WO2015003205A1

WO2015003205A1 - Self powering energy generation by the harnessing of centrifugal force

Info

Publication number: WO2015003205A1
Application number: PCT/AU2014/000694
Authority: WO
Inventors: Geoffrey William Good Leviny
Original assignee: Universal Engines Pty Ltd
Priority date: 2013-07-07
Filing date: 2014-07-07
Publication date: 2015-01-15
Also published as: AU2014289958A1

Abstract

This invention relates to an energy generation method and apparatus. The apparatus comprising: an output shaft rotatably attached to opposite sides of a housing and defining a first axis of orbit; an output gear fixed for rotation to said output shaft; an input sprocket rotatably mounted on said output shaft; a pair of radial arms rotatably mounted on said output shaft; at least one idler gear; at least two frame gear assemblies having an axis of rotation, said frame gear assemblies being mounted for orbital movement by chains around said output gear. Wherein a first force is applied by a mechanical transfer of an input power from an input gear and frame gear assemblies to the output gear through a mechanical sequence of chains and gears, the transfer of energy from the input gear to the output gear has a coupling which is held by and dependent on, centrifugal force acting on weights attached to the weight gears, which by being revolved synchronously are pulled outwards on a radial line. A second force is derived when the weight movement away from the radial line causes the weight gears on which they are mounted by bearings to be pulled by centrifugal force and so spin in response to the torque produced and transmit this as added power via the idler gears to the central output gear, such that the two forces are applied to the output gear. By direct coupling from the output to the input by a variable power regulator an input to the apparatus is maintained.

Description

SELF POWERING ENERGY GENERATIO BY THE HARNESSING OF

CENTRIFUGAL FORCE

TECHNICAL FIELD

This invention generally relates to an energy generation method and apparatus and in particular to a self-powering energy generation method and apparatus which controls the use of centrifugal force for the generation of energy in a controlled manner.

The present invention also relates to a method and apparatus for harnessing centrifugal force into a cranking force to apply energy to a central gear when a revolving gear is manipulated to maintain the centre of gravity/mass within that gear synchronously off centre to one side of that gear regardless of any spinning of that gear about its self.

Furthermore, the present invention also relates to an energy generation method and in particular to a power regulator for recycling some of the energy harnessed so as to provide a self-powering and/or a continuous supply of power for external applications.

BACKGROUND ART

It is true that some inventions can involve ne discoveries. What is the mechanism causing gravitational force is not understood, but it is undeniable that it exists, so it is accepted. In the case of centrifugal force it is theorized that it is simply an apparent reaction to centripetal force, not a force in its own right. This is not proven. Centrifugal force is simply dismissed because the cause is not known or understood, while an explanation is postulated.

The accepted postulation is that centripetal force is applied at right angles to the rotating body and so applies a constant change In direction to the body without retarding it, and so does not retard angular momentum which is known to be a constant.

There is a flaw in this hypothesis. It is that a change in direction can only result from an external force. In the case of a centripetal inward force/pull applied at right angles it can only be caused by an inward movement, whic must require a shortening of the tether, which does not happen. If one considers a mechanical system where both the central pivot and the tethered body move at the same velocity in the sam direction with no shortening of the tether then there is no centripetal force and therefore no change in direction. If the central pivot point is stopped, the tethered body will start to change direction to a circular orbit and express centripetal force.

What has happened is that the orbiting body is attempting to advance ahead of the central pivot. In doing this it attempts to exceed the length of the tether and in doing this is pulied constantly slightly backwards since the tether is a constant length. This is an external force, and this must retard angular momentum. Since angular momentum is a constant without retardation, there must be an externa! force being applied in the opposite direction to the centripetal force to offset that centripetal force. Such a force is called centrifugal force however it is caused.

Conversely, if the tether is broken or the central pivot again moves in a straight line at right angles to the tethered body then there is no centripetal force or induced centrifugal force and no change in direction and the tethered body simply resumes its straight line inertia.

If an orbiting body such as the moon was to be stationary within the principle influence of the earth's gravity, it would be pulled directly toward the earth at an accelerating velocity until it crashed into the earth, in the natural world the moon does not crash into the earth because it is orbiting at a constant velocity that produces centrifugal force at its radius from the eart that balances the earth's gravity.

Note that gravity is a force, it conforms to Newtonian physics since it causes acceleration, accordingly for centrifugal force to balance gravity it must also be a force. While this is not proof of the existence or absence of the nature of centrifugal force, it remains clear that gravity has been resisted, and if this resistance is simply called centripetal force or the reactionary term centrifugal force, there is tension between the earth and moon and it is this that has been harnessed in the present invention.

Gravity must be an ever renewing force for any mass to remain drawn to the earth without any loss of energy as evidenced by no loss of mass. A mass which is spinning around a fixed point at the end of a tether in a frictioniess state, such as in space, will maintain angular momentum without added input. Regardless, it is undeniable that rotating weights spinning around a centra! point exert a continuous outward force as can be seen in the operation of a centrifugal clutch, where brake pads are spun, and so forced out against the inner face of a drum with a force that creates friction to lock the inner rotation to the outer drum. There are many other examples of the use of centrifugal force such as speed regulating governors, the pivoted lawn mower blades and the centrifuge. Centrifugal force represents the effects of inertia that arise in connection with rotation and which are experienced as an outward force away from the centre of rotation. A number of attempts have been made to harness and utilize centrifugal force as a useful energy source_* Examples of apparatus using this principle are disclosed in JP57137741 A2, JP08256470A2, US20040234396A1 , JP10153163A2 and JP10026074A2. As far as the applicant is aware none of the apparatus disclosed in the above documents have been successfully implemented.

For example US20040234396 describes a mode for generating electricity. Following a connection of a controllable electric driving motor and it's switching on of a disc rotor which generates a centrifugal force at the rim of the rotor circumference. The application of this force causing centrifugal acceleration of a liquid and subsequently achieves a rise in liquid pressure. which are quadratic in respect to circumferential velocity measured at the other rim of the disc rotor. The centrifugal force and energy potential are used for driving a hydraulic motor, in order to rotate a driving shaft; and transfer rotating motion to a generator that serves for generating electricity. As far as the applicant is aware this apparatus has not been successfully implemented to produce electricity.

Clearly it would be advantageous of the present invention to provide a contrivance which overcomes or at least ameliorates some of the disadvantages set forth above. Clearly it would be advantageous for the present invention to provide a contrivance which can produce energy without the need for fuel and without pollution or COs emissions.

SUMMARY OF THE INVENTION

Given the properties of mass exhibited by a bod orbiting/spinning around a fixed point expresses angular momentum and centrifugal force, the function of the apparatus is to convey an input power to the output through the orbiting/spinning a body so as to maintain the angular momentum and convert centrifugal force into a cranking force to generate energy from the incidental centrifugaf force. All these forces are known to science and as with solar energy are unlimited. Every serious engineering book gives the formula for centrifugal force as mass times velocity squared divided by the radius, or a derivation of this.

The apparatus and method of energy generation is based on the transfer of centrifugal force into a cranking force to apply energy to a gear. The present invention is implemented by maintaining an added off center weight of a gear to one side of that gear whilst in orbit regardless of any spin it may undergo, suc that the offset mass of the gear orbits in a manner synchronous to the center of orbit while the actual gear may be freely spinning in orbit.

The present invention derives energy or energy is delivered in two ways. Firstly, a first force is a mechanical transfer of an input power from an input gear to an output gear through a mechanical sequence of chains and gears. The transfer is not a completely interconnected sequence. It has one coupling which is held by and dependent on, centrifugal force acting on offset weights attached to gears, which by being revolved synchronously are pulled outwards on the radial line. When the conveyance of the input force is increased the weights are pulled increasingly away from the radiating centrifugal line. A second force is produced b this weight movement away from the radial line causes the gears on which they are mounted by bearings to be pulled by centrifugal force and so spin in response to the torque produced and transmit this as added power via idler gears to the central output gear. This is the second force.

Since the first force is a direct product of the input force and the second force is a consequential force resultant from the offset (advance) of the weights, all the output of the of the second force less frictional loss, is gain, and so can be used to power external applications. Since both forces are governed by the input meeting resistance against rotation of the weight gears by centrifugal force, both the first and second forces apply an equal output force regardless of their revolution rates. Thus input power is amplified to double less friction at the output gear.

In accordance with a first aspect, the present invention provides an energy generation apparatus comprising: a duel function input shaft and output shaft rotatably attached to opposite sides of a housing and defining a first axis of orbit; an output gear fixed for rotation to said output shaft; an input sprocket rotatably mounted on said output shaft; a pair of radial arms rotatably mounted on said output shaft; at least one idler gear; at least two frame gear assemblies having an axis of rotation, said frame gear assemblies being mounted for orbital movement around said output gear in response to an input on the input sprocket and conveyed to the frame gear assembly by chains, and including means to convey said orbital movement to the output gear by the idler gears, each said frame gear assembly comprising: a frame gear; a shaft; a drive sprocket a drive gear and at least two weight gears; means for positioning and maintaining the effective centre of mass of said frame gears at a position or positions synchronously off-centre relative to the centre of said frame gears to cause rotation of said frame gears about their axis of rotation in response to a centrifugal force caused as a consequence of the orbital movement of said frame gear assemblies; and means of coupling said frame gears to said output gear via said idler gear, whereby the power of both orbital motion of said frame gear around said output gear and rotational/spin of said frame gear around its own axis is transmitted to said output shaft each with equal power as applied at the input sprocket less friction and wherein said spin of the output gear is conveyed via the output shaft to return some of the output energy to drive the input by direct or variable mechanical drive, or by any other means such as hydraulic or electric drive systems, so as to maintain drive to the system.

Preferably, the apparatus may include at least one pair of frame gear assemblies, respective frame gear assemblies of said pair being arranged symmetrically on opposite radial sides of the output gear. Each said frame gear assembly may comprise a frame gear and mass adjusting means carried by said frame gear for adjusting the centre of mass of the f ame gear assembly.

Preferably the apparatus may further include a f ame gear shaft for each frame gear assembly and mounted at a position spaced radially from and extending parallel to the output shaft, said frame gear assembly being supported to the frame gear shaft for free rotation there around.

Preferably, the mass adjusting means may comprise weight gears, said weight gears being movably mounted on the frame gear to enable adjustment of the effective centre of mass of the frame gear assembly. The weight gears may comprise a pair or more of weight gears arranged symmetrically on opposite radial sides of th axis of rotation of the fram gear. Each weight gear may be supported on the frame gear for rotation about an axis extending parallel to the axis of the rotation of the frame gear. The centre of mass of each weight gear may be offset relative to its axis of rotation and maintains that offset synchronously such that offset is maintained even when the frame gear rotates about its own axis.

