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Optimization of the finned double-pipe heat exchanger using nanofluids as working fluids

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Abstract

The heat exchanger pipe diameter has a significant effect on the flow characteristics as well as on the initial investment, operation and overall cost. Increasing fin dimensions increases the annulus hydraulic diameters. Even though the total volume of the heat exchanger remains unchanged between the finned and bare designs, the heat duty increases with increased heat transfer area for the finned design. The fins should be designed, and the dimensions should be calculated with special attention for different flow rates and heat exchanger dimensions. In this study, number, geometry and dimensions of the fins are determined using the algorithms available in the literature. The operational condition optimization is carried out accompanied with the cost analysis. In addition, the effects of the types of working fluids and fouled and clean cases are investigated for the total heat transfer enhancement in parallel with performance, lifetime and cost issues. A detailed analysis is presented for finned and unfinned double-pipe heat exchanger models for pure engine oil and its nanofluid mixtures with Ti, TiO2, Cu, CuO, Al and Al2O3 nanoparticles, multi-wall carbon nanotubes and graphene nanosheet having a constant particle concentration in the liquid phase. The nanofluid is flowing in annulus side, whereas the seawater is flowing in the tube side. It is observed that both the pressure drop and the pumping power increase with the increasing fin number and decrease with the cleanliness factor, whereas the total tube number decreases with increasing fin number. It is found that different types of nanofluids affect the cost and optimum annulus side velocity significantly. The results are summarized in several figures that consider the increasing Reynolds number with the cleanliness factor, the heat transfer coefficient and the pressure drop, the friction factor with changing mass flow rate and the cost values with corresponding annulus side velocities. Finally, the overall characteristics of the trend lines are provided in the figures.

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Abbreviations

A :

Heat transfer surface area, m2

A c :

Net free flow area, m2

C :

Pipe element price, USD

CF:

Cleanliness factor

c p :

Specific heat at constant pressure, J kg−1 K−1

d :

Diameter, m

d e :

Equivalent diameter for heat transfer, m

d h :

Hydraulic diameter for pressure drop, m

f :

Friction factor

h :

Convective heat transfer coefficient, W m−2 K−1

H f :

Height of the fin, m

k :

Thermal conductivity, W m−1 K−1

L :

Tube length, m

m :

Fin parameter in Eq. (27)

\(\dot{m}\) :

Mass flow rate, kg s−1

n :

Number of tubes

N f :

Number of fins per tube

N t :

Number of tubes in one leg of heat exchanger

Nu:

Nusselt number

P :

Pumping power, W

Pr:

Prandtl number

P w :

Wetted perimeter for pressure drop, m

P h :

Wetted perimeter for heat transfer, m

\(\dot{Q}\) :

Heat rejection duty, W

R I :

Fouling resistance for tube side, m2 W−1 °C−1

R fo :

Fouling resistance for annulus side, m2 W−1 °C−1

Re:

Reynolds number

s :

Power in Eq. (36) and Eq. (40)

T :

Temperature

T w :

Wall temperature

U :

Overall heat transfer coefficient based on total external surface area, W m−2 K−1

w :

Flow velocity, m s−1

ΔP :

Pressure drop, Pa

ΔT :

Temperature difference, K

Δ:

Fin thickness, m

\(\eta_{\text{f}}\) :

Fin efficiency,  %

\(\eta_{\text{o}}\) :

Overall efficiency,  %

\(\eta_{\text{p}}\) :

Pump efficiency,  %

θ y :

Amortization period, year

θ h :

Operating period, hour

μ :

Dynamic viscosity, Pa s

ρ :

Mass density, kg m−3

Φ:

Particle concentration,  %

c:

Cross section

e:

Equivalent

el:

Electric

f:

Fluid

h:

Hydraulic

i:

Inside

in:

Inlet

m:

Momentum

nf:

Nanofluid

o:

Outside, overall

oc:

Clean conditions

of:

Fouled conditions

ord:

Ordinal number

out:

Outlet

p:

Parallel

pa:

Particle

t:

Total

tb:

Tube

u:

Unfinned

w:

Wall, wetted

1:

Tube side, investment

2:

Annulus side, operating

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Acknowledgements

The fourth author acknowledges the financial support provided by the “Research Chair Grant” National Science and Technology Development Agency (NSTDA), the Thailand Research Fund (TRF) and King Mongkut’s University of Technology Thonburi through the ‘‘KMUTT 55th Anniversary Commemorative Fund.”

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Authors and Affiliations

  1. Heat and Thermodynamics Division, Department of Mechanical Engineering, Faculty of Mechanical Engineering, Yildiz Technical University (YTU), Yildiz, 34349, Besiktas, Istanbul, Turkey

    Ahmet Selim Dalkılıç & Güven Özçelik

  2. Department of Mechatronics Engineering, Faculty of Mechanical Engineering, Yildiz Technical University (YTU), Yildiz, 34349, Besiktas, Istanbul, Turkey

    Hatice Mercan

  3. Department of Mechanical Engineering, Faculty of Engineering and Architecture, Istanbul AREL University, Tepekent, 34537, Buyukcekmece, Istanbul, Turkey

    Güven Özçelik

  4. Fluid Mechanics, Thermal Engineering and Multiphase Flow Research Lab. (FUTURE), Department of Mechanical Engineering, Faculty of Engineering, King Mongkut’s University of Technology Thonburi, Bangmod, Bangkok, 10140, Thailand

    Somchai Wongwises

  5. The Academy of Science, The Royal Society of Thailand, Sanam Suea Pa, Dusit, Bangkok, 10300, Thailand

    Somchai Wongwises

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  1. Ahmet Selim Dalkılıç
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  2. Hatice Mercan
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  4. Somchai Wongwises
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Correspondence to Ahmet Selim Dalkılıç or Hatice Mercan.

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Dalkılıç, A.S., Mercan, H., Özçelik, G. et al. Optimization of the finned double-pipe heat exchanger using nanofluids as working fluids. J Therm Anal Calorim 143, 859–878 (2021). https://doi.org/10.1007/s10973-020-09290-x

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