LOW EMISSION ENERGY SOURCE
A power generator provides power with minimal CO2, NOx, CO, CH4, and particulate emissions and substantially greater efficiency as compared to traditional power generation techniques. Specifically nitrogen is removed from the combustion cycle, either being replaced by a noble gas as a working gas in a combustion engine. The noble gas is supplemented with oxygen and fuel, to provide a combustion environment substantially free of nitrogen or alternatively working in 100% oxygen-fuel combustion environments. Upon combustion, Very little to no nitrogen is present, and thus there is little production of NOx compounds. Additionally, the exhaust constituents are used in the production of power through work exerted upon expansion of the exhaust products, and the exhaust products are separated into their constituents of noble gas, water and carbon dioxide. The carbon dioxide may be used in conjunction with a biomass to accelerate the biomass growth and to recover the oxygen enriched air resulting from algae photosynthesis for enhancing the operation of the power generator using the as Biomass for processing into methanol/ethanol and biological oils as fuel for the power generator. The biomass fuel is seen as a solar fuel and may be used in conjunctions with other solar fuels like heated thermal oil and others, as well as clean fossil fuels to optimize to clean, and efficient operation of the power generator in various regulatory contexts.
This application is a divisional of co-pending U.S. application Ser. No. 10/760,915, filed Jan. 20, 2004 which claims benefit of U.S. provisional patent application Ser. No. 60/441,088, filed Jan. 21, 2004 which is herein incorporated by reference.BACKGROUND OF THE INVENTION
1. Field of the Invention
Embodiments of the present invention generally relate to power generation, more particularly power generation incorporating combustion, such as internal combustion engines, including power generation wherein it is desirable to reduce the emission of oxides of nitrogen, hydrocarbons, carbon dioxide and particulates. More particularly still, embodiments of the invention include power generation using a power source having a regeneration mechanism, whereby emissions from combustion are recovered for reuse as a source of fuel for the power source. Additionally, the power generation methods and apparatus herein may be used to provide solar generation capability.
2. Description of the Related Art
Power generation employing internal combustion engines is traditionally accomplished by introducing fuel (Typically a hydrocarbon based fossil fuel or distilled hydrocarbon fuel) and air into a combustion chamber or volume, and igniting or exploding the fuel, in the presence of oxygen supplied in the air, to cause expansion or increased pressure in the chamber, thereby causing relative movement of a combustion chamber component. The movement of the combustion chamber component is employed to cause a consequent output from the engine, typically in the form of torque and rotation of a shaft extending therefrom. For example, in a piston type of engine the increased pressure caused by the combustion of the fuel-air mixture causes movement of a piston in piston housing, and the piston is connected, through an arm, to a rotatable crankshaft. Likewise, in a gas turbine style of engine, the fuel-air mixture is combusted in a combustion chamber, and the expanding gaseous result passes through a plurality of rotationally mounted finned rotors, causing them to rotate with torque. The result is rotation of a shaft, such as a shaft upon which these the rotors are mounted, the shaft being coupled to a generator, a vehicle or the like, to power the generator or vehicle.
In such internal combustion engines, the efficiency of the engine, as measured by power output on the shaft as compared to the potential power provided by the fuel, is on the order of 30% to 60%. The difference between actual energy recovered and potential energy available, i.e., the 70% to 40% loss in efficiency, is a result of several factors, including inadequate or incomplete combustion of the fuel, generation of wasted heat, frictional losses in the mechanisms used to transform the chemical energy released in combustion to physical energy in the output shaft, exhausting of the combusted mixture before complete recovery of the energy thereof, etc. Each of these factors adds to yield a relatively inefficient internal combustion engine.
One mechanism that has been used in the past to increase the efficiency of the fuel use has been to use the heat remaining in the exhaust to either generate heat for building heating purposes, or to generate further power through a steam turbine, or the like. For example, the temperature of the exhaust of a gas turbine is sufficient to heat and often to superheat steam, which may then be passed through a steam turbine for energy generation therefrom. Thus, the energy recovered in the output of the steam turbine is added to that recovered by the gas turbine as a measure of efficiency. However, gas turbines as a primary engine and without a method of secondary heat recovery are less efficient than diesel cycle engines, which is currently, on a stand alone basis (i.e., no secondary heat recovery based power generation) the most efficient engines commercially available. Further, engines operating on the Stirling cycle would theoretically be more efficient, but have never gained commercial acceptance. The relatively efficient diesel engine using commercial fuels has an exhaust temperature insufficient for efficient steam turbine power generation therewith, whereas the gas turbine has high enough combustion temperature, and exhaust temperature, to allow sufficient heat recovery for commercial uses. The gas turbine with such a heat recovery system is currently the most efficient commercially available system for combustion based electricity production
Several methods have been used or proposed to increase the efficiency of the internal combustion engine itself. One such methodology includes modifying the air used for combustion by enhancing the oxygen percentage thereof. As a result, a greater percentage of oxygen is available in a given volume of air-fuel mixture (as oxygen displaces Nitrogen in the air), resulting in the ability to have a greater quantity of oxygen and fuel in the mixture per unit volume, and a resulting higher combustion temperature. As is known that if the temperature of the combustion reaction is increased the resulting efficiency of the engine should increase, various schemes have been proposed in the past to provide such an increase in both temperature and efficiency. For example, it is known to combine or mix additional oxygen with the air intake of an internal combustion engine, with a resultant substantial increase in energy recovery efficiency. Further, emissions of carbon monoxide, hydrocarbons and particulates were substantially decreased. As naturally occurring air has an oxygen content of about 21%, the added oxygen both raises the combustion temperature and increases the total quantity of fuel combustible in a combustion chamber of a given size. For example, adding sufficient oxygen to air so that the resulting mixture is 35% oxygen, and employing a diesel cycle engine and diesel fuel, has been demonstrated to result in significant increase in power output for an engine, as the greater concentration of oxygen allows greater quantity of fuel to be introduced and combusted. However, the engine also released, as exhaust, unacceptably rich emissions of greenhouse gasses as nitrogen oxides, approximately double that of a non-oxygen enriched diesel cycle engine, and also was unable to be effectively controlled. Although the amount of Nitrogen in the oxygen enriched air is less (because, on a volume to volume comparison, some is replaced by oxygen) and thus one would expect fewer NOX emissions, the increased temperature caused a higher reaction rate or reactivity between nitrogen and oxygen, resulting in a greater efficiency and power output, a lower emission of particulates, CO and other compounds, the production rate of NOX compounds also was significantly increased. As a result, this concept has not been further pursued.
An ongoing issue with the use of fossil fuels or other hydrocarbons in conjunction with internal combustion engines is the generation of pollutants, such as NOx or COX compounds. A portion of these emissions, specifically the NOX compounds, are known to cause disruption of the ozone layer, and/or smog, as well as being generally unhealthy when inhaled. CO is toxic, as is an additional emission gas, CHX, Likewise, CO2 has been implicated in global warming, and the emission of it may become limited in the future. Thus, although the efficiency of the engine can be increased, the resulting pollution is unacceptable.
