Ocean water pressure energy generation system

Abstract

A rigid cylinder structure is vertically positioned at sea bottom,so that the top of the cylinder's surface is at a depth of 300 meters below sea surface. This surface constitutes the upper face of a piston which moves within the cylinder,when it is exposed periodically by way of a shiftable opening & closing valve,which is located at the top of the cylinder,it intervenes,then exposes the piston at regular intervals to sea water pressure of 30 atm. Being basically a Pascal Hydrolic system,this pressure is transmitted through a pipe to a larger area piston,but in addition to the Pascal system, the multiplied pressure is in turn is used to pressurize a gas above it & compresses it to {fraction (1/9)} of it's initial volume. The result of compression is a 14 fold temperature increase-adiabatic. The high pressure & high temnperature as is then contained in a closed cycle second upper volume,which has just the exact dimensions for the gas which is compressed to {fraction (1/9)} of its initial volume. Here,the temperature & pressure is maintained constant as a result of a special valve & repeated compressions which supply additional pressure,which at each compression peak,lets pressure input in,but does not let a pressure loss when large piston makes its downward,hence decompression motion. Also within this volume is the spiraling pipe which attains thermal equilibrium within this space which contains the working gas. And the working gas,which has no condensation throughout the repeated cycles turns the turbines. Having no condensation & on the contrary being very strongly insulated,system eliminates the loss of internal energy. The minor loss of internal energy is more than compensated with each compression.

Description

CROSS REFERENCE TO RELATED APPLICATIONS

[0001] Not Applicable.

STATEMENT REGARDING FEDERALLY SPONSERED RESEARCH OR DEVELOPEMENT

[0002] According to Congressional Research Service;Department of Energy FY1999 Research and Development Budget: Description and Analysis,written by Richard E. Rowberg,under the heading Solar and Renewable Energy R & D.,it is written: “An important function of this program is to help the private sector develop promising new renewable energy technologies for the commercial market.” (page 6,) In same report under the heading Climate Change Technology Initiative, following is written: “Studies sponsered by DOE over the past year along with the PCAST study argued that new energy supply and technology in selected areas could lead to significant reductions in carbon emissions at little or no net cost.” (page 18.) The DOE,Office of Industrial Technologies Inventions and Innovation Program funds up to Usd 200.000 for promosing projects demonstrating both energy related efficiency innovation and future commercial market potential.

REFERENCE TO MICROFICHE APPENDIX

[0003] Not Applicable.

BACKGROUND OF THE INVENTION

[0004] This invention relates to methods of deriving energy from ocean water. It is more particularly concerned with a technology of utilizing renewable-environment friendly energy, specifically the sea water pressure that exists at certain depths within oceans. It is based on the continous availability of ocean water pressure. This invention aims to utilize the water pressure, using a special apparatus to compress a low density,highly compressable gas in order to increase the temperature of such gas by increasing it's Pressure. And then to utilize the heat of the pressurized gas to increase pressure of another gas,which would be the working gas. The system can also be utilized for Central heating of residences or commercial structures at shores.

[0005] Various methods of generating power from ocean waters have been proposed or developed. The ones that are in a marine environment are OTEC,Ebb & Tide systems,and Wave energy.

[0006] More specifically related to renewable energy sources and to the ocean environment,the following concepts and methods for generating energy from oceans are current state of the art. From U.S. Pat. No. 5,899,066 Date of Patent: May 4,1999 Buoyancy and Thermal Differentials Energy Generator,lnventor: Angel Brasea-Flores. The system is based on conversion of energy into another energy using a working gas or generative fluid moved by thermal differentials. System also uses Vertical Buoyancy pressure. From U.S. Pat. No. 5,582,691 Date of Patent: Dec. 10,1996 Ocean Thermal Energy Conversion System,lnventors: Robert J.Flynn & Jonathan D'E.Coony. This is an improved OTEC system,(in all aspects,)one out the many being a combined evaporator/condenser,which maintains a constant low pressure. A more efficient OTEC system. From U.S. Pat. No. 6,100,600 Date of Patent: Aug. 8, 2000 Maritime Power Plant System with Processes for Producing,Storing and Consuming Regenerative Energy,Inventor: Tassilo Pflanz. This system is very comprehensive & has a multiple approach,where a floating or anchored structure with plurality of energy convertors are proposed. And et-al.

