Abstract
Heat engines are based on the physical realization of a thermodynamic cycle, most famously the liquid–vapour Rankine cycle used for steam engines. Here we present a sublimation heat engine, which can convert temperature differences into mechanical work via the Leidenfrost effect. Through controlled experiments, quantified by a hydrodynamic model, we show that levitating dryice blocks rotate on hot turbinelike surfaces at a rate controlled by the turbine geometry, temperature difference and solid material properties. The rotational motion of the dryice loads is converted into electric power by coupling to a magnetic coil system. We extend our concept to liquid loads, generalizing the realization of the new engine to both sublimation and the instantaneous vapourization of liquids. Our results support the feasibility of lowfriction in situ energy harvesting from both liquids and ices. Our concept is potentially relevant in challenging situations such as deep drilling, outer space exploration or micromechanical manipulation.
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Introduction
Ever since the invention of water mills in antiquity, through the development of the steam engine in the 18th century, and up to today’s turbines, many power generators rely on the principle of harnessing a fluid stream to drive rotational motion. Whether it is to power a wind farm or a micro electromechanical system, a central challenge remains the effective conversion of fluidflow energy into useful work despite the friction of a bearing^{1,2}. Heat engines add many practical advantages to energy conversion, most notably the ability to convert the stored chemical energy of fuels, such as coal, gas or radioactive materials, into heat and eventually into mechanical work. However, standard engines often involve several steps, each decreasing the efficiency, with particular care needed to minimize friction when a rotating turbine is involved.
Leidenfrost^{3} first noticed the remarkable lowfriction properties of the instantaneous vapourization of a liquid, also known as thinfilm boiling, in his 1756 ‘tract about some common properties of water’, reporting that a small speck of dust trapped at the interface of a levitating droplet would move ‘with a wonderful velocity’. More recently, it has been shown that effective directed motion of Leidenfrost drops and solids can be achieved by rectifying the flow within their supporting vapour layer using hot anisotropic ratchets^{4,5,6,7}. Because the driving force is supplied by underlying vapour, the resistance experienced by these Leidenfrost ‘karts’ is very low^{8}.
Harvesting thermal energy using sublimation as a phasechange mechanism via the Leidenfrost effect is an attractive concept, as it offers the key advantage of a virtually frictionfree bearing provided by the vapour layer. In addition, alternative, nontraditional fuels can be used to circumvent the complications posed by extreme temperature and pressure conditions of exotic landscapes. For example, it has been recently suggested that, for deep space applications, locally available resources (ices of H_{2}O, CO_{2} and CH_{4}) on the surfaces of planetary bodies could be sources for use in sublimation^{9}. The abundance of such resources is highlighted by recent reports of ‘linear gullies on Mars’ carved by slabs of solid CO_{2} sliding down inclines. Such a process is thought to occur as a consequence of seasonal variations in the environmental temperature, which drive the sublimation of dryice deposits^{10}. This highlights that low pressures and high temperature differences naturally occurring in exotic environments could make energy harvesting and power generation based on alternative heat cycles, and using locally available ices, feasible.
In this paper, we present a sublimation heat engine that exploits the Leidenfrost effect to convert temperature differences into rotational motion. Our concept relies on Leidenfrost vapour rectification by turbinelike surfaces to create lowfriction suspended rotors, and is both applicable to sublimating solids (dry ice) and vapourizing liquids (water). Our experiments focus on the effect of the driving temperature difference, load size and turbine geometry. We further rationalize our results by deriving a creeping flow hydrodynamic model, obtaining an excellent agreement with the experiments. We also build a simple magnetic coil generator based on a dryice Leidenfrost rotor, thus providing a proofofconcept of our method as a new means of energy harvesting.
