CA2025601A1 - Rotor power conversion apparatus and method - Google Patents

Abstract

ROTOR POWER CONVERSION APPARATUS AND METHOD

Abstract of the Disclosure An apparatus for converting fluid flow and pressure into rotational mechanical power at high efficiency, has a hollow pressure-tight rotor with central fluid entrance and radial fluid passages, thrust-jets, a rotor support and bearing means and a fluid supply. The thrust-jets extend from the rotor and impart tangential reaction thrust or torque to the rotor by ejecting fluid approximately tangential to the arc described by the rotor's rotational motion, the thrust being always relative to its point of origin and continuously amplified by the increase in fluid pressure within the rotor due to the enforced rotation of the fluid together with the rotor and the centrifugal force acting on the fluid coincidental to its rotational motion. The rotor has rigid axles attached along its axis of rotation, at least one of the axles being hollow to admit fluid. In one embodiment the rotor is suspended over a fluid reservoir by a solid upper axle with bearings and support frame while the hollow lower axle extends downward from the rotor into the fluid supply beneath the rotor from which fluid enters the rotor through a sealed rotating hollow joint channelling fluid from the bottom of the reservoir via a feed pipe within the reservoir. The upper axle extends through low friction bearings on the upper support frame to provide a power take-off whereby mechanical power may be transmitted by gears, pulleys or the like. Rotor speed governors, an air purging mechanism and a shut-off mechanisms are provided. A method for operating the apparatus is described.

Description

ROTOR POWER CON~TERSIO~ APPARATUS AND ME~HOD

Field of the Invention This invention relates to the field of mechanical power converters and in particular to the field of mechanical power conversion apparatus which convert the flow of the fluid to rotational mechanical power at high efficiency.

Backaround of the Inyention In prior art there are many devices by which rotational mechanical power has been extracted from the kinetic or potential energy of moving fluid. Devices have included the water wheel, the water turbine and "Pelton wheel" and various turbines in which fluid under the influence of external pressure flows radially outwardly or inwardly past curved vanes to impart its force to the vanes and create torque. The present invention falls into the latter category but the method of power conversion is significantly different from the prior art in order to achieve higher efficiencies.

In conventional power conversion apparatus, moving fluid under the influence of gravity or pressure from an outside source is directed tangentially against vanes or paddles as in the case of the water wheel, "Pelton wheel" or water turbine; or it is directed radially outwardly or inwardly to impact against and escape freely past curved vanes as in the case of various water, air and exhaust turbines. The fluid transfers its energy to the paddles or vanPs by impacting against them and, as the paddles or vanes move at increasing velocity away from the point of impact, the force of impact of fluid against them decreases.
Thus, as the tangential velocity of the rim of the wheel or rotor increases, the torque on the wheel or rotor decreases as a ; 35 function of the geometry and angular velocity of the turbine. The moving fluid transfers some of its kinetic energy to the vanes or paddles, losing some of its velocity in the transfer, but escapes past the vanes or paddles, still retaining a considerable proportion of its velocity and Xinetic energy. In the present invention, this escaping energy is reduced as will be further described. In the present invention, the tor~ue on the rotor is caused by jet thrust reaction originating at and acting tangen-tially to the arc described by the outer periphery of the rotor.
Because jet thrust reaction is always relative to its point of origin and undiminished regardless of the movement of that point of origin, being dependent only upon the efficiency of the jet and the pressure which feeds it, the torque on the rotor does not decrease as the rotational speed-of the rotor increases.

Secondly, whereas the movement and/or pressure of fluid in conventional devices is supplied from an outside source such as external pressure or gravity, the working pressure of the fluid in the present invention is increased within the hollow rotor itself by the centrifugal force acting upon the fluid like a yreatly enhanced artificial gravity acting radially outward as the fluid rotates with the rotor. To accomplish this, the working fluid is freely admitted to the centre of the hollow rotor but allowed only restricted escape at the diametral periphery of the rotor through jets much smaller in aggregate cross-sectional area than the aggregate cross-sectional area of the passages by which fluid enters and travels outward from the centre to the periphery within the rotor. At the same time the fluid is forced to rotate with the rotor by being conducted radially outward in discrete passages as it gradually moves outwardly from the centre to the periphery of the rotor to replace fluid which is expelled from the thrust-jets by the centrifugally-induced pressure.

