Open Access

The magnetic-nanofluid heat pipe with superior thermal properties through magnetic enhancement

Nanoscale Research Letters20127:322

DOI: 10.1186/1556-276X-7-322

Received: 12 May 2012

Accepted: 10 June 2012

Published: 20 June 2012


This study developed a magnetic-nanofluid (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 heat-dissipation device and the energy architecture integrated with an additional energy system.


magnetic nanofluids thermal conductivity slug vapor


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 high-cost 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 [46] 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 high-input power [7]. However, its multi-turn architecture limits its integration with electronics.

Among low-cost metal-oxide nanofluids [810], 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 extra-induced 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 closed-loop 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].


Figure 1 shows a closed-loop type of MNFHP. Its main difference from traditional heat pipes is the inner structure, that is, the additional iron porous nozzle in both evaporator and condenser, and magnets on its evaporator and condenser. The iron porous nozzle suppresses magnetic attraction for MNF flowing and forms the flowing pattern of the interval flowing of MNF slug and vapor bubble. Similarly, copper meshes sintered on whole inner surface were also used to transport MNFs by the capillary force against the magnetic attraction.
Figure 1

The closed-loop type of a MNFHP.

The used WFs included water as the reference and different concentrations of MNFs composed of a water solvent and magnetic nanoparticles of Fe3O4 (Taiwan Advanced Nanotech Corp., Taoyuan,Taiwan). The crystallines of magnetic particles were analyzed, as shown in Figure 2a, using a powder X-ray diffractometer (D-500, Siemens Corp., Belgium, Germany) with Cu-Kα radiation at a wavelength of 0.15418 nm. Figure 2a shows that the phases of Fe3O4 agreed with the standard diffraction spectrum (JCPDS no. 65–3107).
Figure 2

Characterization of MNFs. (a) The crystallines of magnetic nanoparticles, (b) hydrodynamic diameters of the magnetic nanoparticles, and (c) the magnetization properties.

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 (RWF) 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.

Both the evaporator and condenser were composed of a copper tube and a porous iron nozzle, as shown in the inset of Figure 3a,b. By connecting the stuffing parts, such as the charging valve and pressure gauge, the evaporator or the condenser was filled with the same amount of WFs. By setting the temperature of the heating or cooling sources (Ts), the temperature variation of WFs, TWF, was measured within different magnetic fields, for example, Figure 3a,b for the MNF of 0.8% in volumetric fraction. In addition, the heat transfer (Q) contributed to WFs in two types: latent heat (Qlatent) and sensible heat (Qsensible). Qlatent was the same regardless of whether the WFs were MNFs or water, but Qsensible was the key property for distinguishing MNFs from water in thermal performance. Therefore, Qsensible is representatively discussed using a one-dimensional model ( Q sensible = k WF A WF T tube T WF d WF = ρ WF V WF C WF d T WF d t ). Here, Qsensible is related to the thermal conductivity (kWF), temperature (TWF), density (ρWF), specific heat (CWF), thickness (dWF), volume (VWF), cross-area (AWF) of the WFs between the outer surface of the iron nozzle and the inner surface of the evaporator or the condenser, and the tube temperature (Ttube). Ttube is the same as Ts with the reasonable assumption of low thermal resistance, and t is the time after applying Q.
Figure 3

Characterization of the subunit. (a) The evaporator in the heating Qsensible procedure, (b) the condenser in the cooling Qsensible procedure, and (c) with the H-dependent kMNFCW / kWCMNF.

This one-dimensional model can be solved as TWF ( T WF = ( T WF . 0 T tube ) e ( k WF A WF d WF ρ WF V WF C WF ) t + T tube ) from the initial temperature of the WFs (TWF,0). Here, the time constant (τ) of TWF is the reciprocal of k WF A WF d W ρ WF V F F C WF . Furthermore, τ is obtained according to the fitting of the TWF 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 kWF / CWF was analyzed based on TWF 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 kWF / CWF was defined as kMNFCW / kWCMNF to examine the effect of WFs by comparing CWF and kw 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 RWF of the MNFHP, defined as T evap T cond / P , was analyzed. Here, Tevap and Tcond 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 (RMNF / RW) was used to compare the effect of WFs, where RMNF and RW 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 TWF increased or decreased exponentially over time for WFs of water or MNFs at different fields. For MNFs, both T WF , f T tube and τ decreased with H s to optimal values at H of 200 Oe, where TWF,f was the final temperature of WF. Furthermore, both T WF , f T tube and τ of MNFs were smaller than those of water. Based on the one-dimensional model, T WF , f T tube decreased with the increase of kWF under the same final heat transfer, Qsensible,f, because Qsensible,f is equal to the system of heat loss. In addition, τ could be evaluated according to the dominator of CWF / kWF. Therefore, the variations of T WF , f T tube and τ were related to the thermal parameters of kWF and CWF.

