EP0001732B1 - Verfahren und Vorrichtung zur Energieumwandlung - Google Patents

Verfahren und Vorrichtung zur Energieumwandlung Download PDF

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Publication number
EP0001732B1
EP0001732B1 EP78400133A EP78400133A EP0001732B1 EP 0001732 B1 EP0001732 B1 EP 0001732B1 EP 78400133 A EP78400133 A EP 78400133A EP 78400133 A EP78400133 A EP 78400133A EP 0001732 B1 EP0001732 B1 EP 0001732B1
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Prior art keywords
rotor
fluid
working fluid
circuit
axis
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EP78400133A
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English (en)
French (fr)
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EP0001732A1 (de
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Bernard Bailly Du Bois
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B3/00—Self-contained rotary compression machines, i.e. with compressor, condenser and evaporator rotating as a single unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/04—Plants characterised by the engines being structurally combined with boilers or condensers the boilers or condensers being rotated in use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • F28D11/04—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller performed by a tube or a bundle of tubes

Definitions

  • the invention relates to industrial energy conversion processes involving at least one step in which the pressure of a working fluid is acted on, in the direction of compression or expansion, possibly, but not necessarily. , in the context of machines where the working fluid circulates in a closed circuit by describing a complete thermodynamic cycle.
  • thermodynamic cycle followed by the fluid can be open or closed, and it is often advantageous that several of its phases take place inside the same rotor.
  • the invention essentially makes it possible to exploit the friction forces in contact with the fluid with the walls which guide it by making the work produced by the displacement of these forces play an important role in the variations of the pressure of the fluid along the circuit, whether in the direction of its compression or of its expansion, pressure variations which are also linked to the potential energy due to rotation.
  • the subject of the invention is a method of energy conversion involving at least one step of compression or expansion of a working fluid inside a rotor and in which the working fluid is made circular in a conduit integral with the rotor which describes a circuit having the shape of a spiral, this spiral being oriented so that the duct approaches the axis of rotation of the rotor when the circuit is traversed by turning around this axis in the same direction that the direction of rotor rotation characterized in that one imposes on the geometrical characteristics of the conduit and the operating conditions that at each point of conduit the angular speed co of the rotor, the relative speed V of the fluid in the conduit, the hydraulic diameter D of the pipe, the coefficient of friction f of the fluid on the walls of the pipe and the angle A made with the meridian plane at the point considered the plane parallel to the axis of the rotor defined by the direction of the circuit at this point , resp ect in operation the condition:
  • the working fluid circulates in a duct, in particular a tubular duct, the walls of which are integral with a rotor movable in rotation around a fixed axis.
  • This duct determines in the rotor a variable azimuth circuit around the axis of rotation.
  • variable azimuth circuit applies here and in everything that follows to circuits having the general shape of a spiral, that is to say that the successive points of the various current lines constituting a circuit are located in respective meridian planes whose azimuth varies in a determined direction and that these successive points are located at the same time at radial distances which vary in a determined direction, for positions which may possibly also vary in axial direction.
  • This denomination includes the particular cases of spirals contained in a plane perpendicular to the axis of rotation, for example the Archimedean spirals, such that the distance to the axis varies in proportion to the azimuthal angle, or the logarithmic spirals, such that the angle made by the directional vector with the radial direction remains constant.
  • the working fluid conduit secured to the rotor approaches the axis of rotation when the circuit is traversed by turning around this axis, relative to the -rotor, in the same direction as the direction of rotation of the rotor (and therefore deviates from the axis when turning in the opposite direction).
  • the working fluid circulates inside the rotor in a spiral-shaped duct which imposes the azimuthal relative displacements of the fluid with respect to the rotor in the same direction throughout the circuit, and this circuit is oriented so such that the fluid approaches the axis if it rotates in the same direction as the rotor in its relative displacement relative to it, and that it moves away from it if it rotates in the opposite direction.
  • the geometric orientation of the spiral therefore depends on the direction of rotation of the rotor, but it does not depend on the direction of movement of the fluid in its duct.
  • the same rotor can comprise several, or even a large number, of similar conduits, in series and / or in parallel on the working fluid circuit.
  • the quantitative conditions imposed on the geometric parameters of the conduits and on the operating conditions in the present invention have the effect of saving mechanical energy or improving its use, by allowing any changes in the enthalpy of the working fluid in according to its entropy and by reducing the energy degradations due to the behavior of the fluid in the duct.
  • This result is particularly obtained when the ratio between the relative speed of the fluid V and the product of the angular speed of rotation ⁇ by the hydraulic diameter D of the conduit is not much greater than unity.
  • the secondary circulations and the dissipative structures induced in conventional turbomachines for low values of the Rossby number seriously contribute to the loss of usable energy.
