FR3040427A1 - FRICTION TURBINE, ENERGY-GENERATING PLANT COMPRISING SUCH A TURBINE AND METHOD OF USING THE SAME - Google Patents

Abstract

The friction turbine comprises a stator for receiving a rotor, provided with at least one inlet of the fluid and an outlet of a fluid, said rotor comprising at least one coil (1), cylindrical with a circular base, open at the ends and free to rotate about a longitudinal axis, said coil being formed of layers of material wound on itself and never touching each other, thereby defining at least one spiral connecting the inlet and the outlet of said fluid and forming a channel fluid flow. The turn (3) of smaller diameter (R3) defines a central duct (4) fluid circulation and it comprises end caps, equipped with a rotation shaft whose free end leaves the stator, each cache end piece being adapted to hold one end of the spool, and one of the end caps is provided with a hollow rotation shaft defining a passage of the fluid and located in the extension of the turn (3) of smaller diameter ( R3). The invention also relates to a power generation installation equipped with such a turbine and its method of use.

Description

FRICTION TURBINE, ENERGY-GENERATING PLANT COMPRISING SUCH A TURBINE AND METHOD OF USING THE SAME

The present invention relates to a friction turbine as well as a power generation plant comprising such a turbine and its method of operation.

Such a turbine is a type of friction turbine, without blade, also called boundary layer turbine, designed in the early twentieth century by TESLA. It is based on the friction of a fluid, usually a gas, on the disk walls, the friction being due to the adhesion of the gas boundary layer and its viscosity. As it flows, the gas gives energy to the discs and drives them in rotation. The absence of blades allows a great robustness of such a turbine being simple construction.

Among the evolutions introduced since its creation, one can quote the addition on the superimposed rotary disks of spirals, engraved in the disks, in order to improve the output of such a turbine. US-A-2014/0252772 discloses such a turbine having a rotor equipped with a hollow central shaft and closed at one end. The gas enters the shaft through the open end and escapes from the shaft by spirals in disks mounted on the shaft. The outputs of the spirals, at the periphery of the rotor, are arranged so as to drive the rotor in rotation, in the opposite direction to the direction of rotation of the spirals. In other words, if there are two spirals, their outputs are diametrically opposed. In one embodiment of this turbine, the spiral has an exponentially increasing radius. Thus the gas exerts a force at a constant angle at every point of the spiral.

This being so, such a turbine is made from a stack of parallel disks, mounted on a central shaft. Such a construction is relatively complex, not only because of the number of parts but also by the difficulty to achieve precise and reliable fasteners between the different parts. Fasteners, due to vibration, tend to loosen and / or break, which is potentially dangerous, not to mention maintenance costs and leaks. Furthermore, it is found that the central shaft tends to expand axially under the effect of the heat generated during operation of the turbine while the discs expand radially. This generates constraints that weaken the structure, especially at the fasteners. The phenomenon of expansion also impacts the geometry of the spirals formed in the discs and therefore affect the performance of the turbine. The differentiated expansion of the discs and the shaft and the presence of fasteners also affect the seal between the constituent parts of the turbine. In addition, such an embodiment of the turbine induces a weight such that it penalizes the operation of the turbine. The aim of the invention is to propose another embodiment of a Tesla-type friction turbine of easy construction and maintenance while having an optimized performance and operation by overcoming the defects inherent in the presence of fasteners and to the construction mode described above. For this purpose, the subject of the invention is a friction turbine comprising at least one stator for receiving a rotor, said stator being provided with at least one fluid inlet and an outlet of a fluid, said rotor comprising at least one at least one coil, cylindrical with a circular base, open at the ends and free to rotate about a longitudinal axis, said coil being formed of layers of material wound on itself and which never touch each other, thus defining at least one spiral connecting the inlet and the outlet of said fluid and forming a fluid flow channel, characterized in that the smaller diameter coil defines a central fluid circulation duct and in that it comprises end covers, equipped with a rotation shaft whose free end exits the stator, each end cap being adapted to hold one end of the coil, and in that at least one of the end caps is eq. uipé of a hollow rotation shaft defining a passage of the fluid and located in the extension of the turn of smaller diameter.

