Steam Generator

This application claims priority to U.S. Provisional Patent Application No. 63/660,924, filed on Jun. 17, 2024, U.S. Provisional Patent Application No. 63/753,812, filed on Feb. 4, 2025, and U.S. Provisional Patent Application No. 63/773,316, filed on Mar. 17, 2025, the entire contents of each of which is incorporated herein by reference.

This disclosure relates generally to systems and apparatus for high-pressure steam generation and more specifically to high-pressure steam generation where the working fluid includes a combination of flue gasses and steam.

Steam is a very effective working fluid but current methods of generating steam are limited by the thermal capabilities of boiler materials.

The present disclosure provides, in one aspect, a boiler including a pressure vessel defining a volume therein, an outlet in fluid communication with the volume, and an aperture open to the volume. A fuel is introduced into the volume and combusted to produce heat and a first gas therein. The aperture is configured to introduce steam into the volume. Both the first gas and the steam are exhausted through the outlet.

The present disclosure provides, in another aspect, a boiler including a pressure vessel defining a volume therein, a combustion chamber provided in the volume, and an outlet in fluid communication with the volume. A fuel is introduced into the combustion chamber and combusted to produce heat and a first gas therein. The combustion chamber is configured to introduce steam into the volume. Both the first gas and the steam are exhausted through the outlet.

The present disclosure provides, in another aspect, a power generation assembly including a turbine having an inlet and a boiler including a pressure vessel defining a volume therein, an outlet in fluid communication with the volume, and an aperture open to the volume. Fuel is introduced into the volume and combusted to generate heat and a first gas therein. The aperture is configured to introduce a first steam flow into the volume to mix with the first gas to form a first working fluid. The first working fluid exits the volume via the outlet and is directed into the turbine via the inlet.

Other features and aspects of the invention will become apparent by consideration of the detailed description and accompanying drawings. Any feature(s) described herein in relation to one aspect or embodiment may be combined with any other feature(s) described herein in relation to any other aspect or embodiment as appropriate and applicable.

Before any embodiments of the disclosure are explained in detail, it is to be understood that the disclosure is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the following drawings. The disclosure is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting.

The figures, described below, and the various embodiments used to describe the principles of the present disclosure are by way of illustration only and should not be construed in any way to limit the scope of the disclosure. Those skilled in the art will understand that the principles of the present disclosure may be implemented in any type of suitably arranged device or system.

Current methods of steam generation are generally limited by boiler materials. Specifically, peak temperatures of steam generators are generally below those of a gas turbine leading to lower efficiency. Burning fuels to provide heat on the outside of a boiler is also inefficient as a lot of heat and energy is lost to the air via the exhaust gasses. All other things being equal, overall increases in operating temperature for steam-based systems are conducive to efficient and clean operation.

Burning methane with air (e.g. an environment having approximately 21% oxygen) leads to oxidation of some of the nitrogen in the air and can produce nitrous oxide, which is both a pollutant and greenhouse gas. The oxygen content in air affects the flame temperature. Generally speaking, the higher the oxygen content in the air, the higher the temperature of the flame. For example, air being only 20% oxygen leads to a much colder flame temperature when burning a given fuel than burning that same fuel in an oxygen-rich environment. Boiler materials cannot withstand such a high heat especially on the outside of the boiler.

illustrates a high-pressure and high-efficiency steam generator or boilerin accordance with the present disclosure. The boileris configured such that a first fuel(e.g., methane) is combusted within a first volumeto produce a first gas(e.g. a flue gas) and heat. The boilerincludes a first steam sourceto introduce a first steam flowinto the first volumeto mix with the first gasand produce a first high-pressure working fluidtherein. The combined first working fluidmay then exit the first volumevia a discharge port(also referred to as an outlet) to be piped to one or more devices to do work (e.g., turbines, heat exchangers, directly to process, and the like). In the illustrated embodiment, the first fuelis methane but it is understood that in other embodiments different fuels may be used such as natural gas and the like.

As shown in, in some embodiments the boilerincludes a pressure vesselenclosing the first volumetherein, an internal combustor assemblyin fluid communication with the first volume, a first steam generatorin fluid communication with the first volume, and a discharge portopen to the first volume.

The pressure vesselof the generatorincludes one or more wallsat least partially enclosing the first volumetherein. In some embodiments, the wallsmay be formed from a high-strength steel, carbon fiber, and/or other materials of sufficient strength to withstand the pressure and heat generated within the first volumeduring operation. In the illustrated embodiment, the pressure vesselincludes a central cylindrical walland two semi-spherical end capsenclosing the ends of the central wallto form an overall capsule shape (see). In other embodiments, different sizes and shapes of pressure vesselmay be used.

