WO1982000495A1

WO1982000495A1 - Improvements to systems for generating power with bladings driven by the water speed

Info

Publication number: WO1982000495A1
Application number: PCT/FR1980/000130
Authority: WO
Inventors: L Collard
Original assignee: L Collard
Priority date: 1980-07-23
Filing date: 1980-08-12
Publication date: 1982-02-18
Also published as: OA06598A; FR2487438A2; EP0057176A1; AR221956A1

Abstract

This blading forms the hydraulic wheel (14) of one-hull boats or boats with two or a plurality of catamarans (15-16) which form venturi and are rigidly supported by a horizontal upper structure (17) forming a frame, also supporting independently the shaft (18) of the hydraulic wheel (14) protected vertically; a speed multiplier block (20) fixed on the beam of the structure (17) and driven by the shaft (18) effecting, directly or indirectly, the driving of an electric generator (23), of a hydraulic pump or any other power generating apparatus. These bladings may also drive directly floating hulls provided in the inside with speed multiplying devices to control a power generating apparatus.

Description

Improvements to energy production systems by blading driven by the speed of water.

The present invention relates to the production of electric or motor energy from floating hollow volumetric solids, driven in rotation by the natural wire of a watercourse.

According to the invention, profiled blades have been produced connecting the periphery of two or more rotating shells mounted on the same fixed or rotary axis, and intended to allow a high efficiency by using only the kinetic energy of the water, due to its own speed. This optimum yield being ensured by the symmetrical and continuous profile of each blade, allowing changes in the direction of the liquid vein over a significant active path, so as to prolong and successively postpone the motive action of the water by effect not massive but fluid, or laminar flow. According to a first characteristic, each blade has a flat strip arranged longitudinally and profiled in the form of a sinusoidal curve, thus forming bent blades forming successive opposite corridors. Each blade being circularly offset from the neighboring blade.

According to another characteristic, a raised axial corridor raised transversely with respect to the axis connecting the rotary hulls, and arranged perpendicularly to this axis, is connected with one or at least two opposite corridors, arranged symmetrically and with an equal or different spacing, so as to authorize the continuous, gradual and symmetrical change of direction of the liquid stream, with a view to its travel on the profile of the blade.

According to another characteristic, the lateral connection faces of the opposite corridors are arranged parallel or in triangulation in the same plane or in different planes, while the corridors proper are also oriented towards each other, either parallel or obliquely. According to another characteristic, the terminal parts of each blade are connected to the spherical parts of the rotating shells by constituting a curved tapered section forming or not leaking spouts of the liquid stream, after its path and guidance on the profiled surface of the blade.

According to another characteristic and as a variant, each blade is presented with a flat strip wound longitudinally in a helix in the form of an Archimedes screw, and more circularly and externally bent around the periphery of the rotating elements, so as to constitute a toroidal crown and helical fixed by any known means and constituting by each blade inclined in a helix, a progressive profile allowing the permanent and continuous support of the liquid stream relative to its directional axis, by effect of viscosity or dynamic fluidity.

According to another characteristic of the alternative embodiment, each toric and helical crown is arranged symmetrically with respect to the neighboring crown, in the case of two juxtaposed shells, so as to form two tori with helical blades with convergent and symmetrical inclinations with respect to the median vertical axis. According to another characteristic, the blades profiled in the form of a curve constitute the hydraulic wheel or wheels of monohull moored boats, with one or two wheels, or else of boats with two or more catamarans of any material, which form a venturi by their profile. rear or front; said catamarans being held rigidly spaced apart, by a horizontal upper frame forming a frame, constituted by the assembly of beams composed in the form of a trellis and intended to mechanically support the rotating axis of the hydraulic wheel housed vertically and protected in height and in width , between said catamarans linked together by said frame. According to another characteristic and in the stated case of boats, the shaft of the hydraulic wheel authorizes in a gear ratio, by means of a transmission forming a speed multiplier, fixed on the lateral beam of the frame, l drive of an electric generator, hydraulic pump or other producing machine or device of energy.

