Duct Design
April 23, 2017 | Author: pvanper | Category: N/A
Short Description
Download Duct Design...
Description
Duct Design Example No.(1) By Badran M. Salem
DESIGN OF AIR DUCT DESIGN CONDITIONS:
Inside room conditions Temperature -----------------------------------------------------------------------------------------------------------
22 oC DB
16 o C WB
Outside room conditions Temperature ----------------------------------------------------------------------------------------------------------Temperature of supply air Mass of outside air,mo
34 o C DB 27 oC WB
----------------------------------15 OC ----------------------------------10 % of mS
Mass of recirculated air, mR
------------------------- 90 % of mS
Air Properties From ASHRAE PSYCHROMETRIC CHART, M.E.T.C, page 75 Outside room conditions, @ 32 O C DB & 27 o C WB
1
Duct Design Example No.(1) By Badran M. Salem
WO 0.0199
kgv m3 kJ ; O 0.898 ; hO 85.6 kgda kg kg
Inside room conditions, @ 22 O C DB & 16 o C WB WO 0.0089
kgv m3 kJ ; O 0.848 ; hO 45 kgda kg kg
Mass of supply air, mS Qs = mS c pa ( t r - t s ) ; mS =
Qs c pa (t r - t s )
Where: mS = mass of supply air c pa
= specific heat of air, 1.0062 kJ kg °K
tr
= inside room temperature, 22 C
t s = supply air temperature, 15 °C
Therefore, mS
230.037 kW kg 32.66 sec kJ 1.0062 22 - 15 O K O kg K
Mass of outside air, mO mS = m1 = m4 ; mo + mR
Where: mS = mass of supply air, 32.66 kg s
mR = mass of recirculated air, 90 % of mS
Therefore, mO mS 1 0.9 32.66 kg sec 1 0.9 3.266 kg sec
2
Duct Design Example No.(1) By Badran M. Salem
Volume flow rate of outside air, Vo VO = mO O
Where: mO = mass of outside air, 3.266 kg s
O = specific volume of outside air, 0.898 m 3 kg
Therefore, kg m3 m3 2.93 VO 3.266 0.898 sec kg sec
Mass of recirculated air, mR mS mo mR ; mR mS
mO
Where: mS = mass of supply air, 32.66 kg s mO = mass of outside air, 3.266 kg sec
Therefore, mR 32.66 kg sec 3.266 kg sec 29.39 kg sec
Volume flow rate of recirculated air, VR V R = m R υi
Where: m R = mass of recirculated air, 29.39 kg s υ i = specific volume of inside air, 0.848 m 3 kg
Therefore, kg m3 m3 VR 29.39 24.93 0.848 sec kg sec
3
Duct Design Example No.(1) By Badran M. Salem
Temperature of air entering the AHU, t2 From the figure, considering point 2
By temperature balance, mo t O mR t 4 mS t 2 ; t 2
Where: mO = mass of outside air, 3.266 kg sec
t O = temperature of outside air, 34 O C
m R = mass of recirculated air, 29.93 kg s t 4 = inside air temperature, 22 o C mS = mass of supply air, 32.66 kg s
Therefore, t2
3.266 kg
sec 34 O C 29.93 kg sec 22 O C 23.56 O C 32.66 kg sec
Capacity of AHU, QAHU QCDA = mS (h4 - h1 )
Where: mS = mass of supply air, 32.66 kg s
h4 = enthalpy of air entering the AHU, kJ kg h1 = enthalpy of air leaving the AHU, kJ kg
4
mo t O mR t 4 mS
Duct Design Example No.(1) By Badran M. Salem
Enthalpy of air entering the AHU, h2 From the figure, considering point 2