The jets eject a relatively small volume of fluid compared to that which can freely flow radially outward from the hub, while being forced to rotate with the rotor, so as not to disturb the predominately static (relative to the rotor) pressure head within the rotor.

By these means, the velocity and kinetic energy of the fluid is first converted to a substantially static pressure head of fluid within the periphery of the rotor and thence to a jet thrust originating at and reacting tangentially to the arc described by the periphery of the rotating rotor, such thrust being always relative to its point of origin and not diminished by the movement of that point of origin. The thrust produces korque on the rotor, relative to a fixed frame of reference, which is extracted as rotational power at the axis in a conven-tional manner.

An explanation of the mathematical relationshipsinvolved will aid in understanding the working ~rinciples of this invention. For simplicity, the diametral periphery of the rotor will be called the rim and the hub where the fluid enters will be called the centre. The jets are at the rim and thrust tangentially to it. The fluid enters at the centre and is forced, by radial passages or partitions, to rotate with the rotor as the fluid moves gradually toward the rim where it is constrained except for a portion which can escape via the thrust-jets. Such portion is a small amount in proportion to that which the passages can transfer with minimal friction losses. The fluid within the rotor acts much like a fluid flywheel exerting centrifugally-induced pressure outwardly from the centre toward the rim of the rotor.

Mathematically, excluding friction losses, thepressure of the fluid inside the rim due to the centrifugal force acting on the column of fluid radially disposed between the centre and the rim, is always proportional to the tangential velocity of the rim regardless of the diameter of the rotor; i.e. a 1 ft.
diameter rotor at 20 R.P.S. gives the same pressure as a 2 ft.
diameter rotor at 10 R.P.S. Quantitatively, by conventional centrifugal pump design formula, it is shown that the centri-fugally-induced pressure within the rim of the rotor is suffi-cient to eiect fluid from the jets at the same velocity, relative to the jet, as the tangential velocity of the jet and rim, 2 ~
relative to a ~ixed fxame o* reference. The acceleration of fluid from the jets tangential to the rim of the rotor, causes an e~ual and opposite reaction thrust to be imposed on the rim of the rotor, such thrust being relative to the jet and not diminished by the tangential rotational movement and velocity of the jet fixture in the opposite direction, the ejected fluid has very little velocity remaining relative to a fixed frame of reference;
having given up almost all of its kinetic energy to ~he rotor as tangential reaction thrust.
Experimental jet thrust velocities of .95 in relation to theoretical values are readily achieved with correct jet design as set forth in various manuals, (Ref. 1) as are net thrust values of .9 of theoretical values in relation to pressure.

Theoretical pressure head H = (V) 2 2g where V = rim velocity, and g = acceleration due to gravity.

Velocity of fluid from jet V = V~--H

After allowing for friction losses and inefficiencies just as in conventional machines, a high ratio of output power to input kinetic or potential energy is nevertheless achieved.

Summary_of the Invention An apparatus for converting fluid pressure into rotational mechanical power has the object of providing a more efficient means for converting input power into output power than is conventionally obtainable.
In its broadest form, the invention provides an apparatus for converting the power of a fluid flow into a mechanical power output, the apparatus comprising a hollow rotor ~56i~ ~
mounted for rotation about a central axis relative to a fixed frame of reference and provided with a thrust-supplying jet on the circumference of the rotor and fluid supply means for supplying the fluid flow to the interior of the rotor at a point on the axis of the rotor. The apparatus is adapted to provide enforced rotation of the fluid in the interior of the rotor together with the rotor, and constrainment of the fluid within a diametral periphery of the rotor, other than fluid flow through the jet. The fluid pressure is thereby converted into a tangen-tial rotational reaction thrust acting at a point at or near thediametral periphery of the rotor, the magnitude of the thrust acting at the point being dependent only on the fluid pressure within the rotor.