  • the geometric characteristics of the working fluid conduit and the operating conditions also comply with the inequality relationship stipulated above, so that in their azimuthal projections (orthogonal projections on the direction perpendicular to the meridian plane ) the friction force exerted by the wall of the duct on the fluid and the Coriolis force are known in the same order of magnitude.
  • the invention thus makes it possible to avoid local variations in pressure, and therefore speed, of the fluid, and the energy degradations which result therefrom in conventional machines, or at least to reduce them notably.
  • it uses, in combination, two categories of forces to act on the fluid and constitute the azimuthal projection of the Coriolis forces induced by the relative flow of the fluid with respect to the rotor, namely the friction forces which s 'exert in a direction parallel to the surface of the walls, and pressure forces which are exerted in a direction perpendicular to this surface and which are the only ones to play a useful role on the blades of conventional machines.
  • the advantages of the invention are obtained if at each point of the duct the ratio of the azimuthal projection of the friction force to the azimuthal projection of the Coriolis force is between 0.2 and 2 and the geometry of the duct is determined so that this condition is met over the entire length of the circuit, throughout the range of fluid flow rates and speeds of the rotor in operation.
  • this ratio would remain lower or at most of the order of 0.1.
  • the relative speed V keeps a value which is roughly uniform locally, for points located in the fluid, in the vicinity of the walls and at a given distance R from the axis of rotation.
  • the coefficient f is determined by the relation or is the pressure drop per unit length of the duct, measured when the rotor is stationary and the fluid of density p is passed through it with an average speed V.
  • the hydraulic diameter D of the duct is equal to four times the ratio between its cross section and the corresponding perimeter on the wall.
  • the compression and expansion yields are all the better as the sliding of the fluid relative to the rotor is low; it is advantageous for this purpose to limit the ratio to a value less than or much less than 0.2.
  • this pipe is then used as a heat exchanger, which can constitute a hot source or a cold source, in a thermodynamic cycle followed by the working fluid.
  • the heat can be brought to the exchanger or removed from it by means of an auxiliary fluid located on the other side of tubular walls defining the conduit of the working fluid.
  • this auxiliary fluid advantageously circulates in spiral circuits parallel to those of the working fluid, in the same direction as the latter or in the opposite direction.
  • heat can be produced or absorbed directly within the fluid itself in the zone of the circuit constituting the hot or cold source.
  • the invention makes it possible, by avoiding local differences in speed of the fluid at a given distance from the axis, to also overcome the drawbacks local variations in the temperature difference between the fluid and the walls of the duct.
  • the Reynolds analogy implies that the Stanton number of the flow is very close to the coefficient f / 2.
  • the uniformity of the wall temperatures at a given distance from the axis one way of fulfilling the condition indicated above consists in imposing that the quantity of heat exchanged with the fluid while the rotor is moving of a radian is between 0.4 times and 4 times the product of the cotangent of angle A by the heat capacity per degree and at constant pressure of the fluid contained in the portion of the circuit considered, multiplied by the average deviation temperature between the fluid and the wall.
  • the coefficient f is practically invariable throughout the operating range of the device; the condition imposed according to the invention then implies that the large variations in fluid flow are accompanied by variations in the same direction of the speed of rotation w.
  • the quantity fVD is proportional to the kinematic viscosity of the fluid ⁇ / o.
  • the imposed condition then leads to fix between two numerical limits the number for the co speeds of use of the device. If, for example, the conduit is materialized by parallel disks separated by a distance D / 2, the number thus defined can be chosen to remain between 5 and 50 and preferably close to 25.
  • angle A With regard to the angle A, the best theoretical performances for the specific power are generally obtained when this angle has a constant value of between 30 and 45 degrees, the conduits then having the form of logarithmic spirals.
  • the constructive problems posed by the realization of small hydraulic diameters very often make it preferable, especially for heat exchangers and turbulent flows, the use of relative trajectories having the form of Archimedes spirals with angles A greater than 60 degrees. or very little below 90 degrees, in practice up to 89 degrees.
  • the cross section of the duct can have any shape. Its walls generally include fins or corrugations which make it possible, in particular, to vary the hydraulic diameter of the flow and the relative speed V, as a function of the distance R from the axis.
  • conduits For the general arrangement of the conduits, three main configurations can be adopted: juxtaposition of stacked discs, perpendicular to the axis, the conduits being delimited in the radial direction by spiral ribs integral with the discs; rows of tubes wound in radial spirals and connected to larger diameter collecting tubes, parallel to the axis of the rotor; large ribbed plates arranged around the axis in the manner of a carpet roll.
  • the invention is not limited to these simplest configurations.
