Detailed Description

Free Energy Devices

Referring to the drawings in detail, in which the same numbers refer to the same parts in each drawing, the numeral 10 designates a supply bottle or tank for a compressed elastic fluid, such as air. Preferably, the air in the bottle 10 is compressed to approximately 1,500 p.s.i. The compressed air from the bottle 10 is delivered through a suitable pressure regulating valve 11 to the chamber 12 of a high pressure tank 13 on one side of a free piston 14 in the bore of such tank. The free piston 14 separates the chamber 12 for compressed air from a second chamber 15 for an inelastic fluid, such as oil, on the opposite side of the free piston. The free piston 14 can move axially within the bore of the cylindrical tank 13 and is constantly self-adjusting there to maintain a proper volumetric balance between the two separated fluids of the system. The free piston has the ability to maintain the two fluids, air and oil, completely separated during the operation of the system.

The regulator valve 11 delivers compressed air to the chamber 12 under a pressure of approximately 500 p.s.i. The working inelastic fluid, oil, which fills the chamber 15 of high pressure tank 13 is maintained under

500 p.s.i. pressure by the expansive force of the elastic compressed air in the chamber 12 on the free piston 14. The oil in the chamber 15 is delivered to a prime mover 16, such as an oil turbine, through a suitable supply regulating or throttle valve 17 which controls the volume of pressurised oil delivered to the prime mover.

The turbine 16 embodies a stator consisting of a casing ring 18 and end cover plates 19 joined to it in a fluid-tight manner. It further embodies a single or plural stage impeller or rotor having bladed wheels 20, 21 and 22 in the illustrated embodiment. The peripheral blades 23 of these turbine wheels receive the motive fluid from the pressurised chamber 15 through serially connected nozzles 24, 25 and 26, connected generally tangentially through the stator ring 18, as shown in Fig.3. The first nozzle 24 shown schematically in Fig.1 is connected directly with the outlet of the throttle valve 17. The successive nozzles 25 and 26 deliver the pressurised working fluid serially to the blades 23 of the turbine wheels 21 and 22, all of the turbine wheels being suitably coupled to a central axial output or working shaft 27 of the turbine 16.

Back-pressure sealing blocks 28, made of fibre, are contained within recesses 29 of casing ring 18 to prevent co-mingling of the working fluid and exhaust at each stage of the turbine. A back-pressure sealing block 28 is actually only required in the third stage between inlet 26 and exhaust 31, because of the pressure distribution, but such a block can be included in each stage as shown in Fig.1. The top surface, including a sloping face portion 30 on each block 28, reacts with the pressurised fluid to keep the fibre block sealed against the adjacent, bladed turbine wheel; and the longer the slope on the block to increase it's top surface area, the greater will be the sealing pressure pushing it against the periphery of the wheel.

Leading from the final stage of the turbine 16 is a low-pressure working fluid exhaust nozzle 31 which delivers the working fluid, oil, into an oil supply chamber or reservoir 32 of a low pressure tank 33 which may be bolted to the adjacent end cover plate 19 of the turbine, as indicated at 34. The oil entering the reservoir chamber 32 from the exhaust stage of the turbine is at a pressure of about 3-5 p.s.i. In a second chamber 35 of the low pressure tank 33 separated from the chamber 32 by an automatically moving or self-adjusting free piston 36, compressed air at a balancing pressure of from 3-5 p.s.i. is maintained by a second pressure regulating valve 37. The pressure regulating valve 37 is connected with the compressed air supply line 38 which extends from the regulating valve 11 to the high pressure chamber 12 for compressed air.

Within the chamber 32 is a gear pump 39 or the like having its input shaft connected by a coupling 40 with the turbine shaft 27. Suitable reduction gearing 41 for the pump may be provided internally, as shown, or in any other conventional manner, to gear down the rotational speed derived from the turbine shaft. The pump 39 is supplied with the oil in the filled chamber 32 delivered by the exhaust nozzle or conduit 31 from the turbine. The pump, as illustrated, has twin outlet or delivery conduits 42 each having a back-pressure check valve 43 connected therein and each delivering a like volume of pressurised oil back to the high pressure chamber 15 at a pressure of about 500 p.s.i. The pump 39 also has twin fluid inlets. The pump employed is preferably of the type known on the market as "Hydreco Tandem Gear Pump," Model No. 151515, L12BL, or equivalent. In some models, other types of pumps could be employed including pumps having a single inlet and outlet. The illustrated pump will operate clockwise or counter-clockwise and will deliver 14.1 g.p.m.

Free Energy Devices

at 1,800 r.p.m. and 1,500 p.s.i. Therefore, in the present application of the pump 39, it will be operating at considerably less than capacity and will be under no undue stress.

Solar Stirling Engine Basics Explained

Solar Stirling Engine Basics Explained

The solar Stirling engine is progressively becoming a viable alternative to solar panels for its higher efficiency. Stirling engines might be the best way to harvest the power provided by the sun. This is an easy-to-understand explanation of how Stirling engines work, the different types, and why they are more efficient than steam engines.

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