Thanks to the invention, the coil, formed in one piece, is held in the stator by the end covers. The shapes of the ends and end covers are adapted to ensure and maintain the assembly during the rotation of the coil which is thus devoid of a central shaft separate from the rest of the coil. Thus, the fixing of the constituent parts of the turbine and the sealing are carried out by complementarity of shapes. This solves the problems due to the differentiated expansion between the parts, it is now always in the axial directions. Furthermore, the expansion of the coil and the end covers in the same direction makes it possible to reinforce the fixing and the sealing between the parts. This makes it possible to use the turbine at high pressures, typically greater than 100 bar, thus obtaining high powers. Such a construction also reduces the number of parts constituting the turbine, thus reducing the weight and bulk of the latter. Such a construction makes it possible to accurately and control the fluid flow channel defined by the turns, which optimizes not only the manufacture but also the efficiency of the turbine. The rotor, de facto formed of the coil and the end covers, is mounted in the stator. The fluid enters, for example, the periphery of the coil and escapes through one of the shafts fixed on the ends of the coil. Due to the absence of a traversing shaft mounted in the rotor, a smooth and undisturbed flow of the fluid is obtained as it circulates in the turbine, resulting in greater efficiency.

According to advantageous but non-mandatory aspects of the invention, such a turbine may comprise one or more of the following features: At least one of the end caps is removably mounted on one end of the coil. - The spaces between the turns of material are parallel to each other over the entire length of the coil. - The spaces between the turns of material are not parallel to each other over the entire length of the coil. - The stator is provided with a longitudinal slot for access to the internal volume whose length is adapted to the length of the coil, the fluid inlet being effected by this slot and its output by an end cap. - The stator is provided with a longitudinal slot for access to the internal volume whose length is adapted to the length of the coil, the fluid outlet being effected by this slot and its input by an end cap. - The entry and the exit of the fluid is carried out by the caches of ends. - A cylinder, de facto forming a stator, surrounds the coil and the end caps, said cylinder being fixed on the output shafts of the end covers. - The turbine comprises several coils connected in series by abutment, their longitudinal axes being merged. - The connection between two butted coils is formed by a connecting member provided on each side of a receiving housing of one end of the coils. The invention also relates to an energy production installation comprising at least one turbine according to one of the preceding characteristics, characterized in that it comprises at least one fluid collection member at the outlet of the turbine connected to a heat source. itself connected to the inlet of the turbine. The invention also relates to a method of using such an installation, characterized in that it comprises at least the following steps: a) introducing the fluid into the turbine at a pressure greater than the internal pressure of the turbine and at a given temperature, b) collect at the outlet of the turbine the fluid at a pressure and at a temperature lower than the inlet pressure and temperature, c) send the fluid collected in step b) to a suitable heat source to give up heat, - d) to collect the fluid at the end of step c) at a pressure and a temperature higher than those of step b), - e) to carry out a new step a) directing the fluid obtained in step d) in the turbine. The invention will be better understood and other advantages thereof will appear more clearly on reading the following description of several embodiments of the invention, given solely by way of nonlimiting example and with reference. In the accompanying drawings in which: FIG 1 is a perspective view of the coil according to an embodiment of the invention, Figure 2 is a view, on a larger scale, of one end of the constituent coil of the rotor of FIG. 1, FIG. 3 is a view similar to FIG. 1, on the same scale, of the coil of FIG. 1 with an end cap in place, FIG. 4 is a side view, at another scale, the coil of FIG. 3 with the two end covers in place, FIG. 5 is a side view, on a different scale, of a turbine with the coil of FIG. 4 in place in a stator, according to one embodiment of the invention, the FIG. 6 is a perspective view, on a smaller scale, of the turbine of FIG. 5 with a fluid inlet member in position on the stator, FIG. 7 is a diagram illustrating the use of a turbine that conforms to FIG. the invention in a closed circuit power generation plant, FIG. 8 is a side view, on a different scale, of several series connected turbines according to another embodiment of the invention, FIG. a perspective view, on a larger scale, of an end cap according to one embodiment of the invention and FIG. 10 is a perspective view, on the same scale as FIG. separator between two coils constituting a rotor in another embodiment,

FIG. 1 illustrates a member constituting the rotatable or rotatable part of a turbine according to one embodiment of the invention. In this case, this member is formed of a coil 1, also called bobbin, equipped with end covers.

