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Copyright © 2005, ASHRAE
ASHRAE HANDBOOK
Additions and Corrections
This report includes additional information and technical errors To cool from 18 to 4°C in a chilled room:
found between June 15, 2002, and April 1, 2005, in the SI editions 
of the 2002, 2003, and 2004 ASHRAE Handbook volumes. Occa-
sional typographical errors and nonstandard symbol labels will be 
corrected in future volumes. The most current list of Handbook addi-
tions and corrections is on the ASHRAE Web site (www.ashrae.org).
The authors and editor encourage you to notify them if you 
find other technical errors. Please send corrections to: Handbook 
Editor, ASHRAE, 1791 Tullie Circle NE, Atlanta, GA 30329, or 
e-mail mowen@ashrae.org. 
2002 Refrigeration
p. 2.2, Figs. 1 and 2. In the captions, replace “ton of refrigeration” 
with “kilowatt of refrigeration.”
p. 2.4, Example 1, Solution. The correct calculations are as follows:
p. 2.10, 2nd col. In the first sentence under Refrigerant Line 
Capacity Tables, replace “tons of refrigeration” with “kilowatts of 
refrigeration.”
p. 2.16, Example 2. In the Solution, the reference to Table 10 
should be to Table 16.
p. 8.5, Table 3. The specific heats above and below freezing for 
bacon should both be 2.70 kJ/(kg·K); for whole cured lean ham 
they should be 3.47 and 2.22 kJ/(kg·K), respectively.
p. 8.8, Eq. (18). The equation should read as follows:
p. 8.9, 2nd col., 3rd equation. Delete the 3 directly to the right of 
the equals sign.
p. 10.9, Table 2. Delete the entry for “Maple syrup.”
p. 12.1, 1st col., 5th line from bottom. Change “15 mph” to 
“25 km/h.”
p. 12.1, 2nd col. In the first full paragraph, change “These values 
decrease” to “These values increase.”
p. 12.2, Example 1. The solution should be as follows:
Specific heat of beef before freezing is listed in Table 3, Chapter 8 
as 3.52 kJ/(kg · K); after freezing, 2.12 kJ/(kg · K). 
Actual temperature drop = (50 × 0.02) 
× (14.0/21.54)1.8
= 0.46 K
Estimated friction loss = 0.46 (50 × 0.749) = 17.2 kPa
Loss for the riser = 6 × 11.3 = 67.8 kPa
Total pressure losses = 67.8 + 17.2 = 85.0 kPa
Saturation pressure at 40°C condensing 
 (see R-22 properties in Chapter 20, 2001 ASHRAE 
 Handbook—Fundamentals)
= 1534.1 kPa
Initial pressure at beginning of liquid line 1534.1 kPa
Total liquid line losses − 85.0 kPa
Net pressure at expansion device = 1449.1 kPa
The saturation temperature at 1449.1 kPa is 37.7°C.
Required subcooling to overcome the liquid losses = (40.0 – 37.7) 
or 2.3 K
H t tr–( ) 1.55 1.26xs
xwa xb–( )Lotf
trt
----------------------------------–+⎝ ⎠
⎛ ⎞=
A
100 × 3.52(18 − 4) = 4928 kJ
To cool from 4°C to freezing point in freezer:
100 × 3.52[4 − (−2)] = 2112 kJ
To freeze: 100 × 233 = 23 300 kJ
To cool from freezing to storage temperature:
100 × 2.12[(−2) − (−18)] = 3392 kJ
Total: 4928 + 2112 + 23 300 + 3392 = 33 732 kJ
p. 12.7, Infiltration Load values. Delete “°C” from the definitions 
for hf, hr, and ρr; for ρi, the entire definition should read only “den-
sity incoming air, kg/m3.”
p. 16.10, 2nd col. The next to the last sentence under Fresh Pork 
Holding should read, “Care must be taken to maintain the ratio of 
kilograms of CO2 to kilograms of meat for the retention period.”
p. 7.14, Fig. 17. The viscosity data are for 38°C, in mm2/s.
p. 22.7, Airflow Requirements. The units for cp should be J/(kg·K), 
and the symbol for mass flow rate of air should be .
p. 25.2, 16th line. Change “metre” to “cubic metre.”
p. 30.2, Controls. Change “several hundred feet” to “hundreds of 
metres.”
p. 31.3, 2nd col., 4th line. The text in parentheses should read 
“(i.e., a total area of 3.0 m2 and a capacity of 0.33 m3).”
p. 34.3, Example 2 values. Change the unit for Ceiling radiating 
area from “mm2” to “m2.”
p. 38.21, Fig. 30. Along the x axis, change “100” to “102.”
p. I.30, Index. Add the following entry after Load coefficients: 
Louvers, F30.45 
sizing, F34.17-18
2003 HVAC Applications
p. 1.4, Evaporative Cooling. The reference to Chapter 50 should be 
to Chapter 51.
