status points of outdoor air fall in the dotted area A in Fig. 21.3a, a differential enthalpy economizer control is recommended. 2. For most locations having moderate outdoor humidity ratios, according to Spitler et al. (1987), the energy savings offered by using a differential enthalpy economizer control instead of a temperature-based economizer are small. The two types of economizer control may differ by only about 5 to 10 percent. A fixed dry-bulb economizer control is recommended. 3. For locations having dry climates, a fixed dry-bulb of economizer control with a temperature setting of 75 to 78°F (23.9 to 25.1°C) sometimes even saves more cooling energy than a differential enthalpy economizer control. A fixed dry-bulb economizer control is strongly recommended. 4. For locations with humid climates, where the space requires a lower relative humidity, a fixed dry-bulb economizer control using a set point T db a few degrees Farenheit lower than space temperature sometimes is beneficial. 5. A survey including the simulation and comparison of various air economizer control alternatives is often beneficial. Water Economizer and Control Differential enthalpy Differential dry bulb Outdoor Off-coil Recirculating Outdoor Mixture Off-coil Temperature, °F 85 55 78 85 79.5 55 Relative humidity, % 24 65 45 24 40 90 Humidity ratio, lb/lb 0.006 0.006 0.0094 0.006 0.0086 0.0086 Enthalpy, Btu/lb 27.0 19.8 28.6 22.4 Enthalpy difference, Btu/lb 7.2 6.2 Amount of outdoor air, % 100 20 Consider a typical water economizer that uses a precooling coil in either an AHU or PU, as shown in Fig. 21.4b, and has the following operating characteristics: ● The cooling tower approach is assumed to be 5°F (2.8°C). ● The mixing temperature of outdoor air and recirculating air T m, is 78°F (25.5°C). ● The minimum temperature difference between T m and the condenser water temperature T con,w is 4°F (2.2°C). ● When the outdoor wet-bulb temperature T o��40°F (4.4°C), the temperature of the condenser water used to replace the entire refrigeration through a heat exchanger is less than 45°F (7.2°C).
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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
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3.10 CHAPTER THREE Coefficients for
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3.12 CHAPTER THREE Temperature also
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3.14 CHAPTER THREE FIGURE 3.3 Mass
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3.16 CHAPTER THREE Moisture Transfe
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3.18 CHAPTER THREE During summer, t
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3.20 CHAPTER THREE TABLE 3.3 Therma
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3.22 CHAPTER THREE 3.7 SOLAR ANGLES
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3.24 CHAPTER THREE ● Solar altitu
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3.26 CHAPTER THREE In Table 3.5, th
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3.28 CHAPTER THREE National Climati
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3.30 CHAPTER THREE silver coatings
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3.32 CHAPTER THREE 3.10 HEAT ADMITT
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3.34 CHAPTER THREE design condition
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3.36 CHAPTER THREE Shading Coeffici
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3.38 CHAPTER THREE 40° north latit
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3.40 CHAPTER THREE and fire protect
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3.42 CHAPTER THREE External Shading
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3.44 CHAPTER THREE FIGURE 3.16 Shad
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3.46 CHAPTER THREE 3.12 HEAT EXCHAN
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3.48 CHAPTER THREE Example 3.2. At
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3.50 CHAPTER THREE Fenestration, in
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3.52 CHAPTER THREE Donnelly, R. G.,
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4.2 CHAPTER FOUR 2. Indoor air qual
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4.4 CHAPTER FOUR 4.3 METABOLIC RATE
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4.6 CHAPTER FOUR When the air veloc
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4.8 CHAPTER FOUR calculated as TABL
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4.10 CHAPTER FOUR FIGURE 4.2 Mean v
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4.12 CHAPTER FOUR FIGURE 4.4 Dimens
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4.14 CHAPTER FOUR Effective Tempera
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FIGURE 4.5 Fanger’s comfort chart
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4.18 CHAPTER FOUR Dew-point tempera
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4.20 CHAPTER FOUR lower boundary in
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4.22 CHAPTER FOUR FIGURE 4.9 Relati
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4.24 CHAPTER FOUR levels are as fol
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4.26 CHAPTER FOUR In Eq. (4.24), 0.
