HIGH-EFFICIENCY THRUSTER INDEPENDENTOF THE OUTSIDE ENVIRONMENT

Abstract

The invention relates to an ecological thrusting device enabling optimum thrust independent from the outside environment. It consists of a special Francis turbine (1) from which the fluid is axially ejected at the outlet of the vane (1′), at a relative speed W2t, and is collected in a defined free space of a straight radial pump (2). Under the action of the centrifugal force, the limit of the current lines forms a fixed virtual barrier Yt, thus preventing the centrifuged fluid from reaching the bottom of the pump in the free space area MNBCPQ, thereby eliminating the antagonistic force exerted on said zone. As a result, the thrusting force exerted on the turbine by the fluid remains intact. As the fluid leaves the pump, it is axially reinjected at a relative speed W2p into a tank (4) for resupplying the turbine. There is therefore an energy exchange between the pumps and the turbine that form a closed circuit, the entire system being driven by a motor (10). It is shown that the thrust force P=(½) pπω2 r4; p being the density of the centrifuged fluid in en Kg/m3; ω being the angular speed of the turbine in rad/s; and r its radius in metres and P in Newtons. The calculation shows that the amount of thrust generated is very high; said thruster can be used to generate mechanical energy anywhere in space, and especially to drive the most highly efficient flying machines.

Description

The present invention relates to an ecological propulsion device, enabling attainment of an optimum thrust with high precision and independent of the exterior environment.

At the 18^th century, mankind was producing mechanical energy by separating water molecules (evaporation by heating). This is the origin of the steam engine or external combustion engine. Then at the end of the 19^th century appeared the internal combustion engine or the spark ignition engine. This time, instead of separating the molecules, they are broken outright (cumbustibles) by oxidation (combustion) in order to produce mechanical energy. Note that in the steam engine, the molecules of fuel (coal) are also broken during combustion in order to heat and vaporize (separate) water molecules.

A technological breakthrough occurred in the middle of 20^th century that completely changes the destiny of humanity: instead of breaking the molecules, the atoms are broken or, exactly, the nuclei of the fissionable element (Uranium 235) releasing a huge amount of energy. This is nuclear fission.

Unfortunately, all these modes of energy production are inevitably accompanied by CO₂, the notorious greenhouse gas, or radioactive waste, harmful to our environment, and that seriously compromise Sustainable Development. Yet Sustainable Development requires energy development.

To cope with this dilemma and break this vicious circle, there is a solution without breaking the material (the molecules of fuel or the fissionable elements); the asymmetry is created from the symmetry of nature, ie breaking its symmetry, which changes neither the nature nor the state of the material. This principle of asymmetry is exploited in order to create the propulsive force in a mechanical system generating symmetrical forces (action and reaction). The invention is therefore to design a mechanical system operating in accordance with this principle that we will discover in the following pages.

The power unit comprises, in fact, according to a first feature, a Francis type reaction turbine, but with certain specialties of design and operation of this Turbine, is axially coupled to a straight radial Pump downstream, and upstream to a variable speed electric motor. The Turbine Pump unit forms a closed circuit, controlled by this variable speed motor which is used to start and to compensate for the loss of hydraulic and mechanical energy.

Unlike the Francis Turbine, the Turbine of the power unit, centerpiece of the system, powered by a straight radial Pump, restores, at the outlet of the wheel, the fluid with a minimal and relative axial velocity, W_2t equal to the circumferential velocity, r×ω (r=radius of the Turbine, ω=angular velocity in radians/second), thus with a non-axial absolute velocity.

C_2t=W_2t √12 and not negligible. Therefore, usable energy still remains after the passage of the fluid in the wheel. The modulus, the direction of the absolute velocity, C_1t, as well as the relative pressure, P_1t at the entrance of the wheel, are calculated, on the one hand, to ensure a given flow rate with a corresponding rotational speed and, on the other hand, to overcome the centrifugal force imposed by the rotation of the fluid. The angle α of C_1t remains fixed and is approximately 45°, irrespective of the flow.

However, the shape of the channel (ceiling and belt) is identical to that of the Francis Turbine, except that the radius at the inlet is the same as that of the outlet. It is determined, by the method proposed by Mr. Bovet, professor at the Polytechnic University of Lausanne, from the velocity figure (see bibliography).