As shown in, the first steam sourceincludes one or more aperturesopen to and in fluid communication with the first volume. During use, a first fluid(e.g., water) flows through the apertureand into the first volumeto form the first steam flow. In some embodiments, the first fluidis in a liquid state as it flows through the aperturewhereby the high-temperature conditions within the volumecause the first fluidto flash to steam as soon as the first fluidenters the volume. In such embodiments, the first fluidmay be warmed before flowing through the apertureto encourage the transition to steam upon passing through the aperture(discussed below). In still other embodiments, the first fluidmay already be sufficiently heated to be in a gaseous state as it flows through the aperture. In the illustrated embodiment, the one or more apertureseach include a nozzle open to and in fluid communication with the first volume. However, in other embodiments, the aperturemay include an orifice, a jet, a vent, a steam valve, a passage, and the like.

As shown in, the first steam sourcealso includes a first heat transfer elementin thermal communication with the first volume. As such, the heatgenerated by the combustion of the first fuelat least partially powers the first steam source. During use, the first heat transfer elementis configured to convey thermal energy from the first volumeto the first fluidcontained therein. In some embodiments, the first fluidis drawn from a reservoir, and pumped by a high-pressure pumpthrough the first heat transfer element. As the first fluidflows through the first heat transfer element, the first fluidabsorbs thermal energy from the first volumeand increases in temperature and/or changes phase. After the first fluidhas traveled through the first heat transfer element, the first fluidthen flows into the first volume, via a corresponding one of the one or more apertures, to form the first steam flow.

In the illustrated embodiment, the first heat transfer elementincludes a series of closely arranged pipes positioned along an inside surfaceof the wallsof the pressure vessel(e.g., is at last partially positioned within the first volume). As such, the first heat transfer elementserves to both warm the first fluidand cool the wallsof the pressure vesselto prevent overheating. While the illustrated heat transfer elementis attached to the inner surfaceof the walls, it is understood that in other embodiments the heat transfer elementmay also at least partially form the wallitself, serving as a structural component of the pressure vesselin lieu of a separate wall element. In still other embodiments, the first heat transfer elementmay be positioned separately within the first volumeaway from the wallsof the pressure vessel.

As shown in, the boileralso includes a second heat transfer element. During use, the second heat transfer elementis configured to convey thermal energy from the first volumeto a second fluid(e.g., water) contained therein. In some embodiments, the second fluidis drawn from a reservoirand pumped by a pumpthrough the second heat transfer element. As the second fluidflows through the second heat transfer element, the fluidabsorbs thermal energy from the first volumeand increases in temperature and/or changes phase. After the second fluidhas traveled through the second heat transfer element, the second fluidmay then be piped to external devices for use in additional processes where heated fluid is needed. Such processes may include but are not limited to, condensing the working fluid, chilling alternative working fluids (discussed below), warming external devices, and the like. In still other embodiments, the second fluidmay be cooled via an external radiator and recirculated back through the second heat transfer element, serving primarily to cool the wallsof the pressure vessel(discussed below).

In the illustrated embodiment, the second heat transfer elementincludes a series of closely arranged pipes positioned on an outside surfaceof the wallsof the pressure vessel. As such, the second heat transfer elementis also configured to help cool the wallsof the pressure vesselto prevent overheating. Furthermore, since the second heat transfer elementis positioned outside the first heat transfer element, the temperatures involved are likely lower than those of the first heat transfer element. As such, the second heat transfer elementmay provide a relatively “low heat” fluid source as opposed to the relatively “high heat” fluid source of the first heat transfer element.

In the illustrated embodiment, the first heat transfer elementand the second heat transfer elementdraw their fluids,, respectively, from separate reservoirs,and operate as two fluidly isolated circuits. However, in other embodiments, the two heat transfer elements,may draw from a common reservoir and/or be interlinked. In still other embodiments, the second heat transfer elementmay also direct its fluidinto the first volumevia an aperture (not shown) to serve as a supplemental steam supply.

As shown in, the internal combustorof the boileris configured to inject the fuel and oxidizers needed for combustion into the first volume. In the illustrated embodiment, the internal combustoris configured to inject the first fuel, and an oxygen-rich gasinto the first volume. However, in other embodiments, the internal combustormay be configured to inject additional fuels (e.g., the second fuel; see). In still other embodiments, the internal combustormay also inject additional chemicals and/or substances into the first volumeto help aid combustion within the first volume.