According to another characteristic, the profiled blades in the form of a curve connect floating hulls internally comprising the speed multiplier mechanism, while being of a diameter greater than that of the external diameter of the vane whose axis receives the tail anti tail; the blades of said blades being further established without any return on the balls. According to another characteristic, the profiled blades in the form of a toric and helical crown, are fixed directly to the outer periphery of a shell allowing internally, by means of their toothed crown, the driving of all speed multiplier devices of the fixed axis. and its retaining means whether or not forming a fixed or adjustable venturi spacing.

These characteristics and others will emerge clearly from the following description.

To fix the subject of the invention, without however limiting it, in the appended drawings:

Figure 1 is a small scale, a perspective view of a profiled blade provided with an anti-torque tail unit, connecting two volumetric shells, and produced according to the invention; Figure 2 is on a larger scale, an external profile view corresponding to Figure 1;

Figure 3 is a front view illustrating the fixing conformation and mounting of each blade relative to the axis connecting two or more shells;

Figure 4 is a side view in transverse section along the line A-A of Figure 3;

Figure 5 is a view similar to Figure 4, but in the case of corridors with curved leading faces; Figures 6, 7 and 8 are schematic front views, illustrating different shapes of a blade and its attachment relative to the axis connecting two shells;

FIG. 9 is a schematic view illustrating an embodiment of a blade made of several interchangeable and assembled elements;

Figure 10 is a schematic view illustrating the arrangement of the blading on either side of a single shell floating;

Figure 11 is a schematic view illustrating the arrangement of a vane between two hemispherical shells and which can contain the energy transformation mechanisms;

Figure 12 is a schematic view illustrating modular blades without axis, arranged on either side of an axial shell; Figures 13 and 14 are schematic views illustrating the circulation and changes of direction of the current streams on the successive convex and concave parts formed by each blade; assumed or actual effect of friction head losses; Figure 15 is on a larger scale, a schematic profile view, illustrating the circulation of the water veins in line with the circular positions of the submerged parts of a blade;

Figure 16 is a small scale, a schematic view illustrating a generator driving from via a connecting shaft, an apparatus or machine placed on the bank;

Figure 17 is a small scale, a schematic view illustrating the drive of an apparatus or machine placed on the bank, by a plurality of generators forming a variable number of modules. Cables mounted in self-triangulation risking the balanced distribution of the retaining force from an axial fixed point on bearings supporting the rotary shaft; Figure 18 is a schematic front view, illustrating the alternative embodiment of a profiled blade in the form of an O-ring with helical peripheral blades. The dashed line illustrates the circular shaping of the vane, after the helical winding of a flat or profiled strip;

FIG. 19 illustrates in a front view, the fixing, the shaping and the mounting of two toric and helical blades made according to the variant, on shells coupled together. This mounting can also be done on the axis connecting them; Figure 20 is on a larger scale, an external profile view corresponding to Figure 19;

Figure 21 is a small scale, a schematic sectional view illustrating a suction pump with a rotor formed by vanes in the form of a toric and helical crown;

Figures 22, 23 and 24 are respectively front views, in plan and in profile, of a boat with two catamara forming a venturi, and equipped with a hydraulic wheel under for sinusoidal curves; these catamarans can also be equipped with one or more helical blades;

FIGS. 25, 25a, 26 and 27 are respectively schematic and side views, illustrating various means of driving a pump, an electric or other mechanical generator, from the rotary shaft of the hydraulic wheel and fixed on a lateral beam of the boat frame;

Figure 28 is a perspective view illustrating the arrangement of a profiled blade connecting two shells of flattened shape, whose fixed axis is coupled to a tail;