An additional method of power generation is solar power, such as a solar energy generating station or “SEGS,” in which solar energy is converted to electricity. As solar energy is unavailable during the night, such SEGS plants are typically used to generate “peak” and mid peak power, i.e., they are used during periods of the day when the sun is shining when electricity demand is highest. These peak times are locale dependant, such as, for example, locations of high solar insulation where the need for electricity to power air conditioning units is much higher in summer months. Alternatively, or additionally, such peaks can occur as electrical consumers return to their homes in the late afternoon or early evening hours, and begin using air conditioners, appliances and the like. To provide the peak power needed, utilities are often willing to pay an a higher charge to the power generator, including SEGS, for this power during peak hours. Further, these peak plants are often operated only during peak demand periods, and thus their cost, i.e., the investment in infrastructure, is not recoverable based upon continuous generation, but rather based on less that full utilization.
Although SEGS have proven to be capable of providing power during peak operation times, there are limits of competitiveness which affect their use for base line power generation needs. As the plants cannot operate in non-daylight hours, the cost of building the solar power generation equipment must be justified based solely upon generation during these daylight hours. Thus, the electricity generated must be capable of being sold at a premium over electricity generated at power stations where the power generation is continuous, i.e., base line plants which operate continuously, 24 hours a day, except when down for maintenance or unusual lack of electricity demand). In localities that have significant disparities base load and peak load, it is not uncommon for peak load to be 2 to 6 times larger then base load requirements. In these localities with big disparities between base load and peak demands it is important to encourage building peaking plants that do not run many hours this incentive is usually provided by providing substantially higher prices or values on peak pricing. Even with substantially higher priced peaking power it is usually the case that economic analysis will determine that it is most beneficial to the energy supplier to meet these requirements with the lowest cost, typically less efficient and more environmentally unfriendly systems than solar. In order to encourage clean energy sources to supply this peak power, incentives are sometimes offered. The incentives often give clean a energy supplier delivery preferences either by accepting clean energy on a first priority basis against other suppliers if they are priced equally, or to allocate some percentage of peak or as delivered energy to be supplied from clean energy sources. As well as the delivery preference a tax environment of specific SEGS benefits are often provided to make of an even tax playing field between SEGS suppliers and fossil fuel plant providers. As a potential supplier of clean energy, SEGS plants, which are based on the delivery of solar thermal sources of energy, are in an unusual position. On one hand they are able to deliver clean energy from solar and they are also able to produce energy by using fossil fuels to power a steam turbine otherwise normally powered from solar energy. Were the SEGS to receive preferences associated with its clean solar delivery it is usual practice to limit the amount of fossil fuel energy the SEGS plant is entitled to produce relative to the solar energy that it produces and requires the plant to produce 100% of its output capacity from solar energy alone.
Solar energy plants which often deliver energy during peak demand hours typically provide that energy as a direct consequence of the amount and intensity of the solar incident light that falls on the solar field, with the solar field being comprised of photovoltaic fields or solar thermal fields. However solar thermal fields have an added flexibility. Solar thermal plants typically operate by raising the temperature of some intermediate fluid to high temperature and then circulate that intermediate fluid through a heat exchanger that boils water, and resultant steam is used to run a steam turbine to make electricity. However it is technically quite easy for the solar thermal steam to be provided by fossil fuel and not just from solar source. Thus when the sun is not shinning a the power block portion of the solar thermal plant is able to operate by using fossil fuel to directly heat the water in a parallel boiler, creating steam to run the turbine. This added flexibility allows solar thermal plants to be available to supply energy then when the sun is available and when the sun is not available. However, because of the limitations on the use of fossil fuels and the requirement that the plant must be able to produce 100% of its rated output from solar alone to receive preferential supply status and certain tax and other benefits of being considered solar, the fossil fuel based generation is minimally used and sub-optimum power generation equipment is used. For example, although it may be reasonable to combine gas turbine and solar generation, the cost effective solar plants available before this new technology are not able to produce for technical reasons the full rated power of the plant from solar alone. Thus a current SEGS plant cannot operate highly efficient combined gas-steam cycle turbines and still be considered a solar plant in many if not all locales. Most solar energy equipment at most can heat an intermediary fluid converted to steam and drive a turbine to temperatures of about 400° C. Whereas, in order to run a highly efficient combined gas-steam turbine, where the waste heat exiting the gas turbine is fed into the steam turbine, the initial temperature of the compressed air entering the gas turbine must be heated to 2000° C. The gap of 1600° C. needed to bridge this gap results in commercial solar fields, are running the most efficient steam turbines at approximately 40% efficiency instead of the most efficient combined cycle plant running a 60% efficiency. There does exist one type of solar collector technology called a power tower, which focuses a large number of mirrors, each one independently shining the sunlight onto a small location at the top of a very tall tower. That location at the top of the tower becomes very hot, in excess of 2000° C. The goal of this design was to be able to obtain temperatures that would be able to run efficient combined gas-steam turbine systems. However for many reasons most of which can ultimately be related to lack of sufficient material technology at this stage this approach is too expensive, inefficient and unreliable to be developed in to a commercial product. Further improvements at the material science level that may take many years to develop must still made.
Therefore, their exists a need in the art for a power source, particularly one using a combustion based engine, wherein the resulting efficiency is increased without the production of, or with a significant reduction in the production of, byproducts such as NOX and CO and particulates in the resulting emission stream, and with greater efficiency than prior art devices. Likewise, there is a need to provide solar based generating capacity (SEGS) having more widespread use, significant increases in efficiency, and significant increases in valuable on-peak delivery of energy and power compared the amount of energy and power delivered off peak. All the above being achieved within frameworks that are consistent with restricted fossil fuel use.SUMMARY OF THE INVENTION
The present invention generally provides a higher efficiency, lower emission, power generator, by virtue of operation of an internal combustion engine in the absence of, or with a relatively restricted amount of, air or materials in the air which contribute to NOX formation. In one aspect, the power generator is an engine is operated by introducing a combination of a fuel, a gas for combustion with the fuel and a noble gas into the combustion chamber of an engine, and combusting the fuel and gas therein. In one aspect, the noble gas is argon. In another aspect, the gas for combustion is oxygen.
In another aspect, the power generator is coupled to a gas and heat recovery system, in which the exhaust resulting from combustion is recovered and the heat is used to generate power. In one aspect, this includes providing a separator to separate the noble gas from the exhaust and reusing the noble gas for further use in the power generator. In another aspect, this includes providing a reaction mechanism for reacting the non-noble gas components with an expansion medium to separate the individual components of the remaining exhaust stream. In a further aspect, this includes providing a separator to separate CO2 components, of the exhaust stream and a biomass for the recovery of oxygen therefrom. In a still further aspect, a reinsertion system is provided to direct the oxygen back into the power generator.
