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Highlights • Typical heterogeneous ice nucleation pattern was revealed under practical nocturnal cooling and freezing conditions. • Distinctive three-stage frosting process was found under subfreezing condition. • Ice nucleation was first initiated on the upper part of the windshield. • Surface roughness or contamination probably triggered an earlier ice nucleation. • The arrival of saturation point could approximately mark the initiation of icing. Abstract In the present study, we theoretically and experimentally investigated a typical and practical heterogeneous ice nucleation process on auto windshield under nocturnal radiative cooling and subfreezing conditions. During the experiment, a general class A passenger car was placed outdoors in a subfreezing environment (i.e., 44.14° N, 126.45° E) during nights in January, with a purpose to produce a nocturnal radiative cooling condition for supercooling the windshield to trigger the ice nucleation. The results revealed a distinctive three-stage frosting process: (I) inhomogeneous occurrence of incipient ice nucleation; (II) small-sized ice crystals grew into large-sized ones primarily based on the incipient nucleation sites, together with a continual formation of new nucleation sites and a merging between large-sized and small-sized crystals; (III) large-sized ice crystals coalesced into large-scale groups, tending to make a full ice coverage. Unlike the classical three-period frosting process, the present study exhibited an absence of the drop-wise condensation but with a presence of dendritic crystals nearly parallel to the supercooled surface. Besides, the incipient ice nucleation was first initiated on the upper part of the windshield, which then propagated downward with a further heat loss of the windshield due to the continual nocturnal radiation. Meanwhile, the probable presence of surface roughness or contamination was much more likely to trigger an earlier initiation of incipient heterogeneous ice nucleation. Additionally, the arrival of saturation point, rather than the nominal supersaturation state (i.e., the condensation nucleation point), could be expected to approximately mark the initiation of icing under a practical engineering condition. Higher relative humidity tended to induce an earlier occurrence of ice nucleation and produce a larger surface coverage. [ABSTRACT FROM AUTHOR]

The present study experimentally and numerically investigated the passive control on flow structure evolution and convective heat transfer enhancement for impinging jet. Four different impinging jets, including a baseline circular jet (CJ) and three passive controlled jets, i.e., an elliptic jet (EJ), a circular-chevron jet (CCJ) and an elliptic-chevron jet (ECJ), were comparatively analyzed by utilizing the Particle Image Velocimetry (PIV) technique, infrared (IR) thermography and large eddy simulation (LES) over a wide range of jet-to-wall distances ( H / D ) at the jet Reynolds number ( Re ) of 20,000. The results showed that, unlike CJ which presented a general shedding of axisymmetric toroidal vortices, EJ showed highly deformed toroidal structures accompanied with the axis switching effect, both CCJ and ECJ exhibited the well-organized counterrotating streamwise vortex pairs developing from the chevron notches. All the three passive controlled strategies were found to induce a stronger mixing and fluctuating activity near around the stagnation region, especially for ECJ (i.e., the passive–passive controlled device) which showed the highest turbulence level approaching the target wall due to the double-passive enhancement. Moreover, compared with the baseline jet CJ, all the passive controlled jets achieved a significant heat transfer improvement in the vicinity of the stagnation point, particularly for ECJ which presented the highest heat transfer enhancement of about 41% at H / D = 5 . Whereas both CCJ and ECJ were found to exhibit a less-than-ideal heat transfer performance at a small H when the heat transfer uniformity was specifically considered, due to the anisotropic thermal imprint distributions. [ABSTRACT FROM AUTHOR]

• The melting process of an ice bead under a hot shear flow on micro-grooved surfaces. • The melting process of the ice bead could be divided into three categories. • The micro-grooves affected wetting length and removable time. • The micro-grooved surfaces were more favorable for the ice bead melting process. In the present study, we experimentally investigated the melting process of an ice bead on the smooth and micro-grooved surfaces under a hot shear flow. One smooth silicon surface and three micro-grooved silicon surfaces were fabricated and tested. A parameter study of the substrate surface temperature and the air flow speed was conducted. During the experiment, an ice bead was first formed from a freezing water droplet on a cold substrate surface. Then, the ice bead was exposed to a hot shear flow and its melting process was recorded by a CCD camera and an infrared camera simultaneously. As for the micro-grooved surfaces, the direction of the hot shear flow was parallel to the micro-grooves. The results showed that the melting process of the ice bead on the smooth and micro-grooved surfaces under a hot shear flow could be divided into three categories. The air flow speed, the surface temperature, and the type of the surface had a significant influence on which category the melting process of the ice bead belonged to. Besides, the presence of the micro-grooves was found to apparently affect the wetting length, the removable time, and the temperature along the centerline of the ice bead. In general, the micro-grooved surfaces were found to be more favorable for the ice bead melting process than the smooth surface. [ABSTRACT FROM AUTHOR]

