Redesign dan Recalculation High Pressure Heater (HPH) 7 PT. PJB UP Paiton pada Zona Subcooled Menggunakan Analisa Termodinamika dan Perpindahan Panas
Dhany Ahmad Barkah 2107 100 143
Dosen Pembimbing
Dr. Eng. Ir. Prabowo, M.Eng
WTP
Latar Belakang
• Kerusakan pada tube.
Latar Belakang
• Kerusakan pada baffle. • Kerusakan pada shell.
Latar Belakang
• Replugging hampir 10% dari total tube.
Latar Belakang
Kerusakan pada HPH 7
Turunnya efisiensi termal pembangkit
Konsumsi batubara semakin meningkat
Semakin besarnya biaya operasi
Perlu redesign dan recalculation
Tujuan Perancangan
• Mendapatkan dimensi zona subcooled.
• Mendapatkan
karakteristik tekanan dan kecepatan yang diizinkan.
• Mendapatkan performa dari HPH 7
Dimensi Subcooled
PENELITIAN TERDAHULU
Irfan S. Husaini, Syed M. Zubair, M. A.
Antar (2005)
Irfan S. Husaini, Syed M. Zubair,
M. A. Antar (2005)
Mohammed A. Antar, Syed M. Zubair
(2006)
Simin Wang, Jian Wen, Yanzhong Li (2008)
METODOLOGI
FLOWCHART PERANCANGAN
HPH 7
A
B
C
Asumsi Overall heat transfer coefficient Subcooling (Uas,sub)
1300 ≤ Uas,sub ≤ 2500
Asumsi Overall heat transfer coefficient Condensing (Uas,cond)
1000 ≤ Uas,cond ≤ 4000 Menghitung Luas Perpan Subcooling (Asub) Menghitung Luas Perpan Condensing (Acond)
Menghitung Panjang tube Subcooling Menghitung Panjang tube Condensing
Menghitung Diameter Dalam Shell (IDshell)
Menghitung Crossflow Area pada Subcooling
Zone Menghitung Crossflow Area pada Condensing
Zone
Menghitung Shell Side Mass Velocity
Subcooling Zone Menghitung Shell Side Mass Velocity Condensing Zone
Menghitung Kecepatan Maksimum Fluida sisi Shell, Subcooling
Menghitung Reynolds Max sisi Shell, Subcooling
Menghitung Nusselt number Subcooling
Menghitung Koefisien Konveksi sisi Shell, Subcooling
Menghitung Koefisien Konveksi sisi Shell, Condensing sub
sub as
sub
sub U LMTD
A Q
, ascond cond
cond
cond U LMTD
A Q
,
Nt do L A
tube sub
sub
Nt do L A
tube cond
cond
2 2
637 .
0 do N PR
CTP
IDshell CL tube t
1
Nb
L
As sub ID shell cond
cond cond
cond
cond As
Vs m
sub sub
sub
sub As
Vs m
sub tube
sub Vs
do ST
V ST
max
sub tube sub sub sub
do d V
max
max Re
Re max Pr 31 13
.
1 sub
m sub sub
sub C d
Nu
sub sub sub
sub do
k ho Nu
4 1
, ,
3 ' 729
.
0
tube cold mean hot sat f
fg l v l l
cond N T T do
h k ho g
1
Nb
L
As cond IDshell cond
START
INPUT :
1. Feedwater : - Temp. Inlet feedwater - Temp. outlet feedwater - Laju alir massa feedwater - Tekanan kerja feedwater 2. Heating Steam : - Temp. Inlet steam
- Laju alir massa steam - Tekanan kerja steam - Temp. outlet steam
Dapatkan :
Properti feedwater sisi tube
Properti steam sisi shell
Hitung Tx1 dan Tx2
Input Dimensi :
- Bahan tube K tube dari asumsi - Jumlah laluan Ni dari asumsi - Layout tube dari asumsi
- Tube Pitch
- Asumsi kecepatan dalam tube
A
Menghitung Laju Perpindahan Panas :
Menghitung ∆LMTD Masing-masing Zona
E
2 . . 2
4 4 1
di v Nt m
Nt di
m v
) (
) (
) (
) (
sup
liquid f
steam sub
f g steam
konden
g steam steam
de
ci co c
c
h h m
q
h h m
q
h h
m q
T T Cp m
q
fo 1i
i o 1
subcooling f
1 f
2 g
1 f 2
g condensasi
Tc Th
Tx ln Th
Tc Th Tx
ΔTLMTD Th
Tx Th
Tx ln Th
Tx Th Tx
ΔTLMTD Th
1 (1 2)1/2 2 Cr Cr
22 11//22 ) 1 ( exp 1
) 1 ( exp
1
Cr NTU
Cr NTU
1 (1 2)1/2 2 Cr Cr
22 11//22 ) 1 ( exp
1
) 1 ( exp
1
Cr NTU
Cr NTU
D
Hitung :
- Kapasitas panas fluida panas (Ch) - Kapasitas panas fluida dingin (Cc)
Cc< Ch
h c
r C
C C
Hitung :
- Rasio kapasitas panas
- NTU
- Effektiveness
Cc
NTU UA
c h
r C
C C
Hitung :
- Rasio kapasitas panas
- NTU
- Effektiveness
Ch
NTU UA
YES NO
∆P ≤ 1.5 E
YES NO
Menghitung pressure drop sisi tube Pressure drop major
Pressure drop minor
mnor
major p
p
p
di v L f
pmajor 2
2 1
180 , ,
,entr mnorext mnorreturn mnor
mnor p p p
p
, 2 2
1 v k pmnorentr
, 2 2
1 v k pmnorext
2 180
, 2
1 v k pmnorreturn
04 . 0
k
1
k
2.
