FIELD OF THE INVENTION

This invention generally relates to an energy generator and in particular to an energy generation method and apparatus for producing rotational torque through an output shaft that utilises centrifugal force to impart the rotational torque on the output shaft.

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 or sprocket when a revolving gear is manipulated to maintain the centre of mass within that gear synchronously off centre to one side of that gear regardless of any spinning of the gear about its self.

BACKGROUND OF THE INVENTION

It should be noted that reference to the prior art herein is not to be taken as an acknowledgement that such prior art constitutes common general knowledge in the art.

Motors and other machines for converting a source of input energy to an output in the form of rotational torque that is delivered through an output shaft have been available for many years. The rotational torque at the output shaft is commonly utilised to produce electricity via a generator, power a pump or other machine, or operate other devices. The input energy for such machines can be provided by a variety of sources. One type of machine that utilises a naturally and readily available source for the input energy is a gravity motor. These machines use the force of gravity on moving weights to create the imbalance necessary to achieve the desired rotational torque to power a generator, pump or other work machine. These machines also utilise centrifugal force.

Over the years, various machines have been developed to utilise the benefits of gravitational and centrifugal forces to rotate an output shaft so that the rotational torque thereof may be utilised to generate electricity or operate another machine. Some of these have been patented.

U.S. Pat. No. 6,237,342 to Hurford describes a gravity motor having an output shaft rotatably mounted on a housing that includes a guide surface against which a weighted follower contacts to drive the follower inward towards a hub, to which the output shaft is fixedly attached. The follower is attached to a connecting rod that is telescopically received in a sleeve. The connecting rod moves in and out of the sleeve in response to the follower contacting the guide surface to place the weights near the hub during the upward portion of the cycle and away from the hub during the downward portion of the cycle, resulting in a net torque that rotates the output shaft. The Hurford motor is defined as a device which modifies energy from a natural source (gravity) by use and inclusion of other natural aspects including momentum and centrifugal forces in conjunction with leverage, weight and cyclic shift to cause a continuous unsymmetrical rotary motion which acts upon a shaft to transfer energy for useful and beneficial purposes.

The Hurford machine has limitations and/or disadvantages that, despite the inherent advantages of using gravity and centrifugal forces to power the machine, have limited their practical use. One such limitation is that the weights end up being too evenly grouped in the opposing drop and lift zones to generate sufficient amounts of net torque that can be used to sufficiently deliver rotational torque to the output shaft for practical benefit.

It is true that some inventions can involve new 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 theorised that it is simply an apparent reaction to centripetal force, not a force in its own right, this is incorrect. While practical problems can always be solved using the strict Newtonian approach, it is often more realistic and intuitively simpler to use a rotating reference frame and introduce the necessary centrifugal forces.

It is accepted 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.

However, this hypothesis is flawed in that a change in direction can only result from an external force. If a stone is whirled round on a tether, in a horizontal plane, the only real force acting on the stone in the horizontal plane is applied by the tether (gravity acts vertically). There is a net force on the stone in the horizontal plane which acts toward the centre. In an inertial frame of reference, were it not for this net force acting on the stone, the stone would travel in a straight line, according to Newton's first law of motion. In order to keep the stone moving in a circular path, a centripetal force, in this case provided by the tether, must be continuously applied to the stone.

In the case of a centripetal inward force/pull applied at right angles it can only be caused by an inward movement, which 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 same 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 is pulled 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 external force being applied in the opposite direction to the centripetal force to offset that centripetal force. In this example, the force is centrifugal force.

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 earth that balances the earth's gravity. Professor Brian Cox is acknowledged for explaining this in a television program aired in 2019.

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 frictionless state, such as in space, will maintain angular momentum without added input.

In Newtonian mechanics, the centrifugal force is an inertial force that appears to act on all objects when viewed in a rotating frame of reference. Newton's Third Law states that for every applied force there is an equal and opposite force. In a reference frame rotating about an axis through its origin, all objects, regardless of their state of motion, appear to be under the influence of a radially (from the axis of rotation) outward force that is proportional to their mass, to the distance from the axis of rotation of the frame, and to the square of the angular velocity of the frame. Or simply, centrifugal force is an inertial force that resists changing the direction or velocity of the object.

The concept of centrifugal force can be applied in rotating devices, such as centrifuges, centrifugal pumps, centrifugal governors, and centrifugal clutches, when they are analysed in a rotating coordinate system. For example, a centrifugal governor regulates the speed of an engine by using spinning masses that move radially, adjusting the throttle, as the engine changes speed. In the reference frame of the spinning masses, centrifugal force causes the radial movement. A centrifugal clutch is used in small engine-powered devices such as chain saws, go-karts and model helicopters. It allows the engine to start and idle without driving the device but automatically and smoothly engages the drive as the engine speed rises. Inertial drum brake ascenders used in rock climbing and the inertia reels used in many automobile seat belts operate on the same principle.

By way of a further example, helicopter rotor systems depend primarily on rotation to produce relative wind which develops the aerodynamic force required for flight. Because of its rotation and weight, the rotor system is subject to forces and moments peculiar to all rotating masses. One of the forces produced is centrifugal force which helicopter engineers rely on to hold the rotors of a helicopter on a horizontal plane. It is defined as the force that tends to make rotating bodies move away from the centre of rotation.

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 utilise 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.

Clearly it would be advantageous if an energy generator could be devised that helped to at least ameliorate some of the shortcomings described above. In particular, it would be beneficial to provide an energy generation method and apparatus for producing rotational torque through an output shaft that utilises centrifugal force to impart the rotational torque on the output shaft for the generation of energy in a controlled manner without any dependence on sunlight or wind for generation of cheap electricity, powering for pumping, desalination, powering of transport, without the use of fossil fuels. The unit could be installed anywhere.

SUMMARY OF THE INVENTION

Given the properties of mass exhibited by a body 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 centrifugal 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 centre weight of a gear to one side of that gear whilst in orbit regardless of any spin it may undergo, such that the offset mass of the gear orbits in a manner synchronous to the centre of orbit while the actual gear may be freely spinning in orbit to generate energy.

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 continuously 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 by 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 second force less friction 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 at the output gear.

In accordance with a first aspect, the present invention provides an energy generator comprising: a support structure; an input shaft having a first axis, and an output shaft having a second axis substantially coaxial to the first axis and both shafts are pivotally supported to and mounted on opposite sides of the support structure; a pair of radial arms rotatably mounted on and between the input and output shafts; an output sprocket fixed for rotation to the output shaft; an input sprocket rotatably mounted on the input shaft; at least two frame gear assemblies having an axis of rotation, each frame gear assembly being mounted for orbital movement around the output sprocket in response to rotation of the input shaft and input sprocket, each frame gear assembly is connected to the output sprocket by a respective output drive belt to convey the orbital movement to the output shaft, each frame gear assembly comprising: a frame gear rotatably mounted on a frame gear shaft, the frame gear shaft is rotatably mounted between the pair of radial arms; a drive sprocket and a drive gear fixed on the frame gear shaft, the drive sprocket is connected to the input sprocket by an input drive belt; at least two weight gears driven by the drive gear, each weight gear having at least one weight; and a frame gear shaft locking device; wherein upon start-up and rotation of the input shaft and input sprocket the radial arms rotate around the first axis while the frame gear assemblies are restrained from rotation by the frame gear shaft locking device, and as rotational speed of the radial arms increases, a centrifugal force is generated to release the frame gear shaft locking device and allow the frame gear assemblies to rotate about their respective axis of rotation; wherein rotation of the radial arms around the first axis and rotation of the frame gear assemblies about their respective axis of rotation allows the weights on the weight gears to position and maintain the effective centre of mass of the frame gears at a position or positions synchronously off-centre relative to the centre of the frame gears to cause rotation of the frame gears about their axis of rotation in response to torque from centrifugal force caused as a consequence of the orbital movement of the frame gear assemblies; and wherein the output drive belt couples each frame gear to the output sprocket whereby motion of each frame gear is transmitted to the output shaft equal to and in the same direction as the input drive sprocket drives the frame gear assemblies around the frame gear shaft.

Preferably, each respective frame gear assembly may be arranged symmetrically on opposite radial sides of the output sprocket. The frame gear shaft of each frame gear assembly may be mounted at a position spaced equally out radially from and extending parallel to the output shaft, each frame gear assembly being supported to the frame gear shaft for free rotation there around.

Preferably, the at least two weight gears may be movably mounted on the frame gear to enable adjustment of the effective centre of mass of the frame gear assembly with all gearing conforming to a one to one gearing or sprocket ratio. The at least two weight gears may be arranged symmetrically on opposite radial sides of the axis of rotation of the frame 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. The weight gears may be arranged such that when each weight or the centre of mass of each weight gear is positioned concurrently radially outer most, and the weight gears on the frame gears on the opposite sides of the output shaft are arranged symmetrically relative to each other.

