Abstract
In this numerical work, the cooling performance of water–Al2O3 nanofluid (NF) in a novel microchannel heat sink with wavy walls (WMH-S) is investigated. The focus of this article is on the effect of NP diameter on the cooling efficiency of the heat sink. The heat sink has four inlets and four outlets, and it receives a constant heat flux from the bottom. CATIA and CAMSOL software were used to design the model and simulate the NF flow and heat transfer, respectively. The effects of the Reynolds number () and volume percentage of nanoparticles (Fi) on the outcomes are investigated. One of the most significant results of this work was the reduction in the maximum and average temperatures of the H-S by increasing both the and Fi. In addition, the lowest and pumping power belong to the state of low NP diameter and higher Fi. The addition of nanoparticles reduces the heat sink maximum temperature by 3.8 and 2.5% at the Reynolds numbers of 300 and 1800, respectively. Furthermore, the highest figure of merit (FOM) was approximately 1.25, which occurred at and Fi = 5%. Eventually, it was revealed that the best performance of the WMH-S was observed in the case of , volume percentage of 0.0437%, and NP diameter of 20 nm.
Introduction
Advances in technology and electronic devices have posed a formidable challenge for related industries. Increasing the power of electronic devices in many cases causes them to heat up; in some cases it reduces the performance of the devices and, in certain circumstances, causes the electronic devices to fail. Hence, it is of absolute necessity to cool this equipment properly. The application of electronic equipment in devices such as cellphones and tablets in a small space has caused heat transfer to occur in a tiny space. CPUs are one of these electronic devices and cooling them is required in all of the abovementioned devices. As their computing power enhances, the generated heat increases, and as a result, they need to be cooled down by heat sinks (H-Ss) to prevent the reduction in their performance (; Sohel Murshed and Nieto de Castro, 2017; ; ; Pordanjani et al., 2021). Owing to the tiny size of the CPUs, it is necessary to employ micro-heat sinks (MH-Ss) in this regard. In MH-Ss, the fluid flows in the microchannels and cools the H-S and consequently the electronic equipment. The growing needs of industries for MH-Ss with increased cooling capacities has led to an increment in studies in recent decades (Tullius et al., 2011; Shalchi–Tabrizi and Seyf, 2012; ; Sohel et al., 2015; ). So far, particularly in recent years, several researchers have conducted various studies on the analysis of cooling devices (; ; Peng et al., 2020; Shadloo et al., 2020; Safdari Shadloo, 2021). In one of these studies, Kumar and Singh () numerically inspected the influence of inlet and outlet on the thermal performance of an H-S. They studied an H-S comprising some parallel microchannels and utilized to cool it. Their simulation results demonstrated that augmenting the Re raises the pressure drop () in the H-S. Furthermore, they also found that increasing the volumetric flow rate of the fluid decreased the thermal resistance of the H-S.
In general, researchers have used both numerical and experimental methods for their studies in the field of fluid mechanics (; ; ; ; ). The use of experimental methods is reliable, but costly. In many numerical studies, validation has been done by the comparison of the numerical results with experimental data, and as a result, experimental work has been expanded (; ; ; Pordanjani et al., 2019; Zheng et al., 2020). Numerical research is less expensive than laboratory work and can be done in less time (; Osman et al., 2019; ; Sokhal et al., 2021).
In a myriad of conducted studies, NFs have been used to cool down different types of heat devices (; ; Sharifpur et al., 2016; ; ). NFs exhibit higher thermal conductivity than simple fluids (Toghyani et al., 2019; Vahedi et al., 2019; ; Yan et al., 2020; Pordanjani and Aghakhani, 2021). Numerous articles have recommended the application of nanotechnology in the industry (; Zhang et al., 2020; ; Tian et al., 2021; Wang et al., 2021). In this regard, studies by , Wu et al. (2016), , and can be referred. In one of these research studies, examined the influence of the presence of hybrid NFs on the performance of a rectangular H-S. They examined a heat sink comprising four similar sections, each containing five microchannels ,and a fixed thermal flux of 100 W/cm2 applied on the bottom of the H-S. Their simulation results demonstrated that increasing the NF velocity from 1 to 3 m/s decreased the of the H-S to approximately 313 K. However, they indicated that increasing the velocity greatly increased the power required to pump the fluid. In several studies, wavy walls have been used instead of smooth walls for micro-channels. Using this type of wall can enhance heat transfer (; ; ).
