STEAM GENERATOR

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

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.

FIELD

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.

BACKGROUND

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

SUMMARY

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.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 illustrates one embodiment of a steam generator in accordance with the disclosure.

FIG. 2 illustrates another embodiment of a steam generator.

FIG. 3 is a side plan view of the steam generator of FIG. 1.

FIG. 4 is a plan view of a power cycle with the steam generator of FIG. 1 incorporated therein.

FIG. 5 is a plan view of another embodiment of a power cycle with the steam generator of FIG. 2 incorporated therein.

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.

DETAILED DESCRIPTION

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.

FIG. 1 illustrates a high-pressure and high-efficiency steam generator or boiler 100 in accordance with the present disclosure. The boiler 100 is configured such that a first fuel 102 (e.g., methane) is combusted within a first volume 108 to produce a first gas 114 (e.g. a flue gas) and heat 118. The boiler 100 includes a first steam source 126 to introduce a first steam flow 130 into the first volume 108 to mix with the first gas 114 and produce a first high-pressure working fluid 138 therein. The combined first working fluid 138 may then exit the first volume 108 via a discharge port 136 (also referred to as an outlet 136) 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 fuel 102 is methane but it is understood that in other embodiments different fuels may be used such as natural gas and the like.

As shown in FIG. 1, in some embodiments the boiler 100 includes a pressure vessel 104 enclosing the first volume 108 therein, an internal combustor assembly 110 in fluid communication with the first volume 108, a first steam generator 126 in fluid communication with the first volume 108, and a discharge port 136 open to the first volume 108.

The pressure vessel 104 of the generator 100 includes one or more walls 106 at least partially enclosing the first volume 108 therein. In some embodiments, the walls 106 may 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 volume 108 during operation. In the illustrated embodiment, the pressure vessel 104 includes a central cylindrical wall 106a and two semi-spherical end caps 106b enclosing the ends of the central wall 106a to form an overall capsule shape (see FIG. 3). In other embodiments, different sizes and shapes of pressure vessel 104 may be used.

As shown in FIG. 1, the first steam source 126 includes one or more apertures 156 open to and in fluid communication with the first volume 108. During use, a first fluid 140 (e.g., water) flows through the aperture 156 and into the first volume 108 to form the first steam flow 130. In some embodiments, the first fluid 140 is in a liquid state as it flows through the aperture 156 whereby the high-temperature conditions within the volume 108 cause the first fluid 140 to flash to steam as soon as the first fluid 140 enters the volume 108. In such embodiments, the first fluid 140 may be warmed before flowing through the aperture 156 to encourage the transition to steam upon passing through the aperture 156 (discussed below). In still other embodiments, the first fluid 140 may already be sufficiently heated to be in a gaseous state as it flows through the aperture 156. In the illustrated embodiment, the one or more apertures 156 each include a nozzle open to and in fluid communication with the first volume 108. However, in other embodiments, the aperture 156 may include an orifice, a jet, a vent, a steam valve, a passage, and the like.

As shown in FIG. 1, the first steam source 126 also includes a first heat transfer element 132 in thermal communication with the first volume 108. As such, the heat 118 generated by the combustion of the first fuel 102 at least partially powers the first steam source 126. During use, the first heat transfer element 132 is configured to convey thermal energy from the first volume 108 to the first fluid 140 contained therein. In some embodiments, the first fluid 140 is drawn from a reservoir 162, and pumped by a high-pressure pump 166 through the first heat transfer element 132. As the first fluid 140 flows through the first heat transfer element 132, the first fluid 140 absorbs thermal energy from the first volume 108 and increases in temperature and/or changes phase. After the first fluid 140 has traveled through the first heat transfer element 132, the first fluid 140 then flows into the first volume 108, via a corresponding one of the one or more apertures 156, to form the first steam flow 130.

In the illustrated embodiment, the first heat transfer element 132 includes a series of closely arranged pipes positioned along an inside surface 148 of the walls 106 of the pressure vessel 104 (e.g., is at last partially positioned within the first volume 108). As such, the first heat transfer element 132 serves to both warm the first fluid 140 and cool the walls 106 of the pressure vessel 104 to prevent overheating. While the illustrated heat transfer element 132 is attached to the inner surface 148 of the walls 106, it is understood that in other embodiments the heat transfer element 132 may also at least partially form the wall 106 itself, serving as a structural component of the pressure vessel 104 in lieu of a separate wall element. In still other embodiments, the first heat transfer element 132 may be positioned separately within the first volume 108 away from the walls 106 of the pressure vessel 104.