The coil 1 is advantageously made of a metal or a metal alloy. As a variant, the coil 1 is made of another material, for example a composite material. According to yet another variant, the coil is made of at least two different types of materials.

In all cases, the coil 1 is formed of several layers of material wound on itself. These layers never touch each other. Thus, they define between them a space configured spiral.

Figure 1 illustrates a coil 1, cylindrical circular base, equipped with a single spiral, according to one embodiment of the invention. In a variant that is not illustrated, the coil comprises a plurality of spirals arranged offset relative to each other by a defined angular value.

The or each spiral starts from the outer face 2 of the coil 1 towards the inside thereof. In a variant not shown, the spiral starts from the center of the coil.

Subsequently, the space, itself configured in the form of a turn, which is located between two turns of material will simply be designated by the term turn.

The last turn 3, namely that having the smallest radius R3, with respect to a longitudinal central axis A of the coil 1, defines a central duct 4 for circulating the fluid. Here, it will be described, first, an embodiment wherein the central duct thus formed ensures the output of the fluid. The or each turn occupies the entire length L1 of the coil 1. Thus, the conduit 4 has the same length as that of the coil 1. The conduit 4 is straight and open at both ends. In other words, the first turn defines de facto a circulation duct which has the same role as a central shaft known from the state of the art but without it being an additional piece.

As shown in FIGS. 1 to 3, the space delimited by two consecutive turns of material has, in this embodiment, a variable width between the turn 5 of larger radius R5 and the turn 3 of smaller radius 3. L space E5 is therefore wider than space E3. Thus, the space between the turns of material is convergent in the radial direction from the outside of the coil 1 towards the inside thereof. The spaces between the turns are parallel to each other, with respect to the longitudinal axis A. In other words, the spaces between the turns can be assimilated to cylindrical housings with circular base, concentric and whose diameter varies according to a step not constant. A convergent spiral is thus produced in the direction of the center of the coil 1. It is conceivable that, in another embodiment, the spiral is divergent. Thus, two types of spiral can be defined: on the one hand, a spiral with parallel turns of material, thus a space-or turn-between the layers of material having a constant width and, on the other hand, a spiral in which turns of material are not parallel, therefore with a non-constant turn of the turn, ie diverging or converging with respect to the center of the coil.

The realization of such a coil 1 can be obtained, for example, by winding on itself a sheet of material, in particular a metal sheet. In another preferred embodiment, the coil 1 is made by techniques, known per se, for example, by wire EDM or by machining or 3D printing techniques. Such techniques, in particular wire machining or electroerosion, make it possible to obtain a dimensional accuracy that is not possible, or at least not in an easy manner, for winding a sheet of material. Indeed, the thickness of the material is generally between 0.1 mm and 300 mm, typically between 0.5 mm and 50 mm, depending on the coil 1 to achieve. The latter has a length L1 generally between a few centimeters and a few meters. It should be borne in mind that the length L1 depends on the flow rate and / or the fluid pressure, the viscosity and the nature of the fluid as well as the desired yields.

Similarly, the developed coil 1, that is to say the length of the sheet of material constituting the coil, before winding, is between a few tens of centimeters and a few tens, or even hundreds of meters, typically between 0.50 m and 500 m.

In all cases, the developed coil 1 must provide a minimum number of turns, for example equal to four, it being understood that there may be several tens or even hundreds of turns. The convergence, that is to say the decrease in the width of the space between the turns of matter, from the space E5 to the space E3, is calculated so that the speed of passage of the fluid in the spaces as far as possible, maximum while preserving a laminar flow. This calculation involves various parameters among which can be mentioned the inlet and outlet pressures of the fluid, the nature of the constituent material of the coil and its surface condition, the inlet and outlet temperatures of the fluid, its flow rate. , its viscosity. Similarly, the thickness of the material and the number of turns of material, and therefore the weight of the coil 1, are adapted to the desired inertia of the coil, therefore de facto of the rotor of the turbine.

In another embodiment not illustrated, the spiral is not convergent or divergent. In this case, the space-or turn-defined between two adjacent turns of material is constant over the entire section of the coil.