[0007] The main prior art OTEC,requires a minimum 20 C water temperature differential between layers of sea water. This limits the applicable geographic regions to only certain latitudes. Furthermore,OTEC is expensive due to expensive heat exchangers & long & large diameter pipes. Bio-fouling is another problem OTEC faces. Ebb & Tide systems also have geographic constraints. Even at most favorable locations,the investment required are usually too costly, relative to the energy that could be generated. This is usually the result of low elevation differences. On average,it is 10-12 meters at Fundy Bay,9 meters at Severn & 8 meters on Rance. And these elevations depend on Moon orbit conditions. Wave energy systems could not prove to be a Globally efficient energy generation system,because these systems are mostly dependent on wind directions & adjustment of systems to wind direction makes these systems inefficient. OTEC systems have costly requirements;because these require warm water flows of 7450 Kg/Sec/MWe & overall great water displacements & also strong pumping needs-operational costs. Prior art systems also need cold water pipes with large diameters (57 feet per 100 MWe,) which all add to high costs. And et-al.

[0008] Therefore,there is a need for a low cost system,less complicated for the energy generation purposes which utilizes the ocean water & which has low operation costs. The continous Non-variable water pressure that increase with depth has been the extensive concern of diving & sub-marine engineering. In fact,water pressure has been considered an undesireable side of the oceans,especially after several hundred meters. But it has not been utilized for energy generation.

[0009] This system would have no constraints such as minimum temperature differential between warm & cold,no need of massive vertical structures or large reservoirs,no use of or problem about the dissolved gases of sea water,no major vulnerability to bio-fouling,no constraint or requirement about salinity differentials between lower & upper layers of sea water,no constraint about weather conditions,and most important,no need to reach depths of 500 meters or more.

[0010] It is known that the sea water pressure increases with increasing depth. The atmospheric pressure at sea level is only 14.7 lb/square inch. But for example at 100 meters depth, this pressure rises to 10 atm/square inch. At 300 meters,(91.44 feet,)there exists a continous 30 atm/square inch pressure. Furthermore,because invention is able to avoid all of the following constraints: a. Does not require sea water temperature differential as OTEC,b. Does not need deep water levels of 500 m or more,c. Does not depend on ebb & tide or currents. d. Cost of production & operation would be efficient,especially given the fact that the world is covered 71% with oceans. It means system could be applied all over the world with a certain efficiency & economies of scale.

SUMMARY OF THE INVENTION

[0011] My invention,to be described in more detail hereinafter,is based mostly on sea water pressure,which is continous & a non-variable natural force that exists within all large water masses on earth within seas & lakes. It solves problems that prior arts have;the need for costly complicated structures,for these are based on sea water temperature gradients of different depths,which require large water masses to be pumped,or salinity differentials,dissolved gases, wave energy,or currents. It does not depend on external thermal properties of sea water and therefore has no geographic limitation. It utilizes the natural high water pressure at 300 meters,to obtain a kinetic compression force mechanically,utilizing the non-compressibility of liquids & then this mechanic force compresses a compressible gas. The main principles of invention are based on: 1. The non-compressibility of fluids,as in an enclosed fluid,as within the Pascal Hydrolic, 2. Compressibility of gases,gas of low density,high compressibility,3. High efficiency thermal equilibrium with limited energy loss,lsochoric. 4. Excluding previous pressure-thermal process, which uses the continous & Cost Free Water Pressure,net energy conversion efficiency for high pressure gas (kinetic through turbine-generators becomes mechanic to electric,) is mechanic to electric conversion which has 97% net efficiency.

[0012] In order to utilize as large a pressure as possible from the natural source and without having to establish the system at depths that are too deep and also to achieve multiplication of the pressure available at a certain depth, the system utilizes a large special under water Pascal Hydrolic.

[0013] As known,Pascal Hydrolic is a force-multiplier device. At 300 meters,there would be continously available water pressure of 30 atm/square inch. If one smaller cross sectional area piston has a surface area of 107.6 square feet & the larger piston of the Pascal Hydrolic has a 215.2 square meters feet area,and only the smaller area piston is subjected periodically to the 30 atm/square inch pressure,then the pressure applied on this 107.6 square feet would be multiplied in accord to Pascal's Law. At 300 meters,it becomes 30×2=60 atm/square inch at large piston. (if large piston area is twice the small area piston.)