Figure 29 is a partial perspective view illus trant the assembly and fixing of the ends of the strips on a flange of the axis; Figure 30 is a purely schematic view illustrating the arrangement of symmetrical panels in the shape of opposite "V", in the case of toric and helical rings fixed peripherally on juxtaposed shells;

Figures 31 and 32 are purely schematic front and side views and in perspective, of a speed multiplier device, housed in a shell, for driving hydraulic pumps;

Figure 33 is a purely schematic view on a small scale, illustrating the drive of an apparatus or machine placed on the bank, by a hydraulic wheel in the form of sinusoidal bands, with an extreme float forming ventu opposite the profile of the bank ;

FIG. 34 is a partial view in section of a speed multiplier device housed in a shell, for the purpose of driving electric generators; Figure 35 is on a small scale, a diametrical sectional view corresponding to the embodiment of Figure 34, and illustrating the mounting of all the generators relative to the toothed ring secured to the shell;

Figure 36 is a partial view, in diametral section, illustrating the mounting and driving of a hydraulic pump fixed at the end of a radial arm;

FIG. 37 is a side view in dirty cross section along line 37-37 of FIG. 36.

According to the present invention, and in the case of two rotary shells 1 and 2 connected diametrically to each other by an axis 3, fixed or possibly driven in rotation, said shells 1 and 2 allow, by their external periphery, the fixing of a blading of great length formed by a plurality of vanes 4 arranged circularly and angularly preferably at regular intervals. These blades 4 being variable in number depending on the diameter of the blade, the speed of the current, or the power. Each blade 4 is presented as illustrated in FIGS. 3, 13 and 14, in the form of a flat strip which is judiciously folded and preferably curved in the same plane, in order to constitute symmetrically and parallel to the axis.

3, a substantially sinusoidal curve disposed in elevation and forming successive and opposite corridors 4 ¹ and 4 ² , preferably of the same profile.

This sinusoidal curve is further established to constitute a symmetry of corridors with respect to the middle part between the two shells 1 and 2, so as to allow the separation of the jet or stream of water into equal parts, on both sides. other of the middle corridor and following the symmetrical profile of said curve, until the evacuation from the ends.

In the example illustrated in FIG. 3, the central corridor 4 ¹ , of concave shape and of semi-circular section, is connected by rectilinear and parallel transverse sides

4 ⁴ also constituting support and fixing points on the axis 3, to the lateral and opposite corridors 4 ² of convex shape, the terminal and tapered ends of which 4 ⁵ are twisted helically to apply tangentially and are fix by any known means, on the periphery of each corresponding shell 1 - 2. It must be considered that the end portions of the connector 4 ⁵ of each blade 4, constitute or not by their inclination due to their positioning not perpendicular but oblique with respect to the axis 3, converging or diverging buckets 4 ⁶ , intended for facilitate and orient the exit of the jet of water after its pushing action over the entire surface.

It is obvious that the end portions of raccor Dement 4 ⁵ may optionally also be arranged perpendicular to the axis 3, so as to obtain a EVACU ation parallel to the direction of water flow. As illustrated in Figures 13 and 14, we note that under the action of the current, illustrated by the broken line, the streams of current change twice in direction, turning either the concave and middle section 4 ¹ , as shown in Figure 13 , or the two opposite and convex sections 4 ² ; the said veins grouping together in the bottom of the said sections 4 ² or of the section 4 ¹ , as the case may be, after having lost pressure, exhausted their living forces.

It must be considered that in the transverse direction, as illustrated in FIG. 15, the water collected in the concave parts 4 ¹ of each blade, tends from position a to position b, to escape towards axis 3, therefore to go up and not to escape down. Between position b and position the water veins then have a reverse movement which consists in escaping downwards, while continuing to push the vane for its rotation, but with a reduced speed thanks to the effect of friction of the energy generator.

We also note that, according to FIG. 15, each blade is angularly offset with respect to the neighboring blade, with a determined angle of incidence α making it possible to obtain maximum torque in the driving direction.