0
k
Finish
FLOWCHART PERHITUNGAN
VARIASI KECEPATAN DALAM TUBE
START
Variasi kecepatan Uas,sub
V1 = 1.8 m/s Uas,cond
V2 = 2.1 m/s ρ
V3 = 2.44 m/s di
V4 = 3 m/s
Vi = V1
2
4 di v Nt m
i
Menghitung Luas Perpan Subcooling (Asub) Menghitung Luas Perpan Condensing (Acond)
Menghitung Panjang tube Subcooling Menghitung Panjang tube Condensing
Menghitung Reynolds Number Sisi Tube
Menghitung Nusselt number Sisi Tube
Menghitung Koefisien Konveksi Sisi Tube
Menghitung pressure drop sisi tube Pressure drop major
Pressure drop minor
mnor
major p
p
p
di v L f
pmajor 2
2 1
180 , ,
,entr mnor ext mnor return
mnor
mnor p p p
p
, 2 2
1 v k pmnor entr
, 2
2 1 v k pmnor ext
2 180
, 2
1 v k
pmnor return
04 . 0
k
1 k
2 . 0 k
AA
1
i
i V
V AB
sub sub
as
sub
sub U LMTD
A Q
,
Nt do
L A
tube sub
sub
cond cond
as
cond
cond U LMTD
A Q
,
Nt do
L A
tube cond
cond
tube tube tube tube tube
di d V
Re
4 . 0 5
/
4 Pr
Re 023 ,
0 tube tube
Nutube
tube tube tube
tube di
k
hi Nu
m
AA
Vi < V4 AB
Grafik hi & ∆p vs Re
FINISH
Ya
Tidak
FLOWCHART PERHITUNGAN
VARIASI JUMLAH BAFFLE
START
- Kecepatan optimal,Vtube - Lsubcooled
- Nb1 = 1 - Nb3 = 4 - Nb2 = 2
Menghitung Diameter Dalam Shell (IDshell)
Nbi = Nb1
) 1
(
Nbi B Lsubcooled
Menghitung Crossflow Area pada Subcooling Zone
Menghitung Shell Side Mass Velocity Subcooling Zone
Menghitung Kecepatan Maksimum Fluida sisi Shell, Subcooling
Menghitung Reynolds Max sisi Shell, Subcooling
Menghitung Nusselt number Subcooling
Menghitung Koefisien Konveksi sisi Shell, Subcooling
- Menghitung nilai pressure drop sisi shell zona condensing
- Menghitung nilai pressure drop sisi shell zona subcooled
s De N Ds Gs pshell cond f
. 10 22 . 5
1 .
2 1
10 2
,
v f N
pshellsub L
2
max2 ,
Menghitung Crossflow Area pada Condensing Zone
Menghitung Shell Side Mass Velocity Condensing Zone
Menghitung Koefisien Konveksi sisi Shell, Condensing
BB
1 BA
i
i Nb
Nb
2 2
637 .
0 do N PR
CTP
IDshell CL tube t
T shell
sub S
C B
As ID
sub sub
sub
sub As
Vs m
cond shell
cond ID L
As 0.5
cond cond
cond
cond As
Vs m
sub tube
sub Vs
do ST
V ST
max
sub tube sub sub
sub
do d V
max
max Re
Re max Pr 31 13
.
1 sub
m sub sub
sub C d
Nu
sub sub sub
sub do
k
ho Nu
4 1
, ,
3 ' 729
.