Preferably, the weight gears may be in mesh with the drive gear, the drive gear is mounted coaxial with the frame gear through which rotation by the input drive belt can be transmitted to the weight gears from the drive sprocket, the drive gear being mounted to the frame gear shaft for rotation therewith. The frame gear shafts may be supported by the spaced radial arms mounted for rotation relative to the input and output shafts, the radial arms extending symmetrically on opposite radial sides of the input and output shafts.

Preferably, the frame gear shafts may be adapted to receive an input from the input sprocket to rotatably drive the drive gears against the weight gears with the weights synchronously held outwards by centrifugal force. The orbital motion may be applied to the frame gear assemblies as torque proportional to the torque conveyed to offset the weight gears causing the input drive belts to act as a solid component to that extent. The solid behaviour of the input drive belts may be applied to the frame gear assembly carried by the radial arms as rotational torque about the output shaft for conveyance of the rotation of the output shaft from the input sprocket to form a first force applied to the output shaft.

Preferably, when each frame gear assembly is rotating about the output shaft all 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 and will increase the power range that can be amplified.

Preferably, the rotation transmitted to the weight gears may cause the weights mounted thereon to move away from the most outward line causing the weights to adjust in response to any differential between the input and output power. Average off-setting movement of the weights being so caused, and being subjected to the 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 applied to the frame gear in a radial line from the output shaft. The torque may be applied through the output drive belt in the same direction to the output sprocket to form a second force applied to the output sprocket.

Preferably, both the first force and the second force may be governed by the input rotation of 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, the generator may further comprise a means of conveying the rotation of the output sprocket via the output shaft to return a portion of the output 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 energy generator.

Preferably, all gear size and sprocket ratio may be configured to maintain the input power when diverting any of the output to drive the input. The gear size and the sprocket ratio may be a one to one gearing or ratio 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 the gears cause at the output.

Preferably, the first force may be applied with any gear sizing or sprocket ratio when it alone is rotating requiring only the gearing or ratio of the second force to be configured one to one such that a combined one to one gearing or ratio is maintained when the frame gears rotate about their own axis.

Preferably, when calculating the one to one gearing or ratio of the second force it 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 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 gear rotation. Preferably, the first force may be a direct product of the input rotation of the input sprocket and is 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 any friction, is gain, and so can be used to power an external application while the first force is returned to the input for maintenance of the energy generator.

Preferably, output 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 power range that can be amplified. Multiple energy generators may be powered in series for multiple amplification of power.

Preferably, the multiple amplification of power from centrifugal force may be harnessed by adding weights which increases to a factor of four from increases in velocity, a power range can be increased by locating the frame gear assembly further out from the input shaft or simply increasing the revolution rate of the radial arms.

Preferably, the means of conveying the rotation of the output sprocket via the output shaft to the input shaft to return a portion of the output to drive the input 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, the power regulator being incorporated within a hydraulic cylinder positioned over inner ends of the input and output shafts.

Preferably, the hydraulic cylinder has a housing which has a length that allows the hydraulic cylinder to slide over the input shaft and output shaft, one end of the housing is aligned and secured to the output shaft by a locking pin passing through both the housing and the output shaft.

Preferably, the hydraulic cylinder may further comprise a pair of pistons located within the hydraulic cylinder and positioned on the input shaft. Each piston may have at least two slots equally spaced around an external surface of each piston and at least two slots equally spaced around an internal surface of each piston. The internal slots may be horizontal slots and the external slots may be helical slots.

Preferably, the input shaft may have an axially extending hole drilled through the middle of the input shaft and extending from one end of the input shaft to an oil outlet hole located between the pair of pistons on the input shaft.

Preferably, threaded holes may be located around the hydraulic cylinder to align with the helical slots in the pistons and to allow the insertion of one or more sets of screw pins. Each set of screw pins may be positioned so as to locate into the helical slots at an outer edge of each piston when an inner edge of each piston is located together at the oil outlet hole on the input shaft.

Preferably, the pistons may be tubular shaped to form a sliding fit around the input shaft. A hydraulic seal may be located on the inner edge of each piston and set back to allow a space between the pair of pistons when they are positioned together, so as to facilitate controlled separation of the pistons by maintaining a space for hydraulic oil. The horizontal slots of each piston may be engaged by a set of locating pins which are inserted equally around, or on opposite sides of the input shaft such that a pair of each of the set of locating pins are spaced to engage with each piston.

Preferably, the pair of locating pins may be fitted into the horizontal slots on the internal surface of each piston by sliding each piston outward after the locating pins are inserted into the input shaft, such that the pistons are then free to slide horizontally on the input shaft as far as the hydraulic seals will permit.

Preferably, the hydraulic cylinder housing may be slid over the pair of pistons to accommodate the pistons centrally on the input shaft, when the pair of pistons are together at the point of the oil outlet hole.

Preferably, the helical slots in the external surface of each piston may be cut at opposite angles to each other and are fitted on the input shaft such that the helical slots form an arrow head shape in the direction of rotation of the input shaft. The helical slots may be cut at any suitable helical angle so as to provide variable differential in rotation between the output shaft and the input shaft for optimal rotation of the weights to near ninety degrees when the pair of pistons are hydraulically separated by a hydraulic pressure to their maximum extent, and when the hydraulic pressure is released the pair of pistons slide back together so as to incrementally reduce the offset of the weights through to no offset of the weights.

Preferably, the input drive sprocket may be coupled to the final drive sprocket of the energy generator by the input drive belt in such a manner that when the pair of 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. The axially extending hole at the one end of the input shaft may be fitted with a rotary oil union and a hydraulic pump is connected to the rotary oil union via a hydraulic hose.

Preferably, the hydraulic fluid pressure may be provided between the pair of pistons to cause the pistons to move apart such that movement of the pistons apart will screw the set of screw pins along the helical slots causing a differential rotational coupling between the output shaft and the input shaft. The 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.

Preferably, the output may be additionally returned to the input or made available to power or drive other applications.

Preferably, the frame gear shaft locking device may further comprise a brake device mounted on one of the radial arms and located adjacent to and extending radially out from each frame gear shaft. The brake device may comprise a tubular housing for encasing and guidance of a sliding arm, the sliding arm has a high friction brake pad positioned at an inner end of the sliding arm, the high friction brake pad is adapted to press against the frame gear shaft. The tubular housing may have one end closed and inserted between the closed end and an outer end of the sliding arm is a coil spring.

Preferably, the coil spring may be a compression spring. The strength of the coil spring may be designed to automatically release to match the centrifugal force produced by the rotation of the radial arms by the input shaft and input sprocket when the radial arms rotate fast enough that the weights on the weight gears would be held out by the centrifugal force, the centrifugal force acting on the sliding arm and the high friction brake pad will compress the coil spring and release the high friction brake pad and allow all input applied to the frame gear shaft to be fully applied to the weight gears so as to turn the weight gears and maintain the offset of the weights as they are synchronously carried by the resultant rotation of the frame gear.

In accordance with a further aspect, the present invention provides an energy generation apparatus for harnessing centrifugal force into a cranking force to apply energy to a shaft when the centre of 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 dual function input/output shaft rotatably attached to opposite sides of a housing and defining a first axis of orbit; an output gear fixed for rotation to the input/output shaft; an input sprocket rotatably mounted on the input/output shaft; a pair of radial arms rotatably mounted on the input/output shaft; at least two idler gears; at least two frame gear assemblies having an axis of rotation, the frame gear assemblies being mounted for orbital movement around the output gear in response to drive from an input on the input sprocket, and including means to convey the orbital movement to the output gear by the idler gears, each frame gear assembly comprising: a frame gear; a frame gear shaft; a drive sprocket and a drive gear; at least two weight gears; and a frame gear shaft locking device; wherein upon start-up and rotation of the input sprocket the radial arms rotate around the first axis of orbit while the frame gear assemblies are restrained from rotation by the frame gear shaft locking device, and as rotational speed of the radial arms increases, a centrifugal force is generated to release the frame gear shaft locking device and allow the frame gear assemblies to rotate about their respective axis of rotation; wherein rotation of the radial arms around the first axis and rotation of the frame gear assemblies about their respective axis of rotation allows the weights on the weight gears to position and maintain the effective centre of mass of the frame gears at a position or positions synchronously off-centre relative to the centre of the frame gears to cause rotation of the frame gears about their axis of rotation in response to torque from centrifugal force caused as a consequence of the orbital movement of the frame gear assemblies; and wherein the idler gears couple the frame gears to the output gear and maintain the direction whereby the rotation of the frame gear is transmitted to the input/output shaft equal to and in the same direction of rotation as the input of the frame gear assemblies around the frame gear shaft.

Preferably, the apparatus may further comprise a means of conveying the rotation of the output gear via the input/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 apparatus.

Preferably, the apparatus may comprise at least one pair of frame gear assemblies, each frame gear assembly of the pair being arranged symmetrically on opposite radial sides of the output gear. Each frame gear assembly may comprise a frame gear and mass adjusting means carried by the frame gear for adjusting the centre of mass of the frame gear assembly. Each frame gear assembly may comprise a frame gear shaft for each frame gear assembly and mounted at a position spaced equally out radially from and extending parallel to the input/output shaft, the frame gear assembly being supported to the frame gear shaft for free rotation there around. The mass adjusting means may comprise weight gears, the 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 the axis of rotation of the frame 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.