During operation, the internal combustoris configured so that the first fueland the oxygen-rich gasare introduced into the first volumein such a manner that the conditions at the point of ignition of the first fuel(e.g., the ignition environment) are optimal for combustion within the volume. More specifically, the internal combustormay include a series of nozzles, jets, baffles, orifices, manifolds, injectors, spreaders, and the like to direct the introduction of the first fuel, the oxygen-rich gas, and any supplemental substances with respect to each other and within the internal combustor.

In some embodiments, the internal combustoris configured to produce an oxygen-rich ignition environment. In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland between 80-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland between 82-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland between 84-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland between 86-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland between 88-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland between 90-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland between 92-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland between 94-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland between 95-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustoris configured to produce an ignition environment that includes a mixture of the first fueland approximately 94% pure oxygen (e.g., 1%, ±2%, ±3%, ±5%, ±10%).

The internal combustoralso includes a first or fuel injectorconfigured to inject the first fuelinto the first volumevia the internal combustor. In the illustrated embodiment where the first fuelis a gas, the first injectorincludes a high-pressure pumpthat draws the first fuelfrom a reservoir or tankand injects the first fuelinto the internal combustorof the first volume. In some embodiments, the pumpis configured to pressurize the first fuelto a pressure greater than the pressure within the first volume. In still other embodiments, the pumpis configured to pressurize the first fuelto a pressure greater than or equal to approximately 2000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the pumpis configured to pressurize the first fuelto a pressure between 2000 PSI and 3000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments where the first fuelis a liquid or solid, other forms of injection may also be used to collect the first fuelfrom the reservoirand inject it into the first volume, overcoming the high pressures (e.g., approximately 2000 PSI) contained therein.

The internal combustoralso includes a second or oxidizer injectorconfigured to inject oxygen-rich gasinto the first volumevia the internal combustor. In the illustrated embodiment where the oxidizer is a gas, the second injectorincludes a high-pressure pumpthat draws the oxygen-rich gasfrom a reservoir or tankand injects the oxygen-rich gasinto the first volume. In some embodiments, the pumpis configured to pressurize the oxygen-rich gasto a pressure greater than the pressure within the first volume. In still other embodiments, the pumpis configured to pressurize the oxygen-rich gasto a pressure greater than or equal to approximately 2000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the pumpis configured to pressurize the oxygen-rich gasto between 2000 PSI and 3000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments where the oxidizer is a liquid or solid, other forms of injection may also be used to collect the oxidizer from the reservoirand inject it into the first volume, overcoming the high pressures (e.g., approximately 2000 PSI) contained therein.

In some embodiments, additional injectors (not shown) may also be present to inject additional liquids, gasses, solids, additives and/or other substances into the first volumeand/or the internal combustor. In still other embodiments where the first fuelcarries its own oxidizer (or where an oxidizer is introduced in another manner), only a first injectormay be present. In still other embodiments, the pumps,are configured to pump the first fueland oxygen-rich gasat rates corresponding to the desired volumetric ratios for ideal combustion.

As shown in, the internal combustoris at least partially enclosed by a barrier. The barrier, in turn, defines one or more apertures or channels(see) extending therethrough to permit fluid communication between the internal combustorand the remainder of the first volume. During use, the barrierand corresponding channelsare configured so that the first gassesgenerated by the combustion of the first fuelwithin the internal combustorcan flow into the remainder of the first volume. The barrieris also configured to at least partially shield the exterior of the pressure vessel(e.g., the walls, the first heat transfer element, and the like) from the infrared radiant energy that is given off by the combustion process itself.

As shown in, the barrierof the internal combustorincludes a third heat transfer elementat least partially enclosing the internal combustorand in thermal communication with the first volume. During use, the third heat transfer elementexchanges thermal energy with the first volume(e.g., the internal combustor) to a third fluid(e.g., water) contained therein. In some embodiments, the third fluidis drawn from a reservoirand pumped by a high-pressure pumpthrough the third heat transfer element. As the third fluidflows through the third heat transfer element, the third fluidabsorbs thermal energy from the internal combustorand increases in temperature and/or changes phase. After the third fluidhas traveled through the third heat transfer element, the third fluidthen flows into the first volumevia one or more aperturesto form a second steam sourceand second steam flow.

In the illustrated embodiment, the third heat transfer elementincludes a series of closely arranged pipes at least partially enclosing the internal combustor(e.g., forming at least a portion of the barrier). As such, the third heat transfer elementserves to both warm the third fluidwhile also cooling and maintaining the integrity of the barrier.

In the illustrated embodiment, the one or more aperturesof the second steam sourceeach include a nozzle open to and in fluid communication with the first volume. However, in other embodiments, the aperturesmay include an orifice, a jet, a vent, a steam valve, a passage, and the like.