[0014] Furthermore,if the upper side of the large piston faces an enclosed & limited initial volume of air or another low density gas with high compressibility,then this gas would be compressed to as small a volume as {fraction (1/9)} of its initial volume. When compressed to such a smaller volume, and if initial temperature of gas would start at 50 C,the compressed gas temperature would rise to 700 C. However,the adiabatic temperature increase & the maximum temperature of above 650 C would be directly correlated to duration & ratio of each compression. So,Frequency of compressions would be vital to reach an Isochoric condition within upper space in the long run. Each new thrust of the small area piston,so also the thrust of large piston would re-compress the gas once again with a compression ratio of 9,repeatedly. An average of 650 C to obtain a high pressure gas is sufficient. Strong insulation,pressure regulation & compressing the gas repeatedly would result in continous average of 650 C. Isochoric within upper volume (16b.)

[0015] Thermal equilibrium stable isochoric condition would equate gas temperature to that of closed cycle circulated gas which would run within the high pressure volume. Continuity of equilibrium would be due to the periodic motions of the small area piston. Before the large area piston would start to make the move downward,the valve below the compression chamber would close,and so the pressure & heat would remain within a constant range.

[0016] This would avoid a sudden decline of temperature of the gas due to expansion. If the system was designed to allow the compressed gas to expand back to its initial volume,which would be the case if the system was not with a valve at the bottom face of the compression chamber volume. (upper most volume,initial gas volume where compressed into,) then the compressed gas would expand back to initial volume,with each large area piston's downward move. To solve this problem & in order to achieve two objectives at once with approximate concurrent timing,(ie.the timing of the closing of the valve and the start of the large piston's downward motion,)the said valve at the bottom of the compression volume,(which has a space to be compatible to the {fraction (1/9)} compression ratio & is designed to maintain compressed gas at {fraction (1/9)} of it's initial volume,) would close the valve and the downward move of the large area piston would start. The ability to move the small area piston back up & down repeatedly would utilize each time 60 atm/square inch pressure,as a multiplied force to other side-on the large area piston repeatedly. So,system would always be able to provide sufficient pressure for the aim to obtain adiabatic temperature increases repeatedly,which at pressure chamber would translate to contant Isochoric.

[0017] Since condensation does not exist,energy loss is avoided & system is not water based. Good insulation & a relatively small volume & small decrease of temperature & keeping pressure gigh for overall volume/cycle would achieve minimum energy loss due to recycling.

[0018] How would the small area piston of the Pascal Hydrolic Press be able to move back & forth,so that it can repeatedly provide the high pressure of about 60 atm to compress the gas above the larae piston? The small area piston would face a 30 atm at 300 meters depth.

[0019] As the valve infront of the small area piston that faces the sea water would open,the 30 atm pressure would push the piston down,thereby increasing pressure at the other side to 60 atm/square inch. When the small area piston would reach its lower most limit,the valve on top of the small area cylinder would close,so would make the sea pressure ineffective temporarily.(FIG.2)

[0020] A pair of adjusted level entry pipes into pump volume,facilitate continuity (as water level due to discharge would diminish gradually,)are connected to the side of the cylinder that holds the sea water volume. The pump then would discharge the trapped water between the piston upper surface & below the valve which closes. Valve function is to discontinue external pressure.

[0021] Given system sizes,discharge volume would be only a total of 1.06 cubic feet. The fact that the air pressure at sea surface,where this volume would be pumped vertically out is only 1 atm,whereas the water pressure that would be trapped between the outer valve of small area piston & the small area piston would be greater than 1 atm,would make the discharge fast and would require only minor quantity of water to be pumped (FIG. 2.)

[0022] Furthermore,as this 1.06 Cubic feet sea water would be discharged,the enclosed fluid of the Pascal Hydrolic Press would start to push the smaller area piston into the space that would constitute a vacuum as the sea water of 1.06 cubic feet would be discharged. Because, as the external pressure would not apply on the small area piston & furthermore as the water would be discharged out fast from the 1.06 cubic feet volume,the weight of the water below the large area piston cylinder side.would be heavier.even at the begining of the discharge,than the 1.06 cubic feet,which would be discharged out completely. So.as soon as water would start to leave the volume above the small area piston,which would be 1.06 cubic feet at the start, the weight above the small area piston would be an exponentially declining weight,as apposed to the oil-hydrolic that is located below the large area piston within the large area cylinder,which is approximately 4.24 cubic feet. Therefore,small area piston would rise back to its initial starting point just below the small area valve (FIG.2)

[0023] When piston would reach this upper most starting point,the valve that made the sea water pressure ineffective would open against the piston would face once again 30 atm/square inch pressure that moves it down,thus moves larger piston up. A certain frequency of repeating this back & forth motion would mean repeatedly re-occuring compressions at the other side of the Pascal Hydrolic. Which would be able to keep an average high temperature,to increase pressure of gas in pipes circulated through the compression chamber's upper most volume. Where the chamber gas would be periodicaly compressed & kept at a high temperature.(FIG.3)

[0024] As working gas would reach about 270 atm pressure at about 675 C,it would turn turbines-generators. (FIG.3) The gas that would pass the turbines would then have lower temperature,as a result of kinetic energy transfer to turbines. (FIG.7) Strong insulation on return cycle is vital.

