This document discusses various types of heat exchangers including shell-and-tube, double-pipe, plate-and-frame, fired heaters, and aerial coolers. It provides details on shell-and-tube exchangers including baffles, tube layout, and TEMA classifications. Examples are given for sizing problems including determining heat duty, selecting the exchanger type, and calculating the number of tubes needed. Common software for heat exchanger design is also listed.
30. Sizing
2
N= required number of tubes
q= heat duty,BTU/hr
U= overall heat transfer coefficient,BTU/hr-ft-F
LMTD= corrected log mean temperature difference,F
L=Tube Length,ft
A´=tube external surface area per foot of length,ft2/ft
30
47. :
:
• T2 = 100 0
F
• P2 = 990 psig
• Water vapor in gas = 28
lb/MMsccf
• Seawater T3 = 75 0
F
• Limit temperature rise to 10
0
F
• Use 1-in . OD 10 BWG tubes
on 1 1
/4 –in
:
• 100MMscf at 0.67 SG (from
table 2-10)
• 6000 bopd at 0.77 SG
• 15 bbl/ MMscf
• T1 =175 0
F
• P1 =1000 psig
• Water vapor in gas = 60
lb/MMscf
47
48. Problem:
1. Calculate water flow rate in outlet and water vapor
condensed.
2. Calculate heat duty.
3. Determine seawater circulation rate.
4. Pick a type of exchanger and number of tubes
required.
48
49. Solution:
1. Calculate free water and water vapor flow rates.
• Water flow rate in inlet:
Free water = (100 MMscfd)(15 bbl/MMscfd) = 1,500 bwpd
• Water flow rate in outlet:
Free water = 1,500 bwpd
• Water vapor condensed:
• Water flo rate in outlet:
9 bwpd + 1500 bwpd = 1509 bwpd
(60 28) 100
* 3200 /
lb MMscf
lb d
MMscf D
−
=
1
3200 * 9
350
lb bbl
bwpd
d lb
=
49
51. • b. condensate duty
qo = 14.6(SG)( ∆T)COQO
Co = 0.535 Btu/lb 0
F (figure 2-
13)
qo = 14.6(0.77)(100175)(0.535)
(6000)
qo = -2707000 Btu/hr
• c. free water duty
qw= 14.6(∆T)Qw
qw= 14.6(100-175)(1509)
qw= 1652000 Btu/hr
• d. water latent duty
q1h = w*λ
w = 3200 lb/d (1d/24hr)=
133 lb/hr
λ = -996.3 Btu/lb (table 2-
6,170 0
F)
q1h = (133)(-996.3) =
-133000Btu/hr
• e . total heat duty
q= -9879000 -2707000
-1652000 -133000
q= -14281000 Btu/hr
51
52. 3. water circulation rate :
• qw= 14.6(T2-T1)Qw
• Qw = qw/14.6(T2-T1)
• Limit ∆T for water to 10 0
F to limit scale
Qw = 14.3 * 106
/14.6(10)
Qw = 97945 bwpd = 2858 gpm
52
53. 4. Heat exchanger type and number of tubes
Choose TEMA R because of large size.
Select type AFL because of low temperature change and
LMTD correction factor.
53
54. The water is corrosive and may deposit solids. Therefore, flow
water through tubes and make the tubes 70/30 Cu/Ni. Flow the
gas through the shell.
• Calculate LMTD :
T1
=175 T2
=100
T3
= 75 T4
= 85
∆T1
= 175-85=90
∆T2
= 100-75=25
LMTD = 50.7 0
F
90
25
90 25
loge
LMTD
−
=
Correction factor (figure 3-10)
P= (85-75)/(175-75) = 0.1
R= (175-100)/(85-75)
F = 0.95
LMTD = (50.7)(0.95) = 48.2 0
F
54
55. • Calculation number of tube:
Assume L = 40 ft
A= 0.2618 ft2
/ ft ( table 2-1)
N = 315 tubes
( )
q
N
UA LMTD Lι
=
6
14.3*10
(90)(0.261)(48.2)(40)
N =
55
Xavier, my suggestions:
point out that this represents production rather than injection, but is a very useful diagram for visualisation of the interaction of sorption, pressure, and multiphase flow, and the concept of relative and effective permeability
Acknowledge Koenig as source
briefly describe the main features on the diagram
Mention that later in the talk you will show the distribution of water saturation and relative permeabilities during an injection process (these are in slides 12 & 13)