By heat balance, mo hO mR h4 mS h2 ; h2
mo hO mR h4 mS
Where: mO = mass of outside air, 3.266 kg sec hO = enthalpy of outside air, 85.6 kJ kg
m R = mass of recirculated air, 29.93 kg s
h4 = enthalpy of recirculated air, 45 kJ kg mS = mass of supply air, 32.66 kg s
Therefore, h4
3.266 kg sec85.6 kJ
kg 29.93 kg sec45 kJ kg kJ 49.8 32.66 kg sec kg
Enthalpy of air leaving the AHU, h3 QT mS h4 - h3 ; h3 h4 -
QT mS
Where: QT = total heat load, 476.228 kWT mS = mass of supply air, 32.66 kg s
h4 = enthalpy of inside air, 45 kJ kg
5
Duct Design Example No.(1) By Badran M. Salem
Therefore, h3 45
kJ 476.228 kWT kJ 30.42 kg 32.66 kg sec kg
Thus, kg kJ Q AHU 32.66 632.9 kW or 179.98 TOR 49.8 - 30.42 sec kg
Volume of supply air, VS VS = m S υ1
Where: mS = mass of supply air, 32.66 kg s
υ1 = specific volume of supply air, m3 kg
From ASHRAE PSYCHROMETRIC CHART, M.E.T.C, page 75 @ 15 O C DB & h1 30.42 kJ kg
1 0.824
m3 kg
Therefore,
VS 32.66 kg sec 0.824 m 3 kg 26.9
m3 sec
AIR DUCT SIZING DESIGN CONDITIONS: Volume flow rate of supply air ------------------------------ 26.9 m 3 sec Duct dimensions
----------------------------------------------
No. of units
------------------------------------------------ 2
6
W = 4H
Duct Design Example No.(1) By Badran M. Salem
No. of branch take-off
---------------------------------------------
5
No. of outlet per branch take off------------------------------------
4
Method of calculation-----------------------------------------------------Fitting Data Elbow, inner & outer radii ratio --------------------------
0.2
Angle, turns and branches-----------------------------------
90 O
Volume flow rate of supply air per branch take-off, QB QB
VS 26.9 m 3 sec m3 5.38 Number o Branch Take off 5 sec
Volume flow rate of supply air per outlet, Q O QO
Volume Flow Rate of Supply Air per Branch Take - off 5.38 m 3 sec m3 1.345 Number of Outlets 4 sec
7
Duct Design Example No.(1) By Badran M. Salem
Duct Sizes For the main duct, from the fan outlet to point O,
From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107. For a volume flow rate of supply air of, QFO 26.9 m 3 s and a P 1.5 Pa m , Deq. f 1.436 m .
From equation 6-8, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 108 Deq. f
0.625 ab 1.30 a b0.25
Where: a = H = height of the rectangular duct, m b = W = width of the rectangular duct, m
Substituting, W 4H to the equation above
8
Duct Design Example No.(1) By Badran M. Salem
Deq. f
0.625 HW 1.30 H W 0.25
4H 1.30
2 0.625
5H 0.25
0.625 4 H 1.25 1.30 0.25 0.25 5 H
2.0677 H
Thus, H 0.4836 Deq. f working equation
For the height, H FO H FO 0.4836 1.436 m 0.694 m
For the width, WFO WFO 4 0.694 m 2.78 m
For the size of duct, AFO AFO H FO x WFO 0.694 m x 2.78 m 1.93 m2 1930 mm2
Run O to A, two branch take – off supplied
From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107. For a volume flow rate of supply air of, QOA 26.9 m3 s and a P 1.5 Pa m , Deq. f 1.436 m .