Nanoparticles (NPs) can be made in different dimensions in nanoscale. Many NPs have different dimensions. Alumina NPs, one of the most widely used NPs, are produced in various dimensions. The dimensions of the NPs can affect the thermal conductivity and viscosity of the NF. However, few researchers have considered the effect of the NP diameter on heat transfer, especially in heat sinks. Owing to the importance of cooling electronic devices, particularly CPUs in various functional devices, this article numerically studied a new H-S. This H-S had four similar sections where the fluid entered through 4 inlets and exited out of 4 outlets. In order to improve heat transfer, NFs were employed for cooling, and microchannels with wavy walls (WW) were also considered. The model used for single-phase viscosity and thermal conductivity also depended on the diameter of the nanoparticles (NPs),and its influence on the thermal performance of the WW in H-S has also been investigated. An innovation of this study is to use wavy channel walls in the heat sink and to assess the effect of the nanoparticle diameter on the thermal efficiency of a heat sink .
Problem Definition
The studied WMH-S, presented in Figure 1, had four inlets and four outlets. This aluminum WMH-S comprised of four similar sections. The height of the WMH-S was 0.5 mm and its overall dimension was 18 × 6.2 mm. The dimensions of the heat sink inlet are 1.8 mm, and the height of microchannels is 0.4 mm. A 0.2-mm-thick aluminum door is placed on the heat sink. Within the WMH-S, nanomaterials, NF with volume percentages ranging from 0 to 5% flowed in a Re of 300, 800, 1,300, and 1,800. A constant heat flux, from the operation of an electronic device, was applied on the bottom of the WMH-S. The aluminum used in the heat sink has a thermal conductivity of 179.96 W/m.K, a density of 2,712.6 kg/m3, and a heat capacity of 0.96 kJ/kg K ().
FIGURE 1
Governing Equations
The general equations governing the fluid flow within the H-S in the single-phase form are as follows. These equations include the conservation of mass, momentum, and energy. The fluid flow is laminar and steady, and the fluid is an incompressible Newtonian ().where , , and are velocity, temperature, and pressure, respectively. In the above equations, represents density, thermal conductivity, specific heat, and viscosity of NF. These properties are related to the NF and the following equations are employed to calculate them
In the above-mentioned equations, the indices p and f refer to the NPs and the base fluid, respectively. The NF viscosity was calculated using the following equation, which is specific to the NF ().where is the diameter of the NPs in nanometers is the volumetric percentage of the NPs. The relationship of thermal conductivity, which depends on the diameter of the NPs, was as follows (Teng et al., 2010).where is the mass percentage of NPs, and is the temperature in degree Celsius. The other properties of the fluid and NPs are provided in Figure 2.
FIGURE 2
Boundary Conditions
Figure 3 shows the boundary condition of the problem. The temperature values and boundary conditions at the inlet and outlet of the heat sink are displayed in Figure 2. The properties of water and NPs are also present in this figure. A constant flux of 100 W/cm2 is applied to the bottom of the heat sink as shown. According to Figure 2, the upper, front, and left walls of the heat sink are insulated, and the symmetry boundary condition is applied to the back and right walls.
FIGURE 3
Numerical Method and Validation
For simulating the problem model, its geometry was first drawn in CATIA software. In the next step, the mentioned geometry was transferred to CAMSOL software. Next, an all-hexagonal mesh was applied to the geometry. Then, by entering the properties of NFs and other boundary conditions in this software, the equations were solved and the necessary simulations were performed using the finite element method. The convergence criterion for Eqs 7–10 is considered. To achieve a proper grid for geometry, many changes were made to the number of elements. Finally it was found that these yield the best results in terms of the solution time as well as the accuracy of the results for the number of 1,550,000 elements. The average temperature changes of the heat sink for the number of different elements are given in Table 1 in the Re = 300 for 5% nanofluid. The trend of the changes in the heat sink average temperature shows the accuracy of selecting this number of elements.
TABLE 1
| Number of Meshes×10−3 | 370 | 980 | 1,145 | 1,310 | 1,550 | 1820 | 2014 |
|---|---|---|---|---|---|---|---|
| Heat sink average temperature | 306.89 | 304.55 | 303.31 | 302.44 | 301.95 | 301.93 | 301.93 |
Average temperature changes of heat sink for different elements at Re = 300 for Fi = 5%.
In order to validate the numerical solution, the results of the present study were compared with some articles, one of which is provided below. Thus, the average Nusselt number obtained from the present work is compared with the experimental work of for different channel lengths (Table 2). It can be observed that the amount of error between the present results and those reported by is less than 4%, indicating that the present simulations are acceptable.
