4 Cooling Load Calculation
4.1 Space Heat Gain and
Space Cooling Load
Space heat gain is the rate at which heat
enters a space, or heat generated within a space during a time interval.
Space cooling load is the rate at which
heat is removed from the conditioned space to maintain a constant space air temperature.
Figure 3 shows the difference between the
space heat gain and the space cooling load. The difference between the space heat gain and
the space cooling load is due to the storage of a portion of radiant heat in the
structure. The convective component is converted to space cooling load instantaneously.
Figure 3 Differences between Space Heat Gain and Space Cooling Load
4.2 Cooling Load Temperature
Difference (CLTD) and Cooling Load Factor (CLF)
Cooling load temperature difference and
cooling load factor are used to convert the space sensible heat gain to space sensible
cooling load.
4.2.1 Cooling Load Temperature Difference
The space sensible cooling load Qrs is
calculated as:
(5)
where A = area of external wall or roof
U = overall heat transfer coefficient of
the external wall or roof.
CLTD values are found from tables, as shown
in Tables 1 and 2, which are designed for fixed conditions of outdoor/indoor temperatures,
latitudes, etc. Corrections and adjustments are made if the conditions are different.
4.2.2 Cooling Load Factor
The cooling load factor is defined as:
(6)
CLF is used to determine solar loads or
internal loads. Some CLF values are shown in Table 3.
Table 1 Cooling Load Temperature Difference
for Conduction through Window Glass
Solar
time, hour
|
1
|
2
|
3
|
4
|
5
|
6
|
7
|
8
|
9
|
10
|
11
|
12
|
13
|
14
|
15
|
16
|
17
|
18
|
19
|
20
|
21
|
22
|
23
|
24
|
CLTD,oC
|
1
|
0
|
-1
|
-1
|
-1
|
-1
|
-1
|
0
|
1
|
2
|
4
|
5
|
7
|
7
|
8
|
8
|
7
|
7
|
6
|
4
|
3
|
2
|
2
|
1
|
The values are calculated for an inside
temperature (Ti) of 25.5oC and outdoor daily mean temperature (Tom) of 29.4oC.
Correct CLTD = CLTD + (25.5 - Ti) + (Tom -
29.4)
Table 2 Cooling Load Temperature Difference (40 degree
North Latitude in July) for Roof
and External Walls (Dark)
Solar
time, hour
|
1
|
2
|
3
|
4
|
5
|
6
|
7
|
8
|
9
|
10
|
11
|
12
|
13
|
14
|
15
|
16
|
17
|
18
|
19
|
20
|
21
|
22
|
23
|
24
|
Roof
|
14
|
12
|
10
|
8
|
7
|
5
|
4
|
4
|
6
|
8
|
11
|
15
|
18
|
22
|
25
|
28
|
29
|
30
|
29
|
27
|
24
|
21
|
19
|
16
|
External
wall
North
North-east
East
South-east
South
South-west
West
North-west
|
8
9
11
11
11
15
17
14
|
7
8
10
10
10
14
15
12
|
7
7
8
9
8
12
13
11
|
6
6
7
7
7
10
12
9
|
5
5
6
6
6
9
10
8
|
4
5
5
5
5
8
9
7
|
3
4
5
5
4
6
7
6
|
3
4
5
5
4
5
6
5
|
3
6
7
5
3
5
5
4
|
3
8
10
7
3
4
5
4
|
4
10
13
10
4
4
5
4
|
4
11
15
12
5
5
5
4
|
5
12
17
14
7
5
6
5
|
6
13
18
16
9
7
6
6
|
6
13
18
17
11
9
8
7
|
7
13
18
18
13
12
10
8
|
8
14
18
18
15
15
12
10
|
9
14
18
18
16
18
17
12
|
10
14
17
17
16
20
10
15
|
11
13
17
17
16
21
11
17
|
11
13
16
16
15
21
12
18
|
10
12
15
15
14
20
11
17
|
10
11
13
14
13
19
11
16
|
9
10
12
12
12
17
19
15
|
The values are calculated for an inside
temperature of 25.5oC and outdoor daily mean temperature of 29.4oC.
