96372302-heat-load-estimation-e20-form-si.xls 6l3m2i
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E20 HEAT LOAD ESTIMATION FORM SHEET
1 of 1
DATE
PREPARED BY
Khairul Anuar Abd Jabar
NAME OF JOB
D35 Upgrade For HVAC System
LOCATION
Miri Serawak
SPACE USED FOR
Electrical Main Room
SIZE
APPROVED
16.00 ITEM
m2 X
2.50
=
SUN GAIN OR TEMP. DIFF
AREA OR QUANTITY
40.00
FACTOR
ESTIMATE FOR
m3 WATTS
m2 x
x
0.57
NE
GLASS
m2 x
x
0.57
SE
GLASS
x
0.57
SW
GLASS
m2 x
x
0.57
m2 x
x
SKYLIGHT
September 4.00 pm
DB
WB
%RH
10.00
0 DIFFERENCE
OUTDOOR AIR
0 Ventilati 0 on
PEOPLE x
7
l/s
m3 =
40
l/s =
11.11
l/s VENTILATION =
11.11
1 Air change/hr :
SOLAR & TRANS. GAIN - WALLS & ROOF m2 x
10.00
x
3.04
304
NE
WALL
10.00
m2 x
10.00
x
3.04
304
SE
WALL
x
3.04
0
SW
WALL
6.50
m2 x
10.00
x
3.04
198
ROOF - SUN
16.00
m2 x
10.00
x
5.00
800
m2 x
m2 x
x
Infiltratio n
ALL GLASS
3.50
m2 x
10.00
x
5.89
206
PARTITION
10.00
m2 x
10.00
x
1.00
100
FLOOR
16.00
INFILTRATION
1.00
-
x
0
x
1.00
m2 x
10.00
x
0.50
5 Dehum. Rise
2
x
245
490 Dehum. 500 l/s
POWER
0.50
KW
x
LIGHTS
40.00
WATTS
x
APPLIANCES, ETC.
x
ADDITIONAL HEAT GAINS
x
1,000.00 1.25
m2 x
x
(-
)
SAFETY FACTOR
5
%
ROOM SENSIBLE HEAT (RSH) =
OUTDOOR AIR
SUPPLY DUCT LEAK LOSS
%+ 11.11
l/s x
-
%+
FAN H.P.
C
x
0.15
BF x
LATENT HEAT l/s x
PEOPLE
-
STEAM
g/kg
3 205
kg/hr x
APPLIANCES, ETC. ADDITIONAL HEAT GAINS VAPOR TRANS.
x
x 2310
-
C - TADP
x
=
1.00 56.00 C
56.00 C) =
3,293.54 ERSH 1.20
l/s OA
SELECTED ADP =
BF) x 0.15 (T RM
(1 -
(47.60) CDEHUM. RISE
(47.60) C
(57.66) l/s DA
=
3,293.54 RSH = ### C (RM - OUTLET AIR)* 1.20
x
(57.66) l/sDA
1.20
x
(47.60) CDESIRED DIFF
3,293.54 RSH =
(57.66) l/sSA
(57.66) l/s SA
(57.66) l/sDA =
l/sBA
*IF THIS T IS TOO HIGH, DETERMINE SUPPLY CFM FOR DESIRED DIFFERENCE BY SUPPLY AIR QUANTITY FORMULA. RESULTING ENT & LVG CONDITIONS AT APPARATUS TRM
-
C +
C,
-
CTROOM
-
C - TADP TEWB
-
C) = TEDB
-
### C) = TLDB
C
47.60 C C
0 **WHEN BYING A MIXTURE OF OUTDOOR AND RETURN AIR, USE SUPPLY l/s, WHEN BYING 0 RETURN AIR ONLY, USE DEHUMIDIFIED l/s. 0
NOTES
0 SQ.m x
0.01
x
-
g/kg x
0
SUB TOTAL SAFETY FACTOR
10
%
ROOM LATENT HEAT (RLH) = SUPPLY DUCT LEAKAGE LOSS OUTDOOR AIR
-
3,293.54 ERTH 56.00 C
11.11 l/sOA x (TOA ### l/s** C TADP 56.00 0.15 BF x (TEDB + TEWB 0 FROM PSYCH. CHART:
3,294
l/s per m
SUPPLY AIR QUANTITY
3,294
0
-
3,293.54 ERSH
=
INDICATED ADP =
3,137 By 157 l/s
0
-
l/s per door=
mX
3,137 Supply 0 l/s
%
EFFECTIVE ROOM SENSIBLE HEAT (ERSH) =