9
Duct Design Example No.(1) By Badran M. Salem
Therefore, H OA 0.4836 1.436 m 0.694 m WOA 4 0.694 m 2.78 m AOA H OA x WOA 0.694 m x 2.78 m 1.93 m 2 1930 mm2
Run A to B, two branch take – off supplied
From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107. For a volume flow rate of supply air of,
QOB 5.38 m3 s 4 21.52 m 3 s P 1.5 Pa m ,
Deq. f 1.306 m
Therefore, H OB 0.4836 1.306 m 0.6316 m WOB 4 0.324 m 2.52 m AOB H OB x WOB 0.6316 m x 2.52 m 1.59 m 2
11
Duct Design Example No.(1) By Badran M. Salem
Run B to C, 3 Branch take – off supplied,
From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107. For a volume flow rate of supply air of, QBA ( 5.38 m3 s )(3) 16.14 m3 s P 1.5 Pa m ,
Deq. f 1.186 m
Therefore, H BA 0.4836 1.186 m 0.5735 m
WBC 4 0.5735 m 2.29 m ABA H BA x WBA 0.5735 m x 2.29 m 1.316 m 2
11
Duct Design Example No.(1) By Badran M. Salem
Run C to D, 4 branch take – off supplied
From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107.
QOC 5.38 m 3 s 2 10.76 m3 s & P 1.5 Pa m , Deq. f 0.966 m
Therefore, H OC 0.4836 0.966 m 0.467 m WOC 4 0.467 m 1.868 m AOC H OC x WOC 0.467 m x1.868 m 0.873 m 2
Run D to E, 5 branch take - off supplied
12
Duct Design Example No.(1) By Badran M. Salem
From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107. QCD 5.38 m 3 s & P 1.5 Pa m , Deq. f 0.756 m
Therefore, H CD 0.4836 0.756 m 0.3656 m WCD 4 0.3656 m 1.46 m ACD H CD x WCD 0.3656 m x1.46 m 0.5338 m 2
Branch outlet dimensions Note: Since the number of outlets in each branch take – off are equal for the whole system, only one branch take – off will be considered in computing for the duct dimensions and the values obtained will be replicated in all seven (7) branch outlets.
Considering Branch Take – off A,
13
Duct Design Example No.(1) By Badran M. Salem
Run A – 1, 4 outlets supplied From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107. For a volume flow rate of supply air of, QA1 5.38 m3 s P 1.5 Pa m ,
Deq. f 0.756 m
Therefore, H A1 0.4836 0.756 m 0.3656 m WA1 4 0.3656 m 1.4624 m
AA1 H A1 x WA1 0.3656 m x 1.4624 m 0.5347 m 2
Run 1 – 2, 3 outlets supplied From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107. For a volume flow rate of supply air of,
Q12 1.345 m3 s 3 4.035 m3 s
P 1.5 Pa m ,
Deq. f 0.7 m
Therefore, H12 0.4836 0.7 m 0.33852 m W12 4 0.33852 m 1.354 m
A12 H12 x W12 0.33852 m x 1.354 m 0.4584 m 2 14
Duct Design Example No.(1) By Badran M. Salem
Run 2 – 3, 2 outlets supplied From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107. For a volume flow rate of supply air of,
Q23 1.345 m3 s 2 2.69 m3 s
P 1.5 Pa m ,
Deq. f 0.58 m
Therefore, H 23 0.4836 0.58 m 0.28 m W23 4 0.28 m 1.122 m A23 H 23 x W23 0.28 m x 1.122 m 0.314 m 2