Correction values for 22 degree north
latitude in July are as follows:
Roof: +0.4oC
Wall: N NE E SE S SW W NW
+1.8oC +1.5oC -0.4oC -2.3oC -3.6oC -2.3oC
-0.4oC +1.5oC
Table 3 Cooling Load Factor for Window Glass
with Indoor Shading Devices
(North Latitude and All Room Construction)
Solar
time,
hour
|
1
|
2
|
3
|
4
|
5
|
6
|
7
|
8
|
9
|
10
|
11
|
12
|
13
|
14
|
15
|
16
|
17
|
18
|
19
|
20
|
21
|
22
|
23
|
24
|
Orientation:
North
North-east
East
South-east
South
South-west
West
North-west
Horizontal
|
0.08
0.03
0.03
0.03
0.04
0.05
0.05
0.05
0.06
|
0.07
0.02
0.02
0.03
0.04
0.05
0.05
0.04
0.05
|
0.06
0.02
0.02
0.02
0.03
0.04
0.04
0.04
0.04
|
0.06
0.02
0.02
0.02
0.03
0.04
0.04
0.03
0.04
|
0.07
0.02
0.02
0.02
0.03
0.03
0.03
0.03
0.03
|
0.73
0.56
0.47
0.30
0.09
0.07
0.06
0.07
0.12
|
0.66
0.76
0.72
0.57
0.16
0.11
0.09
0.11
0.27
|
0.65
0.74
0.80
0.74
0.23
0.14
0.11
0.14
0.44
|
0.73
0.58
0.76
0.81
0.38
0.16
0.13
0.17
0.59
|
0.80
0.37
0.62
0.79
0.58
0.19
0.15
0.19
0.72
|
0.86
0.29
0.41
0.68
0.75
0.22
0.16
0.20
0.81
|
0.89
0.27
0.27
0.49
0.83
0.38
0.17
0.21
0.85
|
0.89
0.26
0.24
0.33
0.80
0.59
0.31
0.22
0.85
|
0.86
0.24
0.22
0.28
0.68
0.75
0.53
0.30
0.81
|
0.82
0.22
0.20
0.25
0.50
0.81
0.72
0.52
0.71
|
0.75
0.20
0.17
0.22
0.35
0.81
0.82
0.73
0.58
|
0.78
0.16
0.14
0.18
0.27
0.69
0.81
0.82
0.42
|
0.91
0.12
0.11
0.13
0.19
0.45
0.61
0.69
0.25
|
0.24
0.06
0.06
0.08
0.11
0.16
0.16
0.16
0.14
|
0.18
0.05
0.05
0.07
0.09
0.12
0.12
0.12
0.12
|
0.15
0.04
0.05
0.06
0.08
0.10
0.10
0.10
0.10
|
0.13
0.04
0.04
0.05
0.07
0.09
0.08
0.08
0.08
|
0.11
0.03
0.03
0.04
0.06
0.07
0.07
0.07
0.07
|
0.10
0.03
0.03
0.04
0.05
0.06
0.06
0.06
0.06
|
4.3 Space Cooling Loads
Space cooling load is classified into three
categories:
4.3.1 External Cooling Loads
External cooling loads have the following
components:
4.3.1.1 Solar Heat Gain through
Fenestration Areas, Qfes
(7)
where As = unshaded area of window glass
Ash = shaded area of window glass
max. SHGFsh = maximum solar heat gain
factor for the shaded area on window glass (Table 4)
max. SHGF = maximum solar heat gain factor
for window glass (Table 5)
SC = shading coefficient (Table 6)
The corresponding space cooling load Qfs
is:
(8)
Table 4 Maximum Solar Heat Gain Factor of
Shaded Area
Month |
Jan. |
Feb. |
Mar. |
Apr. |
May |
June |
July |
Aug. |
Sept. |
Oct. |
Nov. |
Dec. |
SHGFsh, W/m2 |
98 |
107 |
114 |
126 |
137 |
142 |
142 |
133 |
117 |
107 |
101 |
95 |
Table 5 Maximum Solar Heat Gain Factor for Sunit Glass on Average
Cloudness Days
Month
|
Maximum solar heat gain factor for 22 degree north latitude, W/m2
|
|
North
|
North-east
/
north-west
|
East /
west
|
South-east
/
south-west-
|
South
|
Horizontal
|
January.
February.
March.
