Abstract
In accordance with the present invention an apparatus is provided to maintain separate upper and lower water levels in a bi-level tank. The purpose here is to maintain tank configurations for the water portion of an air/water pathway in the tank that will be followed by a buoyant power module during its electricity generating work cycle. During an operation, the module enters the tank and raises the lower water level. The apparatus is then expanded to displace a volume of water in the tank with a volume of air, which raises the upper water level. Subsequently, when the module leaves the tank, the upper water level is lowered. Further, the apparatus is collapsed to drop the lower water level back to its original level in the tank. Thus, the bi-level tank is reconfigured to receive another module, for another duty cycle.
Claims
1. A Machine for generating electricity using the earth's gravitational field, which comprises: a bi-level tank having an upper tank with an upper water level and a lower tank having a lower water level, for receiving and decelerating a power module in the lower tank after the power module falls through air under the influence of gravity, and for returning the power module through the upper tank under the influence of its buoyancy to return the power module to an elevated start point for another cycle; a piston plate having an upper surface and an underside, wherein the piston plate defines a perimeter surrounding a flat plate area A on the upper surface of the piston plate; a flexible enclosure submerged in the lower tank for holding a volume of water within the enclosure at a predetermined pressure H, wherein the enclosure has an opening attached to the perimeter of the piston plate to surround the area A on the upper surface of the piston plate, wherein the enclosure is stabilized against a stationary structure inside the lower tank at a predetermined distance from the upper surface of the piston plate, and wherein the enclosure defines an axis perpendicular to the piston plate; a cylindrical shaped bellows surrounding a hollow chamber between a first open end and a second open end of the bellows, wherein the first end of the bellows is attached to the perimeter of the piston plate to surround an area A on the underside of the piston plate; a receiver tank for maintaining compressed air at a pressure in a range H′±, wherein H′± is greater than the pressure H in the enclosure wherein the flexible enclosure is expandable when the bellows receives a pulse of compressed air from the receiver tank to raise the piston plate and the water level of the upper tank, and wherein the flexible enclosure is collapsible upon exhausting the compressed air pulse from the bellows to the atmosphere to lower the water level of the lower tank; an exhaust chamber connected between the bellows and the receiver tank, wherein the exhaust chamber has a pressure valve for controlling fluid communication between the exhaust chamber and the receiver tank and an exhaust valve for controlling fluid communication between the exhaust chamber and the atmosphere; and an output power system including a linear electric generator, wherein the linear electric generator has a length and is positioned for an interactive engagement with the power module, wherein the power module is vertically guided by gravity for its interactive engagement with the linear generator along the length of the linear generator to generate electricity while the power module is thereby engaged with the linear generator.
2. The Machine of claim 1 further comprising a control unit connected to the pressure valve and to the exhaust valve of the exhaust chamber for a sequential valve operation of a first configuration wherein the pressure valve is OPEN and the exhaust valve is CLOSED to introduce a pulse of compressed air from the receiver tank into the chamber for moving the piston plate in a first direction to radially expand the enclosure outwardly from the axis, a second configuration wherein both the pressure valve and the exhaust valve are CLOSED to hold the piston plate stationary, and a third configuration wherein the pressure valve remains CLOSED and the exhaust valve is OPEN to exhaust compressed air from the exhaust chamber and into the atmosphere to collapse the enclosure and move the piston plate in a second direction to begin another sequential valve operation.
3. The Machine of claim 2 wherein the work performed by the piston plate during the first valve configuration is mgH, wherein m is the mass of a predetermined volume of water, V.sub.w, in the water tank, g is the influence of gravity, and H is a pressure head height of water in the water tank, and wherein the sequential valve operation is determined by movements of the piston plate during a defined duty cycle Δt, and the duty cycle Δt comprises: a first phase between a time t.sub.0 and a time t.sub.1 for the first valve configuration; a second phase between the time t.sub.1 and a time t.sub.2 for the second valve configuration; and a third phase between the time t.sub.2 and a time t.sub.3 for the third valve configuration.