0
tube cold mean hot sat f
fg l v l l
cond N T T do
h k ho g
FLOWCHART PERHITUNGAN NTU &
ε
ANALISA TERMODINAMIKA
Control Volume HPH 7
m
𝑚 =125.280 Kg/hr T = 349 °C P =41,9 Kg/cm²
𝑚 = 1.351,2 Kg/hr
T = 206 °C 𝑚 = 1.351,2 Kg/hr
T = 250 °C
𝑚 = 125.280 Kg/hr
T = 215 °C
properties of steam
T inlet (C) 349 T outlet (C) 215 Pressure (bar) 41.58
h inlet (J/kg) 3085200 h outlet (J/kg) 920940
34.8 T sat 252.63 hg(J/kg) 2798400 hf (J/kg) 1098200 𝑚 h(kg/s)
properties of water
T inlet (C) 206 T rata-rata (C) 228 T outlet (C) 250 ρ (kg/m3) 843.1 Pressure (bar) 193.19 k (W/m.K) 0.6607
h inlet (J/kg) 886680 µ 1.21E-04 h outlet (J/kg) 1087400 Pr 0.835727
375.32 Tx1 (C) 209.6256293 Cp (J/kg.K) 4533.2 Tx2 (C) 244.1338684
𝑚 (kg/s)
𝑄 = 𝑚 𝑠𝑡𝑒𝑎𝑚 𝑜𝑡,𝑖 − 𝑜𝑡,𝑜
𝑄 = 34.8𝑘𝑔𝑠 (3085200 − 920940)𝑘𝑔𝐽 𝑄 = 75316248𝐽𝑠
𝑄𝑐 = 𝑚 𝑐𝑜𝑙𝑑𝐶𝑝𝑐𝑜𝑙𝑑 𝑇𝑐𝑜𝑙𝑑,𝑜 − 𝑇𝑐𝑜𝑙𝑑,𝑖 𝑄𝑐 = 375.32𝑘𝑔𝑠 𝑥 4533.2𝑘𝑔 𝐶𝐽 𝑥 (250 − 206) 𝐶𝑜
𝑄𝑐 = 74861627.46𝐽𝑠
ANALISA TERMODINAMIKA
Feedwater in Feedwater out Steam in
Steam out Zona desuperheating
Zona condensing
Zona subcooled
𝑄𝑑𝑒𝑠𝑢𝑝 = 𝑚 𝑠𝑡𝑒𝑎𝑚 𝑜𝑡,𝑖 − 𝑔
𝑄𝑑𝑒𝑠𝑢𝑝 = 34.8𝑘𝑔𝑠 3085200 − 2798400 𝑘𝑔𝐽 𝑄𝑑𝑒𝑠𝑢𝑝 = 9980640 J/s
𝑄𝑐𝑜𝑛𝑑 = 𝑚 𝑠𝑡𝑒𝑎𝑚 𝑔 − 𝑓
𝑄𝑐𝑜𝑛𝑑 = 34.8𝑘𝑔𝑠 2798400 − 1098200 𝑘𝑔𝐽 𝑄𝑐𝑜𝑛𝑑 = 59166960 J/s
𝑄𝑠𝑢𝑏 = 𝑚 𝑠𝑡𝑒𝑎𝑚 𝑓 − 𝑜𝑡,𝑜
𝑄𝑠𝑢𝑏 = 34.8𝑘𝑔𝑠 1098200 − 920940 𝑘𝑔𝐽 𝑄𝑠𝑢𝑏 = 6168648 𝐽/𝑠
𝑄𝑠𝑢𝑏,𝑜𝑡 = 𝑄𝑠𝑢𝑏,𝑐𝑜𝑙𝑑
6168648 𝐽/𝑠 = 𝑚 𝑐𝑜𝑙𝑑𝐶𝑝𝑐𝑜𝑙𝑑(𝑇𝑥1 − 𝑇𝑐𝑜𝑙𝑑,𝑖) 𝑇𝑥1 = 𝑚 𝑄𝑠𝑢𝑏,𝑠𝑡𝑒𝑎𝑚
𝑓𝑒𝑒𝑑𝑤𝑎𝑡𝑒𝑟𝐶𝑝 + 𝑇𝑐𝑜𝑙𝑑,𝑖 𝑇𝑥1 = 209.6 𝐶𝑜
𝑄𝑑𝑒𝑠𝑢𝑝,𝑜𝑡 = 𝑄𝑑𝑒𝑠𝑢𝑝,𝑐𝑜𝑙𝑑