Preferably, th weight gears may b arranged such that when each weight or centre of mass of each weight gear is concurrently radially outer most and wherein the weight gears on frame gears on the opposite sides of the output shaft are arranged symmetrically relative to each other.

Preferably, said weight gears may be in mesh with a common drive gear coaxial with the frame gear through which rotation by a drive chain can be transmitted to the weight gears from the input sprocket, said drive gear being mounted to the frame gear shaft for rotation therewith.

Preferably, the frame gear shafts may be supported by spaced radial arms mounted for rotation relative to the output shaft, the radial arms extending symmetrically on opposite radial sides of the output shaft.

Preferably, each said frame gear assembly may be coupled to the output gear through the idler gears.

Preferably, said frame gear shafts may be adapted to receive an input from said input sprocket to rotatably drive the drive gears against the weight gears with said weights which are synchronously held outwards by centrifugal force. The orbital motion may be applied to said frame gear assemblies as torque. The torque may be resisted as spin by the coupling to the output gear causing the drive chains to act as a solid component. The solid behaviour of the chains may be applied to the frame gear assembly as rotational torque about the output shaft for complete conveyance of all input from the input sprocket iess any friction through the meshing of the drive gear to the weight gears to the frame gears to the idler gears to the output gear to form a first force applied to the output gear,

Preferably, when the frame gear assembly is rotating about the output shaft ail parts of the frame gear may express centrifugal force as a by-product which increases as the radial arms rotate faster. Any increase in revolution rate of the radial arms may increase both rotational force and centrifugal force applied to the weights by a factor of four proportionally in accordance with E= ½ mv² and F= mv²/R and will increase the power range that can be amplified.

Preferably, said rotation transmitted to the weight gears may cause the weights thereon mounted to move away from the most outward line causing said mass adjusting in response to any differential between the input and output power caused by friction or output load. Averag movement of the weights being so caused, and being subjected to said centrifugal force, may apply the same torque as that force that caused it in the conveyance of the first force. The torque may be applied to the frame gear in response to the centrifugal force applying to it in a radial line from the output shaft. The torque less any friction from the gears may be applied through the idler gears in a reverse direction to the output gear to form a second force applied to the output gear.

Preferably, both the first force and the second force may be governed by the input o the input sprocket meeting a resistance against rotation of the weight gears which are held by centrifugal force being a by-product of angular momentum, both the first and second forces apply equal output force regardless of their revolution rates.

Preferably, all gearing may be configured to suit the method of maintaining the input power when diverting any of the output to the input. The gearing may be a one to one gearing if all power is to be returned at a one to one revolution rate which requires the rotation of either the frame gears or the radial arms singularly, or any combined rotation of the frame gears or the radial arms to match the input rotation rate that these gears cause at the output, and with both applying the same torque the output will equal twice the input power less any loss due to f riction. Preferably, the first force ma be applied with any sprocket sizing when it alone is rotating requiring only the gearing of the second force to be configured one to one such that a combined one to one gearing is maintained when the frame gears rotate about their own axis. Calculating the one to one gearing of the second force may be factored in that throughout each rotation of the radial arms, the weight gears maintain their orientation, and in doing so revolve around the drive gear, such that the driv gears must turn the number of teeth as there are on the weight gears in addition to the one full turn of the drive gear required to match the rotation of one frame gear rotation.

Preferably, the first force may be a direct product of the input force and is fuliy conveyed to the output, and the second force is a consequential force resultant from centrifugal: force acting on the advance of the weights, all the output of the second force less frictional loss, is gain, and so can be used to power an external application.

Preferably, power may be increased by incorporating multiple frame gears, weight gears or the use of modified weight arms whereby the weight gears can be mounted on shafts extending through the frame gears and mounted on bearings such that the non-gear drive side has a weight arm attached, such that with the weights balanced on either side, a more even load would be applied to the frame gears while increasing the mass of the weights and so the powe range that can be amplified.

Preferably, multiple force or energy amplifying apparatuses may be powered in series for multiple amplification of power for returning power for self- powering.

In accordance with a further aspect, the present invention provides an apparatus for harnessing centrifugal force into a cranking force to apply energy to a shaft when the centre of gravity/mass within a gear is manipulated to rotate continuously off centre to one side of that gear around the centre of another gear, the apparatus comprising: a duel function input shaft and output shaft rotatably attached to opposite sides of a housing and defining an axis of orbit; an output gear fixed for rotation with said output shaft; an input sprocket rotatably mounted on said output shaft; at least two frame gear assemblies, each said frame gear assembly comprising a frame gear and an idler gear, wherein said at least two frame gear assemblies having an axis of rotation, said frame gear assemblies being mounted for orbital movement around said output gear in response to an input from said input sprocket, and means to convey said orbital movement to the output gear; means for positioning and maintaining the effective centre of mass of said frame gear assemblies at a position or positions synchronously off-centre relative to the centre of said frame gears to cause rotation of said frame gear assemblies about their axis of rotation in response to a centrifugal force caused as a consequence of the orbital movement of said frame gear assemblies; and means of coupling said frame gears to said output gear via said idler gear whereby motion of said frame gear is transmitted to said output shaft equal to said input of the frame gear assemblies around said output gear.

Preferably, energy at the output shaft may be transmitted to the input sprocket to recycle energy so as to provide power for self-powering the apparatus and providing a continuous supply of power for external applications. The self-powering apparatus may be a variable power hydraulically controlled returning apparatus or a power regulator for maintaining, increasing, reducing or stopping the power transmitted from the output to the input, said power regulator being incorporated within a multiple chain sprocket. A hydraulic cylinder may be created on an inner side of said multiple chain sprocket to form the housing of the variable power returning apparatus. The hydraulic cylinder further comprising two pistons located on the inner side of the multiple chain sprocket. Each piston may have at least two slots equally spaced around the inside and outside of both pistons. The inside slots may be horizontal and the outside slots are helical. Preferably, the threaded holes may be located around the multiple chain sprocket to align with the said helical slots and to allow the insertion of screw pins. Each set of screw pins may be positioned so as to locate into the helical slots in the outside of each said piston.

Preferably, said pistons may be tubular such that they are located to neatly fit around the output shaft. Hydraulic seals may be located on the inner facing ends of each said piston and set back to allow a space between the two pistons when they are together, so as to facilitate controlled separation by maintaining a space for hydraulic oil. Each set of pistons may be engaged by a set of locating pins which are inserted equally around, or on opposite sides of the output shaft such that half of the locating pins are spaced to engage with each piston. The engaging pins may be fitted into said longitudinal slots on the inside of said pistons, by sliding said pistons outward after the pins are inserted into the output shaft, such that the pistons are then free to slide horizontally on the output shaft as far as the seals will permit.

Preferably, said output shaft may have an axially extending hole drilled through the middle of the output shaft and extending from one end on the side of multiple chain sprocket to an outlet hole located in line with the mid line of the final drive sprocket A cylinder of the multiple chain sprocket may be slid over the pistons to accommodate the pistons centrally, when the pistons are together at the point of the oil outlet hole so as to align with the mid line of the final drive sprocket. Th helical slots in the outside of the two pistons may be cut at opposite angles to each other and are fitted on the output shaft such that the slots form an arrow head in the direction of rotation of the output shaft. The slots may be cut at any suitable helical angle so as to provide optimal rotation of the weights to near ninety degrees when the pistons are hydraulically separated by an hydraulic pump to their maximum extent.

Preferably, the multiple chain sprocket may be coupled to the final drive sprocket of the apparatus by the drive chains in such a manner that when the pistons are together at the outlet oil hole, each of the weights on the weight gears are set outwards on the radial line or slightly backwards from it. On the drilled end of said output shaft may be fitted a rotary oil union wit an hydraulic pump connected via a hydraulic hose to the rotary oil union. The hydraulic fluid pressure may b provided between the pistons to cause the pistons to move apart such that movement of the pistons apart will screw the cooperating pins along the slots causing a differential rotational coupling between the input sprocket and the output shaft.

Preferably, said rotational differential coupling may transfer downstream to force and hold the weights off-centre. The weight offset may cause torque and rotation of the frame gear assembly to be applied to the output. The output may be additionally returned to the input or made avaiiable to power or drive other applications. In accordance with a stili further aspect, the present invention provides an energy generation apparatus comprising: a housing frame and an output shaft, th output shaft is rotatabiy mounted on opposite sides of the housing frame, the output shaft defining an axis of orbit; at least two pair of identical parallel radial arms mounted on the output shaft by a pair of bearings; an output gear fixed to the output shaft and located between the pair of radial arms; an idler gear meshed with said output gear and located within each pair of radial arms, the idler gear rotating on an axle between the pair of radial arms; a frame gear assembly comprising a frame gear meshed with the idler gear, the frame gear is mounted by bearings and located between the pair of radial arms, the frame gear located on a frame gear axle, the frame gear axle being located between and towards the outer ends of the radial arms, each frame gear axle is mounted b bearings to the radial arms with one end of the frame gear axle extending through the radial arm; a final drive sprocket fixed to the frame gear axle for receiving input from a looped drive chain from a multiple drive sprocket; the multiple drive sprocket is eoaxially centered on bearings on the output shaft, the multiple drive sprocket being located outside the radial arms and comprising parallel sprockets of the same size for coupling to each final drive sprocket; a final drive gear located adjacent the frame gear and fixed to the frame gear axle; a set of two or more weight gears with a weight attached to one side and meshed with the final drive gear, the weight gears are free to rotate on shafts spaced evenl around each frame gear, and each weight gear is meshed with the final drive gear in such a manner that each set of weight gears have their weights in the same quadrant pointing away from the output shaft, the position of each set of weight gears is set interconnected by aligning one weight gear on every frame gear directly away from the output shaft such that all weights on all weight gears are aligned directly away from the output shaft before connecting the looped drive chains around the multiple drive sprocket and the finai drive sprocket; wherein a first force is applied by a mechanical transfer of an input power from an input gear and frame gear assemblies to the output gear through a mechanical sequence of chains and gears, the transfer of energy from the input gear to the output gear has a coupling which is held by and dependent on, centrifugal force acting on the weights attached to the weight gears, which b being revolved synchronously are pulled outwards on a radiai line, wherein the conveyance of the input force is increased as the weights are pulled increasingly away from the radiating centrifugal line; and a second force is derived when the weight movement away from the radial line causes the weight gears on which they are mounted by bearings to be pulled by centrifugal force and so spin in response to the torque produced and transmit this as added power via the idler gears to the central output gear, such that the two forces are applied to the output gear.

Preferably, each weight gear may have a weight which is identical in size and weight attached to one side of the weight gear.

