Mathematical Problems in Engineering

Volume 2010 (2010), Article ID 765729, 19 pages

http://dx.doi.org/10.1155/2010/765729

## Thermal Characterizations of Exponential Fin Systems

Thermal Engineering and Desalination Technology Department, King Abdulaziz University, P.O. Box 80204, Jeddah 21589, Saudi Arabia

Received 14 December 2009; Accepted 7 April 2010

Academic Editor: Francesco Pellicano

Copyright © 2010 A.-R. A. Khaled. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

#### Abstract

Exponential fins are mathematically analyzed in this paper. Two types are considered: (i) straight exponential fins and (ii) pin exponential fins. The possibility of having increasing or decreasing cross-sectional areas is considered. Different thermal performance indicators are derived. The maximum ratio between the thermal efficiency of the exponential straight fin to that of the rectangular fin is found to be 1.58 at an effective thermal length of 2.0. This ratio is even larger when exponential fins are compared with triangular and parabolic straight fins. Moreover, the maximum ratio between the thermal efficiency of the exponential pin fin to that of the rectangular pin fin is found to be 1.17 at an effective thermal length of 1.5. However, exponential pin fins thermal efficiencies are found to be lower than those of triangular and parabolic pin fins. Moreover, exponential joint-fins may transfer more heat than rectangular joint-fins especially when differences between their senders and receivers portions dimensionless indices are very large. Finally, it is found that increasing the joint-fin exponential index may cause straight exponential joint-fins to transfer more heat than rectangular joint-fins.

#### 1. Introduction

Enhancing heat transfer between solids and the adjoining fluids is one of the most important objectives in thermal engineering. Therefore, many methods were proposed to achieve this goal. Bergles [1, 2] classified these methods to active and passive methods. Active methods are those requiring external power to maintain their enhancement such as well stirring the fluid or vibrating the solid surface [3, 4]. On the other hand, the passive methods do not require external power to maintain the enhancement effect as when fins are utilized. Fins are widely used in industry, especially in heat exchanger and refrigeration industries [5–10]. Moreover, fins are used in cooling of large heat flux electronic devices as well as in cooling of gas turbine blades [11].

According to design aspects, fins can have simple designs such as rectangular, triangular, parabolic, hyperbolic, annular, and pin fins [9]. Complicated designs of fins such as spiral fins have been utilized [12, 13]. In addition, fins can be arranged uniformly on the solid surface [10]. In contrast, they can be arranged on the solid surface in complex networks as can be seen in the works of Alebrahim and Bejan [14], Almogbel and Bejan [15] and Khaled [16]. Moreover, fins can be further classified based on the number of the adjoining fluids interacting with their surfaces. Examples of works including fins surrounded by more than one adjoining fluid can be found in the works of Khaled [17, 18]. In addition, fins are usually attached to solid surfaces [5–13] but they may have roots in the solid walls [19]. To the best knowledge of the author, thermal characterization of exponential fin systems received almost negligible attention in the literature. Perhaps, this is due to the difficulty associated with manufacturing them in the past. However, the recent advancements in manufacturing technologies, which led to accurate micro- and nanosystems fabrications, may increase the opportunities of these passive systems to be implemented in industry.

In this paper, fins with exponentially varying cross-sectional areas are modeled and mathematically analyzed. Two types were considered: (i) exponential straight fins and (ii) exponential pin fins. The appropriate energy equations are solved, and the temperature distributions are found. Accordingly, different thermal performance indicators are calculated. The analysis is expanded to account for exponential joint-fins. Extensive parametric study is performed for the various controlling parameters in order to evaluate these kinds of systems.

#### 2. Problem Formulation

It should be mentioned before starting the analysis that the following assumptions are considered: (i)one-dimensional heat transfer analysis,(ii)conduction and convection heat transfer rates being governed by the Fourier law and the Newtons law of cooling, respectively,(iii)having, for exponential pin fins, ,(iv)uniform heat transfer coefficient between the fin and the fluid stream.

##### 2.1. Straight Fins with Exponentially Varying Widths

Consider a rectangular fin having a uniform thickness *t* that is much smaller than its width *H(x)* and length *L* as shown in Figure 1. The fin width varies along the fin centerline axis (*x*-axis) according to the following relationship:
where and *b* is a real number named as the exponential index. The quantity represents the fin half-width at its base ( = 0). Note that, when , the analysis corresponds to the right portion of the joint-fin shown in Figure 1 while it corresponds to the left fin portion of the joint-fin when .