BRIEF DESCRIPTION OF THE DRAWINGS

[0025] FIG.1 is shown in perspective of the completion of first stage,that is,what distance the motion of the small cross sectional area (10 square meter,)piston of the Pascal Hydrolic Press makes & it is depicted at the lower most position as it completes the move. (Set in motion downward,by the sea water pressure of 30 atm/ square inch.) This picture shows entire structure, excluding recycling loop & heat transfer pipes,representing the initial input,the system adapted to utilize and increase the sea water pressure,which moves small piston that moves a large piston. Small piston pushes the hydrolic fluid through and large piston compresses the gas repeatedly.

[0026] FIG.2 is shown in perspective as enlarged partial view of the invention adapted to utilize pressure difference between the sea surface low pressure & the limited sea water volume that would be trapped between the closed upper valve on top of the cylinder & the small area piston, with higher pressure,after this sea water volume would have completed the push of the small area piston down initially,for the purpose of discharging this volume. This part of the Pascal Hydrolic Press constitutes the smaller cylinder in which the small area piston of the Pascal Hydrolic Press would move periodically up & down. This picture shows how this volume of sea water, which initially made the small area piston to move down,would be discharged in a short time,to facilitate the up & down motions of the small area piston.

[0027] FIG.3 is shown in perspective as enlarged partial view of the pressure chamber,where a gas of low density-large compressibility would be compressed,which would result in the rise of the temperature of this gas. This picture shows how the gas pipes that would be routed through this limited volume,where the gas within the pipes would reach high pressure. The temperature regulation cycle also shown in perspective with as pump(31,) & gas temperature regulator (32.) Pressure control loop also shown (17).

[0028] FIG.4 Is a cross sectional & enlarged partial view of external & internal materials of the system. Shown only at pressure input side of system.

[0029] FIG.5 is a cross sectional side view representation of the entire system,inclusive pressure chamber & pressure chamber's valve which closes & opens,to keep internal pressure continously at an optimal maximum range by seperating the compression volume from the rest of the compression large area piston up & down motion allowance volume,periodically.

[0030] FIG.6 is a diagramatic view of the gas line & the generators which it would activate.

[0031] FIG.7 is a diagram of the gas exit & gas closed cycle pressure adjuster,with after turbine exit gas pump (31,) & gas pressure regulator (32,)which benefits from the sea water externally to get only a very limited cooling of the exit gas used,which is an enclosed system.

DETAILED DESCRIPTION OF THE INVENTION

[0032] As shown in FIG.1 .a piston of 107.6 square feet area 10,makes repeated moves within a cylinder with non-corrosive external coating of h=49.2 ft,with radius r=5.8 ft. Research hitherto indicates that concrete or polyvinyl chloride might be the cost effective material for this external coating 11 for internal sides,different but non-corrosive polymer such as fiber or composites such as carbon-carbon that is coated 34,35 is proper. For moving pistons,recently invented zero friction carbon surface 35,could be utilized. (Argon lab.) Large piston must also be heat resistant.

[0033] The piston would exert force on an internal fluid (Oil)12,the force that would apply on piston is external sea water with 30 atm/square inch. This force would exert pressure to the hydrolic fluid within the vertical cylinder of the Pascal. The pressure p=f/a is transmitted through the 229 ft connecting pipe 13,which enables a very great pressure to be produced by the application of a small force. (External water pressure.) Force proceeds onto a larger cylinder 14,of non-corrosive material,with r=8.3 ft & h=49.2 ft,equiped with larger piston of area,215.2 square feet,pictured in compression position 15.(FIG.1) Pascal hydrolic press being a force multiplier,would increase the 30 atm/square inch water pressure to 60 atm hydrolic pressure at larger piston side of 107.6 square feet 15. Both pistons have rods which connect lower & upper sections 36,37.

[0034] Initially,the gas above large piston would be at a pre-compression pressure of 2 atm.at 50 C. As the compression would start,closed cycle gas 16a,would be forced into gas volume 16b,through the valve 28,16a & 16b is seperated by surface 40,since compressions are repeated,gas compressed to {fraction (1/9)} of its initial volume would reach 700 C,14 fold temperature rise. The compression of the gas at each compression stroke of the larger piston 15,would be a time limited adiabatic temperature rise which can be repeated at specific frequencies.