9980640 J/s = 𝑚 𝑐𝑜𝑙𝑑𝐶𝑝𝑐𝑜𝑙𝑑(𝑇𝑐𝑜𝑙𝑑,𝑜 − 𝑇𝑥2) 𝑇𝑥2 = 𝑇𝑐𝑜𝑙𝑑,𝑜 − ( 𝑄𝑑𝑒𝑠𝑢𝑝,𝑠𝑡𝑒𝑎𝑚
𝑚 𝑓𝑒𝑒𝑑𝑤𝑎𝑡𝑒𝑟𝐶𝑝𝑐𝑜𝑙𝑑) 𝑇𝑥2 = 244.13 𝐶𝑜
ANALISA TERMODINAMIKA
Tho
Tsat1
Tx2 Tco
Tsat2
349
Desuperheating Thi Subcooling
215
Condensing T (oC)
206 252.63
D.C.A
T.T.D 250
Tx1 Tci
x
ANALISA PERPINDAHAN PANAS
METODE LMTD
∆𝑇𝐿𝑀𝑇𝐷𝑠𝑢𝑏= 𝑇𝑠𝑎𝑡;𝑇𝑥2 ; 𝑇𝑠𝑎𝑡;𝑇𝑥1
ln 𝑇𝑠𝑎𝑡−𝑇𝑥2
𝑇𝑠𝑎𝑡−𝑇𝑥1
∆𝑇𝐿𝑀𝑇𝐷𝑠𝑢𝑏= 252.63;244.13 ; 252.63;209.6 ln 252.63−244.13
252.63−209.6
∆𝑇𝐿𝑀𝑇𝐷𝑠𝑢𝑏= 19.151
∆𝑇𝐿𝑀𝑇𝐷𝑐𝑜𝑛𝑑= 𝑇𝑠𝑎𝑡;𝑇𝑥1 ; 𝑇𝑜;𝑇𝑐𝑖
ln 𝑇𝑠𝑎𝑡−𝑇𝑥1
𝑇𝑜−𝑇𝑐𝑖
∆𝑇𝐿𝑀𝑇𝐷𝑐𝑜𝑛𝑑= 252.63;209.6 ; 215;206 ln 252.63−209.6
215−206
∆𝑇𝐿𝑀𝑇𝐷𝑐𝑜𝑛𝑑= 19.5668
Analisa Perpan Bagian Internal
variasi kecepatan 1.8
2.1 2.44
3
𝑁𝑡 = 𝜌 4𝑚𝑐
𝑓𝑒𝑒𝑑𝑤𝑎𝑡𝑒𝑟𝑣𝑡𝑢𝑏𝑒𝜋𝑑𝑖2 =
4 𝑥 34.8𝑘𝑔𝑠
843.1𝑚3𝑘𝑔 𝑥 2.44𝑚𝑠 𝑥 𝜋 𝑥 0.011659𝑚 2 𝑁𝑡 = 1709.032 ≈ 1710
METODE LMTD Analisa Perpan Bagian Internal
𝐴𝑠𝑢𝑏 = 𝑈 𝑄𝑠𝑢𝑏
𝑠𝑢𝑏 𝑥 ∆𝐿𝑀𝑇𝐷𝑠𝑢𝑏
𝐴𝑐𝑜𝑛𝑑 = 𝑈 𝑄𝑐𝑜𝑛𝑑
𝑐𝑜𝑛𝑑 𝑥 ∆𝐿𝑀𝑇𝐷𝑐𝑜𝑛𝑑 𝐴𝑠𝑢𝑏 = 4226.338 𝑥 19.576168648 J
𝐴𝑐𝑜𝑛𝑑 = 2942.43 𝑥 19.1559166960 J 𝐴𝑠𝑢𝑏 = 74.594 𝑚2
𝐴𝑐𝑜𝑛𝑑 = 1049.968 𝑚2
𝐿𝑠𝑢𝑏 = 𝜋𝑑𝑜𝐴𝑠𝑢𝑏
𝑡𝑢𝑏𝑒𝑁𝑡
𝐿𝑐𝑜𝑛𝑑 = 𝜋𝑑𝑜𝐴𝑐𝑜𝑛𝑑
𝑡𝑢𝑏𝑒𝑁𝑡 𝐿𝑠𝑢𝑏 = 𝜋 𝑥 0.01588 𝑚 𝑥 171074.594 𝑚2
𝐿𝑐𝑜𝑛𝑑 = 𝜋 𝑥 0.01588 𝑚 𝑥 17101049.968 𝑚2 𝐿𝑠𝑢𝑏 = 0.874 𝑚
𝐿𝑐𝑜𝑛𝑑 = 12.308 𝑚 𝑅𝑒𝑑𝑡𝑢𝑏𝑒 = 𝜌𝑡𝑢𝑏𝑒 𝑥 𝑉𝜇𝑡𝑢𝑏𝑒 𝑥 𝑑𝑖𝑡𝑢𝑏𝑒
𝑡𝑢𝑏𝑒
𝑅𝑒𝑑𝑡𝑢𝑏𝑒 = 843.1
𝑘𝑔
𝑚3 𝑥 2.44𝑚𝑠 𝑥 0.011659 𝑚 1.21𝐸;04 𝑃𝑎.𝑠 𝑅𝑒𝑑𝑡𝑢𝑏𝑒 = 198218.802
METODE LMTD Analisa Perpan Bagian Internal
𝑁𝑢𝑡𝑢𝑏𝑒 = 0.023 𝑥 𝑅𝑒𝑡𝑢𝑏𝑒4/5 𝑥 𝑃𝑟𝑡𝑢𝑏𝑒0.4
𝑁𝑢𝑡𝑢𝑏𝑒 = 0.023 𝑥 198218.802 4/5 𝑥 0.8357270.4 𝑁𝑢𝑡𝑢𝑏𝑒 = 369.1302
𝑖𝑡𝑢𝑏𝑒 = 𝑁𝑢𝑡𝑢𝑏𝑒𝑑𝑖 𝑥 𝑘𝑡𝑢𝑏𝑒
𝑡𝑢𝑏𝑒
