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Kern Method of
SHELL-AND-TUBE HEAT EXCHANGER Analysis
P M V SubbaraoProfessor
Mechanical Engineering Department
I I T Delhi
A Knowledge Bank for Run-of-theMill Problems..
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From the Preface of The book
A portion of the material which is included in conventional
texts is rarely if ever applied in the solution of run-of-the-
mill engineering problems. ..
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Major Steps in Design
Initial Decisions.
Tube side Thermal Analysis.
Thermal analysis for Shell side flow. Overall Heat Transfer coefficient.
Hydraulic Analysis of Tube side.
Hydraulic Analysis of Shell side.
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Initial Decisions
Spatial allocation of fluid.
Determination of flow velocity.
Initial guess for number of tubes. Correction for standard tube diameter.
Effect of number of tubes on tube length.
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Tube Outside Diameter From the heat transfer viewpoint, smaller-diameter tubes
yield higher heat transfer coefficients and result in a more
compact exchanger. However, larger-diameter tubes are easier to clean and
more rugged.
For mechanical cleaning, the smallest practical size is
19.05 mm. For chemical cleaning, smaller sizes can be used.
Small tube diameters (8 to 15mm) are preferred for greater
area to volume density but are limited for the purposes of
cleaning. Large tube diameters are often required for condensers and
boilers.
The most common plain tube sizes have 15.88,19.05, and
25.40 mm tube outside diameters.
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Tube Wall Thickness
The wall thickness of heat exchanger tubes is standardized
in terms of Birmingham Wire Gage BWG of the tube.
Tube thickness is selected based on pressure of the fluid
and erosion/corrosion characteristics of the fluid.
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Number of Tubes Vs Reynolds Number
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Tube Length
Tube length affects the cost and operation of heat exchangers.
Longer the tube length (for any given surface area), Fewer tubes are needed, requiring less complicated header plate
with fewer holes drilled.
Shell diameter decreases resulting in lower cost.
Typically tubes are employed in 8, 12, 15, and 20 foot lengths. Mechanical cleaning is limited to tubes 20 ft and shorter, although
standard exchangers can be built with tubes up to 40 ft.
Shell-diameter-to-tube-length ratio should be within limits of 1/5to 1/15
Maximum tube length is dictated by
Architectural layouts
Transportation (to about 30m.)
Structural stability
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Tube Length : Tube & Header Plate Deformation
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Tube Length : Tube & Header Plate Deformation
Thermal expansion of tubes needs to be taken into account for
heat exchangers operating at elevated temperatures.
Tube elongation due to thermal expansion causes:
Header plate deformation
Shell wall deformation near the header plate
Fatigue strength of the tube, header plate and shell joint needs
to be considered when using
Longer tubes
High operating tube side temperatures
Cyclic thermal loads
Creative Ideas are Essential to Handle Long Tube/Shelllength Applications.
These Ideas can Help in Solving Few More Issues.
Any New Issues due to New Ideas????
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Tube Passes
A pass is when liquid flows all the way across from one end to
the other of the exchanger. An exchanger with one shell pass and two tube passes is a 1-2
exchanger.
At any time halve the number of tubes present in a shell willhandle the entire flow.
Almost always, the tube passes will be in multiples of two (1-2,1-4, 2-4, etc.)
Odd numbers of tube passes have more complicated mechanicalstresses, etc.
A large number of tube passes are used to increase the tube sidefluid velocity and heat transfer coefficient and minimize fouling.
This can only be done when there is enough pumping power sincethe increased velocity and additional turns increases the pressuredrop significantly.
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Single Pass and Double Pass S&T Hx
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Four Pass S & T Hx
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Eight Pass S & T Hx
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Partitions in End Bonnets
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Shell Diameter Vs Number of Passes
Additional conditions to select number of passes:
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Tube-Side Nusselt Number
For turbulent flow, the following equation developed by Petukhov-
Kirillov is used:
2
322
1
28.3Reln58.1
1Pr2
7.1207.1
PrRe2
t
t
tt
tube
fWhere
f
f
Nu
Properties are evaluated at mean bulk temperature and constants
are adjusted to fit experimental data.
Validity range: 104 < Ret < 5 x 106 and 0.5 < Prt < 2000 with
10% error.
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For laminar flow, the Sieder and Tate correlation is be used.
31
PrRe86.1
L
dNu
itt
tube
is applicable for 0.48 2.
The heat transfer coefficient for the tube-side is expressed asfollows:
i
t
tt
d
kNuh