[0035] Because the process within compression area 16a,is adiabatic & in constant high pressure volume is Isochoric 16b,to achieve thermal equilibrium with the gas closed cycle circuit 20, which as system parameter must reach 700 C for superheated gas,following must be satisfied: The limited temperature decrease proportion of working gas volume 29,to total volume of working gas 20,is only 10%, of total working gas at any moment/cycle. Ex-turbine gas at 500 C, would be 40% of the total working gas/cycle. If so.50% ex-turbines would equal to gas passage rate/cycle. So,during one cycle,50% of working gas would Not be subjected to a temperature disequilibrium state/cycle. While 10% would have a very limited,a ⅓ energy loss,40% would loose ¼/cycle.

[0036] As follows: During one cycle completion time of working gas 20,0nly 10% of the total working gas would decline in temperature by {fraction (1/3.)}29. 50% of working gas 20 would remain in thermal equilibrium: a) As 270 atm,675 C pre-turbine gas,turbines with voltage synthesization,b) 40%, 500 C ex-turbine gas, (175 C loss to kinetic energy, transfer to turbines)c). Only 50 C loss due return/cycle.it would return at 450 C,at about 180 atm. This is sine qua non of system;only 10% of working gas goes through ⅓ energy loss/cycle. Consequently,of the total volume of working gas 2O,50% superheated gas remains in thermal equilibrium state/cycle. Heat transfer from pre-turbine to ex,would be minor,since 175 C difference would limit heat current from hot to colder.

[0037] So,thermal equilibrium volume 16b,would have only a minor loss of internal energy.(−175 C of 50%,out of 100% working gas at 675 C/cycle.) For this,total quantity of volume of working gas 20, must be such a quantity as to facilitate said proportions as percentages of the total.

[0038] This invention would make it possible to keep a high pressure gas on a continous basis. with frequently repeated adiabatic processes. Then it would become volume limited 16b,Isochoric through which gas pipes 20,would be circulated within high pressure volume 16b. So this volume 16b,would facilitate a volume for thermal equilibrium,(16b with 20,)(FIG.3) Compressed gas 16b, would reach thermal stability in the long run,since temperature would be maintained at a specific range due to repeated compressions of larger piston 15,of Pascal hydrolic.which repeatedly would supply heat with each new compression. (Frequency every 45 minutes.) At north latitudes where sea water temperature is lower.frequency of compressions have to be increased to about every 20 minutes. Piston 15,would have compression ratio of {fraction (1/9)} within 16a. Compressed gas would be pushed up with high pressure into 16b,through valve 28.therefore becoming limited volume Isochoric,where pressure would be kept always high within,16b. Above Threshold temperature of said gas,thermal equilibrium would be attained. For maximum temperature within this volume 16b,must reach 700 C,the supercharged gas temperature 20,is 675 Celsius & exit to temperature regulation is 500 C,& the lower temperature gas 29,retums at 450 C(10% of working gas.)so the Treshold temperature,above which superheated gas could be obtained is 540 C & slightly above, within volume 16b. The limited 10% lower temperature return gas at 450 C,would be critical in system efficiency in order to reach thermal equilibrium and to reach critical temperature of 500 C to obtain a supercharged working gas. Strong insulation on return cycle path has vital importance.

[0039] Small piston 10,would repeatedly move back to initial position,as valve 18,closes. So,external water pressure would become ineffective during discharge. Prior discharge,water would be in between upper face of small piston & the lower face of the valve 18,the discharge volume of 1.06 cubic ft 26,would flow into the pump 24,then to the sea surface. The valve 18,moves into a protective container 25,at open mode. So,discharge system would take out sea water 26, each time small piston 10, reaches lower end.

[0040] Furthermore,the compression chamber volume above 16b,would have a valve 28,below it. Which would close,before large area piston would make its downward move. This is to avoid an expansion of the gas back to its initial state. However,since the pressure of gas in 16b would be greater than the gas pressure of 16a,in the long run as a system parameter,being counter to the gas pressure interaction in light of the second law,(gases seep through an opening from a high pressure region to a low pressure one,)it would require a Special Valve 28,that would work one way only,that would make gas to enter 16b from 16a,despite higher pressure of 16b. This is possible since for only a limited time during the compressions,the pressure within 16a,would far exceed the high pressure within 16b. Then the pressure of volume 16a,would decline fast,down to near atmosperic pressure,after the start & during downward motion of large piston 15. (Volume 16a,would face adiabatic compression then expansion,but pressure in 16b has to be constant.)