In another aspect, a method of generating power includes providing a mixture of noble gas and combustion gas to a combustion location, providing a quantity of fuel to the combustion location and initiating combustion, and converting at least a portion of the generated energy into a physically useable form. In one aspect, the generation is provided in an internal combustion engine, and the power is removed from the power generator by virtue of a rotating shaft.
In another aspect, the method includes recovering the gas stream resulting from combustion, such that the noble gas is separated from the gas stream and reused in the power generator as a carrier gas for further combustion. In another aspect, this includes combining the non-noble gas constituents with a reaction medium to convert these gasses to their constituent elements. In a further aspect, this includes separating components of the exhaust stream having combustible gasses therewith, and directing them to a biomass for the recovery of combustible gasses therefrom. In a still further aspect, a combustible gasses recovered from the biomass are reinvested into the power generator. In a still further aspect, the combustible gasses include oxygen. In a still further aspect, the reaction medium is superheated steam or water.
In additional aspects, the power generator may be combined with additional resources for exploitation thereof. For example, the generator may be used as the engine for a vehicle, such as a road vehicle, a railroad vehicle, a ship's power plant and the like. Likewise, the power generator may be combined with other power generation schemes for greater utility. In a still further aspect, the exhaust of the power generator may, either before or after separation, or in a partially separated composition, be used to heat water or another liquid for use in generating a steam turbine or for otherwise producing heat for commercial and/or residential uses, such as heating.
In another aspect, the power generator may be combined, with a solar generating capacity, to provide a substantially increased generating capacity. In this aspect, a power generator includes an internal combustion engine. A burner is supplied, upstream from the gas turbine, in which oxygen and fuel are combined and combusted. This high pressure high temperature stream of the products of combustion is then passed through the turbine to generate power at the output shaft thereof. To provide oxygen for combustion with the fuel, air is passed through a chiller and the oxygen separated therefrom is passed on the burner. Additionally, to reduce the occurrence of greenhouse gasses, the natural gas is passed through a chiller, causing the nitrogen therein to precipitate therefrom before the introduction of the gas to the burner. The exhaust stream, after passing through the turbine, is used in a secondary recovery system, to further extract energy therefrom and cool, the exhaust stream. In one aspect the exhaust stream is separated into its individual components, and the components are further used. In an additional aspect, this includes passing the CO2 in the exhaust stream to a biomass, and converting the carbon dioxide and biomass into additional biomass and oxygen for reuse in the burner. In another aspect, the solar component of the power generator is the growth of the biomass and the recovery of fuel and oxygen therefromBRIEF DESCRIPTION OF THE DRAWINGS
So that the manner in which the above recited features of the present invention can be understood in detail, a more particular description of the invention, briefly summarized above, may be had by reference to embodiments, some of which are illustrated in the appended drawings. It is to be noted, however, that the appended drawings illustrate only typical embodiments of this invention and are therefore not to be considered limiting of its scope, for the invention may admit to other equally effective embodiments.
Referring still to
Referring still to
As the fuel-argon mixture is ported into the intake manifold 17 of the engine 16, the oxygen is ported to the combustion chamber 18. This is accomplished, in this embodiment, by providing a cryogenic pump 9 and imposing a modest pressure to push the oxygen along a thermally insulated oxygen line 11 to a pressure amplification fuel injection system 12, such as a HEIU system available from Caterpillar industries or a MEFIS system available from Mazrek. The injectors of this system preferably include nozzle heads with hardened components or surfaces, to increase wear resistance in the hostile combustion chamber 18 environment. By using this configuration, the oxygen may be cryogenically pumped to the engine 16 with minimal parasitic losses, yet may be pressurized to enable injection into the combustion chamber 18 when it reaches the combustion chamber 18. To regulate the temperature and pressure in the oxygen line 11, the line 11 is ported to a intermediate high pressure overflow chamber 13, as well as a temperature control unit 14 which may heat or cool the line 11, as needed, to maintain the proper temperature (approximately −170C) and pressure in the line 11. Dampeners 120 are provided in the line 11 immediately before the terminus thereof at the amplification fuel injection system 12 to minimize resonance on the line 11. Such a dampener can be a pressure regulator, such as a spring loaded piston or a membrane which enables change in the volume of the line immediately before the amplification fuel injector system 12, or simply an additional pipe dead headed from line 11 immediately before the amplification fuel injector system 12.
The amplification fuel injection system 12 provides pressure amplification of the oxygen, and injection thereof in a liquid state, to the combustion chamber. The actual amplification level is set to optimize the combustion cycle and the overall efficiency of the power generation system. Where the engine 16 is a diesel cycle engine, the amplification is on the order of 10 to 20 to one or greater, thereby injecting at a pressure on the order of 200 to 250 MPa and minimizing the Cryogenic pump 9 pressure requirements and is in the range of current cryogenic pump capability. For example, pumps such as the PD series of cryogenic pumps, available from Chart Industries, Inc., would operate acceptably. Where a spark based combustion engine is employed as engine 16, the pressure amplification and cryogenic pump pressures may be lower, as the pressure in the combustion chamber 18 into which the oxygen must be injected is lower. Referring still to
The second stage of the separator system 180 provides first heat recovery as the heated gas and the superheat highly pressurized water is injected into the heat recovery unit in a manner describe below. Subsequent to the heat recovery stage, within the chamber the expansion increases the temperature of the gas which will drop significantly preparing the components of the gas for separation of the exhaust stream components, in this embodiment primarily H2O, COx and argon. Additionally, the COX will, with proper operation of the engine 16 and variations of fuel, oxygen and argon, be primarily composed of CO2 with only trace amounts of CO. Thus, in this second stage, in the engine heat recovery and gas separator 23 the exhaust gasses are further reduced in temperature to a temperature on the order of −50C. In the third stage the cooled gasses are pressurized and at the same time cooled by liquid nitrogen (See
Referring now to
The operation of the abutments 142, 144 with the rotor 140 is described with respect to the lower abutment 144, as follows. The lower abutment 144 includes an interior end 146 which is maintained in very close position adjacent to the surface of the rotor 140, such as several microns of space therebetween, and a second end which is extendable through an abutment sleeve 147 extending through the cylindrical housing 134. As the rotor 140 rotates about the shaft 138, the abutment 144 is linearly moved inwardly and outwardly of the volume in the cylindrical housing 134, always maintaining a very close spacing between the interior end 146 of the abutment 144 and the face of the rotor 140. Thus, as shown in
To move the abutments 142, 144 inwardly and outwardly, abutment controls 180 (184) are provided. Each abutment control, as shown schematically in
The rotary engine 130 may be used as an internal combustion engine, for example, by having the fuel/carrier gas mixture enter the intake and having the gas for combustion injected into the combustion chamber, or it may be used as an energy recovery and exhaust cooling system To use the rotary engine as a energy recovery system and exhaust cooling system, the exhaust gasses from engine 16, consisting primarily of CO2, Argon, and H2O from combustion (but not superheated 350° C. engine exit cooling water) are passed through the heat exchanger and enter the low pressure intake chamber through intake line 126 which is ported to intake port 168, thereby introducing the gasses into the low pressure intake chamber 152. The movement of the rotor reduces the pressure in the input chamber sucking in the exhaust gas from the heat exchanger into the chamber. As rotor 140 rotates about shaft 138, it passes over intake port 168, thereby causing no further exhaust to be taken into the particular volume being drawn into the low pressure intake chamber 152, and causing the volume to now exist in the compression chamber 154. This volume of emission/exhaust is thus compressed, and the exhaust gases CO2, Argon and H2O as the volume of the compression chamber is reduced as the rotor continues to rotate and as a result the approximately 500° C. intake gases are heated to high temperatures. At an appropriate time a valve 173, which is either electrically controlled or mechanically timed, such as through a cam and arm arrangement connected to the shaft 138, opens to enable the compressed exhaust to pass through the compressed gas inlet 172 and thence into the combustion chamber 160. Simultaneously, the low pressure chamber has reformed as bounded by the abutment 144 and the opposed side of the rotor 140.
