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Numerical analysis of a heat exchanger with curved segmental baffle and Cassini oval cross-section tubes in various bundle arrangements

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Abstract

An increase in the thermal performance of heat exchangers leaves a dramatic influence on the energy consumption of industries, addressing why such studies are of interest. The current numerical work, therefore, aims to increase heat transfer in a shell-and-tube heat exchanger by innovative, novel topological changes, using Cassini cross-sectional tubes and proposed segmental curved baffles. Cassini oval and triple Cassini cross sections in horizontal, vertical, and oblique tube arrangements are applied, not investigated yet. Further, the heat transfer is augmented by adding carbon nanotubes to the pure water. The inlet Reynolds number is chosen between 10,000 and 30,000 and the nanotube volume fraction falls in the range of 0 and 2%. The friction factor, Nusselt number, performance evaluation criteria as well as the second law of thermodynamics analysis, including thermal and frictional entropy generation, are monitored. The Witte–Shamsunder efficiency is also detected to consider both the first and second low. Using the water as the working fluid and irrespective of the baffle geometry, the case with the triple Cassini cross-section tube has the highest value of the Nusselt number up to 100, while the circular tube case sets in the lowest rank, with the value near 50. Additionally, the circular tubes show the worst PEC value, while triple Cassini tubes pretend as the most valuable case, with values of 40–50% higher than those of circular tubes, highlighted more at the lower Reynolds numbers. The cases with curved baffles make the PEC increment in all cases up to 15% compared to those with simple baffles. The entropy generation reduces by using the curved baffles up to 20%.

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Abbreviations

CNT:

Carbon nanotube

EEC:

Efficiency evaluation criteria

PEC:

Performance evaluation criteria

RNG:

Renormalization group

T.K.E.:

Turbulent kinetic energy

in:

Inlet

Lm:

Logarithmic mean temperature difference

nf:

Nanofluid

W-S:

Witte–Shamsunder

A:

Area, m2

A o :

Total heat transfer area, m2

C p :

Specific heat, j kg−1 K−1

d:

Diameter, m

d h :

Hydraulic diameter, m

Exloss :

Exergy loss

f :

Friction factor

h :

Convection heat transfer coefficient, w m−2 K−1

k :

Turbulent kinetic energy, m2 s−2

\(\dot{m}\) :

Mass flow, kg/s

N g :

Dimensionless volumetric entropy generation

Nu:

Nusselt number

P :

Pressure, Pa

P k :

Turbulent generation, m2 s−3

Pr:

Prandtl number

Q:

Thermal energy, j

r:

Radius, m

Re:

Reynolds number

\({\dot{\mathrm{S}}}_{\mathrm{g}}^{\mathrm{^{\prime}}\mathrm{^{\prime}}}\) :

Entropy generation rate, W K−1 m−3

T:

Temperature, K

T o :

Ambient temperature, K

u :

Velocity component, m s−1

x :

Coordinate component, m

ε :

Shape factor, m−1

ε ijk :

Turbulent dissipation rate, m2 s−3

λ :

Levi-Civitia symbol

φ :

Conduction heat transfer coefficient, w m−1 K−1

β :

Nanofluid volume friction

ρ :

Density, kg m−3

μ:

Dynamic viscosity, kg m−1 s−1

\({\upsilon }_{\mathrm{t}}\) :

Kinematic viscosity, m2 s−1

τw :

Wall shear stress, Pa

ξ:

Vorticity, s−1

bf:

Base flow

eff:

Effective

i, j, k:

Dummy indexes

lm:

Logarithmic mean temperature difference

nf:

Nanofluid

t:

Turbulent

o:

Base state

out:

Outlet

p:

Particle

Δp:

Frictional

Δt:

Thermal

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Authors and Affiliations

  1. Department of Mechanical Engineering, University of Kashan, Kashan, Iran

    Sajjad Mazdak, Ghanbar Ali Sheikhzadeh & Abolfazl Fattahi

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  1. Sajjad Mazdak
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  2. Ghanbar Ali Sheikhzadeh
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Correspondence to Ghanbar Ali Sheikhzadeh.

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Mazdak, S., Sheikhzadeh, G.A. & Fattahi, A. Numerical analysis of a heat exchanger with curved segmental baffle and Cassini oval cross-section tubes in various bundle arrangements. J Therm Anal Calorim 148, 8459–8476 (2023). https://doi.org/10.1007/s10973-023-12062-y

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