In order to increase the attack surface of each blade 4, the central corridor 4 ^{1 as} well as the lateral and opposite corridors 4 ² , can be made transversely with attack faces which are no longer flat, but curved and rounded - transversely at 4, as illustrated in Figure 5. Likewise, each blade 4 can be produced with an asymmetry of successive corridors including, for example, a central corridor with a large opening connecting with lateral corridors with the same opening. In the same way, the corridors

4 ¹ or, 4 ² may be of any section, such as partially round, as illustrated in FIG. 6, or else very open, FIG. 7, or tightened, FIG. 8. The blades thus obtained are arranged circularly and according to a variable outside diameter in function of the rotation speed to be obtained; in principle, a small diameter generating a high speed of rotation, and vice versa.

It is also emphasized that these blades can be produced by molding in one or more interchangeable elements, assembled together as illustrated in FIG. 9, and also by modular elements, as illustrated in FIGS. 11 and 12, with shells of all shapes and all suitable materials. These vanes thus defined can authorize by a current or water fall, the rotation drive of any floating member such as hulls, provided with any mechanical device generating electrical energy, hydraulic pump, pneumatic or other pressure pump. This drive takes place via the vane, acting simultaneously either on the hulls and the integral axis, or only on the hulls, the axis remaining in this case fixed, or even only on the axis, the hulls remaining immobilized.

It should also be emphasized, as illustrated in FIG. 10, that this blading can be applied to a single shell, the blades being fixed symmetrically in opposition on the outer periphery and possibly on the fixed or rotating projecting axis.

According to an alternative embodiment illustrated in FIGS. 18, 19 and 20, each blade is in the form of a crown crown with externally and peripherally, a plurality of helical blades. To this end, this blade is obtained for example from a flat metal strip 10 wound in a helix around a fictitious longitudinal axis 0, so as to form, like an Archimedes screw, a plurality of helical blades 10 of the same pitch, and of which the number is a function of the developed peripheral length of the shells 1 or 2 to be driven. Each blade 10 ¹ is either perpendicular to the imaginary axis 0, or even angularly with a width

U variable, taking into account the drive power to be obtained.

After formation of the blades 10 ¹ , this assembly constituting an Archimedes screw, is then wound around the shell 1 or 2, and preferably along a plane corresponding to its largest diameter, to thus form a toric and helical crown which is fixed, by any appropriate means, on the periphery of said shell, perpendicular to the axis 3. It is obvious that this blade can be produced by a plurality of helical elements assembled together by riveting, welding or other means.

In the case of a plurality of shells 1 and 2 assembled together and rotating on the common axis 3, each toric and helical crown is. arranged symmetrically with respect to the neighboring crown, as illustrated in FIG. 19, so as to allow convergence of the blades relative to the median axis X-X.

According to FIG. 16, an exemplary application of the blading forming a hydraulic generator has been illustrated, for the supply of an electric generator G fixed on the bank and mechanically connected to the rotary axis 3, via of cardans H.

According to another example of application, illustrated in FIG. 17, the motor shaft 3 is driven in rotation by a plurality of generators G made up of modular elements coupled together. This assembly, connected either to a generator G placed on the bank, or to any other receiving device or machine, rotates on points of articulation? intended to limit the bending of the shaft 3. A plurality of cables C arranged symmetrically in triangulation and braced by cross members C ¹ , allows the equal distribution of the force from the fixed point R to the bearings P.

It is obvious that apart from electricity production, the mechanical generator thus produced can drive receivers using a high torque at low speed, such as material elevators, winches, bucket water lifting pump, conveyors ... This blading device can be completed by an anti-torque tail unit allowing the guidance of the assembly, parallel to the stream of water, while avoiding the reverse sernent of the assembly due to the importance of the resistive torque. This empennage is established in the form of two vertical plates 7 and 8, arranged laterally and vertically, braced between them by rods 9 or by any other means. These plates 7 and 8 form a counterweight at 7 ¹ and 8 ¹ at their rear ends, to balance the floating assembly during the rotation of the blade.