4. The Machine of claim 3 wherein, as a portion of the duty cycle Δt, the first phase is equal to 1/xΔt, wherein the work required to be performed by the piston plate during the entire duty cycle Δt is mgH/Δt, while the actual work performed by the piston plate during the second phase and the third phase is zero, to establish the input power to operate the piston plate during the duty cycle Δt equal to 1/x mgH/Δt.
5. The Machine of claim 4 wherein the output power system generates an output power proportional to a buoyancy factor B of the power module and wherein the power module falls through air from an elevated start point under the influence of gravity and engages with the linear generator to generate electricity before falling into the lower tank where it decelerates for a return through the upper tank under the influence of its buoyancy to return the power module to the elevated start point to begin another duty cycle Δt, and wherein the power generated by the power module during the duty cycle Δt is equal to BmgH.
6. The Machine of claim 5 wherein the output power BmgH of the output power system is compared with the input power 1/xmgH/Δt of the input power system to determine an efficiency for generating electricity.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
(1) The novel features of this invention, as well as the invention itself, both as to its structure and its operation, will be best understood from the accompanying drawings, taken in conjunction with the accompanying description, in which similar reference characters refer to similar parts, and in which:
(2) FIG. 1 is a conceptualized perspective view of a Machine for generating electricity in the earth's gravitational field with a submerged displacement device of the present invention shown in phantom for context location purposes only;
(3) FIG. 2 is a cross section view of a displacement device in accordance with the present invention when configured at the beginning of its duty cycle Δt, wherein the pressure valve is OPEN and the exhaust valve is CLOSED to initiate a duty cycle Δt, at the time t.sub.0;
(4) FIG. 3 is a diagrammatic view of components in the Machine, with the components separated into separate input and output energy systems;
(5) FIG. 4A-4C show sequential configurations for the displacement device during successive phases of a displacement device's duty cycle, namely, a power input phase (FIG. 4A), a holding phase (FIG. 4B), and an exhaust phase (FIG. 4C);
(6) FIG. 5 is a graph of the pressure profile of compressed air against the underside surface of the piston plate during a displacement device duly cycle Δt;
(7) FIGS. 6A-6C show the respective power requirements for work done during a displacement device duty cycle Δt, namely, work done by the air compressor to maintain a pressure H′± in the receiver tank (FIG. 6A), work required by the piston plate to lift a predetermined volume of water ΔV.sub.w (FIG. 6B), and the work harvested from a power module (FIG. 6C), and
(8) FIG. 7 is a diagram of the Machine components that are monitored and operated by a control unit for the present invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
(9) Referring initially to FIG. 1, a Machine to be driven by the present invention is shown and generally designated 10. As shown, the Machine 10 includes a bi-level tank 12 which has a lower tank 14 and an upper tank 16 that are connected for selective fluid communication with each other. FIG. 1 also shows a power module 18 that is intended to transit the bi-level tank 12 on a pathway 20 which is indicated by the arrows 20a-d. In more detail, the pathway 20 includes an air portion 22 where the power module 18 falls under the influence of gravity. As it falls the power module 18 engages with an electric generator 24 to generate electric power. FIG. 1 further shows that the pathway 20 also includes a water portion 26. On this water portion 26 of the pathway 20, the module 18 first decelerates and then returns by its buoyancy to an elevated start point 28 where it begins a next cycle. FIG. 1 also shows the intended location for a displacement device 30 of the present invention, i.e. submerged in the lower tank 14 of the bi-level tank 12.
(10) FIG. 2 shows, in a cross-section view, that the displacement device 30 includes a skirt 32 (i.e. enclosure) which is connected between a wall of the bi-level tank 12 and a piston plate 34. Structurally, the skirt 32 is cylindrical shaped with open ends; it is centered on an axis 36; and it is preferably made of a flexible, impervious, non-stretchable material. Within the skirt 32 a skirt volume V.sub.s is established between the bi-level tank 12 and the piston plate 34. An important requirement of the skirt volume V.sub.s is that it maintains a constant volume, at a constant pressure, during an operation of the displacement device 30. As intended for the present invention, the constant pressure equal to H in the skirt volume V.sub.s will be maintained by a pressure regulator 38, wherein H is the head height of water in the upper tank 16.