It is then possible, according to this other embodiment to manufacture such a coil by interlocking mutual prefabricated concentric cylinders. These cylinders are kept at constant spacing by the end caps or by separating members. It is conceivable that openings must be provided in the cylinders to ensure the flow of fluid between the outside and the inside of the rotor. In this case, it is necessary to perform a forced flow of fluid between the inside and the outside of the coil, so that the circulating fluid rotates the concentric cylinders. For this, it is necessary to perform baffles between the cylinders.

FIG. 3 illustrates a coil 1, one end of which is equipped with an end cap 8. This cap 8 is in the form of a circular cup whose internal diameter and the height of the edge are adapted to receive one end of the coil 1 This cover 8 is particularly visible in FIG.

The cover 8 is equipped with a central rotation shaft 7 extending perpendicularly outwardly from the face 8 of the cover 8 furthest from the coil. When the cover 6 is in place, the shaft 7 is in the extension of the duct 4 central coil. The attachment of the shaft 7 is removable. For this, the shaft 7 is screwed into a tapped hole centrally in the face 8 of the cover 8. The screwing is performed in the opposite direction of the rotation of the coil 1, so that the tightening is all the more strong that the rotation of the coil 1 about its axis A is fast. Such a solution has the advantage of achieving optimum sealing regardless of the speed of rotation of the rotor. In a variant, the shaft 7 is permanently fixed on the cover 6.

The face 80 opposite the face 8, therefore the facing face of the spool 2 when the cover 6 is in position, is provided with a housing for receiving the end 10 of the spool 1, the receiving housing is, advantageously, formed by circular grooves 81, which define turns, convergent or not, according to the embodiment of the turns of the coil 1, of shape and dimension complementary to the turns of the coil 1. In the case where, by for example, the turns of the coil 1 are concentric and non-convergent, the same is true of those constituting the receiving housing of the end cap 6, In other words, the face 80 of the end cap 6 is grooved so as to receive the free ends 10 or 11 of the coil 1, the connection and the seal between the cover 6 and the end 10 are provided by complementarity of shapes: in other words, we fix the cover 6 on the end 10. The rotation of the bob ine is advantageously carried out in the same direction as the winding of the turn, which induces a tightening all the more important that the friction forces are high.

If necessary, a seal is positioned at the bottom of the groove 81 to optimize the seal. Such a construction mode of the rotor allows a reversible mounting, without fixing, with a minimum of parts. Moreover, not only the question of expansion is solved, but the safety is improved since the faster the rotor rotates and the more the connection between the coil 1 and the cover 6 is tightened.

As illustrated in Figure 4, another cover 9, identical to the cover 6, equips the end 11 opposite the end 10 receiving the cover 6. The cover 9 is also provided with a central shaft 12 of rotation perpendicularly outwardly from the face 13 of the cover 9 farthest from the coil 1 and a receiving housing of the end 11, identical to the housing 81. In other words, whatever the end 10 or 11 of the coil, the latter can be mounted in a cover 6 or 9.

Thus, as shown in FIG. 4, the shafts 7 and 12 are aligned and in the extension of the duct 4,

At least one of the shafts, for example, shaft 7, is hollow and defines an outlet 70, visible in FIG. 5, of the fluid of the coil towards the outside of the turbine. The other tree 12 is here full.

In another embodiment not shown, the faces 80, 81 of the covers are not grooved. In this case, the ends of the coil are in direct support on the faces of the covers. If necessary, a seal is provided. Keeping the covers in place on the coil, in a sealed manner, is obtained, for example by threaded rods connecting the two covers, the length of each rod being greater than that of the coil.

In another embodiment not shown, at least one, advantageously both, cache 6 or 9 is permanently fixed on one end of the coil. Fixing is performed, for example, by welding.

FIG. 5 illustrates an embodiment in which the coil 1 is equipped with the covers 6 and 9, thus the rotor of the turbine T, in place in a stator 14. This is a cylinder with a circular base, of shape and shape. dimensions complementary to those of the coil 1. The cylinder 14 is provided with two openings 15, 16 formed in its full ends. These openings allow the passage, respectively, of the shafts 7 and 12. The shafts 7, 12 thus extend, by their free ends, out of the stator 14.