𝑖𝑡𝑢𝑏𝑒 = 369.1302 𝑥 0.6607𝑚.𝐾𝑊 0.011659 𝑚
𝑖𝑡𝑢𝑏𝑒 = 20918.1163𝑚𝑊2.𝐾
variasi kecepatan Ltot hi Re
1.8 12.81 16462.41 146469.08
2.1 14.82 18623.05 170880.60
2.44 17.14 20998.45 198546.98
3 21.13 24772.65 244115.14
METODE LMTD Analisa Perpan Bagian Internal
Pressure Drop
Pressure Drop Major Pressure Drop Minor
∆𝑝𝑚𝑎𝑦𝑜𝑟= 𝑓1
2𝜌𝑣2 𝐿𝑡𝑜𝑡 𝑑𝑖
∆𝑝𝑚𝑎𝑦𝑜𝑟= 0.029 𝑥 12 𝑥 843.1𝑚𝑘𝑔3 𝑥 (2.44 𝑚/𝑠)2 𝑥 0.011659 𝑚17.418 𝑚
∆𝑝𝑚𝑎𝑦𝑜𝑟= 111797.183 𝑃𝑎 = 1.139 𝑘𝑔/𝑐𝑚2
∆𝑝𝑚𝑖𝑛𝑜𝑟= ∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑛𝑡𝑟 + ∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑥𝑡 + ∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑟𝑡𝑟𝑛 𝑏𝑒𝑛𝑑
METODE LMTD Analisa Perpan Bagian Internal
Pressure Drop Minor
∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑛𝑡𝑟= 𝑘𝜌𝑣2 2
∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑛𝑡𝑟= 0.04 𝑥 866.83 𝑚3𝑘𝑔 𝑥 2.44𝑚𝑠 2
2
∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑛𝑡𝑟= 103.215 𝑃𝑎 = 0.001052 𝑐𝑚𝑘𝑔2
∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑥𝑡= 𝑘𝜌𝑣2 2
∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑥𝑡= 1 𝑥 819.69 𝑚3𝑘𝑔 𝑥 2.44𝑚𝑠 2
2
∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑥𝑡= 2440.0532 𝑃𝑎 = 0.0249 𝑘𝑔/𝑐𝑚2
∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑟𝑡𝑟𝑛 𝑏𝑒𝑛𝑑= 𝑘𝜌𝑣2 2
∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑟𝑡𝑟𝑛 𝑏𝑒𝑛𝑑= 0.2 𝑥 844.43 𝑘𝑔
𝑚3 𝑥 2.44𝑚𝑠 2
2
∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑟𝑡𝑟𝑛 𝑏𝑒𝑛𝑑= 502.7398 𝑃𝑎 = 0.00512 𝑘𝑔/𝑐𝑚2
