Handbook of air conditioning and refrigeration / Shan K

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FIGURE 21.14 Fan-powered boxes: (a) series box; (b) parallel box, draw-through; (c) parallel box, blow-through. 21.49
21.50 CHAPTER TWENTY-ONE The drawbacks of a parallel fan-powered box include the need for a careful balance of flow and total pressure of two airstreams, the difficulty in selection of the size of the box, and its more complicated controls. The size and capacity of a fan-powered box is determined by the capacity of the fan, the VAV box, and the heating coil. The heating coil in a fan-powered box can be a hot water coil or an electric duct heater located downstream from the fan-powered box. Fan-powered boxes are usually built in sizes corresponding to the associated VAV box primary air volume flow rates from 300 to 3200 cfm (150 to 1600 L/s) and fan supply volume flow rates of 250 to 4000 cfm (125 to 2000 L/s). Most fan-powered boxes have a fan total pressure between 0.5 and 0.8 in. WC (125 and 200 Pa) and an external pressure loss of about 0.25 in. WC (63 Pa) to offset the pressure drop of downstream flexible ducts and diffusers. The pressure drop of the VAV box and the corresponding pressure drop of flexible ducts and diffusers due to cold primary air should be offset by the supply fan in the primary air AHU or PU. The speed of the centrifugal fan in the fan-powered box can be adjusted to high, medium, or low or even variable-speed drive. Both radiated and duct-borne sound paths should be checked to determine whether they can meet the space air required NC criteria. Because the fan total pressure is higher in a fan-powered box than in a fan-coil unit, a temperature rise due to fan power heat gain of 0.75°F (0.4°C) should be considered in psychrometric analysis. The VAV box a in fan-powered box can be either pressure-dependent or pressure-independent. Pressure-independent fan-powered boxes are widely used. Fan Characteristics in Parallel Fan-Powered Boxes In a fan-powered VAV system using a parallel fan-powered box, two fan-duct systems are connected in parallel: the cold primary airstream discharged from the supply fan F1 in the AHU or PU and the recirculating plenum airstream extracted by fan F2, as shown in Fig. 21.15. At the combining point A, the pressures of these two airstreams must be equal, and the volume flow rate is the sum of the volume flow rates of the cold primary air V˙ sn,c and the recirculated plenum air V˙ sn,r. For a control zone in the perimeter zone using a parallel fan-powered box at its zone peak supply volume flow rate with conventional air distribution V˙ sn,d (a supply air temperature of 55°F, or 12.8°C), in cfm (L/s), the distribution is as follows: Zone supply volume flow rate of control zones at summer design conditions Zone supply volume flow of recirculating plenum air from parallel fan-powered box 0 According to Yu et al. (1993), the zone supply volume flow rates of control zones in the interior zone using a parallel fan-powered box with cold air distribution at summer design conditions are as follows: Supply volume flow rate of 44°F (6.7°C) cold primary air, cfm (L/s) Supply volume flow rate from fan-powered box (recirculating plenum air), cfm (L/s) Zone supply volume flow rate for control zones in the perimeter zone at winter heating design conditions must meet the following requirements: Cold primary air for ventilation Supply temperature differential T s � T r 1.0V˙ sn,d 0.6V˙ sn,d 0.4V˙ sn,d 0.3V˙ sn,d � 15°F (8.3°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
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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 and 1044: 21.10 CHAPTER TWENTY-ONE dry-bulb e
Page 1045 and 1046: 21.12 CHAPTER TWENTY-ONE Consider a
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: 21.48 CHAPTER TWENTY-ONE Fan-Powere
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 1119 and 1120: 22.28 CHAPTER TWENTY-TWO ● The as
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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