The openings 15, 16 are adapted to allow the free rotation of the shafts 7 and 12 around the longitudinal axis A, thus the free rotation of the coil 1, while avoiding the exit of the fluid. Advantageously, they are equipped with a seal. Similarly, in order to facilitate regular rotation, they can be equipped with sealed ball bearings. Thus, in the cylindrical stator 14, the rotor, formed by the coil 1 and the two covers 6 and 9, is free to rotate. The fluid, as indicated above, can exit through the conduit 70 formed in the shaft 7. As a variant, not illustrated, the stator has a shape other than cylindrical with a circular base. It may be for example a square-based volume, it being understood that the internal volume of the stator must preferably be of complementary shape to that of the coil 1. The fluid inlet in the turbine T, therefore the passage fluid from outside the stator 14 inside thereof is provided by an input member 17, visible in an embodiment illustrated in Figure 6. The input member 17 comprises a pipe d 170 of the fluid and a portion 171 which provides the connection between the pipe 170 and a slot, not visible, formed in the stator 14. The portion 171 has the same length, except that it is three-dimensional, that the slot of introduction of the fluid into the stator 14. The slot is oriented along the axis A of the coil 1. The slot has the same length as the opening of the turn 5 of greater width. In other words, the length of the slot corresponds to the length L1 of the coil 1, when it is devoid of the end covers 6 and 9. Thus the portion 171 has a generally so-called inverted hopper configuration. Such a shape, the slot and the portion 171, ensures a flow of the same fluid in the pipe 170 and in the slot, so when it arrives on the rotor. Advantageously, the portion 17 is fixed permanently on the stator, for example by welding.

Since the dead volume between the stator 14 and the rotor 1, 6, 9 is at constant pressure, the fluid inlet can be carried out at any zone of the rotor. Thus, in addition to the lateral inlet as illustrated, it is possible to provide a fluid inlet at the opening 16, for example, by a sleeve surrounding the shaft 12 and opening through an open end into the opening 16 and thus in the dead volume located between the stator and the rotor. In other words, the inlet and the outlet of the fluid are carried axially, through the shafts 7 and 12. Alternatively, the fluid inlet can be done at any other point of the stator.

It is easy to see that the flow of the fluid can also be carried out in the opposite direction to that described above. In other words, there is nothing to prevent such a turbine from being able to operate in both directions of circulation of the fluid, namely either as described or with a fluid inlet via the central duct 4 and an outlet through the 17. Of course, this requires a free rotation in both directions of the coil, without locking a direction of rotation is provided.

In another embodiment, a cylinder surrounds the coil and the end caps. This cylinder is sealingly attached to the output shafts of the covers, it being understood that this fixing may be final or not. Such a cylinder, de facto integral in rotation with the rotor, defines a member having the same function as a stator. It is understood that this configuration is also that encountered when the turbine is made with several concentric cylinders: the outer cylinder ensures, de facto, the role of stator.

The operation of the turbine T is now described with reference to FIGS. 1 to 8. A fluid is brought under pressure by the pipe 170 in the portion 171 and introduced through the slot into the internal volume of the stator 14.

By the shape of the portion 171.1a fluid inlet pressure is identical at any point of the introduction slot. The fluid is isobarically distributed between the inner face of the stator 14 and the outer face 2 of the coil, the dead volume between the stator and the rotor being at constant pressure. As the central duct 4 of the coil is in depression with respect to the outside of the coil 1, so with respect to the fluid introduction pressure, the latter moves towards the central duct 4, by taking the defined spaces by the turns of matter. Because of the small width of these spaces, namely less than 2 mm, it induces a significant friction of the fluid on the walls of the turns. This friction makes it possible to transform the kinetic energy of the fluid into mechanical energy. This is communicated to the coil 1 and drives it in rotation about its longitudinal axis A,

As the spacing E5 in the turn is, in the example, a width less than that of the slot, this causes an acceleration of the fluid when it enters the coil 1 and a decrease in its pressure.

During its passage between the turns closest to the outer face 2 of the coil 1, so at the beginning of the convergence of the space between the turns from the outside of the coil, the fluid accelerates while decreasing its pressure and temperature. The closer the fluid is to the duct 4 and the more the convergence is such that the space between the turns is of small width, the space E3 being the narrowest. The frictional forces of the fluid on the walls of the coil rotate the rotor. The acceleration of the fluid in the coil is also so strong that it also generates significant frictional forces that drive the rotor in motion.