It is also noted that these plates 7 and 8 allow centering and maintaining the ends of the fixed axis 3 or even its free rotation by forming bearings. This empennage can receive any fixed member of an engine cooperating with the axis 3, in the case of its rotational drive.

Finally, it is important to note that the blading device as produced, can be driven in rotation by motor, for the sole purpose of ensuring the propulsion of a boat or other floating object.

According to FIG. 21, the profiled blades 4 or 10 as described above, are fixed to the circular periphery of a shell or of a hub 11, to be housed in the arrangement of a housing 12 of a body of pump, so as to constitute, by their rotation generated by any known means on their axis 13, the blades or rotor of a suction or discharge pump for liquid, gas, powdery products or the like; said blades which can inversely receive any jets of liquid or gas to form a pneumatic or hydraulic motor.

According to the embodiment illustrated in FIGS. 22, 23 and 24, the profiled blades 4 or 10, but preferably, the blades 4 in the form of a sinusoidal curve, constitute the hydraulic wheel or wheels 14 of monohull boats moored or cir culting in a stream of water; or also boats with two or more catamarans 15 and 16 arranged vertically and laterally below an upper frame 17. Each catamaran 15 or 16 is in the form of a non-submersible block or box, of parallelepiped section, with at its ends sloping interior faces

15 ¹ and 16 ¹ forming by their symmetrical and axial profile in

"V", uh venturi intake opposite the hydraulic wheel or wheels 14. The catamarans are fixed by their upper side, on lugs integral with the base of the profiled frame 17 in the form of a frame.

This frame 17 is constituted by the assembly of profiled beams in the form of a trellis, of prismatic section, and whose lateral beams 17 ¹ allow the fixing of supports receiving the bearings in which the shaft 18 of the hydraulic wheel 14 rotates. .

It should be considered that the hydraulic wheel 14 interposed between the catamarans 15 or 16 forming floats, is of a width corresponding on the one hand to its own driving value and to that of the venturi, and of a determined external diameter allowing additionally in height, the protection of its blades by the lower overflow of catamarans 15 - 16, during launching or in the event of a significant drop in the water level. The shaft 18 of the hydraulic wheel 14 authorizes by any speed multiplier devices fixed on the corresponding lateral beam 17 ¹ , the drive of any device or machine, generator of electric current, pump or other. According to the embodiment illustrated in FIG. 25, the shaft 18 transmits by toothed pinions connected by a chain 19, the rotary movement to a speed multiplier block 20 fixed on a metallic sole fixed to the base of the lateral beam 17 ¹ . This block 20 directly allows by its output shaft, the coupling of the shaft of an electric generator 21. As a variant, as illustrated in FIG. 25, the chain 19 can be arranged between the multiplier 20 and the generator 21. According to the illustrated in figure 26, the block speed multiplier 22 is directly coupled to the end of the shaft 18, and receives, as before, the electric generator 23. According to the embodiment illustrated in FIG. 27, the shaft 18 allows, by means of a known flexible coupling 24 , the drive of a hydraulic pump 25 with hose for drawing from the watercourse and external distribution.

Oh also note that in this case of application of blades 4 to form the hydraulic wheel 14, the terminal parts of each blade 4 are connected directly and perpendicularly at 4 relative to the shaft 18, while being fixed by rivets 26 or otherwise, on a corresponding flange 18 ¹ , as illustrated in FIG. 29I It is quite obvious that, as indicated initially, the blades 4 can be disposed between rotating shells 1 - 2 connected transversely to each other by a fixed axis 3 or possibly driven in rotation , and the ends of which are made integral with an anti-tail stabilizer 7. In this embodiment, it is planned to establish said shells 1 - 2, with a diameter greater than that of the ribs 4, to ensure their circular protection, and to produce the rotating shells 1 - 2 in the form of a flattened sphere as illustrated in FIG. 28. In the case of the shells being driven 1 -2 by the blades 4 or 10, the latter comprise retaining means f orming or not venturi, and internally speed multiplier means, using the rotary movement of a ring gear fixed between the two hemispheres of each shell, to act on any device generating electric current, pump or other. To this end, according to FIGS. 31, 32, provision is made for making a shell 27 driven alone or coupled with; other shells, by means of the blades 4 or 10, and provided internally with a multiplier means. speed for driving hydraulic pumps.