As shown in FIG. 1, the boiler 100 also includes a second heat transfer element 128. During use, the second heat transfer element 128 is configured to convey thermal energy from the first volume 108 to a second fluid 170 (e.g., water) contained therein. In some embodiments, the second fluid 170 is drawn from a reservoir 174 and pumped by a pump 178 through the second heat transfer element 128. As the second fluid 170 flows through the second heat transfer element 128, the fluid 170 absorbs thermal energy from the first volume 108 and increases in temperature and/or changes phase. After the second fluid 170 has traveled through the second heat transfer element 128, the second fluid 170 may 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 138, chilling alternative working fluids (discussed below), warming external devices, and the like. In still other embodiments, the second fluid 170 may be cooled via an external radiator and recirculated back through the second heat transfer element 128, serving primarily to cool the walls 106 of the pressure vessel 104 (discussed below).

In the illustrated embodiment, the second heat transfer element 128 includes a series of closely arranged pipes positioned on an outside surface 182 of the walls 106 of the pressure vessel 104. As such, the second heat transfer element 128 is also configured to help cool the walls 106 of the pressure vessel 104 to prevent overheating. Furthermore, since the second heat transfer element 128 is positioned outside the first heat transfer element 132, the temperatures involved are likely lower than those of the first heat transfer element 132. As such, the second heat transfer element 128 may provide a relatively “low heat” fluid source as opposed to the relatively “high heat” fluid source of the first heat transfer element 132.

In the illustrated embodiment, the first heat transfer element 132 and the second heat transfer element 128 draw their fluids 140, 170, respectively, from separate reservoirs 162, 174 and operate as two fluidly isolated circuits. However, in other embodiments, the two heat transfer elements 128, 132 may draw from a common reservoir and/or be interlinked. In still other embodiments, the second heat transfer element 128 may also direct its fluid 170 into the first volume 108 via an aperture (not shown) to serve as a supplemental steam supply.

As shown in FIG. 1, the internal combustor 110 of the boiler 100 is configured to inject the fuel and oxidizers needed for combustion into the first volume 108. In the illustrated embodiment, the internal combustor 110 is configured to inject the first fuel 102, and an oxygen-rich gas 186 into the first volume 108. However, in other embodiments, the internal combustor 110 may be configured to inject additional fuels (e.g., the second fuel 154; see FIGS. 2 and 3). In still other embodiments, the internal combustor 110 may also inject additional chemicals and/or substances into the first volume 108 to help aid combustion within the first volume 108.

During operation, the internal combustor 110 is configured so that the first fuel 102 and the oxygen-rich gas 186 are introduced into the first volume 108 in such a manner that the conditions at the point of ignition of the first fuel 102 (e.g., the ignition environment) are optimal for combustion within the volume 108. More specifically, the internal combustor 110 may include a series of nozzles, jets, baffles, orifices, manifolds, injectors, spreaders, and the like to direct the introduction of the first fuel 102, the oxygen-rich gas 186, and any supplemental substances with respect to each other and within the internal combustor 110.

In some embodiments, the internal combustor 110 is configured to produce an oxygen-rich ignition environment. In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and between 80-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and between 82-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and between 84-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and between 86-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and between 88-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and between 90-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and between 92-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and between 94-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and between 95-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the first fuel 102 and approximately 94% pure oxygen (e.g., 1%, ±2%, ±3%, ±5%, ±10%).

The internal combustor 110 also includes a first or fuel injector 112 configured to inject the first fuel 102 into the first volume 108 via the internal combustor 110. In the illustrated embodiment where the first fuel 102 is a gas, the first injector 112 includes a high-pressure pump 194 that draws the first fuel 102 from a reservoir or tank 198 and injects the first fuel 102 into the internal combustor 110 of the first volume 108. In some embodiments, the pump 194 is configured to pressurize the first fuel 102 to a pressure greater than the pressure within the first volume 108. In still other embodiments, the pump 194 is configured to pressurize the first fuel 102 to a pressure greater than or equal to approximately 2000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the pump 194 is configured to pressurize the first fuel 102 to a pressure between 2000 PSI and 3000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments where the first fuel 102 is a liquid or solid, other forms of injection may also be used to collect the first fuel 102 from the reservoir 198 and inject it into the first volume 108, overcoming the high pressures (e.g., approximately 2000 PSI) contained therein.