  • a specific low heat gas preferably of molecular mass at least equal to that of nitrogen, is used to constitute the working fluid suspension of submicron particles of a body with a high atomic mass greater than 90.
  • This solution has the advantage of reconciling the requirements of low specific heat and high atomic mass, desirable for increasing the temperature difference between hot source and cold source for a given peripheral speed of the rotor (or conversely for decreasing the speed rotation) without using heavy gases such as mercury vapor, the use of which is not always possible, for reasons of chemical corrosion or harmfulness.
  • the dimensions of the particles, at most of the order of a micron are sufficiently small to ensure temperature uniformity in the fluid and for their sliding speed in the gas to remain negligible in a high gravitational potential.
  • the support gas is advantageously nitrogen or a monoatomic gas with an atomic mass greater than the molecular mass of the azote, preferably argon or krypton, or optionally xenon.
  • the particles can consist of chemical elements, of usual commercial purity, in solid phase, of atomic mass greater than 90, preferably tungsten, lead, bismuth, thorium or uranium. These particles can be covered with a very thin layer of a compound of said chemical elements, preferably an oxide in a monomolecular layer, or of any dispersive material, with the aim in particular of neutralizing the Van der Vals forces.
  • the thickness of these particles is advantageously at most 0.1 micron on average, and preferably between 0.001 and 0.1 micron; the specific surface of the powder thus formed is greater than 5 square meters per gram.
  • the advantages of the invention can easily be obtained with a ratio between the mass of the solid phase and the mass of the gas phase in the mixture of between 0.25 and 8 approximately.
  • the presence of such particles makes it possible to increase the density of fluid, which however retains the compressibility of a gas.
  • the invention makes it possible to artificially favor exchanges of mechanical energy over heat exchanges.
  • thermodynamic cycle Another way of increasing the temperature differences between cold source and hot source in the implementation of a complete thermodynamic cycle, consists in using recuperator exchangers between high and low pressure, advantageously included in the same rotor of the device of l 'invention. It is then desirable to use for the transfer of the heat recovered by an intermediate circuit, a fluid whose specific heat is much higher than that of the working fluid, so as to produce a kind of internal heat pump with natural circulation in the gravity field, automatically taking from the global cycle the amount of usable energy necessary to compensate for friction in the intermediate circuit and operating with a small temperature difference.
  • a first way, in itself known, of ensuring this tightness consists in using a ferromagnetic liquid in a rotating joint.
  • a second way of ensuring this etan cheity consists in avoiding any rotating joint separating the atmosphere from the working fluid and in using, to constitute the working fluid itself, a suspension of ferromagnetic particles in a gas, this fluid being subjected to magnetic fields whose intensity varies in absolute value, created by magnets located outside the rotor.
  • a third way of ensuring this sealing makes it possible to eliminate any rotating joint between the external aposphere and a working fluid without particular magnetic properties. It consists in passing successively the working fluid describing a thermodynamic evolution in a closed circuit in the ducts of the rotor, in accordance with the process which is the subject of the invention, and in the ducts of another member entirely incorporated in the rotor, this reaction member being kept artificially stationary, according to a first variant, or able to rotate around the same axis as the rotor, but with a different angular speed, possibly in opposite directions, according to a second variant.
  • the relative movement of the rotor and of the internal reaction member makes it possible to transform into work, in one direction or the other, the usable energy contained in the working fluid.
  • FIG. 2 represents a section of a basic device operating as a compressor.
  • This device comprises, in the example corresponding to this figure, an axis 1 in the center of the rotor, driven in rotation in the direction indicated by the arrow 2, a cylindrical casing 3 which surrounds the rotor and on which are reported the mechanical forces exerted by the gravitational field on the internal structures.
  • the fluid circuit comprises six intake tubes 4 and six manifold tubes 5, all of large diameter and axes parallel to the axis of the rotor, arranged symmetrically around the axis of the rotor.
  • the intake tubes are connected to the collection tubes by conduits 6, of small diameter, arranged in spirals, which constitute the conduits of the working fluid according to the invention.
  • the angle A considered above has been shown in the figure. In the particular case, this angle is close to 86 degrees.
  • the conduits 6 are finned internally in the longitudinal direction and are arranged in contiguous rows juxtaposed in the axial direction.
  • connection points on the same intake tube, belonging to different successive rows, are offset from one row to the other in the azimuth direction to facilitate the production of welds, but the entire assembly has symmetry of order six and is thus dynamically balanced around the axis of rotation.
  • the spirals are described in the opposite direction to the direction of rotation of the rotor when they are traversed away from the axis. In the case under consideration, their distance from the axis increases by an amount equal to six times the outside diameter of the conduits, for each revolution around the axis in the movement relative to the rotor.