[0041] More specifically,the invention causes repeated adiabatic processes that results in temperature rise of a gas. Which then could be maintained within a range of high temperature within a limited volume becoming Isochoric therein,to raise pressure of another closed cycle gas 20,with entry 19, in FIG. 1,only this entry depicted,)and would be circulated through the compression volume 16b.The gas closed cycle pipe system 20,would be independent from pressure conditions in the compression volume 16b,therefore the internal condition of gas pipes would be Isobaric.

[0042] The Isochoric volume 16b,would be kept as an Isochoric volume because of the repeated compressions of the larger piston 15,which would compress the gas repeatedly(every 30 or 45 minutes. Note,in compressed position;piston 15,remains at that compression position until it is time again for the piston 15,to make the downward motion.)and thereby would keep the pressure high & temperature of compression gas 16b,at a range between 600 C minimum & 700 C maximum throughout all cycles.

[0043] Strong insulation & the mentioned structure with a valve 28,which eliminates a gas expansion out of 16b,would stabilize pressure. (During large piston 15,downward move.) The thermodynamic condition of the gas pipes 20,that would be circulated within this compressed space 16b,would be Isobaric,because the circulation pipes would not be influenced by the high pressure within the Isochoric volume 16b. Within this compression chamber 16b,the gas pipes would be circulated 20,within which pressure of said gas rises. This gas would reach three turbines 41,through distributor 33,& three pipes 30,at high pressure of 270 atm which come from gas pipe 20,which is in a strongly insulated protective container 21. Then gas would go through turbines(3 units,41.) Gas having mostly lost its kinetic energy would exit turbines 41 ,at 500 C,and would first reach the gas pump 31 ,then gas temperature regulator 32,& then main temperature adjuster 23,which would only cause a very limited temperature-pressure decline. Turbines 41 ,are in cylinders 22.

[0044] Entire system would be fixed to ocean bottom with legs 27,thirty two point eight feet above bottom. The specific improvement of this system,compared to OTEC for example is that,system does not depend on sea water thermal differentials between close to surface & deep waters. Said system does not depend on natural variables like wind,solar.ebb & tide or currents,which all are more or less confined to only certain geographic regions. For example OTEC can only be efficient between north & 20 south latitudes. The important features of Ocean Water Pressure Energy Generation System(OWPGS,)have the following specific improvements:

[0045] 1. The input force which makes the system function is the continous Non-Variable & abundantly available-Renewable Cost Free sea water pressure.

[0046] 2. The natural pressure is multiplied by a simple & established process of Pascal.

[0047] 3. Since the system has no explosion or burning process involved,system is more stable both thermally & mechanically & has no exhaust-greenhouse gas emission problems,

[0048] 4. The system parameters & structure does not require very complicated parts that would not need a big investment.

[0049] 5. The cost of operation of said system would be efficient;71% of the planet is covered with seas.

[0050] 6. Because it is not based on thermal differential of different layers of ocean or lake water,system could be applied even at northern latitudes.

[0051] 7. It is 100% environment friendly.

[0052] 8. Because the system has no condensation process,of the total working gas 20,only 10%(29,) is subject to minor energy loss of ⅓,so loss from overall internal energy is very limited & the minor loss can be compensated by a much greater proportion with each mechanic move of the large piston 15,which would repeatedly supply compressed high pressure gas from volume 16a to volume 16b,to keep pressure & temperature within volume 16b,constant.

[0053] 9. Because the system is 300 meters below sea surface it is naturally protected from surprise air offense, in the case of war or terrorist attack.

[0054] 10. System control station could be at a nearest point at the shore,where system could be monitored electronically from the coast-since 300 meters depth is usually not very far from coastline.

[0055] 11. Because the system would be within water & also due to the Pascal mechanics involved within the system,plus due to the fact of utilizing a gas,not a fluid,as working gas;system would have almost no Gravity constraint. Gravity,which on land reduces all of the machine efficiencies & is a major constraint that slows down,demands extra energy input,or creates other complications.