The blade of the Turbine, having the shape a half spoon and adopting the profile of the channel, is curved so as to straighten the velocity vectors at the inlet, C_1t orthogonal to the axis of rotation, 90° and radially straight at the outlet. Thus, at the outlet, these velocity vectors are parallel to the axis of the Turbine. The assembly is surrounded by a cylindrical sleeve forming the exterior wall of the belt. According to the conditions of flow, another variant of blading, approximating that of the Francis Turbine, is a trapezoidal plate, twisted and curved so as to ensure the same function of recovery as previously. The number of blades is a function of the specific velocity, and is between eleven and seventeen. At the outlet of the Turbine, the blade will be placed side by side to that of the Pump, thus forming a solid piece for the continuity of fluid flow. Finally in order to best ensure the sealing of the shaft with the exterior environment, the bottom of the Turbine is equipped with fins in order to keep the fluid away from the shaft by centrifugation.

The straight radial Pump, actuated by the Turbine, recuperates the fluid at the outlet of the latter with a relative velocity, W_1p=W_2t. The relative velocity at the outlet of the Pump is also axial, having modulus W_2p=R×ω(R=exterior radius of the Pump). The exterior radius R of the Pump is approximately double that of the Turbine. The fin of the Pump is a plate having a radially enlarged straight L-shape, extension of the blade of the Turbine. The fins are maintained and reinforced by two spaced profiled crowns, forming cells that guide the flow of the fluid. To better convey the fluid, these cells adopt to the boundaries of the lines of current. From the outlet side of the Turbine, its configuration is a truncated cone with exponential curvature, and from the opposite side it is a truncated straight cone whose generator is tangent to the current lines that we will see later in the mathematical study of the flow.

Between the hub and the centrifuged fluid, is provided a free space (without centrifuged fluid) that has the shape of a truncated paraboloid surmounting the base of a cone just to the inlet of the Pump. This free space, its form and its volume play a crucial role in the design and the operation of the power unit that we will see later. To avoid overlap between the threads of current at the inlet of the Pump, the radius of the hub must not be less than 37% of that of the Turbine. At the outlet of the Pump, the fluid having acquired its maximum energy, passes axially through a stationary tank. A spacer part of the tank, at the axil between the Pump and Turbine, is used to guide the flow of fluid to the inlet of the latter in order to resupply it. The outlet of the Pump limited by the exterior diameter of this spacer, forms a ring whose thickness determines the rate of flow. In operation, there is thus energy exchange between the Turbine and the Pump.

The bottom of the Pump, in the free space, has two cooling ports whose opening is controlled by two solenoid valves. The cooling circuit operates only in case of overheating of the Turbine Pump unit. While in the zone where the centrifuged fluid exists, a port is provided for measuring the static pressure of the centrifuged fluid at a given point, and one deduces from it the volume of free space in order to regulate it by adding or removing the necessary volume of the centrifuged fluid. The width of the crown of the centrifuged fluid determines the relative pressure, P_1t at the inlet to the Turbine.

As the velocities are uniformly distributed on concentric circles at the outlet of the Pump, the fluid will be channeled in a circular, non spiral tank as the case of the Francis Turbine. We have already seen that from the relative axial velocity at the outlet of the Pump, W_2p=R×w, it follows that its absolute velocity, C_2p=×√2. W_2p, deviates from 45° with respect to the direction of the axis, and in the direction of rotation. The tank having the form of a bowl with flat bottom constitutes, with the spacer, a channel that directs the fluid to the Turbine via the distributors. The profile of the distributor is that of an elongated drop of least hydrodynamic resistance. We recall that the mean line of the distrubutor forms an angle α of C_1t of approximately 45° at the inlet of the Turbine. In order to reduce vibration, the number of distrubutor fins must not be multiple of the number of blades of the Turbine.

At the ends of the common shaft of the Turbine Pump unit, axial stops are mounted in tandem with sealed bearings for supporting the thrust generated by the power unit. The assembly of the Turbine Pump tank unit is envelopped by a cylindrical structure that forms a closed chamber, allowing traversal of the common shaft coupled to a drive motor.

The materials used in the manufacture of the hydraulic turbomachine and its technology fit perfectly in the implemenation of the power unit.