METODE LMTD Analisa Perpan Bagian Internal
Pressure Drop
∆𝑝𝑡𝑜𝑡= ∆𝑝𝑚𝑎𝑦𝑜𝑟 + ∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑛𝑡𝑟 + ∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑒𝑥𝑡 + ∆𝑝𝑚𝑖𝑛𝑜𝑟,𝑟𝑡𝑟𝑛 𝑏𝑒𝑛𝑑
∆𝑝𝑡𝑜𝑡= 1.139 𝑘𝑔/𝑐𝑚2 + 0.001052 𝑐𝑚𝑘𝑔2 + 0.0249 𝑘𝑔/𝑐𝑚2 + 0.00512 𝑘𝑔/𝑐𝑚2
∆𝑝𝑡𝑜𝑡= 1.17 𝑘𝑔/𝑐𝑚2
variasi kecepatan ∆p mjr tube (kg/cm2) ∆p mnr (kg/cm2) ∆p total (kg/cm2) 1.8 0.455882183 0.016891593 0.472773776 2.1 0.717783678 0.022991335 0.740775013 2.44 1.120755218 0.031038824 1.151794042
3 2.05300897 0.046921092 2.099930062
METODE LMTD Analisa Perpan Bagian Internal
𝑣 = 𝑅𝑒𝜇𝜌𝐷
𝑣 = 198546.98 𝑥 1.21𝑥10−4 𝑃𝑎.𝑠 843.1𝑘𝑔
𝑚3𝑥 0.011659 𝑚 𝑣 = 2.44 𝑚/𝑠
METODE LMTD Analisa Perpan Bagian Eksternal
𝐼𝐷𝑠𝑒𝑙𝑙 = 0.637 𝐶𝑇𝑃𝐶𝐿 𝜋𝑑𝑜2𝑁𝑡(𝑃𝑅2)
𝐼𝐷𝑠𝑒𝑙𝑙 = 0.637 0.870.9 𝜋 𝑥 (0.01588 𝑚)2 𝑥 1710 𝑥 1.3852 𝐼𝐷𝑠𝑒𝑙𝑙 = 1.0099 𝑚
𝐴𝑠𝑠𝑢𝑏 = 𝐼𝐷𝑠𝑒𝑙𝑙2 𝑥 𝐿𝑠𝑢𝑏
𝐴𝑠𝑠𝑢𝑏 = 1.0099 𝑚 𝑥 0.8731 𝑚
2 𝑚
𝐴𝑠𝑠𝑢𝑏 = 0.44086 𝑚2
𝐴𝑆𝑐𝑜𝑛𝑑 = 0.5 𝑥 𝐼𝐷𝑠𝑒𝑙𝑙 𝑥 𝐿𝑐𝑜𝑛𝑑
𝐴𝑠𝑐𝑜𝑛𝑑 = 0.5 𝑥 1.0099 𝑚 𝑥 12.308 𝑚 𝐴𝑠𝑐𝑜𝑛𝑑 = 6.215 𝑚2
𝑉𝑠𝑠𝑢𝑏 = 𝐴𝑠 𝑚 𝑠𝑢𝑏
𝑠𝑢𝑏 𝑥 𝜌𝑠𝑢𝑏 𝑉𝑠𝑐𝑜𝑛𝑑 = 𝐴𝑠 𝑚 𝑐𝑜𝑛𝑑
𝑐𝑜𝑛𝑑 𝑥 𝜌𝑐𝑜𝑛𝑑
𝑉𝑠𝑠𝑢𝑏 = 34.8 𝑘𝑔/𝑠
0.44086 𝑚2 𝑥 851.52 𝑘𝑔/𝑚3 𝑉𝑠𝑐𝑜𝑛𝑑 = 34.8 𝑘𝑔/𝑠
6.215 𝑚2 𝑥 818.53 𝑘𝑔/𝑚3
𝑉𝑠𝑠𝑢𝑏 = 0.0926 𝑚/𝑠 𝑉𝑠𝑐𝑜𝑛𝑑 = 0.0068 𝑚/𝑠
METODE LMTD Analisa Perpan Bagian Eksternal
𝑉𝑚𝑎𝑥 = (𝑆𝑇;𝑑𝑜)𝑆𝑇 𝑉𝑠𝑠𝑢𝑏
𝑉𝑚𝑎𝑥 = (0.022 𝑚;0.01588 𝑚)0.022 𝑚 0.0926 𝑚/𝑠 𝑉𝑚𝑎𝑥 = 0.333 𝑚/𝑠
𝑅𝑒𝑑, 𝑚𝑎𝑥 = 𝜌𝑠𝑢𝑏 𝑥 𝑉𝑚𝑎𝑥𝑠𝑢𝑏 𝑥 𝑑𝑜 𝜇𝑠𝑢𝑏
𝑅𝑒𝑑, 𝑚𝑎𝑥 = 825.58
𝑘𝑔