  • the value of tgA is on average 16 for this circuit.
  • this device is coupled to a synchronous motor rotating at the speed of 3000 revolutions per minute and where it must provide a flow rate corresponding to a speed of 10 meters per second in the conduit, the fluid entering the conduit at a distance of 25 cm from the axis and leaving it at a distance of 50 cm, its density being high enough for the Reynolds number to exceed 10 5 and the roughness of the walls being such that the coefficient f remains constant and equal to 0.6%.
  • We impose a value for these conditions values which vary between 0.4 and 1.6, which allows most of the advantages of the present invention to be preserved.
  • By replacing the synchronous motor with a motor whose operating value can vary from 1000 to 4000 revolutions per minute, it is also possible to vary a factor greater than 12 the volume flow rates.
  • the heat transferred every second by the fluid is 1 , 26 kilowatts.
  • FIG. 5 indicates, on a temperature (t) -entropy diagram (S), the evolution of the fluid between the inlet a and the outlet b.
  • the dotted curve represents an isobaric evolution.
  • the speed of rotation of the rotor and the direction of circulation of the fluid determine the variation of the mechanical energy, while the temperature difference between the fluid and the wall determines the contributions or withdrawals of heat.
  • the advantages reported for compressor operation would be found for a turbine by inverting the fluid's inputs and outputs.
  • the spirals of Figure 2 can schematically ribs attached to discs perpendicular to the axis of rotation; they can also represent the intersection with a plane perpendicular to the axis of rotation of two profiled sheets welded on the two edges and wound around the axis of rotation while remaining parallel to it. It is also seen that all the devices usually used to obtain the coefficient f and the hydraulic diameter D desired in exchangers can be used to obtain conduits satisfying the conditions characterizing the process according to the invention.
  • Machine II shown in FIG. 3, is an engine in which the working fluid describes a thermodynamic cycle between two thermal sources where it is at different temperatures and where it exchanges heat with an external auxiliary fluid, through the walls of conduits which control its circulation.
  • the hot spring is constituted by a pressurized water circuit and the cold source by a water circuit at room temperature.
  • the heat supply is accompanied by a relaxation of working fluid and the heat extraction is accompanied by a compression.
  • the working fluid circulates in the rotor 41 inside a circuit, part of which is located in a member 59 which is entirely incorporated in the rotor but which is held stationary, by magnetic coupling with a fixed support 55 located at the 'outside.
  • the working fluid circuit is thus hermetically sealed from the outside of the rotor.
  • the thermodynamic evolution is represented by the diagram of figure 6, representing the variations of the temperature according to the entropy. It consists of a quasi-adiabatic compression from (d) to (e), a quasi-isothermal relaxation from (e) to (f), a quasi-adiabatic relaxation from (f) to (g) and a quasi-isothermal recompression from (g) to (d).
  • the working fluid is krypton, the pressure in the circuit of which is several tens of bars when the machine stops.
  • This gas contains a suspension of an equivalent mass of fine tungsten particles. These tungsten particles have a thickness of the order of a tenth of a micron and they are covered with a monomolecular layer of carbide.
  • the specific heat at constant pressure of the mixture is thus five times lower than that of air and the ratio of specific heats at constant pressure and volume remains quite high.
  • the rotor 41 of the machine is capable of rotating at a peripheral speed of between 400 and 500 m / sec. In operation, it drives an alternator producing electricity, coupled to the axial shaft 42 of the rotor, beyond the connections for auxiliary fluids, but not shown in the figures.
  • the working fluid circuit and the auxiliary hot and cold water circuits are rigidly fixed to this rotor which comprises three separate frames, namely a cold frame 43, a hot frame 44 and a feedback frame 45, independently connected to the axis of rotation to reduce thermal stresses.
  • the two thermal sources are formed annularly around the axis of the rotor, the hot source being more distant from this axis than is the cold source.
  • the main circuit comprises in the cold frame 43, three intake tubes 46 and three manifold tubes 47, of large diameter, the axes of which are parallel to the axis of the rotor, arranged around this rotor on two concentric cylinders.
  • These intake tubes and these manifold tubes are connected together by conduits 48, of small diameter, in an arrangement similar to that of the basic device of FIG. 2, but with a ternary symmetry.
  • the conduits 48 are internally finned and the importance of these fins increases when one deviates from the axis so that the product of the passage section by the hydraulic diameter is inversely proportional to the local density of the job.
  • the tungsten suspension in the krypton constituting the working fluid circulates inside the conduits 48, following spiral circuits oriented so as to rotate around the axis of rotation, in a direction opposite to that of the rotation of the machine, when moving away from the axis.