In the present study, we report for the first time the observations of the melting process of an ice bead in a hot shear flow. During the experiment, a water droplet was first deposited onto a glass surface. Then, the surface temperature was cooled down to a desirable subfreezing value by a constant temperature bath circulator and the water droplet turned into an ice bead. After that, the ice bead was exposed to a hot shear flow and its melting process was recorded by two cameras. The results showed that, both the air flow speed and substrate surface temperature had significant effects on the melting process of the ice bead. The increase of the air flow speed resulted in a significant change of the runback phenomenon of the liquid water generated from the melting ice bead. Besides, as the decrease of the substrate surface temperature, the deicing time of the ice bead increased apparently. In addition, during the melting process of the ice bead, the temperatures of two characteristic points along the centerline demonstrated apparent differences. [ABSTRACT FROM AUTHOR]

In the present study, we experimentally investigated the impact and freezing processes of a water droplet on different cold cylindrical surfaces. The results showed that, during the impact process of the water droplet, the maximum contact diameter along azimuthal direction was generally larger than that along axial direction. Besides, during the water droplet recoiling process, the radius of the cylindrical surface was found to have an apparent effect on the spreading factor along azimuthal direction but a minor influence on that along axial direction. During the freezing process of the water droplet, the change of the temperature as well as the radius of the cylindrical surface did not result in a significant variation of the ice bead shape. [ABSTRACT FROM AUTHOR]

In the present study, we report for the first time the detailed dynamic motions of a water droplet impacting on an ice surface. Besides, the effects of the initial height of the water droplet and the ice surface temperature on the impact and freezing processes of the water droplet were experimentally investigated. During the experiment, an ice surface was generated first and then kept at a desired temperature by a constant temperature bath circulator. After that, a deionized water droplet was deposited onto the ice surface and its impact and freezing processes were recorded. The results showed that, during the impact process of the water droplet, once the water droplet reached its maximum contact diameter, the contact line of the water droplet was pinned on the ice surface without recoiling. Besides, at the same initial height of the water droplet, the decrease of the ice surface temperature resulted in the reduction of the maximum spreading factor and an apparent increase of the height of the ice bead. Moreover, once the droplet initial height was increased, the maximum spreading factor increased while the height of the ice bead reduced significantly. [ABSTRACT FROM AUTHOR]

In the present study, we report for the first time the observations of the successive freezing processes of water droplets on an ice surface. During the experiment, an ice surface was generated first and then kept at a desired temperature by a semi-conductor cooler. After that, three deionized water droplets were deposited onto the ice surface successively and their freezing processes were recorded. The results show that both ice surface temperature and the initial height of the water droplet have significant effects on not only the droplet freezing time, but the contact diameter, angle, and height of the ice bead as well. When the initial height of the water droplet was relatively small, the subsequent water droplet could only cover a portion of the ice bead formed by the previous droplet. Besides, under the same initial height of the water droplet, the decrease of the ice surface temperature could result in an obvious reduction of the contact diameter of the ice bead and an apparent increase of the ice bead angle. [ABSTRACT FROM AUTHOR]

The present study experimentally investigated the impact process of a water droplet on a cold surface with different inclined angles. The inclined angle of the surface was changed from 0.0° to 60.0°, while the surface temperature was varied from room temperature 21.0 °C to −15.0 °C. During the impact process of the water droplet, the inclined angle of the surface was found to have an apparent influence on the spreading time and displacements of the foremost and rearmost points. Besides, once the inclined angle of the surface was high enough (e.g., α = 60.0°), the water droplet could not keep as a single droplet all the time during its impact process. It split into two smaller droplets and produced satellite droplets at the same time. In addition, during the freezing process of the water droplet, the inclined angle of the surface could affect the final geometry of the ice bead. [ABSTRACT FROM AUTHOR]