Results
Heat engine concept
The general concept of a heat engine, depicted in Fig. 1a, is centred on a working substance that absorbs a quantity of heat Q_{in} from a hot reservoir, held at temperature T_{h}. Part of the heat absorbed is converted into work W, while a quantity Q_{out} is dissipated to a cooler reservoir held at temperature T_{c}. The underpinning basis of our heat engine is the achievement of Leidenfrostbased rotational motion, which we depict in Fig. 1b. The working substance, in the present case, solid CO_{2} or liquid H_{2}O, is converted into superheated vapour by absorbing a quantity of heat Q_{in} supplied by a neighbouring turbinelike surface held at a temperature T_{c}>T_{L}, where T_{L} is the temperature of the Leidenfrost point. The released vapour is then rectified to produce mechanical work, W, and cooled to the original temperature T_{c}, giving off an amount Q_{out} of heat to the surroundings. This new thermal cycle is the solidtovapour analogue of the liquidtovapour Rankine cycle, which is widely used in steampowered engines. However, the present cycle involves sublimation (or thinfilm boiling) as the phase change and ensures the stabilization of a lowfriction vapour layer by keeping the temperature of the hot surface above T_{L}. The first quantity of interest is the theoretical thermal efficiency of the engine. This is the maximum efficiency attainable in the absence of operational losses. The theoretical efficiency, ε≡1–Q_{in}/Q_{out}, is limited by the efficiency of a Carnot engine operating between the two same heat reservoirs, ε≡1–T_{c}/T_{h}. One approximation of the theoretical efficiency of the Leidenfrost engine, motivated by the approach used in a simplified Rankine cycle, is ε≈1–T_{c}/T_{ave}, where T_{ave} is the average temperature between the temperature of the working substance and the superheating temperature after the phase change. A more precise approximation would depend on the specific thermodynamic phase diagram of the working substance^{11}. For example, for dry ice taking T_{ave}=(T_{c}+T_{h})/2, with T_{h}=500 °C and T_{c}=−78 °C, gives a maximum thermal efficiency of ε≃0.67; such a high efficiency arises because of the high temperature differences involved.
Experimental
For our experiments, we fabricated aluminium turbinelike textured substrates of varying radius R with N=20 asymmetric teeth using standard computer numerical control machining (Fig. 2a). The surface of the turbines was characterized using surface profilometry (Fig. 2a inset). Figure 2b shows the height profile of the turbine at a fixed radius along the angular coordinate, θ. The surfaces were designed to keep the height of the ridges, H, constant with a sweep based on a standard axial gas turbine design. The local azimuthal length of the ridges, l, is determined by the number of teeth, N, and increases with increasing distance from the centre, r, that is, l(r)=2πr/N. Therefore, the local inclination angle of the teeth along the azimuthal direction, θ, decreases with increasing distance from the centre, r, according to tan^{−1}(H/l)=tan^{−1}(R/rtanα), where α is the inclination angle at the edge, where the length of the teeth reaches its maximum value, L=l(R).
Solid CO_{2} discs were placed on top of the turbines as shown schematically in Fig. 3a. The turbines were preheated to temperatures in the range 350 °C<T<500 °C. We identified two distinctive regimes determined by the weight of the discs. For large weights, Leidenfrostinduced levitation is hampered by the underlying surface. In the experiments, this was evident by imprints left by the turbine on the surface of the dryice disc. Decreasing the mass of the loads below a critical value m_{c} leads to a second regime where the discs levitate freely on top of the turbinelike surface. However, a marked difference to the familiar Leidenfrost levitation is that the turbinelike substrates drive the rotation of the discs along the angular direction. Figure 3a shows a time sequence of the rotation of a 2.0 cm CO_{2} disc on top of a turbine held at a temperature T_{h}=500 °C (see also Supplementary Movie 1). Because the substrates are fixed, the CO_{2} discs act as selfpowered rotors. Stable rotation was achieved by using confining rings, which help redirect the vapour flow across the gap formed between the dryice disc and the ring walls. Therefore, it is reasonable to assume that the disc is kept in a centred position because of Bernoulli’s principle: a small displacement of the disc towards the boundary ring causes a higher pressure acting on the region closer to the ring, therefore displacing the disc back to the centre. We carried out a second set of experiments, under identical conditions, using water droplets in place of the CO_{2} discs. The droplets were stabilized by placing a hydrophilic metal plate on top of the droplet as shown in the schematic in Fig. 3b (see also Supplementary Movie 2). As with the CO_{2} discs, the Leidenfrostinduced thinfilm boiling of the droplet results in rotational motion, in this case evident by the rotation of the top plate (Fig. 3b right panels). In both cases, rotation occurred in the downhill direction along the teeth of the turbine.
