Centrifugal motor (CM)
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A two-stage power generator which operates solely on re-circulating fluid. In the first stage a spinning container develops centrifugal force which pressurizes the fluid inside, creating a hybrid form of energy—Potential Energy in Motion (PEM). In the second stage the spinning pressurized fluid drives a turbine forward relative to its own motion i.e. the PEM is reconverted into Kinetic Energy as it also imparts its own speed. By using mechanical advantage in the second stage to increase the force applied to the turbine and incorporating the speed of the spinning pressurized fluid, the power output of the turbine is greatly enhanced; substantially exceeding the power needed for continuous operation i.e. the power required to continuously accelerate the fluid necessary to keep the container refilled and spinning at operating speed.

Bowles, John Charles (Marietta, GA, US)
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John Charles Bowles (MARIETTA, GA, US)
1. A machine which uses spinning fluid pressurized by centrifugal force to drive a turbine making possible energy output in excess of energy input; a machine capable of enhancing both turbine driving force, depending on the level of mechanical advantage employed, and turbine velocity depending on the augmentation resulting from the velocity of the spinning fluid. A centrally operated mechanism activated by centrifugal force, which controls the flow of pressurized fluid out of a Centrifugal Motor's pressurization container, preventing flow until radial velocity reaches a predetermined level and also preventing flow when radial velocity exceeds a higher predetermined level.



While the CM is in operation, centrifugal force pressurizes fluid accelerated by impellers inside a spinning cylindrical container. The pressurized fluid, spinning along with the container, then spews upward through small ports in the periphery of the container lid driving forward a turbine mounted above. The expelled fluid then falls to the bottom of the housing enclosure to be re-circulated back into the system.

The turbine's relative velocity is determined by 1) the rate at which the pressurized fluid spews up out of the ports and 2) the pitch of the turbine blades i.e. the mechanical advantage employed. The turbine's total or true velocity is equal to its relative velocity plus the radial velocity of the pressurized fluid at the periphery of the container.

The turbine's available power greatly exceeds that needed to keep the CM running i.e. to accelerate the necessary volumes of fluid and keep the cylindrical container spinning at operating speed. Such a “perpetual motion” machine was previously thought impossible; how could a machine actually produce energy? Energy is the ability to do work i.e. apply force over a distance. When Kinetic Energy (the energy of movement) is converted into Potential Energy (stored energy) and back again into KE, ordinarily there is at least some loss of energy due to friction. But the CM actually increases both the force and distance elements of the energy/work equation in two stages. In the first stage centrifugal force (artificial gravity) pressurizes fluid and produces a hybridform of energy i.e. Potential Energy in Motion. In the second stage, the PE of the spinning pressurized fluid is reconverted into KE as it drives a turbine. Using mechanical advantage in this re-conversion process, the force imparted to the turbine is increased many fold. With this force magnification, as is the case with use of mechanical advantage generally, the distance over which the turbine moves is correspondingly reduced; but only relative to the movement of the pressurization container. Since the actual or true movement of the turbine includes this relative movement plus the movement of the pressurized fluid at the periphery of the container (motion imparted in the first stage) the distance element of the energy equation is also increased; greater force plus greater distance equals greater energy!


FIG. 1—represents a side view of the CM through a translucent enclosure. All of the principal elements are shown. At the very bottom is the bearing into which the central shaft is inserted. Just above, the centrifugal pump, along with its lower input section, are depicted. The two recirculation hoses are shown connecting the centrifugal pump with the fluid distributor housing. Just below this housing the water level is shown where it will appear while the CM is operating; and just above is the pressurization container. Above this container is the turbine with its gear top center. Next to and parallel with the upper portion of the central shaft is the drive shaft with both its lower and upper gears shown. Meshing with the upper gear the central shaft gear is shown. Depicted at the very top is the plastic cone which will be used to start the model.

FIG. 2—shows an angular view of the upper-most of 6 sections of the pressurization container.

FIG. 3—shows an angular view of the turbine.

FIG. 4—shows a vertical cross section of the turbine, its bearing and a portion of the central shaft; clearance provided for the container lid's collar can also be seen.

FIG. 5—shows the top side of the pressurization container's lid.

FIG. 6—shows the under-side of the pressurization container's base plate.