According to one aspect of the invention the apparatus converts input power to output power at high efficie.ncy by a sustainable rotational reaction thrust originating on a rotor, where the thrust, being relative to the rotor, propels the rotor at high rotational velocity relative to a fixed frame of reference. The apparatus has thrust-jets, a pressure-tight hollow rotor radially disposed around a hollow hub with fluid entrance at one or both sides of the hollow hub and thrust-jets tangentially oriented around the diametral periphery. The hollow rotor has discrete radially oriented internal passages or partitions extending from the hub to, or nearly to, the internal diametral periphery of the rotor to freely conduct fluid radially outward from the hub while enforcing its rotation together with the rotor. The apparatus has a rotor support shaft and low-friction bearing means, a bearing support, a power take-off and a fluid supply. The thrust-jets extend from the rotor and impart rotational thrust to the rotor by ejecting a pressurized stream of fluid in a direction approximately tangential to the arc described by the rotor's rotational motion while, at the same time, the rotor's rotational motion causes a centrifugally induced increase in the pressure of the fluid which feeds the thrust-jets from within the rotor; the pressure thus generated being additive to external input pressure to the hub of the . . .

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rotor. ~he rotor has a rigid a~le or axles as hollow intake pipe or pipes attached to the rotor along the axis of rotation, the axle(s) being supported by the bearing means to freely rotate therein. Fluid is admitted to the hollow intake pipe(s) or hollow intake pipe(s) which may also serve as axle(s), and thence through the hollow hub to the radial feed arms or channels within the rotor. The radial feed arms or channels feed fluid through at least an 8:1 contraction ratio to the thrust-jets. In the case of liquid being used as the working fluid, fluid is admitted to the inta]ce pipe(s) through a rotating seal in order to exclude air. The axle(s) extend through low friction bearings on the rot~r support to provide a power take-off whereby mechanical power may be transmitted by gears, pulleys and the like.
Starting mechanism, rotor speed governors, air purging mechanism in the case of liquid operated units, and shut-off mechanisms are provided.

Brief Description of the Drawing Figure 1 is a front elevation view, partially in cross-section of one embodiment of the apparatus showing the retract-able, jet-siphon pressure injection nozzle in its retracted position~

Z5 Figure 2 is a front elevation view, partially in cross- section, of one embodiment of the apparatus showing the retract-able, ~et-siphon pressure injection nozzle in its pressure injection engaging position.

Figure 3 is a front elevation view, partially in cross~
section, of a second embodiment of the apparatus showing the one-way valve in the open position.

Figure 4 is a top oblique view, partially cut away, of one embodiment of the rotor of the invention.

Figure 5 is a top oblique view, partially cut away, of a second embodiment of the rotor of the invention.

Figure 6 is a top oblique view, partially cut away, of a third embodiment of the rotor of the invention.

Figure 7 is a top elevation view, partially cut away, of greater detail of the outer end of a radial feed arm of the third embodiment of the rotor of the invention showing a centrifugal-force operated, poppet type governor release valve, a pressure operated jet-siphon air purging mechanism, and a correctly shaped thrust-jet.

Detailed Description of the Preferred Embodiment Figure 1 illustrates the invention having thrust-jets 1, rotor 2, power take-off 3, rotor support 4, fluid supply 5, and fluid reservoir 6. Thrust-jets 1 extend from rotor 2 and impart rotational thrust to rotor 2 by ejecting a stream of fluid 7 in a direction indicated by arrow "A" in Figure 4, approximate-ly tangential to the arc described by the rotor's rotational motion. Fluid 7 (such as water) is supplied to the fluid supply line 5 through the open bottom 22 in order to exclude entrained air bubbles. Rotor 2 has rigid upper axle 8 and rigid lower intake pipe 9 attached to the rotor 2 along the rotor's axis of rotation 10. Rotor 2 is suspended over fluid reservoir 6 on axle 8 by rotor support 4. Fluid supply line 5 is supported in fluid reservoir 6 centrally aligned beneath rotor 2. Intake pipe 9 is hollow and communicates with fluid supply line 5 to channel fluid 11 from fluid supply line 5 to rotor 2. Fluid 7 is channelled from intake pipe 9 through rotor 2 in one of the manners further illustrated below. Intake pipe 9 is seated in seals 12 mounted in the upper end of supply line 5, where such seals may be of a conventional ceramic, composite or carbon-graphite wear-ring ` type. Axle 8 extends through low friction bearings (not shown) in upper bearing housing 13 on rotor support 4 and connects to power take-off 3. Axle 8 is solid or sealed from rotor 2 and intake pipe 9 such that fluid 7 in rotor 2 and intake pipe 9 is 2~2~
prevented from entering axle 8. Mechanical power is transmitted from power take-off 3 by attaching suitable gears, pulleys or the like.