p. 8.2, Indoor Air Quality, 4th line. Delete “by a minimum of 
1.5 K.”
p. 9.2, Power Consumption and Availability. Change “to main-
tain gas mileage” to “for minimum vehicle fuel use.”
p. 13.6. Reverse the order of Figures 6 and 7.
p. 13.10, Example 1. The unit for total floor area should be m2.
p. 16.9, Semiconductor Cleanrooms, 1st paragraph. Insert 
“(0.0283 m3)” after “cubic foot.”
p. 16.10, Airflow in Semiconductor Cleanrooms, 4th para-
graph. Change “horsepower” to “kilowatt.”
p. 16.13, Temperature and Humidity, 3rd paragraph. If full-
coverage smocks are not used, temperature set points can be higher, 
not lower.
Ch. 17. This chapter has been reassigned to TC 9.9, which recom-
mends using ASHRAE’s Thermal Guidelines for Data Processing 
Environments (2004) as a primary source of information for data 
processing environment design.
m·
.1
A.2 2005 ASHRAE Handbook—Fundamentals (SI)
p. 23.7, Fig. 8. The bottom part of the figure was cut off; refer to the 
full version here.
p. 26.7, 2nd line from bottom. Change “only a very few grains of 
moisture” to “very little moisture.”
p. 27.2, Adiabatic Compression. In the second paragraph, change 
“1.84W” to “1.884W.” In the definitions for Equation (1), units for 
E should be 1 kJ/(102 m·kg). In Example 1, units for the solution 
should be kW.
p. 27.6. Step 6 should read, “The enthalpy of air hai at 28°C satu-
rated and 104.983 kPa is 109 kJ/kg. Σai = 109 – (4.1868)(0.037) 
(28) = 104.66 kJ/kg.”
p. 27.10, 2nd col., 5th full paragraph. Change “calorific” to 
“heat.” In Equation (18), change “Btu/h” to “kW.”
p. 27.11, Eq. (19). Rt should be turbulent resistance.
p. 31.5, Type II Hoods, Condensate hood. The second and third sen-
tences for this item should read, “The hood is designed to direct the 
condensate toward a perimeter gutter for collection and drainage, 
allowing none to drip onto the appliance below. Flow rates are typi-
cally based on 255 to 380 L/s per square metre of hood opening.”
p. 31.11, Traditional Registers. Terminal velocities should be 
≤0.25 m/s.
p. 32.4, 2nd col., last paragraph. In the second sentence, velocity 
should be limited to a maximum of 0.03 m/s.
p. 32.6, 2nd col., 4th paragraph. Change “flashing” to “flushing.” 
The units for free residual chlorine content should be mg/kg.
p. 33.22, 1st col. In the third line under Equation (38), change “KJ” 
to “kJ.”
p. 34.2, Lower Initial Cost, 3rd paragraph. Change “660 W” to 
“660 kW.”
Fig. 8 Grain Recirculators Convert Bin Dryer to
High-Speed Continuous-Flow Dryer
(2003 HVAC Applications, Chapter 23, p. 7)
p. 36.3, Table 3. Add the following footnote:
3. For updated information on heat pump life, see Lovvorn and Hiller (2002).
p. 36.9, 1st column, 3rd line. The subscript for PWF should be “ser.”
p. 36.13, References. Add the following source after Lovvorn and 
Hiller (1985):
Lovvorn, N.C. and C.C. Hiller. 2002. Heat pump life revisited. ASHRAE 
Transactions 108(2):107-112.
p. 41.28, Case Study, 2nd paragraph. Change “3200 KW” to 
“3200 kW.”
p. 45.6, 2nd col., end of 1st paragraph. The correct Research 
Project is RP-1134 (Tompkins 2002).
p. 45.13, References. Delete Idem 2002 and insert the following 
source after Sterling and Kabayashi 1981:
Tompkins, D. 2002. Evaluation of photocatalytic air cleaning capability. 
ASHRAE Research Project RP-1134.
p. 47.15, Tables 8 and 9. The titles for Tables 8 and 9 should read 
“with 25 mm Fiberglass Lining” and “with 50 mm Fiberglass Lin-
ing,” respectively.
p. 47.22, Table 22. In the footnote, change “1.5 pcf” to “24 kg/m3.”
p. 47.23, Ex. 3. Change “5 ft” to “1.52 m.”
p. 47.41, 1st col., 3rd paragraph. Change “12 m/s” to “1.2 m/s.”
p. 49.6, Fig. 7. The arrow for “Union (typical)” should point to the 
union symbol, not the gate valve symbol. The correct figure is pre-
sented here.
p. 50.1, Snow-Melting Heat Flux Requirement. The fourth list 
item should be “wind speed near the heated surface.”
p. 51.7, Cooling Large Motors,3rd paragraph. Delete “hour” 
after “kilowatt.”
p. 53.3, Fig. 3. Delete the entire note below the figure.
p. 53.9, Symbols. Delete the entries for “clo” and “met.”
p. 54.4, Eqs. (7) and (8). In the definitions for Wp, delete “in new-
tons = mass.”
p. 54.12, 1st col., 4th line from bottom. Change “??°C” to 
“590°C.”
p. I.4, Index. Add “F15.12” to the entries for BAS and Building 
automation system.
