# Parametric Study of Entropy Generation in a Fluid with Internal Heat Generation between Two Rotating Cylinders Subjected to Convective Cooling at the Surface

Authors: M. El Haj Assad; Hakan F. Oztop
Journal: ISRN Chemical Engineering
 (2012)

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## Abstract

Entropy generation analysis of a steady fluid flow with internal heat generation between two rotating cylinders was presented. The surface of the inner cylinder was kept at constant temperature while the surface of the outer cylinder was exposed to convection cooling. Analytical expressions for velocity and temperature distributions within the fluid were obtained. The effects of velocity ratio, Biot number, Brinkman number and other dimensionless parameters on the temperature distribution and local and total entropy generation rates were investigated and the results were presented graphically.


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## Body

## 1. Introduction

Heat transfer analysis in annuli with rotating inner and outer cylinders is an important research field and has a wide range of many engineering applications such as swirl nozzles, commercial viscometers, journal bearings, chemical mixing devices, and electric motors.Entropy generation and its minimization have been considered as an effective tool to improve the performance of any heat transfer process. Entropy generation minimization of diabatic distillation column with trays has been investigated using a new approach [1] in which the exchanged heat has been considered as a control variable instead of temperature. A numerical study of mixed convection and entropy generation in Poiseulle-Benard channel in different angles has been presented [2]. A numerical study of entropy generation using 3D in the case of liquid metal laminar natural convection in a differentially heated cubic cavity and in the presence of an external magnetic field orthogonal to the isothermal walls has been carried out [3]. A numerical analysis has been presented to study laminar-forced convection and entropy generation in a helical coil with constant wall heat flux [4] where optimal Reynolds numbers were found to be related to the wall heat flux. Entropy generation analysis has been applied to a natural convection cooling of heat source mounted inside a cavity [5]. Second law analysis has been used to obtain analytically the entropy generation for a laminar flow in semicylindrical ducts subjected to constant wall heat flux [6]. Entropy generation due to convection and conduction mode of heat transfer (conjugate natural convection) in enclosures bounded by vertical solid walls with different thicknesses has been studied [7]. Entropy generation has been obtained analytically by using second law analysis for a laminar flow in rectangular ducts with semicircular ends [8]. In the analysis [8], the effects of constant wall heat flux and constant wall temperature as boundary conditions have been studied.Entropy generation analysis in an annuli flow with inner cylinder at rest, and rotating outer cylinder has been presented [9] where the entropy generation in the system due to the heat transfer has been considered and the entropy generation due to fluid friction has been neglected. An experimental study of heating fluid between two concentrating cylinders with cavities with rotating inner cylinder and outer cylinder at rest has been conducted [10]. Entropy generation for nonlinear viscoelastic fluid in concentric rotating cylinders subjected to different boundary conditions has been investigated [11] in which the results show that entropy generation number increases with increasing Brinkman number. The problem of natural convection of gas in an annulus between two horizontal coaxial cylinders at rest with uniform internal heat generation and different temperatures at the boundaries has been introduced and investigated numerically [12]. The effect of variable viscosity of fluid flow on entropy generation between two concentric cylinders at rest with a convective cooling at the outer cylinder has been investigated [13]. Entropy generation analysis inside concentric annuli with relative rotation has been presented [14] without investigating the effect of internal heat generation within the fluid and without considering the exact fluid temperature in calculating the entropy generation rate. More research studies related to entropy generation can be found in the literature [15–18].As can be seen from the above research works related to annular flow between two rotating cylinders, the effect of internal heat generation on local and total entropy generation rates has not yet been investigated in the literature and this study is considered as a first approach to consider that effect.


## 2. Mathematical Formulation

In this section, We developed a mathematical model for the flow and thermal characteristics of a fluid between two rotating cylinders which rotate in the same direction. The schematic diagram of the physical problem is illustrated in Figure1. It is assumed that the fluid thermal properties are temperature independent. The flow considered in the present is one-dimensional, steady, laminar and purely tangential. The radius of the inner cylinder is r1 and of the outer cylinder is r2. It is assumed that the outer cylinder wall thickness is negligible and has the same thermal conductivity as that of the fluid. The inner and the outer cylinders are rotating at angular velocities ω1 and ω2, respectively. The inner fluid surface is kept at temperature T1 while the outer surface is subjected to convection by a coolant at temperature T∞.Figure 1
Schematic diagram of concentric rotating annuli.