Finally the variable speed drive motor with frequency modulation enables the start-up, the maintenance of rotation during the exchange of energy between the Pump and the Turbine, and the control of the thrust with great precision.

Regarding the operation, let us return to our Turbine. After having transferred its energy in the wheel up to the outlet, that is to say, to the immediate inlet of the Pump in free space, the fluid retains its relative minimal axial velocity, proportional to the radius (W_2t=r×ω). Consider a reference XOY linked to the Turbine, OX being carried by the axis of rotation and OY by its outlet base which represents the radius, r of the Turbine

We have W_2t=r×ω=Y×ω=W_1p

At the inlet of the Pump, the element of fluid mass dm of the fluid is subjected to the centrifugal force f=dm×r ω²=dm×Y. ω², Yet f=dm×γ=dm×Y″(t); thus Y″(t)=Y(t)×ω²

By integrating this differential equation, we obtain:

Y=Y_o exp_ωt  (1)

On the OX axis, we have X=W_1p xt=Y_o×ωt or X/Y_O=ωt

By replacing ωt with X/Y_O in (1), we obtain: Y=Y_O·exp X/Y_O

These lines of current are thus independent of w and depend only on Y_O. We demonstrate that they are tangent to the line Y=e·X (e=2.7182 . . . ) which is fixed. In other words, whatever its velocity, the fluid ejected from the Turbine will not pass through the line Y=e·X, but it is diverted to the exterior of the free space. This free space is limited by a volume of revolution, determined by this tangent and a section of parabola of equation X=(r²×ω²)/2 g, g being the acceleration of gravity. It is therefore a paraboloid section surmounting the base of a cone we have already mentioned above. Its volume is therefore determined. It is in the zone of this free space where is created the imbalance (asymmetry) of the forces exerted by the moving fluid. Therefore, the ejected fluid will not reach the bottom of the Pump in the free space zone. It is as if this bottom were shifted to the infinit. The Turbine Pump unit must be therefore be partially filled with centrifuged fluid.

Let us now see the thrust generated by the power unit. For reasons of symmetry, the forces exerted by the moving fluid on the walls outside of the axial free space zone cancel out. Only remaining is the thrust exerted on the Turbine in the axial zone opposite the free space. Let us first calculate the maximum flow rate Q (with the radius of the hub r₀=0 and neglecting the section of the blade relative to that of the Turbine).

We know that at the outlet, we have a linear distribution of velocities: V=r×ω.

dQ=V·ds with ds=2πr·dr

We thus have: Q=∫₀^rV·ds=∫₀^r rω·2πr·dr=(⅔)πωr³

And the mass flow rate q=p×Q=(2/3)p^-rrwr³, p being the density of the fluid. According to the principle of linear momentum, by being ejecting from the Turbine, the fluid exerts on the latter a dynamic thrust P such that:

P=∫₀^rV·p dQ=p ∫₀^r r² ω²2 πr·dr=(½)ρπω² r⁴

One can say that the free space that exists in the Pump creates the asymmetry, source of this thrust P on the sealed rotating Turbine, because if the Turbine Pump unit were completely filled with centrifuged fluid, all the forces exerted by the moving fluid would be symmetrical and therefore self cancel. Consequently, this finite volume free space, breaking the symmetry of nature, plays an important role in the propulsion system that we have mentioned above. In addition to its large useful load bearing capacity [(½) ρπω² r⁴], this power unit, independent of the exterior environment and environmentally friendly, assures optimal safety for priceless human lives, thanks to its flexibility and workability.

To improve the performance of the power unit, one can reduce the frictional forces by covering the surfaces that contact the fluid flow with a layer of PTFE (Teflon), and use as centrifuged fluid, carbon tetrachloride (CCl₄) in place of water, since it is more dense and has a substantially equivalent dynamic viscosity, given that the thrust is proportional to the density of the centrifuged fluid. Note that the presence of the hub radius r₀ (nonzero)=37% of r, radius of the Turbine provided above, does not practically change the intensity of the thrust P, because [(½) ρπ² (37%·r)⁴] is negligible [(½) ρπω² r⁴]. Finally the drive motor with variable speed frequency modulation allows the thrust control at will with great accuracy. One can use the power unit throughout space propellant to produce mechanical energy, thus energy in general and in particular to equip the flying vehicles, even those with vertical takeoff. For example, the power unit whose radius of the Turbine, r=10 cm, rotating at 3000 rev/min, and using water as centrifuged fluid, generates a thrust P approximately 1550 kg. This thrust is sufficient to vertically levitate a flying vehicle of more than one ton.