During operation of the steam generatorof, the first injectorand second injectorpressurize and inject the first fueland oxygen-rich gasinto the internal combustorof the first volume. The size, shape, and layout of the internal combustorcauses the first fueland oxygen-rich gasto mix and produce the desired ignition environment therein (e.g., an oxygen-rich environment as discussed above). The first fuelthen ignites and continues to burn within the internal combustorof the first volumeas both injectors,continue to operate. In the illustrated embodiment, the presence of an oxygen-rich ignition environment causes the first fuelto burn at a relatively higher temperature (e.g., approximately 4000 degrees Fahrenheit).

The combustion of the first fuel, in turn, generates the first gasand heat. In the illustrated embodiment, the combined high-pressure (e.g., approximately 2000 PSI; e.g., ±1%, ±2%, ±3%, ±5%, ±10%), high-temperature (e.g., approximately 4000 degrees; e.g., ±1%, ±2%, ±3%, ±5%, ±10%), and oxygen-rich ignition environment results in a first gasthat primarily contains large volumes of COand water vapor and only trace amounts to no nitrous oxide. In other embodiments, ash and other substances may also be present in trace amounts.

As combustion of the first fuelcontinues, the heated first gassesmay exit the internal combustorvia the channelsformed in the barrierand enter the rest of the first volume. Meanwhile, the majority of the infrared thermal energy generated by the combustion of the first fuelis absorbed by the barrierand third heat transfer element.

Furthermore, while combustion of the first fuelcontinues, the first fluidis pumped through the first heat transfer elementwhere it absorbs the thermal energy of the first volumeand begins to warm. After flowing through the first heat transfer element, the first fluidflows into the first volumevia the one or more aperturesof the first steam sourceto produce the first steam flow. The first steam flowthen mixes with the first gassescontained within the first volume.

Still further, while combustion of the first fuelcontinues, the third fluidis pumped through the third heat transfer elementwhere it exchanges thermal energy with the first volumeand begins to warm. After flowing through the third heat transfer element, the third fluidflows into the first volumevia the one or more aperturesof the second steam sourceto form the second steam flow. The second steam flowthen mixes with the first gassesand the first steam flowcontained within the first volumeto form a combined working fluid.

As the generator continues to operate, the above elements generally produce a set of operating condition within the first volumeduring steady-state operation. For example, in some embodiments the steady-state temperature in the first volumemay be between 500 degrees Fahrenheit and 1000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the steady-state temperature in the first volumemay be between 1000 degrees Fahrenheit and 1500 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature in the first volumemay be between 1500 degrees Fahrenheit and 2000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature in the first volumemay be between 2000 degrees Fahrenheit and 2500 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature in the first volumemay be between 2500 degrees Fahrenheit and 3000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature in the first volumemay be between 3000 degrees Fahrenheit and 3500 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature in the first volumemay be between 3500 degrees Fahrenheit and 4500 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the steady-state temperature in the first volumemay be between 3600 degrees Fahrenheit and 4400 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature in the first volumemay be between 3700 degrees Fahrenheit and 4000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature in the first volumemay be between 3800 degrees Fahrenheit and 4200 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature in the first volumemay be between 3900 degrees Fahrenheit and 4100 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature within the first volumemay be approximately 3500 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 3600 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 3700 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 3800 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 3900 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 4000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 4100 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%).

In some embodiments, the steady-state pressure within the first volumemay be between 500 PSI and 1000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the steady-state pressure within the first volumemay be between 1000 PSI and 1500 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state pressure within the first volumemay be between 1500 PSI and 2500 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state pressure within the first volumemay be between 1600 PSI and 2400 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state pressure within the first volumemay be between 1700 PSI and 2300 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state pressure within the first volumemay be between 1800 PSI and 2200 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state pressure within the first volumemay be between 1900 PSI and 2100 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state pressure within the first volumecan be approximately 1500 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 1600 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 1700 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 1800 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 1900 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 2000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 2100 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%), 2200 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%).

When the steady-state pressure and temperature are taken together, few substances can withstand the conditions inside the volume. As such, the first fuelis completely combusted forming little to no ash or undesirable by-products. To avoid the oxidization of nitrogen within the first volume, oxygen rich ignition conditions are used as discussed above.

Finally, the combined working fluidcontained within the first volumeat may then flow out of the first volumevia the discharge portto do work (discussed below). In some embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 700 to 1300 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 700 to 1000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 700 to 900 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 800 to 1200 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 900 to 1100 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat approximately 1000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%).