To this end, the toothed ring 28 allows its free rotation from its shoulders relative to the fixed carriages 29 held in position relative to the hollow fixed axis 30, by means of arms 31. Each carriage 29 internally receives a train of speed multiplier pinions, the small pinion 32 of which is driven by the teeth of the crown 28, and the external pinion 33 meshes with the wheel 34 mounted at the end of the shaft 35 passing through said carriage 29 On the shaft 35 of each carriage, is fixed a pulley 36 connected by belt 37 to the controlled pulley 38 of a longitudinal shaft 39 held by two flanges and intended to allow by its opposite ends, the rotation drive of all devices such as fixed pumps 40 communicating with the longitudinal opening of the hollow axis 30 which thus forms, by one of its ends, a suction branch 30 plunging into the stream, and on the opposite side, the discharge line 30 2 terminating towards the outside of the shell 27.

In another embodiment illustrated in FIG. 34, the fixed axis 41 receives the support frame of all of the opposite electrical generators 42 and of their multi-speed plicator devices cooperating with the teeth of the crown 43.

These generators 42 are integral with radial arms 44 with or without centering rollers 45 cooperating with the crown 43.

According to FIG. 35, the speed multiplier device drives one or more pumps 46 for discharging or sucking a fluid terminating in a hydraulic motor.

According to FIG. 30, the single or coupled rotating shells provided with blades 4 or 10 are housed between profiled panels 47 - 47 arranged symmetrically while forming a venturi. These panels 47 and 47 forming anti-torque of the axis, can be adjustable in spacing according to the force of the current. According to FIG. 33 and in the same way, in the case of mounting a hydraulic wheel 14 produced as indicated above, or of a succession of rotating shells mounted on the same shaft 48, the latter controls a generator 49 placed on the bank, while on the opposite side, the shaft 48 is held by a vertical float 50 adjustable or not in position, the profile of which in the shape of a "V" cooperates with the symmetrical profile 51 formed by the block 51 or profile of the bank , so as to form venturi.

It is also emphasized that the profile of the venturi can also be adjustable according to the profiles of the bed and the bank. To this end, said venturi can be extended externally on each side, by elements 52 - 53 hinged together and established in the form of metal frames or not. These frameworks can also be non-floating and fixed to the bottom of the water. It is important to note that it is also planned, within the framework of the invention, to equip the rotating shells 1 - 2 so that their fixed shaft 3 constitutes the stator, 'while the internal profile or possibly the crown 43 or 28 forms the rotor, according to conventional criteria or those defined in linear electric motors.

On the other hand, it is quite obvious that the generator (s) equipping hulls or boats, can be dynamos or alternators with an adjoining or inherent regulating panel, controlled by switches or automatically electronically, to authorize changes in intensity (by resistive circuits for example), for the sole purpose of choosing the value of the electric current according to the requested use. This provision also makes it possible to install one or more additional motors on the boats corresponding to floods and high waters.

