Open AccessArticle

Entropy Generation and Mixed Convection of a Nanofluid in a 3D Wave Tank with Rotating Inner Cylinder

Ammar I. Alsabery

Mohammed J. Alshukri

Nasr A. Jabbar

Adel A. Eidan

and

Ishak Hashim

^4,*

Refrigeration & Air-Conditioning Technical, Engineering Department, The Islamic University, Najaf 540011, Iraq

Department of Mechanical Engineering, Faculty of Engineering, Kufa University, Najaf 54002, Iraq

Najaf Technical College, Al-Furat Al-Awsat Technical University, Najaf 540011, Iraq

⁴

Department of Mathematical Sciences, Faculty of Science & Technology, Universiti Kebangsaan Malaysia, Bangi 43600, Malaysia

Author to whom correspondence should be addressed.

Energies 2023, 16(1), 244; https://doi.org/10.3390/en16010244

Submission received: 18 October 2022 / Revised: 29 November 2022 / Accepted: 22 December 2022 / Published: 26 December 2022

(This article belongs to the Section J1: Heat and Mass Transfer)

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Abstract

The generation of entropy and mixed convection in a nanofluid-filled 3D wavy tank containing a rotating cylinder is investigated. The top wavy surface of the tank is heated and all vertical surfaces are assumed to be adiabatic, while the bottom horizontal surface remains isothermally cold. The tank contains a solid cylinder and is saturated with an Al₂O₃–water nanofluid. The numerical simulations using the FEM are performed for the Richardson number (

0.01 \leq R i \leq 100

), nanoparticle volume fraction (

0 \leq ϕ \leq 0.04

) and number of oscillations (

0 \leq N \leq 4

). The numerical results of the present work are given in terms of 3D streamlines, isotherms and local entropy generation, as well as average heat transfer and Bejan number. The results show that for low values of the Richardson number and oscillation, heat transfer enhancement can be achieved by increasing the nanoparticle volume fraction.

Keywords:

combined convection; entropy generation; rotating inner cylinder; 3D wave tank; nanofluid

1. Introduction

Fluid flow and heat transfer mechanisms in closed cavities are important in many engineering applications, including heat exchangers, electronics cooling, room ventilation, containment building cooling, etc. However, the use of pure fluids, such as water and ethylene glycol, has some disadvantages in terms of improving heat transfer due to low thermal conductivity. Therefore, by immersing small particles (nanoparticles) in the pure fluid, the thermophysical properties of this fluid are improved, avoiding such limitations and improving the heat transfer rate. The technology of nanofluids is used for numerous engineering purposes, for example, thermal management of vehicles, cooling of electronics, hyperthermia, biomedicine, engine cooling and heat exchangers [1,2,3,4,5,6,7,8,9,10,11]. Abu-Nada and Chamkha [12] analysed several models of variable properties of CuO–EG–water nanofluid on natural convection heat transfer characteristics. They concluded that, generally, the behaviour of the average Nusselt number was more affected by the viscosity models than the thermal conductivity models. The rotating solid cylinder in a square 2D cavity changes the thermal appearance because the thermophysical properties of the rotating cylinder have an important influence on the process of convective heat transfer [13]. The concept of heat line in heat transfer and flow in a square 2D cavity loaded with nanofluids and different states of thermal boundaries was studied by Basak and Chamkha [14]. A high heat transfer rate in a 2D cavity with an internal fixed rotating cylinder was achieved by adding a high nanoparticle concentration [15]. Sheremet et al. [16] studied entropy formation and natural convection in a 2D cavity filled with a nanofluid that contains a thermally active solid block. Alsabery et al. [17] examined the effects of non-uniform heating on convection of a nanofluid in a trapezoidal cavity. Including a rotating cylinder in a 2D lid-driven cavity can enhance the heat transfer rate [18]. Alsabery et al. [19] investigated convection of a two-phase nanofluid in a 2D cavity with a square inner body. Recently, Alsabery et al. [20] investigated the influence of the two-phase flow of nanofluids and heat source on energy transfer in a 3D cubic container with a lid and an inner solid cylinder.