  • All the intake tubes and manifolds of the cold part are based on a mechanical structure allowing the centrifugal forces to be transmitted to an external cylindrical shell of the frame 43.
  • the hot frame 44 In the hot frame 44 are arranged three intake tubes 51 and three manifold tubes 52 similar to those of the cold part, but of smaller diameter and arranged respectively further and closer to the axis 42. These tubes are connected between them by conduits 53, internally finned, whose diameter is also smaller than those of the cold part. These conduits are arranged in juxtaposed rows, each of which comprises three turns wound in a plane perpendicular to the axis. The spirals are oriented so that we move in the same direction as that of the rotation of the machine when we approach the axis of rotation.
  • the set of conduits 53 rests on a mechanical structure transmitting most of the centrifugal forces to a very thick ferrule of the frame 44 surrounding the whole of the hot zone.
  • the three collecting tubes 47 of the cold zone are individually connected respectively to the three intake tubes 51 of the hot zone by three radial connection tubes 54.
  • the differential expansions are compensated by the bending of these radial tubes.
  • the three collecting tubes 52 of the hot zone are connected to orifices 57 of the feedback frame 45 by three connecting tubes 56 comprising a radial part and an axial part.
  • These orifices 57 include blades similar to the distributor blades of an axial turbine and they are located opposite similar blades 58 carried by an immobile member 59.
  • This immobile expansion member comprises conduits 61, of decreasing section , arranged in spirals oriented in the same direction as the direction of rotation of the rotor and leading to orifices 62, further from the axis of rotation, also comprising blades and located opposite an inlet diffuser in the rotor .
  • the stationary member 59 has an annular shape; it rests on a bearing constituted by the axis 42 of the rotor, by means of a gas cushion 86 which is obtained by sampling a low flow rate of the working fluid between the orifices 57 and 62 where the static pressures are which separates the fixed part from the mobile part while ensuring aerodynamic lubrication. Sealing labyrinths, not shown in the figure, separate the two series of orifices 57 and 62.
  • the fixed member 59 carries part of a magnetic circuit 64 whose polarities are alternated in the azimuth direction, this magnetic circuit closing through the frame 45 (the thickness of which is small in the air gap 66) in a fixed support, referenced 55, located outside the rotor.
  • the auxiliary cold water circuit comprises an intake pipe 74, arranged in the center of the rotor shaft, and annular exhaust ducts 75, one and the other connected to annular connection sealing devices.
  • the external network schematically shown in 76 and 77, and to radial tubes 78 and 79, ensuring their connection to the cold water box which surrounds the conduits 48 of the cold part, according to an arrangement similar to that of the machine I, except that the water circulates in the same direction as the working fluid.
  • the hot water inlet and outlet are made according to provisions similar to those of the cold circuit, by means of the inlet pipes 82, outlet 83, and the radial connection pipes 84 and 85.
  • the water circulates in the hot water box, around the walls of the working fluid conduits, approaching the axis of the machine.
  • the hot circuit is connected via rotary seals and a pump to a pressurization and reheating device comprising burners outside the rotor. These devices have not been shown in the figures.
  • the working fluid When the machine Il of FIG. 3 is in operation, the working fluid describes the thermodynamic cycle of FIG. 6. It is compressed almost adiabatically in the tubes 54, during its transfer from the cold zone to the hot zone, and it heats up, for example 300 ° C. This transformation is globally adiabatic for the mixture of krypton and tungsten, but it is not for krypton considered separately; the temperature of krypton is very slightly higher than that of tungsten which acts as a heat sink. The gravitational field increases the enthalpy per unit mass of the mixture and this results in a sharp increase in density and pressure.
  • the mixture yields to the rotor mechanical energy corresponding to the variation of the potential energy due to the rotation.
  • the fluid leaves the hot part with a temperature reduced by about twenty degrees like that of water.
  • the heat received by the working fluid is equal to the change in potential energy due to the rotation minus the change in enthalpy.
  • the density is divided by an important factor; the diameter of the tubes is determined so that the speed of the fluid relative to the rotor is of the order of 15 meters / second in the middle of the hot zone.
  • the fluid is then expanded in an generally adiabatic manner, first in the three tubes 56 integral with the rotor, then in the stationary member 59 where its static temperature continues to decrease in favor of an increase in kinetic energy which allows it to return to the rotor at 62, at a different level of gravitational potential.
  • This expansion zone is the one where the thermodynamic efficiency is the lowest, but the losses remain however of the same order of magnitude as in two successive stages of an axial turbine and they relate only to the useful work of the engine.
  • the expansion ends in the rotor and the fluid enters the cold zone at a temperature slightly above the inlet temperature of the cooling water.