FIG. 1 shows a section along the central axis of rotation of the power unit.

FIG. 1 shows the blade of the Turbine (1′) in perspective.

FIG. 3 shows a variant of the blade of the Turbine (1″) in perspective.

FIG. 4 shows the lines of current (13) at the inlet of the Pump.

FIG. 5 shows the distributors (12) seen from above.

Referring to these drawings, the device includes a special type Francis Turbine (1) whose blade of the wheel (1′) rectifies the velocity vectors at the entrance, C_1t (FIG. 5) orthogonal to the axis of rotation, 90° and radially straight to the outlet with an axial minimum relative velocity, equal to the circumferential velocity, r×w (r being the radius of the Turbine, w the angular velocity). At the outlet, the fluid is collected in a free space, MADQ (MNBCPQ being the net free space) by a straight radial Pump (2), whose fin (2′) forms a part united with the Turbine blade (1′) for continuity of flow.

The fins (2′) are maintained and reinforced by two spaced streamlined crowns (3′) forming cells (3) that guide the fluid flow. To better convey the fluid, these cells (3) match the boundaries of the current lines Yi (FIG. 4) which are fixed, regardless of the speed of rotation. The relative velocity at the outlet of the Pump, W_2p is also axial and equal to the circumferential velocity, R×ω (R being the radius of the Pump). The fluid will then be directed to the inlet of the Turbine via the distributors (12) in FIG. 5, contained in the tank (4). The Turbine (1) will thus be powered for operating the Pump and the cycle recommences in the closed Turbine Pump. Thus there is energy exchange between the Turbine and the Pump.

The turbine Pump unit is secured to a common drive shaft (7) mounted on the ends of axial stops in tandem with sealed bearings (6) for supporting the thrust generated by the power unit. The Turbine Pump tank assembly is contained in a sealed chamber enveloped by a cylindrical structure (11) enabling passing of the drive shaft coupled to a motor (10). The startup is provided by the motor (10) having variable speed and frequency modulation, which controls the thrust of the power unit with high accuracy.

The shape of the channel of the Turbine (ceiling and belt) is the same as that of the Francis Turbine, except that the radius at the inlet is the same as that of the outlet. The shape of the blade of the wheel (1′) in FIG. 2 is that of a curved half-spoon so that the velocity vectors relative to the outlet, W_2t, are axially straight as we already specified above. Under the conditions of flow, another variant of blading approximating that of the Francis Turbine, is a trapezoidal plate (1″) in FIG. 3, twisted and curved so as to ensure the same recovery function. The bottom of the Turbine is equipped with sealing fin (5) in order to separate the fluid from the shaft by centrifugation, which enables to better provide the sealing of the relative to with the exterior environment.

The fin of the Pump (2′), following the wheel (1′), has the shape of a radially enlarged straight L in order to satisfy the flow conditions imposed above. The bottom of the Pump comprises two ports communicating with the cooling circuit (9) in the free space zone, whose opening is controlled by two solenoid valves that operate only in case of overheating of the closed circuit Turbine Pump. The width of the crown of the centrifuged fluid (L) determines the relative pressure, P_1t, at the inlet of the Turbine. This parameter is controlled through the third port (8) by removing or adding the centrifuged fluid according to the measure of the static pressure by a pressure gauge, carried out there. The flow rate depends on the width of oulet (E) of the Pump. The tank (4) lined with a spacer (4′), having the shape of a bowl with flat bottom, is compartmentalized by distributors (12) whose center line forms an angle α of C_1t of approximately 45° (FIG. 5). The profile of the distributor is that of an extended drop having least hydrodynamic resistance.