(11) Still referring to FIG. 2, it is to be appreciated that the piston plate 34 has an upper surface 40 and an underside 42. Both the upper surface 40 and the underside 42 of the piston plate 34 have a substantially same plate area A, and the piston plate 34 is centered on the axis 36 for a coaxial alignment with the skirt 32. As shown, an open end of the skirt 32 is connected to the periphery around the area A on the upper surface 40 of the piston plate 34. Below the piston plate 34, its underside 42 is connected to a bellows 44.
(12) The bellows 44 is a hollow cylindrical shaped structure with open ends. An upper end of the bellows 44 is connected to the periphery around the area A on the underside 42 of the piston plate 34. The lower end of the bellows 44 is connected to an exhaust chamber 46. With its connections between the piston plate 34 and the exhaust chamber 46, the bellows 44 is coaxially aligned with the skirt 32. Thus, with the action of the bellows 44, the piston plate 34 can be moved up and down along the axis 36 through the distance s shown in FIG. 2. For purposes of the present invention, it is important that the distance s be established so that a movement of the piston plate 34 will pass through a volume, sA, that is equal to the volume V.sub.m of a power module 18.
(13) With specific reference to the exhaust chamber 46, FIG. 2 shows that the exhaust chamber 46 essentially includes a pressure valve 48 and an exhaust valve 50. The primary purpose of this exhaust chamber 46 is to control air pressures against the underside 42 of the piston plate 34 by operating the valves 48 and 50 in accordance with a predetermined protocol. In the disclosure provided below, the valves 48 and 50 are represented by three circles. Hereinafter, all OPEN valves are depicted in the Figures as a line of three circles. On the other hand, all CLOSED valves are depicted by three dots.
(14) FIG. 3 is a depiction of the present invention as two different energy systems, separated by a dashed line 52. To the left of the dashed line 52 is an input energy system generally designated 54, and to the right of the dashed line 52 is an output energy system generally designated 56. For the present invention, although they are interactive, the energy systems 54 and 56 are structurally and functionally considered individually. The only link between the two energy systems 54 and 56 is that both are partially submerged in a same body of water, i.e. the lower tank 14 of the bi-level tank 12. As noted above in the assumptions presented in the Summary of the invention, the present invention assumes there is no transfer of energy between the input energy system 54 and the output energy system 56.
(15) In FIG. 3, it is seen that the input energy system 54 includes an air compressor 58 that provides compressed air for a receiver tank 60. Further, it is shown that the receiver tank 60 is connected in fluid communication with the exhaust chamber 46 via pressure valve 48. As intended for the present invention, compressed air pressure in the receiver tank 60 is maintained within a pressure range H′± at all times. This pressure range H′± is monitored by a regulator 64 which is connected to, and controls, the operation of the air compressor 58. Specifically, the pressure range H′± must always be equal to or greater than the head height H in the upper tank 16, and in V.sub.s of the skirt 32.
(16) It is also shown in FIG. 3 that the output energy system 56 essentially includes the bi-level tank 12, the power module 18 and the linear generator 24. In contrast with each other, the input energy system 54 provides an input power represented by the arrow 66, while the output energy system 56 provides an output power represented by the arrow 68. Obviously, the purpose of the present invention is to ensure that the output power 68 exceeds the input power 66. As recognized by the present invention, a valid comparison of these input and output powers 66/68 can be best understood by evaluating an operation of the displacement device 30.