Model of a turbine surface and Leidenfrost rotor
To deduce the mechanism behind the Leidenfrost rotation, we focus on the release of vapour from the surface of the levitating rotor. Following the recent work in refs 4, 12, 13, our model is based on the vapour rectification by the underlying surface, which induces a net viscous drag along the azimuthal direction on the levitating dryice disc or water film (Fig. 4). We assume that the energy flux across the vapour layer, q_{in}, occurs by conduction, that is, q_{in}≈λΔT/h, where ΔT is the temperature difference across the vapour layer, of thermal conductivity λ and thickness h. For temperatures above the Leidenfrost point, the energy flux is mainly expended in the phase change of the fuel (the liquid or the ice). This allows us to estimate the speed of evaporation at the rotor surface, ν_{n}≈q_{in}/σρ=λΔT/σρh, where σ is the latent heat associated with the phase change and ρ is the density of the vapour. As depicted in Fig. 4, the vapour stream is rectified by the turbine, causing a net flow along the azimuthal coordinate and downhill along the teeth.
To determine the flow pattern within the vapour layer, we use the hydrodynamic mass and momentum conservation laws for an incompressible fluid, which correspond to the familiar continuity and Navier−Stokes equations. A dimensional analysis reveals that the ratio of inertial to viscous forces acting on a fluid element of vapour can be quantified by the Reynolds numbers Re_{r}=ρh^{2}U_{r}/ηR and Re_{θ}=ρh^{2}U_{θ}/ηl, corresponding to the radial and azimuthal components of the flow. Here U_{r} and U_{θ} are the typical radial and angular velocities, and η is the dynamic viscosity of the vapour. From mass conservation we find U_{r}=(R/h)ν_{n}, which eventually leads to Re_{r}≈λΔT/ησ. This ratio is of the order 10^{−2} for the material properties and temperature differences of both water and dryice loads (see Supplementary Table 1 for a list of physical properties). Noting that l=2πr/N, the azimuthal Reynolds number reads Re_{θ}=ρh^{2}ωN/2πη, where ω is the angular velocity of the disc. Using h~H, we then find Re_{θ}≈0.2. Therefore, the flow within the vapour layer is dominated by viscous friction. Furthermore, because the vapour layer thickness, h, is much smaller than the lateral length scale of the gap, R, we can invoke the lubrication approximation of the hydrodynamic equations^{14}. The continuity and Navier–Stokes equations are henceforth reduced to
and
The first equation is the continuity equation averaged over the thickness of the vapour layer, where ‹v_{r}› and ‹v_{θ}› are the local radial and azimuthal components of the velocity field (also averaged over the thickness of the vapour layer). The second and third equations correspond to Darcy’s law, and determine the relation between the local average velocity and the gradient of the pressure field, p(r,θ). Substitution of equations (2) and (3) into equation (1) gives the following secondorder partial differential equation for the pressure field:
The effect of the underlying tooth pattern enters in the variation of the local thickness, and consequently in the speed of release of the vapour, that is, h=h(r,θ) and v_{n}=v_{n}(h(r,θ)). To simplify the mathematical problem, we consider the effect of small local inclination angles, that is, , and focus on the limit where the height of the teeth is small compared with the typical thickness of the vapour layer. The local layer thickness can thus be approximated by
where h_{0} is the thickness of the layer for a flat turbine and . The hydrodynamic equations can be solved perturbatively in powers of ξ by linearizing equation (4) and writing
The pressure field then follows by substituting this ansatz into equation (4), solving order by order in ξ. The perturbation solution gives the leading order contributions to the flow field in the vapour layer. For a detailed derivation of the solution of the pressure field, we refer the reader to the Supplementary Note 1.
Because of the (approximately) uniform vapour release at the surface of the rotor, the pressure profile decays from the centre of the bottom surface towards the edge. This is captured by the zerothorder contribution to the pressure,
where v_{n0}=v_{n}(h_{0}). This excess pressure balances the weight of the rotor, leading to levitation, and determines the thickness of the vapour layer h_{0} (ref. 4). Because the turbine substrates are not flat, levitation is favoured when the thickness of the vapour layer is larger than the depth of the teeth, thus avoiding contact between the two surfaces. In our experiments, H is of the order of hundreds of microns, we thus expect that close to the onset of rotation the vapour layer thickness is of the same order. By setting h_{0}≈H, we obtain a criterion for the critical mass to achieve rotation,
where l_{LF}≡(ηλΔT/(σρρ_{f}g))^{1/3} is a Leidenfrost length scale characterizing the competition between vapour pressure and the weight of the rotor (of mass density ρ_{f}).