The internal combustor 110 also includes a second or oxidizer injector 116 configured to inject oxygen-rich gas 186 into the first volume 108 via the internal combustor 110. In the illustrated embodiment where the oxidizer is a gas, the second injector 116 includes a high-pressure pump 204 that draws the oxygen-rich gas 186 from a reservoir or tank 208 and injects the oxygen-rich gas 186 into the first volume 108. In some embodiments, the pump 204 is configured to pressurize the oxygen-rich gas 186 to a pressure greater than the pressure within the first volume 108. In still other embodiments, the pump 204 is configured to pressurize the oxygen-rich gas 186 to a pressure greater than or equal to approximately 2000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the pump 194 is configured to pressurize the oxygen-rich gas 186 to 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 reservoir 208 and inject it into the first volume 108, 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 volume 108 and/or the internal combustor 110. In still other embodiments where the first fuel 102 carries its own oxidizer (or where an oxidizer is introduced in another manner), only a first injector 112 may be present. In still other embodiments, the pumps 194, 204 are configured to pump the first fuel 102 and oxygen-rich gas 186 at rates corresponding to the desired volumetric ratios for ideal combustion.

As shown in FIG. 1, the internal combustor 110 is at least partially enclosed by a barrier 122. The barrier 122, in turn, defines one or more apertures or channels 123 (see FIG. 2) extending therethrough to permit fluid communication between the internal combustor 110 and the remainder of the first volume 108. During use, the barrier 122 and corresponding channels 123 are configured so that the first gasses 114 generated by the combustion of the first fuel 102 within the internal combustor 110 can flow into the remainder of the first volume 108. The barrier 122 is also configured to at least partially shield the exterior of the pressure vessel 104 (e.g., the walls 106, the first heat transfer element 132, and the like) from the infrared radiant energy that is given off by the combustion process itself.

As shown in FIG. 1, the barrier 122 of the internal combustor 110 includes a third heat transfer element 212 at least partially enclosing the internal combustor 110 and in thermal communication with the first volume 108. During use, the third heat transfer element 212 exchanges thermal energy with the first volume 108 (e.g., the internal combustor 110) to a third fluid 216 (e.g., water) contained therein. In some embodiments, the third fluid 216 is drawn from a reservoir 220 and pumped by a high-pressure pump 224 through the third heat transfer element 212. As the third fluid 216 flows through the third heat transfer element 212, the third fluid 216 absorbs thermal energy from the internal combustor 110 and increases in temperature and/or changes phase. After the third fluid 216 has traveled through the third heat transfer element 212, the third fluid 216 then flows into the first volume 108 via one or more apertures 228 to form a second steam source 232 and second steam flow 236.

In the illustrated embodiment, the third heat transfer element 212 includes a series of closely arranged pipes at least partially enclosing the internal combustor 110 (e.g., forming at least a portion of the barrier 122). As such, the third heat transfer element 212 serves to both warm the third fluid 216 while also cooling and maintaining the integrity of the barrier 122.

In the illustrated embodiment, the one or more apertures 228 of the second steam source 232 each include a nozzle open to and in fluid communication with the first volume 108. However, in other embodiments, the apertures 228 may include an orifice, a jet, a vent, a steam valve, a passage, and the like.

During operation of the steam generator 100 of FIG. 1, the first injector 112 and second injector 116 pressurize and inject the first fuel 102 and oxygen-rich gas 186 into the internal combustor 110 of the first volume 108. The size, shape, and layout of the internal combustor 110 causes the first fuel 102 and oxygen-rich gas 186 to mix and produce the desired ignition environment therein (e.g., an oxygen-rich environment as discussed above). The first fuel 102 then ignites and continues to burn within the internal combustor 110 of the first volume 108 as both injectors 112, 116 continue to operate. In the illustrated embodiment, the presence of an oxygen-rich ignition environment causes the first fuel 102 to burn at a relatively higher temperature (e.g., approximately 4000 degrees Fahrenheit).