Preferably, 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. The weight gears may be 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. The 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, the 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 input/output shaft, the radial arms extending symmetrically on opposite radial sides of the input/output shaft. Each frame gear assembly may be coupled to the output gear through the idler gears.

Preferably, the frame gear shafts may be adapted to receive an input from the input sprocket to rotatably drive the drive gears against the weight gears with the weights which are synchronously held outwards by centrifugal force. The orbital motion may be applied to the frame gear assemblies as torque proportional to the torque conveyed to offset the weight gears. The torque may be resisted as spin by the coupling of 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 carried by the radial arms as rotational torque about the input/output shaft for conveyance of all input from the input sprocket 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 input/output shaft all 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 and will increase the power range that can be amplified.

Preferably, the rotation transmitted to the weight gears may cause the weights mounted thereon to move away from the most outward line causing the mass adjusting in response to any differential between the input and output power. Average off-setting movement of the weights being so caused, and being subjected to the 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 applied to the frame gear in a radial line from the input/output shaft. The torque may be applied through the idler gears in the same direction as 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 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.

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.

Preferably, the first force may 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. When calculating the one to one gearing of the second force it 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 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 gear rotation.

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 the centrifugal force acting on the advance (offset) of the weights, all the output less any friction of the second force is gain, and so can be used to power an external application while the first force is returned to the input for maintenance of the apparatus.

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 power 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 selfpowering.

Preferably, 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, the power regulator being incorporated within a multiple chain sprocket on the input/output shaft. 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.

Preferably, the variable power hydraulically controlled returning apparatus may further comprise a pair of pistons located on the inner side of the multiple chain sprocket. Each piston may have at least two slots equally spaced around an external surface of each piston and at least two slots equally spaced around an internal surface of each piston. The internal slots may be horizontal slots and the external slots may be helical slots.

Preferably, the input/output shaft may have an axially extending hole drilled through the middle of the input/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.

Preferably, threaded holes may be located around the multiple chain sprocket to align with the helical slots in the pistons and to allow the insertion of sets of screw pins. Each set of screw pins may be positioned so as to locate into the helical slots at an outer edge of each piston when an inner edge of each piston is located together at the oil outlet hole on the input/output shaft. The pistons may be tubular shaped to form a sliding fit around the input/output shaft. A hydraulic seal may be located on the inner edge of each piston and set back to allow a space between the pair of pistons when they are positioned together, so as to facilitate controlled separation by maintaining a space for hydraulic oil.

Preferably, the horizontal slots of each piston may be engaged by a set of locating pins which are inserted equally around, or on opposite sides of the input/output shaft such that a pair of each of the set of locating pins are spaced to engage with each piston. Preferably, the pair of locating pins may be fitted into the horizontal slots on the internal surface of each piston, by sliding the pistons outward after the locating pins are inserted into the input/output shaft, such that the pistons are then free to slide horizontally on the input/output shaft as far as the seals will permit.

Preferably, the variable power hydraulically controlled returning apparatus may further comprise a cylinder of the multiple chain sprocket is slid over the pair of pistons to accommodate the pistons centrally on the input/output shaft, when the pair of pistons are together at the point of the oil outlet hole so as to align with the mid line of the final drive sprocket.

Preferably, the helical slots in the external surface of each piston may be cut at opposite angles to each other and are fitted on the input/output shaft such that the helical slots form an arrow head in the direction of rotation of the input/output shaft. The helical slots may be cut at any suitable helical angle so as to provide variable differential in rotation between the output and the input for optimal rotation of the weights to near ninety degrees when the pistons are hydraulically separated by hydraulic pressure to their maximum extent and the angle of the helical slots will always guide the pistons together when hydraulic oil pressure is released so as to incrementally reduce the offset of the weights through to no offset of the weights.

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 pair of 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.

Preferably, on the axially extending hole at the one end of the input/output shaft may be fitted with a rotary oil union with a hydraulic pump connected via a hydraulic hose to the rotary oil union. The hydraulic fluid pressure may be provided between the pair of pistons to cause the pistons to move apart such that movement of the pistons apart will screw the cooperating pins along the helical slots causing a differential rotational coupling between the input sprocket and the input/output shaft. The 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. Preferably, the output may be additionally returned to the input or made available to power or drive other applications.

Preferably, the frame gear shaft locking device may further comprise a brake device mounted on one of the radial arms and located adjacent to and extending radially out from each frame gear shaft. The brake device may comprise a tubular housing for encasing and guidance of a sliding arm, the sliding arm has a high friction brake pad positioned at an inner end of the sliding arm, the high friction brake pad is adapted to press against the frame gear shaft. The tubular housing may have one end closed and inserted between the closed end and an outer end of the sliding arm is a coil spring. The coil spring may be a compression spring.

Preferably, the strength of the coil spring may be designed to automatically release to match the centrifugal force produced by the rotation of the radial arms by the input sprocket when the radial arms rotate fast enough that the weights on the weight gears would be held out by the centrifugal force, the centrifugal force acting on the sliding arm and the high friction brake pad will compress the coil spring and release the high friction brake pad and allow all input applied to the frame gear shaft to be fully applied to the weight gears so as to turn the weight gears and maintain the offset of the weights as they are synchronously carried by the resultant rotation of the frame gear.

In accordance with a still further aspect, the present invention provides an energy generation apparatus comprising: a housing frame and an output shaft, the output shaft is rotatably 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 the 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 frame gear axle locking device that upon start-up of the apparatus restrains the frame gear axle from rotation until the rotational speed of the radial arms increases, a centrifugal force is generated to release the frame gear axle locking device and allow the frame gear assemblies to rotate about their respective axis of rotation; 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 centred 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, centrifugal force acting on the weights attached to the weight gears, which by being revolved synchronously are pulled outwards on a radial 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.

Preferably, each weight gear may have a weight which is identical in size and weight and attached to one side of the weight gear. Preferably, the first force may be a turning force applied to the input sprocket and the frame gear assemblies carried by the radial arms, 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 conveyance of all input motion 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, as the frame gear assembly is rotating about the output shaft all parts of the frame gear may 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 and will increase the power range that can be amplified. 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 the mass adjusting in response to any differential between the input power and output load. Average off-setting movement of the weights may be subjected to the 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 applied to the frame gear in a radial line from the output shaft.

Preferably, the torque 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 the 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, the gearing of each gear may be configured to suit the method of maintaining the input power when diverting any of the output to the input.

Preferably, a unique gearing ratio may maintain the rotation of the radial arms and the spin of the frame gear and prevents the rotation of the radial arms and the spin of the frame gear building to the revolutions of the input while depleting the revolutions of the rotation of the radial arms and the spin of the frame gear. Preferably, the gearing ratio of the energy generator may be such that when the energy generator is running with or without the mechanical transfer system, the first force defined as the revolution rate from both the mechanical transfer of the input revolutions from the multiple chain sprocket to the output is the same as the second force defined as the revolution rate from harnessed centrifugal force with the combined revolution rate delivered to the output always the same as the input.

Preferably, the gearing ratio may be a one to one ratio.

Preferably, for the one to one gearing ratio the gearing of the second force may always be that the number of teeth in one turn of the multiple chain sprocket divided by the number of teeth on the final drive sprocket multiplied by the number of teeth on the final drive gear and this divided by the teeth on the weight gear will equal two. To achieve the one to one gearing each respective gear may contain 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 46 teeth.

Preferably, multiple apparatus 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 maintained from the one low capacity controlled differential coupling without the need to install controlled differential coupling to any other apparatus.

Preferably, the frame gear shaft locking device may further comprise a brake device mounted on one of the radial arms and located adjacent to and extending radially out from each frame gear shaft. The brake device may comprise a tubular housing for encasing and guidance of a sliding arm, the sliding arm has a high friction brake pad positioned at an inner end of the sliding arm, the high friction brake pad is adapted to press against the frame gear shaft.

Preferably, the tubular housing may have one end closed and inserted between the closed end and an outer end of the sliding arm is a coil spring.

Preferably, the coil spring may be a compression spring. Preferably, the strength of the coil spring may be designed to automatically release to match the centrifugal force produced by the rotation of the radial arms by the input sprocket when the radial arms rotate fast enough that the weights on the weight gears would be held out by the centrifugal force, the centrifugal force acting on the sliding arm and the high friction brake pad will compress the coil spring and release the high friction brake pad and allow all input applied to the frame gear shaft to be fully applied to the weight gears so as to turn the weight gears and maintain the offset of the weights as they are synchronously carried by the resultant rotation of the frame gear.

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 any losses.

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, aircraft, 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.

Any one or more of the above embodiments or preferred features can be combined with any one or more of the above aspects.