In order to use this rotary engine 132 as a energy recovery system and a gas expansion and separation system, a further modification is needed, in order that the volume achievable in the expansion chamber 148 and the exhaust chamber 144 are enlarged in comparison to the volume of compression chamber 154 and low pressure intake chamber 152. With the high temperature gases compressed into the combustion chamber, the 400° C. superheated engine exit cooling water pumped by the pump located in the Heat Exchanger and Water Pump under modest pressure, 10 Mpa (1,470 PSI) is pumped into the Pressure Amplification Water Injection System (22a) with 25 times amplification. The highly energized water, similar in state to water exiting a steam turbine boiler enter the combustion chamber, but because the water has been injected at such great pressure (250 Mpa, 36,750 PSI) the water enters the chamber as micro size supercharged droplets that essential explode in the high temperature gas environment. This explosive expansion pressurizes the combustion chamber followed by the expansion chamber allow most of the energy to be recovered from the exhaust gas, and even the exist engine cooling water.
Referring now to
As the bypass cutout is a three dimensional feature, i.e., it has a perimeter as well as a thickness equal to the thickness of the partition 188, there is the possibility, and in fact likelihood, of leakage between combustion expansion chambers 148, 148′ and the exhaust chambers 150, 150′, and thus an additional isolation paradigm is needed. To provide isolation, the bypass cutout 194 is configured to enable a secondary seal to be interposed between the rotors 140, 140′ when the rotors are simultaneously passing the bypass cutout 194. In this embodiment, as shown in
As shown in
Thus, when exhaust gas is introduced to low pressure intake chamber 152, it becomes compressed in compression chamber 154 and enters combustion chamber 160 where it is combined with superheated droplets of water. When the combustion chamber 160 is then vented to the combustion expansion chamber 148, the products of the combination of superheated water and the exhaust stream expands also into combustion expansion chamber 148′ by flowing through the cutout 194. Thus, the combined exhaust-superheated water expands, in this embodiment, into three times the volume the exhaust was compressed into, to enable the mixture to be substantially expanded and thereby cooled. Once the rotors have moved to create the maximum volume of the combustion expansion chambers 148, 148′, the rotor tips pass over exhaust ports 164, 164′, and the separated by phase mixture passes into exhaust manifold 166. Thus, as the rotors 140, 140′ rotate, consecutive volumes of exhaust gasses are compressed, mixed with superheated water, expanded, and exhausted into exhaust manifold 166.
In addition to the expansion and consequent phase based separation of the exhaust components afforded by the engine 132, the expansion of the exhaust gasses/superheated water mixture releases energy which is converted to power by virtue of the expanding mixture pushing on the rotors 140, 140′ to cause rotation of the shaft 138, and likewise supply energy in excess of that needed to compress the incoming exhaust gasses. Thus, shaft 138 may be coupled to a generator to generate electricity, or may be coupled to other work transfer devices, such as a working shaft to power equipment, motor vehicles, ships, trains and the like.
Although the exhaust gasses have been cooled in rotary engine 132, they are still above the condensation temperature of the CO2. Therefore, the exhaust manifold 166 of the second stage rotary engine 132 is coupled to the inlet of an additional second rotary engine 132′, in this embodiment having the configuration of the rotary engine 132 of
Once the exhaust has exited the second rotary engine 132′, it enters the third stage of the separation system 180, in this embodiment a low temperature compressor, which compresses the exhaust stream from the second rotary engine 132′, and thereby solidifies the H2O resulting in each of the three components of the waste stream into separate phases. These three phases may then be separated physically, to provide water, argon and carbon dioxide. Specifically, as the exhaust stream flows through the compressor 200, the pressure of the fluid increases to the point where H2O becomes solid, and the stream is then flowed through a separator 202 such as a conduit having tines or screening therein which traps the solid H2O, and the argon is bled off through a conduit 204. The remaining CO2 is flowed out of the compressor 200, and into a storage container 27 (in
Referring now to
Several methodologies are currently feasible for the production of fuel from algae. For example, methane may be produced therefrom via biological or thermal gasification. The biomass may be fermented, thereby forming ethanol. It may be burned directly. It may be pressed to release the oils therefrom and those oils may be transesterified, in which the triglicerols therein are reacted with a simple alcohol, to form alkyl ester, which is commonly known as biodiesel. Additionally, it is known that certain green algae will, when subjected to an anaerobic environment, produce hydrogen, which may be recovered and used as a fuel.
Once the oxygen enriched gas stream has passed from the end 210, the gas stream is then flowed to a mechanical filtering system 4 removing some of the nitrogen and CO2 from the oxygen emitted from the algae field. Such filter are commercially available, and while not purifying the oxygen for use it creates an it is effectively enhance oxygen air with is ported to the Nitrogen Air Chiller 6 and Air Selection Valve (both in
In an additional embodiment, the methanol, ethanol and/or algae oil streams 13, 15, 17 may be directed to a reformer 219, to convert the streams into constituent elements, including H2, CO2, H2O and carbon, as well as an output of power. Each of these constituents may be reused by being recycled back into the biomass 202, used as cooling water for the engine, or sold for value.
Referring now to
The bottom line comparison can be understood by looking at the potential efficiency of the power generator hereof. The potential of the power generator of the present invention is 57% efficient compared to the Combined Cycle, Gas/Steam Turbine system which is rated at 55% efficiency. It should be noted that the bottom line efficiency presented is the efficiency at the user location. The efficiency takes into consideration transmission losses at the user location. Because the power generator of the present invention is a zero emission engine it is possible and practical for it to be located at a large user location in urban and even downtown environments. This placement is not acceptable for Combined Cycle because of the NOX and CO2 emission.