Furthermore, considering the variation of H s and MNF concentrations in both the evaporator and condenser, Figure 3c indicates that all kMNFCW / kWCMNF 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 kMNFCW / kWCMNF of the evaporator was larger than that of the condenser. The reasons were explained in kWF and CWF at different H s and temperatures.

For magnetic nanoparticles of Fe3O4kMNF was larger than kW in proportion to the concentration [8, 9]. kMNF 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, CMNF decreased with H s, becoming smaller than 300 Oe [14]. Because the origin of mechanism is the same as that of kMNF, there was possibly an optimal value for the variation of CMNF with H s. This was valid for other H-dependent optical properties of MNFs based on this mechanism [15]. Regardless, kMNF / CMNF had an optimal value at a specific H, but kW / CW maintained the same value for all H s.

In WF temperature, kMNF decreased as the temperature rose [16], but kW almost remained the same [17]. Similarly, CMNF decreased slightly as the temperature rose, but CW almost remained the same [14]. Effectively, kMNFCW / kWCMNF is smaller at high temperatures than at low temperatures if the effect of CMNF is smaller than that of kMNF.

Therefore, for the enhanced time of heat transfer in an evaporator or a condenser, kMNFCW / kWCMNF, 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.

Furthermore, by filling MNFs with 0.8% in volumetric fraction into an entire MNFHP, thermal performance of RMNF / RW at different H s was analyzed in Figure 4a, indicating that RMNF / RW was less than 1 at all H s except zero field. The worst RMNF at zero fields was unexpected according to kMNFCW / kWCMNF of a single evaporator or a condenser in the Qsensible test, larger than 1. Possibly, MNF with the high concentration easily resulted in the deposition of magnetic nanoparticles on the tube wall of the evaporator. Conversely, for the smaller RMNF / RW at the nonzero field, the deposition phenomenon was possibly avoided. The reason was that the more violent scour on the tube walls of a condenser and an evaporator caused by the faster MNF flowing under higher kMNFCW / kWCMNF might decrease the MNP deposition. The minimum of RMNF / RW occurred at the same as 200 Oe with kMNFCW / kWCMNF of a single evaporator and condenser in Figure 3c. Furthermore, RMNF / RW of the entire MNFHP could be viewed as the ratio of the effective thermal conductivity (kW,MNFHP / kMNF,MNFHP) with a simple conduction model in that the thermal resistance R was equal to kWF,MNFHPAtube / dtube, where the effective thermal conductivity of the entire MNFHP filled with some WF (kWF,MNFHP), the cross area (Atube) and diameter (dtube) of the tube are in form, derived from the one-dimensional conduction model. Therefore, the minimal value of RMNF / RW of approximately 0.6 was equal to this maximal value of kMNF,MNFHP / kW,MNFHP of 1.6. This value is similar with the smaller optimal value of kMNFCW / kWCMNF in a single condenser rather than that of the larger single evaporator. It could be concluded that the thermal performance of an entire MNFHP was limited by the smaller one because of the series assembly of an evaporator and a condenser, as well as a minor thermal resistance of the flowing mechanism.
Figure 4

Characterization of a MNFHP filled with MNFs of 0.8% in volumetric fraction. (a) The H-dependent RMNF / RW, and (b) the flowing pattern 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.


This study developed an MNFHP in a closed-loop 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 kMNFCW / kWCMNF 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 Electro-Optical 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 nano-scale manufacturing.





magnetic nanofluids


magnetic-nanofluid heat pipe


working fluids.



The financial support of this work was provided by the National Science Council, Taiwan, under grant number NSC98-2622-E003-003-CC3.

Authors’ Affiliations

Department of Mechanical Engineering, Chinese Culture University
Institute of Electro-Optical Science and Technology, National Taiwan Normal University
Department of Mechanical Engineering, National Central University


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© Chiang et al.; licensee Springer. 2012

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