The present study experimentally investigated the effects of droplet size and surface temperature on the impact, freezing, and melting processes of a water droplet on an inclined cold surface. The temperature of the inclined surface was changed from room temperature 20.0 °C to −14.0 °C while water droplets of three sizes ( D 0 = 2.21, 2.92, and 3.31 mm) were tested. The results show that the increase of droplet size led to the increases of spreading time, spreading maximum diameter, gliding maximum diameter, and maximum displacement of foremost point. Besides, during the relaxation phase, as the decrease of surface temperature, the formost point retracted a longer distance and the spreading factor decreased more smoothly. In addition, test plate temperature was found to have an effect on the freezing time, air bubble sizes, and frost accretion. At last, the melting processes of the ice beads under different conditions were also illustrated and compared. [ABSTRACT FROM AUTHOR]

• The evap. and cond. HTCs of 9 AMFHPs with 3 fluids at FR100% were tested. • Higher q e causes the rise of evap. HTCs and the fall of cond. HT of most samples. • Higher v air results in the fall of evap. HTCs as well as cond. HT of most samples. • Cooper correlation predicts the evap. HTCs of AMFHPs at high FR excellently. • Rohsenow correlation predicts cond. HTCs of R134a at FR100% well. An experimental investigation was conducted to evaluate the evaporation as well as condensation heat transfer of air-cooled multi-port flat heat pipes (AMFHPs), designed for extreme working conditions of power battery thermal management in electric vehicles. The experimentally obtained evaporation as well as condensation heat transfer coefficients (HTCs) under various working conditions were compared and analyzed. It was found that, both the orders of the intensity of heat transfer mode in the liquid pool and the condensation Nu c were R134a > ammonia > acetone. The orders of the evaporation HTCs referring to ammonia and R134a AMFHPs with different filling ratios (FRs) were 50 > 30 > 100 > 70 and 30 > 50 > 70 > 100%, while those of Nu c were 50 > 30 > 70 > 100 and 30–50–70 > 100%, respectively. In most cases, evaporation HTC increased with the rise of heating power as well as the decrease of cooling air velocity, while the condensation Nu c decreased with the increasing in the heating power as well as the air velocity slightly. The measured evaporation HTCs were compared with some predictive correlations of pool boiling and pool boiling-thin film evaporation expressions for the evaporator section at different FRs, and the condensation HTCs were also evaluated by several available filmwise condensation models. Results showed that Cooper correlation for pool boiling revealed quite a good agreement with measured results for the AMFHPs of 100% R134a, 70% ammonia and 100% ammonia, and Rohsenow correlation predicted the condensation HTCs of R134a AMFHPs with FR<100% accurately. However, for ammonia, the prediction of the evaporation HTCs in the case of FR < 70% was difficult, and Nusselt theory significantly overestimated the condensation HTCs of all the ammonia samples. [ABSTRACT FROM AUTHOR]

Abstract: The present study experimentally investigated the effect of synthetic jet on the icing process of a water droplet on a cold surface. A synthetic jet actuator using a loudspeaker as the exciting source was designed and fabricated. The test plate surface was cooled down from room temperature to well below 0°C by a semi-conductor cooler. The synthetic jet actuator started to operate when the temperature of the test plate reached a certain degree. The results show that the synthetic jet not only increased the temperatures of the test plate when droplet icing process began and ended, but also prolonged the freezing time of the water droplet. Besides, the synthetic jet resulted in the accretion of dense and irregular frost crystals on the outer surface of the ice bead. [Copyright &y& Elsevier]

• The impact process of a supercooled water droplet onto a cold SLIPS was studied. • The freezing process of a supercooled water droplet onto a cold SLIPS was studied. • The melting process of a supercooled water droplet onto a cold SLIPS was studied. • The effects of the droplet supercooling degree and the SLIPS temperature were tested. • The freezing process could happen during the supercooled water droplet recoiling process. In the present study, we report for the first time the observations of the impact, freezing, and melting processes of a supercooled water droplet onto a cold slippery liquid-infused porous surface (SLIPS). A parameter study of the droplet supercooling degree and the SLIPS temperature was carefully performed. Moreover, the impact process of a water droplet onto the SLIPS under the room temperature conditions was also measured for comparisons. The results showed that the impact kinematics of a water droplet on a SLIPS under the room temperature conditions was significantly different from those of the supercooled water droplet impinging onto a cold SLIPS. Under the same water droplet temperature conditions, the spreading factors rapidly increased to their maximum values at a similar rate, regardless of the change of the SLIPS temperature. Besides, under the same SLIPS temperature conditions, the maximum spreading factor of the water droplet at room temperature was significantly greater than those of the supercooled water droplet cases. When the temperatures of the water droplet and SLIPS were relatively high, freezing process started after the recoiling process had already finished for a certain period of time. However, when the temperatures of the water droplet and SLIPS were relatively low, freezing process could happen during the supercooled water droplet recoiling process. In addition, under the same water droplet temperature conditions, the decrease of the SLIPS temperature could result in the increase of the average energy dissipation rate of the water droplet. [ABSTRACT FROM AUTHOR]