### 2.1. Velocity Distribution

Under the above flow conditions, the momentum equation can be written as(1)d2vθdr2+1rdvθdr-vθr2=0,
where vθ is the tangential velocity. The boundary conditions are
(2)atr=r1:vθ=v1=ω1r1,(3)atr=r2:vθ=v2=ω2r2.
Consider the following dimensionless parameters:
(4)w=v2v1,R=rr1,z=r2r1,V=vθv1.
The momentum equation of (1) can be written in a dimensionless form as
(5)d2VdR2+1RdVdR-VR2=0.
Consider the following dimensionless boundary conditions:
(6)V(R=1)=1,V(R=z)=w.
The solution of (5) subjected to the boundary conditions in (6) is obtained as
(7)V=z2-R2+wzR2-wzR(z2-1).


### 2.2. Temperature Distribution

The energy equation of the fluid with internal heat generation between the two rotating cylinders can be expressed as(8)1rddr(rλdTdr)+q˙+μϕ=0,
where q˙ is the internal heat generation, λ is the thermal conductivity, μ is the dynamic viscosity, and ϕ is the viscous dissipation. The viscous dissipation is
(9)ϕ=[rddr(vθr)]2.
The thermal boundary conditions are
(10)T(r=r1)=T1,-λ(dTdr)r=r2=α[T(r=r2)-T∞],
where α is the convection heat transfer coefficient. In order to express (8) in a dimensionless form, the following dimensionless parameters are introduced as
(11)θ=T-T∞T1-T∞,Bi=αr2λ,Pr=μcpλ,Ec=v12cp(T1-T∞),Br=PrEc,Q=q˙r12λ(T1-T∞),
where Bi is the Biot number, Br is the Brinkman number, Ec is the Eckert number, Pr is the Prandtl number, Q is the dimensionless internal heat generation, and cp is the specific thermal capacity. Using the parameters of (11), (8) can be rewritten as
(12)d2θdR2+1RdθdR=-Q-Br[dVdR-VR]2,
with the dimensionless thermal boundary conditions as
(13)θ(R=1)=1,(dθdR)R=z=-Bizθ(R=z).
The solution of (12) can be obtained as
(14)θ=-Q4R2-D2Br4R2+C1ln(R)+C2,
where
(15)C1=-Bi[-(Q/4)z2-D2Br/4z2+D2Br/4+Q/4+1]1+Biln(z)+(Q/2)z2-D2Br/2z21+Biln(z),(16)C2=1+Q4+D2Br4,(17)D=2z(w-z)z2-1.


## 2.1. Velocity Distribution

Under the above flow conditions, the momentum equation can be written as(1)d2vθdr2+1rdvθdr-vθr2=0,
where vθ is the tangential velocity. The boundary conditions are
(2)atr=r1:vθ=v1=ω1r1,(3)atr=r2:vθ=v2=ω2r2.
Consider the following dimensionless parameters:
(4)w=v2v1,R=rr1,z=r2r1,V=vθv1.
The momentum equation of (1) can be written in a dimensionless form as
(5)d2VdR2+1RdVdR-VR2=0.
Consider the following dimensionless boundary conditions:
(6)V(R=1)=1,V(R=z)=w.
The solution of (5) subjected to the boundary conditions in (6) is obtained as
(7)V=z2-R2+wzR2-wzR(z2-1).