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:

Fig. 1 shows a top view of an energy generator in accordance with an embodiment of the present invention;

Fig. 2 shows one end view of the energy generator of Fig .1 ; Fig. 3 illustrates a perspective side view from above of the energy generator of Fig.1 ;

Fig. 4 shows one side view from the output side of the energy generator of Fig.1 ;

Fig. 5 illustrates the energy generator of Fig. 1 with the associated components for use attached;

Fig. 6 illustrates the components of a controlled differential coupling used as a power return system in accordance with the present invention;

Figs. 7 and 8 show front and top schematic views of an energy generator in accordance with another embodiment of the present invention; and

Fig. 9 illustrates how synchronous rotation of multiple weights maintains a constant offset despite any spin of gear on which they are mounted.

DESCRIPTION OF THE PREFERRED EMBODIMENT

The following description, given by way of example only, is described in order to provide a more precise understanding of the subject matter of a preferred embodiment or embodiments.

The present invention was designed to provide an energy generation method and apparatus for producing rotational torque through an output shaft 20, 40 that utilises centrifugal force to impart the rotational torque on the output shaft 40 for the generation of energy in a controlled manner. In its broadest form and as illustrated in Figs 1 and 7, the energy generator can be implemented in a belt drive system as in Figs. 1 to 5 or an idler gear system as in Figs. 7 and 8. The energy generation apparatus of the present invention is designed as an open system which utilises centrifugal forces to impart a rotational torque on an output shaft 20, 40 for the generation of energy in a controlled manner.

As shown in Figs. 1 to 5, the energy generator is supported for rotation on a support structure 1 , 1 a by an input shaft 30 having a first axis, and an output shaft 40 having a second axis substantially coaxial to the first axis. Both shafts 30, 40 are supported for rotation to and mounted on opposite sides of the support structure 1 , 1 a by a plurality of bearings 22, 22a. The input shaft 30 is rotatably mounted to the support structure 1 , 1 a by bearings 22 and the output shaft 40 is rotatably mounted to the support structure 1 , 1 a by bearings 22a. The support structure consists of a base 1 to which uprights 1 a are mounted perpendicular to the base 1 . Each bearing 22, 22a is mounted to the top surface of an upright 1 a of the support structure.

A pair of radial arms 3 are rotatably mounted on and between the input and output shafts 30, 40. In this embodiment the radial arms 3 are shown as a radial arm frame with two longitudinally extending arms 3 mounted on opposing sides to the input shaft 30 and the output shaft 40. Each radial arm 3 is rotatably mounted to the respective input or output shaft 30, 40 by bearings 23. Each input/output shaft 30, 40 extend perpendicularly to and through respective radial arms 3 to be positioned within the radial arm frame. An output sprocket 4 is fixed for rotation to an end of the output shaft 40 and is positioned within the radial arm frame. An input sprocket 14 is rotatably mounted on the input shaft 30 and is also positioned to lie within the radial arm frame.

Also mounted at opposite ends of the radial arm frame and between the radial arms 3 are at least two frame gear assemblies having an axis of rotation with a frame gear shaft 6 rotatably mounted to the radial arms 3 by bearings 24. Each frame gear assembly is mounted for orbital movement around the output sprocket 4 in response to rotation of the input shaft 30 and input sprocket 14 with each frame gear assembly connected to the output sprocket 4 by a respective output drive belt 41 and frame gear sprocket 90 to convey the orbital movement to the output shaft 40. Each frame gear assembly has a frame gear 5 rotatably mounted by bearings 26 on the frame gear shaft 6, a drive sprocket 1 1 a and a drive gear 7 fixed on the frame gear shaft 6. Each drive sprocket 1 1 a is connected to the input sprocket 14 by a respective input drive belt 33. Each frame gear assembly also has at least two weight gears 9 which mesh with and is driven by the drive gear 7. Each weight gear 9 is positioned on pedestal shafts on opposing sides of the frame gear shaft 6. Each weight gear 9 is rotatably mounted on the pedestal shaft by a bearing 27. Each weight gear 9 has at least one weight 10 positioned on the weight gear 9. Each frame gear assembly also has a frame gear shaft locking device 100 for preventing rotation of the frame gear shaft 6.

Any coupling method e.g. a drive chain or belt to an input drive assembly 35 mounted to the frame 1 , 1 a can be used to drive the input shaft 30 and input drive sprocket 14. As illustrated in Fig 5 the external starter drive pulley 31 connects the input shaft 30 and input drive sprocket 14 via a drive belt 34 to an input drive assembly 35 mounted to the frame 1 , 1 a. Alternatively, the input drive assembly 35 could be connected to drive sprocket 32 positioned on an end of the input drive shaft 30. In Fig. 5 the input drive assembly 35 is a DC electric motor 35 powered by a rechargeable battery 70. The input drive assembly 35 is applied to start the operation of the apparatus to a required revolution rate.

The present invention further comprises a disengaging means (not shown) for isolating the input drive assembly 35. By way of example only, the disengaging means could incorporate a one way clutch between the external starter drive pulley 31 and the input drive sprocket 14. When the present apparatus is operating at or above the required revolution rate the input drive assembly 35 can be disengaged to further reduce drag and wear. This is also important when the energy generating apparatus is in self powering operation which will be described further below.

In use, upon start-up and rotation of the input shaft 30, input sprocket 14 and the radial arms 3 rotate around the first axis while the frame gear assemblies are restrained from rotation by the frame gear shaft locking device 100. As rotational speed of the radial arms 3 increases, a centrifugal force is generated to release the frame gear shaft locking device 100 and allow the frame gear assemblies to rotate about their respective axis of rotation. Rotation of the radial arms 3 around the first axis and rotation of the frame gear assemblies about their respective axes of rotation allows the weights 10 on the weight gears 9 to position and maintain the effective centre of mass of the frame gears 5 at a position or positions synchronously off-centre relative to the centre of the frame gears 5 to cause rotation of the frame gears 5 about their axis of rotation in response to torque from centrifugal force caused as a consequence of the orbital movement of the frame gear assemblies. Accordingly, the output drive belt 41 couples each frame gear 5 to the output sprocket 4 whereby motion of each frame gear 5 is transmitted to the output shaft 40 equal to and in the same direction as the input drive sprocket 14 drives the frame gear assemblies around the frame gear shaft 6. T1

With the energy generation apparatus operating at or above the required revolution rate a return from the output shaft 40 can be applied to maintain or self power the energy generator apparatus and compensate for energy losses including the non-recoverable losses of friction within the apparatus. The preferred return system is a variable direct coupling or helical piston coupling 50 as illustrated in Fig. 6. The helical piston coupling 50 (while not shown on the apparatus) is positioned in between the output shaft 40 and the input shaft 30 to allow the rotation of the output shaft 40 to be conveyed to the input drive sprocket 14.

The helical piston coupling 50 provides a method for returning output energy to the input by a controlled differential coupling. The controlled differential coupling controls the amount of off-set of the mass within the rotating frame gear 5, by varying the advance or offset of the weights 10 from the radial line and so varying the torque energy generated by centrifugal force. The helical piston coupling 50 is actuated by variable hydraulic pressure through a rotary coupling connected to a hydraulic source. The hydraulic pressure activates the two helical slotted piston couplings (HSPC) 15 to move apart, thus causing rotational variation between the output shaft 40 and the input shaft 30.

Two HSPC’s 15 are slid over an inner end of the input shaft 30, and are free to slide horizontally, while restrained from rotation by horizontal internal slots 19 which accommodate drive pins 1 10 extending out of the input shaft 30. The drive pins 110 are located and retained within apertures 28 in the input shaft 30. The apertures 28 extend into the input shaft 30 but do not extend into the drilled oil line 17 extending axially within the input shaft 30 as illustrated in Fig. 6.

To fit the drive pins 1 10 into the apertures 28 in the input shaft 30, both pistons 15 are slid onto the input shaft 30 from the inner side end of the shaft 30 with the seals 29 on each piston 15 placed adjacent to each other. The pistons 15 are then slid along the input shaft 30 so as to expose the inner pin apertures 28, this allows the insertion of the drive pins 1 10 into the inner pair of apertures 28 in the input shaft 30. With the pins 1 10 inserted in the inner pair of apertures 28, the horizontal slot 19 in each piston 15 is located over the pins 1 10 to allow the piston 15 to slide back along the input shaft 30 as far as the seal 29 will allow. This then exposes the pair of apertures 28 at the opposing end of the input shaft 30 and allows the insertion of the drive pins 1 10 into the apertures 28. With the pins 1 10 inserted into their apertures 28 in the input shaft 30 the pistons 15 are slid to where they are located centrally aligned at the oil outlet hole 18 in the input shaft 30. At this point the hydraulic cylinder 1 15 can be slid over the pistons 15 to enclose the pistons 15 on the input shaft 30.