Fluid flow and heat transport in complex wave-shaped cavities play an important role in various engineering processes. These include insulation of cavity surfaces, condensers in refrigerators, industrial heat radiators, grain storage bins and solar collectors and various other purposes. Cho and Chen [21] considered convection and entropy generation in a 2D wavy cavity filled with nanofluids. The convective heat transfer problem in a nanofluid-filled 2D lid-driven wavy cavity was considered by Abu-Nada and Chamkha [22]. Jassim et al. [23] showed that orthogonal sinusoidal walls of a 2D cavity gave better heat transfer performance than that of sinusoidal vertical walls. It was found that increasing the number of undulations had a positive effect on the convection of natural flow and heat transfer of nanofluids in a 2D porous cavity [24]. Kadhim et al. [25] analysed convective heat transfer of a hybrid nanofluid in a tilted 2D wavy cavity, partially filled with a porous layer. In the present work, the problem of convection and entropy generation of nanofluids in a 3D wavy cavity containing a solid rotating cylinder shall be investigated.

2. Mathematical Formulation

Consider the model of convection and entropy generation of nanofluids in a 3D wavy cavity of dimensions

L

containing a solid rotating cylinder of length

r

, as shown in Figure 1. The top wavy surface is considered isothermal. The straight horizontal bottom surface remains at a certain cold temperature, while all vertical surfaces are adiabatic. The edges of the surface are impermeable, and the space between the rotating cylinder and the wave-shaped tank is loaded with a solution of water–Al₂O₃ nanofluid. The Boussinesq approximation remains relevant. Considering the above hypotheses, the dimensionless governing equations are as follows [10]:

\nabla \cdot V = 0,

(1)

V \cdot \nabla V = - \nabla P + \frac{ρ_{f}}{ρ_{n f}} \frac{μ_{n f}}{μ_{f}} \frac{1}{R e} \nabla^{2} V + \frac{{(ρ β)}_{n f}}{ρ_{n f} β_{f}} R i θ,

(2)

V \cdot \nabla θ = \frac{{(ρ C_{p})}_{f}}{{(ρ C_{p})}_{n f}} \frac{k_{n f}}{k_{f}} \nabla^{2} \frac{1}{R e \Pr} θ,

(3)

\nabla θ_{s} = 0,

(4)

where

V

is the dimensionless vector of velocity (

U, V, W

) to be explained. Equations (1)–(4) were made dimensionless using the following parameters:

X = \frac{x}{L}, Y = \frac{y}{L}, Z = \frac{z}{L}, V = \frac{v}{U_{0}}, θ = \frac{T - T_{c}}{T_{h} - T_{c}},

θ_{s} = \frac{T_{s} - T_{c}}{T_{h} - T_{c}}, R = \frac{r}{L}, P = \frac{p L^{2}}{ρ_{f} α_{f}^{2}}, \Pr = \frac{ν_{f}}{α_{f}},

(5)

G r = \frac{g β_{f} (T_{h} - T c) L^{3}}{ν_{f}^{2}}, R e = \frac{U_{0} L}{ν}, R i = \frac{G r}{R e^{2}} .