April
May
June
July
August
September
October
November
December
|
88
97
107
119
142
180
147
123
112
100
88
84
|
140
265
404
513
572
589
565
502
388
262
142
101
|
617
704
743
719
687
666
671
694
705
676
606
579
|
789
759
663
516
404
355
391
496
639
735
786
790
|
696
578
398
210
139
134
140
223
392
563
686
730
|
704
808
882
899
892
880
877
879
854
792
699
657
|
Table 6 Shading Coefficient for Window Glasses with Indoor Shading
Devices
Window
glass
|
Nominal
thickness,
mm
|
Solar
transmission
|
Shading coefficient
|
|
|
|
Venetian
|
Roller shade, opaque
|
Draperies, light colour
|
|
|
|
Medium
|
Light
|
Dark
|
White
|
Openb
|
Closedb
|
Clear
|
3 - 12
|
0.78 - 0.79
|
0.64
|
0.55
|
0.59
|
0.25
|
0.65
|
0.45
|
Heat-absorbing
|
5 - 6
|
0.46
|
0.57
|
0.53
|
0.45
|
0.30
|
0.49
|
0.38
|
Heat-absorbing
|
10
|
0.34
|
0.54
|
0.52
|
0.40
|
0.28
|
|
|
Reflective
coated
SCa=0.30
SCa=0.40
SCa=0.50
SCa=0.60
|
|
|
0.25
0.33
0.42
0.50
|
0.23
0.29
0.38
0.44
|
|
|
0.23
0.33
0.41
0.49
|
0.21
0.28
0.34
0.38
|
Insulating
glass:
|
|
|
|
|
|
|
|
|
Clear
out-clear in
SCa=0.84
|
6
|
0.80
|
0.57
|
0.51
|
0.60
|
0.25
|
0.56
|
0.42
|
Heat
absorbing out-clear in
SCa=0.55
|
6
|
0.56
|
0.39
|
0.36
|
0.40
|
0.22
|
0.43
|
0.35
|
Reflective
SCa=0.20
SCa=0.30
SCa=0.40
|
6
|
0.80
|
0.19
0.27
0.34
|
0.18
0.26
0.33
|
|
|
0.18
0.27
0.36
|
0.16
0.25
0.29
|
a Shading coefficient with no shading device.
b Open weave means 40% openness, and closed weave indicate 3% openness.
Table 7 Overall Heat Transfer Coefficient for Window Glasses
Window
Glass
|
Overall heat transfer coefficient, W/m2K
|
|
Summer (outdoor wind velocity = 3.33m/s)
|
Winter (outdoor wind velocity = 6.67m/s)
|
|
3 mm
thickness
|
5 mm
thickness
|
6 mm
thickness
|
12 mm
thickness
|
3 mm
thickness
|
5 mm
thickness
|
6 mm
thickness
|
12 mm
thickness
|
Single-glazed
Reflective
Double-glazed 6mm airspace
Double glazed 12mm airspace
|
5.4
3.2
2.8
|
5.2
3.0
2.7
|
5.0
4.7
2.9
2.6
|
4.3
|
6.1
3.1
2.7
|
5.7
2.9
2.6
|
5.4
5.0
2.8
2.4
|
4.6
|
4.3.1.2 Conduction Heat Gain
through Fenestration Areas, Qfe
The space cooling load due to the
conduction heat gain through fenestration area is calculated as:
(9)
where A = fenestration area
U = overall heat transfer coefficient for
window glass (Table 7)
CLTD = cooling load temperature difference
(Table 1)
4.3.1.3 Conduction Heat Gain through Roofs
(Qrs) and External Walls (Qws)
The space cooling load due to the
conduction heat gain through roofs or external walls is calculated as:
(10)
where A = area for external walls or roofs
U = overall heat transfer coefficient for
external walls or roof
CLTD = cooling load temperature difference
(Table 2)
4.3.1.4 Conduction Heat Gain through
Interior Partitions, Ceilings and Floors, Qic
The space cooling load due to the
conduction heat gain through interior partitions, ceilings and floors is calculated as:
(11)
where A = area for interior partitions,
ceilings or floors
U = overall heat transfer coefficient for
interior partitions, ceilings or floors
Tb = average air temperature of the
adjacent area
Ti = indoor air temperature
4.3.2 Internal Cooling Loads
4.3.2.1 Electric Lighting
Space cooling load due to the heat gain
from electric lights is often the major component for commercial buildings having a larger
ratio of interior zone. Electric lights contribute to sensible load only. Sensible heat
released from electric lights is in two forms:
(i) convective heat from the lamp, tube and
fixtures.