## 2.2. Temperature Distribution

The energy equation of the fluid with internal heat generation between the two rotating cylinders can be expressed as(8)1rddr(rλdTdr)+q˙+μϕ=0,
where q˙ is the internal heat generation, λ is the thermal conductivity, μ is the dynamic viscosity, and ϕ is the viscous dissipation. The viscous dissipation is
(9)ϕ=[rddr(vθr)]2.
The thermal boundary conditions are
(10)T(r=r1)=T1,-λ(dTdr)r=r2=α[T(r=r2)-T∞],
where α is the convection heat transfer coefficient. In order to express (8) in a dimensionless form, the following dimensionless parameters are introduced as
(11)θ=T-T∞T1-T∞,Bi=αr2λ,Pr=μcpλ,Ec=v12cp(T1-T∞),Br=PrEc,Q=q˙r12λ(T1-T∞),
where Bi is the Biot number, Br is the Brinkman number, Ec is the Eckert number, Pr is the Prandtl number, Q is the dimensionless internal heat generation, and cp is the specific thermal capacity. Using the parameters of (11), (8) can be rewritten as
(12)d2θdR2+1RdθdR=-Q-Br[dVdR-VR]2,
with the dimensionless thermal boundary conditions as
(13)θ(R=1)=1,(dθdR)R=z=-Bizθ(R=z).
The solution of (12) can be obtained as
(14)θ=-Q4R2-D2Br4R2+C1ln(R)+C2,
where
(15)C1=-Bi[-(Q/4)z2-D2Br/4z2+D2Br/4+Q/4+1]1+Biln(z)+(Q/2)z2-D2Br/2z21+Biln(z),(16)C2=1+Q4+D2Br4,(17)D=2z(w-z)z2-1.


## 3. Entropy Generation Analysis

The local entropy generation rate due to fluid temperature gradient and fluid friction (viscous dissipation) is given as [19]
(18)S˙′′′=λT2(dTdr)2+μT[rddr(vθr)]2.
The first term of (18) corresponds to the heat transfer irreversibility and the second term corresponds to the irreversibility due to viscous dissipation. Equation (18) considers the exact local temperature of the fluid obtained by (14). Using the dimensionless parameters defined in (4) and (11), the entropy generation number can be obtained from (2) as
(19)Ns=r12S˙′′′λ=1(θ+t/(1-t))2(dθdR)2+Br(θ+t/(1-t))[dVdR-VR]2,
where t=T∞/T1 is the temperature ratio of the coolant fluid to the inner cylinder surface temperature. The total entropy generation is expressed as
(20)S˙=∫AS˙′′′LdA,
where A is the cross-sectional area of the gab between the cylinders and L is the length of the rotating cylinders. Substituting (19) into (20), the total entropy generation rate can be obtained as
(21)S˙=2πλLr12∫r1r2Nsrdr.
Equation (21) can be written in a dimensionless form as
(22)Nt=S˙2πλL=∫1zNsRdR,
where Nt is the dimensionless total entropy generation rate.