We now turn our attention to the rotational motion of the loads, which is dominated by the viscous drag acting on the bottom surface of the rotors. From the perturbative solution of the flow within the vapour layer, the average tangential stress acting on the rotor surface along the angular direction is, to leading order in the approximation, , where b is a dimensionless constant. This result is consistent with the result of reference 13, which was derived for linear ratchets using scaling arguments and verified numerically. The total torque acting on the disc follows by integrating rτ_{zθ} over the rotor surface,
where c is a numerical constant. The torque increases with increasing weight because the vapour layer becomes thinner, increasing the local viscous drag. The scaling with increasing radius arises because the drag force has both a longer moment arm and a larger area to act on. Finally, the geometry of the turbine substrate enters in the inclination angle α, which determines the degree of rectification and therefore acts to increase the torque. The number of teeth sets the periodicity of the pattern, L=2πR/N, and hampers rectification at large N.
Discussion
To test our prediction for the critical mass for rotation, equation (8), we carried out experiments over a wide range in the temperature difference, disc radius and average thickness of the turbine teeth (See Supplementary Tables 2 and 3). For each set of experimental conditions (ΔT, R, H), we measured the probability of rotation of the disc, P_{s}(m), for a wide range in the mass of the loads, m (typically 60 trials). The inset of Fig. 5 shows a typical probability curve, showing the transition to rotation as the mass of the discs is reduced. The experimental state diagram shown in Fig. 5 confirms the scaling of the critical mass, defined as P_{s}(m_{c})=0.5, with ΔT(R/H)^{4}, as predicted by equation (8).
To test the theoretical prediction for the torque acting on Leidenfrost rotors, we carried out further experiments measuring the angular acceleration of dryice discs of different mass and radii over a range of temperature differences and teeth inclination angles (see inset of Fig. 6 and Supplementary Table 4). We then determined the torque from rigidbody kinematics. The resulting data, shown in Fig. 6 and Supplementary Table 5, shows an excellent agreement (over two decades) with the proposed scaling of equation (9). Moreover, a fit of the data gives a prefactor within 20% of the theoretical prediction. Such a good agreement suggests that effects arising from inhomogeneities on the turbine substrate and dissipative energy losses are relatively small, thus supporting that the sublimationbased heat engine can be a new approach to energy harvesting.
In our experimental proofofconcept realization of a sublimation heat engine, the conversion of the latent heat of the phase transition into rotational motion is low in efficiency (~10^{−6}). Some of the loss is due to the viscous dissipation within the gap, some is due to the escape of gas along the turbine edge and some is from the evaporation from the top and side faces of the disc. However, a large fraction of the latent heat of the phase transition, either sublimation or thinfilm boiling, is used to sustain the levitation of the disc. The total generated power can be written as P=P_{lev}+P_{rot}, where P_{lev}=(πR^{2}p_{atm}+mg)v_{n0} is the power generated to sustain levitation^{15} and P_{rot}=Γω is the power generated by rotation of the disc. The total power should be compared with the rate of energy release due to the phase transition, . The speed of release of vapour molecules, v_{n0}, can be found by mass conservation, that is, . Using the experimentally measured values for m, R, dm/dt, Γ and ω, along with reported values for the physical parameters (see Supplementary Note 1), we find , P_{lev}≃4.2 J s^{−1} and P_{rot}≃2 × 10^{−5} J s^{−1}. The energy released by the phase transition is therefore dominantly sustaining the levitation, an effect that could be removed by design at the expense of introducing friction within a bearing.
To further demonstrate the feasibility of harvesting thermal energy using the sublimation heat engine, we constructed a simple electric generator. By attaching a frame with eight Neodynium magnets to a dryice rotor and lowering a multisegment induction coil system into close proximity to the rotating assembly, we were able to generate an alternating voltage (see Supplementary Movie 3).
The new concept of a thermal cycle based on either sublimation or thinfilm boiling introduced in this paper is appealing because it can lead to new routes for power generation and energy harvesting as we have demonstrated by our proofofconcept. Future optimized designs of a Leidenfrostbased engine could focus on efficiency using geometries where the gap between the disc and the turbine surface is controlled, where the precise sweep and shape of blades are optimized and where energy losses can be minimized by reducing the escape velocity of the vapour at the edge of the turbine. As supported by our experiments with water, the extension to liquid fuels can be accomplished. Further work in this direction can focus on the design of wicking surfaces that act as fueldispensing shafts.
The temperature differences occurring in space and the abundant naturally occurring liquids and ices on planetary bodies^{9} give one example where the transport of fuel is prohibitive, but local conditions can provide all that is needed for a sublimation engine. Given recent progress in reducing the Leidenfrost temperature exploiting superhydrophobic coatings^{16} and low pressures^{17}, another potential field of application is in microsystems, where high surface areatovolume ratios pose significant challenges for any moving part. Here the concept of a motor exploiting the intrinsic lowfriction vapour bearing provided by thinfilm boiling could have wide applicability.