𝑚3𝑥0.333𝑚𝑠𝑥 0.01588 𝑚 0.000114 𝑃𝑎.𝑠 𝑅𝑒𝑑, 𝑚𝑎𝑥 = 38265.433
𝑁𝑢𝑠𝑢𝑏 = 1.13 𝑥 𝐶𝑠𝑢𝑏 𝑥 𝑅𝑒𝑑, 𝑚𝑎𝑥𝑠𝑢𝑏 𝑚 𝑥 𝑃𝑟𝑠𝑢𝑏13
𝑁𝑢𝑠𝑢𝑏 = 1.13 𝑥 0.470501 𝑥 38265.433 0.563917 𝑥 0.8440011/3 𝑁𝑢𝑠𝑢𝑏 = 193.043
METODE LMTD Analisa Perpan Bagian Eksternal
𝑜𝑠𝑢𝑏 = 𝑁𝑢𝑠𝑢𝑏 𝑥 𝑘𝑠𝑢𝑏 𝑑𝑜𝑠𝑢𝑏
𝑜𝑠𝑢𝑏 = 193.043 𝑥 0.6367 𝑚.𝐾𝑊 0.01588 𝑚
𝑜𝑠𝑢𝑏 = 8102.227𝑊 𝑚2.𝐾
𝑜𝑐𝑜𝑛𝑑 = 0.729 𝑔𝜌𝑙(𝜌𝑙 − 𝜌𝑔)𝑘𝑙3′𝑓𝑔
𝑁𝑙 𝑥 𝜇𝑙(𝑇𝑚𝑒𝑎𝑛,𝑐𝑜𝑙𝑑− 𝑇𝑠𝑎𝑡,𝑜𝑡)𝑑𝑜𝑡𝑢𝑏𝑒
1/4
𝑜𝑐𝑜𝑛𝑑 = 0.729 9.81
𝑚
𝑠2 𝑥 818.53 𝑘𝑔/𝑚3(818.53;20.904)𝑘𝑔/𝑚3 𝑥 (0.6303𝑚.𝐾𝑊 )3 𝑥 1743615.77 𝐽/𝑘𝑔 88 𝑥 0.0001114 𝑃𝑎.𝑠 239.19 𝐶0 ;252.63 𝐶0 𝑥 0.01588 𝑚
1/4
𝑜𝑐𝑜𝑛𝑑 = 4411.767 𝑊 𝑚2.𝐾
METODE LMTD Analisa Perpan Bagian Eksternal
∆𝑝𝑠𝑢𝑏= 𝑁𝐿𝑋 𝜌𝑣𝑚𝑎𝑥2 2 𝑓
∆𝑝𝑠𝑢𝑏= 44 𝑥 1.04 𝑥 825.58 𝑘𝑔/𝑚3 0.86 𝑚/𝑠 2
2 𝑥 0.45
∆𝑝𝑠𝑢𝑏= 6197.0733 𝑃𝑎 = 0.06315 𝑘𝑔/𝑐𝑚2
∆𝑝
𝑐𝑜𝑛𝑑=
12
𝑓𝐺𝑠2𝐼𝐷𝑠𝑒𝑙𝑙 𝑁:1 5.22 𝑥 1010𝐷𝑒 𝑠
∆𝑝
𝑐𝑜𝑛𝑑=
1 2
0.0011𝑓𝑡2𝑖𝑛2 𝑥 (151372.134 𝑟.𝑓𝑡2𝑙𝑏 )2 𝑥 3.31 𝑓𝑡 𝑥 261 5.22 𝑥 1010 𝑥 0.075 𝑓𝑡 𝑥 62.5
∆𝑝
𝑐𝑜𝑛𝑑= 0.044 𝑝𝑠𝑖 = 0.00309
𝑐𝑚𝑘𝑔2METODE LMTD Analisa Perpan Bagian Eksternal
Nb ho ∆p (kg/cm2)
4 13473.74 0.06
2 9916.97 0.03
1 7775.43 0.01
1 17291.83 0.01
METODE LMTD Pemilihan Design Optimal
0 0,5 1 1,5 2 2,5
0 5000 10000 15000 20000 25000 30000
140000 160000 180000 200000 220000 240000 260000
hi
Re
hi & ∆p vs Re
hi vs Re pressure drop
0 0,01 0,02 0,03 0,04 0,05 0,06 0,07
0 5000 10000 15000
0 1 2 3 4
ho
Nb
ho & ∆p vs Nb
ho sv Nb dlta (p) vs Nb
Asub Acond Adesup Lsub Lcond Ldesup IDshell kecepatan Jumlah tube Jumlah baffle sub