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4.28 CHAPTER FOUR 1. Total particul
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4.30 CHAPTER FOUR Outdoor Air Requi
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4.32 CHAPTER FOUR 4.12 SOUND LEVEL
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4.34 CHAPTER FOUR Human Response an
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4.36 CHAPTER FOUR FIGURE 4.11 Room
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4.38 CHAPTER FOUR hazardous, contam
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4.40 TABLE 4.10 Climatic Conditions
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4.42 CHAPTER FOUR 3. Outdoor weathe
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CHAPTER 5 ENERGY MANAGEMENT AND CON
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The 1973 energy crisis greatly boos
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The later the building is construct
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Control Methods ENERGY MANAGEMENT A
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5.3 CONTROL MODES Two-Position Cont
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Floating Control Proportional Contr
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The set point is the desired value
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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
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Comparison between Various Air-to-A
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Gas-Engine Chiller Gas Engines HEAT
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When the engine jacket water is rou
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CHAPTER 13 REFRIGERATION SYSTEMS: C
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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
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(5.6 to 6.7°C) in temperature diff
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● The maintenance cost can be red
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FIGURE 13.10 (Continued ) where Q r
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13.6 CAPACITY CONTROL OF CENTRIFUGA
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Comparison between Inlet Vanes and
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Condenser Water Temperature Control
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7. After the oil pressure has been
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The log-mean temperature difference
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Therefore, from Eq. (13.12) the eva
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The actual percentage of design pow
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water enters the condenser T en, c
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Chiller Minimum Performance Design
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REFRIGERATION SYSTEMS: CENTRIFUGAL
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14.2 CHAPTER FOURTEEN Historical De
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14.4 CHAPTER FOURTEEN Equilibrium C
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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
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14.12 CHAPTER FOURTEEN Also, Therma
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14.14 CHAPTER FOURTEEN Coefficient
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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
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14.26 CHAPTER FOURTEEN Coefficient
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CHAPTER 15 AIR SYSTEMS: COMPONENTS
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FIGURE 15.1 Types of fans: (a) cent
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The fan power input on the fan shaf
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where �p t,s � fan total pressu
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The total pressure developed is AIR
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Forward-Curved Fans AIR SYSTEMS: CO
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AIR SYSTEMS: COMPONENTS—FANS, COI
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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
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Water Circuits Contact conductance
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If the thermal resistance of copper
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Coil Construction Parameters AIR SY
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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
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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
Page 765 and 766:
AIR SYSTEMS: EQUIPMENT—AIR-HANDLI
Page 767 and 768:
15.10, the cooling coil face veloci
Page 769 and 770:
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
Page 783 and 784:
Page 785 and 786:
FIGURE 16.9 Interior core fan room:
Page 787 and 788:
CHAPTER 17 AIR SYSTEMS: AIR DUCT DE
Page 789 and 790:
p� 1 � � 1v 1 2 (17.4) If bot
Page 791 and 792:
Stack Effect where � � air dens
Page 793 and 794:
Velocity Distribution Equation of C
Page 795 and 796:
FIGURE 17.3 Pressure characteristic
Page 797 and 798:
where Psy � each air system total
Page 799 and 800:
Rectangular Ducts AIR SYSTEMS: AIR
Page 801 and 802:
17.15 TABLE 17.2 Rectangular Ferrou
Page 803 and 804:
TABLE 17.4 Round Ferrous Metal Duct
Page 805 and 806:
17.4 DUCT HEAT GAIN, HEAT LOSS, AND
Page 807 and 808:
Temperature Rise Curves If the temp
Page 809 and 810:
In an ideal smooth tube or duct, th
Page 811 and 812:
loss per unit length �p f, in in.