Methods
Dryice discs
Dryice discs were produced by depositing liquid carbon dioxide (BOC) onto a snowpack dryice maker (VWR). The resulting dryice snow was shaped into discs using a bespoke pressure mould of variable diameter. Discs were further flattened using a commercial hot plate (VWR VMSC7) at 150 °C.
Hot plate
The hot plate used in the experiments consisted of a machined block of aluminium fitted with 2 × 200 W 1/2′′ × 3′′ cartridge heaters (RS Components) and a Ktype thermocouple to monitor the temperature. The cartridge heaters were controlled using a ProportionalIntegralDerivative (PID) controller. The hot plate was isolated from the working bench using ceramic pillars.
Confinement rings
Confinement rings were made from a stock steel bar and were turned on a lathe to have a desired internal diameter and a square cross section of 5 × 5 mm.
Angular acceleration and torque measurements
The mass and radius of dryice discs were measured immediately before each experiment. A small mark was made on the top surface of the discs using a drywipe marker to allow visualization of rotational motion. The discs were then placed on the turbine, inside the confinement ring and filmed from above at 50 frames per second using an SVSi MemView highspeed camera. The video files were then analyzed to determine the period of rotation and tracked for the first six rotations. The average angular velocity for each complete rotation was plotted as a function of time. The angular acceleration was then extracted from these measurements. The torque was extracted using data for the angular acceleration assuming rigidbody kinematics.
Onset of spinning
Experiments were carried out using a single turbine to ensure the consistency of results. The dryice disc radius and mass were controlled for each trial using confinement rings of different radii. For each experiment the dryice disc was placed on the turbine. A disc was classed as spinning if the disc underwent a full rotation within the first 10 s of being placed on the turbine and sustained the rotational motion for at least five revolutions.
Turbines
Turbines were manufactured using standard computer numerical control machining from a thin sheet of aluminium.
Electromagnetic generator
The electromagnetic generator was manufactured by laser cutting two pieces of 3mm thick mediumdensity fibreboard and laminating them together to form an eightlobed commutator. Each lobe was fitted with a Neodynium magnet. The commutator was fixed to the top surface of a dryice disc using three small tacks. A stator was made by winding 0.15mm diameter varnished copper wire into 8 cylindrical coils with a core diameter of 7 mm, an external diameter of 27 mm and length 12 mm, with approximately 4,000 turns per coil. The coils were then laid flat into the lobe pattern to match the commutator and fixed into place using SampleKwick Fast cure acrylic (203560). Visualization of the electric signal was performed using a standard oscilloscope.
Additional information
How to cite this article: Wells, G. G. et al. A sublimation heat engine. Nat. Commun. 6:6390 doi: 10.1038/ncomms7390 (2015).
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Acknowledgements
We thank Dr J. Martin (Reece Innovation), Dr A. Stokes and Professor A. J. Walton (University of Edinburgh) and Professor R. Bennacer (ENSCachan, France) for useful discussions; and the Faculty of Engineering and Environment at Northumbria University and the School of Engineering at the University of Edinburgh for technical support.
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The study was jointly conceived, developed and designed. K.S. designed and produced the turbines. G.G.W. carried out the experiments. G.G.W. and R.L.A. analyzed the data. R.L.A. developed the theoretical model. G.G.W. designed the proofofconcept engine. R.L.A. and G.M. wrote the paper with contributions from G.G.W. and K.S.
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Supplementary information
Supplementary Tables and Supplementary Note
Supplementary Tables 15, Supplementary Note 1 (PDF 272 kb)
Supplementary Movie 1
Rotation of a dryice block on a hot turbinelike surface via the Leidenfrost effect. (MOV 1115 kb)
Supplementary Movie 2
Rotation of an aluminium plate supported by a water droplet on a hot turbinelike surface via the Leidenfrost effect. (MOV 1193 kb)
Supplementary Movie 3
Electromagnetic generator powered by a sublimation heat engine. (MOV 2937 kb)
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Wells, G., LedesmaAguilar, R., McHale, G. et al. A sublimation heat engine. Nat Commun 6, 6390 (2015). https://doi.org/10.1038/ncomms7390
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DOI: https://doi.org/10.1038/ncomms7390
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