The associated boundary conditions are:

On the hot wavy top surface:

V = 0, θ = 1, \forall (X, Y and Z),

(6)

On the adiabatic vertical surfaces:

V = 0, \frac{\partial θ}{\partial V} = 0, \forall (X, Y and Z),

(7)

On the cold bottom surface:

V = 0, θ = 0, \forall (X, Y and Z),

(8)

θ = θ_{s}, on cylinder surface,

(9)

V = \pm Ω, \frac{\partial θ}{\partial n} = k_{r} \frac{\partial θ_{s}}{\partial n},

(10)

where

k_{r} = \frac{k_{s}}{k_{n f}}

is the thermal conductivity ratio of the cylinder and the fluid. The nanofluid’s properties are [26]:

{(ρ C_{p})}_{n f} = (1 - ϕ) {(ρ C_{p})}_{f} + ϕ {(ρ C_{p})}_{p}, α_{n f} = \frac{k_{n f}}{{(ρ C_{p})}_{n f}}, ρ_{n f} = (1 - ϕ) ρ_{f} + ϕ ρ_{p}, {(ρ β)}_{n f} = (1 - ϕ) {(ρ β)}_{f} + ϕ {(ρ β)}_{p}, \frac{μ_{n f}}{μ_{f}} = 1 / (1 - 34.87 {(d_{p} / d_{f})}^{- 0.3} ϕ^{1.03}), \frac{k_{n f}}{k_{f}} = 1 + 4.4 R e_{B}^{0.4} \Pr^{0.66} {(\frac{T}{T_{f r}})}^{10} {(\frac{k_{p}}{k_{f}})}^{0.03} ϕ^{0.66},

where

R e_{B}

is defined as

R e_{B} = \frac{ρ_{f} u_{B} d_{p}}{μ_{f}}, u_{B} = \frac{2 k_{b} T}{π μ_{f} d_{p}^{2}} .

(11)

Water’s molecular diameter (

d_{f}

) is provided as [24]:

d_{f} = 0.1 {[\frac{6 M}{N^{*} π ρ_{f}}]}^{\frac{1}{3}} .

(12)

At the heated wavy top surface, the local Nusselt number was calculated as:

N u = - \frac{k_{n f}}{k_{f}} {(\frac{\partial θ}{\partial W})}_{W},

(13)

where

W

denotes the length of the heated wavy surface as a whole.

On the heated wavy surface, the average Nusselt number is calculated as follows:

\bar{N u} = \int_{0}^{W} N u d W .

(14)

In dimensionless style, local entropy creation is extracted as follows:

S_{G E N} = \frac{k_{n f}}{k_{f}} [{(\frac{\partial θ}{\partial X})}^{2} + {(\frac{\partial θ}{\partial Y})}^{2} + {(\frac{\partial θ}{\partial Z})}^{2}]

+ \frac{μ_{n f}}{μ_{f}} N_{μ} \{2 [{(\frac{\partial U}{\partial X})}^{2} + {(\frac{\partial V}{\partial Y})}^{2} + {(\frac{\partial W}{\partial Z})}^{2}]

+ {(\frac{\partial^{2} U}{\partial Y^{2}} + \frac{\partial^{2} V}{\partial X^{2}})}^{2} + {(\frac{\partial^{2} U}{\partial Y^{2}} + \frac{\partial^{2} V}{\partial X^{2}})}^{2}\},

(15)

where

N_{μ} = \frac{μ_{f} T_{0}}{k_{f}} {(\frac{α_{f}}{L (Δ T)})}^{2}

is the irreversibility distribution ratio and

S_{G E N} = S_{g e n} \frac{T_{0}^{2} L^{2}}{k_{f} {(Δ T)}^{2}}

. The following form can be used to separate the terms in Equation (15):

S_{G E N} = S_{θ} + S_{Ψ},

(16)

HTI (heat transfer irreversibility) and FFI (fluid friction irreversibility) generate

S_{θ}

and

S_{Ψ}

of entropy, respectively.

S_{θ} = \frac{k_{n f}}{k_{f}} [{(\frac{\partial θ}{\partial X})}^{2} + {(\frac{\partial θ}{\partial Y})}^{2}]

(17)

S_{Ψ} = \frac{μ_{n f}}{μ_{f}} N_{μ} \{2 [{(\frac{\partial U}{\partial X})}^{2} + {(\frac{\partial V}{\partial Y})}^{2}] + {(\frac{\partial^{2} U}{\partial Y^{2}} + \frac{\partial^{2} V}{\partial X^{2}})}^{2}\}

(18)

GEG (global entropy generation) in this study is gained by integrating Equation (16) in charge of the domain:

G E G = \int S_{G E N} d X d Y = \int S_{θ} d X d Y + \int S_{Ψ} d X d Y .