Helical slots 16 located on the outer surface of each piston 15 accommodate sets of drive pins 21 extending in from the hydraulic cylinder 1 15 when the hydraulic cylinder 1 15 is positioned over the input shaft 30 and the output shaft 40. The hydraulic cylinder 1 15 has a length which allows the cylinder housing to extend over both the input shaft 30 and the pistons 15 and the output shaft 40. With the hydraulic cylinder 1 15 placed over the pistons 15 the helical slot 16 on the inside piston 15 is located to allow a first set of drive pins 21 to be inserted through the drive pin threads 20 in the cylinder 1 15 and be located within the helical slots 16 to lock the inside piston 15 in place.

When the hydraulic cylinder 1 15 is inserted over the pistons 15 the outside piston 15 has a tendency to slide inwards along the horizontal slot 19 due to a close tolerance between the inner surface of the hydraulic cylinder 1 15 and the outer surface of the pistons 15. This can prove problematic when trying to locate the set of drive pins 21 into the helical slot 16 of the outside piston 15. To overcome this problem a threaded aperture (not shown) is inserted into the end of the outer piston 15 for receiving a fastener therein. The fastener allows the attachment of a cord to the end of the outer piston 15 to allow the helical slots 16 in the outer piston 15 to be easily aligned with the set of drive pin threads 20 in the hydraulic cylinder 1 15. This allows the insertion of the drive pins 21 into the helical slots 16 of the outer piston 15. The cord and the fastener are then removed from the end of the outer piston 15.

With both sets of drive pins 21 installed in respective helical slots 16 of the pistons 15 and the pistons 15 positioned on the input shaft 30 with inner ends adjacent the oil outlet hole 18 in the input shaft 30 the hydraulic cylinder 1 15 can be secured to the output shaft 40 by a locking pin (not shown) which passes through both the cylinder 1 15 and the output shaft 40.

In use, the hydraulic cylinder 115 is fitted over the inner side of the input shaft 30 such that when the HSPCs 15 are centrally inserted on the input shaft 30 with lateral retaining thrust stoppers or collars installed on the input shaft 30 to maintain the alignment of the pair of HSPCs 15 at the oil outlet 18. A hydraulic pressure line is connected to an external pump via a rotary union in the end of the input shaft 30 to variably pressurize the drilled oil line 17 inside the input shaft 30 with an outlet 18 located between the two HSPCs 15 which have appropriate oil seals 29 fitted to an inner edge of the pair of HSPCs 15. Increase in pump pressure applied through the rotary union coupling causes the HSPC’s 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. This effectively makes available rotational variation in the direct drive coupling from the output shaft 40 to the input shaft 30.

With drive transferred from the output shaft 40 to the input shaft 30 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. When the pistons 15 slide together this effectively reduces or removes the rotational advancing and the powering that causes, such that the apparatus power can be reduced or stopped. Springs may be installed against the ends of the helical piston coupling 50 to return each HSPC 15 to a start position 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 input shaft 30 proportionally to the curved shape. The slots 16 may be cut at any suitable helical angle so as to provide variable differential in rotation of the output shaft 40 and the input shaft 30 for optimal rotation of the weights 10 to near ninety degrees when the pistons 15 are hydraulically separated by hydraulic pressure to their maximum extent and providing strong sliding back together action when the hydraulic pressure is released so as to incrementally reduce the offset of the weights 10 through to no offset of the weights 10. Since the apparatus can be run in either direction the HSPCs 15 should be fitted so that the helical slots 16 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 or be offset suitably for the direction of operation.

When assembling the helical piston coupling 50 the relative rotational connection can be random. But rotational connection from the output to the input is critical. This is set when connecting the input drive belts 33. With each HSPC 15 resting together the input drive belts 33 must be installed to connect the input drive sprocket 14 with the final drive sprocket 1 1 a 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 energy generation apparatus.

At this setting the energy generation apparatus can be started by an input drive assembly 35 applied to the input drive sprocket 14 via the external starter drive pulley 31 . With the output drive shaft 40 connected to the input drive shaft 40 by the helical piston coupling 50 for controlled differential coupling, and when the required revolution rate of the radial arms 3 has been reached (generally 100- 250) a hydraulic pump can be activated to gradually increase the hydraulic pressure. The hydraulic pump is monitored by a pressure gauge so as to advance the weights 10 to the point that the energy generation apparatus increases rpm at the output shaft 40. At this point the input drive assembly 35 should be turned off or disengaged by the one way clutch leaving the energy generation apparatus to self-power or recycle power to the input.

When any extra output power is required, hydraulic pressure can 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 energy generation apparatus.

As best illustrated in Fig. 2, the input and output shafts 30, 40 are supported for rotation by bearings 22, 22a and mounted on opposite sides of the support structure 1 , 1 a. Each upright 1 a has a bearing 22, 22a fixed to an upper flat surface of the upright 1 a by any suitable fastener. The support structure base 1 and the uprights 1 a are constructed from a rectangular steel tube welded together to form the support structure 1 , 1 a. Alternatively, any other material or shaped tube may be used to provide the support structure 1 , 1 a. The support base 1 is designed to allow the energy generator apparatus to be placed and operated on any substantially flat surface. The base 1 may also include apertures for receiving fasteners for securing the base 1 to the surface if required. Alternatively, the base 1 may further be provided with a plurality of D-ring tie down anchors which can be used to tether the energy generator apparatus to the support surface.

As described above and as illustrated in Figs. 3 and 4 the radial arms 3 are rotatably mounted on and between the input and output shafts 30, 40 by bearings 23. Likewise, each frame gear shaft 6 is rotatably mounted at opposing ends to the radial arms 3 by bearings 24. The bearings 23, 24 allow the rotation between parts but are designed to support a predominantly axial load of the frame gear assemblies and the frame gear shaft 6 to the radial arms 3 and the axial loads applied by the radial arms 3 to the input and output shafts 30, 40. Also, thrust bearings may be located on the frame gear shafts on the inside of the radial arms abutting the bearings so as to prevent lateral movement of the frame gears 5 which could cause binding with the radial arms 3 and prevent the transfer of the centrifugal force to the output shaft 40.

As illustrated in Figs 1 and 3 the alignment of each frame gear assembly within the radial arms 3 is important for the dynamic balancing of the energy generator during rotation. As such, the frame gear sprockets 90 are fixed to the frame gear shaft 6 by a collar (not shown) so as to correctly align the frame gear sprocket 90 with the output sprocket 4. The collar ensures that each frame gear assembly is always symmetrically centred on opposite sides of the first and second axes of the input and output shafts 30, 40 and in alignment between the radial arms 3. This also applies to the positioning and alignment of the final drive sprocket 1 1 a and the input drive sprocket 14.

In order to provide a quick start-up of the energy generator each frame gear assembly is provided with a frame gear shaft locking device 100 to prevent the rotation of the frame gear shaft 6 until the radial arms 3 are rotating at the required revolution rate. At the required revolution rate the radial arms 3 are rotated fast enough for centrifugal force to hold the weights 10 out.

By way of example only, the frame gear shaft locking device 100 may be constructed as a cylindrical hollow tube body with one closed end and one open end. The open end has a central aperture sized to receive therein a threaded shaft. The cylindrical body has a pair of flanges extending outward from the periphery of the body and adjacent the open end to allow the frame gear shaft locking device 100 to be secured to the outer side of the radial arms 3 and over the end of each frame gear shaft 6. When secured to the radial arms 3 one end of the threaded shaft of the frame gear shaft locking device 100 is located within a receiving slot cut into the end of the frame gear shaft 6. The one end of the threaded shaft forming a key which when received within the slot in the end of the frame gear shaft 6 locks the frame gear shaft 6 from rotation. A collar with a central threaded aperture is located within and adjacent the closed end of the cylindrical body for receiving the other end of the threaded shaft.

The collar is also designed to ensure that the threaded shaft is aligned squarely within the receiving slot in the end of the frame gear shaft 6. A spring is positioned between the backside of the collar and the closed end of the cylindrical body and an interchangeable weight with a central aperture is adapted for receiving the threaded shaft therein. The spring tension maintains the end of the threaded shaft within the slot in the end of the frame gear shaft 6. The frame gear shaft locking device 100 is designed to prevent the rotation of the frame gear shaft 6 until the radial arms 3 are rotating at the required revolution rate. At the required revolution rate centrifugal force activates the frame gear shaft locking device 100 to release the end of the threaded shaft from within the slot in the end of the frame gear shaft 6.

The combination of the masses of the interchangeable weight, the threaded shaft and the collar when acted upon by the centrifugal force overcomes the spring tension and releases the frame gear shaft 6. The frame gear shaft 6 is then free to rotate. Different interchangeable weights can be substituted to vary the revolution rate at which the frame gear shaft locking device 100 releases the frame gear shaft 6. The centrifugal force applied to the rotating combination of the masses of the interchangeable weight, the threaded shaft and the collar matches the centrifugal force applied to weights 10 when the radial arms 3 rotate above that required for the weights 10 on the weight gears 9 to hold out on the radial line. Alternatively, the threaded shaft may be replaced with a sliding arm with a high friction brake pad which contacts the frame gear shaft 6 to prevent the frame gear shaft 6 from rotating. As above a spring is placed between the sliding arm and the closed end of the cylindrical housing. The sliding arm rests against the coil spring at its outer end with the brake pad pressed against the frame gear shaft 6 at the opposing end. The strength of the coil spring is selected to match the centrifugal force for automatic release when the radial arms 3 rotate fast enough that the weights 10 on the weight gears 9 would be held out by centrifugal force, the centrifugal force acting on the sliding arm and its brake pad will compress the spring and so release the brake and allow all input applied to the frame gear shaft 6 to be fully applied to the weight gears 9 so as to turn the weight gears 9 and maintain the offset of the weights 10 as they are synchronously carried by the resultant spin of the frame gear 5.