Preferably, the first force may be a turning force applied to the input shaft and said frame gear assemblies, the turning force is resisted as spin by the coupling to the output gear causing the drive chains to act as a solid, the solid behaviour of the drive chains is applied to the frame gear assemblies as rotational torque about the output shaft for complet conveyance of all input motion less friction through the meshing of the drive gear to the weight gears to the frame gears to the idler gears to the output gear to form the first force applied to the output gear.

Preferably, the frame gear assembly may be rotating about the output shaft all parts of the frame gear will express centrifugal force as a by-product which increases as the radial arms rotate faster, any increase in the revolution rate of the radial arms increases both rotational force and centrifugal force applied to the weights by a factor of four proportionally in accordance with the formulas for kinetic energy of E= ½ mv² and the centripetal force F= mv²/R and will increase the power range that can be amplified.

Preferably, the rotation transmitted to the weight gears may cause the weights mounted to the weight gears to move away from the most outward line causing said mass adjusting in response to any differentiai between the input and output power caused by friction or output load. The average movement of the weights may be subjected to said centrifugal force, will apply the same torque as that force that caused it in the conveyance of the first force. The torque may be applied to the frame gear in response to the centrifugal force applying to it in a radial line from the output shaft. The torque, less any friction in the gears may be applied through the idler gears to the output gear to form a second force applied to the output gear.

Preferably, both the first force and the second force may be governed by the input meeting resistance against rotation of the weight gears which are held by centrifugal force, being a by-product of angular momentum, both the first and second forces may apply equal output force regardless of their revolution rates.

Preferably, the gearing of each gear is configured to suit the method of maintaining the input power when diverting any of the output to the input. The gearing of the gears may be a one to one gearing if all power is to be returned at a one to one revolution rate which requires th rotation of either the frame gears or the radial arms singularly, or any combined rotation of the frame gears and the radial arms to match the input rotation rate that these gears cause at the output, and with both applying the same torque, the output will equal twice the input power less any friction in the apparatus.

Preferably, when calculating the one to one gearing of the second force it may be factored in that throughout eac rotation of the radial arms, the weight gears maintain their orientation, and in doing so revolve around the drive gear, such that the drive gears must turn the number of teeth as there are on the weight gears in addition to the one full turn of the drive gear required to matc the rotation of one frame gear rotation.

Preferably, to achieve a on to one gearing each respective gear may contain the folio wing number of teeth: (a) weight gears with 46 teeth; (b) final drive gear with 30 teeth; (c) frame gear with 120 teeth; (d) output gear with 120 teeth; (e) final drive sprocket with 15 teeth; and (f) multiple chain sprocket with 38 teeth.

Preferably, the first force may be a direct product of the input force and is fully conveyed to the output, and the second force is a consequential force resultant from centrifugal force acting on the advance of the weights, all the output of the of the second force less any frictional loss in the apparatus, is gain, and so can be used to power an external application. Power may be increased by incorporating multiple frame gears, weight gears or the use of modified weight arms whereby the weight gears can be mounted on shafts extending through the frame gears and mounted on bearings such that the non- gear drive side has a weight arm attached, such that with the weights balanced a more even load would be applied to the frame gears while increasing the mass of the weights and so the powe range that can be amplified.

Preferably, multiple force or energy amplifying apparatuses may be powered in series for multiple amplification of power for returning power for self- powering the apparatus.

An input power source is required to start up the system or apparatus. When running, some energy is required to be returned to the input to maintain the operation upstream of the output, and to compensate for fractional tosses.

The apparatus of the present invention has a number of applications inciuding as stand-alone power plants as single units or multiple units in any configuration including stacked on top of one another, side by side inciuding on common axle shafts, for any mechanical energy application inciuding water pumping and treatment, the generation of electricity, powering of vehicles, marine vessels, air craft, or any other mechanical devise including use in space or anywhere. The machine of the invention may be made to any size to suit any requirement for on-site and portable, to regional supply of energy. Regional power generation would eliminate the need and costs associated with long distance transportation of energy be it electricity or fossil fuel.

BRIEF DESCRIPTION OF THE DRAWINGS

For a better understanding of the present invention and to show more clearly how it may be carried into effect reference will now be made, by way of example, to the accompanying drawings in which:

Figure 1 is the diagram for assessing both, the effect of gearing on revolution on components and, the power amplification calculations;

Figure 2 illustrates the components of a controlled differential coupling used as a power return system in accordance with the present invention;

Figure 3 shows front and top schematic views of the powering system in accordance with the present invention;

Figure 4 illustrates how synchronous rotation of multiple weights maintains a constant offset despite any spin of gear on which they are mounted; Figure 5 illustrates a practical embodiment of apparatus according to the invention; and

Figures 6 to 16 are charted test results carried out on the apparatus of

FIG. 5.

DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring to Figures 1 to 4 an energy generation apparatus is described which has a duel function input shaft and output shaft 2 that is rotatably attached to opposite sides of a housing 1 by bearings 22 and define a first axis of orbit. An output gear 4 is fixed for rotation to said output shaft 2. An input sprocket 14 is also rotatably mounted on said input/output shaft 2. Pair of identical parallel radial arms 3 are mounted on the output shaft 2 by a pair of bearings 26. The radial arms 3 are rotatably mounted on said output shaft 2. At least one idler gear 8 is meshed with said output gear 4 and located within each pair of radial arms 3, the idler gear 8 rotating on an axle between the pair of radial arms 3.

Two frame gear assemblies having an axis of rotation and comprising a frame gear 5 meshed with the idler gear 8, the frame gear 5 is mounted by bearings 26 and located between the pair of radial arms 3. The frame gear 5 is located on a frame gear axie 6, the frame gear axie 6 being located between and towards the outer ends of the radial arms 3. Each frame gear axle 6 is mounted by bearings 24 to the radial arms 3 with one end of the frame gear axle 6 extending through the radial arm 3. The frame gear assemblies being mounted for orbital movement around said output gear 4 in response to an input on the input sprocket 14. A final drive sprocket 11 fixed to the frame gear axle 6 for receiving input from a looped drive chain 13 from a multiple drive sprocket 12. The multiple drive sprocket 12 is coaxially centered on bearings on the output shaft 2 and the multiple drive sprocket 12 being located outside the radial arms 3 and compristng parallel sprockets of the same size for coupling to each final drive sprocket 1 1.

The frame gear assemblies also include means to convey said orbital movement to the output gear 4 by the idler gears 8. Each frame gear assembly comprises a frame gear 5, a shaft or axle 6, a drive sprocket 11. a drive gear 7 and at least two weight gears 9. A final drive gear 7 is located adjacent the frame gear 5 and is fixed to the frame gear axle 6,

The apparatus also includes a means for positioning and maintaining the effective centre of mass of said frame gears 5 at a position or positions synchronously off-centre relative to the centre of said frame gears 5 to cause rotation of said frame gears 5 about their axis of rotation in response to a centrifugal force caused as a consequence of the orbital movement of said frame gear assemblies.

The means for positioning and maintaining the effective centre of mass is a set of two or more weight gears 9 with a weight 10 attached to one side and meshed with the final drive gear 7. The weight gears 9 are free to rotate on shafts spaced evenly around each frame gear 5, and each weight gear 9 is meshed with the final drive gear 7 in such a manner that each set of weight gears 9 have their weights 10 in the same quadrant pointing away from the output shaft 2. The position of each set of weight gears 9 is set interconnected by aligning one weight gear 9 on every frame gear 5 directly away from the output shaft 2 such that all weights 10 on all weight gears 9 are aligned directly away from the output shaft 2 before connecting the looped drive chains 13 around the multiple drive sprocket 12 and the final drive sprocket 1 1.

In another arrangement the apparatus uses a means of coupling the frame gears 5 to said output gear 4 via said idler gears 8 and reversing the direction whereby motion of said frame gear 5 is transmitted to said output shaft 2 equal to said input of the frame gear assemblies around said output gear 7.

In accordance with this arrangement the spin of the output gear 4 is conveyed via the output shaft 2 to return some of the output energy to drive the input by direct or variable mechanical drive, or by any other means such as hydraulic or electric drive systems, so as to maintain drive to the system. This is described further below.

Referring to the drawings and firstly to Fig. 3 where power is generated from an apparatus which is made up of a housing frame 1 and an output shaft 2 held by bearings 22 on opposite sides of the frame 1. On the output shaft 2 are two symmetrical radial arms 3 each with two or more branches of equal length mounted by bearings 23. In-between the radial arms 3 and at the centre, is an output gear 4 which is locked onto the output shaft 2. Mounted on the radial arms 3 at the outer edge of the output gear 4 are pedestal shafts projecting out from each branch of the radial arms 3 being equally spaced around the frame gear 5 by bearings 24, On these are reverse idler gears 8 and bearings 25 located to mesh with the output gear 4.

Mounted between the radial arms 3 at the outer edge of the output gear 4 is a shaft holding a reverse idler gear 8 by bearings 23 such that the idler gear 8 is meshed to the output gear 4. The shaft can be secured to the radial arms 3 in a manner that will hold the radial arms 3 securely parallel. An alternative to this is to connect the pair of radial arms 3 by a structure that reaches around any gears.

At the outer edge of the reverse idler gears 8 and meshed wit them is a frame gear 5 which is free to rotate on bearings 26 around a frame gear shaft 6 mounted through both of all branches of the radial arms 3. Also mounted on each frame gear shaft 8 is a drive gear 7 which is locked onto the drive gear shaft 6 adjoining the f ame gear 5.

Two or more weight gears 9 are mounted on bearings 27 to pedestal shaft projecting out from all frame gears 5 equally spaced around the frame gear 5, with each weight gear 9 on each frame gear 5 meshed with the drive gear 7. Each weight gear 9 has one weighted side (This may be bui!t in or added as by an attached weight) each of which is arranged so that when one weighted side faces directly away from the output shaft 2, all weighted sides of all weight gears 9 face directly away from the output shaft 2.

Mounted on and locked to each frame gear shaft 6 outside the radial arms 3 is a final chain sprocket 11 mounted on the output gear shaft 2 is a free spinning collar with multiple chain sprockets 12 attached. Each final chain sprocket 11 is coupled to a multiple chain sprocket 12 by a drive chain 13. The cluster of multiple chain sprockets 12 is driven by the input drive sprocket 14 by any coupling method e.g. a drive chain to an input drive mounted to the frame 1. A drive source is applied to the input drive to start the operation of the apparatus to a required revolution rate and thereafter a return from the output can be applied to maintain this and compensate for energy losses including the non-recoverable losses of friction within the apparatus. The preferred return system is a variable direct coupling of the present invention.