(19)

To determine whether the irreversibility of heat transfer or fluid friction predominates, the Bejan number should be calculated. This is how the Bejan number is calculated:

B e = \frac{\int S_{θ} d X d Y d Z}{\int S_{G E N} d X d Y d Z} .

(20)

The HTI is predominant when

B e > 0.5

, while the FFI is predominant when

B e < 0.5

. Equations (1)–(4) are dimensionless equations. Equations (1)–(4) are directed to dimensionless boundary conditions. The weighted Galerkin residual FEM is used to determine Equations (6)–(10). As shown in Figure 2, the computational domain is discretized within triangular components. Figure 3 represents a flowchart of the solution method. The Newton–Raphson iteration approach was used to simplify the nonlinear components in the momentum equations. Convergence of the solution is reached when the following criteria are met:

|\frac{Γ^{i + 1} - Γ^{i}}{Γ^{i + 1}}| \leq 10^{- 6} .

In Table 1, we present some grid independence test results for the case of

Ω = 15

R i = 10

N = 3

and

ϕ = 0.02

. Based on Table 1, the G5 grid is employed for all computations. Figure 4 shows a comparison between our results and those of Costa and Raimundo [13]. The problem considered mixed convection heat transfer of pure fluid in a vertically heated cavity containing a rotating cylinder for

Ω = 500

N = 0

ϕ = 0

R = 0.2

and

\Pr = 0.7

3. Results and Discussion

Numerical results of isentropic lines, 3D streamlines and isotherms were computed for the following ranges:

0.01 < R i < 100

0 < N < 4

and

0 < ϕ < 0.04

. The other parameters were fixed:

R e = 100

Ω = 15

k_{s} = 0.76

A = 0.1

Θ = 360

\Pr = 4.623

and

R = 0.2

. The relevant properties of the Al₂O₃–water nanofluid are given in Table 2.

Figure 5 illustrates the influences of different

R i

values on 3D streamlines, isotherms and isentropy for

N = 3

and

ϕ = 0.02

. Forced convection dominates at low

R i

values (

R i = 0.01

), and the flow inside the corrugated tank is characterized by double-streamline cells arranged clockwise around the rotating cylinder. The isothermal lines appear to have a relatively low density inside and near the solid cylinder, which is affected by the flow motion. On the other hand, the isothermal lines along the surfaces of the cavity have a high density. The relatively low irreversibility of heat transfer at the right and left surfaces affected by the irrelevant heat flux and the inertial velocity is the main contributor of the entropy production. As Ri increases, the strength of the streamlines is increased, since the buoyancy forces are more effective than the viscosity forces. The strength of the isotherms also increases, leading to an increase in the space between the undulant tank and the solid cylinder. The local entropy production increases (see Figure 5d).

The effects of

N

on the 3D streamlines, isotherms and isentropy are depicted in Figure 6 for

R i = 10

and

ϕ = 0.02

. The wavenumber N has a clear impact on the flow cells, isotherms and isentropic line distributions. The flow inside the 3D wavy tank is represented by two streamline cells on the outer segments of the rotating cylinder. The isothermal lines adhere to the active surfaces of the tank with a high density. Inside the 3D cavity, there is a weak distribution of entropy generation; high-density entropy lines are formed, which are affected by a weaker thermal gradient. As N increases, the intensity of streamlines increases and the flow circulation improves. Further, the intensity of isothermal lines evolves near an active surface and a solid cylinder as

N

increases. As

N

increases, the entropy production, which is affected by the effective fluid circulation, tends to increase.