Centrifugal force at any operating revolution rate can be increased by extending the radius of orbit of the weights 10 from the output shaft 40. For example, by constructing the energy generator by locating the frame gears 5 further out from the output shaft 40. This will also require extending the length of both the input and output drive belts 33, 41 to suit.

The present invention requires a unique gearing ratio in order to maintain the rotation of the radial arms 3 and the spin of the frame gear 5, and prevents the rotation of the radial arms 3 and the spin of the frame gear 5 building to the revolutions of the input while depleting the revolutions of the rotation of the radial arms 3 and the spin of the frame gear 5. The gearing ratio of the energy generator is such that when the energy generator is running with or without the mechanical transfer system 50, the first force defined as the revolution rate from both the mechanical transfer 50 of the input revolutions from the input shaft 30 to the output is the same as the second force defined as the revolution rate from harnessed centrifugal force with the combined revolution rate delivered to the output always the same as the input.

Therefore, the gearing or sprocket ratio must be a one to one ratio. In order to achieve the one to one gearing or sprocket ratio the gearing of the second force must always be that the number of teeth in one turn of the input sprocket 14 divided by the number of teeth on the final drive sprocket 1 1 a multiplied by the number of teeth on the final drive gear 7 and this divided by the teeth on the weight gear 9 will equal two. Any combination of teeth on the input sprocket 14, final drive sprocket 1 1 a, final drive gear 7 and weight gear 9 can be used provided the above formula is always equal to two.

To convey the second force, the weight gears 9 must be turned twice. One turn as the frame gear 5 turns one full turn and once to maintain the synchronous alignment of the weight gears 9. This is achieved by the gearing such that both the first and second forces deliver one turn of the output from one turn of the input no matter which force is responding to the input. This is the one to one gearing. By way of example only, for the one to one gearing of the second force it must be factored in that throughout each rotation of the radial arms 3, the weight gears 9 maintain their orientation, and in doing so revolve around the drive gear 7, such that the drive gears 7 must turn the number of teeth as there are on the weight gears 9 in addition to the one full turn of the drive gear 7 required to match the rotation of one frame gear rotation.

As shown in Figs. 7 and 8, the energy generator consist of a housing frame 1 and a dual function input/output shaft 2 that is rotatably attached to opposite sides of a housing 1 by bearings 22 and define a first axis of orbit. Two identical parallel radial arms 3 are rotatably mounted on the input/output shaft 2 by a pair of bearings 23. An output gear 4 is fixed for rotation to the input/output shaft 2 and located between the radial arms 3. An input sprocket 14 is also rotatably mounted on the input/output shaft 2. Also located between the two radial arms 3 is at least one idler gear 8 which is meshed with the output gear 4, the idler gear 8 rotating on an axle between the pair of radial arms 3.

Two frame gear assemblies are located between the pair of radial arms 3 and define a second axis of rotation. Each frame gear assembly consists of a frame gear 5 meshed with the idler gear 8, the frame gear 5 being mounted by bearings 26 to the frame gear axle 6. Each frame gear axle 6 is 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 one of the radial arms 3. The frame gear assemblies are mounted for orbital movement around the output gear 4 in response to an input on the input sprocket 14. A final drive sprocket 1 1 is fixed to the one end of the frame gear axle 6 extending through the radial arm 3, the final drive sprocket 1 1 receiving input from a looped drive chain 13 from a multiple drive sprocket 12. The multiple drive sprockets 12 is coaxially centred on bearings on the input/output shaft 2 and the multiple drive sprockets 12 are located outside the radial arms 3. The multiple drive sprockets 12 consist of parallel sprockets of the same size for coupling to each final drive sprocket 1 1 . Each final drive sprocket 1 1 is fixed to the one end of the frame gear axle 6. Also fixed adjacent the one end of the frame gear axle 6 is a frame gear axle locking device (not shown) for preventing rotation of the frame gear axle 6 on start-up of the energy generator. The frame gear axle locking device is identical to that described above in relation to the belt drive system.

Each frame gear assembly also include means to convey the 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 1 1 , 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 weight gears 9 and weights 10 on each weight gear 9 provide a means for positioning and maintaining the effective centre of mass of the frame gears 5 at a position or positions synchronously off-centre relative to the centre of the frame gears 5. The means for positioning causes rotation of the frame gears 5 about the second axis of rotation in response to a centrifugal force caused as a consequence of the orbital movement of the 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 associated weights 10 attached to one side of the weight gear 9. Each weight gear 9 is 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 input/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 input/output shaft 2 such that all weights 10 on all weight gears 9 are aligned directly away from the input/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 the output gear 4 via the idler gears 8 and reversing the direction whereby motion of the frame gear 5 is transmitted to the input/output shaft 2 equal to the input of the frame gear assemblies around the output gear 4. In accordance with this arrangement the spin of the output gear 4 is conveyed via the input/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.

As described above each final chain sprocket 1 1 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 assembly (not shown) mounted to the frame 1 . A drive source is applied to the input drive assembly to start the operation of the apparatus to a required revolution rate. While the radial arms 3 are being rotated to the required revolution rate the frame gear axles 6 are restrained from rotation by the frame gear axle locking devices 100 as described above. Once the radial arms 3 have reached the required revolution rate the centrifugal force generated by the rotation of the radial arms 3 releases the frame gear axle locking devices 100 and allows the frame gears 5 to be rotated by the frame gear axles 6. Thereafter a return from the output can be applied to maintain the input drive assembly and compensate for energy losses including the non-recoverable losses of friction within the apparatus. The preferred return system is a variable direct coupling or helical piston coupling 50 as described in further detail below.

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. Once the required revolution rate is attained, and when a clockwise drive is applied to the input drive sprockets 14 and is conveyed via the drive chains 13 to the final chain sprockets 1 1 and through to the drive gears 7 and their meshing with the weight gears 9.

With the frame gear axles 6 locked, the acceleration and friction of the above components 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 input/output shaft 2 and so create centrifugal force to the outer components, and most relevantly the weight gears 9, so that at the required revolution rate (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 all input (less friction) through the meshing of the frame gear 5 to the idler gears 8 to the output gear 4 and to the input/output shaft 2 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 tension between the input and output, at the meshing of the drive gear 7 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 will convey the second driving force, being the product of centrifugal force (a non-input requiring by-product of angular momentum) through the idler gears 8 to the output gear 4 and to the input/output shaft 2 to which it is attached. This is the second force to spin the input/output shaft 2 clockwise.

As described above, with the energy generation apparatus operating at or above the required revolution rate a return from the input/output shaft 2 can be applied to maintain or self power the energy generator apparatus and compensate for energy losses including the non-recoverable losses of friction within the apparatus. This will now be described in relation to Figs 7 and 8 and how it will be implemented for this embodiment. The preferred system for returning output energy is a controlled differential coupling 50 as illustrated in Fig. 6 which connects the input/output shaft 2 to the input in a manner that provides controlled differential coupling, so as to control the amount of offset of the mass within the rotating frame gear 5, by varying the advance of the weights 10 from the radial line and so varying the torque energy generated by centrifugal force.

The helical piston coupling 50 is actuated by a variable hydraulic pressure through a rotary coupling. The hydraulic pressure causes the two helical slotted piston couplings (HSPC) 15 to move apart, thus causing rotational variation between the input/output shaft 2 and the input at the multiple drive sprocket 12. Located within the multiple drive sprocket 12 are two helical slotted piston couplings 15 which are slid over the input/output shaft 2, and free to slide horizontally, while restrained from rotation by horizontal internal slots 19 which accommodate drive pins 110 extending out of the input/output shaft 2. The drive pins 1 10 are located and retained within apertures 28 in the input/output shaft 2. The apertures 28 extend into the input/output shaft 2 but do not extend into the axially extending drilled oil line 17 in the input/output shaft 2 as illustrated in Fig. 6.