Run 3 – 4, 1 outlets supplied From figure 6-2, Pressure drop in straight, circular, sheet metal ducts, REFRIGERATION AND AIRCONDITIONING by Stoecker & Jones, page 107. For a volume flow rate of supply air of, Q34 1.345 m3 s P 1.5 Pa m ,
Deq. f 0.43 m
Therefore, H 34 0.4836 0.43 m 0.208 m W34 4 0.208 m 0.832 m A34 H 34 x W34 0.208 m x 0.832 m 0.173 m 2
15
Duct Design Example No.(1) By Badran M. Salem
Air Velocity, υ Q = A υ; υ =
Q A
Where: υ = velocity of air, m s Q = volume
of supply air, m 3 s
A = area of the air duct, m 2
Branch take - off From fan outlet to branch take – off O, FO FA
QF 0 26.9 m3 sec 13.937 m sec AF 0 1.93 m 2
Where: QFO = 26.9 m 3 s
AFO = 1.93 m 2
Run A-B, AB AB
Q AB 21.52 m 3 sec 13.53 m sec AAB 1.59 m 2
Where: Q AB = 21.52 m 3 s
16
Duct Design Example No.(1) By Badran M. Salem
AAB = 1.59 m 2
Run B -C, BC BC
QBC 16.14 m 3 sec 12.26 m sec ABC 1.316 m 2
Where: QBC = 16.14 m 3 s ABC = 1.316 m 2
Run C - D, CD CD
QCD 10.76 m 3 sec 12.325 m sec ACD 0.873 m 2
Where: QCD = 10.76 m 3 s ACD = 0.873 m 2
Run D - E, υ DE DE
QDE 5.38 m 3 sec 10.078 m sec ADE 0.5338 m 2
Where: Q DE = 5.38 m 3 s
ADE = 0.5338 m 2
17
Duct Design Example No.(1) By Badran M. Salem
Branch Outlets Note: Since the number of outlets in each branch take – off are equal for the whole system, only one branch take – off will be considered in computing for the duct velocities and the values obtained will be replicated in all seven (7) branch outlets.
Run A - 1, υ A1 A1
Q A1 5.38 m 3 sec 10.06 m sec AA1 0.5347 m 2
Where: Q A1 = 5.38 m 3 s AA1 = 0.5347 m 2
Run 1 - 2, υ12 12
Q12 4.035 m 3 sec 8.802 m sec A12 0.4584 m 2
Where: Q12 = 4.035 m 3 s A12 = 0.4584 m 2
18
Duct Design Example No.(1) By Badran M. Salem
Run 2 - 3, υ23 23
Q23 2.69 m 3 sec 8.57 m sec A23 0.314 m 2
Where: Q23 = 2.69 m 3 s A23 = 0.314 m 2
Run 3 - 4, υ34 34
Q34 1.345 m 3 sec 7.77 m sec A34 0.173 m 2
Where: Q34 = 1.345 m 3 s A34 = 0.173 m 2
Determination of Pressure Drops Considering the Run FOA A1 A2 A3 A4
Run FO, Straight Duct 19
Duct Design Example No.(1) By Badran M. Salem
PFO LFO P m 4.6387 m 1.5 Pa m 6.958 Pa
Run O, Turn From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.20 2 ΔPTOB (vOB )2 (ρair ) = 0.25
Where: 3
ρair = density of supply air, kg / m
vOB = velocity of air in run O, 13.937 m / sec
From table 6 – 2, Viscosity and Density of dry air at standard atmospheric pressure, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 106 Temperature Viscosity , Density , O C kg / m3 Pa - s 10 17.708 1.2467 20 18.178 1.2041 Since the temperature of the supply air is at 15 0C, by interpolation, @ 15 C = 1.2254 kg / m3 Therefore, POT
2 vOB air 0.25
2
13.937 m 0.25
Run OA, Straight Duct POA LOA P m 10.4360 m 1.5 Pa m 15.654 Pa
Branch take – off A, Turn
21
sec 1.2254 kg m3 2 2
29.75 Pa