• The temperature distributions within a melting ice bead was experimentally studied. • A parameter study of the airflow speed and the airflow temperature was carefully performed. • The melting time decreased as the increase of the airflow temperature and the airflow speed. • The ice beads melted at a much faster rate under the forced convection conditions. In the present study, we report for the first time the temperature measurements inside the melting ice bead in a hot shear flow by utilizing Molecular Tagging Thermometry (MTT) technique. A parameter study of the airflow temperature and airflow speed was carefully performed. Moreover, the melting process of an ice bead under the natural convection condition was also measured for comparisons. One CCD camera and an intensified CCD camera were used to record the ice bead melting process. The results showed that, based on the phosphorescence images, the temperature distributions within the melting ice bead could be obtained by the MTT technique. For all the cases, the average temperature within the melted water region increased gradually from an initial value of about 1.0 ℃ to a final value of approximately 4.0 ℃. Besides, the ice beads melted at a much faster rate under the forced convection conditions than that of the natural convection condition. Furthermore, when subjected to a hot shear flow, the melting time of ice bead decreased as the increase of the airflow temperature and the airflow speed. In addition, as for the cases of relatively higher airflow speed and higher airflow temperature, the vertical movement coefficient of the windward three-phase junction point was increasing at a much faster rate than that of the leeward three-phase junction point. Besides, we proposed an equation to estimate the total melting time for the ice bead under the influence of the hot shear flow. Good agreements were found between the experimental and theoretical values of the total melting time for the ice beads under different conditions. [ABSTRACT FROM AUTHOR]

• The arrangement of heaters and coolers affects the temperature distribution. • The highest value of Nu loc occurs at the junction of the heater and the cooler. • The existent magnetic field suppresses the nanofluid convection. • By increasing the block side length, the Nu ave increases. • The heat transfer rate in Case 1 is most effective, followed by Case 3 and Case 2. A two-dimensional (2D) numerical simulation is presented to study the effect of magnetic field on Ag-MgO nanofluid forced convection and heat transfer in a channel with active heaters and coolers. A Fortran code according to Lattice Boltzmann method (LBM) is developed for this purpose. The effects of thermal arrangement (Case1, 2 and 3), block side length (0.3 ≤ h ≤ 0.5), Reynolds number (50 ≤ Re ≤ 100), Hartmann number (0 ≤ Ha ≤ 60) and volume fraction of nanoparticles (0 ≤ ϕ ≤ 0.02) on flow pattern and heat transfer characteristics are analyzed systematically. The obtained results showed that the highest value of local Nusselt number occurs at the junction of the heater and the cooler due to the high temperature gradient, followed by the sharp corner of heaters and coolers. Moreover, the heat transfer at the heater sharp corner is higher than that of the cooler sharp corner. The average Nusselt numbers indicated that the rate of heat transfer increases with increasing ϕ or decreasing Ha. Finally, the heat transfer rate in Case 1 is more than Case 3 and Case 2. [ABSTRACT FROM AUTHOR]