If the transmission losses were not considered an integral part of the analysis, and in the case of the power generator hereof, the 1% amount of loss was added back into the output of the power generator hereof, then the efficiency for some typical large size engine (on the order of 300 MW) would be 58%, and the efficiency of the Combined Cycle engine would be on the order of 60%. Thus, one may say that, excluding transmission inefficiencies the Combined Cycle engine is slightly more efficient than the power generator hereof.
However, the comparison between the two engines performed in the above manner is inadequate because the power generator of the present invention is a nearly zero emission engine while the Combined Cycle engine may be clean when compared to conventional engines, but compared to the power generator of the present invention it is a major contributor to NOX and to greenhouse effects by emitting CO2. If the Combined Cycle system were to be modified, and a final stage added to absorb and reduce the CO2 release to near zero, this would cost the Combined Cycle engine an approximate 10% drop in efficiency with no economic means to reduce NOX emissions to zero. Thus, the Combined Cycle system, the most efficient of today's systems, has an operational efficiency of 50% when normalized to a Zero CO2 emissions, but has a major, non-correctable disadvantage in the NOX emissions area.
For comparison, assuming the power generator of the present invention is using a diesel combustion cycle, which uses the better current techniques that are achieving approximately 49% efficiency. The additional use of high-pressure fuel injection amplification increases the efficiency by another 3% bringing the overall engine efficiency to (49%+3%) 52%. The higher combustion temperature resulting from the enhanced O2 environment and the use of argon instead of nitrogen increases the overall efficiency of engine operation by 12%+52%=64%. The energy gain from the downstream heat recovery in rotary engines 132, 132′ adds approximately another 12% to the overall useful work from the engine or 12%+64%=76%. The losses in efficiency associated with the production of reasonably pure O2, and the separation and precipitation of Argon, CO2 and H2O is approximately 18%, reducing the overall efficiency or 76%−18%=58%. If the power generator of the present invention is located at a remote site for electricity generation, and additional 1% of losses should be expected, resulting in 58%−1%=57% efficiency.
In another aspect of the invention, the power generator of the present invention may be used in two operating modes, a non-recycling mode, i.e., where the exhaust stream is ultimately vented to the ambient surroundings and a zero, or near zero, emission mode. This is useful where, for example, the power generator is used to power a mobile vehicle, but is also used to provide power in a stationary location.
Referring now to
In Operational Mode 2: Standard Driving Conditions. The above described vehicle engine is used as a standard engine consuming ordinary available fuels and running with generally available efficiency and emission levels. In this mode of operation, Air is moved to the Turbo Mixer 10 instead of methane or low N2 level natural gas, and Argon is transmitted to the engine 16 using the air received and compressing it into the combustion chamber of the engine instead of the noble gas/fuel mix as would be the case in Operational Mode 1. The operational performance of the Turbo Mixer 10 will be adjusted under the control of the Intelligent Control System 250. It will adjust the operation to best known control practices as an air turbo engine feed. Standard fuels such as gasoline or diesel will be fed into the engine 16 based on the type of engine used, i.e., spark or compression based. In this mode of operation, the gasoline or diesel fuel will be injected into the combustion chamber 18 through a standard readily available 2nd gasoline or diesel fuel injection system 244. The standard fuel Injector system 244 parallels the O2 fuel injection system which is utilized in Operational Mode 1. Once again, the Intelligent Control System 250 would operate the fuel injection and combustion controls in an optimum manner. During Operational Mode 2, the engine heat recovery and gas separator system 23 will be physically and functionally engaged with the engine 16, and the exhaust gases from the engine heat recovery and gas separator system 23 would exit through a standard exhaust system 248 with standard catalytic converters etc.
Referring again to
To convert the energy of the fuel and oxygen mixture and heat generated thereby into useful energy, the output shafts of the three engines, engines 16, 132 and 132′, are preferably linked to a gearbox 254 or transmission, and then further connected, from an output shaft of the gearbox, to a generator for the generation of electricity. The output shafts may be separately linked to the gearbox 254, or the output shaft of engine 16 linked to one side of the shaft 140 of engine 132 and the output side of shaft 140 linked to the input side of shaft 140′ of engine 132′. The output side of shaft 140′ would then be linked to the gearbox 254. The gearbox 254 is likewise controllable by the control system 250, such as through the operation of solenoids or other electrically or pneumatically operated methods, to change the relative speed of the input(s) to the gearbox 252 through the interposition of different ones of sets of gears on the input and output sides thereof. Thus, the speed and torque of the output shaft of the gearbox 252 may be adjusted to address changing conditions downstream of the generator and thus match the output of the generator to electrical loads. Simultaneously, in this aspect, the quantity of the fuel and oxygen reaching the engine 16 may be adjusted to increase or decrease the energy discharged therefrom through its output shaft, thereby further enabling the matching of the generator 254 to any downstream electrical load. The output of the generator 254 may be used to provide local power to a home, building, etc., or it may be input into the local electric grid. Furthermore, where the power generator of the present invention is used to power a large mobile vehicle, such as a ship, the output of the gearbox 252 may, with appropriate backlash and other drive train components, be directly coupled to a propeller.
Although the present invention has been described herein primarily as used in conjunction with methane as a fuel, other fuel options are specifically envisioned. Ethane or a combination of ethane and methane, deliverable to the power generator of the present invention in gaseous or vapor form, are readily interchangeable and combinable for intake into what would otherwise be the “air” intake of the engine 16. The methane and/or ethane are readily provided from source of natural gas where the source has a low N content, from natural gas after filtering N therefrom, or from the algae field. Additional fuels may be used, and if so, certain modifications may be necessary to introduce them into the engine 16 combustion chamber 18. For example, diesel fuel or gasoline having a low nitrogen content, or filtered for a low nitrogen content, could be introduced to the combustion chamber through an injector, in which case only argon need be introduced through the intake manifold.
Referring now to
Intake section 302 includes N2 Air Cooler 308, into which air from ambient surroundings is introduced and cooled before the air enters the Cryogenic N2 Separator 310 after which the oxygen is introduced to a turbo-mixer 312, in this aspect a turbocharger. The remaining components of the cooled air, primarily N2, H2O, and CO2 are then circulated optionally to the Generator for cooling down the Generator 314 to low temperatures reducing the thermal loss IR resistance potentially to zero using superconductor materials. The N2 may then be recirculated to the coolant side of the heat exchanger forming the N2 Air Cooler 308. Alternatively the liquid N2 might be fed directly back to the air inlet side of the N2 Air Cooler 308. In parallel to the separation of O2 out of the air through precipitating out the N2 and trace components from O2 in the air, a similar operation takes place with the natural gas, wherein the natural gas is fed into a separator, likewise a heat exchanger in which the natural gas is fed through one side thereof, and a liquid having a temperature below the boiling point of nitrogen is flowed through the other portion thereof, such that nitrogen and natural gas without nitrogen are recoverable therefrom in separate streams. Natural gas enters and is pre-cooled in the N2 Natural Gas Cooler 316 before entering the Cryogenic N2 Separator 318 where the N2, H2O and CO2 and other low liquefaction trace elements are separated from the natural gas fuel elements mostly methane and ethane. The liquid N2 and other trace elements are then circulated optionally to the Generator 314 for cooling down the Generator 314 to low temperatures thereby reducing the thermal loss IR resistance potentially to zero using superconductor materials and then feeding back the N2 coolant to the N2 Air Coolers 308, 316, alternatively the liquid N2 might be fed directly back to the N2 Air Cooler 308, 316. The O2 emanating from the Cryogenic N2 is fed into the Turbo Mixer 312. Alternatively the separation of N2 from both the O2 in the air and from the natural gas can be all made using one pre-cooler station and one Cryogenic Separator for the two functions. However for safety reasons and certain optimizations that may be possible by uses separate paths the preferred embodiment is describes two separate channels for separating out the N2.