TABLE 2
| Re | 135 | 390 | 655 | 915 | 1,300 | 1,530 |
|---|---|---|---|---|---|---|
| 6.07 | 7.71 | 10.12 | 12.14 | 13.15 | 13.63 | |
| Present work | 5.88 | 7.43 | 9.72 | 11.83 | 12.82 | 13.43 |
| %Err | 3.1 | 3.6 | 3.9 | 2.5 | 2.5 | 1.4 |
Average Nusselt number along the channel for the present work and .
Data Reduction
To assess the thermal performance of the H-S, it was of necessity to investigate parameters such as the heat transfer coefficient (HTC) and the pumping power PP. The convective HTC for the H-S was defined as follows (). can be obtained using , where is the inlet temperature and is the outlet temperature. is also the average temperature of the H-S bottom and represents the thermal flux applied to the WMH-S.
In the following relations, two increased ratios of HTC and PP are introduced.
In the PP relation, indicates the volumetric flow rate of the fluid and is the pressure difference on both sides of the H-S.
Other parameters can also be utilized to measure the thermal performance of H-Ss. Two important parameters in evaluating the performance of H-Ss are the thermal resistance and temperature uniformity, the relationships of which are listed below. The lower the two parameters, the better the performance of H-Ss.
In the above equations, the indices Max and Min represent the maximum and minimum temperatures on the lower surface of the H-S.
A parameter that is considered when using NFs in various devices is the figure of merit (FOM), whose relationship is presented below, indicates the ratio of convective HTC of NF to to the of NF to ().
Results and Discussion
Figure 3 demonstrated the temperature contour of the WMH-S for and NF 2% in different Re. At low velocities of the fluid, it can be seen that the fluid heated up at the beginning of WMH-S and had a low heat transfer in the end. As the fluid velocity increased, the fluid with lower temperatures moved inside the WMH-S, and as a result, cooling in the end of the WMH-S increased.
Figure 4 shows the at the bottom of the WMH-S for variations of Re, d, and Fi. As it can be observed, an intensification in the Re always decreased the . Faster passage of fluid through the WMH-S improved cooling, thus, the heat transfer increased and the WMH-S temperature got closer to the fluid temperature. Hence, the was also decreased. Increasing the Fi also reduced the of the WMH-S. The application of NF resulted in a higher thermal conductivity of the fluid, which increased the heat transfer from the WMH-S to the fluid. Therefore, it lowered the temperature of the WMH-S. In the higher Fi, the obtained using NF containing small-sized NPs was lower, while in the low volume percentage, NF containing large-sized NPs generated lower . Both the viscosity and the thermal conductivity depend on the temperature, the volumetric percentage of the NPs, and the diameter of the NPs; hence, in different volume percentages and temperatures, the effect of NP diameter on the heat transfer could vary.
FIGURE 4
Figure 5 displays the average temperature of the bottom of the H-S for variations of Re, d, and Fi. As it can also be observed, an intensification in the Re diminished the average temperature in the WMH-S and an intensification in the Fi decreased the average temperature. As mentioned above, the increase in these two parameters increased the heat transfer between the WMH-S and the fluid, thus reducing the overall temperature of WMH-S and making its temperature closer to the temperature of the fluid. The changes in the average temperature varied based on the changes in the NP diameter at different volume percentages. Of course, the amount of these changes was far less than the temperature changes with the Fi and Re. The average temperature appeared to be lower in medium-sized NPs, especially at high volumetric percentages.
FIGURE 5
Figure 6 demonstrated the PP required to flow the fluid for dissimilar values of Re, d, and Fi. The intensification in Re and, consequently, the escalation in fluid velocity greatly increased the PP. Increasing the , as well as the flow rate by increasing the Re, raised the PP. An increase in the Fi also increased this parameter, stemming from the increase in in the WMH-S. It can be seen that the variations in the PP with the NP diameter were very small; however, in a high-volume percentage, employing smaller NPs resulted in the requirement of less PP. The use of smaller NPs increased the viscosity, and consequently, the shear stress reduced. As a result, the employment of smaller NPs slightly increased PP.
FIGURE 6
Figure 7 demonstrates the increase percentage in the HTC for different values of Re, d, and Fi. Increasing the Re and the Fi always increased the HTC. It was seen that growing the Fi maintained the upward trend of increasing the HTC and always increased it. However, with the intensification of the Re in the high volume percentages of NPs, the increase in the HTC was initially low, but in higher Re, the increasing trend was steeper and increased significantly; while in the low Fi, the increase in the Re always created an increasing trend in the HTC. It was also noticed that in high and low Re, the effect of adding NPs was more promising than that in medium Re. Furthermore, the increase in the HTC was higher for the average-sized NPs.