Duct Design Example No.(1) By Badran M. Salem
From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.20 2 PAT
v AT 2 air
0.25
Where: 3
ρair = density of supply air, 1.2254 kg / m
v AT = velocity of air in run OA, 13.937 m / sec
Therefore, PAT 0.25
vOB 2 air 2
0.25
13.937 m
2
Run AA1, Straight Duct PAA1 LAA1 P m 2.1703 m 1.5 Pa m 3.255 Pa
Run AA2, Straight Duct PAA2 LAA2 P m 5.7749 m 1.5 Pa m 8.6623 Pa
Run AA3, Straight Duct PAA3 LAA3 P m 9.613 m 1.5 Pa m 14.4195 Pa
Run AA4, Straight Duct PAA4 LAA4 P m 12.4634 m 1.5 Pa m 18.6951 Pa
21
sec 1.2254 kg m3 2
29.75 Pa
Duct Design Example No.(1) By Badran M. Salem
Therefore, PFOA 4 PFO POT POA PAT PAA1 PAA2 PAA3 PAA4
6.958 29.75 15.654 29.75 3.225 8.6623 14.4195 18.6951 Pa PFOBA 7 127.1439 Pa
Considering the Run FOBB1B 2 B3 B 4
Run FO, Straight Duct PFO LFO P m 4.6387 m 1.5 Pa m 6.958 Pa
Run O, Turn From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.29 2 PTOB
vTO 2 air
0.25
Where: 3
ρair = density of supply air, 1.2254 kg / m
22
Duct Design Example No.(1) By Badran M. Salem
vTO = velocity of air in run OB, 13.937 m / sec
Therefore, PTO 0.25
vTO 2 air 2
0.25
13.937 m
sec 1.2254 kg m3 2 2
29.75 Pa
Branch take – off A, Duct Straight Through From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114 PDST A
2 VOA air 0.41 VOA
PDST A
2 13.53 m sec 1.2254 0.41
2
2
V AB
2
13.53 13.937
2
PDST A 0.038 Pa
Run OB, Turn From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.29 2 PTOB
vTOB 2 air
0.25
Where: 3
ρair = density of supply air, 1.2254 kg / m
vTOB = velocity of air in run OB, 13.53 m / sec
Therefore, PTOB
2 vTOB air 0.25
2
13.53 m 0.25
23
sec 1.2254 kg m3 2 2
28.04 Pa
Duct Design Example No.(1) By Badran M. Salem
Run OB, Straight Duct POB LOB P m 18.136 m 1.5 Pa m 27.204 Pa
Run BB1, Straight Duct PBB1 LBB1 P m 2.3628 m 1.5 Pa m 3.5442 Pa
Run BB2, Straight Duct PBB 2 LBB 2 P m 5.9674 m 1.5 Pa m 8.9511 Pa
Run BB3, Straight Duct PBB3 LBB3 P m 9.8055 m 1.5 Pa m 14.708 Pa
Run BB4, Straight Duct PBB 4 LBB 4 P m 12.6559 m 1.5 Pa m 18.9838 Pa
Therefore,
24
Duct Design Example No.(1) By Badran M. Salem
PFOBB 1B 2 B3B 4 PFO PTO PDSTA PTOB POB PBB1 PBB 2 PBB 3 PBB 4
6.958 29.75 0.038 28.04 27.204 3.5442 8.9511 14.708 18.9838 Pa
PFOBA 7 138.1771 Pa
Considering the Run FOCC1C 2C 3C 4
Run FO, Straight Duct PFO LFO P m 4.6387 m 1.5 Pa m 6.958 Pa
Run O, Turn From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.29 2 PTOB
vTO 2 air
0.25
Where: 3
ρair = density of supply air, 1.2254 kg / m
vTO = velocity of air in run OB, 13.937 m / sec
25
Duct Design Example No.(1) By Badran M. Salem
Therefore, PTO 0.25
vTO 2 air 2
0.25
13.937 m
sec 1.2254 kg m3 2 2
29.75 Pa
Branch take – off A, Duct Straight Through From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114 PDST A