Page 813 and 814:
Circular Equivalents Example 17.1.
Page 815 and 816:
17.29 42 15.6 17.1 18.5 19.9 21.1 2
Page 817 and 818:
For galvanized steel flat oval duct
Page 819 and 820:
AIR SYSTEMS: AIR DUCT DESIGN 17.33
Page 821 and 822:
FIGURE 17.12 Round and flat oval te
Page 823 and 824:
FIGURE 17.14 Openings mounted on a
Page 825 and 826:
FIGURE 17.16 Total pressure loss
Page 827 and 828:
FIGURE 17.17 Combination of flow re
Page 829 and 830:
Fig. 17.19a, are given as and (17.6
Page 831 and 832:
● An optimal duct system layout w
Page 833 and 834:
● From node 1, the total pressure
Page 835 and 836:
TABLE 17.10 Duct Leakage Classifica
Page 837 and 838:
each fire damper. Many regulatory a
Page 839 and 840:
The designer then compares various
Page 841 and 842:
T Method planes 1 and 2, and the vo
Page 843 and 844:
h, or in I-P units For SI units, FI
Page 845 and 846:
When the total pressure loss of the
Page 847 and 848:
TABLE 17.11 Local Loss Coefficients
Page 849 and 850:
Return or Exhaust Duct Systems AIR
Page 851 and 852:
and the sized diameter 0.0147 � 2
Page 853 and 854:
FIGURE 17.25 Rectangular supply duc
Page 855 and 856:
If the height of the rectangular du
Page 857 and 858:
FIGURE 17.28 A return duct system w
Page 859 and 860:
Design Interface AIR SYSTEMS: AIR D
Page 861 and 862:
vacuum used in duct cleaning is oft
Page 863 and 864:
accurate measurement, an inclined m
Page 865 and 866:
AIR SYSTEMS: AIR DUCT DESIGN 17.79
Page 867 and 868:
18.2 CHAPTER EIGHTEEN Design Consid
Page 869 and 870:
18.4 CHAPTER EIGHTEEN cooling load
Page 871 and 872:
18.6 CHAPTER EIGHTEEN FIGURE 18.2 F
Page 873 and 874:
18.8 CHAPTER EIGHTEEN Confined Air
Page 875 and 876:
18.10 CHAPTER EIGHTEEN Free Nonisot
Page 877 and 878:
18.12 CHAPTER EIGHTEEN Ceiling Diff
Page 879 and 880:
18.14 CHAPTER EIGHTEEN Slot Diffuse
Page 881 and 882:
18.16 CHAPTER EIGHTEEN TABLE 18.1 P
Page 883 and 884:
18.18 CHAPTER EIGHTEEN FIGURE 18.12
Page 885 and 886:
18.20 CHAPTER EIGHTEEN 18.4 MIXING
Page 887 and 888:
Page 889 and 890:
Page 891 and 892:
Page 893 and 894:
18.28 CHAPTER EIGHTEEN ● The loca
Page 895 and 896:
18.30 CHAPTER EIGHTEEN ● The aver
Page 897 and 898:
18.32 CHAPTER EIGHTEEN ● Cost. In
Page 899 and 900:
18.34 CHAPTER EIGHTEEN ● A termin
Page 901 and 902:
Page 903 and 904:
18.38 CHAPTER EIGHTEEN The return s
Page 905 and 906:
18.40 CHAPTER EIGHTEEN Ventilating
Page 907 and 908:
18.42 CHAPTER EIGHTEEN 18.8 STRATIF
Page 909 and 910:
18.44 CHAPTER EIGHTEEN 18.9 PROJECT
Page 911 and 912:
18.46 CHAPTER EIGHTEEN Target Veloc
Page 913 and 914:
18.48 CHAPTER EIGHTEEN Application
Page 915 and 916:
18.50 CHAPTER EIGHTEEN Heat Unneutr
Page 917 and 918:
18.52 CHAPTER EIGHTEEN CFD Becomes
Page 919 and 920:
18.54 CHAPTER EIGHTEEN Conducting C
Page 921 and 922:
18.56 CHAPTER EIGHTEEN Wendes, H.,
Page 923 and 924:
19.2 CHAPTER NINETEEN Sound Paths T
Page 925 and 926:
19.4 CHAPTER NINETEEN 9. Check this
Page 927 and 928:
19.6 CHAPTER NINETEEN Branch ducts
Page 929 and 930:
19.8 CHAPTER NINETEEN TABLE 19.3 So
Page 931 and 932:
19.10 CHAPTER NINETEEN End Reflecti
Page 933 and 934:
19.12 CHAPTER NINETEEN 19.4 SILENCE
Page 935 and 936:
19.14 CHAPTER NINETEEN facing. A so
Page 937 and 938:
19.16 CHAPTER NINETEEN Active Silen
Page 939 and 940:
19.18 CHAPTER NINETEEN Recommendati
Page 941 and 942:
19.20 CHAPTER NINETEEN FIGURE 19.6
Page 943 and 944:
19.22 CHAPTER NINETEEN TABLE 19.11
Page 945 and 946:
19.24 CHAPTER NINETEEN Array of Cei
Page 947 and 948:
19.26 CHAPTER NINETEEN Environmenta
Page 949 and 950:
19.28 CHAPTER NINETEEN Octave band
Page 951 and 952:
19.30 CHAPTER NINETEEN Sound Source
Page 953 and 954:
19.32 CHAPTER NINETEEN Structure-Bo
Page 955 and 956:
CHAPTER 20 AIR SYSTEMS: BASICS AND
Page 957 and 958:
Air Distribution Systems Ventilatio
Page 959 and 960:
20.2 BUILDING LEAKAGE AREA AND BUIL
Page 961 and 962:
20.3 SPACE PRESSURIZATION Space Pre
Page 963 and 964:
doors and windows are closed. When
Page 965 and 966:
Wind speed from a meteorological st
Page 967 and 968:
In Eq. (20.8), m˙ inf indicates th
Page 969 and 970:
System Operating Point FIGURE 20.4
Page 971 and 972:
20.6 SYSTEM EFFECT ● Condition 1.
Page 973 and 974:
Inlet System Effect Loss fan inlet
Page 975 and 976:
FIGURE 20.7 Outlet system effect: (
Page 977 and 978:
For a SWSI centrifugal fan with A b
Page 979 and 980:
Two Fan-Duct Systems Connected in S
Page 981 and 982:
volume flow and fan total pressure.