INFILTRATION
160 ADP
1.2
l/s per person =
EXHAUST FAN
0 Outlet Temp. 0 Diff
SUB TOTAL
SUPPLY DUCT HEAT GAIN
DOORS x
50
SUB TOTAL STORAGE
OPEN DOORS
EFFECTIVE SENSIBLE HEAT FACTOR
ESHF
10.00
INTERNAL HEAT
PEOPLE x
-
l/s INFILTRATION = l/s OUTDOOR AIR THRU APPARATUS = APPARATUS DEW POINT & DEHUMIDIFIED AIR QUANTITY
m2 x
PEOPLE
SWINGING REVOLVING DOORS
CRACK
0
TRAN. GAIN - EXCEPT WALLS & ROOF
m2 x
g/Kg
-
20
10.00
CEILING
10 hours
DP
0 ROOM (RM)
NW WALL
ROOF - SHADED
LOCAL TIME SUN TIME
OUTDOOR (OA)
NW GLASS
m2 x
PEAK LOAD
HOUR/DAY
CONDITIONS
SOLAR GAIN - GLASS
3.50
LOCAL TIME SUN TIME
EQUIPMENT OPERATION
11.11
l/s x
-
g/kg x
0.15
0 0 0
15
%
0
BF x
3
0
EFFECTIVE ROOM LATENT HEAT (ERLH) =
0
EFFECTIVE ROOM TOTAL HEAT (ERTH) =
3,294
OUTDOOR AIR HEAT SENSIBLE
11.11
l/s X
-
Cx
(1-
0.15
BF) x 1.2
0
LATENT
11.11
l/s X RETURN DUCT % RSH + LEAKAGE GAIN
-
g/kg x
(1-
0.15
BF) x
0
RETURN DUCT HEAT GAIN RETURN AIR OR BLOW - THRU FAN
3
% RSH kw. x 1000
GRAND TOTAL HEAT (GTH) OR DEHUMIDIFIER LOAD = UMP H.P.
% GTH +
PIPING HEAT GAIN
% GTH REFRIGERATION LOAD =
0
CHECK FIGURES BTU/HR/SQ.FT =
0 SQ.FT/PERSON = 3,294 VENT. AIR CFM/SQ.FT 0
TOTAL AIR CHANGE
3,294 AIR CONDITIONING LOAD ESTIMATE
65.28 GRAND TOTAL WATT/SQ.FT = TOTAL AIR CFM/SQ.FT MIN. OUTSIDE AIR CHANGE
RM SENS.
MIN.
FORM E - 20 (3 - 72)
1 of 1
DATE
PREPARED BY
Khairul Anuar Abd Jabar
NAME OF JOB
D35 Upgrade For HVAC System
LOCATION
Miri Serawak
SPACE USED FOR
Electrical Main Room
SIZE
APPROVED
16.00 ITEM
m2 X
2.50
=
SUN GAIN OR TEMP. DIFF
AREA OR QUANTITY
40.00
FACTOR
ESTIMATE FOR
m3 WATTS
m2 x
x
0.57
NE
GLASS
m2 x
x
0.57
SE
GLASS
x
0.57
SW
GLASS
m2 x
x
0.57
m2 x
x
SKYLIGHT
September 4.00 pm
DB
WB
%RH
10.00
0 DIFFERENCE
OUTDOOR AIR
0 Ventilati 0 on
PEOPLE x
7
l/s
m3 =
40
l/s =
11.11
l/s VENTILATION =
11.11
1 Air change/hr :
SOLAR & TRANS. GAIN - WALLS & ROOF m2 x
10.00
x
3.04
304
NE
WALL
10.00
m2 x
10.00
x
3.04
304
SE
WALL
x
3.04
0
SW
WALL
6.50
m2 x
10.00
x
3.04
198
ROOF - SUN
16.00
m2 x
10.00
x
5.00
800
m2 x
m2 x
x
Infiltratio n
ALL GLASS
3.50
m2 x
10.00
x
5.89
206
PARTITION
10.00
m2 x
10.00
x
1.00
100
FLOOR
16.00
INFILTRATION
1.00
-
x
0
x
1.00
m2 x
10.00
x
0.50
5 Dehum. Rise
2
x
245
490 Dehum. 500 l/s
POWER
0.50
KW
x
LIGHTS
40.00
WATTS
x
APPLIANCES, ETC.
x
ADDITIONAL HEAT GAINS
x
1,000.00 1.25
m2 x
x
(-
)
SAFETY FACTOR
5
%
ROOM SENSIBLE HEAT (RSH) =
OUTDOOR AIR
SUPPLY DUCT LEAK LOSS
%+ 11.11
l/s x
-
%+
FAN H.P.