V 2 air 0.41 VOA OA
PDST A
13.53 m sec2 1.2254 0.41
2
2
V AB
2
13.53 13.937
2
PDST A 0.038 Pa
Branch take – off B, Duct Straight Through From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114 PDSTB
V 2 air 0.41 VOB BC
PDSTB
2 2 12.26 m sec 1.2254 12.26 0.4 1
PDSTB
2
2 0.03245 Pa
2
VBC
13.53
Run OC, Turn From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.29
26
Duct Design Example No.(1) By Badran M. Salem
2 PTOC
vTOC 2 air
0.25
Where: 3
ρair = density of supply air, 1.2254 kg / m
vTOC = velocity of air in run OB, 12.26 m / sec
Therefore, PTOC 0.25
vTOC 2 air 2
0.25
12.26 m
sec 1.2254 kg m3 2 2
Run OC, Straight Duct POC LOC P m 25.836 m 1.5 Pa m 38.754 Pa
Run CC1, Straight Duct PCC1 LCC1 P m 2.4153 m 1.5 Pa m 3.623 Pa
Run CC2, Straight Duct PCC2 LCC2 P m 6.0199 m 1.5 Pa m 9.02985 Pa
Run CC3, Straight Duct PCC3 LCC3 P m 9.858 m 1.5 Pa m 14.787 Pa
Run CC4, Straight Duct PCC4 LCC4 P m 12.7084 m 1.5 Pa m 19.0626 Pa
27
23.0234 Pa
Duct Design Example No.(1) By Badran M. Salem
Therefore,
PFOCC1C 2C 3C 4 PFO PTO PDSTA PDSTB PTOC POC PCC1 PCC2 PCC3 6.958 29.75 0.038 0.03245 23.0234 38.754 3.623 Pa 9.02985 14.787 19.0626 PFOCC1C 2C 3C 4 145.0583 Pa
Considering the Run FODD1D 2 D3 D 4
Run FO, Straight Duct PFO LFO P m 4.6387 m 1.5 Pa m 6.958 Pa
Run O, Turn From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.29 2 PTOB
vTO 2 air
0.25
Where:
28
Duct Design Example No.(1) By Badran M. Salem 3
ρair = density of supply air, 1.2254 kg / m
vTO = velocity of air in run OB, 13.937 m / sec
Therefore, PTO
2 vTO air 0.25
2
13.937 m 0.25
sec 1.2254 kg m3 2 2
Branch take – off A, Duct Straight Through From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114 PDST A
V 2 air 0.41 VOA OA
PDST A
13.53 m sec2 1.2254 0.41
2
2
V AB
2
13.53 13.937
2
PDST A 0.038 Pa
Branch take – off B, Duct Straight Through From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114 PDSTB
2 VBC air 0.41 VOB
PDSTB
2 2 12.26 m sec 1.2254 12.26 0.4 1
PDSTB
2
2 0.03245 Pa
2
VBC
13.53
Branch take – off C, Duct Straight Through From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114 29
29.75 Pa
Duct Design Example No.(1) By Badran M. Salem
PDSTC
2 VOC air 0.41 VOC
PDSTC
2 2 12.325 m sec 1.2254 12.325 0.4 1
PDSTC
2
2
VBC
2 0.001046 Pa
12.26
Run OD, Turn From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.29 2 PTOD
vTOD 2 air
0.25
Where: 3
ρair = density of supply air, 1.2254 kg / m
vTOD = velocity of air in run OD, 12.325 m / sec
Therefore, PTOD
2 vTOD air 0.25
2
12.325 m 0.25
sec 1.2254 kg m3 2 2
Run OD, Straight Duct POD LOD P m 33.536 m 1.5 Pa m 50.304 Pa
Run DD1, Straight Duct PDD1 LDD1 P m 1.9931 m 1.5 Pa m 2.9896 Pa
31
23.268 Pa
Duct Design Example No.(1) By Badran M. Salem