To fit the drive pins 110 into the apertures 28 in the input/output shaft 2, both pistons 15 are slid onto the input/output shaft 2 from one end of the input/output shaft 2 and positioned within the multiple drive sprocket 12 with the seals 29 on each piston 15 placed adjacent to each other. The pistons 15 are then slid along the input/output shaft 2 so as to expose the inner pin apertures 28, this allows the insertion of the drive pins 1 10 into the inner pair of apertures 28 in the input/output shaft 2. With the pins 1 10 inserted in the inner pair of apertures 28, the horizontal slot 19 in each piston 15 is located over the pins 1 10 to allow the piston 15 to slide back along the input/output shaft 2 as far as the seal 29 will allow. This then exposes the pair of apertures 28 at the opposing end of the input/output shaft 2 and allows the insertion of the drive pins 1 10 into the apertures 28. With the pins 1 10 inserted into their apertures 28 in the input/output shaft 2 the pistons 15 are slid to where they are located centrally aligned at the oil outlet hole 18 in the input/output shaft 2. At this point the multiple chain sprocket 12 can be slid over the pistons 15 to enclose the pistons 15 on the input/output shaft 2. Helical slots 16 located on the outer surface of each piston 15 accommodate sets of drive pins 21 extending in from the multiple chain sprocket 12 when the multiple chain sprocket 12 is positioned over the input/output shaft 2. The multiple chain sprocket 12 has a length which allows the cylindrical housing to extend over the input/output shaft 2 and the pistons 15. With the multiple chain sprocket 12 placed over the pistons 15 the helical slot 16 on the inside piston 15 is located to allow a first set of drive pins 21 to be inserted through the drive pin threads 20 in the multiple chain sprocket cylinder and be located within the helical slots 16 to lock the inside piston 15 in place.

When the multiple chain sprocket cylinder 12 is inserted over the pistons 15 the outside piston 15 has a tendency to slide inwards along the horizontal slot 19 due to a close tolerance between the inner surface of the multiple chain sprocket cylinder 12 and the outer surface of the pistons 15. This can prove problematic when trying to locate the set of drive pins 21 into the helical slot 16 of the outside piston 15. To overcome this problem a threaded aperture (not shown) is inserted into the end of the outer piston 15 for receiving a fastener therein. The fastener allows the attachment of a cord to the end of the outer piston 15 to allow the helical slots 16 in the outer piston 15 to be easily aligned with the set of drive pin threads 20 in the multiple chain sprocket cylinder 12. This allows the insertion of the drive pins 21 into the helical slots 16 of the outer piston 15. The cord and the fastener are then removed from the end of the outer piston 15.

With both sets of drive pins 21 installed in respective helical slots 16 of the pistons 15 and the pistons 15 positioned on the input/output shaft 2 with inner ends adjacent the oil outlet hole 18 in the input/output shaft 2 and the multiple chain sprocket 12 secured around the pistons 15 the device 50 provides controlled differential coupling, so as to control the amount of offset of the mass within the rotating frame gear 5, by varying the advance of the weights 10 from the radial line and so varying the torque energy generated by centrifugal force.

Helical slots 16 are located on the outer surface of the pistons 15 in opposing directions and accommodate drive pins 21 extending in from the multiple drive sprocket 12. When the HSPCs 15 are centrally inserted within the multiple drive sprocket 12 and lateral retaining thrust stoppers or collars installed on the input/output shaft 2 maintain the multiple drive sprocket 12 alignment. A hydraulic pressure line is connected to an external pump via a rotary union to variably pressurise a drilled oil line 17 located inside the input/output shaft 2. Located centrally between the two HSPC’s 15 is an oil outlet 18 with each HSPC 15 having appropriate oil seals 29 to prevent the loss of hydraulic oil. An increase in pump pressure applied through the rotary union coupling causes the two HSPC’s 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. This makes available rotational variation in the direct drive coupling from the input/output shaft 2 to the input at the multiple drive sprocket 12.

With drive transferred from the input/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. When the hydraulic pressure is removed the pistons 15 will slide together and so reduce or remove the rotational advancing and the powering to the multiple drive sprocket 12, such that the energy generator apparatus power can be reduced or stopped. Springs may be installed against the stoppers to assist in returning the HSPC’s 15 to the rest position when hydraulic pressure is reduced or removed to reverse rotational advancing.

The rate of change in advance can be built into the helical piston coupling 50 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 12 proportionally to the curved shape. Since the apparatus can be run in either direction the HSPC’s 15 should be fitted so that the helical slots 16 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 the relative rotational connection can be random. But rotational connection from the output to the input is critical. This is set when connecting the drive chains 13. With the HSPC 15 resting together the drive chains 13 must be installed to connect the multiple drive sprocket 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 energy generator apparatus. In this position the energy generator apparatus can be started by the input drive assembly 35 such as a starter motor applied to the multiple drive sprocket 12 or the input/output shaft 2. With the multiple drive sprocket 12 locked to the input/output shaft 2 by the controlled differential coupling 50, and when operating revolutions 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 energy generator apparatus increases rpm at the output. At this point input drive assembly 35 can be turned off or disengaged leaving the energy generator apparatus to self-power or recycle power to the input via the controlled differential coupling 50.

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 energy generator apparatus.

When the energy generator is running at or above the required revolution rate with the controlled differential coupling 50 installed the revolution rate from both the transfer of the input revolutions to the output (the first force) must be the same as the revolution rate from harnessed centrifugal force (the second force). The embodiments described have a unique gearing ratio which maintains the rotation of the radial arms 3 and the spin of the frame gear 5.

Each one full turn of the input shaft 30 or the multiple chain sprocket 12 will cause the drive chains 13 or input drive belts 33 to act as a solid and turn the radial arms 3 one full turn regardless of any sprocket size 12, 14. Each time the radial arms 3 rotate 360 degrees with the frame gear 5 held by the weight gears 9 and unable to turn on its own axis, it will turn the output gear 4 one full turn. This is fed back to the input shaft 30 or multiple drive sprocket 12 through the controlled differential coupling 50, in the belt drive system of Figs 1 to 5 by coupling the output shaft 40 to the input shaft 30 and in the idler gear system of Figs. 7 and 8 by coupling the output/input shaft 2 to the multiple drive sprocket 12. In the idler gear system of Figs. 7 and 8, gearing must be set to deliver the train of the output power equally from both the mechanical input, the first force and the catalytic second force, since both forces are interconnected at the output, both must be geared one to one. That is one turn of the multiple drive sprocket 12 no matter what size will always turn the radial arms 3 one revolution if the final drive sprocket 1 1 is held from turning. This is the input delivered to the output as the first force.

In accordance with the principle of the invention, it is the continuous offsetting of the weight gears 9 that cause the frame gears 5 to receive torque from centrifugal force and so spin the frame gears 5. Accordingly one turn of the weight gears 9 will turn the frame gears 5 one revolution when the radial arms 3 are stationary, and when the first force has rotated the radial arms 3 one revolution, this adds one spin to the frame gear 5 relative to any line of centrifugal force. This added spin must be allowed for in the gearing to the weight gear 9, meaning that the weight gear 9 must spin twice for each revolution of the radial arms 3. 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 so that the input revolution rate will match the output revolution rate with twice the power. Three weight gears 9 per frame gear 5 should always be used because if only two weight gears 9 per frame gear 5 are installed, the inner weight 10 will have far less centrifugal force than the outer weight 10. This makes it far harder for the inner weight 10 to respond to its offset and spin out to the outer position. This may not matter at low revolutions as any load will cause greater offset of the weights 10 but becomes increasingly relevant if revolutions are increased. The problem is overcome by spacing three or more weight gears 9 around each frame gear 5.

The energy generator of the present invention must have a gearing ratio which maintains the rotation of the radial arms 3 and the spin of the frame gear 5 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 will always be the same as the input rate and preventing either building to the revolutions of the input while depleting the revolutions of the other. Gearing must be such that when the energy generator is running with or without a mechanical return system such as a HSPC the revolution rate from both the transfer of the input revolutions from the multiple chain sprocket 12 to the output (the first force) must at all times be the same as the revolution rate from harnessed centrifugal force (the second force) with the combined revolution rate delivered to the output always the same as the input.

Incorrect gearing can prevent the energy generator from operation. As an example where the final drive sprocket 1 1 of a unit should be 28 teeth but it is fitted with a 22 tooth final drive sprocket 1 1 it makes it far harder to turn than a 28 tooth as it should be for 1 :1 , in which case the input would go to rotating the radial arms 3 with less torque to offset the weights 10 to balance the output load, causing the frame gear 5 to spin slower (and stop spinning) than the radial arms 3 and add less power from centrifugal force.

Alternatively if the final drive gear 7 was larger, say 38 teeth it would be far easier to turn and so offset the weights 10 beyond the torque to balance the output load causing the frame gear 5 to spin faster and therefore the radial arms 3 would slow and drop centrifugal force

Therefore for a one to one gearing ratio the second force must always be that the number of teeth in one turn of the multiple chain sprocket 12 divided by the number of teeth on the final drive sprocket 1 1 multiplied by the number of teeth on the final drive gear 7 and this divided by the teeth on the weight gear 9 will equal two. Any combination of teeth on the multiple chain sprocket 12, final drive sprocket 1 1 , final drive gear 7 and weight gear 9 can be used provided the above formula is always equal to two.