  • the fluid transfers its heat (from (g) to (d)) while moving away from the axis again, and its azimuthal displacement is carried out in the opposite direction to the rotation of the rotor . It receives mechanical work taken from the rotor. This work is a little higher than the heat given to cold water, because its enthalpy increases by about twenty degrees.
  • the power of the engine is controlled by the flow of the hot water current, by means of a valve placed on the auxiliary pump circuit.
  • the machine III which is shown in FIG. 4 is a motor operating between two almost isothermal sources and using an intermediate recuperator. Heat is brought to the rotor by radiation at a temperature close to 600 ° C and the cold source is cooled by an atmospheric air circulation. An aerodynamic reaction member 99 is incorporated in the rotor.
  • the working fluid is xenon, the pressure of which is several tens of bars when the machine stops; it describes a thermodynamic cycle represented diagrammatically by figure 7, which indicates the variations of the temperature (t) according to the entropy (S). It receives the heat of recovery between (h) and (i); it is held in the hot source between (i) and (j), restores the heat of recovery between (j) and (k) and it is recompressed in the cold source between (k) and (h). In machine III, the expansion takes place in the reaction member 99 which rotates inside the rotor 91, but in the opposite direction.
  • the rotor 91 contains the cold source 92 and the hot source 93, on either side of the recuperator 94.
  • the working fluid circuit successively comprises the peripheral tubes 95 of the recuperator 94; which describe axial helices, from one end to the other of the recuperator in the longitudinal direction, the tubes or spiral conduits 96 of the hot source 93, the helical tubes 97 of the internal zone of the recuperator 94, the tubes or conduits 98 in spirals of the cold source 92.
  • the circuit then passes inside a reaction member 99 similar to that of machine II, which is movable in rotation about the same axis as the rotor 91, but independently of the latter.
  • the circuit is formed by nozzles 101 connecting to the ducts of the rotor 91 by annular chambers comprising axial blades. he these are converging nozzles wound around the axis of the machine in spirals oriented in the same direction as the direction of rotation of the rotor when moving away from the axis.
  • the circuit of the cooling air in the cold source 92 passes through blades parallel to the axis of the rotor, marked 111, fixed at the periphery of the rotor opposite fixed inlet and outlet diffusers.
  • the air passes in 102 following spiral paths between the conduits 98 of the cold source, which include very developed external fins. It then flows radially away from the axis to exit the rotor at 103.
  • the auxiliary fluid used in the hot source 93 is NaK eutectic which circulates in channels 104 located in the vicinity of a radial surface 105 of the rotor, heated by radiation, then between the conduits 96 of the main circuit.
  • An expansion volume containing argon is provided in 106.
  • the auxiliary fluid of the recovery circuit is helium under high pressure, containing a suspension of submicron particles of graphite.
  • the auxiliary fluid circuit comprises radial tubes 107 and 108 for passing from an external annular chamber containing the tubes 95 to an internal annular chamber containing the tubes 97, respectively in the forward direction and in the return direction.
  • the auxiliary fluid passes through a capacity 109 the inlet and outlet of which are offset in the azimuth direction, which makes it possible to obtain, by the effect of inertia, when the machine is started, a movement initiating the circulation of this auxiliary fluid in the desired direction.
  • the air circuit includes an expansion phase with heat supply, which contributes to reducing the amount of mechanical energy supplied to it by the rotor to maintain its circulation against the gravitational field (since its density decreases) and friction forces.
  • the fins 1 1 of the inlet and outlet diffusers provide it with the additional energy necessary for its movement.
  • the NaK circuit does not have a pump. It functions spontaneously by natural circulation because the channels 104 are arranged so that the zone of heating by radiation is a little further from the axis of rotation than the zone of cooling of this auxiliary fluid in contact with the walls of the conduits 96 .
  • the helium circuit also functions as a closed circuit heat pump in the gravitational field of the rotor 91.
  • the average temperature difference between the internal tubes 97 and the peripheral tubes 95 of the recovery circuit is greater than the difference of temperature corresponding to the adiabatic equilibrium of the mixture of helium and graphite in the gravitational field and circulation takes place naturally.
  • the orifices of the helium duct in capacity 109 are set back from each other in the azimuth direction as indicated above.
  • FIG. 7 represents the development of the working fluid, taking as a reference the stopping temperature with respect to the rotor 91.
  • the working fluid expands in the nozzles 101, almost adiabatic, by increasing its kinetic energy.
  • the difference in potential energies due to rotation determines the amount of usable energy released by the relative movement of the rotor and the internal movable member 99 (aerodynamic reaction member).
  • the power of the motor is controlled by means of the radiation flux arriving on the face 105 of the rotor.
  • the energy released by the action of the fluid on the rotor 91 and the member 99 is used in an electricity generator represented on the left part of the machine of FIG. 4.