(17) The understanding of an operation for the displacement device 30 will be best appreciated by first considering the sequence of side drawings which are shown respectively in a FIGS. 4A-C. In the side drawing of FIG. 4A, a module 18 is shown immediately after it enters the lower tank 14. At this point, an access valve 70 is CLOSED behind the module 18 and a transfer valve 72 ahead of the module 18 is OPEN. In this configuration, water pressure in the bi-level tank 12 will equal H. In the side drawing of FIG. 4B, the module 18 is shown, still in the lower tank 14, but positioned to enter the upper tank 16. The side drawing of FIG. 4C then shows conditions in the bi-level tank 12 after the module 18 exits the lower tank 14 and has entered the upper tank 16. Note: it is only after the module 18 has exited the lower tank 14, and the transfer valve 72 is CLOSED, that the access valve 70 is OPEN to receive the next module 18 (not shown) in sequence. Importantly, to receive the next module 18, with the access valve OPEN, the water pressure in the lower tank 14 has lowered from H to a single atmospheric head height “h”.
(18) With reference back to FIG. 4A, the displacement device 30 is shown configured at a time t.sub.0 to begin a displacement device 30 duty cycle Δt. For this configuration, at the time t.sub.0 the exhaust valve 50 of the exhaust chamber 46 is CLOSED and the pressure valve 48 is OPEN. The consequence of this is that a pulse of compressed air 74 (shown as an arrow) enters the bellows 44 from the receiver tank 60 via the conduit 62, at a pressure H′±. As disclosed above, H′±>H. Thus, the resultant pressure differential causes the piston plate 34 to be moved upwardly through the distance s.
(19) FIG. 4B shows the displacement device at a time t.sub.1 in the duty cycle Δt. At the time t.sub.1, the piston plate 34 has been raised through the distance s, and through a volume equal to sA=V.sub.m. Two important changes in the configuration of the displacement device 30 have occurred between the times t.sub.0 and t.sub.1 which are particularly noteworthy. For one, the skirt 32 has been radially expanded. In effect, this expansion displaces a volume of water equal to sA=V.sub.m in the lower tank 14. For another, the pressure valve 48 is CLOSED at the time t.sub.1. Indeed, both the pressure valve 48 and the exhaust valve 50 need to be held CLOSED at the same time during the interval of time from t.sub.1 to t.sub.2. The reason here is that between the times t.sub.1 and t.sub.2 the piston plate 34 must be held stationary, and not lowered, until after the module 18 has cleared the transfer valve 72 and is completely inside the upper tank 16. It is important to note that between t.sub.1 and t.sub.2, while the piston plate 34 is held stationary, no work is done.
(20) As shown in FIG. 4C, at the time t.sub.2 in the duty cycle Δt of the displacement device 30, the exhaust valve 50 is OPEN while the pressure valve 48 remains CLOSED. With the exhaust valve 50 OPEN, and the pressure valve 48 CLOSED, the pulse of air 74 under the piston plate 34 is exhausted into the atmosphere. As this pulse of air 74 is exhausted from the exhaust chamber 46, the effect is for air pressure under the piston plate 34 to immediately lower from the pressure H′± to the much lower atmospheric pressure h at the time t.sub.3. In review, it is important to note that the piston plate 34 essentially does no work from the time t.sub.1 to the time t.sub.3 in the duty cycle Δt of the displacement device 30.
(21) For a review of the air pressures against the underside 42 of the piston plate 34, FIG. 5 shows the variations in these air pressures during a duty cycle Δt of the displacement device 30. With reference to FIG. 5, recall that the duty cycle Δt begins at t.sub.0 when the module 18 enters the lower tank 14 and pressure in the tank equals h. The work portion of the duty cycle Δt extends only during the time between t.sub.0 and t.sub.1 while the piston plate 34 is being raised to lift a volume of water equal to sA=V.sub.m. It is this lifting action that causes the skirt 32 to expand radially and thereby displace the volume of water equal to sA=V.sub.m. In this action, the skirt 32 is merely an intermediary that functions to transfer a predetermined volume of compressed air from the receiver tank 60 into a displacement volume of water in the lower tank 14. In this transfer, the work done by the piston plate 34 merely reconfigures the skirt 32 for its intended purpose. It is with this reconfiguration that a volume of water equal to sA=V.sub.m is displaced from the lower tank 14 into the upper tank 16. It must be appreciated that all of the work done between the receiver tank 60 and the lower tank 14 begins at the air compressor 58.