Drive belts and pulleys may be used instead of drive chains and chain sprockets. I this configuration, when viewed from the side the weight gears 9 are mounted

With appropriate adjustments the apparatus can be run in either direction but the following will be described by a clockwise rotation by way of example only. When a clockwise drive is applied to the input drive sprockets 14 it is conveyed via the drive chains 7 to the final chain sprockets 1 1 and through to the drive gears 7 and their meshing with the weight gears 9.

The acceleration and friction of these components at start up applies resistance at the final chain sprocket 1 1 which will make the drive chains act to that extent as a solid, causing the radial arms 3 with their components of idler gears 8 and frame gear assemblies to be induced to rotate clockwise around the output shaft 2 and so create centrifugal force to the outer components, and most relevantly the weight gears 9, so that at adequate revolutions (around 150 rpm upwards) the weights 10 are unable to spin due to the increased outward pull of centrifugal force and they are held synchronously on the widest radial line.

With the final chain sprocket 1 1 unable to spin there is a complete conveyance of ail input (less friction) through the meshing of the frame gear 5 to the idler gears 8 to the output gear 4 and to the output shaft to which it is attached. This is the first force to spin the output gear 4 clockwise. Resulting from this all parts of the frame gear 5 will express greater centrifugal force as the radial arms 3 rotate faster.

If an output load is applied, an equal input is required to maintain the radial arms 3 rotation rate (note input equal to output), but the increase in tenston between the input and output, at the meshing of the drive gear to the weight gear 9, will cause the weights 10 to be forced past the central radial line, and so transfer the centre of gravity (the line of centrifugal force) to the side of the frame gear 5 on which they are mounted, and so apply torque to the frame gears 5 due to centrifugal force and so cause the frame gears 5 to spin clockwise with the weight gears 9 synchronously locked. The clockwise spinning of the frame gears 5 wili convey the second driving force, being the product of centrifugal force (a non-input requiring byproduct of angular momentum) through the idler gears 8 to the output gear 4 and to the output shaft 2 to which it is attached. This is the second force to spin the input shaft 2 clockwise.

Figure 4 is an illustration of a frame gear 5 in three states of spin while in orbita! rotation in which state the weights 10 are pulled outwards (up the page) and are the reason for the conveyance of both forces that are delivered to the output.

First is the resistance to rotation that allows only proportional offset of the weights 10, due to the input expressed through the drive gear to the weight gears 9 against the synchronous lock which causes all input to be delivered through to the output.

Second is the torque applied by centrifugal force to that proportional offset of the weights 10 that introduces an equal amount of a second power source for delivery to the output.

Depending on gearing, a mix of the two spin or revolution rates will occur, but with a one to one gearing their aggregate rate combining at the output wili always be the same as the input rate.

Given that any increase in revolution rate of the radial arms 3 produces a four-fold increase in centrifugal force applying to the weights 10; it follows that the second forc applied by the apparatus will accordingly increase its contribution to the rotation rate of the output gear 4. At any given input rpm. the more the final chain sprocket 11 rotates (in contrast to non-spin that applies the first force rotation of the frame gears 5) in response to resistance by any load applied to the output, against the input torque, it will drive the weights 10 to advance, and so maintain an added off centre weight of the weight gears 9 to one side of the frame gear 5 whilst in orbit, regardless of any spin the frame gear 5 may undergo, such that the offset mass of the weight gears 9 orbit in a manner synchronous to the centre of orbit of the frame gear 5 while they may be freely spinning in orbit. This will increase the power of the second force while simultaneously increasing resistance by the final chain sprocket 11 and so increasing the conveyance of the first force at the same power. Since revolution rate of the first and second force may vary, gearing must be on a one for one gearing ratio or it will cause a change in input to output ratio that will trigger internal tensions thai drain energy or even cause breakage, if return of power is not controlled as by variable systems.

Since the first force is a direct product of the input force and is fully conveyed to the output, and the second force is a consequential force resultant from centrifugal force acting on the advance of the weights 10, all the output of the of the second force less f rictionai loss, i gain, and so can be used to power external applications.

As illustrated in Figure 1 it will now be described how the input forc is amplified to a doubling at the output. We will follow the flow of the forces mechanically through the apparatus with units of force in newtons and their torque in newton meters. These forces and their flow can be measured as follows, using newtons as units of force and their direction indicated as 'cw" for clockwise and "acw" for anti-clockwise.

Capital letters in italics designate the point of force on the tangent of that component as listed below, and normal Capital letters in the calculations are for force in newtons. In the model where the apparatus is at operating rev with the radial arms 3 rotating at 159 rpm cw. (NB rpm is an adjustable selection for operation) centrifugal force holds the weights 10 in the outer quadrant no matter what the positioning or spin of the frame gears 5, enabled by their synchronous gearing, this enables the conveyance from D to G.

Calculating only one side for simplicity as the other side is a mirror image. The weights are of 1 kg mass each equal to a force of 9.8066 N each and located on the circumference of the weight gear 9, accordingly one side has a total of 19.6133 N.

When an input is applied to th tangent of the outer edge of the multiple drive sprocket at of 2961.87 N cw it applies 2961.87 X 0.19 Nm = 562.755 Nm.

And a matching output torque acw is applied to the output gear of

562.755 Nm. Calculating only one side for simplicity as the other side is a mirror image. This provides the following force at their respective radiuses on the working prototype. ITEM TEETH SYMBOL SYMBOL DIAMETER RADIUS (m) I

NO FORCE DISTANCE AT (cm) 1

Weight Gears 46 Q Q 23 0. 115

Final Gear Drive 30 D D IS 0.075

Frame Gear 120 G G 60 03 1

Idler Gear 60 30 0.15

Output Gear 120 M 60 0.3

Final Drive 15 L L 15 0.075

Sprocket

Multiple Chain 38 K K 38 0.19

Sprocket I

Input at K of 2961.87 N cwjrom an electric motor conveyed to the output

This is the 1^s* force

This is conveyed by the drive chain to L as

K X K÷ L

L = 2961.87 X .19 ~ .075 = 7503.4 N at L cw

This is conveyed to D cw

D = L X L ÷ D

7503.4 X .075 ~ .075 = 7503.4 N at D cw

This is conveyed to O acw against centrifugal

force

Q = D X D ~ Q

Q = 7503.44 X .075 ÷ .1 15 = 4893.52 N at Q acw This conveyed to G being the outer edge of the

frame gear G = Q X Q ÷ G

G - 4893.52 X .1 15 ÷ . 3 - 1875.85 N cw at G

G conveyed to M via the

idler gear M = G

X G ÷ M

M = 1875.85 X .3 - .3 =

WW pw = a torque

of 562.755 Nm

Being the same as the input

f orce at K cw of K = M

X M ÷ K K.= 1875.85 X.3 ~ .19 = 2961.87 at K at .19 = 562.755 Nm

This is the same as the input. This is the input fully returned once conforming to the iaw of conservation of energy, and so prevents any reverse or acw turning of the output gear 4 by balancing the output load to the input. There is however some frictional losses which cannot be quantified but are no more significant than any mechanicai devise, and relative to the centrifugal force as calculated is insignificant, but in the case of this devise they are actualfy mostly offset by the mechanics of the second force as appraised below. This is because friction through the gears tends to hold the weights more acw and so increase the distance from the radial line of the weights and so add to the second force.

An alternative train of force for conveyance of the input which eliminates most friction is the rotation of the radial arms 3, due to the resistance to spin of the final drive sprocket 14₍ alt torque at the input is applied by the drive chains to the final drive sprockets 14 so all input torque is applied to rotating the radial arms 3 which being bound to the output gear 4 applies output rotational torque equal to the input to the output gear 4.

This is input fully delivered once

Calculating the force at the edge of the output gear 4, resulting from Centrifugal force on the weights 10,

This is the 2"^u force.

At this point the weights 10 express centrifugal force from their rotation about the central point of rotation of the radial arms 3, this being the output shaft 2 calculated as follows.

Centrifugal force (F) = mv²÷r

Taking the average radius (distance) of the weights 10 from the centre of rotation around the output shaft as M + circumference of idler gear + G

Radius = .3m +(2 X .15) + .3 = .9m.

Circumference = 2 ττ r

Circumference ~ 2 X 3.14159 X .9 Circumference - 5.655 m

Velocity = c X rpm ÷ 60 in m/s

v « 5.655. X 159 ÷ 60

v = 14.985 m/s Centrifugal force on weights = m X v² ÷ r

Centrifugal force = 19.6133 X 14,985 X 14,985 ÷ ,9

Centrifugal force = 4893.5 at Q cw.

Q expressed at G

G = Q X Q ÷ G

4893.5 X .115 ÷ .3 - 1875.85 N at G

G conveyed to via the idler gear M G X G ÷M = M

1875.85 X .3 ÷ .3 =. 1875.85 N cw at M or 562,75 Nm Being the same as the input force at K cw of K = M X ÷ K

= 1875.85 X .3 ÷ .19 = 2961.87N at K at .19 = 562.75 Nm

This is†hft in u fully <teliver< a second |(m^_r

This applied to the weights at a distance of .3m applies 562.75 Nm.

With 1 ^ force - 562.75 Nm and 2^nd force = 562.75 Nm

Total output = 1125.5 Nm which is twice the input of 562.75 Nm.

This is a power amplification of one to two.

The capacity of apparatus to handle greater power input can be achieved by incorporating multiple frame gears 5, weight gears 9 or the use of modified weight arms whereby instead of these being attached to the weight gears 9 which in turn are mounted by bearings to pillars, the weight gears 9 can be mounted on shafts extending through the frame gears 5 and mounted on bearings such that the non-gear drive side could also have a weight arm attached. With the weights 10 balanced on either side a more even load would be applied to the frame gears 5 while increasing the mass of the weights 10 and so the power capacity range of that apparatus.

Further multiple apparatus on the common output shaft would multiply the output. The test frame housing could have room for at least three or more mechanisms.

Multiple apparatus engines may be run in series for any reason and only needing one low capacity controlled differential coupling to be installed on the first of the series coupled apparatus, so that power control of the, or all downstream apparatus can be made from the one low capacity controlled differential coupling without the need to install controlled differential coupling to any other apparatus. In order to self-power or recycle energy from the output to the input, the spin of the output gear 4 can be conveyed via the output shaft 2 to return one half of output energy to drive the input drive sprocket 14 of any apparatus by direct or variable mechanical drive, or by any other means such as chain, hydraulic or electric drive systems, or the preferred power regulator so as to maintain the system.

All gearing must be configured to suit the method of maintaining the input power when diverting any of the output to an input. Gearing must be considered at two levels as follows:

Gearing of the apparatus must be considered for both alternative transfer sequences of input revs to output revs, the first is the gearing from the input drive to the rotation of the radial arms 3 and through to the output gear 4, and the second_., the gearing from the input drive to the rotation of the weight gears 9 and by their centrifugal lock, rotation of the frame gear 5 through to the output gear 4.