In some embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 700 to 2000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 800 to 1900 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 900 to 1700 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 800 to 1500 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 1000 to 1600 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 1100 to 1500 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 1200 to 1400 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat between approximately 900 to 1100 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluidcan flow out of the first volumethrough the discharge portat approximately 1300 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%).

After flowing through the discharge port, the high-pressure working fluidcan be directed into an inlet of one or more turbines, where it can be used to generate torque to drive a pump, a generator, and the like. In other embodiments, all or a portion of the high-pressure working fluidmay also be sent directly to process.

Althoughillustrates an example steam generator, various changes may be made to steam generator. For example, the sizes, shapes, and dimensions of the steam generatorand its individual components can vary as needed or desired. Also, the number and placement of various components of the steam generatorcan vary as needed or desired. In addition, the steam generatormay be used in any other suitable steam generation process and is not limited to the specific processes described above.

illustrates an example of a power cyclehaving the steam generatorincorporated therein. As shown inand described above, the steam generatoris in communication with a fuel sourceand an oxygen-rich gas or oxidizer source. In some embodiments, the fuel sourcemay include a reservoir or tankas described above. In other embodiments, the fuel sourcemay include attachment to a local utility or even a local well. In still other embodiments, a combination of the above may be used. Furthermore, the oxygen-rich gas sourcemay include a reservoir or tankas described above. In other embodiments, the oxygen-rich gas sourcemay include an oxygen generator that produces the gas on demand. In still other embodiments, a combination of the above may be used.

The generatormay also be in fluid communication with one or more fluid sources (e.g., water sources). As discussed above, the generatoritself may have one or more fluid sources associated therewith, each having a separate reservoir,,. In other embodiments, all fluids,,may be drawn from a common reservoirthat, in turn, is fed by the power cycle. More specifically, the power cyclemay include a pumpor other conveyance mechanism to pump reclaimed fluids from the working fluiddownstream of the work stations(e.g., water reclaimed by the separator, described below) back to the common sump. In still other embodiments, a subset of the fluids,,may be drawn from the common reservoir.

The power cyclemay also include one or more work stationswhere the working fluidis used to do work. In the illustrated embodiment, the work stationsinclude one or more turbines. During use, the high-pressure working fluidexits the first volumeof the generatorwhere it is directed into the inlet of at least one of the one or more the turbines. The turbines, in turn, receive the high-pressure working fluid, and output low-pressure working fluidand torque. In other embodiments, different forms of work stationsmay be used such as heat exchangers, and the like.

The power cyclealso includes a condenserpositioned downstream of the work station. During use, the condenseris configured to cool the working fluidsuch that any steam remaining therein will condense into a liquid state.

The power cyclefurther includes a CO/HO separatorpositioned downstream of the condenser. During use, the separatoris configured to physically separate the COgas from the condensed HO of the working fluid. Once separated, the separatoris configured to output the separated COgas via a first outputand output the separated HO via a second outputto be returned to the steam generator.

The power cyclefurther includes a biomass growth facility. In the illustrated embodiment, the biomass growth facilityreceives the separated COgas from the separator, compresses the gas using a compressor, and then uses the compressed COgas to grow various forms of vegetation such as, but not limited to, algae, moss, wood, and the like.

illustrate another embodiment of the steam generator. The steam generatoris substantially similar to the steam generatordescribed above so only the differences between the two embodiments will be described in detail herein. As shown in, the illustrated steam generatoris configured to burn both the first fueland a second fuelduring operation. Specifically, the generatoris configured to burn “wet biomass” as the second fuel to supplement the combustion of the first fuel. In some embodiments, a wet biomassmay include but is not limited to algae, moss, wood, and the like that are not subject to any drying operations before being introduced into the internal combustorand therefore retain most if not all of their natural moisture content. As a clean, renewable fuel stock, wet biomassoffers a high gross thermal combustion energy due to the presence of volatile hydrocarbons not present in dry biomass materials. The wet biomassalso contains a relatively high water content.

The steam generatorincludes a third injectorconfigured to inject the second fuelinto the first volumevia the internal combustor. In the illustrated embodiment where the second fuelis in a solid state, the third injectorincludes one or more biomass pressure chamberswhich can provide a metered, incremental supply of wet biomassto the combustorof the steam generatorunder conditions which do not cause the temperature in the combustorto significantly drop, and in amounts which can be cleanly combusted along with the first fuel. In some embodiments, the wet biomassis stored in a reservoirat or near atmospheric pressure, and then undergoes a pressing or airlock processwhere a select amount of the biomass is transitioned into the biomass pressure chambersat or near the working pressure of the first volume. Once in the pressure chamber, the wet biomassmay be injected into the internal combustoras needed to support combustion overall.