pd mechanical dsgn
TRANSCRIPT
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Step 1: Specification
Material T in C T out C
34o API Crude oil 40 67
42o API Kerosene 200 90
T in T out
Shell 200 90
Tube 40 67
T mean 145 C
Cp (145C) 2.47 kJ/KgC
Duty 754.7222222 kW 754722.222
Step 2: Physical Properties
Kerosene Inlet Mean Outlet
Temperature 200 145 90
Specific Heat 2.72 2.47 2.26
Thermal Conductivity 0.13 0.132 T
Density 690 730 770
Viscosity 0.22 0.43 0.8
Step 3: Overall Coefficient
For an exchanger for this type, the overall coefficient will be in the range of 300-500 w/mC
See figure 12.1 and table 12.1; so start with 300
Step 4: Exchanger Type Dimension
Tlm = (Thi - Tco) - (Tho -
ln [(Thi - Tco)/(Th
Tlm = 81.89229794
R = Thi - Tho
Tco - Tci
= 4.074074074
S = Tco - Tci
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Thi - Tci
= 0.16875
From figure 12.19, Ft = 0.92
Tm = 75.34091411
Step 5: Heat Transfer Area
Uo = q
AoTm
Ao = q
UoTm
= 33.39142841
Step 6: Layout and Tube Size
Using a split ring floating head exchanger for efficiency and ease of cleaning
Outer Diameter 19.05 mm 0.01905
Internal Diameter 14.83 mm 0.01483Triangular 23.81 mm 0.02381
Long Tubes 5 m 5000
Pitch/ Diameter 1.25
Step 7: Number of Tubes
Area of one tube (neglecting thickness of tube sheet)
= 0.2992367 m
Number of tubes = 111.5886801 Say
So, 2 passes, tube per pass = 55.5 Say
Check the tube-side velocity at this stage to see if it look reasonable
Tube cross sectional area = 0.000172732 m
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Area per pass = 0.009672978 m
Volumetric Flow Rate = Flow of Crude x
3600
= 0.016818708 m/s
Tube Side Velocity, Ut = 1.738731069 m/s
Hence, the velocity is satisfactory, between 1 and 2 m/s.
Step 8: Bundle and Shell Diameter
From Table 12.4, for tube passes, K1 = 0.249
n1 = 2.207
Bundle Diameter, Db = Outer Diameter x (Nt/K1)^(1/n1)
Pt = 1.25do
do = 0.019048 m
Db = 302.150182 mm
For a spliting floating head exchanger the typical shell clearance from figure 12.10 is 53 mm,
Ds = 355.150182 mm
Step 9: Tube Side Heat Transfer Coefficient
Re = xUtxDi
= 6049.309164
Pr = CpxThermal Conductivity
= 53.5880597
L/D = 337.1544167
From figure 12.23, jh = 0.0038
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Nu = jh x Re x Pr^0.33
Nu = 85.52278363
hi = Nu x (Thermal Conductivity/ Internal Di
= 772.7614974
Step 10: Shell-side heat transfer coefficient
As a first trial take the baffle spacing = Ds/5
= 71.03003641
As = 5041.014512
Equilateral triangular pitch
de = 1.1 (Pt - 0.917do)
do
= 13.51957786 mm
Volumetric flow rate on shell side = 0.003805175
Shell side velocity = 0.754845276
Re = 17325.63009
Pr = 8.046212121
Use segmental baffles with a 25% cut. This should give a reasonable heat transfer coefficient
From figure 12.29, jh = 0.0048
hs = 1615.795011 W/mC
Step 11: Overall coefficient
Kw = 55
1/hi = 0.00129406
1/hid = 0.00035
ln do/di = 0.250414945
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1/ho = 0.00061889
1/hod = 0.0002
1/Uo = 0.002930853
Uo = 341.1975878
Step 12: Pressure Drop
Re = 6049.309164
Ut = 1.738731069
From figure 12.24, jf = 0.0053
Pt = 41930.37008 N/m
= 0.42 bar
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Pressure in (bar) Permissible Pressure drop (bar) Fouling Factor (W/m2C)
6.5 1 0.0003
5 1 0.0002
Hours Second
1 3600
W
Crude oil Outlet
C Temperature 67
kJ/kgC Specific Heat 2.07
W/mC Thermal Conductivity 0.134
kg/m Density 812
mNsm- Viscosity 2.86
w/mC
Tci)
o - Tci)]
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m
mm
mm
111 tubes
56
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1
density
19.05 mm
0.302 m
o the shell inside diameter
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meter)
say 71
mm 0.005041 m
0.01352 m
m/s
without too large a pressure drop.
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Mass Flowrate (kg/h)
50000
10000
Mean Inlet
53.5 40 C
2.04 2.01 kJ/kgC
0.134 0.135 W/mC
825.8 840 kg/m
3.52 4.3 mNsm-
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cost estimation
guthrie method
K1 4.8306 log10Cp= 4.274003
K2 -0.8509 Cp= 2033986
K3 0.3187
A 33.4
Fm 1 Cbm= 6691816
Fp 1
b1 1.63
B2 1.66
Cp 2033986
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45
6
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14
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2526
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3637
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Heat Exchanged
Transfer Rate, Service
Tube Type
CONSTRUCTION OF ONE S
Corrosion Allowance mm
Tube No.