2004 HVAC Systems and Equipment
p. 2.5, Fig. 8. The caption for Figure 9 should read “Chemical 
Dehumidification.”
p. 6.7, Table 1. The complete table is supplied here. 
Fig. 7 Reverse/Return Manifold Systems
(2003 HVAC Applications, Chapter 49, p. 6)
Additions and Corrections A.3
p. 7.22, 1st col., 13th line from bottom. Change “horsepower” to 
“power.”
p. 7.23, Turbocharger Heat Recovery. Delete “(280 kJ/kWh).”
p. 8.5, Fig. 5. The top two figures, for air/air and water/air refriger-
ant changeover, were cut off. The two figures are provided here.
Table 1 Thermal Resistance of Ceiling Panels
(2004 HVAC Systems and Equipment, Ch. 6, p. 7)
Thermal Resistance
Type of Panel
rp ,
(m2·K)/W
rs ,
(m2·K)/W
0.32
0.38
0.10
≤ 0.12 
xp
kp
-----
xp
kp
-----
xp
kp
-----
xp Do /– 2
kp
----------------------- 0≈
xp Do /– 2
kp
-----------------------
p. 12.9, Fig. 16. The figure for reverse-return two-pipe systems was 
incorrect; the corrected version is provided here.
p. 24.2, 1st two lines. Change “15 to 35 cfm” to “7 to 16.5 L/s,” and 
“15 cfm” to “7 L/s.”
p. 25.4, Eq. (5). There should be an equals symbol after Dpc.
p. 25.21, Tables 8 and 9. Delete “g·” from the units for KGa.
p. 31.3, 2nd equation. The unit for qc should be W.
p. 34.31, Symbols. Delete the definition for gc.
p. 35.19, Purging, 2nd paragraph. Change “Chapters 35 and 38 of 
this volume” to “Chapter 38 of this volume.”
p. 36.4, Fig. 9. Change “350 to 500 ft” to “100 to 150 m.”
p. 36.14, Fig. 25. The corrected figure is supplied on p. A.4.
p. 44.10, Fig. 5. Replace with the corrected figure, supplied on p. A.4.
Fig. 16 Direct- and Reverse-Return Two-Pipe Systems
(2004 HVAC Systems and Equipment, Ch. 12, p. 9)
Fig. 5 Heat Pump Types (first two rows)
(2004 HVAC Systems and Equipment, Ch. 8, p. 5)
A.4 2005 ASHRAE Handbook—Fundamentals (SI)
p. 44.19, Ex. 4, Step 7. The reference to Figure 17 should be to Fig-
ure 19.
p. 44.25, Bibliography. The correct entry for the ASHRAE (1974) 
source is as follows:
ASHRAE. 1974. Symposium on heat recovery. ASHRAE Transactions
80(1):302-332.
Index. The following are the correct page numbers for these entries:
Compressors, heat pump systems, S8.6 
Control, heat recovery systems, S8.18 
Defrosting, air-source heat pump coils, S8.7, 8; S45.9 
Heat balance (HB), studies, S8,19 
Heat pumps (all subentries with S1 should be S8) 
Heat recovery (all subentries with S1 should be S8) 
Fig. 5 Variation of Pressure Drop and Effectiveness with Air 
Flow Rates for a Membrane Plate Exchanger
(2004 HVAC Systems and Equipment, Ch. 44, p. 10)
Industrial applications, heat pumps, S8.8 
Net positive suction, S39.9 
Refrigerant control devices, R45 
 heat pumps, system, S8.7 
Solar energy, heat pump systems, S8.4
Fig. 25 Cooling Tower Performance—167% Design Flow
(2004 HVAC Systems and Equipment, Ch. 36. p. 14)
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	2002 Refrigeration
	2003 HVAC Applications
	Fig. 7 Reverse/Return Manifold Systems
	Fig. 8 Grain Recirculators Convert Bin Dryer to High-Speed Continuous-Flow Dryer
	2004 HVAC Systems and Equipment
	Table 1 Thermal Resistance of Ceiling Panels
	Fig. 16 Direct- and Reverse-Return Two-Pipe Systems
	Fig. 5 Heat Pump Types (first two rows)
	Fig. 5 Variation of Pressure Drop and Effectiveness with Air Flow Rates for a Membrane Plate Exchanger
	Fig. 25 Cooling Tower Performance-167% Design Flow