74.5945 1049.968 361.397 0.8744 12.30777 4.23632 1.009889 2.44 1710 4
METODE NTU
𝐶𝑐 = 𝑚 𝑐𝐶𝑝𝑐
𝐶𝑐 = 375.2𝑘𝑔𝑠 𝑥 4.533𝑘𝑔.𝐶𝑘𝐽 𝐶𝑐 = 1700.78𝑠.𝐶𝑘𝐽
𝐶 = 𝑄𝑐/(∆𝑇) 𝐶 = 74834.39 𝑘𝐽/𝑠
(349;215)0𝐶 𝐶 = 558.46𝑠.𝐶𝑘𝐽
>
Tci 206C Thi 349C Nt 1710
Tco 250C Tho 215 do 0.01588
Tmean 228C Tmean 282C di 0.011659
Pc,i 197kg/cm2 Phs,i 42.4 kg/cm2 Atube 0.000107
mc 375.2kg/s mh 34.8 kg/s ST 0.022
cp,c 4.533kj/kgC cp,h 16.04786207kj/kgC C 0.470501
Cc 1700.782 Ch 558.4656Cmin m 0.563917
ρc 843.1 kg/m3 ρh 18.755 kg/m3 ID 1.009889
µc 0.000121 Pa.s µh 0.00001943 Pa.s L 17.41849
Pr 0.835727 Pr 1.182744 As 17.59074
kc 0.6607 W/mC kh 0.04851 W/mC Aselim(m²) 0.9
cold hot Tube &Shell dimension
METODE NTU
𝐶𝑟 = 𝐶𝑚𝑖𝑛
𝐶𝑚𝑎𝑥 = 𝐶
𝐶𝑐 = 0.328 𝑈𝑡𝑜𝑡 = 𝐴 𝑄𝑡𝑜𝑡
𝑡𝑜𝑡∆𝑇𝐿𝑀𝑇𝐷 𝑈𝑡𝑜𝑡 = 74861627 𝐽/𝑠
1450.152 𝑚2 𝑥 37.533 𝐶 𝑈𝑡𝑜𝑡 = 1375.414𝑚𝑊20𝐶
𝑈𝑡𝑜𝑡 = 𝑑𝑜 1
𝑑𝑖 1
𝑖:𝑅𝑘𝑜𝑛𝑑:𝑜1
𝑜 = 1 1
𝑄𝑡𝑜𝑡;𝑅𝑘𝑜𝑛𝑑;𝑑𝑜𝑑𝑖𝑖1
𝑜 = 1 1
74861627 𝐽/𝑠 ; 4.80758𝐸;05 𝑚2.𝐾𝑊 ; 0.011659 𝑚0.01588 𝑚 1
20918.1163 𝑊 𝑚2𝐶
𝑜 = 1582.735𝑚𝑊2𝐶
Atot ∆LMTD qtotal Utot Rkond di do hi ho
1485.959 37.53292 74861627 1342.271 4.81E-05 0.011659 0.01588 20918.1163 1582.73531
METODE NTU
𝐴𝑝𝑒𝑟𝑝𝑎𝑛 = 𝜋. 𝑑𝑜. 𝑁𝑡𝑝𝑙𝑢𝑔. 𝐿𝑡𝑜𝑡
𝐴𝑝𝑒𝑟𝑝𝑎𝑛 = 𝜋 𝑥 0.011659 𝑚 𝑥 1710 𝑥 17.418 𝑚 𝐴𝑝𝑒𝑟𝑝𝑎𝑛 = 1485.96 𝑚2
𝑁𝑇𝑈 = 𝑈𝐴𝐶𝑝𝑒𝑟𝑝𝑎𝑛
𝑚𝑖𝑛 = 1.376
𝑘𝑊
𝑚2𝐶 𝑥 1485.96 𝑚2 558.46𝑘𝑊𝐶 𝑁𝑇𝑈 = 3.57
𝜀 = 2 1 + 𝐶𝑟 + (1 + 𝐶𝑟2)1/2 𝑥 1:𝑒𝑥𝑝 ;𝑁𝑇𝑈(1:𝐶𝑟2)1/2 1;𝑒𝑥𝑝 ;𝑁𝑇𝑈(1:𝐶𝑟2)1/2
;1
𝜀 = 2 1 + 0.328 + (1 + 0.3282)1/2 𝑥 1:𝑒𝑥𝑝 ;3.57 (1:0.3282)1/2
1;𝑒𝑥𝑝 ;3.57 (1:0.3282)1/2
;1
𝜀 = 0.822