(ii) radiation absorbed by walls, floors,
and furniture and convected by the ambient air after a time lag.
The sensible heat released (Qles) from
electric lights is calculated as:
(12)
where Input = total light wattage obtained
from the ratings of all fixtures installed
Fuse = use factor defined as the ratio of
wattage in use possibly at design condition to the installation condition
Fal = special allowance factor for
fluorescent fixtures accounting for ballast loss, varying from 1.18 to 1.30
The corresponding sensible space cooling
load (Qls) due to heat released from electrical light is:
(13)
CLF is a function of
(i) number of hours that electric lights
are switched on (for 24 hours continuous lighting, CLF = 1), and
(ii) types of building construction and
furnishings.
Therefore, CLF depends on the magnitude of
surface and the space air flow rates.
4.3.2.2 People
Human beings release both sensible heat and
latent heat to the conditioned space when they stay in it. The space sensible (Qps) and
latent (Qpl) cooling loads for people staying in a conditioned space are calculated as:
(14)
(15)
where n = number of people in the
conditioned space
SHG = sensible heat gain per person (Table
8)
LHG = latent heat gain per person (Table 8)
Adjusted values for total heat shown in
Table 8 is for normal percentage of men, women and children of which heat released from
adult female is 85% of adult male, and that from child is 75%.
CLF for people is a function of
(i) the time people spending in the
conditioned space, and
(ii) the time elapsed since first entering.
CLF is equal to 1 if the space temperature
is not maintained constant during the 24-hour period.
Table 8 Heat Gain from Occupants at Various Activities (At Indoor Air
Temperature of 25.5 oC)
Activity
|
Total heat, W
|
Sensible
heat, W
|
Latent
heat, W
|
|
Adult,
male
|
Adjusted
|
|
|
Seated at
rest
Seated, very light work, writing
Seated, eating
Seated, light work, typing,
Standing, light work or walking slowly,
Light bench work
Light machine work
Heavy work
Moderate dancing
Athletics
|
115
140
150
185
235
255
305
470
400
585
|
100
120
170b
150
185
230
305
470
375
525
|
60
65
75
75
90
100
100
165
120
185
|
40
55
95
75
95
130
205
305
255
340
|
b Adjusted for latent heat of 17.6W person released from food.
4.3.2.3 Power Equipment
and Appliances
In estimating a cooling load, heat gain
from all heat-producing equipment and appliances must be taken into account because they
may contribute to either sensible or latent loads, and sometimes both. The estimation is
not discussed in this lecture note. For more information, Chapter 26 of ASHARE Handbook -
1993 Fundamentals can be referred.
4.3.3 Loads from Infiltration and
Ventilation
Infiltration load is a space cooling load
due to the infiltrated air flowing through cracks and openings and entering into a
conditioned room under a pressure difference across the building envelope. The
introduction of outdoor ventilation air must be considered in combination with the
infiltrated air. Table 9 shows the summer outdoor design dry bulb and wet bulb
temperatures at 22 degree north latitude.
Infiltration and ventilation loads consist
of both sensible and latent cooling loads. Eqns (3) and (4) are valid to estimate the
sensible and latent cooling loads respectively.
Table 9 Summer Outdoor Design Dry Bulb
And Wet Bulb Temperatures At 22 Degree North Latitude
Solar
time, hour
|
1
|
2
|
3
|
4
|
5
|
6
|
7
|
8
|
9
|
10
|
11
|
12
|
13
|
14
|
15
|
16
|
17
|
18
|
19
|
20
|
21
|
22
|
23
|
24
|
Dry bulb
temp. oC
|
28.4 |
28.3 |
28.2 |
28.1 |
28.0 |
28.0 |
28.2 |
29.0 |
29.9 |
30.8 |
31.8 |
32.2 |
32.8 |
33.0 |
32.7 |
32.5 |
31.8 |
31.1 |
30.4 |
29.7 |
29.1 |
28.8 |
28.6 |
28.4 |
Wet bulb
temp. oC
|
25.8 |
25.7 |
25.7 |
25.6 |
25.6 |
25.5 |
25.7 |
26.4 |
26.7 |
27.0 |
27.5 |
27.6 |
27.8 |
28.0 |
27.9 |
27.6 |
27.4 |
27.1 |
26.8 |
26.7 |
26.5 |
26.3 |
26.1 |
25.9 |
|