  • the movable member 99 does not have an electrical winding, but only conductors 114 located at the periphery, parallel to the axis and short-circuited at their ends (mounting known as squirrel cage).
  • This member has no internal recesses and its moment of inertia is close to that of the rotor 91.
  • the fluid conduits can in particular be constituted by finned tubes which describe Archimedean spirals and which are connected in parallel on the fluid circuit according to a symmetry of revolution of a ternary order at least.
  • the working fluid can circular either inside or outside of these tubes.
  • a ferromagnetic fluid can be used.
  • the fluid must pass through the rotor and through a fixed member, or through the rotor and through a member rotating at a different speed.
  • machine II it is possible to pass the working fluid through an acceleration or relaunching enclosure which is located inside the walls of the rotor but which remains stationary relative to the outside. , the transmission of the forces necessary to compensate for the engine or resistant torque of the machine being ensured by means of a magnetic coupling.
  • machine III it is also possible (machine III) to pass the fluid from a first rotor to a second rotor, this second rotor being entirely located inside the first, having a moment of inertia comparable to this first rotor and rotating in the opposite direction. , the torque exerted on each other by the two counter-rotating rotors being balanced by magnetic forces exerted on electrical windings which play the role of armature or inductor.
  • These electromagnetic circuits make it possible to extract usable energy from the working fluid, or on the contrary to communicate mechanical energy to it via electrical energy penetrating into the main rotor by means of rotary contacts.
  • planar spirals are only a special case of variable azimuth conduits. They could be replaced by curves presenting in projection perpendicular to the axis of the forms of plane spirals, but extending in volume parallel to the axis. All variants of such conduits, as well as all variants of the various elements of the devices and machines described, also form part of the present invention.
  • the invention also extends to numerous variants of the methods described. It applies for example to processes where the working fluid undergoes phase changes by evaporation or condensation, inside conduits where it moves at relatively low speeds.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (11)

1. Verfahren zur Energieumwandlung, mit mindestens einem Verdichtungs- oder Entspannungsschritt eines Arbeitsströmungsmittels im Inneren eines Rotors, in welchem man das Arbeitsströmungsmittel innerhalb einer Leitung umlaufen läßt, die fest mit dem Rotor verbunden ist und eine Bahn beschreibt, welche die Form einer Spirale aufweist, wobei diese Spirale so ausgerichtet ist, daß sich die Leitung der Drehachse des Rotors nähert, wenn man die Bahn durchläuft, indem man diese Achse in derselben Richtung umrundet wie die Drehrichtung des Motors, dadurch gekennzeichnet, daß man für die geometrischen Eigenschaften der Leitung und die Betriebsbedingungen fordert, daß in jedem Punkt der Leitung die Winkelgeschwindigkeit w des Rotors, die Relativgeschwindigkeit V des Strömungsmittels in der Leitung, der hydraulische Durchmesser D der Leitung, der Beiwert der Reibung f des Strömungsmittels an den Wänden der Leitung und der Winkel A, welchen mit der Meridianebene im in Betracht gezogenen Punkt die Ebene parallel zur Achse des Rotors bildet, welcher durch die Richtung der Bahn in diesem Punkt bestimmt ist, beim Betrieb die folgende Bedingung einhalten:
Figure imgb0011
2. Verfahren zur Energieumwandlung mit mindestens einem Verdichtungs- oder Entspannungsschritt eines Arbeitsströmungsmittels beim Umlauf in einem Rotor, wobei es einen thermodynamischen Zyklus beschreibt, dadurch gekennzeichnet, daß man das Arbeitsströmungsmittel in der nach Anspruch 1 oder 2 gebildeten Leitung und unter den entsprechenden Bedingungen umlaufen läßt, und daß mindestens au einem Teil der genannten Bahn die Leitung eine Wärmequelle oder eine Kältequelle bildet, wo die Wärme auf das Arbeitsströmungsmittel übertragen oder diesem entzogen wird.
3. Verfahren nach Anspruch 2, dadurch gekennzeichnet, daß das Arbeitsströmungsmittel mindestens in einer der genannten Quellen in gasförmigem Zustand vorliegt.
4. Verfahren zur Energieumwandlung nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, daß man zur Bildung des Arbeitsströmungsmittels ein Gas verwendet, dessen molare Masse mindestens gleich ist jener des Stickstoffs, wobei das Gas in Suspension Partikel enthält, deren Abmessung kleiner oder höchstens gleich 0,1 ,um ist, mit einem Körper mit erhöhter Atommasse, die über 90 liegt.