The cold O2 and natural gas are fed into the Turbo Mixer 312 in correct proportions and from there into the Burner 320. The high temperature high pressure gases, higher temperature are then passed through the Gas Turbine 300, in the usual manner producing torque to turn the Generator 314, the exhaust gas from the Gas Turbine 300 is fed into the Heat Exchanger and Steam Turbine 322 which services as a heat recovery system adding to the Generator 300 torque. An Optional third stage Low Temperature Heat Exchanger and Turbine 324 is shown. A Gas Turbine Combined Cycle system normally would not have a third level heat recovery stage. However the most preferred configuration feeds the CO2 and H2O into an associated algae growth environment as described in
Use of the Power Generator for “Solar” Applications
The power generator of this aspect is also suitable for use in conjunction with SEGS, wherein the power is generated with the same or similar, low emissions resulting from solar energy. Likewise, where a solar facility, such as the SEGS facility employing simple boiling, is used in conjunction herewith, simultaneous power generation with the fuel and solar generation can result in a net doubling of output power and may be accomplished economically during peak generating requirement periods. Another aspect in order to meet the established criteria of being considered a solar power station of double the initial capacity for purposes of being classified a SEGS plant it is necessary to be able to operate the entire double capacity at least for some period of time. With the aspect of the algae field and algae produce clean solar burning this could be accomplished simply by running one full set of capacity on algae solar fuel. In the absence of algae solar fuel, the plant could be run as a double plant by storing sufficient heating fluid, so that for some portion of the peak hours, one full rated steam turbine could be run from the solar field heating fluid flow, and the other could be run from the stored heating fluid.
Where, as described with respect to
The reduction of NOX, CO, and other emissions to effectively zero emission levels allows the emission of these engines to be fed into algae and another growth processes to accelerate the growth cycle feed gases from less clean system could have possible negative effects with unacceptable toxin levels along with the useful and positive impact it should have on accelerating growth.
Where, as is described herein with respect to
The gain in power output capacity stability results from the fact that in standard gas turbines and combined cycle gas-steam turbine systems efficiency and power are based to a large extent on the input ambient and the combustion temperature of the system. Changes in operating temperature not only change the theoretical thermal efficiency in addition they effect plant design, which is optimized for one operation condition or another. While the combustion temperature is usually fixed at optimized levels for the system, the ambient temperature can change between day and night and between summer and winter by as much as 50° C. or more, thereby varying the output of the plant by 2% to 4%. An inlet temperature dependent drop in output capacity thus typically occurs during the summer months during the daytime hours. These happen to be precisely the hours when many regions require the maximum output from their plants to meet the need of summer air conditioning. This summer air-conditioning load sets the requirements for new plant acquisition, usually inexpensive, low efficiency and relatively high emissions plants just to produce electricity to meet these needs.
There are gains and losses with respect to efficiency of the power generator hereof using a 100% O2—fuel combustion system compared with competing combined cycle gas-steam turbine technology. As stated previously, on balance the two systems would run at about the same overall efficiency depending on precise design factors. This aspect of the power generator system loses certain operating efficiency by cooling the incoming fuel to precipitate out the N2 from the combustion process, on the other hand the colder temperature of the incoming O2 and natural gas reduces the parasitic losses of the air fuel intake turbocharger and/or compressor feeding the combustible mix to the burner and then to the turbine. The elimination of the N2 as a working gas and which was not a combustion gas in the combustion cycle would for a the same quantity of gas/unit time entering the combustion cycle, now composed of, for example, only fuel and O2, would produce substantially more heat per unit of time. Thus as a practical matter the quantity of O2 and fuel supplied into the system per unit of time would not be made to fully substitute for the quantity of N2 eliminated. But from the preceding it can be seen that increases of temperature and pressure are possible and clearly without the negative factor of added NOX generation. This increase in operating temperature and pressure will have a tendency to increase the efficiency of the system. The increased temperature and pressure increase the efficiency of the system.
Where the power generator uses a 100% O2 and fuel mix and a conventional steam turbine recovery as the second stage of heat recovery, the only difference in this application to standard steam turbine heat recovery methods is that the operating combustion temperature and pressure would be somewhat higher and as a result, the input emission gases into the Heat Exchanger and Steam Turbine 232 would be somewhat higher and the temperature of the exit gases would be somewhat higher. Under standard operations not in conjunction with the use of an algae field for oxygen and biomass production, power generator would exhaust the gases from the steam-turbine to the atmosphere which would be non-toxic, all NOX essentially eliminated with other trace compounds, but CO2 would be released along with water. If it is desired to eliminate the CO2 and/or gain the other operational benefits from site produced fuel then it is necessary to feed the emission gases, CO2 and H2O into the enclosed algae field. To do so it is desirable to cool the output emissions further and to recover some additional energy out of the waste exhaust heat. This can be accomplished using a Low Temperature Heat Exchanger and Turbine 324 such that the exhaust gases from the steam turbine boil Freon in a liquid state converting it to a gas state and drive a low temperature Freon gas driven turbine. Other gases and configurations are possible.
The power generator of
Where the power generation scheme described with respect to
It can be seen that the peak output of the basic initial SEGS station would be on the order of 5.5 times greater when converted into a power generated (
It should be appreciated that the power generation scheme provided as described with respect to
Use of the Power Generator for Low Emission Applications
In addition to the use of power generators of the present invention for solar generation, the power generator of the present invention, in particular the embodiments of FIGS. 1 to 6 hereof, may be produced for vehicle-sized engines to very large power system sizes. The power generator hereof, when operated in the manner described, produces energy and power at higher efficiency and lower emission levels, and at a higher reliability than competing diesel and gas turbine systems. The power generator of the present invention differs from existing state of the art combustion engines in the following important ways:
Most engines burn fuel in normal air environments using the approximately 21% oxygen level in the air to enter into a chemical reaction with the selected fuel. The power generator of the present invention uses enriched O2 combustion.