The application of the energy equation [20] on a fin differential element results in the following differential equation:
where *T*, , *k*, and *h* are the fin temperature, free stream temperature, fin thermal conductivity, and the convection heat transfer coefficient between the fin and the fluid stream, respectively. The quantities and are the cross-sectional and the surface areas of the fin, respectively. Equation (2.2) has the following dimensionless form:
where and . The quantity *m* is called the fin index while is the fin temperature at its base. Equation (2.3) prescribes the following general solution:
where and* s _{2}* are equal to
where . The quantity

*X*is named as the dimensionless exponential fin parameter. It represents the ratio of the fin index,

*m*, to the exponential index,

*b*. When , cross section gradients near the base are expected to be larger than the nearby temperature gradients. The opposite scenario occurs when . The boundary conditions for an adiabatic fin tip are given by As such, the dimensionless temperature distribution has the following form:

The rate of heat transfer through the fin is called the fin heat transfer rate. For this case, it is equal to where and factors are smaller than unity. They are equal to

Utilizing (2.9) and (2.10), the fin lengths and that make and equal to 0.99, respectively, can be approximated by
where quantity *mL _{∞}* is called the effective thermal length. This is because the fin material exists after encounters negligible heat transfer rates and should be removed. The fin thermal efficiency is defined as the fin heat transfer rate divided by the fin heat transfer rate if the fin temperature is kept at . For this case, it can have the following forms:
where is the fin heat transfer rate when . Now, define the fin performance indicator as the ratio of the fin heat transfer rate when to the fin heat transfer rate for a rectangular fin having a uniform width of , uniform thickness

*t*and an infinite length. As such,

*γ*is equal to

##### 2.2. Pin Fins with Exponentially Varying Radii

Consider a pin fin of radius , as shown in Figure 2, that varies exponentially along the *x*-axis according to the following relationship:
where . As such, (2.2) changes to:
where . It can be shown that the general solution of (2.15) is
where .As such, the fin heat transfer rate is

For a fin with an infinite length (), the constants *C _{1}* and

*C*are given by This is because approaches infinity as

_{2}*x*approaches infinity; hence approaches infinity. Thus,

*C*is equal to zero.

_{1}For adiabatic fin tips, boundary conditions given by (2.6) should be satisfied. Accordingly, the constants *C _{1}* and

*C*are equal to

_{2}The fin efficiency * η_{f}* for can be found to be equal to
where is obtained from the solution of the following equation:

The fin performance indicator for this case is defined as the ratio of the fin heat transfer rate when to that of a rectangular pin fin having a uniform radius of *r _{b}* and an infinite length. It is equal to the following:

For cases when ; *X* is replaced with −*X*, and the constants *C _{1}* and

*C*for a fin with infinite length are replaced by As such, the fin thermal efficiency and the indicator when change to

_{2}##### 2.3. Pin Fins with Exponentially Decaying Temperature Distribution

Consider a pin fin having a given fin temperature distribution that varies exponentially with *x* according to the following relationship:
where and *a* is the exponential index. The dimensionless form of the energy equation has the following form
where and . By substituting (2.25) in (2.26), a differential equation of first order constructed. It has the form
where . The solution to (2.27) is given by

For engineering problems, cannot be negative and it should intersect with fin centerline at when . As such, is found to be equal to
In situations when , is minimally equal to (= *4.605/a*; ). Under this constraint, the heat transfer rate at the fin tip () is always 0.01 times the fin heat transfer rate. The rate of heat transfer through the fin base is equal to

As such, the fin thermal efficiency and the performance indicator for this case are equal to

##### 2.4. Exponential Joint-Fins

Consider an infinite exponential fin joining two different fluid streams separated by a wall of negligible thickness such as a pipe wall. The convection coefficient between the fin and the fluid stream of the heat source side (side with maximum free stream temperature ) is *h _{1}*. This coefficient is

*h*for the heat sink side (side with ) as illustrated in Figure 1. The joint-fin portion on the source side is named as the “joint-fin receiver portion” while the other portion is named as the “joint-fin sender portion”. The heat transfer rates through a straight exponential joint-fin , pin exponential joint-fin , and the pin joint-fin with exponential decaying temperature are given by the following equations: where the exponential index for the joint-fin receiver portion is considered to be negative, , while that for the sender portion is positive, . This is only for cases represented by (2.32) and (2.33).

_{2}By solving (2.32)–(2.34), the temperature at the joint-fin base () can be calculated. They are equal to
where *M* and *N* are given by
By substituting (2.35)–(2.37) in (2.32)–(2.34), the joint-fin heat transfer rates reduce to the following forms:

Define the joint-fin performance indicator as the ratio of the joint-fin maximum heat transfer rate to maximum heat transfer rate through a rectangular joint-fin with uniform cross-section (). It is mathematically defined as The heat transfer rate through the joint fin when is obtainable from [17]. It is equal to As such, can be written in the following forms:

#### 3. Discussion of the Results

Figure 3 illustrates the effects of the fin dimensionless parameter *X* on the effective thermal length for a straight exponential fin. When , increases as *X* increases. It also increases as *X* increases for the other case until *X* reaches almost unity. For both cases, approaches to an asymptotic value of 2.65 as . Similar findings can be noticed for exponential pin fins except that, when , increases as *X* increases until* X* reaches almost the value of as shown in Figure 4. On the other hand, decreases as *X* increases for pin fins with exponential decaying temperature when . For exponential pin fins, the effective thermal lengths values shown in Figure 4 are correlated to the parameter *X* by the following correlations:
These correlations were obtained using the least square method by utilizing a specialized iterative statistical software. The maximum percentage error between correlations (3.1), and (3.2) and the results shown in Figure 4 are found to be 7.5% and 13% at when , and , respectively.