Run DD2, Straight Duct PDD2 LDD2 P m 5.904 m 1.5 Pa m 8.856 Pa
Run DD3, Straight Duct PDD3 LDD3 P m 8.6386 m 1.5 Pa m 12.9579 Pa
Run DD4, Straight Duct PDD4 LDD4 P m 11.1831 m 1.5 Pa m 16.7746 Pa
Therefore, PFODD1D 2 D3D 4 PFO PTO PDSTA PDSTB PDSTD PTOD POD PDD1 PDD 2
P
6.958 29.75 0.038 0.03245 0.001046 23.268 50.304 Pa 2.9896 8.856 12.9579 16.7746 151.932 Pa 2 3 4
FODD1D D D
Considering the Run FOEE1E 2 E 3 E 4
31
Duct Design Example No.(1) By Badran M. Salem
Run FO, Straight Duct PFO LFO P m 4.6387 m 1.5 Pa m 6.958 Pa
Run O, Turn From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.29 2 PTOB
vTO 2 air
0.25
Where: 3
ρair = density of supply air, 1.2254 kg / m
vTO = velocity of air in run OB, 13.937 m / sec
Therefore, PTO 0.25
vTO 2 air 2
0.25
13.937 m
sec 1.2254 kg m3 2 2
Branch take – off A, Duct Straight Through From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114
32
29.75 Pa
Duct Design Example No.(1) By Badran M. Salem
PDST A
2 VOA air 0.41 VOA
PDST A
2 13.53 m sec 1.2254 0.41
2
2
V AB
2
13.53 13.937
2
PDST A 0.038 Pa
Branch take – off B, Duct Straight Through From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114 PDSTB
2 VOB air 0.41 VOB
PDSTB
2 2 12.26 m sec 1.2254 12.26 0.4 1
PDSTB
2
2
VBC
2 0.03245 Pa
13.53
Branch take – off C, Duct Straight Through From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114 PDSTC
2 VOC air 0.41 VOC
PDSTC
2 2 12.325 m sec 1.2254 12.325 0.4 1
PDSTC
2
2 0.001046 Pa
2
VCD
12.26
Branch take – off D, Duct Straight Through
33
Duct Design Example No.(1) By Badran M. Salem
From Equation 6 – 16, REFRIGERATION and AIRONDITIONING by Stoecker & Jones, page 114 PDSTD
2 VOD air 0.41 VOD
2
PDSTD
2
VDE
10.078 m sec2 1.2254 0.41 10.078 2
2
12.325
PDSTD 0.827 Pa
Run OE, Turn From figure 6 – 8, Pressure losses in rectangular elbows, REFRIGERATION and AIRCONDITONING by: Stoecker & Jones, page 113 For a width to height ratio (W/H) equal to 4, inner and outer radius ratio of 0.29 2 PTOE
vTOE 2 air
0.25
Where: 3
ρair = density of supply air, 1.2254 kg / m
vTOE = velocity of air in run OD, 10.078 m / sec
Therefore, PTOE 0.25
vTOE 2 air 2
0.25
10.078 m
2
Run OE, Straight Duct POE LOE P m 41.236 m 1.5 Pa m 61.854 Pa
34
sec 1.2254 kg m3 2
15.557 Pa
Duct Design Example No.(1) By Badran M. Salem
Run EE1, Straight Duct PEE1 LEE1 P m 2.1971 m 1.5 Pa m 3.295 Pa
Run EE2, Straight Duct PEE 2 LEE 2 P m 5.5437 m 1.5 Pa m 8.316 Pa
Run EE3, Straight Duct PEE 3 LEE 3 P m 8.4626 m 1.5 Pa m 12.6939 Pa
Run EE4, Straight Duct PEE 4 LEE 4 P m 11.20005 m 1.5 Pa m 16.8 Pa
Therefore,
PFOEE 1E 2 E 3 E 4 PFO PTO PDSTA PDSTB PDSTC PDSTD PTOE POE PEE 1 PEE 2 PEE 3 6.958 29.75 0.038 0.03245 0.001046 0.827 15.557 61.854 Pa 3 . 295 8 . 316 12 . 6939 16 . 8 P 1 2 3 4 156.122 Pa FOEE E E E
35
View more...
Comments