Once in the conduit 4, the fluid is expanded relative to its inlet pressure. Likewise, the temperature of the fluid is lower than its initial temperature, it being understood that, in certain configurations, this temperature may be negative when the temperature is expressed in degrees Celsius.

At the outlet of the turbine T, the fluid is therefore at a pressure and at a temperature lower than that which it had when it entered the turbine T. The fluid is then discharged, in a non preferred embodiment, to the outside. Such a solution involves the reintroduction of a fluid under pressure relative to the final pressure of the turbine.

Another advantageous solution is to use this fluid in a closed circuit and, for this purpose, to bring it, at constant volume, to recover heat, for example via a heat exchanger on a device or by a heat source. external. Thus, the fluid, once recompressed and brought into contact with the heat source, will have its pressure and its temperature which will increase and will be greater than those which it had at the exit of turbine T, the cycle of production of energy then being able restart.

Figure 7 schematically illustrates such a cycle. The arrow F indicates the flow direction of the fluid in the installation. For use in a closed circuit, the shaft 7, receiving the outlet duct 70, is closed at its free end 71. A lateral opening 72 is formed in the shaft 7. At this opening a sleeve 18 surrounds the shaft 7. The sleeve 18 is provided with orifices ensuring the passage of the shaft 7 and allowing its free rotation, while preventing the fluid from coming out. Here the sleeve 18 is shown as being cylindrical with a circular base. It constitutes a fluid collection member at the outlet of the turbine T. In a variant, it has another shape. The sleeve 18 is connected by a conduit 19 to a heat source 20. This heat source 20 may be of various origin, in particular it may be a source of non-carbonaceous heat.

The heat source is connected to the fluid inlet pipe 170. The fluid in heat of the heat source 20 has a pressure and a temperature higher than those which it had at the exit of turbine T, the cycle, therefore the rotation of the coil 1 can continue.

As the shafts of the coil are, in known manner, connected to generatrices, the rotation of the coil 1 allows an electricity production or, alternatively, the rotational drive of a motor shaft.

Since such a turbine T can operate in a range of temperatures, inlet and outlet, between -10 ° C and 800 ° C, it is appropriate to choose the materials used to make the different parts according to these temperatures as well as pressures. Indeed, such a turbine T can operate between 1 bar absolute and 2000 bar absolute, preferably between 1 bar absolute and 500 bar absolute.

Figure 8 illustrates another embodiment of the turbine. Here, several coils, identical or not, are mounted in series. Such a solution makes it possible to produce turbines of great length by avoiding, or at least limiting, the phenomenon of kinking or twisting. For ease of reading, the stators and corresponding input members are not illustrated.

The coil 1D is identical to the coil 1, its shaft 12D being full. In order to optimize the rotation of the coils 1A to 1D, the fluid inputs of each stator receiving one of the coils 1A to 1D are angularly offset. In an advantageous variant, these inputs are aligned. In any case, it is to facilitate the synchronous rotation of the various coils 1A to 1D synchronously,

The connection between the coils 1A to 1D is ensured so as not only to allow optimum circulation of the fluid between the coils but also preserving the removable nature of the turbine. For this, as illustrated in Figure 10, the connection between two coils and performed by means of a connecting member 21 or separator. This member is a flat disc whose two faces 22, 23 are provided with a receiving housing 24 of a free end of a coil 1A to 1D, the housing being similar to the housing 81 equipping the covers 8, 9. As for the grooves 81, the grooves 24 form a spiral with a constant pitch. It is conceivable that, the connection between the connecting member 21 and the coils 1A to 1D being made by complementarity of shapes, the dimensions of the grooves 24 are adapted to those of the ends of the coils. In other words, if one or two coils 1A to 1D are provided with a convergent spiral, the grooves 24 then form a complementary convergent spiral. A seal will be placed, if necessary, between the coils and the separator (s). Alternatively, the faces 22, 23 of the separator 21 are devoid of grooves 24. The separator and the ends of the coil are then devoid of complementary shape and are assembled with a single seal.

In order to ensure the exit of the fluid and the passage of the latter between the coils 1A to 1D, the center 25 of the connecting member 21 is pierced with a through orifice ensuring the passage of fluid on either side of the the member 21, the orifice having the same dimensions as the central flow channel of the coil. It is the same on the cover 6, the center 82 is open and communicates with the interior of the shaft 7.