Figure 7 shows the effects of

N

\bar{N u}

for

ϕ = 0.02

and various Ri. Due to the motion of the rotating cylinder, the heat transfer rate decreases as Ri increases. Due to the available region between the rotating cylinder and the walls of the tank,

\bar{N u}

remains maximum for

N = 3

. Figure 8 illustrates the influences of different N on the Bejan number for

ϕ = 0.02

and various Ri. Increasing

R i

resulted in an improvement in the Bejan number. Higher wavenumbers contribute to an increase in the Bejan number.

Figure 9 plots

\bar{N u}

against Ri at

N = 3

and different values of

ϕ

. Due to the increase in viscous forces compared to buoyancy forces, increasing Ri results in a decreasing heat transfer rate. However, when

ϕ

increases, the thermal conductivity is also increasing, which then leads to an improvement in

\bar{N u}

. The effects of

R i

on Be for several values of

ϕ

at N = 3 are depicted in Figure 10. As Ri increases, Be increases, showing the dominance of irreversibility due to heat at high Ri. Moreover, the introduction of a tiny concentration (

ϕ = 0.01

) leads to a sharp increase in Be.

4. Conclusions

In the current study, two modes are combined, one is convection and the other is entropy generation in a 3D wavy tank loaded with nanofluids and containing an inner rotating cylinder. The Al₂O₃–water nanofluids fill the region between the 3D wavy surface of the container and the fixed rotating inner cylinder. The numerical simulations were carried out using the FEM. The main results of the study are given below:

(1): The inner rotating cylinder affects the flow behaviour, temperature distribution and isentropic lines in conductive heat transfer.
(2): The heat transfer rates remain an increasing function of the number of waves and the nanoparticle volume fraction.
(3): When the heat transfer is irreversible, the Bejan number is formed by increasing the Richardson number.

Author Contributions

Conceptualization, A.I.A. and M.J.A.; methodology, A.I.A.; software, A.I.A., M.J.A. and I.H.; validation, A.I.A.; formal analysis, A.I.A. and A.A.E.; investigation, A.I.A., M.J.A., A.A.E., N.A.J. and I.H.; resources, A.I.A. and I.H.; draft preparation, A.I.A., I.H., M.J.A., A.A.E. and N.A.J.; writing and editing, A.I.A. and I.H.; visualization, A.I.A. and M.J.A.; supervision, I.H. and A.A.E. All authors have read and agreed to the published version of the manuscript.

Funding

The work was supported by the Universiti Kebangsaan Malaysia (UKM) research grant GP-2021-K006388.

Conflicts of Interest

The authors declare no conflict of interest.

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Figure 1. (a) 2D schematic representation in the plane (X and Y axes); (b) 3D schematic representation of the physical design.

Figure 2. Grid-point distributions (a) 2D on XY-plane and (b) 3D.

Figure 3. Flowchart of the solution method.

Figure 4. (left) Costa and Raimundo [13] and (right) the present work: (a) streamlines and (b) isotherms for

Ω = 500

N = 0

ϕ = 0

R = 0.2

\Pr = 0.7

Figure 4. (left) Costa and Raimundo [13] and (right) the present work: (a) streamlines and (b) isotherms for

Ω = 500

N = 0

ϕ = 0

R = 0.2

\Pr = 0.7

Figure 5. (left) 3D streamlines, (centre) isotherms and (right) isentropic lines: (a)

R i = 0.1

, (b)

R i = 1

, (c)

R i = 10

and (d)

R i = 100

for

ϕ = 0.02

and

N = 3

Figure 5. (left) 3D streamlines, (centre) isotherms and (right) isentropic lines: (a)

R i = 0.1

, (b)

R i = 1

, (c)

R i = 10

and (d)

R i = 100

for

ϕ = 0.02

and

N = 3

Figure 6. (left) 3D streamlines, (centre) isotherms and (right) isentropic lines: (a)

N = 0

, (b)

N = 1

, (c)

N = 2

, (d)

N = 3

and (e)

N = 4

for

R i = 10

and

ϕ = 0.02

Figure 6. (left) 3D streamlines, (centre) isotherms and (right) isentropic lines: (a)

N = 0

, (b)

N = 1

, (c)

N = 2

, (d)

N = 3

and (e)

N = 4

for

R i = 10

and

ϕ = 0.02

Figure 7.