With a power regulator installed a lock is engaged between:

1. The output shaft rotation 2:

2. The rotation rate of the radial arms 3; and

3. The rotation rate of the weight gears 9.

Since these are all then interconnected, all three must be geared one to one. Such a one to one gearing then allows the rotation of either the frame gears 5 or the radial arms 3, or any combined rotation of them to match the output rotation that these cause at the output On the working model the gearing is:

Other Examples of a 1 :1 gearing from input to output; ITEM NUMBER OF TEETH Any Other Multiple

Weight Gears 46 30

Final Drive Gear 30 30

Frame Gear 120 100

Output Gea 120 100

Final Drive Sprocket 15 10

Multiple Chain Sprockets 38 20

idler Gear Any Size Any Size

Weights 10 in the prototype may have been 1 Kg each but this must be varied to suit a particular apparatus to suit its dimensions of length, intended revs and strength and the input and output power that is intended.

Offset of weight 10 from centre of weight gears 9 must be sized such that the sizes of the weight gear 9 and the final drive gear 7 allows clearance for the weights 10 to clear the frame gear shaft when the frame gears 5 spin, and the inner weight gear 9 needs to clear the shaft.

If the invention is run without a power regulator installed, the idler gear 8 needs to be large enough to allow the weights 10 to clear the frame gear shaft at start up, when the weight gears 9 spin on their own axis before centrifugal force hoids them out as the radial arm 3 get to revolve fast enough.

F!G. 1 also provides an illustration for reference to confirmation of one to one gearing showing that input revs are always the same as the output revs no matter what the input revs of the multiple chain sprocket 12, provided the weight gears 9 do not spin (not spinning means the weights 10 are always further away from the output shaft 2 than are the unweighted end of the arms that hold the weights 10 to the weight gears 9 even when the frame gear 5 spins. This is synchronous rotation of the weights 10 as they are rotated around the output shaft 2 carried on the frame gear 5 regardless of whether the fram gear 5 is spinning).

If the multiple chain sprocket 12 is given exactly one turn from point K through 360 degrees back to point K, and the final drive sprocket 11 does not turn but stays at point L ie at 3.00 o'clock as viewed synchronously relative to the output shaft 2 when viewing the frame gear 5 being at 12,00 o'clock. Thus for one turn of the input (multiple chain sprocket 11 ) the final drive sprocket 11 and the radial arms 3 on which they are mounted carrying the frame gear 5 and idlers 8 must rotate one revolution. With all gears locked by their coupling to the locked final drive sprocket 11 , the idler gears 8 meshing with the output gear 4 must rotate it one turn.

If the multiple chain sprocket 12 is given exactly one turn from point through 360 degrees back to point K, but the radial arms 3 are not allowed to be rotated and the weight gears 9 cannot spin because they are held outwards by centrifugal force, then: the 38 teeth turn of the multiple chain sprocket 12, turns the final drive sprocket 38/15 of a spin. This is 2 & 8/15 spins. This spin of the final drive gear of 2 & 8/15 spins of its 30 teeth delivers 38/15 times 30 = 76 teeth advance.

This is meshed with the 46 teeth weight gears 9 which are mounted on the frame gear 5. If the weight gears 9 were locked onto the frame gear 5 (which they are not) then one full turn of the final drive gear would spin the frame gear 5. This is 30 teeth advance of the final drive gear's teeth.

But since the weight gears 9 are free to spin synchronously, then each time the frame gear 5 does one spin the weight gears 9 must also spin one revolution relative to the frame gear 5. This is 46 teeth.

This requires a total of 30 plus 46 teeth advance, this is 76 teet advance of the final drive gear. This is exactly the advance of the final drive gear teeth as shown above.

So since one turn of the input through the radial arms 3 equals one turn of the output, and one turn of the input through the frame gear 5 spin equals one turn of the output, any combination results in one input revolution gives one revolution of the output

FIG. 2 illustrates a preferred embodiment of the method and apparatus for returning output energy by a controlled differential coupling which connects the output shaft to the input in a manner that provides controlled differential coupiing, so as to control the amount of off set of the gravity/mass within the rotating gear, by varying the advance of the weights 10 from the radial line and so vary the torque energy generated by centrifugal force. FiG. 2 show the detail of this variable coupling which is actuated by variable hydraulic pressure through a rotary coupling and which causes the two helical slotted piston couplings (HSPC) 15 to move apart, thus causing rotational variation between the output shaft and the input at the multiple drive sprocket (MDS) 12. This is done b connecting the output shaft 2 to the input in a manner that provides controlled differential coupling so as to control the amount of off-set of the gravity/mass within the rotating frame gear 5, and so vary the energy generated.

Located within the multiple drive sprocket (MDS) 12 are two "helical slotted piston couplings"(HSPC) 15 which are slid over the output shaft 2, and free to slide horizontally, while restrained from rotation by horizontal internal slots 19 which accommodate drive pins extending out of the output shaft 2.

Helical slots 18 are located on the outer surface of the pistons 15 in opposing directions and accommodate drive pins extending in from the MDS 12 such that when the HSPCs 15 are centrally inserted within the MDS 12 with lateral retaining thrust stoppers or collars installed on the output shaft to maintain the output sprocket alignment and with a hydraulic pressure line created from an external pump via a rotary union to variably pressurize a drilled oil line 17 inside the input shaft with an outlet 8 between the two HSPCs 15 which have appropriate seals 29; increase in pump pressure applied through a rotary union coupling causes the two HSPC 15 to move apart causing the helical slots 16 to rotate the drive pin threads 20 to receive the drive pins 21 in each HSPC 15 make available rotational variation in the direct drive coupling from the output shaft 2 to the input at the MDS 12. The shaft 2 also has internal pin housing holes 28 through which the drive pins 21 pass.

With drive transferred from the output shaft 2 to the input through the drive pins 21, the helical angling of the outer slots means that for separation and the additional rotation that occurs, hydraulic pressure is required between the two pistons 15, which when removed will cause the pistons 15 to slide together and so reduced or remove the rotational advancing and the powering that causes, such that the apparatus power can be reduced or stopped. Springs may be installed against the stoppers to assist return of the HSPC 15 when hydraulic pressure is reduced to reverse rotational advancing. The rate of change in advance can be built into the system by shaping the helical slots 16 to any curved shape such that a constant rate of increase in hydraulic pressure will advance the multiple drive sprocket (MDS) 12 proportionally to the curved shape.

Since the apparatus can be run in either direction the HSPCs 15 should be fitted so that the helical slots 18 form the head of an arrow pointing in the direction of rotation, then separation caused by the application of hydraulic pressure will give differential rotation that causes the weight gears 9 to advance suitably for the direction of operation.

When assembling the HSPC 15 th relative rotational connection can be random. But rotational connection f rom the output to the input is critical. This is set when connecting th drive chains. With the HSPC 15 resting togethe the drive chains must be installed to connect the MDS 12 with the final drive sprocket 1 1 in such a manner that the weights 10 are held at neutral to slightly retarded, (that is ahead of the rotational direction of the radial arms 3) This is necessary for depowering the apparatus.

At this setting the apparatus can be started by an external power supply such as a starter motor applied to the MDS 12 or the output shaft 2 since this is locked to the MDS 12 by the controlled differential coupling, and when operating revs of the radial arms 3 are reached (generally 100-250) a pump can be activated to gradually increase the hydraulic pressure and monitored by a pressure gauge so as to advance the weights 10 to the point that the apparatus increases rpm at the output. At this point the starter motor should be turned off or disengaged leaving the apparatus to self-power or recycle power to the input.

When any extra output power is required, hydraulic pressure should be increased so as to increase the advance of the weights 10 causing the second force to proportionally increase, and so provide the power needed for the added output load and maintain the increased input need to power the apparatus.

F!G. 3 shows front and top schematic views of the powering system of an apparatus in accordance with the present invention.

FIG. 4 shows the effect of synchronous rotation of the weights 10 relative of the radial line which maintains a constant weight offset when the frame gear 5 is spun when two weight gears 9 are used unlike if only one weight gear 9 was used, On the left is a single weight gear system 50 and on the right a two weight gear system 60. The radial line of the frame gear is represented by line 51 and torque line of the offset weight is shown as 52.

A power monitor sensor should be fitted to regulate the power. Such a sensor can include a pressure gauge on the hydraulic power control line because this pressure is directly proportional to the advance of the weights 10, as measured as horizontal deviation from the radial line, and this is directly proportional to the power required to advance the weights 10, which in turn is proportional to the power output.

Care must be taken not to increase the hydraulic pressure too much, such that rpm continues to increase. If such rpm increase does occur the hydraulic pressure must be instantly reduced to prevent potentially very dangerous exponential increase in self powering of the apparatus. A suitable pressure release system may be installed for this function.

In this configuration the operational equipment is:

1. A starter motor;

2. A power regulator system (via the hydraulic pump);

a) By increasing hydraulic pressure; or

b) By releasing hydraulic pressure;

3. Two power monitor systems;

a) Pressure gauge; and

b) b) Rev counter,

All references to the term "centrifugal force" are meant as a descriptive term for an equal and opposite outward pull to centripetal force and are not dependent on any particular definition.

The current invention is intended as a description of the principles of power generation and application. The interconnection of the components may be varied for any reason including convenience or efficiency. The components herein may be altered for any suitable function to apply the principles as implied herein. The number of any components may be varied for greater convenience or efficiency but this does not alter the method of operation. The drawings herein do not display definitive specifications as they are for explanatory and demonstration purposes only. The non-inclusion of idler gears or locating them at a different point may change the mechanics of the operation but ot the principle of converting centrifugal force into a useable energy resource. Dimensions, rpm, direction of rotation, gearing and weight of components may be varied for the efficiency and output of any unit.

Conveyance of torque or rotation may be by chain or belt anywhere such as from a frame gear 5 to the output shaft 2.

Centrifugal force at any operating revs can be increased by extending the radius of orbit of the weights 10 from the output shaft 2, by any method such as constructing the apparatus by locating the frame gears 5 further out from the output shaft 2, and coupling it by a longer chain or belt, or if transfer of torque of the frame gear 5 to the output is by idler gears 8, the use of larger idler gears 8 or odd numbers of multiple idler gears 8 may be used in line.

If conveyance of the torque/spin of the frame gear 5 is by chain or belt from the frame gear 5 to the output gear 4, this eliminates the need or use of any idler gear 8 and allows construction to be varied in its radius from the output shaft to the frame gear 5 more easily than the use of large idler gears 8. It also removes the complication of configuring the weight gears 9 to avoid hitting the idler gear shaft at start up if the output is not locked to the input.