Highlights • Local aero-thermal behavior of RFETHXs with different arrangements is compared. • Comparison of global performance of three types of RFETHXs is illustrated. • Contribution analysis of structural factors to global performance is revealed. • Performance optimizations of three types of RFETHXs using EBF are conducted. Abstract Tube arrangement largely determines the flow structure as well as aero-thermal performance in finned tube heat exchangers (FTHXs). Most of the previous studies did not cover both overall performance and local thermal flow characteristics due to the physical complexity. This work is related to the comparison of various aero-thermal behaviors of rectangular finned elliptical tube heat exchangers (RFETHXs) with different tube arrangements in a turbulent flow region, from basic characteristics to optimal structures. Using 3-D numerical simulation based on the validated standard k - ε model, the local thermal flow characteristic as well as overall dimensional and dimensionless performances of three arrangements is investigated. Then, using variance analysis, the contribution of each structural parameter of the three arrangements on overall performance is compared after the screening of the factor of longitudinal tube pitch. Using the same CFD data as variance analysis, an elliptical basis function (EBF) model of each type of arrangements is constructed to understand the distribution of j / f 0.5 as well as PEC in the parameter range of this work. Moreover, optimal structural parameters of each arrangement are provided. It is observed that, each tube arrangement presents its own characteristic of flow separation and heat transfer coefficient distribution on fins. For the in-line and staggered row arrangements, the contributions of all the main factors and the two-way interactions on various overall performances are close, while the situation of the staggered column is different. The influence of two-way interactions is marginal in the staggered column structure, while it cannot be neglected in the two other arrangements in most cases. For j / f 0.5, the optimal structural parameter combination of the in-line and staggered row arrangements is fin thickness 0.6 mm, fin pitch 2 mm and transverse tube pitch 54 mm, whereas that of the staggered column arrangement is 0.6 mm, 2 mm and 70 mm in turn. [ABSTRACT FROM AUTHOR]

Graphical abstract Highlights • MHD natural convection in a baffled U-shaped enclosure is studied. • KKL correlations are used to obtain nanofluid thermal conductivity and viscosity. • Governing equations have been solved by the lattice Boltzmann method. • Effects of Ra , Ha , ϕ and AR on the flow and heat transfer have been examined. Abstract In this study, nanofluid natural convection in a baffled U-shaped enclosure in the presence of a magnetic field is investigated. Lattice Boltzmann method (LBM) is used to study present problems. KKL (Koo-Kleinstreuer-Li) correlation is applied to calculate the effective thermal conductivity and viscosity of nanofluid. The effect of the Brownian motion on the effective thermal conductivity is considered in this correlation. The combination of the four topics (nanofluid, U-shaped enclosure, baffle, magnetic field) is the main novelty of the present study. Effect of Rayleigh number, Hartmann number, nanoparticle volume fraction and cavity aspect ratio on the flow field and heat transfer characteristics have been investigated. The results demonstrate that the average Nusselt number increases by increments of the Rayleigh number, nanoparticle solid volume fraction and aspect ratio. However, the rate of heat transfer is suppressed by the magnetic field. The effect of magnetic field on heat transfer is more significant at higher Rayleigh number and the effect of Ra on the average Nusselt number is more noteworthy at lower Ha. Besides, the effect of Rayleigh number on heat transfer enhancement becomes more significant at higher aspect ratio. [ABSTRACT FROM AUTHOR]

The objective of this study is to investigate the performance of rectangular finned elliptical tube heat exchangers (RFETHXs) of low number of rows ( N ) in turbulent region, with an emphasis on the characteristics with the increase of N . Using 3D numerical simulations based on the validated standard k-ε turbulence model, the average thermal-hydraulic characteristics of each row as well as the overall performance along with N are investigated. Then the contribution of each structural factor and the interaction effects between various parameters on the performance are revealed using variance analysis in 4 sub-row-regions. The most significant interaction effect on the performance evaluation criterion ( PEC ) between structural parameters is confirmed using Response Surface Method (RSM). It is observed that, for the RFETHXs with N  > 2, the heat transfer coefficient of the second row of fins is the largest, while those of the first and the last rows remain the smallest two. A 2-row RFETHX has better performance compared to the RFETHXs with larger N . In most cases, the flow and heat transfer of RFETHXs enters fully developed state from the fifth row, but as the transverse tube pitch ( P t ) increases or the fin thickness declines, such state is postponed to deeper rows. It demonstrates that significant impact of N on PEC exists in the sub-row-range of 2–3. With the incline of N , the effect of fin pitch ( F p ) to j and f decreases while that of P t increases, and the interaction effect between P t and F p to j and PEC becomes more pronounced. This interaction reduces with the increase of frontal velocity. The reason for such interaction is discussed. At last, results of RMS analysis further depict that the interaction effect between P t and F p on PEC of a 6-row RFETHX is more significant than that of a 2-row RFETHX. [ABSTRACT FROM AUTHOR]