A diesel engine as described with respect to FIGS. 1 to 6 hereof uses enriched O2 combustion which would begin with a 35% O2, 65% Argon mix, and then the mixture would be modified to optimize the engine performance, probably increasing the percentage of O2 to Argon as more familiarity and experience with control is gained. The first described embodiment uses Argon as the noble gas and uses an O2, Argon (Ar) fuel mix as a combustion environment rather than an O2, N2, fuel mix, which occurs when air is used. The gaseous mix with Argon, instead of N2, reduces NOx emissions to near zero, the quantity limited only by the level of purity of the fuel for no nitrogen therein, and any leakage of ambient air into the system. The result is a near zero undesirable emissions engine instead of a zero emission engine because, as a practical matter, trace amounts of nitrogen will remain in the O2—Ar mix, and as a result, some portion of the trace amounts of N2 will oxidize in the combustion process. Also, small amounts of N2 will most likely appear in most of the fuels used. Careful handling of the O2 and Ar separation and mixing process, and careful selection and handling of the fuels, should allow N2 in the system to be reduced to less than 1% of the amount found in the standard combustion process.
The 35% O2/65% Ar mixture benefit not only reduces NOx emission, it also increases engine output power above a factor of two and further increases efficiency. Note that the invention is not limited to a 35%/65% mix. Various mix ratios are possible and the optimum point will very from engine configuration to engine configuration. There will be a tendency to improve performance by increasing the O2 to Argon ratio. The 35%/65% ratio is used because of the published experience, as set forth in the background hereof, of diesel engines operating in 35% O2 enriched air environments, but one skilled in the art will appreciate that other ratios may be appropriate. The use of the an O2/Ar mixture provides another efficiency improvement due to the presence of Ar, noble (mono-atomic) gas in the combustion cycle gases instead of a di-atomic compound like N2, where a portion of the energy produced is lost in the excitation of the duo-atomic N—N bond. The combustion efficiency associated with this substitution increases on the order of 12% (for a 65% Ar substitution for N2). This efficiency gain results from removing the di-atomic gas, which itself absorbs approximately 12% of the combustion heat and wastefully throws the absorbed heat into the atmosphere, without expending the thermal energy on useful work. The single Ar atom does not suffer from heat absorbent internal oscillation between the di-atomic compounds and does not produce losses associated with the inter-atom oscillation. The result is a proportionally higher available efficiency engine. Additional gains will also be achieved due to higher operating temperatures.
Using a highly enriched oxygen environment in the combustion chamber assists in efficiency because it results in higher combustion temperatures and increases power because it allows greater amounts of fuel to be burned in each combustion cycle. However, the higher temperature and pressure creates certain instability in the combustion cycle. This invention overcomes these instabilities by utilizing multivariable modeling and control techniques that model the combustion timing, uniform expansion, the useful contribution of each combustion cycle to the uniform forward movement of the engine, the completeness of combustion, etc. The models are updated on the basis of ongoing testing (Design of Experiments, DOE) and normal running operations on the engine as a whole. Design of Experiments models each cylinder, and/or expansion chamber, and/or mixing chamber, and/or fuel variant that is used throughout the intake system through the fluid handling system, through the combustion cycle, through the heat recovery, and the exhaust systems. These models are then used to optimize the operation of the system as a whole by controlling the state of the composite collection of lower level subsystems to achieve the overall optimized control objectives based on historic understanding collected from the data and mathematical extrapolations. This invention utilizes the public domain modeling, control, and optimization techniques like neuro-nets and genetic algorithms, and the InSyst proprietary yield optimization technology (patent number) to control, stabilize, and optimize this cycle and system inclusive of its collection of subsystems.
In order for the exhaust gases to be as emission free as possible, the lubricating oil used between the cylinder and the piston, which enters the combustion cycle, must be eliminated. To accomplish this, an exceedingly low friction, long lasting, precision cylinder and piston surface are desirable. Such materials like alumna oxide and/or diamond coated alumna oxide may be employed. While the power generator hereof based upon engine 16 operating as a diesel engine is able to work without the low friction piston and use lubricants instead, as is traditionally done without affecting the efficiency objectives, the inclusion of the lubricant would somewhat increase emission levels and make it more difficult to obtain or meet a possible statutory zero emission standard.
While heat recovery cogeneration systems are commonly used in conjunction with gas turbines these systems are not commonly used in conjunction with internal combustion engines, especially diesel engines, because the high percentage of useful energy extraction results in relatively low temperature of emission gases, which is not typically converted at economically worthwhile costs into additional electricity. The power generator described herein is applicable for both internal and external combustion engines. However, in this invention, unlike standard internal combustion engine applications, the heat recovery and gas separation system is an economically useful part of the system as a whole. This is true in part because of the inventive use of the heat recovery system as both a heat recovery system and a gas separator, in part due to the higher temperature of the exit gases of the engine because of the higher temperature combustion cycle, in part because of the need to recover the Argon from the exit gases and re-circulate it back into the combustion cycle, and in part because of the high value in the preferred embodiment of using the CO2 exiting the combustion cycle to accelerate growth of algae, which in turn is used locally to produce fuels for the engine itself. When fuel is burned in an O2/Ar gaseous environment, the post combustion exhaust gases consist of mostly Ar, H2O (water), CO2 and small amounts of unburned O2. Because Ar is costly and not readily available, the power generator hereof includes an integral means for extracting the Ar from the exhaust gases, and allows the Ar to recycle into a new combustion cycle. The heat recovery system Stage 1 of the Heat Recovery and Gas Separation System extracts heat from the exhaust gases through volumetric expansion. Stage 2 of the Heat Recovery and Gas Separation System receives the reduced temperature gases from Stage 1 and through additional volumetric expansion reduces the exhaust gases from Stage 2 to temperatures below −40° C., typically on the order of −50C, the liquidification level of CO2, and much below the liquidification level of water. Stage 3 of the Heat Recovery and Gas Separation System (
A preferred embodiment would involve using the CO2 to feed through a piping system algae farm in the general vicinity. In this embodiment, it is envisioned that the oxygen emanating from the algae farm would be filtered out and piped in to the power generator site where it would be compressed and cryogenically cooled. Any CO2 mixed into the O2 would be separated and fed back to the algae farm through a return piping system. The O2, together with any O2 cryogenically separated from the air, would be placed in a tank for use in future combustion cycles. The algae at the algae farm would be processed into fuel and piped to the engine.
When the fuel produced from the algae or other agricultural process refinement is H2 instead of methane, ethane, methanol, ethanol, or an algae derived oil, and the H2 is used as the source of fuel for the power generator of the present invention, then CO2 is a waste product of the H2 production process and is in turn fed back into the algae growth cycle. The power generator using H2 as fuel would operate on a simpler cycle mixing H2 with Argon as a working gas-fuel mix. The heat recovery system design described above can be simplified making it necessary only to precipitate out the H2O and re-circulate the Ar into the combustion cycle. Alternatively, or in addition, the H2, which is a processed refined fuel product of the algae growth process, can be used as a fuel in other more conventional fuel cell applications.