The non-use of idler gears 8 also allows for easier bracing of the two parallel radial arms 5.

It also eliminates the use of output gears 4_S idler gears 8 and frame gears 5 by replacing these with chain or belt drive pulleys or sprockets, allowing the frame gear 5 to be any frame structure that accommodates the weight gears 9.

While two weight gears 9 on each frame gear 5 will amplify power in accordance with the principles of the apparatus, as claimed three or more weight gears 9 can be used on each frame gear 5. Where two weight gears 9 are used, when the frame gears 5 during their rotation hold the weight gears 9 in the radial line with the output gear{see Fig 3), the outer most gear is subject to greater centrifugal force than the inner gear relative to their distance from the point of rotation about the output axel. In consequence more power is required to spin the frame gear 5 until both weight gears 9 are horizontal and thereafter less power is required until the weight gears 9 are again on the radial line, all be it having changed position with each other. This sequence is repeated during ail spinning of the frame gear 5.

This fluctuation in input power demand is overridden by the spin of the frame gear 5 caused by the synchronous offset of the weights 10 in a working apparatus. The fluctuation will however cause a fluctuation in load that will show on an amp mete to the motor if such is being used, causing the meter to show peak !oad rather than average power. The use of three weight gears 9 on each frame gear 5 eliminates this fluctuation.

The use of three or more weight gears 9 also increases the total mass that is offset by any specific degree of spin of the weight gears 9 holding weights 10 of the same mass when compared with the total mass offset when using two weight gears 9 on eac frame gear 5. This therefore increases the power capacity of an apparatus.

It is important that the apparatus should have at least a speed reducing system such as the power regulator; additionally a breaking system can be installed on the output to prevent uncontro!led power in an emergency,

As an addition if desired a band may be located to contain the passage of the frame gears 5 as they rotate about the output axel so as to provide a support against the centrifugal load on the axel and bearings 26 that support the frame gears 5.

Said band may be of any construction such as a bearing where the outer case is mounted to the housing frame 1 and the inner case located to support the passage of the frame gears 5 as they rotate about the output axel. The inner face of said case may be of a teeth receiving formation or as required to contain the passage of the frame gears 5 wit minimum wear. The two cases would be separated by bearings allowing free rotation of the inner case whereby the additional transit of the frame gear 5 caused by any spin of the frame gear 5. is provided for.

A braking system can be installed between the outer and inner cases as an addition or alternative safety braking system. It should be noted that such a braking system has the same effect as a load or braking on the output as both are downstream from the centrifugal torque on the frame gear 5 which is the last input.

Said braking could be used to reduce or even stop any power to the output. Said control of power may be integrated with any power or braking systems.

Said band may be used for a lubricating point for the frame gear 5 hereby such lubrication would be carried on to the idler gears 8 and output gears 4. Lubrication may be by any means such as stopping the apparatus and applying a lubricant to all parts, any spray system while in operation or oil gallery such as by entry into the output shaft to the radial arms 3 to the frame gear shaft and out to the final drive gear. Alternatively the radial arms 3 could contain a reservoir of lubricant from which centrifugal force would power transfer to the frame gear shaft and on to the final drive gears.

All the above is limited by structural strength. This again can be enhanced by the use of superior materials.

All moving parts should be enclosed by protective casing to prevent injury or damage that would be caused by any intrusion into the machinery or the escape of any parts which could be at high velocity under circumstances of mechanical failure however caused.

Although it is unnecessary due to the relative insignificance of friction, even this could be reduced by th application of the protective casing being a vacuum sealing casing and so eliminate wind friction if thought desirable.

All bearings and abrading or frictional surfaces must be kept appropriately lubricated, with any spillage or recycling able to be effected by a dual function of the protective casing.

TEST RESULTS

In testing of the practical embodiment of the apparatus shown in FIG. 5 and under constant slowly run electric motor input, the weights 10 can be seen to advance 450 on their arc when hand pressure resistance is applied to the output shaft 2 and when removed the weights 10 return to full extension of the radius. Using a photo tachometer D-2236 to measure the rpm of various components, with a digital camera recording the reading on movie mode, and these readings transcribed to a spread sheet and converted to a chart, conformation of the two forces have been shown.

With the apparatus powered by a 650 W electric drill various charts were formulated using Microsoft Office Excel 2003 as illustrated in the charts of FIGS. 8 to 16 which in each case show variations in output RPM (vertical axis) over time (horizontal axis). Each chart formulation process was duplicated to confirm the reliability. It was shown by the above testing that:

1. The second force i.e. produced by cranking centrifugal force has been applied.

2. The output force from apparatus is not stored kinetic energy from the flywheel effect.

3. More output is delivered than input is applied.

F!GS. 6 and 7 show the charting of separate forces with the input only powered by the electric drill with respective charted lines showing total output. the output due to the first force and the output due to the second force. The rpm of the output shaft was recorded while input force was applied, with peak rpm of 255.7 & 257.9 at whic point input force was withdrawn. The chart then shows a sudden two refresh interval drop of rpm to 177.7 & 184.5.

When this is compared with the charts of the rpm of the radial arms 3 (being the rate of revolution of the frame gears 5 mounted to the arms 3) which show a peak rpm of 193.3 & 197.5, a difference in peak rpm between the radial arms and the output is revealed, 255.7 less 193.3=62.4 and 257.9 less 197.5-60.4 which can only be explained by the addition of rprn from the second force, due to the centrifugal force applying on the weights 10 as they are advanced by the input and amplified by the gearing differential between the frame gear 5 and output gear 4.

Once the drill's input was withdrawn, and in the absence of a return of the output power to the input shaft, and thus no drive to the input shaft to create the second force, the sudden two refresh interval drop of rpm to 177.7 & 184.5 is in response to the only remaining force left, the kinetic flywheel energy, which then gives the steady reduction in rpm as seen in all four charts of no return, tapering down to the 100 rpm rate. Below 100 rpm the centrifugal lock of the frame gears can give way caustng the frame gears to spin and so no longer drive the output gear with the flywheel effect.

The additional energy supplied by the weights 10 under centrifugal force responsible for the increase in rpm of 255.7 minus 193.3=62,4 rpm or 32,3% (see FIGS. 6 and 7) and 257.9 minus 197.5=80.4 rpm or 30.5% is particularly significant as it comes on top of the input force as applied to the flywheel energy, and as such requires exponentially greater energy (E-V2 mv²).

When output power was returned to the input by direct belt drive, the additional energy supplied by the weights 10 under centrifugal force responsible for the increase in rpm of 813.6 minus 157.1=656.5 rpm or 417.8% (see FIG. 8) and 748.5 minus 165.1 =583.4 rpm or 353.3% (see FIG. 9)

Further tests showed that output power does not come from the kinetic, or flywheel energy alone. This is shown in tests recording the radial arms 3 rotation, while the output is under strong hand resistance load. Irrespective of whether power was being returned to the input or not, aii tests in both configurations showed that there was no drop in rpm of the radial arms 3 while the resistance was applied. There was however a drop in rpm of the output shaft 2 which could only be a reduction of the second force attributable to the additional energy supplied by the weights 10 under centrifugal force.

The figures from the tests of the radial arms 3 rotation during full drill input with hand resistance applications intermittently throughout were:

Radial arms 3 with return of power from the output shaft 2 to the input shaft (FIG. 10): constant rise from 28.1 to 249.1 when drill was removed.

Radia! arms 3 without return of power from the output shaft 2 to the input shaft (FIG. 1 1): constant rise from 32.6 to 220.4 when drill was removed.

Radial arms 3 without return of power from the output shaft 2 to the input shaft (FIG. 12); constant rise from 38.8 to 164.9 when drill was removed

In all cases when the drill input was withdrawn constant rpm reductions occurred.

The figures from the tests of the output shaft 2 during full drill input with hand resistance applications intermittently throughout were:

Output shaft 2 with return of output power to the input shaft: decreases from 692.1 to 447.1 (see FIG. 13) and from 503.9 to 322.7. Output shaft 2 without return: decreases from 249.8 to 45.3 (see FIG.

14) and from 313.1 to 122.2

Output shaft 2 without return: decreases from 248.5 to 178.3 (see FIG,

15) and from 258.6 to 105.7 and from 183.5 to 56.4.

FIG. 16 shows, with full power constantly applied to the drill, the rpm of the input shaft was measured without the output returned. Records show the rpm rose in one frame to 845.9 and held in the range of 845.9 to 963.1 until hand resistance was applied to the input. During this period hand resistance was applied to the output twice.

The first application was progressive commencing gently at 963.1 and increased to maximum effort at 925.3 rpm. Rpm during this progressively decreased through 963.1 , 942,1 , 934.2, 923.5, 925.3, 919.9, 915.7, 914.5, and 911.1 at which point hand resistance was removed and rpm rose to 948.5 when hand resistance was again applied for a short application and rpm dropped to 921.7, with hand resistance again removed rpm rose to 934.6, 915.7 and 911.2 at which time the same level of hand resistance was applied to the input shaft (with full power still applied from the drill) which slowed to 883.6, 533.6 & 162.4 at which point the drill's power was removed and rpm recorded were 162.4, 166.1 , 176.2, and 170.9.

In summary, FIGS. 7 and 8 show there is an additional force driving the output.

FIGS. 8 and 9 show additional force when output is returned.

FIGS. 10 to 15 show kinetic flywheel force is not being drained under hand load.

FiG. 16 shows the output is a far greater force than that supplied from the drill.

Therefore since the additional force at the output does not come from the kinetic flywheel and it exceeds the power of the drill, and is compounded when output is returned to the input, it must come from the centrifugal force applying on the weights, this is the second force referred to above.

In the tests the prototype apparatus having only weights 10 of less than one pound and the radial arms only run to less than 250 rpm without return of power, centrifugal force delivered to each weight is only 11.57 kg under the formula (vlRN2/2933. As a prospective, if a purpose machined built apparatus were to run at 7,000 rpm with only the same weights, it would generate a centrifugal force of 7,666 kg.

The principles of the apparatus apply to any different configurations of apparatus but may give a different balance of contributions from the first and second output forces, since any variation in the balance in total frame gear mass and the mass of the weights will change the dynamics of each, because the energy to supply to or extract from both a flywheel and centrifugal force varies with mass, as well as this both of these also vary with radius,

ADVANTAGES

Given the properties of mass exhibited by a body spinning around a fixed point expresses angular momentum and centrifugal force, the function of the unit is to spin a body so as to maintain the angular momentum and convert centrifugal force into a cranking force to generate energy.