BEST MODE OF CARRYING OUT THE INVENTION

[0056] Refering to FIG. 1,reference numeral 10 designates the input side piston,on which sea water pressure of 30 atm.,repeatedly provides the input force to the Pascal system. Specifically,downward pressure applied on piston 10,which is within a cylinder 11,which stands vertically & piston 10,makes down & up motions therein,thereby forcing Hydrolic oil 12,as hydrolic pushes through a pipe 13,to multiply the force applied from this side to a larger area piston 15,(both pistons have connecting rods 36 & 37,which connects a lower piston to another above it. The rod moves through a middle surfaces 38 & 39,which seperates the environment of lower piston with that of upper. These rods also serve to transfer the motion of one piston below,directly to the one above.) Large area piston 15,(upper piston,)compresses repeatedly a low density-compressible gas above it,which is within a closed cycle. (FIG. 7.) As it gets compressed to {fraction (1/9)} of it's initial volume,this gas goes through an adiabatic temperature increase of 14 fold in a limited space 16a.(FIG. 3 & 7)

[0057] Another volume 16b,is just above the volume 16a. Between 16a & 16b is a special valve 28, which at the peak of compression of piston 15,lets high pressure-high temperature gas at 700 C to flow into this upper volume 16b. But the same valve 28,does not let the compressed,heated gas to escape back to volume 16a,as piston 15,starts its downward motion. So,within volume 16b,which has a space to accommodate the {fraction (1/9)} compressed gas,the pressure & temperature is kept at a constant-Isochoric,or approximate Isochoric(with very minor fluctuations of pressure & temperature, but constant volume.)

[0058] Within this volume 16b,second closed cycle working gas is circulated through spiraling pipes 20,in order to have a thermal equilibrium within, 16b. This working gas within closed cycle 20,turns turbines at 675 C,with 270 atm. Same gas having left most of it's kinetic energy to turbines,at 500 C, & 180 atm. would exit turbines.

[0059] Then closed cycle working gas is recycled through very strongly insulated pipes & pumped into the system again. The energy loss due to cycling is very limitedas the system does not have a condensation process & instead very strong insulation keeps heat generated. Repeated compressions of large area piston 15,provides a greater amount of additional pressure-heat which compensates the minor energy loss due to recycling of the working gas. Following formula explains the initial Adiabatic process due to compression of the large area piston 15,compressing the gas volume 16a,above it with a compression ratio of 9: 1 T ⁢   ⁢ 2 = T ⁢   ⁢ 1 ⁢ ( V ⁢   ⁢ 1 / V ⁢   ⁢ 2 ) Y - 1 = ( 555 ⁢ K ) ⁢ ( 9 ) 0.40 = ( 7770 ⁢ K ) = 700 ⁢   ⁢ C . ( 1 )

[0060] (If air with Gamma=1.40 is compressed. Another low density highly compressible gas,with no oxygen content may have to be used,or oxygen of air has to be taken out.) Then,this pressurized hot gas is directed & entrapped within the Isochoric volume 16b. Here,the working gas pipes 20, reach thermal equilibrium at 675 C,with 25 C loss due to reaching thermal equilibrium state. To calculate the pressure: 2 p ⁢   ⁢ 2 = p ⁢   ⁢ 1 ⁢ ( V ⁢   ⁢ 1 / V ⁢   ⁢ 2 ) Y = ( 2.0 × 10 ⁢   ⁢ Pa ) 5 ⁢ ( 9 ) 1.40 = 270 ⁢   ⁢ atm . ( 2 )

[0061] (Again if compression gas is air,with Gamma=1.40 & initial temperature is 50 C at initial pressure of 3 2.0 × 10 5

[0062] Pa.)

[0063] The net work W done by the system is: (Basis internal energy U.)

U2−U1=Delta U=Q−W. (Q=Energy added,W=Work.)

U2−U1=U=−W (finite time adiabatic,but compressions are Repeated.)  (3)

[0064] The change in the internal energy of the system,in an adiabatic processes equal in magnitude to the work done by the system. If the work W is negative,as when a system is compressed,then −W is positive,U2 is greater than U1,and the internal energy of the system increases. As the pressure & heat energy is transferred into the upper volume 16b,Repeatedly-every 30 to 45 minutes from 16a to obtain thermal equilibrium with the working gas which is circulated through spiral pipes 20,Delta V=0 within volume 16b,is an approximate Isochoric process,since each controlled & limited re-supply of pressure & heat into this volume 16b,is to keep pressure & heat constant therein.

Claims

1. A method in which a gas could be compressed repeatedly to {fraction (1/9)} of it's initial volume within an enclosed space,as a result of mechanic piston,turning water pressure to mechanic-kinetic,in a Pascal hydrolic system. Input force exerted being the sea water pressure turned into mechanic motions of piston. Repeated every 30 to 45 minutes;has to be correlated to cycle completion time.