Claims

claims

1. Profile blading for the rotary control of axes of drag of energy producing mechanisms mounted on floats, or of floats or hulls directly driven in rotation and including mechanisms producing herbs and comprising a plurality of blades respectively disposed circularly and radially between said shells spaced apart from one another, characterized in that it is in the form of a flat strip (4) profiled in the form of a substantially sinusoidal or helical curve with a symmetry of successive and opposite corridors or blades (4 ¹ - 4 ² ), allowing the change of direction of the liquid vein over a long distance, so as to prolong the motor action of the water thanks to the sliding effect and lapiinary flow thereof, and not thanks to its mass effect;

2. Profile airfoil according to claim 1, characterized in that the axial passage (4 ¹ ) between the shells (1 - 2), is raised transversely relative to the axis connecting said shells, while being disposed perpendicularly to connect symmetrically with opposite corridors

(4 ² ) similar or not, arranged in an equal or different spacing and opening, so as to take advantage of the laminar flow;

3. Profile airfoil according to claims 1 and 2, charac terized by the fact that the outer curves formed by the corridors and forming leading faces, are inclined or curved along their width, and made in any section, in order to obtain a optimal pressure drop;

4. Profile blading according to: claims 1, 2 and 3, charac terized by the fact that the lateral connection faces (4 ⁴ ) of successive and opposite corridors, are arranged perpendicular or oblique with respect to the axis connecting the shells ( 1 - 2) with or without transverse inclination;

5. Blasting according to claims 1, 2, 3 and 4, characterized by the fact that the terminal parts (4 ⁵ ) of each blade connect with the spherical parts of the rotating shells by constituting a tapered and curved section forming leakage necks (4 ⁶ ) converging or diverging from the liquid stream, after its passage and laminar guidance on the profiled surface of the strip (4) where it has acted flididically;

6. Profile auger according to claim 1, characterized in that according to an alternative embodiment, each strip (10) is wound on the one hand in a helix, like an Archimedes screw, and then applied and fixed circulate on the outer periphery of each shell (1) (2) or an axis connecting them, so as to constitute a toric and helical crown constituting by each of its inclined blades (10 ¹ ) arranged radially and perpendicular to the axis of rotation, a continuous profile allowing by the effect of sliding and laminar flow, the progressive support of the liquid vein, so as to prolong the motor action;

7. Profile blading according to claim 6, characterized in that each toric and helical crown is arranged symmetrically with respect to the neighboring crown, in the case of two shells (1) (2) juxtaposed, so as to form two tori with helical blades with convergent and symmetrical inclinations with respect to the vertical axis;

8 profiled auger according to claims 1, 2, 3, 4, 5, 6 and 7, characterized in that each blade is only made integral with the axis (3), for its drive in rotation relative or not floating hulls;

9. Profile airfoil according to claims 1, 2, 3, 4, 5, 6 and 7, characterized in that each blade is or is not only made integral with floating shells, the axis (3) remaining fixed;

10. Profile airfoil according to claims 1, 2, 3, 4, 5, 6 and 7, characterized in that each blade is produced by molding in one or more interchangeable elements assembled together, of the same modules or of different modules;

11. Profile airfoil according to claims 1, 2, 3, 4, 5, 6 and 7, characterized in that it comprises a tail fin in the form of vertical plates (7) (8) forming cdntre-weight (7 ¹ ) (8 ¹ ), arranged laterally and braced eh (9) to allow centering and holding the rotating ends or not of the axis (3);

12. Profile blading according to claims 1 and 6, characterized in that it constitutes the hydraulic wheel or wheels (14) of monohull boats, or of boats with two or more catamarans (15 - 16) which form venturi from their flare (15 ¹ - 16 ¹ ), and are held rigidly and vertically apart, by a hori zohtale upper frame (17) forming a frame, constituted by the assembly of composite beams; said frame also supporting, independently, the bearings of the shaft (18) of the hydraulic wheel (14) whose periphery is protected by said catamarans (15), means ensuring the driving of any fixed apparatus or machine or not on the framework (17);

13. Profile airfoil according to claim 12, characterized in that the terminal parts of each blade (4 ¹ ) in the form of a strip, are connected directly and perpendicularly at (4) at each end on a flange (18 ¹ ) of the tree (18);