The apparatus of the present invention has a number of applications including as stand-alone power plants as single units or multiple units in any configuration including stacked on top of one another, side by side including on common axle shafts, for any mechanical energy application including water pumping and treatment, the generation of electricity, powering of vehicles, marine vessels, air craft, or any other mechanical devise including use in space or anywhere. The machine of the invention may be made to any size to suit any requirement for on-site and portable, to regional supply of energy. Regional power generation would eliminate the need and costs associated with long distance transportation of energy be it electricity or fossil fuel.

The powering system incorporated in the current invention has been tested and provides a simple, compact energy generating system and is lighter in its construction and so is cost effective when compared to internal combustion motors or other mechanical systems. It can operate anywhere and is not dependent on environmental conditions particularly in that it requires no fuel and emits no emissions or waste by- products such as noise and heat, it can be made to sizes from very small to very large to suit most any application that an internal combustion motor could be used. The present invention uses the same principal as spinning weights with continuous outward force, but instead of applying friction by the outward force for locking as with the centrifugal clutch, it applies torque to a rotating gear, which is then transmitted to the output.

The novelty of the present invention is that rotating weights are held synchronously outwards by centrifugal force, while pulled offset from their radial line collectively to one sid of an outer gear (frame gear) by the tension of transmitting the input to the output, and so the offset is proportional to that tension. The offset weights being under centrifugal force apply incidental torque as free energy to the system.

When a rotational force is applied to the input of the apparatus of the current invention it is conveyed to the output shaft, at the same time the revolving that transfers that force acts as a catalyst to produc centrifugal force.

Elongation forces wilt be applied to the tether by centrifugal force (or reaction to centripetal force). Since the tether is revolving, the tether's tension can be used as a crank on an offset weight which is harnessed to crank the output as a second application of that force, and so both forces are delivered to the output. This is input doubled at the output less friction. This is the harnessing of centrifugal force.

VARIATIONS

The terms "comprising" or "comprises" as used throughout the specification and claims are taken to specify the presence of the stated features, integers and components referred to but not preclude the presence or addition of one or more other feature/s, integer/s, component/s or group thereof.

Whilst the above has been given by way of illustrative embodiment of the invention, all such variations and modifications thereto as would be apparent to persons skilled in the art are deemed to fall within the broad scope and ambit of the invention as defined in the appended claims.

LIST OF PARTS

1. Housing frame.

2. Input/Output shaft.

3. Radial arms. 4. Output gear.

5. Frame gear.

6. Frame gear shaft.

7. Drive gear.

8. Idler Gear.

9. Weight gear.

10. Weights.

11. Final chain sprocket.

12. Multiple drive sprocket (MDS)

13. Drive chain.

14. Input drive sprocket

15. Helical slotted pistons.

16. Hefical slots.

17. Oil line.

18. Oil line outlet.

19. Internal slots.

20. Drive pin threads.

21. Drive pins.

22. Output shaft to frame bearing.

23. Radial arms to output shaft bearing.

24. Radial arms to frame gear shaft bearing.

25. Idler gear bearing.

26. Frame gear bearing.

27. Weight gear bearing.

28. Internal pin housing hole.

29. Oil Seal.

50. Single weight gear system.

51. Radial line of frame gear.

52. Torque line of offset weight.

60. Two weight gear system.

Claims

ΡΓ'Τ/ A mm, 1 /0006 4 2015/003205 ³⁹ PCT/AU2014/000694

1. An energy generation apparatus for harnessing centrifugal force into a cranking force to apply energy to a shaft when the centre of gravity/mass within a gear is manipulated to rotate continuously off centre to one side of that gear around the centre of another gear, the apparatus comprising;

a duel function input shaft and output shaft rotatably attached to opposite sides of a housing and defining a first axis of orbit;

an output gear fixed for rotation to said output shaft;

an input sprocket rotatably mounted on said output shaft;

a pair of radial arms rotatably mounted on said output shaft;

at least one idler gear;

at least two frame gear assemblies having an axis of rotation, said frame gear assemblies being mounted for orbital movement around said output gear in response to drive from an input on the input sprocket, and including means to convey said orbital movement to th output gear by the idler gears, each said frame gear assembly comprising:

a frame gear;

a shaft;

a drive sprocket and a drive gear; and

at least two weight gears;

means for positioning and maintaining the effective centre of mass of said frame gears at a position or positions synchronousiy off-centre relative to the centre of said frame gears to cause rotation of said frame gears about their axis of rotation in response to torque from centrifugal force caused as a consequence of the orbital movement of said frame gear assemblies;

means of coupling said frame gears to said output gear via said idler gears and maintain the direction whereb motion of said frame gear is transmitted to said output shaft equal to and in the same direction of rotation as said input of the frame gear assemblies around said frame gear axie; and

means of conveying the spin of the output gear via the output shaft to return some of the output energy to drive the input by direct or variable mechanical drive, or by any other means such as hydraulic or electric drive systems, so as to maintain drive to the system. ΡΓ'Τ/ A mm , 1 /0006 4 2015/003205 40 PCT/AU2014/000694

2. Apparatus as claimed in claim 1 , and including at least one pair of frame gear assemblies, respective frame gear assemblies of said pair being arranged symmetrically on opposit radial sides of the output gear,

3. Apparatus as claimed in claim 1 or claim 2, wherein each said frame gear assembly comprises a f rame gear and mass adjusting means carried by said frame gear for adjusting the centre of mass of the frame gear assembly.

4. Apparatus as claimed in an one of claims 1 to 3, further including a frame gear shaft for each frame gear assembly and mounted at a position spaced equally out radially from and extending parallel to the output shaft, said frame gear assembly being supported to the frame gear shaft for free rotation there around.

5. Apparatus as claimed in claim 3, wherein said mass adjusting means comprise weight gears, said weight gears being movably mounted on the frame gear to enable adjustment of the effective centre of mass of the frame gear assembly.

6. Apparatus as claimed in claim 5, wherein said weight gears comprise a pair or more of weight gears arranged symmetrically on opposite radial sides of the axis of rotation of the frame gear.

7. Apparatus as claimed in claim 5 or claim 6, wherein each weight gear is supported on the frame gear for rotation about an axis extending parallel to the axis of the rotation of the frame gear.

8. Apparatus as claimed in any one of claims 5 to 7, wherein the centre of mass of each weight gear is offset relative to its axis of rotation and maintains that offset synchronously such that offset is maintained even when the frame gear rotates about its own axis.

9. Apparatus as claimed in any one of claims 5 to 8, wherein said weight gears are arranged such that when each weight or centre of mass of each weight gear is concurrently radially outer most and wherein the weight gears on frame gears on the opposite sides of the output shaft are arranged symmetrically relative to each other.

10. Apparatus as claimed in any one of claims 5 to 9, wherein said weight gears are in mesh with a common drive gear coaxial with the frame gear through which rotation by a drive chain can be transmitted to the weight gears ΡΓ'Τ/ A mm, 1 /0006 4 2015/003205 41 PCT/AU2014/000694 from the input sprocket, said drive gear being mounted to the frame gear shaft for rotation therewith,

11. Apparatus as claimed in claim 10 wherein said frame gear shafts are supported by spaced radial arms mounted fo rotation relative to the output shaft, the radial arms extending symmetrically on opposite radial sides of the output shaft.

12. Apparatus as claimed in 11 wherein each said frame gear assembly is coupled to the output gear through the idler gears.

13. Apparatus as claimed in any one of the preceding claims, wherein said frame gear shafts are adapted to receive an input from said input sprocket to rotatably drive the drive gears against the weight gears with said weights which are synchronously held outwards by centrifugal force.

14. Apparatus as claimed in claim 13, wherein said orbital motion is applied to said f ame gear assemblies as torque.

15. Apparatus as claimed in claim 14, wherein the torque will be resisted as spin by the coupling to the output gear causing the drive chains to act as a solid component.

16. Apparatus as claimed in claim 15, wherein the solid behaviour of the chains is applied to the frame gear assembly as rotational torque about the output shaft for complete conveyance of all input from the input sprocket less any friction through the meshing of the drive gear to the weight gears to the frame gears to the idler gears to the output gear to form a first force applied to the output gear.

17. Apparatus as claimed in any one of claims 14 to 16, wherein when the frame gear assembly is rotating about the output shaft all parts of the frame gear will express centrifugal force as a by-product which increases as the radial arms rotate faster,

18. Apparatus as claimed in any one of claims 14 to 17, wherein any increase in revolution rate of the radial arms increases both rotational force and centrifugal force applied to the weights by a factor of four proportionally in accordance with E- ½ mv² and F= rnv^/R and will increase the power range that can be amplified. ΡΓ'Τ/ A mm, 1 /0006 4 2015/003205 ⁴² PCT/AU2014/000694

19. Apparatus as claimed in any one of claims 5 to 18, wherein said rotation transmitted to the weight gears will cause the weights thereon mounted to move away from the most outward line causing said mass adjusting in response to any differential between the input and output power caused by friction or output load.

20. Apparatus as claimed in claim 19, wherein average movement of the weights being so caused, and being subjected to said centrifugal force, will apply the same torque as that force that caused it in the conveyance of the first force.

21. Apparatus as claimed in claim 19 or claim 20, wherein the torque is applied to the frame gear in response to the centrifugal force applying to it in a radial line from the output shaft.

22. Apparatus as claimed in claim 21 , wherein said torque less any friction from the gears is applied through the idler gears in a reverse direction to the output gear to form a second force applied to the output gear.

23. Apparatus as claimed in any one of claims 19 to 22. wherein both the first force and the second force are governed by the input on the input sprocket meeting a resistance against rotation of the weight gears which are held by centrifugal force being a by-product of angular momentum, both the first and second forces apply equal output force regardless of their revolution rates.

24. Apparatus as claimed in claim 23, wherein all gearing is configured to suit the method of maintaining the input power when diverting any of the output to the input.

25. Apparatus as claimed in claim 24, wherein the gearing is a one to one gearing if all power is to be returned at a one to one revolution rate which requires the rotation of either the frame gears or the radial arms singularly, or any combined rotation of the frame gears or the radial arms to match the input rotation rate that these gears cause at the output, and with both applying the same torque the output will equal twice the input power less any loss due to friction.

26. Apparatus as claimed in claim 25, wherein the first force is applied with any sprocket sizing when it alone is rotating requiring only the gearing of the ΡΓ'Τ/ A mm, 1 /0006 4 2015/003205 ⁴³ PCT/AU2014/000694 second force to be configured one to one such that a combined one to one gearing is maintained when the frame gears rotate about their own axis,

27. Apparatus as claimed in claim 25 or claim 26, wherein calculating the one to one gearing of the second force it must be factored in that throughout each rotation of the radial arms, the weight gears maintain their orientation, and in doing so revolve around the drive gear, such that the drive gears must turn the number of teeth as there are on the weight gears in addition to the one full turn of the drive gear required to match the rotation of one frame gea rotation,

28. Apparatus as claimed in any one of claims 25 to 27, wherein the first force is a direct product of the input force and is fuliy conveyed to the output. and the second force is a consequential force resultant from centrifugal force acting on the advance of the weights, all the output of the second force less frictional loss, is gain, and so can be used to power an external applicatio while the first force is returned to the input for maintenance of the apparatus.