As regards the operation, one knows that the energy density of the fluid is maximum at the inlet of the Turbine, and minimum at the outlet. After having transferred its energy into the blade of the wheel (1′) of the Turbine, the fluid is collected in the free space MADQ of the Pump with a relative axial and minimumal velocity W_2t=r×ω=W_1p, relative velocity at the inlet of the Pump; thus it is subjected to centrifugal acceleration, r×w². In relation to a reference XOY tied to the Turbine (FIG. 4), OX being drawn by the axis of the Turbine, and OY by its base, which represents the radius, it is shown that the equation of the lines of current is of the form Y=Y_o·exp X/Y_o, independent of w, and that these lines of current are tangent to the line Y_t=e·X(e=2.7182 . . . ) which is fixed. This tangent plays some role, the role of virtual barrier preventing centrifuged fluid, ejected from the Turbine, from reaching the bottom of the Pump in the free space zone, which creates an imbalance of forces exerted by the moving fluid. Furthermore, it enables direction of the fluid towards the outlet of the Pump to resupply the Turbine, thus forming the closed circuit.

Knowing the distribution of relative axial velocities at the outlet of the Turbine, the mass flow rate q=(⅔) ρπω² (r³−r₀³) can be calculated, r₀ being the radius of the Turbine hub, and p the density the centrifuged fluid. Let us now study the thrust of the power unit. For reasons of symmetry, the forces exerted by the moving fluid on the walls outside the axial free space zone are canceled out. By ejecting from the Turbine, according to the principle of linear momentum, we show that the fluid excerts a dynamic thrust P=(½) ρπω² r⁴ (neglecting r_o, the radius of the hub of the Turbine, and the section of the blade relative to that of the Turbine). In the case where the radius of the hub of the Turbine, r₀=37% of r, radius of the Turbine cited above, the calculation shows that the new thrust P′=98% of P. Finally, to improve the performance of the power unit, the contact surfaces with the fluid flow will be covered with a layer of PTFE (Teflon) to reduce friction, while using, as centrifuged fluid, carbon tetrachloride (CCl₄) in place of water, since the CCl₄ is more dense and has a dynamic viscosity slightly equivalent.

The power unit is designed to produce mechanical energy, thus energy in general without CO₂ emission or radioactive waste, and in particular to propel flying machines, even those having vertical takeoff, throughtout space while preserving the environment and ensuring Sustainable Development in the field of energy.

Claims

1. An ecological power unit characterized in that it comprises a special turbine of the Francis type, from where the fluid is axially ejected to the outlet of the blade with a relative velocity, W2t, and is collected in a free space (without centrifuged fluid) of a straight radial Pump in order to be axially reinjected with a relative velocity, W2p into an immobile tank in order to be resupplied to the Turbine via distributors with an absolute velocity C1t with the pressure P1t, thus forming the closed circuit in a sealed wall, the Turbine Pump unit being actuated by a motor coupled to a common shaft.

2. A power unit according to claim 1 characterized in that the relative axial velocity, W2t (or W1p, relative velocity at the inlet of the Pump) is equal to the circumferential velocity, r×ω, and it is the same as the relative axial velocity at the outlet of the Pump, W2p.

3. A power unit according to claims 1 characterized in that the absolute velocity, C1t at the inlet of the Turbine with a pressure, P1t, ensures, first, a given flow rate and, second, overcoming the centrifugal force imposed by the corresponding rotation of the fluid.

4. A power unit according to claim 3 characterized in that the radius of the hub at the outlet of the Turbine, r0 is equal or greater than 37% of the radius of the Turbine outlet, r; in order to avoid overlap between the current threads in the free space zone of the Pump.

5. A power unit according to claim 4 characterized in that the blade of the Turbine could have the form according to the conditions of the fluid flow.

6. A power unit according to claim 1 characterized in that the bottom of the Turbine is equipped with sealing fins in order to separate the centrifuged fluid from the common shaft communicating towards the exterior.

7. A power unit according to claim 1 characterized in that the bottom of the Pump comprises a port for the taking of the static pressure of the centrifuged fluid, and regulating it if necessary.

8. A power unit according to claim 7 characterized in that the bottom of the Pump, in the free space zone, comprises two ports whose opening is controlled by two solenoid valves that communicate with the cooling circuit towards the exterior.

9. A power unit according to claim 1 characterized in that the contact surfaces with the fluid flow are coated with a layer of PTFE (Teflon) in order to reduce the friction.