System is based on the following laws of physics: a. The non-compressibility of fluids.same with the Pascal Hydrolic,but in addition to Pascal,invention utilizes, b. The compressibility of gases of low density,high compressibility. Utilizing the continously vailable sea water pressure at 300 meters depth,as regularly repeated input pressure,the system would compress a closed cycle gas. This gas would reach thermal equilibrium with working gas.

2. Since,a. The planet is covered 71% with water & b. Because system does not need an external sea water thermal gradient input,as in OTEC,& also c. Production of system would not require heavy investment,return on investment could be attained in a short time. System structure is such that,it can achieve economies of scale in production & be efficient at operation, because system can be applicable world wide,(planet is covered 71% with seas.) d. Furthermore,how the design is,can account for 80% of production costs.

3. The method of claim 1,including the step of introducing said moving pressure to the hydrolic press means to multiply the initial force applied. Said system is to multiply the input pressure of 30 atm/square inch at the small area piston,to at least 60 atm/square inch pressure,to be effective on the large area piston,which would compress the gas above it,to {fraction (1/9)} of it's initial volume.

4. The method of claim 3,which would include closed cycle low density,highly compressible gas, to be compressed to said fraction of it's initial volume,& obtained pressure is then placed into a pressure chamber.with a circulation loop for pressure control. Upper compression chamber (16b) is designed to keep said fraction of gas at high pressure & to serve the purpose to increase & keep a temperature of 650 C average. Because this limited time adiabatic temperature increase is of mechanic origin that can be repeated frequently,the lower compression volume would continuously provide pressure (similar to an air pump),input into the upper compression chamber,compensating the small energy loss/cycle.by at least 100%. Keeping Isochoric condition in upper volume 16b. Gas within the closed cycle pipes 20,would attain thermal equilibrium with pressurized gas in volume 16b. Because a gas with large specific heat capacity would be used.the decline in temperature,when thermal equilibrium is reached. (700 C,)would only be about 25 C. Providing a superheated working gas of about 675 C.with about 270 atm working gas. Final energy conversion is mechanic to electric.

5. The method of claim 4,in which said gas would reach a maximum pressure.this said chamber would include at least one special one way high pressure resistant valve for directing pressurized gas from compression volume 16a into 16b.but not vice versa located between volumes 16a.16b.

6. The method of claim 5,which would include a set of pressure detectors & regulators.

7. The method of claim 1 which would involve a sequential order,that is,at that time when the valve below the compression chamber would close.large area piston would move back to it's initial position,to get ready for the next thrust-compression and also consequently,to avoid the compressed gas within compression chamber (16b,) to expand back to it's initial volume of pre-compression. As a result.at the other side,small area input piston would move back up.

8. The method of claim 3,in which compressions would be repeated periodically. Along with valve separation during piston downward motions & by good insulation.gas in 16b would be maintained at an optimal high temperature within a range of 550 to 650 Celsius. Which is to reach thermal equilibrium with a closed cycle working gas,to increase the pressure of the same to 270-300 atm. Internal energy loss of system is avoided as system has no condensation process.

9. The method of claim 8,in which temperature average of 650 Celsius would be achieved.to keep only the upper volume at Isochoric condition.(16b.) The condition within compression space 16a,would be adiabatic/cycle,but which can be repeated frequently to supply 16b. (Every 45 mins.)

10. The method of claim 9,which as a result of thermal equilibrium at 675 C,is to obtain a working gas at about 270 atm pressure,for turbines that are to be compatible to said pressure.

11. The method of claim 7,in which said system of water discharge.re-positions the small area piston repeatedly. (Sea water pressure input side & same side of sea water discharge.)

12. The method of claim 1,and because entire system structure is such that: a) No burning of fossil fuel is involved or no explosive burning occurs in the process.b) No heat pollution occurs, c) No chemical pollution into the sea occurs,system fullfills a high quality environment protection objective,as a System of Renewable Energy.

13. The method of claim 1, where the Pascal based system is within water & also utilizes water pressure as input force.system is not subject to Gravity constraints since Pascal hydrolic is not subject to Torricelli's theorem of speed of efflux,as the hydrolic oil is in an enclosed system. Furthermore,since the discharge water quantity at the pressure input side is a small quantity & relative pressure conditions between sea surface & discharge volume is favorable to move said quantity with minor pumping,water to be discharged periodically would also not be a Gravity constraint. Furthermore,the thermal equilibrium & working gases do not constitute a Gravity problem.due to low density.