The magneticnanofluid heat pipe with superior thermal properties through magnetic enhancement
 YuanChing Chiang^{1},
 JenJie Chieh^{2}Email author and
 ChiaChe Ho^{3}
DOI: 10.1186/1556276X7322
© Chiang et al.; licensee Springer. 2012
Received: 12 May 2012
Accepted: 10 June 2012
Published: 20 June 2012
Abstract
This study developed a magneticnanofluid (MNF) heat pipe (MNFHP) with magnetically enhanced thermal properties. Its main characteristic was additional porous iron nozzle in the evaporator and the condenser to form a unique flowing pattern of MNF slug and vapor, and to magnetically shield the magnet attraction on MNF flowing. The results showed that an optimal thermal conductivity exists in the applied field of 200 Oe. Furthermore, the minor thermal performance of MNF at the condenser limited the thermal conductivity of the entire MNFHP, which was 1.6 times greater than that filled with water for the input power of 60 W. The feasibilities of an MNFHP with the magnetically enhanced heat transfer and the ability of vertical operation were proved for both a promising heatdissipation device and the energy architecture integrated with an additional energy system.
Keywords
magnetic nanofluids thermal conductivity slug vaporBackground
With the gradually increasing development of dense electrical circuit electronics, several aspects were considered for the typical improvements on a heat pipe, referred to as a heat superconductor. Nanofluids with excellent thermal conductivity [1] were applied as the working fluids (WFs) of traditional heat pipes to enhance the thermal performance [2, 3]. However, either highcost metal nanoparticles solved in water were used as nanofluids or these heat pipes were operated only in a horizontal or limited tilt arrangement, rather than the vertical arrangement, in which their thermal performance deteriorates because nanoparticles always accumulate on the evaporator of heat pipes with evaporation converting water to vapor.
An oscillating heat pipe [4–6] with an additional heat transfer mechanism of conventional force through the interval liquid slug and vapor bubble beyond that of the phase change can overcome the deposition problem. Its closed loop suppresses the entrainment limit, that is, the shear force between condensing and evaporating flow in highinput power [7]. However, its multiturn architecture limits its integration with electronics.
Among lowcost metaloxide nanofluids [8–10], magnetic nanofluids (MNFs) have the magnetically enhanced thermal conductivity [8, 9] to compete with metal nanofluids. However, the common disadvantage of developed MNFHPs in overcoming the deposition problems is the extrainduced problem of magnetic manipulation resulting from unsuitable designs of either active or complex magnetic fields [11, 12]. To avoid the extra power consumption from actively controlling the MNF flowing, a novel MNFHP in a closedloop architecture was proposed for several main objects: the first was the flowing pattern of the interval vapor moving the MNF slug; the second was the superior suppression of the entrainment limit; and the third was the expansible ability for the integration with some energy storage [13].
Methods
The size distribution of the magnetic particles was investigated, as shown in Figure 2b, using dynamic laser scattering (Nanotrac 150, Microtrac Corp., PA, USA). The average hydrodynamic diameter was 10 nm ± 14 nm. The diameter that was detected using dynamic laser scattering is a hydrodynamic diameter because detecting the Brownian motion of the particles was conducted by probing the Doppler frequency shift of the scattered light with respect to the incident light.
The magnetization properties of MNFs were examined using a vibration sample magnetometer (Model 4500, EG&G Corp, California, USA). The concentration of MNFs was diluted with deionized (DI) water. For example, the magnetization of 4 emu/g, equal to 0.8% in volumetric fraction, was obtained (Figure 2c).
Measurements and analysis models
In designing the decrease of the total thermal resistance (R_{WF}) of an MNFHP, the major thermal resistance of the evaporator or condenser was reduced using MNFs with excellent thermal conductivity. The thermal resistance related with the MNF flowing between an evaporator and a condenser was accomplished by specifically configuring an MNFHP. Therefore, the improvement of the heat transfer in an evaporator or a condenser with magnetic fields was initially evaluated by testing the evaporator or condenser.
This onedimensional model can be solved as T_{WF} (${T}_{\text{WF}}=({T}_{\text{WF}.0}{T}_{\text{tube}}){e}^{\left(\raisebox{1ex}{${k}_{\text{WF}}{A}_{\text{WF}}$}\!\left/ \!\raisebox{1ex}{${d}_{\text{WF}}{\rho}_{\text{WF}}{V}_{\text{WF}}{\text{C}}_{\text{WF}}$}\right.\right)t}+{T}_{\text{tube}}$) from the initial temperature of the WFs (T_{WF,0}). Here, the time constant (τ) of T_{WF} is the reciprocal of $\raisebox{1ex}{${k}_{\text{WF}}{A}_{\text{WF}}$}\!\left/ \!\raisebox{1ex}{${d}_{\text{W}}{\rho}_{\text{WF}}{\text{V}}_{\text{F}\text{F}}{\text{C}}_{\text{WF}}$}\right.$. Furthermore, τ is obtained according to the fitting of the T_{WF} variation with time, as shown in Figure 3a,b. To examine the influences of WFs and applied magnetic field (H) on the conductivity of an evaporator or a condenser, the thermal indicator of k_{WF} / C_{WF} was analyzed based on T_{WF} under the reasonable assumption of the similar densities for water and MNFs for the test concentration of 0.8% and 0.003% in volumetric fraction. Hence, the enhanced ratio of k_{WF} / C_{WF} was defined as k_{MNF}C_{W} / k_{W}C_{MNF} to examine the effect of WFs by comparing C_{WF} and k_{w} of DI water.