## 4. Results and Discussion

Entropy generation of a steady fluid flow with internal heat generation between two rotating cylinders is presented for different parameters. The tangential velocity profiles along the radial direction for the radius ratio (z) z=2 and z=3 are presented in Figures 2(a) and 2(b), respectively, at different velocity ratio (w) values. The figures show that the velocity decreases as R increases for w=0 and w=0.5 but the velocity has a minimum value for w=1. This minimum velocity can be obtained from the velocity expression given in (7) at R=[z(z-w)/(wz-1)]1/2. It should be remembered that maximum value of R is equal to z and the value of w·z should always be larger than 1 to insure that such a minimum in velocity exists.Velocity distribution ((a)z=1; (b) z=3).
(a)
(b)The dimensionless temperature distributions of the rotating fluid as function ofR are shown in Figures 3–5 for different set of parameters such as Brinkman number (Br), Biot number (Bi), and dimensionless internal heat generation (Q) at different velocity ratio w values. Figure 3 shows the effect of Brinkman number on the temperature variation for Q=1, Bi=1, and z=3. The figure shows that as Brinkman number increases the temperature increases. The difference between the temperature profiles widens as Brinkman increases, and this difference is very clear in Figure 3(c) for Br=5. In all Figures 3(a)–3(c), the temperature has a maximum value at a certain R location. The temperature of the outer rotating fluid surface increases as w decreases for the same Br and R values but this temperature increases as Brinkman increases for the same w and R values.Temperature distribution ((a)Br=0.5; (b)  Br=1; (c) Br=5).
(a)
(b)
(c)Temperature distribution ((a)Bi=0.5; (b) Bi=5).
(a)
(b)Temperature distribution ((a)Q=0; (b) Q=2).
(a)
(b)The effect of Biot number on the fluid temperature distribution as function ofR is given in Figure 4 for Q=1, Br=1, and z=3. It is shown in Figure 4 that an increase in Biot number results in a decrease in fluid temperature at the outer surface due to better convection cooling. In Figure 4, the fluid temperature has a maximum value for all w and Bi values considered in this study. This maximum temperature is closer to the outer surface at lower Biot number due to the lower heat convection to the surroundings. When Biot number increases in more heat will be transferred to the surroundings resulting in a higher fluid temperature gradient at the outer fluid surface as can be seen in Figures 4(a) and 4(b). The maximum temperature is shifted closer to the inner surface as Biot number increases.The maximum temperature is an important factor because the contribution of thermal effect on entropy generation will be equal to zero at that maximum value. Figures5(a) and 5(b) show the temperature distribution for the case with no internal heat generation (Q=0) and with internal heat generation (Q=2), respectively, for Bi=1, Br=1, and z=3. It is shown in Figure 5(b) that the internal heat generation results in higher fluid temperature. The maximum temperature value is reached at higher R value (closer to the outer surface) as Q increases.The variations of local entropy generation numberNs with R are shown in Figures 6–8 for the same set of parameters considered in Figures 3–5. Figures 6(a) and 6(c) correspond to Figures 3(a) and 3(c), Figures 7(a) and 7(b) correspond to Figures 4(a) and 4(b), and Figures 8(a) and 8(b) correspond to Figures 5(a) and 5(b). Figure 9 shows the effect of the temperature ratio t on the local entropy generation number for Q=1, Br=1, Bi=1, and z=3. Figures 6–9 show that the local entropy generation number decreases to reach a minimum value at a certain R location and then increases very slowly as the outer surface is approached. It can be seen from (19) that even if we have maximum temperature and minimum velocity at the same R location, this will not result in zero entropy generation, that is, Ns=(Br/(θ+t/(1-t)))[V/R]2.Local entropy generation number distribution ((a)Br=0.5; (b) Br=1; (c) Br=5).
(a)
(b)
(c)Local entropy generation number distribution ((a)Bi=0.5; (b) Bi=5).
(a)
(b)Local entropy generation number distribution ((a)Q=0; (b) Q=2).
(a)
(b)Local entropy generation number distribution ((a)t=0.7; (b) t=0.9).
(a)
(b)Figures6–9 also show that the effect of w on local entropy generation number is higher at the inner fluid surface and this effect vanishes as the outer surface is reached. The total entropy generation variations with w are shown in Figures 10–13 for different set of parameters. Figure 10 corresponds to Figure 6, Figure 11 corresponds to Figure 7 except one more case for Bi=1 is added, and Figure 12 corresponds to Figure 8 except one more case for Q=1 is added. Figure 13 corresponds to Figure 9 except one more case for t=0.8 is added. It is shown in these figures that increasing Brinkman number results in an increase in the total entropy generation, increasing Biot number results in a decrease in the total entropy generation, decreasing internal heat generation yields in lower total entropy generation, and decreasing temperature ratio value t results in an increase in the total entropy generation. Figures 10–13 show that there exists a minimum total entropy generation for all the set of parameters considered in this study and this minimum occurs at w=3.Figure 10
Effect ofBr on dimensionless total entropy generation rate.Figure 11
Effect ofBi on dimensionless total entropy generation rate.Figure 12
Effect ofQ on dimensionless total entropy generation rate.Figure 13
Effect oft on dimensionless total entropy generation rate.


## 5. Conclusions

A mathematical model of a fluid with internal heat generation between two rotating cylinders has been developed for velocity, temperature, local entropy generation rate, and total entropy generation rate. It has been proved that the local and the total entropy generation rates have minimum values for all the parameters considered in this work. It is concluded that decreasing Brinkman number, increasing Biot number, decreasing the internal heat generation, and increasing the temperature ratiot result in lower total entropy generation rate. It is believed that the results of this study will be of great importance in engineering applications.



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