The objective of this study is to investigate the air side thermal–hydraulic characteristics of rectangular finned elliptical tube heat exchangers (RFETHXs) using 3D numerical simulations based on the validated standard k-ε turbulence model. First, fin efficiency of RFETHXs is investigated. The effects of various parameters such as row number, transverse tube pitch, longitudinal tube pitch, fin pitch, fin thickness and Re have been studied. Then the influences of structural parameters on the thermal-hydraulic performance of RFETHXs are examined, not only the characteristics including the effect of fin thermal resistance but also the pure convective performance excluded this effect. The contribution ratios of each structural parameter on fin efficiency and air side thermal-hydraulic performance are given. It is observed that, the most important structure factors for fin efficiency are fin thickness and fin pitch. For the RFETHXs with fully developed air side flow and heat transfer (N > 5), from the third row to the last second row, the average fin surface Nu of each row is almost stable, and the value of the second row is 9% higher than the stable value. The results show that the air side heat transfer performance and friction factor of RFETHXs is mainly determined by the transverse tube pitch. For j/f 1/2 at fixed Re, the contribution ratio of transverse tube pitch is 32% while the value is 24% at fixed frontal velocity. Moreover, two sets of multiple correlations, both including and excluding fin thermal resistance, are proposed to describe the air side heat transfer and friction characteristics of RFETHXs in turbulent flow regime. [ABSTRACT FROM AUTHOR]

The present study experimentally investigated the impact and freezing processes of a water droplet on different inclined cold surfaces. The surface temperature was changed from room temperature 24.0 °C to −15.0 °C. The materials of the surfaces included red copper, quartz glass, carbon fiber reinforced composite (CFRC), and glass fiber reinforced composite (GFRC). During the impact process of the water droplet, the surfaces were found to have a minor influence on the spreading time and gliding time but an apparent effect on the equilibrium time. Besides, these surfaces significantly affected the spreading maximum diameter, gliding maximum diameter, and maximum displacement of foremost point of the water droplet. In addition, once the equilibrium state of water droplet was reached, the contact diameter of the water droplet depended heavily on the type of the surfaces. As for the freezing process, the cold surfaces affected not only the freezing time of the water droplets, but the shape of the ice beads as well. [ABSTRACT FROM AUTHOR]

• R134a AMFHP with 50% FR achieves the best performance among the three FRs. • The performance order of AMFHPs with 50% FR are ammonia > R134a > acetone. • Analysis is conducted about the liquid pool heat transfer of 3 fluids in AMFHPs. • The effect of air velocity on t e ¯ is obvious, however, its influence on λ eff is marginal. • Optimum air velocities for each AMFHP with different working fluids are presented. An experimental investigation is conducted to study the effect of the type of working fluid, liquid filling ratio (FR) and the cooling and heating conditions on the performance of air-cooled multi-port flat heat pipes (AMFHPs) designed for the thermal management of power battery. The results show that, under the same FR of 50%,the ammonia AMFHP owns the highest thermal performance, whose equivalent thermal conductivity is 2.21–3.30 times that of one filled with acetone and 1.05–1.31 times that of one using R134a as working substance. Evaporation thermal resistance of acetone AMFHP is significantly larger than those of the AMFHPs filled with ammonia and R134a, whereas their condensation thermal resistance values are comparative. Secondly, it is found that the equivalent thermal conductivity of the R134a AMFHP with 50% FR is 1.63–2.22 times that of one with 30% FR and 1.14–1.63 times that of one with 70% FR, respectively. Thirdly, result indicates that the effect of cooling air velocity on the equivalent thermal conductivity of AMFHP is insignificant, but the temperature of evaporation section is tightly connected to the cooling air velocity. There exists an economic air velocity for each AMFHP, the appropriate air velocities of the AMFHPs filled with R134a, acetone and ammonia at FR=50% are 3.5 m/s, 2.5 m/s and 3.5 m/s, respectively. In addition, analysis of heat transfer reveals that, the intensity of heat transfer mode of the AMFHPs in liquid pool ranges from R134a, ammonia and acetone, under the same working condition and filling ratio. The most direct conclusion is that the R134a AMFHP with appropriate FR is suitable to meet the thermal management requirements of lithium ion batteries for electric vehicles. [ABSTRACT FROM AUTHOR]