Consequently, to determine the total thermal performance of the entire MNFHP, the proposed scheme was modified with some additional parts to measure the pressure and temperature, as well as the WF stuffing (Figure 1). For different WFs or applied fields, the operation conditions were the same. In addition to the observation of the flowing pattern through the acrylic tube between the evaporator and condenser, the R_{WF} of the MNFHP, defined as $\left({T}_{\text{evap}}{T}_{\text{cond}}\right)/P$, was analyzed. Here, T_{evap} and T_{cond} are the temperatures of WF in the evaporator and condenser, and the heat transfer of the heat pipes, P, is obtained via the thermal exchange of the cooling water surrounding the condenser. Similarly, the enhanced thermal resistance ratio (R_{MNF} / R_{W}) was used to compare the effect of WFs, where R_{MNF} and R_{W} were under the MNFHP filled with MNFs and water, respectively.
Results and discussion
Regarding the analysis of the thermal properties of an evaporator or a condenser, Figure 3a,b shows that T_{WF} increased or decreased exponentially over time for WFs of water or MNFs at different fields. For MNFs, both $\left{T}_{\text{WF},f}{T}_{\text{tube}}\right$ and τ decreased with H s to optimal values at H of 200 Oe, where T_{WF,f} was the final temperature of WF. Furthermore, both $\left{T}_{\text{WF},f}{T}_{\text{tube}}\right$ and τ of MNFs were smaller than those of water. Based on the onedimensional model, $\left{T}_{\text{WF},f}{T}_{\text{tube}}\right$ decreased with the increase of k_{WF} under the same final heat transfer, Q_{sensible,f}, because Q_{sensible,f} is equal to the system of heat loss. In addition, τ could be evaluated according to the dominator of C_{WF} / k_{WF}. Therefore, the variations of $\left{T}_{\text{WF},f}{T}_{\text{tube}}\right$ and τ were related to the thermal parameters of k_{WF} and C_{WF}.
Furthermore, considering the variation of H s and MNF concentrations in both the evaporator and condenser, Figure 3c indicates that all k_{MNF}C_{W} / k_{W}C_{MNF} increased with H s and have an optimal value at a specific H. The optimal phenomenon was not significant for low concentrations of MNFs. Moreover, the k_{MNF}C_{W} / k_{W}C_{MNF} of the evaporator was larger than that of the condenser. The reasons were explained in k_{WF} and C_{WF} at different H s and temperatures.
For magnetic nanoparticles of Fe_{3}O_{4}k_{MNF} was larger than k_{W} in proportion to the concentration [8, 9]. k_{MNF} increased with H s and had an optimal value at a specific H[8, 9]. The specific field increased, whereas the concentration was lower [8]. Because of the formation of magnetic clusters, C_{MNF} decreased with H s, becoming smaller than 300 Oe [14]. Because the origin of mechanism is the same as that of k_{MNF}, there was possibly an optimal value for the variation of C_{MNF} with H s. This was valid for other Hdependent optical properties of MNFs based on this mechanism [15]. Regardless, k_{MNF} / C_{MNF} had an optimal value at a specific H, but k_{W} / C_{W} maintained the same value for all H s.
In WF temperature, k_{MNF} decreased as the temperature rose [16], but k_{W} almost remained the same [17]. Similarly, C_{MNF} decreased slightly as the temperature rose, but C_{W} almost remained the same [14]. Effectively, k_{MNF}C_{W} / k_{W}C_{MNF} is smaller at high temperatures than at low temperatures if the effect of C_{MNF} is smaller than that of k_{MNF}.
Therefore, for the enhanced time of heat transfer in an evaporator or a condenser, k_{MNF}C_{W} / k_{W}C_{MNF}, as depicted in Figure 3c, achieved up to 3.5 and 1.6, separately, under the optimal condition of MNFs of 0.8% in volumetric fraction at 200 Oe.
Moreover, under the optimal condition of MNFs of 0.8% in volumetric fraction at 200 Oe, the total thermal performance of the entire MNFHP under the optimal condition achieved the maximal P of 60 W and the flowing pattern of the MNF slug and vapor bubble, as shown in the photos at the time interval of 1 sec in Figure 4b, was observed in the acrylic tube between the evaporator and the condenser, thus confirming that the flowing pattern was the design.
Conclusion
This study developed an MNFHP in a closedloop scheme with magnetically enhanced thermal properties, the flowing pattern of the interval liquid slug and vapor bubble, and the separated paths of evaporated fluids and condensed fluids. The feasibility of an MNFHP with magnetically enhanced thermal performance is valid. The enhanced thermal conductivity ratio of an MNFHP showed that the entire MNFHP was limited by the k_{MNF}C_{W} / k_{W}C_{MNF} of a condenser subunit. This was useful in designing an MNFHP.
Authors’ information
YCC has been an assistant professor in the Department of Mechanical Engineering, Chinese Culture University. His research interests include thermodynamics, heat transfer in electronics, and energy engineering. JJC has been an associate professor in the Institute of ElectroOptical Science and Technology, National Taiwan Normal University. His research interests include photonics, energy, and biomagnetism. CCH was a PhD degree candidate in the Department of Mechanical Engineering, National Central University. He had rich practical experiences of related manufacturing equipment in addition to his major in micro and nanoscale manufacturing.
Abbreviations
 DI:

deionized
 MNFs:

magnetic nanofluids
 MNFHP:

magneticnanofluid heat pipe
 WFs:

working fluids.
Declarations
Acknowledgment
The financial support of this work was provided by the National Science Council, Taiwan, under grant number NSC982622E003003CC3.
Authors’ Affiliations
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