C
x
0.15
BF x
LATENT HEAT l/s x
PEOPLE
-
STEAM
g/kg
3 205
kg/hr x
APPLIANCES, ETC. ADDITIONAL HEAT GAINS VAPOR TRANS.
x
x 2310
-
C - TADP
x
=
1.00 56.00 C
56.00 C) =
3,293.54 ERSH 1.20
l/s OA
SELECTED ADP =
BF) x 0.15 (T RM
(1 -
(47.60) CDEHUM. RISE
(47.60) C
(57.66) l/s DA
=
3,293.54 RSH = ### C (RM - OUTLET AIR)* 1.20
x
(57.66) l/sDA
1.20
x
(47.60) CDESIRED DIFF
3,293.54 RSH =
(57.66) l/sSA
(57.66) l/s SA
(57.66) l/sDA =
l/sBA
*IF THIS T IS TOO HIGH, DETERMINE SUPPLY CFM FOR DESIRED DIFFERENCE BY SUPPLY AIR QUANTITY FORMULA. RESULTING ENT & LVG CONDITIONS AT APPARATUS TRM
-
C +
C,
-
CTROOM
-
C - TADP TEWB
-
C) = TEDB
-
### C) = TLDB
C
47.60 C C
0 **WHEN BYING A MIXTURE OF OUTDOOR AND RETURN AIR, USE SUPPLY l/s, WHEN BYING 0 RETURN AIR ONLY, USE DEHUMIDIFIED l/s. 0
NOTES
0 SQ.m x
0.01
x
-
g/kg x
0
SUB TOTAL SAFETY FACTOR
10
%
ROOM LATENT HEAT (RLH) = SUPPLY DUCT LEAKAGE LOSS OUTDOOR AIR
-
3,293.54 ERTH 56.00 C
11.11 l/sOA x (TOA ### l/s** C TADP 56.00 0.15 BF x (TEDB + TEWB 0 FROM PSYCH. CHART:
3,294
l/s per m
SUPPLY AIR QUANTITY
3,294
0
-
3,293.54 ERSH
=
INDICATED ADP =
3,137 By 157 l/s
0
-
l/s per door=
mX
3,137 Supply 0 l/s
%
EFFECTIVE ROOM SENSIBLE HEAT (ERSH) =
INFILTRATION
160 ADP
1.2
l/s per person =
EXHAUST FAN
0 Outlet Temp. 0 Diff
SUB TOTAL
SUPPLY DUCT HEAT GAIN
DOORS x
50
SUB TOTAL STORAGE
OPEN DOORS
EFFECTIVE SENSIBLE HEAT FACTOR
ESHF
10.00
INTERNAL HEAT
PEOPLE x
-
l/s INFILTRATION = l/s OUTDOOR AIR THRU APPARATUS = APPARATUS DEW POINT & DEHUMIDIFIED AIR QUANTITY
m2 x
PEOPLE
SWINGING REVOLVING DOORS
CRACK
0
TRAN. GAIN - EXCEPT WALLS & ROOF
m2 x
g/Kg
-
20
10.00
CEILING
10 hours
DP
0 ROOM (RM)
NW WALL
ROOF - SHADED
LOCAL TIME SUN TIME
OUTDOOR (OA)
NW GLASS
m2 x
PEAK LOAD
HOUR/DAY
CONDITIONS
SOLAR GAIN - GLASS
3.50
LOCAL TIME SUN TIME
EQUIPMENT OPERATION
11.11
l/s x
-
g/kg x
0.15
0 0 0
15
%
0
BF x
3
0
EFFECTIVE ROOM LATENT HEAT (ERLH) =
0
EFFECTIVE ROOM TOTAL HEAT (ERTH) =
3,294
OUTDOOR AIR HEAT SENSIBLE
11.11
l/s X
-
Cx
(1-
0.15
BF) x 1.2
0
LATENT
11.11
l/s X RETURN DUCT % RSH + LEAKAGE GAIN
-
g/kg x
(1-
0.15
BF) x
0
RETURN DUCT HEAT GAIN RETURN AIR OR BLOW - THRU FAN
3
% RSH kw. x 1000
GRAND TOTAL HEAT (GTH) OR DEHUMIDIFIER LOAD = UMP H.P.
% GTH +
PIPING HEAT GAIN
% GTH REFRIGERATION LOAD =
0
CHECK FIGURES BTU/HR/SQ.FT =
0 SQ.FT/PERSON = 3,294 VENT. AIR CFM/SQ.FT 0
TOTAL AIR CHANGE
3,294 AIR CONDITIONING LOAD ESTIMATE
65.28 GRAND TOTAL WATT/SQ.FT = TOTAL AIR CFM/SQ.FT MIN. OUTSIDE AIR CHANGE
RM SENS.
MIN.
FORM E - 20 (3 - 72)
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