Fluid supply line 15 is supplied with fluid under pressure from an outside source through fluid supply valve 16 and extends into fluid supply line 5 through leak proof connections or weldment and its inward end is affixed centrally below and in line with intake pipe 9. Retractable jet-siphon assembly 18 telescopes onto the inward vertical end of fluid supply line 15 and is provided with one or more 0 ring seals along its interior diameter to provide a sliding (telescoping) fluid-tight joint.
Unless forced upward by internal pressure from fluid supply line, jet-siphon assembly is held in the retracted position shown in Figure 1 by retraction springs 19 attached to fluid supply line 5. Ventilator pipe 17 communicates with fluid supply line 5 at its lower end and with open air at its upper end 20. Ventilator 17 is provided so that ambient air may be introduced into fluid supply line 5 to interrupt the supply of fluid 7 into rotor 2 from reservoir 6. While retractable jet-siphon assembly 18 is retracted under the spring force of retraction springs 19, introduction of ambient air from ventilator 17 into fluid supply line 5 will, if rotor 2 is spinning, cause rotor 2 to decelerate as air is drawn up through intake pipe 9 and into rotor 2 to replace fluid 7 exhausting through jets 1.

Ventilator 17 has air intake 20 and communicates with fluid supply line 5 near its lower end but above butterEly valve 21 which is positioned in supply line extension 1~ near opening 22 and may be rotated from an open position (shown in solid lines), in which position fluid from reservoir 6 is free to enter fluid supply line 5 through opening 22; to a closed position (shown in broken lines), in which position fluid from reservoir 6 is prevented from entering supply line 5 and ambient air from ; 35 ventilator 17 may be entrained into fluid supply line 5. Ambient air from ventilator 17 is entrained into fluid supply line 5 if static fluid pressure in fluid supply line 5 is lower than the 2~2~

ambient atm~spheric static pressure. A lower than ambient pressure in supply line 5 will exist if valve 21 is closed and rotor 2 is spinning.

As illustrated in Figure 2, retractable jet-siphon assembly is mounted on the end of supply line 15 supported concentrically within fluid supply line 5. Retractable jet-siphon assembly 18 has restricted inner nozzle 50 with outer venturi 51 affixed in cooperative relationship to it, forming a jet-siphon. Nozzle 50 has a diameter significantly less than the diameter of pipe 15. As the force acting to advance retractable jet-siphon assembly 18 increases due to increased fluid pressure from fluid supply line 15 acting on the interior of the retract-able assembly 18, retractable jet-siphon assembly 18 advances toward opening 23 in rotor intake pipe 9. Conversely, as fluid static pressure from fluid supply line 15 is decreased, assembly 18 retracts away from rotor intake pipe 9 under the force of retraction springs 19.

When jet-siphon assembly 18 is fully advanced, upper side of venturi ring 24 seals against the underside of seal 12 so that jet-siphon 18 injects fluid from fluid supply 7, mixed with and assisted by fluid under high pressure from fluid supply line 15, directly into intake pipe opening 23. By these means, a high pressure, low volume fluid supply from fluid supply line 15 is used to provide a higher volume of fluid to the rotor at somewhat lower pressure. Conversely, as fluid static pressure from fluid supply line 15 is decreased, nozzle 18 retracts away from lower rotor axle 9 under the foxce of retraction springs 19.
Retraction springs 19 are secured to supply line 5.

Figure 3 illustrates a second embodiment of the inven-tion. A one-way valve 25 is provided in the supply line 5 instead of retractable jet-siphon assembly 18. One-way valve 25 is biased from a closed position, in which position fluid from reservoir 6 is prevented from entering through opening 22, to an open position (shown in bro~en lines) in which fluid from fluid 2~

reservoir 6 flows into supply line 5 when static fluid pressure in supply line 5 is lower than ambient atmospheric static pressure. Static fluid pressure in supply line 5 is lower than ambient atmospheric static pressure when fluid supply valva 16 is closed and rotor 2 is spinning. Rotor 2 in this embodiment is supplied with fluid under pressure from an outside source by pressurizing fluid in supply line 5 from fluid supply line 15.
This pressurization closes one-way valve 25 and forces pressur-ized fluid from supply line 15 into rotor 2 and out thrust-jets 1 as fluid 7. In this embodiment fluid supply line 15 enters supply line 5 between intake pipe 9 and one-way valve 25.