Tubesheet-Stationary
Channel or Bonnet
Shell Steel
Rating
Size
Connection
Intermediate
Out
In
No. Passes per Shell
Design Temperature C
Design/ Test Pressure kPa (ga)
Latent Heat kJ/kg @ C
Inlet Pressure kPaVelocity m/s
Pressure Drop, Allow./Calc kPa
Fouling Resistance (Min.)/Calc mC/W
Temperature (In/Out) C
Density kg/m
Viscosity/ Liquid mPa.s
Molecular Mass, Vapor
Molecular Mass, Noncondensable
Specific Heat Capacity kJ/(kgC)
Vapor (In/Out)
Liquid
Steam
Water
Noncondesable
Fluid Name
Surf/ Unit (Gross/Eff)
Thermal Conductivity J/(s.m.C/m)
Service of Unit Oil to Oil Exchange
Size
Fluid Quantity, Total kg/h
Plant Location
Customer
Fluid Allocation
PERFORMANCE OF ONE U
Address
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45
46
47
48
49
50
5152
53
54
55
56 Remark
Weight/ Shell
Code Requirement
Floating Head
Expansion Joint: Carbon Steel
Gasket-Shell Sidev- Inlet Nozzle
Bypass Seal Arrangement
Support: Tube
Baffles: Long
Type: SegmBaffles: Cross
Floating Head Cover
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Material: Carbon Steel
Tubesheet: Floating
Channel Cover
Shell Cover
ELL
ODID
Tube Side
3
2
Shell Side
3
2
0.0003
100
650
0.0002
100
500
Sketch (Bundle/ Nozzle Orien
150#
4.3
840
40
2.26
0.135
Crude Oil
50 000
In
10 000
0.135
2.012.72
0.13
Out
90
770
0.8
In
200
690
0.22
Kerosene
r Item No. E-4
Connected In Parallel
Reference No.
Date: Rev:
Proposal No.
NIT
Shell Side Tube Side
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Type: Flanged
Impingement Protection
InletSpacing: 75 mm%Cut (Diameter/ Area): 25%ented
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ation)
2.86
812
67
Out
0.134
2.07
Series
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MECHANICAL DESIGN
specification
shell 355.15 mm
tubes 14.83 mm id
19.05 mm od
length 5000 mm
kerosene in the shell, operating pressure 5 bar
crude in the tubes, operating pressure 6.5 bar
material of construction, semi-killed or silicon killed crbon steel
a) Design Pressure: takes 10% greater than operating pressure
shell = 4.4 = 440000 N/m2
tubes= 6.05 =650000 N/m2
design temperature: 200 oC
take this design temperature both shell and tubes. The tubes could reach the kerosene
temperature if there was no flow of crude oil
b) corrosion allowance
kerosene= 2 mm
crude oil= 4 mm
c) end covers used torispherical, header-cover flat plate
d) stressing
from table 13.2, design stress is 105 N/mm2 at 200oC
shell: e= 0.0008 m = 0.8 mm
add corrosion allowance= 2.8 mm
thiss is less than the minimum recommended thickness so round up to 5 mm
header: e= 0.0011 m = 1.1 mm
add corrosion allowance = 5.1 mm
shell end cover, torispherical,
take Rc = 0.3
Rk/Rc = 0.1
Cs = 2.37 take joint factor as 1 formed he
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e = 0.00148 m = 1.5 mm
add corrosion allowance = 3.5 mm
floating head torispherical:
from figure 12.10 bundle to shell clearance, take as split ring
Db = 53.15 mm = 53
take Rc = 0.3
Rk/Rc = 0.1
Cs= 2.37
e= 0.00206 m = 2.1 mm
add corrosion allowances = 6.1 mm
flat plate (header cover) type e,
Cp= 0.55
Di= 355 mm = 0.35 m
De= 0.4 m
e= 0.167 m = 16.7 mm
add corrosion allowance = 20.7 mm
all thickness will be rounded to the nearest standard size
e) Tube rating
tube id= 14.83 mm
tube od= 19.05 mm
design stress = 105000000 N/m2
design pressure = 6.05 N/m2
thickness required , e = 0.0000053 m = 0.005
actual wall thickness = 2.11 mm
f) tube sheet thickness should not be less than tube diameter
take thickness as 20 mm
shell od= 365.15 mm say 370 mm
design pressure= = 440000 N/m2
design temperature 200 oC
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refer to table 13.5, 6 bar rating will be satisfactory
floating head od 350 mm
design pressure 6.05 N/m2
design temperature 200 oC
based on the table 13.5 use 10 bar rated flanged
h) supports
use saddle supports
diameter 0.4 m
length 10 m
shell and header volume of steel 0.063 m3volume of shell head, take as flat 0.0004
volume of floating head, take as flat 0.0005
volume of flat plate end cover 0.0026
volume of tube-sheet 0.0026 ignoring the holes
volume of tube 0.115
number of baffles 77
taking baffles as 3 mm thick and ignore the baffle cut
volume = 0.027
total volume of steel
shell 0.063
shell head 0.0004
floating head 0.0005
end cover 0.0026
tube sheet 0.0026
tubes 0.115
baffles 0.027
total 0.2111 m3
taking density of steel as 7800 kg/m3
mass of HE= 1646.58 kg
weight HE= 16152.9498 N
mass of water, ignore volum of tube 1257 kg
weight= 12331.17 N
maximum load on supports= 28484.12 N
29 kN