29. Apparatus as claimed in claim 28, wherein power is increased by incorporating multiple frame gears, weight gears or the use of modified weight arms whereby the weight gears can be mounted on shafts extending through the frame gears and mounted on bearings such that the non-gear drive side has a weight arm attached, such that wit the weights balanced on either side. a more even load would be applied to the frame gears white increasing the mass of the weights and so the power range that can be amplified.

30. Apparatus as claimed in clam 29, wherein multiple force or energy amplffying apparatuses may be powered in series for multiple amplification of power for returning power for self-powering.

31. Apparatus as claimed in any one of claims 28 to 30 , wherein the self- powering apparatus is a variable power hydraulically controlled returning apparatus or a power regulator for maintaining, increasing, reducing or stopping the power transmitted from the output to the input, said power regulator being incorporated within a multiple chain sprocket.

32. Apparatus as claimed in claim 31 , wherein a hydraulic cylinder is created on an inner side of said multiple chain sprocket to form the housing of the variable power returning apparatus. ΡΓ'Τ/ A mm, 1 /0006 4 2015/003205 44 PCT/AU2014/000694

33. Apparatus as claimed in claim 32, further comprising two pistons located on the inner side of the multiple chain sprocket.

34. Apparatus as claimed in claim 33, wherein each piston has at least two slots equally spaced around the inside and outside of both pistons.

35. Apparatus as claimed in claim 34, wherein the inside slots are horizontal and the outside slots are helical.

36. Apparatus as claimed in claim 35, wherein threaded holes are located around the multiple chain sprocket to align with the said helical slots and to ailow the insertion of screw pins.

37. Apparatus as claimed in claim 36, wherein each set of screw pins is positioned so as to locate into the helical slots in the outside of each said piston.

38. Apparatus as claimed in any on of claims 33 to 37, wherein said pistons are tubular such that they are located to neatly fit around the output shaft.

39. Apparatus as claimed in claim 38, wherein hydraulic seals are located on the inner facing ends of each said piston and set back to allow a space between the two pistons when they are together, so as to facilitate controlled separation by maintaining a space for hydraulic oil.

40. Apparatus as claimed in claim 39, wherein each set of pistons is engaged by a set of locating pins which are inserted equally around, or on opposite sides of the output shaft such that half of the locating pins are spaced to engage with each piston.

41. Apparatus as claimed in claim 40, wherein said engaging pins are fitted into said longitudinal slots on the inside of said pistons, by sliding said pistons outward after the pins are inserted into the output shaft, such that the pistons are then free to slide horizontally on the output shaft as far as the seals will permit.

42. Apparatus as claimed in claim 41 , wherein said output shaft has an axiaily extending hole drilled through the middle of the output shaft and extending from one end on the side of multiple chain sprocket to an outlet hole located in line with the mid line of the final drive sprocket.

43. Apparatus as claimed in any one of claims 29 to 42, further comprising a cylinder of the multiple chain sprocket is slid over the pistons to accommodate ΡΓ'Τ/ A mm, 1 /0006 4 2015/003205 45 PCT/AU2014/000694 the pistons centrally, when the pistons are together at the point of the oil outlet hole so as to align with the mid line of the final drive sprocket,

44. Apparatus as claimed in claim 43, wherein the helical slots in the outside of the two pistons are cut at opposite angles to each other and are fitted on the output shaft such that the slots form an arrow head in the direction of rotation of the output shaft.

45. Apparatus as claimed in claim 44, wherein the slots are cut at any suitable helical angle so as to provide optimal rotation of the weights to near ninety degrees when the pistons are hydraulically separated by an hydraulic pump to their maximum extent

46. Apparatus as claimed in claim 45, where the multiple chain sprocket is coupled to the final drive sprocket of the apparatus by the drive chains in such a manner that when the pistons are together at the outlet oil hole, each of the weights on the weight gears are set outwards on the radial line or slightly backwards from it.

47. Apparatus as claimed in claim 42, wherein on the drilled end of said output shaft is fitted a rotary oil union with an hydraulic pump connected via a hydraulic hose to the rotary oil union.

48. Apparatus as claimed in claim 47, wherein the hydraulic fluid pressure is provided between the pistons to cause the pistons to move apart such that movement of the pistons apart will, screw the cooperating pins along the slots causing a differential rotational coupling between the input sprocket and the output shaft.

49. Apparatus as claimed in claim 48, wherein said rotational differential coupling will transfer downstream to force and hold the weights off-centre,

50. Apparatus as claimed in claim 49, wherein said weight offset will cause torque and rotation of the f rame gear assembly to be applied to the output.

51. Apparatus as claimed in claim 50, wherein the output can be additionally returned to the input or made available to power or drive other applications.

52. An energy generation apparatus comprising:

a housing frame and an output shaft, the output shaft is rotatabiy mounted on opposite sides of the housing frame, the output shaft defining an axis of orbit;

2015/003205 ⁴⁶ PCT/ at (east two pair of identical parallel radial arms mounted on the output shaft by a pair of bearings;

an output gear fixed to the output shaft and located between the pair of radial arms;

an idler gear meshed with said output gear and located within each pair of radial arms, the idler gear rotating on an axle between the pair of radial arms; a frame gear assembly comprising a frame gear meshed with the idler gear, the frame gear is mounted by bearings and located between the pair of radial arms, the frame gear located on a frame gear axle, the frame gear axle being located between and towards the outer ends of the radial arms, each frame gear axle is mounted by bearings to the radial arms with one end of the frame gear axle extending through the radial arm;

a final drive sprocket fixed to the frame gear axle for receiving input from a looped drive chain from a multiple drive sprocket; the multiple drive sprocket is coaxially centered on bearings on the output shaft, the multiple drive sprocket being located outside the radial arms and comprising parallel sprockets of the same size for coupling to each final drive sprocket;

a final drive gear located adjacent the frame gear and fixed to the frame gear axle;

a set of two or more weight gears with a weight attached to one side and meshed with the final drive gear, the weight gears are free to rotate on shafts spaced evenly around each frame gear, and each weight gear is meshed with the final drive gear in such a manner that each set of weight gears have their weights in the same quadrant pointing away from the output shaft, the position of each set of weight gears is set interconnected by aligning one weight gear on every frame gear directly away from the output shaft such that all weights on all weight gears are aligned directly away from the output shaft before connecting the looped drive chains around the multiple drive sprocket and the final drive sprocket;

wherein a first force is applied by a mechanical transfer of an input power from an input gear and frame gear assemblies to the output gear through a mechanical sequence of chains and gears, the transfer of energy from the input gear to the output gear has a coupling which is held by and dependent on, ΡΓ'Τ/ A mm, 1 /0006 4 2015/003205 ⁴⁷ PCT/AU2014/000694 centrifugal force acting on the weights attached to the weight gears, which by being revolved synchronously are pulled outwards on a radiai line, wherein when the conveyance of the input force is increased as the weights are pulled increasingly away from the radiating centrifugal line; and a second force is derived when the weight movement away from the radial line causes the weight gears on which they are mounted by bearings to be pulled by centrifugal force and so spin in response to the torque produced and transmit this as added power via the idler gears to the central output gear, such that the two forces are applied to the output gear.

53. The energy generation apparatus of claim 52, wherein each weight gear has a weight which is identical in size and weight attached to one side of the weight gear.

54. The energy generation apparatus of claim 52 or claim 53, wherein the first force is a turning force applied to the input sprocket and said frame gear assemblies, the turning force is resisted as spin by the coupling to the output gear and any load thereon causing the drive chains to act as a solid, the solid behaviour of the drive chains is applied to the frame gear assemblies as rotational torque about the output shaft for complete conveyance of all input motion less friction through the meshing of the drive gear to the weight gears to the frame gears to the idler gears to the output gear to form the first force applied to the output gear.

55. The energy generation apparatus of any one of claims 52 to 54, wherein as the frame gear assembly Is rotating about the output shaft all parts of the frame gear will express centrifugal force as a by-product which increases as the radial arms rotate faster, any increase in the revolution rate of the radiai arms increases both rotational force and centrifugal force applied to the weights by a factor of four proporttonally in accordance with the formulas for kinetic energy of E= ½ mv² and the centripetal force F= mv²/R and will increase the power range that can be amplified.

56. The energy generation apparatus of any one of claims 52 to 55, wherein the rotation transmitted to the weight gears causes the weights mounted to the weight gears to move away from the most outward line causing said mass ΡΓ'Τ/ A mm , 1 /0006 4 2015/003205 48 PCT/AU2014/000694 adjusting in response to any differential between the input and output power caused by friction or output load.

57. The energy generation apparatus of claim 56, wherein the average movement of the weights is subjected to said centrifugal force, will apply the same torque as that force that caused it in the conveyance of the first force.

58. The energy generation apparatus of claim 57, wherein the torque is applied to the frame gear in response to the centrifugal force applying to it in a radial line from the output shaft,

59. The energy generation apparatus of claim 58, wherein the torque, less any friction in the gears is applied through the idler gears to the output gear to form a second force applied to the output gear.

60. The energy generation apparatus of any one of claims 52 to 59, wherein both the first force and the second force are governed by the input meeting resistance against rotation of the weight gears which are held by centrifugal force, being a by-product of angular momentum, both the first and second forces may apply equal output force regardless of their revolution rates.

81. The energy generation apparatus of any one of claims 52 to 60, wherein the gearing of each gear is configured to suit the method of maintaining the input power when diverting any of the output to the input.

62. The energy generation apparatus of claim 61 , wherein to achieve a one to one gearing each respective gear contains the following number of teeth:

(a) weight gears with 46 teeth;

(b) final drive gear with 30 teeth;

(c) frame gear with 120 teeth;

(d) output gear with 120 teeth ;

(e) final drive sprocket with 15 teeth; and

(f ) multiple chain sprocket with 38 teeth.

63. The energy generation apparatus of any one of claims 52 to 62, wherein multiple apparatus are run in series for any reason and only needing one low capacity controlled differential coupling to be installed on the first of the series coupled apparatus, so that power control of the, or all downstream apparatus can be maintained from the one low capacity controlled differential coupling Dr' /Ainni,i/oo06 4 2015/003205 49 PCT/AU2014/000694 without the need to install controlled differential coupling to any other apparatus.