Page 983 and 984:
FIGURE 20.12 Two parallel fan-duct
Page 985 and 986:
Similarly, the residual pressure of
Page 987 and 988:
Modulation of Fan-Duct Systems AIR
Page 989 and 990:
FIGURE 20.14 (Continued) AIR SYSTEM
Page 991 and 992:
Plot the fan performance curve Ft a
Page 993 and 994: 20.9 CLASSIFICATION OF AIR SYSTEMS
Page 995 and 996: To save energy, most AHU and PU man
Page 997 and 998: where ws,wr � humidity ratio at t
Page 999 and 1000: exchanger is called the sensible co
Page 1001 and 1002: compressed air, or ultrasonic force
Page 1003 and 1004: AIR SYSTEMS: BASICS AND CONSTANT-VO
Page 1005 and 1006: FIGURE 20.21 Adiabatic mixing and b
Page 1007 and 1008: and the heating coil load is 20.16
Page 1009 and 1010: Cooling mode operation in summer co
Page 1011 and 1012: 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
Page 1017 and 1018: Air Conditioning Rules Graphical Me
Page 1019 and 1020: FIGURE 20.25 Effect of sensible hea
Page 1021 and 1022: 2. Because the air temperature at t
Page 1023 and 1024: At a temperature of 72°F (22.2°C)
Page 1025 and 1026: Because w m � w s, Therefore, Fro
Page 1027 and 1028: Part-Load Operation 7. Draw a verti
Page 1029 and 1030: Reheating is a simple and effective
Page 1031 and 1032: Operating Parameters and Calculatio
Page 1033 and 1034: REFERENCES AIR SYSTEMS: BASICS AND
Page 1035 and 1036: 21.2 CHAPTER TWENTY-ONE 21.1 SYSTEM
Page 1037 and 1038: FIGURE 21.1 A single-zone VAV syste
Page 1039 and 1040: 21.6 CHAPTER TWENTY-ONE FIGURE 21.2
Page 1041 and 1042: 21.8 CHAPTER TWENTY-ONE Region IV:
Page 1043: 21.10 CHAPTER TWENTY-ONE dry-bulb e
Page 1047 and 1048: 21.14 CHAPTER TWENTY-ONE ● The ou
Page 1049 and 1050: 21.16 CHAPTER TWENTY-ONE outdoor ve
Page 1051 and 1052: 21.18 CHAPTER TWENTY-ONE 7. When T
Page 1053 and 1054: 21.20 CHAPTER TWENTY-ONE VAV Reheat
Page 1055 and 1056: 21.22 CHAPTER TWENTY-ONE FIGURE 21.
Page 1057 and 1058: 21.24 CHAPTER TWENTY-ONE FIGURE 21.
Page 1059 and 1060: 21.26 CHAPTER TWENTY-ONE In dead-ba
Page 1061 and 1062: 21.28 CHAPTER TWENTY-ONE For the pe
Page 1063 and 1064: 21.30 CHAPTER TWENTY-ONE calculated
Page 1065 and 1066: 21.32 CHAPTER TWENTY-ONE For the wi
Page 1067 and 1068: 21.34
Page 1069 and 1070: 21.36 CHAPTER TWENTY-ONE Number of
Page 1071 and 1072: 21.38 CHAPTER TWENTY-ONE Mixing Mod
Page 1073 and 1074: 21.40 CHAPTER TWENTY-ONE ● Modula
Page 1075 and 1076: 21.42 CHAPTER TWENTY-ONE where Q rs
Page 1077 and 1078: 21.44 CHAPTER TWENTY-ONE From Eq. (
Page 1079 and 1080: FIGURE 21.13 (Continued) 21.46
Page 1081 and 1082: 21.48 CHAPTER TWENTY-ONE Fan-Powere
Page 1083 and 1084: 21.50 CHAPTER TWENTY-ONE The drawba
Page 1085 and 1086: 21.52 CHAPTER TWENTY-ONE Zone Contr
Page 1087 and 1088: 21.54 CHAPTER TWENTY-ONE Percentage
Page 1089 and 1090: 21.56 CHAPTER TWENTY-ONE ● During
Page 1091 and 1092: 21.58 CHAPTER TWENTY-ONE Wendes, H.
Page 1093 and 1094: 22.2 CHAPTER TWENTY-TWO 22.1 RETURN
Page 1095 and 1096:
22.4 CHAPTER TWENTY-TWO 22.2 FAN CO
Page 1097 and 1098:
22.6 CHAPTER TWENTY-TWO Recirculati
Page 1099 and 1100:
22.8 CHAPTER TWENTY-TWO flow rate o
Page 1101 and 1102:
