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Heat transfer enhancement through a square duct fitted with twisted tape inserts

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Abstract

Experimental investigations of friction factor and heat transfer characteristics of a square duct fitted with twisted tapes of different twist ratios have been reported at nearly uniform wall temperature conditions. The experimental results indicate that the friction factor and Nusselt number increases with decreasing twist ratio. The maximum heat transfer enhancement was observed for a minimum twist ratio. The thermohydraulic performance analysis is made to identify potential benefits of using a twisted tape.

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Abbreviations

A :

Plain duct flow cross sectional area (W·D) (m2)

C p :

Specific heat of test liquid at constant pressure (J/kg K)

D :

Depth of duct cross section (m)

D e :

Equivalent diameter of square duct, D e = 4A/2(W + D) (m)

D o :

Outside diameter of duct (m)

D 1 :

Inner diameter of annulus (m)

D 2 :

Outer diameter of annulus (m)

f :

Fanning friction factor (dimensionless)

g :

Acceleration due to gravity (m2/s)

h i :

Average convective heat transfer coefficient (W/m2 K)

Δh :

Differential height of vertical manometer (m)

H :

Axial distance for 180° rotation of the tape, m

k :

Thermal conductivity of the test liquid (W/m K)

L :

Length of test section (m)

m :

Mass flow rate of fluid (Kg/s)

N :

Number of heat transfer tubes

p :

Pumping power (kW)

ΔP :

Pressure drop across test section, ΔP = Δh(ρm − ρ)g (N/m2)

Pr :

Prandlt number, Pr = C Pμ/k, dimensionless

Q avg :

Average heat transfer rate (kW)

R 1 :

Thermohydraulic performance ratio (Nu a/Nu 0), on constant mass flow rate (dimensionless)

R 3 :

Thermohydraulic performance ratio (Nu a/Nu 0), on constant pumping power (dimensionless)

T :

Temperature (K)

∆T :

Difference in test liquid temperature (K)

v :

Average velocity of test liquid (m/s)

y :

Twist ratio of the twisted tape, y = (H/D e) (dimensionless)

W :

Width of duct, as well as insert (m)

z :

Axial distance between RTD placed at outer surface of test section

δ:

Wall thickness of duct and tape (m)

ρm :

Density of manometer fluid (Kg/m3)

ρ:

Density of test liquid (Kg/m3)

μ:

Viscosity of test liquid (Kg/ms)

Nu :

Nusselt number (defined on the basis of equivalent diameter): Nu = h i D e/k

Pr :

Prandlt number: Pr = C pμ/k

Re :

Reynolds number (defined on the basis of equivalent diameter): Re = D e vρ/μ

a :

Augmented case

b :

Bulk mean condition

c :

Cold fluid

e :

Based on equivalent diameter, D e

h :

Hot fluid

m :

Manometer fluid

ln:

Logarithmic mean

o :

Equivalent plain duct dimensionless number, Nu o, Re o

w :

Wall condition

1, 2:

Inlet condition and outlet condition of cold fluid

3, 4:

Inlet condition and outlet condition of hot fluid

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Acknowledgments

This work was done by Mr. S. V. Patil (Research Scholar) as a part of his doctoral programme during July 2007 to July 2010, at the Department of Chemical Engineering, Dr. Babasaheb Ambedkar Technological University, Lonere, under the guidance of Professor P. V. Vijay Babu. We are thankful to the authorities at Dr. BATU; for providing all facilities for completing this work.

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  1. Department of Chemical Engineering, Dr. Babasaheb Ambedkar Technological University, Lonere, Mangaon, Raigad, 402103, Maharashtra, India

    S. V. Patil & P. V. Vijaybabu

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  1. S. V. Patil
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  2. P. V. Vijaybabu
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Correspondence to S. V. Patil.

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Patil, S.V., Vijaybabu, P.V. Heat transfer enhancement through a square duct fitted with twisted tape inserts. Heat Mass Transfer 48, 1803–1811 (2012). https://doi.org/10.1007/s00231-012-1031-9

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