14. Profile cutting according to claims 12 and 13, characterized in that the shaft (18) of the hydraulic wheel (14) transmits by toothed pinions connected by an endless chain (19), the rotary movement to a multiplier block speed (20) fixed on a metal sole integral with the lateral beam (17 ¹ ) of the frame (17); said block (20) authorizing by its output shaft, the coupling of the shaft of one or more electric generators (21) also fixed on the sole;

15. Profile blading according to claims 12 and 13, characterized in that the speed multiplier block (22) is directly coupled at the end of the shaft (18) of the hydraulic wheel (14), and receives directly at the end the electric generator (23);

16. Profiled auger according to claims 12 and 13, characterized in that the shaft (18) allows, via a coupling (24), the driving of a hydraulic pump (25) with drawing pipe in the watercourse and outside distribution;

17. Profile blading according to claims 1 and 6, charac terized in that it constitutes the blades of a rotary pump after its free rotation housing in the bore of a housing (12) of a pump body , for suction or delivery of any liquid, gaseous or pulverulent product

18. Profile airfoil according to claims 1 and 6 and its arrangement between rotary hulls (1 - 2) connected transversely to each other by an axis (3) whose ends are made integral with an anti-torque tailplane (7), characterized by the the fact that said rotating shells (1) and (2) are of flattened spherical shape, with a diameter greater than that of said blade (4); said spheres internally received any speed multiplier device;

19. Blade according to claims 1, 6 and 18, characterized in that a speed multiplier device, housed inside each shell (27), comprises a toothed ring (28) which cooperates with fixed carriages ( 29) integral with the hollow axis (30) and arranged radially; each carriage receiving a pinion (32) driven by the toothing of the crown (28) and which meshes with an external pinion (33) luf itself engaged with a wheel (34) mounted on a shaft (35) passing through said carriages ( 29); said shaft (35) cooperating by pulley and belt with one of the corresponding pulleys (38) of a common shaft (30) held by fixed flanges and intended to allow, by its ends, the drive in rotation of all devices or machines housed inside the hull (27);

20. Blading according to claims 1, 6, 18 and 19, characterized in that the shaft (35) allows by its ends, the driving of fixed pumps (40) communicating with the longitudinal opening of the hollow axis (30) which forms on the one hand on one side, a suction branch (30 ¹ ) plunging into the watercourse, and on the opposite side, the delivery pipe (30 ² ) leading to the 'exterior of the shell (27);

21. Profiled auger according to claims 1, 6, 18, 19 and 20, characterized in that each rotary shell or more rotary shells (1) or (27) are inserted axially between vertical profiled panels (47) and (47 ¹ ) with fixed or variable spacing, to form a venturi and also hold the axis in position (3) or (30);

22. Profile airfoil according to claims 1, 6 and 21, charac terized by the fact that in the case of a hydraulic wheel (14) or of a uniform succession of rotating shells (1 - 2) mounted on the same shaft (48 ) and connected by blades or directly extending from blades, said shaft (48) controls a generator (49) placed on the bank, while being held on the opposite side, by an adjustable float (50) whose profile in the form of " V "cooperates symmetrically with the profile (51 ¹ ) formed by the solid (51) or profile of the bank, so as to constitute a venturi adjustable in spacing, according to the 'roughness of the current, of the elements (52 - 53) articulated between euk and in the form of floating or non-floating frames, extending the venturi according to the profile of the bed and the bank;

23. Profile airfoil according to claims 1, 6 and 18, characterized in that the fixed shaft (3) of each rotary shell (1) or (2) constitutes the stator, while the crown (28) or directly the interior of the hull, receives or forms the rotor, in the manner of linear electric motors;

24. Profile auger according to claims 1, 6, 12, 14, 15 and 19, characterized in that the electric generators are connected to a regulating element with manual or automatic control, allowing the variation of the intensity of the electric output current, according to the required use.