22.10 CHAPTER TWENTY-TWO FIGURE 22.
Page 1103 and 1104:
22.12 CHAPTER TWENTY-TWO The system
Page 1105 and 1106:
22.14 CHAPTER TWENTY-TWO to balance
Page 1107 and 1108:
22.16 CHAPTER TWENTY-TWO The fixed
Page 1109 and 1110:
22.18 CHAPTER TWENTY-TWO air is ext
Page 1111 and 1112:
22.20 CHAPTER TWENTY-TWO Air Econom
Page 1113 and 1114:
22.22 CHAPTER TWENTY-TWO (2) The re
Page 1115 and 1116:
Page 1117 and 1118:
Page 1119 and 1120:
22.28 CHAPTER TWENTY-TWO ● The as
Page 1121 and 1122:
Page 1123 and 1124:
22.32 CHAPTER TWENTY-TWO Design Con
Page 1125 and 1126:
22.34 CHAPTER TWENTY-TWO �a � a
Page 1127 and 1128:
22.36 CHAPTER TWENTY-TWO The pressu
Page 1129 and 1130:
22.38 CHAPTER TWENTY-TWO REFERENCES
Page 1131 and 1132:
CHAPTER 23 AIR SYSTEMS: MINIMUM VEN
Page 1133 and 1134:
ASHRAE Standard 62-1999 control, a
Page 1135 and 1136:
The system outdoor air volume flow
Page 1137 and 1138:
CO 2 Sensor or Mixed-Gases Sensor L
Page 1139 and 1140:
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
Page 1159 and 1160:
consumption than proportional contr
Page 1161 and 1162:
Page 1163 and 1164:
Page 1165 and 1166:
REFERENCES AIR SYSTEMS: MINIMUM VEN
Page 1167 and 1168:
24.1 IAQ PROBLEMS CHAPTER 24 IMPROV
Page 1169 and 1170:
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
Page 1179 and 1180:
and final filter in air systems wit
Page 1181 and 1182:
REFERENCES IMPROVING INDOOR AIR QUA
Page 1183 and 1184:
25.2 CHAPTER TWENTY-FIVE energy res
Page 1185 and 1186:
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
Page 1197 and 1198:
25.16 CHAPTER TWENTY-FIVE Unit elec
Page 1199 and 1200:
25.18 CHAPTER TWENTY-FIVE Physical
Page 1201 and 1202:
25.20 CHAPTER TWENTY-FIVE condensin
Page 1203 and 1204:
25.22 CHAPTER TWENTY-FIVE Condenser
Page 1205 and 1206:
25.24 CHAPTER TWENTY-FIVE The polyn
Page 1207 and 1208:
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
Page 1215 and 1216:
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
Page 1225 and 1226:
26.14 CHAPTER TWENTY-SIX Exterior l
Page 1227 and 1228:
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-
Page 1233 and 1234:
27.6 CHAPTER TWENTY-SEVEN TABLE 27.
Page 1235 and 1236:
27.8 CHAPTER TWENTY-SEVEN FIGURE 27
Page 1237 and 1238:
27.10 CHAPTER TWENTY-SEVEN Effectiv
Page 1239 and 1240:
27.12 CHAPTER TWENTY-SEVEN consumpt
Page 1241 and 1242:
50 50 13.0 27.14 40 40 60 60 50 50
Page 1243 and 1244:
27.16 CHAPTER TWENTY-SEVEN Assume t
Page 1245 and 1246:
27.18 CHAPTER TWENTY-SEVEN System C
Page 1247 and 1248:
27.20 CHAPTER TWENTY-SEVEN If the e
Page 1249 and 1250:
27.22 CHAPTER TWENTY-SEVEN coil and
Page 1251 and 1252:
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
Page 1257 and 1258:
Induction Systems annoying. A recei
Page 1259 and 1260:
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
Page 1271 and 1272:
AIR CONDITIONING SYSTEMS: SPACE CON
Page 1273 and 1274:
where w s � humidity ratio of fan
Page 1275 and 1276:
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
Page 1297 and 1298:
d. That is capable of being set bac
Page 1299 and 1300:
volume flow rate when the total pre
Page 1301 and 1302:
FIGURE 29.2 A VAV reheat packaged s
Page 1303 and 1304:
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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