As illustrated in Figures 1, 2 and 3, support frame 26 depends from rotor support 7 into fluid reservoir 6. Support frame 26 and bearing housing 13 support fluid deflectors 27 which deflect and diffuse fluid streams from jets 1 into reservoir 6.
Rotor housing 26 extends below rotor 2 into reservoir 6 to rigidly support fluid supply line 5. Coil spring 28 is supported at its lower end in the inner surface of supply line 5 and resiliently supports seals 12 within supply line 5. Reservoir 6 has overflow port 29.

It will be understood that while the above specific embodiments have been described, other methods of commencing the spinning of the rotor may be used without altering the basic principles of the invention.

Figures ~, 5 and 6 illustrate three embodiments of rotor 2. Rotor 2 in Figure 4 has straight or curved radially oriented guide partitions 30 within rotor casing 31 and extending from the fluid entrance in hub 32 to, or almost to, the inner rim 33 of rotor 2. On initial acceleration of rotor 2 from rest, pressurized fluid from intake pipe 9a and/or intake pipe 9 (not shown) is forced away from rotor hub 32 between partitions 30 to rotor rim 33, where the pressurized fluid is forced from jets 1 to accelerate rotor 2. Centrifugal force due to rotational motion of rotor 2 further pressurizes fluid constrained within L
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rotor casing 31 against rotor rim 33. Fluid from open inner end of intake pipe(s) 9 and/or 9a enters casing 31 and is accelerated rotatively as it is impelled/ by centrifugal force, radially outward from rotor hub 32, between partitions 30 to rotor rim 33 where it continuously replaces the fluid forced from jets 1 or from governor pressure release valves 34. The rotational velocity of the fluid is great compared to its radial velocity in order to ensure maximum pressure build-up due to centrifugal force, and minimum turbulence and static pressure head loss due to fluid friction within the rotor 2. Governor pressure release valves 34 regulate rotational speed of rotor 2 by releasing fluid radially from rotor 2 when centrifugal force, plus static fluid pressure head within rotor 2 exceeds a predetermined level exerted against governor pressure release valves 34. Release of fluid from governor pressure release valves 34 limits rotational speed of rotor 2 by increasing the flow of fluid through rotor 2 and thereby increasing the amount of power used to rotationally accelerate fluid without increasing the tangential jet thrust imposed on rotor 2.
Figure 5 illustrates an embodiment of rotor 2 where hollow spokes 35 and hollow tubular rim 36 are substituted for radial partitions 30 and rotor casing 31.

Figure 6 illustrates an embodiment of rotor 2 where hollow arms 37 are substituted for radial partitions 30 and rotor casing 31.

In embodiments illustrated in Figures 4, 5 and 6 the combined cross-sectional areas of intake pipe or pipes 9 and/or 9a, and the combined cross-sectional areas of spokes 35 and of arms 37, are at least 8 times greater than the combined cross-sectional areas of the nozzle openings in jets 1 in order to reduce pressure losses within rotor 2.
Figure 7 illustrates an embodiment in greater detail of spoke 37 incorporating a jet-siphon air purging mechanism 38 \

for machines using liquid operating fluid 7. Air line 39 connects the central interior cavity of rotor hub 32 to intake area 44 of air purging mechanism 38. When rotor 2 is sp.inning, a small amount of air inevitably entrained in fluid 7 is centrifuged out of fluid 7 and would otherwise collect in the centre of rotor 2, thus reducing centrifugally induced pressure build-up in the working fluid 7 within rotor 2. Jet-siphon purging mechanism 38 uses a small amount of fluid 7 under high pressure from within rotor 2 and conducts it via passage 46 to high-pressure siphon-jet 48. The fluid 7 is ejected at high velocity through venturi area 47 and draws air along connecting passages 45, through intake area 44 and through air line 39, from the hub 32 of rotor 2. The air, entrained with working fluid 7 in venturi 47, is exhausted from purging mechanism outlet 40, either radially or tangentially-assisting jet thrust from thrust-jets 1.