Thanks to the connecting member 21, it is possible to associate, in a demountable manner, the number of coils required to form a given rotor. The connection is effected in all cases in a sealed manner, by complementarity of shapes.

When the fluid outlet is effected by the member 17, the operation is similar to that described above.

It is also possible alternatively to make the stator, and therefore the outer casing of the coil, integral with it, for example by welding or machining. In this case, the stator is integral in rotation with the coil.

Claims (12)

1, - Turbine (T) friction comprising at least one stator (14) for receiving a rotor, said stator being provided with at least one inlet (17) of the fluid and one outlet (70) of a fluid, said rotor comprising at least one coil (1; 1A to 1D), cylindrical with a circular base, open at the ends (10, 11) and free to rotate about a longitudinal axis (A), said coil (1; 1A to 1D ) being formed of layers of material wound on itself and which never touch each other, thereby defining at least one spiral connecting the inlet (17) and the outlet (70) of said fluid and forming a fluid flow channel, characterized in that the smaller diameter coil (3) (R3) defines a central fluid circulation duct (4) and comprises end caps (8, 9) equipped with a shaft of rotation (7, 12) whose free end (71) leaves the stator (14), each end cap (6, 9) being adapted to hold an end 10, 11) of the coil (1; 1A to 1D), and in that at least one (8) of the end caps is provided with a hollow rotation shaft (7) defining a passage (70). ) of the fluid and located in the extension of the turn (3) of smaller diameter (R3). 2, - turbine according to claim 1, characterized in that at least one of the end caps (6, 9) is removably mounted on one end (10, 11) of the coil (1; 1A to 1 D). 3, - Turbine according to one of claims 1 or 2, characterized in that the spaces (E3, E5) between the turns (3, 5) of material are parallel to each other over the entire length (L1) of the coil ( 1). 4, - Turbine according to one of claims 1 or 2, characterized in that the spaces (E3, E5) between the turns (3, 5) of material are not parallel to each other over the entire length (L1) of the coil (1). 5. Turbine according to one of the preceding claims, characterized in that the stator (14) is provided with a longitudinal slot for access to the internal volume whose length is adapted to the length (L1) of the coil (1). ), the inlet (17) of the fluid being effected by this slot and its outlet (70) by an end cap (6). 6, - Turbine according to one of claims 1 to 4, characterized in that the stator (14) is provided with a longitudinal slot access to the internal volume whose length is adapted to the length (L1) of the coil (1), the fluid outlet being effected by this slot and its inlet (70) by an end cap (6), 7, - Turbine according to one of claims 1 to 4, characterized in that the inlet and the outlet of the fluid is effected by the end caps (6, 9), 8. - Turbine according to one of the preceding claims, characterized in that a cylinder, de facto forming a stator, surrounds the coil and the end caps (6, 9), said cylinder being fixed on the output shaft (7, 12) end covers (6, 9). 9. - Turbine according to one of the preceding claims, characterized in that it comprises a plurality of coils (1A to 1D) connected in series by abutment, their longitudinal axes being merged. 10, - Turbine according to claim 9, characterized in that the connection between two butted coils (1A to 1 D) is formed by a connecting member (21) provided on each face (22, 23) of a receiving housing ( 24) of one of the ends of the coils (1A to 1D). 11. - Power generation installation comprising at least one turbine (T) according to one of the preceding claims, characterized in that it comprises at least one collection member (18) of the fluid output (72) of the turbine (T) connected (19) to a heat source (20) itself connected (170) to the inlet (17) of the turbine (T). 12, - A method of use of an installation according to claim 11, characterized in that it comprises at least the following steps: - a) introducing the fluid into the turbine (T) at a pressure greater than the internal pressure of the turbine (T) and at a given temperature, b) collecting at the outlet (72) of the turbine (T) the fluid at a pressure and at a temperature below the inlet pressure and temperature, - c) sending the fluid collected in step b) on a heat source (20) adapted to give off heat, - d) collecting the fluid at the end of step c) at a pressure and at a temperature higher than those of step b), e) performing a new step a) directing the fluid obtained in step d) in the turbine (T),