FIGURE 7
Figure 8 demonstrates the temperature uniformity on the bottom of the WMH-S for dissimilar values of Re, d, and Fi. Here, the intensification in the Re and the volumetric percentage of the NPs reduced the Theta, indicating that the temperature at the bottom of the WMH-S was uniform. The decrease in temperature caused the temperature to be uniform in this part, stemming from better heat transfer between the fluid and the solid walls. In the average diameters of NPs, Theta was higher, meaning that the larger diameter of NPs had better temperature uniformity.
FIGURE 8
Figure 9 shows the FOM for dissimilar values of Re, d, and Fi. The best case for adding NPs in terms of heat transfer to was in high Re such that the highest FOM was approximately 1.25, which occurred in the Re of 1800 for 5% of the Fi. In higher Re, the increase in HTC was greater than the increase in ; while in lower Re (300), the decrease in FOM was less than one, meaning the ratio of increase in with the addition of NPs was higher than the increase in HTC. Investigating the NP diameter demonstrated that application of NPs with a larger size resulted in a higher FOM.
FIGURE 9
Conclusion
In this article, a new WMH-S with five microchannels was simulated. The walls of the microchannels were wavy.
and
NF were employed as the coolant. The model utilized for viscosity and conductivity of the NF was related to the diameter of the NPs. With the changes in the
Re, the volumetric percentage of the NPs, and their diameters, the thermal performance of the WMH-S was considered and the main obtained results are as follows:
1) Increasing the Re and the percentage of NPs reduced the maximum and minimum temperatures at the bottom of the WMH-S.
2) Increasing the diameter of the NPs at a higher Fi increased the of the WMH-S, while those at a low volume percentage reduced it. The addition of nanoparticles reduces the heat sink maximum temperature by 3.8 and 2.5% at the Reynolds numbers of 300 and 1800, respectively.
3) With increasing the Re and volume percentage, more PP was required. Thus, the cost of PP also increases.
4) In high percentages of NPs, the increase in the size of NPs also raised the PP.
5) The HTC augmented with increasing Re and Fi.
6) The temperature uniformity increased with the intensification of Re and the volumetric percentage of NPs, and its thermal resistance decreased.
7) The highest FOM was approximately 1.25, occurring in high Res and volume percentages of NPs.
Statements
Data availability statement
The original contributions presented in the study are included in the article/Supplementary Material, further inquiries can be directed to the corresponding authors.
Author contributions
All authors wrote the manuscript, provided critical feedback, and helped shape the research, analysis, and manuscript. All authors discussed the results and commented on the manuscript.
Funding
This work was supported by the Taif University Researchers Supporting grant number (TURSP-2020/266) of Taif University, Taif, Saudi Arabia.
Conflict of interest
The authors declare that the research was conducted in the absence of any commercial or financial relationships that could be construed as a potential conflict of interest.
Publisher’s note
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Summary
Keywords
heat sink, electronic component, nanoparticles diameter, alumina–water nanofluid, numerical simulation
Citation
Khetib Y, Abo-Dief HM, Alanazi AK, Cheraghian G, Sajadi SM and Sharifpur M (2021) Simulation of Nanofluid Flow in a Micro-Heat Sink With Corrugated Walls Considering the Effect of Nanoparticle Diameter on Heat Sink Efficiency. Front. Energy Res. 9:769374. doi: 10.3389/fenrg.2021.769374
Received
01 September 2021
Accepted
23 September 2021
Published
10 November 2021
Volume
9 - 2021
Edited by
Cong Qi, China University of Mining and Technology, China
Reviewed by
Basharat Jamil, Rey Juan Carlos University, Spain
Hossein Nasiri, Brazil University, Brazil
Updates
Copyright
© 2021 Khetib, Abo-Dief, Alanazi, Cheraghian, Sajadi and Sharifpur.
This is an open-access article distributed under the terms of the Creative Commons Attribution License (CC BY). The use, distribution or reproduction in other forums is permitted, provided the original author(s) and the copyright owner(s) are credited and that the original publication in this journal is cited, in accordance with accepted academic practice. No use, distribution or reproduction is permitted which does not comply with these terms.
*Correspondence: Yacine Khetib, ykhetib@yahoo.com; Mohsen Sharifpur, mohsen.sharifpur@up.ac.za
This article was submitted to Process and Energy Systems Engineering, a section of the journal Frontiers in Energy Research
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