In a further embodiment rotor 2 may have air purging means (not shown) consisting of a small diameter tube centrally affixed within feed pipe 5 and extending upward through the centre of intake pipe 9 into the central interior cavity of rotor 2; the lower end of said tube extending through fluid-tight connectors through the wall of feed pipe 5 and through the outer wall of reservoir 6 to communicate with outside air or with the inta~e of an external vacuum pump, whereby air may be purged from the central cavity of rotor 2 by incoming fluid pressure into rotor 2 forcing air out of the small diameter purge tube, or air may be drawn out said purge tube by vacuum from the said vacuum pump and expelled to outside air.
Figure 7 also illustrates in cross section, governor pressure release valve assembly 38. As rotational speed of rotor 2 increases beyond a pre-determined limit, increasing centrifugal force and fluid pressure within arm 37 of rotor 2 presses outward against valve stem 42 and valve head 61. Valve stem 42 with retainer 63, is forced against coil spring 43, allowing valve head 61 to move away from valve seat 49 in valve body 62.

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Pressurized fluid 7 from within arm 37 of rotor 2 is thus allowed to escape through passages 60 in valve body 62 and thence out between valve seat 49 and valve head 61; then being exhausted radially from arm 37 of rotor 2. As previously stated, the 5releasa of fluid from governor pressure release valve 34 increases the outward radial movement of fluid 7 within arm 37 of rotor 2 without a corresponding increase in tangential jet thrust; and more fluid per unit of time is caused to be acceler-ated from its curvilinear velocity at the hub 32 (Figures 4, 5 10and 6) of rotor 2 to its curvilinear velocity at the outer end of arm 37 of rotor 2, as it moves radially outward within arm 37 of rotor 2, than that which is ejected to produce jet thrust at the jets 1. The increased fluid-acceleration demand imposes an increased drag force upon the rotational movement of rotor 2 15without a corresponding increase in propulsive force from the jets 1, thus preventing rotor 2 from overspeeding. Conversely, when transmission of power from power take-off 3 (Figure 1) holds the rotational speed of rotor 2 within the predetermined limit, valve spring 43, reacting against valve spring retainer 63 on 20valve stem 42, pulls valve head 61 firmly against valve seat 49;
thus preventing the escape of fluid 7 through governor pressure release valve 34 and allowing rotor 2 to operate at full efficiency. Figure 7 also illustrates a correctly configured thrust-jet 1 having very short, constant diameter jet tube and 25smoothly rounded approach 41 so as to produce fluid stream 7 from jets 1 with low pressure loss in the nozzle and maximum velocity.

In a further embodiment, rotor 2 may have governor jets (not shown). Whereas jets 1 provide an accelerating thrust to 30rotor 2, governor nozzles are directed in a direction generally opposi~e that of jets 1 to provide a decelerating thrust to rotor 2. Governor jets are activated when static fluid pressure in rotor 2 exceeds a predetermined level exerted on governor jets.
The governor jets may be interspersed between thrust-jets 1.
Also in a further embodiment (not shown), rotor 2 may have governor means to limit rotational speed of rotor 2 by ..

deployment of deflectors against the stream of fluid 7 issuing from jets 1 or by rotation of jets l in their mountings, thus to modify or change the direction of thrust from jets 1 reacting against rotor 2; said means being actuated manually or automati-cally by appropriate linkages in manners already well known tothose skilled in the art.

Referring to Figures l and 2, in operation, rotor 2 is accelerated from rest by opening fluid supply valve 16 and advancing retractable jet-siphon assembly 18 so that upper side of venturi ring 24 seals against the underside of seal 12 which communicates with intake pipe 9 of rotor 2. Pressurized fluid is injected into rotor 2 via intake pipe 9. Rotor 2 fills with pressurized fluid and pressurized fluid 7 is forced from jets 1 and the reaction thrust thus originating at jets 1 and acting tangentially to the arc described by the rotation of rotor 2, accelerates rotor 2 from rest. As the rotational speed of rotor 2 increases, centrifugal force acting on fluid 7 predominately constrained within rotor 2, further increases the pressure and the thrust at the jets 1, additively to that which results from external input pressure alone into intake pipe 9 of rotor 2.
Centrifugal force increases as the square of the rotational speed and thus the pressure increase resulting from the centrifugal force is in approximately the same ratio but slightly reduced by fluid friction. Once rotor 2 has been accelerated to its pre-determined operating speed, mechanical power may be transmitted from take~off 3 in accordance with the design capacity of the apparatus.