Vehicles, including cars, trucks, trains, and/or ships, could also be equipped with the power generator hereof. The power generator hereof used in vehicles can use any clean fuel. A clean fuel is a fuel that contains hydrocarbon substances with, at most, trace quantities of sulfur, nitrogen, and other potentially polluting substances. Filters may be placed between the fuel tank and the fuel injection system to filter out unwanted substances if the fuel is not sufficiently clean. The fuels can be either liquid or gas. If the fuel is a gas, it is mixed with the Ar as shown in
In one embodiment, the vehicle equipped with the power generator of the invention, operating as a zero emission or near zero emission engine, would be connected to O2 supply, natural gas input supply, and a piping system which transports the separated CO2 to locations where the CO2 can be used for algae or other vegetation growth applications, or collected and distributed to a place or places where it can be used, thereby off-setting alternative CO2 production requirements. Such interconnection systems could be set up at home, work, shopping center parking facilities, or the places where vehicles are parked for extended periods of time. At the locations where fuel, O2, and collection of CO2 facilities are available such vehicles, which are running at very high efficiency, and at essentially zero emission levels, could supply electrical power to those facilities in a very reliable manner and at very low cost.
While the foregoing is directed to embodiments of the present invention, other and further embodiments of the invention may be devised without departing from the basic scope thereof, and the scope thereof is determined by the claims that follow.
1. A power generator, comprising:
- a supply of gas for the combustion of fuel therewith, said supply having substantially only a single species of gas therewith;
- a supply of fuel;
- a combustion chamber operatively coupled in fluid communication with said supply of gas and said supply of fuel and operatively coupled to an exhaust;
- a turbine in fluid communication with said exhaust and in fluid communication with a secondary exhaust therefrom, and further having an output shaft;
- a steam turbine in fluid communication with said secondary exhaust, said steam turbine further including a second output shaft.
2. The power generator of claim 1, further including a generator coupled to at least one of said output shaft and said second output shaft.
3. The power generator of claim 2, further including:
- a fuel supply separator; and
- a gas for combustion separator.
4. The power generator of claim 3, wherein:
- said gas for combustion separator includes: an ambient air intake: a chiller section capable of separating, from a stream of air brought into said separator, at least the nitrogen therein and leave behind, for combustion, at least the oxygen components of the air.
5. The power generator of claim 3, wherein:
- said fuel supply separator includes: a fuel intake: a chiller section capable of separating, from a stream of fuel brought into said separator, at least the nitrogen therein.
6. The power generator of claim 1, wherein said gas for combustion is high purity oxygen.
7. The power generator of claim 6, further including a biomass;
- a exhaust gas separator;
- a separator for separating oxygen from the environment of said biomass;
- a converter for converting the biomass to fuel to said engine combustion chamber;
- wherein, said power generator generates electricity using at least 75% of its operating fuel as fuel converted from said biomass.
8. The power generator of claim 6, further including additional, non-biomass based, solar generation.
9. The apparatus of claim 8, wherein said solar generation includes:
- a plurality of solar heaters
- a tank; and
- a steam turbine connected to the solar heaters and tank for the passage of superheated water therethrough.
10. The apparatus of claim 9, wherein:
- said solar generation alone provides a full rated capacity of a plant operated during the peak need and peak solar hours; and
- said steam turbine may be selectively energized by the passage of solar generation superheated water or from the exhaust stream of a gas turbine.
11. The apparatus of claim 10, wherein the solar generation may include:
- hot thermal fluid heated by solar collectors or hot thermal fluid that had been heated by solar collectors and is stored for this purpose;
- biomass fuel grown on the site of the power generator; and
- biomass fuel produced at off-site location and brought to the site.
12. A method of generating power; comprising the steps of:
- providing a combustion volume;
- providing, to the combustion volume a quantity of gas for combustion and a quantity of fuel;
- combusting the fuel gas mixture;
- passing the combusted mixture to a gas turbine, the combusted mixture passing therethrough and exerting work to provide energy at an output shaft thereof;
- passing the mixture, to a steam turbine, the mixture causing work to be generated and energy to be available on a steam turbine output shaft;
- connecting at least one of the output shaft and steam turbine shaft to an electrical generator;
- passing the exhaust from the steam turbine to a secondary steam turbine;
- recovering useful work from the secondary steam turbine output shaft as the exhaust passes therethrough;
- passing the exhaust, from a secondary turbine exhaust to a gas separation system; and
- recovering components of the exhaust.
13. The method of claim 12, further including the steps of:
- providing an air separator;
- passing air through the separator and separating at least nitrogen therefrom; and
- passing from the separator, to the combustion chamber, substantially pure oxygen forming the gas for combustion.
14. The method of claim 12, further including the steps of:
- supplying a fuel separator;
- passing fuel, through said separator and removing at least the nitrogen therefrom;
- passing the fuel on to the combustion chamber for combustion with the oxygen.
15. The method of claim 14, wherein the separator is a heat exchanger and the fuel is passed through one side of the heat exchanger and coolant, below the vapor phase temperature of nitrogen, is passed through the other side of the heat exchanger.
16. The method of claim 15, further including the steps of:
- separating, from the exhaust stream, at least carbon dioxide;
- providing a biomass;
- providing the separated carbon dioxide to the biomass;
- growing the biomass in the presence of sunlight and the carbon dioxide to form further biomass and O2; and removing the O2 therefrom;
- converting the grown biomass into a fuel;
- providing the fuel and the oxygen to the combustion volume;
- providing supplemental fuel, other than the biomass derived fuel, to the combustion volume in a ratio of less than 25%.
17. The method of claim 16, wherein an additional solar generation paradigm is used to augment the operation of the power generator, and wherein, said power generator generates electricity using at least 75% of its operating fuel as fuel converted from said biomass or from other solar means.
18. The method of claim 17, wherein the additional solar paradigm is a thermal solar paradigm.
19. The method of claim 17, wherein peak solar insulation and off-peak electrical demands in a specific location overlap or nearly overlap and, 25% of the fuel used for power generation is non-biomass fossil fuel, minus a modest reserve such that the solar generator and solar paradigm together are reproducing the maximum output possible during these peak hours.
20. The method of claim 19, wherein the thermal solar paradigm alone provides the full rated capacity of the plant operated during the peak need and peak solar hours
21. A method of claim 20, where the solar thermal paradigm may include
- a fluid heated by solar collectors or fluid that had been heated by solar collectors and is stored for this purpose
- biomass fuel grown on the site of the power generator
- biomass fuel produced at off-site location and brought to the site.
22. The method of claim 21, further including the step of:
- expanding the capacity of the power generator during on peak hours through the use of a combined cycle gas-steam turbine generator and wherein the full capacity of the gas turbine component of the combined cycle power generator a biomass fuel will be used.
Filed: Feb 20, 2007
Publication Date: Jan 3, 2008
Inventor: Arnold GOLDMAN (Jerusalem)
Application Number: 11/676,641
International Classification: F02B 53/00 (20060101);