\bar{N u}

vs. Ri for various N and

ϕ = 0.02

Figure 7.

\bar{N u}

vs. Ri for various N and

ϕ = 0.02

Figure 8. Be vs.

R i

for different

N

ϕ = 0.02

Figure 8. Be vs.

R i

for different

N

ϕ = 0.02

Figure 9.

\bar{N u}

vs. Ri for various

ϕ

N = 3

Figure 9.

\bar{N u}

vs. Ri for various

ϕ

N = 3

Figure 10. Be vs. Ri for various

ϕ

N = 3

Figure 10. Be vs. Ri for various

ϕ

N = 3

Table 1. Grid independence tests:

\bar{N u}

and

B e

for

Ω = 15

R i = 10

N = 3

and

ϕ = 0.02

Table 1. Grid independence tests:

\bar{N u}

and

B e

for

Ω = 15

R i = 10

N = 3

and

ϕ = 0.02

Grid Size	Number of Elements	$\bar{N u}$	$B e$
G1	29,232	3.2125	0.75409
G2	40,048	3.1114	0.76723
G3	64,062	3.0628	0.77657
G4	117,485	3.0419	0.77769
G5	196,494	3.0286	0.78236
G6	358,668	3.0201	0.78238

Table 2. Thermophysical characteristics of water containing nanoparticles (Al₂O₃ at T = 310 K) [26].

Physical Properties	Al₂O₃	Fluid Phase (Water)
$ρ$ (kg/m³)	3970	993
$C_{p}$ (J/kgK)	765	4178
$β \times 10^{- 5} (1 / K)$	0.85	36.2
$k ({Wm}^{- 1} K^{- 1})$	40	0.628
$d_{p} (nm)$	33	0.385
$μ \times 10^{- 6} (kg / ms)$	–	695

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Alsabery, A.I.; Alshukri, M.J.; Jabbar, N.A.; Eidan, A.A.; Hashim, I. Entropy Generation and Mixed Convection of a Nanofluid in a 3D Wave Tank with Rotating Inner Cylinder. Energies 2023, 16, 244. https://doi.org/10.3390/en16010244

AMA Style

Alsabery AI, Alshukri MJ, Jabbar NA, Eidan AA, Hashim I. Entropy Generation and Mixed Convection of a Nanofluid in a 3D Wave Tank with Rotating Inner Cylinder. Energies. 2023; 16(1):244. https://doi.org/10.3390/en16010244

Chicago/Turabian Style

Alsabery, Ammar I., Mohammed J. Alshukri, Nasr A. Jabbar, Adel A. Eidan, and Ishak Hashim. 2023. "Entropy Generation and Mixed Convection of a Nanofluid in a 3D Wave Tank with Rotating Inner Cylinder" Energies 16, no. 1: 244. https://doi.org/10.3390/en16010244

APA Style

Alsabery, A. I., Alshukri, M. J., Jabbar, N. A., Eidan, A. A., & Hashim, I. (2023). Entropy Generation and Mixed Convection of a Nanofluid in a 3D Wave Tank with Rotating Inner Cylinder. Energies, 16(1), 244. https://doi.org/10.3390/en16010244

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Entropy Generation and Mixed Convection of a Nanofluid in a 3D Wave Tank with Rotating Inner Cylinder

Abstract

1. Introduction

2. Mathematical Formulation

3. Results and Discussion

4. Conclusions

Author Contributions

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