FIG. 7—shows the fluid distributor cylinder. The central portion is machined out to a depth of ¾″ to provide clearance for the base plate's collar.

FIG. 8—shows both the high and low speed control sections of the shut-off mechanisms which will be affixed to the central shaft within the pressurization container.

FIG. 9—shows one of the eight slide sections of the shut-off mechanisms.


The CM model, as described in the abstract, will be started using a variable speed electric drill equipped with a special tool designed to engage the inverted cone atop the central shaft. When the central shaft is turned, it will spin the drive shaft which in turn will spin the turbine wheel. The pressurization container, the centrifugal pump impeller and the fluid distributor's rotating cylinder, all attached to the central shaft, will also spin. Fluid will fill the pressurization container and excess air will be expelled through small holes near the center of the lid. After only a few seconds the container will be completely filled, all excess air will have been expelled and speed can be increased to operating levels. The RPM of the CM, which will be geared to gradually increase, will be moderated by the periodic engagement of the high speed shut-off mechanism.

The blades of the turbine, as they pass directly over the ports, will be pushed forward by the force of the escaping pressurized fluid as it is being reconverted into KE. The pressurized fluid inside the container will exert force in all directions equally i.e. it will be neutral with respect to forward movement of the container.

By using mechanical advantage in the re-conversion process, the force element of the kinetic energy can be increased many fold while the velocity element (relative to the spinning container/pressurized fluid) is of course correspondingly reduced. Assuming a mechanical advantage of six to one, the turbine's relative velocity will be equal to one-sixth the expulsion speed of the fluid spewing upward through the ports.

But the much higher true turbine velocity will actually determine energy output. The advantage of the CM is that its true turbine velocity will include its relative velocity plus the peripheral velocity of the container/pressurized fluid. Using mechanical advantage, the CM's turbine will benefit from increased force without suffering a compensating loss of distance/speed, previously thought unavoidable.

The CM will be capable of generating many times the power needed for continuous operation i.e. the power needed to continuously accelerate the volumes of fluid necessary to maintain operating speed. This is what makes the CM so revolutionary and so important as a new source of usable energy.

Assuming an 80% level of efficiency (relatively modest for a turbine), a CM of the size set forth in this description operating at a container velocity of 2400 RPM can be expected to continuously produce a net of more than 500 HP.

    • Water weighs 0.03611111 per cubic inch
    • The area of a 24″ D circle is over 450 sq in. Thus the weight of water in the cylinder is over 16 pounds per inch of depth.
    • Fluid Pressure at the periphery of the container is 310 ppsi. The theoretical center of gravity of any wedge of fluid inside the container is 8.9 inches from the center. At 40 RPS this center of gravity is traveling at 186.4 Feet Per Second (FPS). Therefore the fluid pressure in pounds is 310 ppsi i.e. 186.4×186.4÷32×12÷8.9×16÷75.4.
    • Based upon Torricelli's Law the expulsion speed of water pressurized at 310 ppsi is 214 feet per second? The depth of water necessary to produce a pressure of 310 ppsi is 715 feet i.e. 310÷0.036111÷12. The speedofan object falling 715 feet is 214 FPS. √{square root over ((715÷16.08))}×32.16.
    • The weight of water expelled each second is 78.8 lbs. The eight ports less the portion covered by the width of the turbine blades is 0.85 sq. inches. Thus the total water expelled per second is equal to 2,183 cubic inches i.e. 0.85×214×12; its weight is 78.8 lbs (2,183×0.0361111).
    • To accelerate 78.8 lbs to a speed of 251 FPS every second requires the equivalent of 141 HP. The force required in pounds is 618 i.e. Mass×Acceleration÷32 or (78.8×251÷32). Applying this force at an average velocity of 125.5 FPS yields a HP requirement of 141 i.e. 618×125.5÷550.
    • At mechanical advantage of 6 to 1, the force imparted to the turbine blades by the pressurized water is 6×310×0.85 or 1,581 pounds. The radial velocity of the turbine wheel is 286.6 Feet Per Second (the 251 FPS velocity of the container plus an additional 35.6 FPS relative to the container i.e. 214 FPS÷6). Thus the energy potential of the turbine is 823 HP i.e. 286.6×1,581÷550.