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Heat Exchangers:Design ConsiderationsChapter 11Sections 11.1 through 11.3

TypesHeat Exchanger TypesHeat exchangers are ubiquitous to energy conversion and utilization. They involve heat exchange between two fluids separated by a solid and encompass a wide range of flow configurations. ConcentricTube Heat Exchangers
Simplest configuration.
Superior performance associated with counter flow.

Types (cont.) Crossflow Heat Exchangers
For crossflow over the tubes, fluid motion, and hence mixing, in the transverse
direction (y) is prevented for the finned tubes, but occurs for the unfinned condition. Heat exchanger performance is influenced by mixing.

Types (cont.) ShellandTube Heat Exchangers
Baffles are used to establish a crossflow and to induce turbulent mixing of the
shellside fluid, both of which enhance convection. The number of tube and shell passes may be varied, e.g.:
One Shell Pass,Two Tube PassesTwo Shell Passes,Four Tube Passes

Types (cont.) Compact Heat Exchangers
Widely used to achieve large heat rates per unit volume, particularly when
one or both fluids is a gas. Characterized by large heat transfer surface areas per unit volume, small
flow passages, and laminar flow.(a) Fintube (flat tubes, continuous plate fins)(b) Fintube (circular tubes, continuous plate fins)(c) Fintube (circular tubes, circular fins)(d) Platefin (single pass)(e) Platefin (multipass)

Overall CoefficientOverall Heat Transfer Coefficient An essential requirement for heat exchanger design or performance calculations.
Contributing factors include convection and conduction associated with the
two fluids and the intermediate solid, as well as the potential use of fins on both sides and the effects of timedependent surface fouling. With subscripts c and h used to designate the hot and cold fluids, respectively,
the most general expression for the overall coefficient is:

Overall CoefficientAssuming an adiabatic tip, the fin efficiency is

LMTD MethodA Methodology for Heat ExchangerDesign Calculations The Log Mean Temperature Difference (LMTD) Method  A form of Newtons Law of Cooling may be applied to heat exchangers by
using a logmean value of the temperature difference between the two fluids:

LMTD Method (cont.) ParallelFlow Heat Exchanger:
Note that Tc,o can not exceed Th,o for a PF HX, but can do so for a CF HX.
For equivalent values of UA and inlet temperatures,
ShellandTube and CrossFlow Heat Exchangers:

Energy BalanceOverall Energy Balance Assume negligible heat transfer between the exchanger and its surroundings
and negligible potential and kinetic energy changes for each fluid. Assuming no l/v phase change and constant specific heats,
Application to the hot (h) and cold (c) fluids:

Special ConditionsSpecial Operating Conditions Case (c): Ch=Cc.

Problem: Overall Heat Transfer CoefficientProblem 11.5: Determination of heat transfer per unit length for heat recoverydevice involving hot flue gases and water.
KNOWN: Geometry of finned, annular heat exchanger. Gasside temperature and convection coefficient. Waterside flowrate and temperature.
FIND: Heat rate per unit length.

Problem: Overall Heat Transfer Coefficient (cont.)
ASSUMPTIONS: (1) Steadystate conditions, (2) Constant properties, (3) Onedimensional conduction in strut, (4) Adiabatic outer surface conditions, (5) Negligible gasside radiation, (6) Fullydeveloped internal flow, (7) Negligible fouling.
PROPERTIES: Table A6, Water (300 K): k = 0.613 W/m(K, Pr = 5.83, ( = 855 ( 106 N(s/m2.
ANALYSIS: The heat rate is
where

Problem: Overall Heat Transfer Coefficient (cont.)
the internal flow is turbulent and the DittusBoelter correlation gives
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_1127122567.unknown
The overall fin efficiency is
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_1046423368.unknown
_1034651414.unknown
From Eq. 11.4,
_1034651715.unknown
With
_1034651066.unknown

Problem: Overall Heat Transfer Coefficient (cont.)
Hence
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_1046423615.unknown
_1046423484.unknown
It follows that
_1046423700.unknown
_1046423701.unknown
and

Problem: Overall Heat Transfer Coefficient (cont.)
COMMENTS: (1) The gasside resistance is substantially decreased by using the fins
and q is increased.
_1127635733.unknown
(2) Heat transfer enhancement by the fins could be increased further by using a material of larger k, but material selection would be limited by the large value of Tm,h.

Problem: Ocean Thermal Energy ConversionProblem 11.47: Design of a twopass, shellandtube heat exchanger to supply vapor for the turbine of an ocean thermal energy conversion system based on a standard (Rankine) power cycle. The powercycle is to generate 2 MWe at an efficiency of 3%. Ocean water enters the tubes of the exchanger at 300K, and its desiredoutlet temperature is 292K. The working fluid of the powercycle is evaporated in the tubes of the exchanger at itsphase change temperature of 290K, and the overall heat transfercoefficient is known.
FIND: (a) Evaporator area, (b) Water flow rate.
SCHEMATIC:

Problem: Ocean Thermal Energy Conversion (cont)
ASSUMPTIONS: (1) Negligible heat loss to surroundings, (2) Negligible kinetic and potential energy changes, (3) Constant properties.
PROPERTIES: Table A6, Water (
= 296 K): cp = 4181 J/kg(K.
_1035542590.unknown
ANALYSIS: (a) The efficiency is
_1035542652.unknown
Hence the required heat transfer rate is
_1035542707.unknown
Also
_1035542736.unknown
and, with P = 0 and R = (, from Fig. 11.10 it follows that F = 1. Hence

Problem: Ocean Thermal Energy Conversion (cont)
b) The water flow rate through the evaporator is
_1035542973.unknown
_1035543048.unknown
COMMENTS: (1) The required heat exchanger size is enormous due to the small temperature differences involved,
(2) The concept was considered during the energy crisis of the mid 1970s but has not since been implemented.