(22) A breakdown of the work done by individual components of the displacement device 30 is shown sequentially in FIGS. 6A-C. With cross reference back to FIG. 5, FIG. 5A shows that the air compressor 58 effectively works continuously during the duty cycle Δt, starting from the time t.sub.0 and ending at the time t.sub.3/0, wherein the subscript 3/0 is used to indicate the end of one duty cycle Δt and the beginning of the next sequential duty cycle Δt. During this time, the air compressor 58 does mgH worth of work with an input power 66 equal to mgH/Δt.
(23) FIG. 6B shows that the piston plate 34 also does mgH worth of work. But the piston plate 34 does all of its work within a portion 1/x of the work cycle Δt at a power equal to mgH/1/xΔt. With reference to FIG. 6C, it is seen that during a duty cycle Δt the module 18 has been engaged with the linear generator 24. Considering its buoyancy factor B, the module 18 has generated an output power 68 equal to BmgH/Δt.
(24) A power comparison between the output power 68 and the input power 66 of the Machine 10 will be best appreciated by considering the specific power that is, and is not, required during the duty cycle Δt.
(25) At the time t.sub.0, the start time of a duty cycle Δt, the receiver tank 60 of the displacement device 30 holds compressed air at a pressure H′±. With the pulsing of a volume of compressed air V.sub.c from the receiver tank 60 during the first interval 1/xΔt, the power to raise the piston plate 34 is equal to mgH/1/xΔt. After the first pulse, however, no more work is done by the piston plate 34 for the remainder of the duty cycle Δt. It is important to remember that the work 1/xmgH has been done by the air compressor 58 during each interval 1/xΔt within the duty cycle Δt. On the other hand, from a power perspective, during the entire duty cycle Δt, the piston plate 34 receives an input power 66 from the receiver tank 60 that is equal to mgH/Δt. Stated differently, the piston plate 34 does the same amount of work, mgH, during the pulse, 1/xΔt, as it does during the entire duty cycle Δt. Accordingly, the input power 66 requirement from the receiver tank 60 for the Machine 10 can be compared with 1/xmgH/1/xΔt.
(26) With reference to FIG. 7, an operation of the Machine 10 is controlled by a control unit 76. As shown for this purpose, the control unit 76 is electronically connected with the receiver tank 60, the exhaust chamber 46, and the piston plate 34, to provide the input power 66 for the input energy system 54 of the Machine 10. Specifically, the control unit 76 is connected in a two-way communication with the receiver tank 60 and the air compressor 58 to thereby maintain a compressed air pressure of H′± in the receiver tank 60 during successive duty cycles Δt. Further, the control unit 76 provides direct control over the pressure valve 48 and the exhaust valve 50 of the exhaust chamber 46. Also, the control unit 76 provides direct control over the piston plate 34, via the exhaust chamber 46, to coordinate an operation of the displacement device 30 with an operation of the bi-level tank 12.
(27) FIG. 7 also shows that the control unit 76 is in two-way communication with the bi-level tank 12, primarily for the purpose of monitoring the transit of a power module 18 along the air/water pathway 20. More specifically, by monitoring movements of the piston plate 34, and its movements that determine the duty cycle Δt of the displacement device 30, the control unit 76 controls the respective water levels of the lower tank 14 and the upper tank 16. With this control, the output power 68 is maintained for the input energy system 54.
(28) While the particular Energy Balanced System for Generating Electric Power as herein shown and disclosed in detail is fully capable of obtaining the objects and providing the advantages herein before stated, it is to be understood that it is merely illustrative of the presently preferred embodiments of the invention and that no limitations are intended to the details of construction or design herein shown other than as described in the appended claims.