Becausethecentrifugal-force-inducedpressureincrease within rotor 2 varies approximately as the square of the rotational speed of rotor 2, the tangential jet thrust from thrust-jets l on rotor 2 increases in the same proportion; the latter (the thrust) being exactly dependent upon the former (the pressure which feeds the jets). In further relationship, because the overall power output of the apparatus is the product of the aggregate jet thrust reaction multiplied by the velocit~

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(curvilinear in this case) of the point of origin of that thrust reaction, the said velocity varying directly as the rotational speed of rotor 2; the graph of the power output plotted in relationship to rotational speed, is a concave ascending curve quite unlike that of conventional power conversion apparatus.
It is therefore necessary to operate the apparatus at very close to its designed rotational speed if maximum power output is to be obtained because torque and power decrease very rapidly as rotational speed of rotor 2 decreases. Conversely, for the same reasons as stated above, it is also necessary that the rotational speed of rotor 2 of the apparatus be automatically; and quickly governed in order to prevent rotor 2 from overspeeding and quickly destroying itself.

As will be apparent to those skilled in the art in the light of the foregoing disclosure, many alternations and modifications are possible in the practice of this invention without departing from the spirit or scope thereof. Accordingly, the scope of the invention is to be construed in accordance with the substance defined by the following claims.

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Claims (3)

1. discrete, straight or curved, radially oriented passages extending from said hollow axis to, or nearly to, the internal peripheral diameter of said hollow rotor thereby to enforce rotation of fluid introduced into said hollow axis of said hollow rotor together with said rotor while freely conducting said fluid from said hollow axis to said internal peripheral diameter of said hollow rotor;

2. a spaced array of tangentially directed exit orifices or "jets", externally affixed at or near the peripheral diameter of said rotor and communicating with said hollow interior of said rotor, the aggregate cross-sectional area of said radially oriented passages to the aggregate cross sectional area of said exit orifices being of a ratio greater than 8:1;

3. a source of fluid communication with said hollow axis;
(b) applying an external source of power to said rotor to rotate said rotor on said axis, and thereby causing said fluid to be expelled from said orifices thereby generating a tangential rotational reaction thrust relative to said rotor, said thrust being increased by the increase in fluid pressure within said rotor, said increase in pressure being caused by centrifugal force acting upon said fluid coincidental to the enforced rotation of said fluid together with said rotor and its constrainment within said peripheral diameter of said rotor;

(c) removing said external power source once said rotor reaches sufficient rotational velocity in accordance with designed operating speed;

(d) continuing to supply fluid to said hollow axis of said rotor, thereby to utilize the high efficiency of power conversion above described.

(29). An apparatus for conversion of input power into mechan-ical output power, comprising:

a hollow rotating rotor having an input port along an axis of rotation of said rotor and a periphery at the outer edges of said rotor distal from said port;

support means for rotatably supporting said rotor;

first filling means for initial filling of said rotor with a fluid;

second filling means for continual filling of said rotor with said fluid through said at least one port;

initial accelerating means for initially rotationally accelerating said filled rotor about an axis of rotation of said rotor as said rotor is being filled by said first and second filling means;

channelling means for radial channelling of said fluid from said port to said periphery;

jet means adapted to expel said fluid from said periphery in a direction approximately tangential to an arc described by said rotating of said periphery;

purging means for purging of gaseous phase fluid from said fluid in said rotor;

governing means for governing said acceleration of said rotor; and, power extraction means for extracting mechanical power from said rotation of said rotor, wherein said power conversion apparatus is characterized by:

a sustainable rotational vectored non-diminishing thrust resultant of said vectored expulsion of said fluid acting on said rotor and said fluid within said rotor;

a high optimum operational rate of said rotation of said rotor;

an unrestricted movement of said fluid through said at least one port and along said channelling means;

a constrainment of said fluid by said periphery within said rotor, whereby centrifugal force due to said rotation causes an increase in pressure acting on said fluid at said periphery within said rotor;

a low radial velocity of said fluid along said channelling means towards said periphery;

(30). The apparatus of claim 29, wherein said expulsion of said fluid from said jet is further characterized by a low volume, high pressure stream of said fluid, said fluid being pressurized by said centrifugal force.