The energy generator of the present invention has a gearing ratio which maintains the rotation of the radial arms 3 plus the spin of the frame gear 5 to the output gear 4 and prevents either building to the revolutions of the input while depleting the revolutions of the other. Gearing must be such that when the energy generator is running with or without a mechanical return system such as a HSPC 15, the revolution rate from both the transfer of the input revolutions from the multiple chain sprocket 12 to the output (the first force) must at all times be the same as the revolution rate from harnessed centrifugal force (the second force) with the combined revolution rate delivered to the output is always the same as the input. Incorrect gearing can prevent the energy generator from operating in accordance with the present invention. As an example where the final drive sprocket 1 1 of a unit should be 28 teeth but it is fitted with a 22 tooth final drive sprocket 1 1 it makes it far harder to turn than a 28 tooth as it should be for 1 :1 gearing ratio, in which case the input would go to rotating the radial arms 3 with less torque to offset the weights 10 to balance the output load, causing the frame gear 5 to spin slower (and stop spinning) than the radial arms 3 and add less power from centrifugal force.

Alternatively if the final drive gear 7 was larger say 38 it would be far easier to turn and so offset the weights 10 beyond the torque to balance the output load causing the frame gear 5 to spin faster and therefore the radial arms 3 would slow and drop centrifugal force. For the energy generator to operate in accordance with the present invention a 1 :1 gearing ratio is required.

Consideration must be given to the actual weight of the weights 10 as this interacts with the revolutions per minute (rpm) of the radial arms 3 and resultant centrifugal force and momentum.

They weights 10 are the sole component that are moved to offset from the radial line through the frame gears 5 which makes the frame gears 5 spin. Heavy weights will resist being offset and so direct all input revolutions to the radial arms 3 and so further increase centrifugal force and further resist offset. This requires a greater output load which intern requires a matching input. Lighter weights will offset more easily and provided they are not forced beyond 90 degrees will maintain the torque on the radial arms 3 while adding torque to the frame gears 5 equal to the output load.

Fig. 9 is an illustration of a frame gear 5 in three states of spin while in orbital 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 7 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. Also, Fig. 9 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. The two weight gear system 60 has a radial line of the frame gear 5 is represented by line 51 and torque line of the offset weight is shown as 52.

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 will 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 applied to the weights 10, it follows that the second force applied by the energy generation 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 1 1 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 to one gearing ratio or it will cause a change in input to output ratio that will trigger internal tensions that 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 second force less any frictional loss, is gain, and so can be used to power external applications.

For the belt drive system of Figs 1 to 5, the centrifugal force at any operating revolution rate can be increased by extending the radius of orbit of the weights 10 from the output shaft 40. For example, by constructing the energy generator by locating the frame gears 5 further out from the output shaft 40 and providing a longer coupling output drive belt 41 and input drive belt 33. If transfer of torque of the frame gear 5 to the output 2 is by idler gears 8 as in the idler gear system of Figs. 7 and 8, the use of larger idler gears 8 or odd numbers of multiple idler gears 8 may be used in line.

The capacity of the energy generator apparatus to handle greater power input can also 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 pedestals, 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 the energy generator.

Alternatively, further multiple energy generators on a common output shaft 2, 40 would multiply the output torque. In use the support frame 1 , 1 a could be modified to house at least three or more energy generators. Multiple energy generators may be run in series for any reason and only needing one low capacity controlled differential coupling 50 to be installed on the first energy generator of the series of coupled energy generators, so that power control of the first and/or all downstream energy generators can be made from one low capacity controlled differential coupling 50 without the need to install controlled differential coupling 50 to any other energy generator.

In order to self-power or recycle energy from the output to the input, the spin of the output gear or output sprocket 4 can be conveyed via the output shaft 2, 40 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.

The weights 10 in the energy generator have been provided as a 1 Kg weight mounted on the weight gears 9. However, the weight 10 may be varied to suit a particular energy generator to suit its dimensions of length, intended revolutions and strength and the input and output power that is intended. The offset position of weight 10 from the centre of weight gears 9 must be sized such that the physical size of the weight gear 9 and the final drive gear 7 allows sufficient clearance for the weights 10 to clear the frame gear shaft 6 when the frame gear 5 rotates.

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 an increase in rpm 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.

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. By way of example only, and as defined in Newtonian mechanics, the centrifugal force is an inertial force that appears to act on all objects when viewed in a rotating frame of reference. Newton's Third Law states that for every applied force there is an equal and opposite force. In a reference frame rotating about an axis through its origin, all objects, regardless of their state of motion, appear to be under the influence of a radially (from the axis of rotation) outward force that is proportional to their mass, to the distance from the axis of rotation of the frame, and to the square of the angular velocity of the frame. Or simply, centrifugal force is an inertial force that resists changing the direction or velocity of the object.

The present invention is intended as a description of the principles of power generation and its method of 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 8 or locating them at a different point may change the mechanics of the operation but not 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, 40 or from the input shaft 30 to the final drive sprocket 1 1 a.

Centrifugal force at any operating rate of revolution can be increased by extending the radius of orbit of the weights 10 from the output shaft 2, 40, by any method such as constructing the energy generator apparatus by locating the frame gears 5 further out from the output shaft 2, 40 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 or sprocket 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 6 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 3. It also eliminates the use of output gears 4, 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 assembly will amplify power in accordance with the principles of the energy generator apparatus, as claimed three or more weight gears 9 can be used on each frame gear assembly. 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 9), 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 shaft 2, 40. 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 all spinning of the frame gear 5.

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 each frame gear 5. This therefore increases the power capacity of an energy generator.

It is important that the energy generator should have at least a speed reducing system such as the power regulator; additionally a braking system can be installed on the output to prevent uncontrolled 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 shaft 2, 40 so as to provide a support against the centrifugal load on the shaft 2, 40 and frame gear bearings 26 that support the frame gears 5.

The 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 shaft 2, 40. 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 with 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. The braking system could be used to reduce or even stop any power to the output. The control of power may be integrated with any power or braking systems.

The band may be used for a lubricating point for the frame gear 5 whereby 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 2, 40 to the radial arms 3 to the frame gear shaft 6 and out to the final drive gear 7. Alternatively the radial arms 3 could contain a reservoir of lubricant from which centrifugal force would power transfer to the frame gear shaft 6 and on to the final drive gears 7.

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. 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.

When multiple amplification of power is required, this can put excessive load on shafts and bearings, it is therefore most desirable to build all moving parts from a material which is strong and is a lightweight material with only the weights 10 being formed from a heavy metal material. The principles of the energy generator apply to any different configurations of energy generator 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, aircraft, or any other mechanical device including use in space or anywhere. The energy generator of the present 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 with far less components 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 greenhouse gasses, 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 side 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 energy generator 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 produce centrifugal force. Elongation forces will 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. The energy generator apparatus can be run without any mechanical return system such that input power from any source can be increased at the output so as to reduce the cost, pollution or energy source of 100% generation.

An embodiment of the present invention provides an energy generator which is driven by a drive belt system which overcomes the problems of gears binding to prevent the conveyance of revolutions and power to the output.

The present invention requires a unique gearing ratio in order to maintain the rotation of the radial arms and the spin of the frame gear and prevents the rotation of the radial arms and the spin of the frame gear building to the revolutions of the input while depleting the revolutions of the rotation of the radial arms and the spin of the frame gear. The gearing ratio of the energy generator is such that when the energy generator is running with or without the mechanical transfer system, the first force defined as the revolution rate from both the mechanical transfer of the input revolutions from the input to the output is the same as the second force defined as the revolution rate from harnessed centrifugal force with the combined revolution rate delivered to the output always the same as the input.

Therefore, the gearing ratio must be a one to one ratio. In order to achieve the one to one gearing ratio the gearing of the second force must always be that the number of teeth in one turn of the input sprocket divided by the number of teeth on the final drive sprocket multiplied by the number of teeth on the final drive gear and this divided by the teeth on the weight gear will equal two.

To convey the second force, the weight gears must be turned twice. One turn as the frame gear turns one full turn and once to maintain the synchronous alignment of the weight gears. This is achieved by the gearing such that both the first and second forces deliver one turn of the output from one turn of the input no matter which force is responding to the input. This is the one to one gearing.

The present invention also provides a frame gear shaft locking device which holds the frame gear shaft from turning until the radial arms rotate at a revolution rate which is fast enough for centrifugal force to hold them out. Once the revolution rate has been achieved the frame gear locking device is set to release the frame gear shaft in response to the centrifugal force and allow the energy generator to harness centrifugal force and add power. The present invention also provides a means for isolating or disengaging the input drive assembly when the energy generator is operating at or above the required revolution rate. The input drive assembly can be disengaged to further reduce drag and wear. This is also important when the energy generating apparatus is in self powering operation.

The present invention uses centrifugal force which unlike gravity does not deplete when energy is consumed because it is radially applied and constantly renewed. The present invention can be located or installed most anywhere and operate independent of wind, sunlight or any other green energy power supply and so can be a base energy supply. Using only centrifugal force as an energy source there is no fuel transport costs or risk of supply failure. Power can be increased by constructing the invention with longer radial arms with the frame gear mounted further from the output shaft such that at the same revolutions the velocity of the weights orbit is increased.

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.