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Advances in triple tube heat exchangers regarding heat transfer characteristics of single and two-phase flows in comparison to double tube heat exchangers part 2

  • Dogan Akgul ORCID logo , Hatice Mercan ORCID logo , Ozgen Acikgoz ORCID logo and Ahmet Selim Dalkilic ORCID logo EMAIL logo
Published/Copyright: October 30, 2023
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Abstract

Triple concentric-tube heat exchangers are often used in a variety of industries, including HVAC, food and beverage manufacturing, and chemical processing. They may also be utilized in applications requiring thermal homogeneity, such as food and pharmaceutical production. They are appropriate for a number of applications since they may be constructed to withstand a range of temperatures and pressures. The purpose of this study is to examine the most current papers, covering single- and two-phase flows having pure and nanofluids with a particular emphasis on the heat transfer and hydrodynamic properties. The use of advanced surfaces improves heat transfer with respect to smooth surfaces, and the use of nanofluids has a positive influence on heat transfer characteristics with the increase in nanoparticle volume concentration since nanoparticles rise thermal conductivity, heat transfer area, and Brownian motion. The practical calculation methodologies, proposed correlations for calculating the Nusselt number and friction factor in triple ones are shown. There are insufficient studies to comment on pressure drop features, and correlations for Nusselt numbers and friction factors that are only known for single-phase flows. The research indicates that the heat transfer characteristics of triple concentric-tube heat exchangers surpass those of double tube heat exchangers. Important progress is supposed to occur for the design and utilization of triple ones as a substitute for double ones soon. Finally, there are a limited number of experimental two-phase flow studies in triple ones. It is essential to work on this topic to meet the important lack in open sources.


Corresponding author: Ahmet Selim Dalkilic, Department of Mechanical Engineering, Faculty of Mechanical Engineering, Yildiz Technical University (YTU), Istanbul 34349, Türkiye, E-mail:

Award Identifier / Grant number: FOA-2021-4270

Acknowledgments

The authors would like to acknowledge that this paper is submitted in partial fulfilment of the requirements for PhD degree at Yildiz Technical University.

  1. Research ethics: Not applicable.

  2. Author contributions: The authors have accepted responsibility for the entire content of this manuscript and approved its submission.

  3. Competing interests: The authors states no conflict of interest.

  4. Research funding: This work was supported by a grant of the Yildiz Technical University Scientific Research Project Coordination Unit, YTU-BAPK, Project no: FOA-2021-4270.

  5. Data availability: Not applicable.

Nomenclature

A

heat transfer surface area, m2

C

heat capacity, W/°C

c p

specific heat at constant pressure, J/kg °C

D

tube diameter, m

D h

hydraulic diameter, m

f

friction factor

h

heat transfer coefficient, W/m2 °C

h fg

enthalpy of vaporization, J/kg

k

thermal conductivity, W/m°C

L

tube length, m

m ˙

mass flow rate, kg/s

Nu

Nusselt number

P

pressure, Pa

r

tube radius, m

Re

Reynolds number

T

temperature, °C

Q ˙

heat transfer rate, W

U

overall heat transfer coefficient, W/m2 °C

V

average velocity, m/s

x

vapor quality

W ˙

pumping power, W

Greek letters

ΔP

pressure drop

ρ

density, kg/m3

μ

dynamic viscosity, kg/ms

ε

effectiveness

η

performance index

Acronyms

CFD

computational fluid dynamics

DTHEX

double tube heat exchanger

GNP

graphene nanoplatelet

HEX

heat exchanger

HT

heat transfer

LMTD

logarithmic mean temperature difference

MWCNT

multi-walled carbon nanotube

NTU

number of transfer units

TTHEX

triple tube heat exchanger

Subscripts

1

innermost tube

1i

inner side of innermost tube

1o

outer side of innermost tube

2

outermost tube

i

inner side of middle tube

2o

outer side of middle tube

avg

average

c

fluid flowing through the middle tube

i

inlet

h

hot

lm

logarithmic

max

maximum

min

minimum

o

outlet

o1

according to innermost tube’s outer surface area

o2

according to middle tube’s outer surface area

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Received: 2023-10-10
Published Online: 2023-10-30
Published in Print: 2023-12-15

© 2023 Walter de Gruyter GmbH, Berlin/Boston

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