5. Verfahren nach Anspruch 4, dadurch gekennzeichnet, daß das Gas unter Stickstoff, Argon und Krypton ausgewählt ist, und daß der Körper mit erhöhter Atommasse unter Wolfram, Blei, Wismut, Thorium und Uran ausgewählt ist.
6. Einrichtung zum Verdichten oder Entspannen eines Arbeitsströmungsmittels, mit einem Rotor (3) mit einer bestimmten Drehrichtung (2), worin Leitungen (6) für Arbeitsströmungsmittel eingebracht sind, welche eine spiralige Bahn festlegen, dadurch gekennzeichnet, daß die geometrischen Eigenschaften der Leitungen bei dem Betrieb den Bedingungen eines der Ansprüche 1 bis 5 entsprechen.
7. Einrichtung nach Anspruch 6, dadurch gekennzeichnet, daß sie rohrförmige Wärmeaustauschwände (48) umfaßt, welche mindestens einen Teil der genannten Leitungen bilden, sowie Mittel zum Umpumpen eines Arbeitsströmungsmittels bzw. eines Hilfsströmungsmittels beiderseits der genannten Wände.
8. Einrichtung nach Anspruch 6 oder 7, dadurch gekennzeichnet, daß die genannten Leitungen von Rohren 48) gebildet sind, welche Archimedes'sche Spiralen beschreiben und parallel an den Strömungsmittelumlauf angeschlossen sind, und zwar in einer mindestens dreifachen, polarsymmetrischen Anordnung.
9. Einrichtung nach einem der Ansprüche 6 bis 8, dadurch gekennzeichnet, daß sie Mittel aufweist, um das Arbeitsströmungsmittel wechselweise in den genannten Leitungen des Rotors in einem geschlossenen Umlauf sowie in Leitungen umlaufen zu lassen, die im Inneren eines Teils zur Relativbewegung bezüglich des Rotors um dieselbe Achse eingebracht sind, sowie mechanische oder elektromagnetische Kupplungsmittel zwischen dem genannten Rotor und dem genannten Teil, was es gestattet, einen Teil der nutzbaren Energie des genannten Arbeitsströmungsmittels in mechanische Energie umzuwandeln.
10. Einrichtung nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, daß in den unterschiedlichen Zonen des Rotors die genannten Leitungen sich mit Abständen zur Achse befinden, welche sich von einer Zone sur anderen unterscheiden, wobei von den genannten Zonen die eine die Wärmequelle und die andere die Kältequelle für das in den Leitungen umlaufende Arbeitsströmungsmittel bilden.
EP78400133A 1977-10-20 1978-10-11 Verfahren und Vorrichtung zur Energieumwandlung Expired EP0001732B1 (de)

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FR7731551A FR2406718A1 (fr) 1977-10-20 1977-10-20 Procede de conversion thermodynamique de l'energie et dispositif pour sa mise en oeuvre
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EP1180656A1 (de) * 2000-08-18 2002-02-20 Renzmann + Grünewald GmbH Spiralwärmeaustauscher
WO2008098968A1 (en) * 2007-02-14 2008-08-21 Heleos Technology Gmbh Process and apparatus for transferring heat from a first medium to a second medium
US9765994B2 (en) * 2007-02-14 2017-09-19 Heleos Technology Gmbh Process and apparatus for transferring heat from a first medium to a second medium
AT505532B1 (de) * 2007-07-31 2010-08-15 Adler Bernhard Verfahren zum umwandeln thermischer energie niedriger temperatur in thermische energie höherer temperatur mittels mechanischer energie und umgekehrt
AU2009265652B2 (en) * 2008-07-04 2015-10-29 Heleos Technology Gmbh Process and apparatus for transferring heat from a first medium to a second medium
GB0913988D0 (en) * 2009-08-11 2009-09-16 New Malone Company Ltd Closed loop thermodynamic
EP2489839A1 (de) 2011-02-18 2012-08-22 Heleos Technology Gmbh Verfahren und Vorrichtung zur Erzeugung von Arbeit
AT515210B1 (de) * 2014-01-09 2015-07-15 Ecop Technologies Gmbh Vorrichtung zum Umwandeln thermischer Energie
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US4010018A (en) * 1970-10-06 1977-03-01 Kantor Frederick W Rotary thermodynamic apparatus and method
US3931713A (en) * 1973-10-11 1976-01-13 Michael Eskeli Turbine with regeneration
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IT7828902A0 (it) 1978-10-19
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IT1101657B (it) 1985-10-07
JPH0253601B2 (de) 1990-11-19
FR2406718B1 (de) 1981-02-20
EP0001732A1 (de) 1979-05-02
JPS5477846A (en) 1979-06-21
FR2406718A1 (fr) 1979-05-18
US4285202A (en) 1981-08-25
ES474339A1 (es) 1979-12-01

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