Figure 5 shows the relation between the effective thermal length on the fin thermal efficiency for a straight exponential fin. It is seen that when is greater than the fin thermal efficiency of rectangular, triangular, and parabolic straight fins having the same thermal length. However, the latter thermal efficiencies are greater than the fin thermal efficiency for the straight exponential fin when . It can be shown using Figure 5 that the maximum ratio between the thermal efficiency of the exponential straight fin to that of the rectangular fin is at an effective thermal length of . For pin exponential fins with , is found to be higher than for the rectangular pin fins and lower than those for triangular and parabolic pin fins having the same thermal length as shown in Figure 6. It is recommended to operate pin exponential fins, , at smaller values of as their efficiencies increase as decreases as can be seen from Figure 6. In addition, the maximum ratio between the thermal efficiency of the exponential pin fin to that of the rectangular pin fin is found to be 1.17 at an effective thermal length of 1.5.

Exponential straight or pin fins having increasing cross-sectional areas always exhibit higher fin heat transfer rates relative to rectangular straight or pin fins as can be seen from Figures 7 and 8. However, values for those having decreasing cross-sectional areas are always smaller than unity as shown in Figures 7 and 8. Exponential joint-fins are found to transfer more heat than rectangular joint-fins fins at smaller values of *X _{1}* and larger values of

*X*as can be seen from Figures 9 and 10. On the other hand, pin joint-fins with exponentially decaying temperatures were found to be preferable over rectangular pin joint-fins at smaller

_{2}*X*and

_{1}*X*values as shown in Figure 11.

_{2}The effect of increasing the exponential index *b* on can be illustrated using Figures 9 and 10, for example, increasing *b* by a factor of 10 while maintaining the other parameters results in reductions in both *X _{1}* and

*X*values by a factor of 0.1, for example, if and . This produces and . Increasing

_{2}*b*by factor of 10 changes the joint-fin performance indicators and which are smaller than the initial values. In contrast, initially selecting and which produce and results in final and which lead to and . As such, we can conclude that only may increase as

*b*increases when is relatively large.

#### 4. Conclusions

Exponential fin systems were modeled and mathematically analyzed in this work. The possibility of having decreasing or increasing cross-sectional areas was considered. Rectangular and circular cross-sectional areas are considered. Special thermal performance indicators were derived. The maximum ratio between the thermal efficiency of the exponential straight fin to that of the rectangular fin was found to be 1.58 at an effective thermal length of 2.0. This ratio was found to be larger when the exponential fin was compared with triangular and parabolic fins. Meanwhile, the maximum ratio between the thermal efficiency of the exponential pin fin to that of the rectangular pin fin was found to be 1.17 at an effective thermal length of 1.5. However, exponential pin thermal efficiency was found to be lower than those of triangular and parabolic pin fins. In addition, exponential joint-fins may transfer more heat than rectangular joint-fins especially when differences between their senders and receivers portions dimensionless indices are very large. Finally, the summary of the closed-form solutions and correlations reported in this work as compared to those of rectangular, triangular, and parabolic fin systems are summarized in Table 1.

#### Nomenclature

a, b: | Exponential functions indices |

H: | Half-fin width |

: | Half-fin width at its base |

h: | Convection heat transfer coefficient between the fin and the fluid stream |

h:_{1} | Convection heat transfer coefficient for the joint-fin source side |

h:_{2} | Convection heat transfer coefficient for the joint-fin sink side |

I:_{n}(x) | Modified Bessel functions of the first kind of order n |

K:_{n}(x) | Modified Bessel functions of the second kind of order n |

k: | Fin thermal conductivity |

L: | Fin length |

: | Effective fin length |

m: | Fin thermal index |

: | Fin heat transfer rate |

r: | Pin fin radius |

: | Pin fin radius at its base |

T: | Fin temperature |

: | Fin base temperature |

: | Free stream temperature of the adjoining fluid |

: | Free stream temperature of the source side adjoining fluid |

: | Free stream temperature of the sink side adjoining fluid |

t: | Fin thickness |

X: | Dimensionless exponential fin parameter |

X:_{1} | Dimensionless exponential parameter of the receiver fin portion |

X:_{2} | Dimensionless exponential parameter of the sender fin portion |

x: | Coordinate axis along the fin centerline |

: | Pin fin length for exponential fins with exponentially decaying temperature |

: | Dimensionless x-coordinate. |

#### Greek Symbols

: | Dimensionless fin temperature |

: | Fin second thermal performance indicators |

: | Joint-fin thermal performance indicator |

: | Fin thermal efficiency. |

#### Acknowledgment

The author acknowledges the support of this work by King Abdulaziz City for Science and Technology (KACST).

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