The combustion of the first fuel 102, in turn, generates the first gas 114 and heat 118. 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 gas 114 that primarily contains large volumes of CO₂ and 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 fuel 102 continues, the heated first gasses 114 may exit the internal combustor 110 via the channels 123 formed in the barrier 122 and enter the rest of the first volume 108. Meanwhile, the majority of the infrared thermal energy generated by the combustion of the first fuel 102 is absorbed by the barrier 122 and third heat transfer element 212.

Furthermore, while combustion of the first fuel 102 continues, the first fluid 140 is pumped through the first heat transfer element 132 where it absorbs the thermal energy of the first volume 108 and begins to warm. After flowing through the first heat transfer element 132, the first fluid 140 flows into the first volume 108 via the one or more apertures 156 of the first steam source 126 to produce the first steam flow 130. The first steam flow 130 then mixes with the first gasses 114 contained within the first volume 108.

Still further, while combustion of the first fuel 102 continues, the third fluid 216 is pumped through the third heat transfer element 212 where it exchanges thermal energy with the first volume 108 and begins to warm. After flowing through the third heat transfer element 212, the third fluid 216 flows into the first volume 108 via the one or more apertures 228 of the second steam source 232 to form the second steam flow 236. The second steam flow 236 then mixes with the first gasses 114 and the first steam flow 130 contained within the first volume 108 to form a combined working fluid 138.

As the generator continues to operate, the above elements generally produce a set of operating condition within the first volume 108 during steady-state operation. For example, in some embodiments the steady-state temperature in the first volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may be between 500 PSI and 1000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the steady-state pressure within the first volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 can 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 108. As such, the first fuel 102 is completely combusted forming little to no ash or undesirable by-products. To avoid the oxidization of nitrogen within the first volume 108, oxygen rich ignition conditions are used as discussed above.

Finally, the combined working fluid 138 contained within the first volume 108 at may then flow out of the first volume 108 via the discharge port 136 to do work (discussed below). In some embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 700 to 1300 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 700 to 1000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 700 to 900 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 800 to 1200 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 900 to 1100 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at approximately 1000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%).

In some embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 700 to 2000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 800 to 1900 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 900 to 1700 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 800 to 1500 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 1000 to 1600 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 1100 to 1500 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 1200 to 1400 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 900 to 1100 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at approximately 1300 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%).

After flowing through the discharge port 136, the high-pressure working fluid 138 can be directed into an inlet of one or more turbines 5016, 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 fluid 138 may also be sent directly to process.

Although FIG. 1 illustrates an example steam generator 100, various changes may be made to steam generator 100. For example, the sizes, shapes, and dimensions of the steam generator 100 and its individual components can vary as needed or desired. Also, the number and placement of various components of the steam generator 100 can vary as needed or desired. In addition, the steam generator 100 may be used in any other suitable steam generation process and is not limited to the specific processes described above.

FIG. 4 illustrates an example of a power cycle 5000 having the steam generator 100 incorporated therein. As shown in FIG. 4 and described above, the steam generator 100 is in communication with a fuel source 5004 and an oxygen-rich gas or oxidizer source 5008. In some embodiments, the fuel source 5004 may include a reservoir or tank 198 as described above. In other embodiments, the fuel source 5004 may 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 source 5008 may include a reservoir or tank 208 as described above. In other embodiments, the oxygen-rich gas source 5008 may include an oxygen generator that produces the gas on demand. In still other embodiments, a combination of the above may be used.

The generator 100 may also be in fluid communication with one or more fluid sources (e.g., water sources). As discussed above, the generator 100 itself may have one or more fluid sources associated therewith, each having a separate reservoir 162, 174, 220. In other embodiments, all fluids 140, 170, 216 may be drawn from a common reservoir 5012 that, in turn, is fed by the power cycle 5000. More specifically, the power cycle 5000 may include a pump 5018 or other conveyance mechanism to pump reclaimed fluids from the working fluid 138 downstream of the work stations 5016 (e.g., water reclaimed by the separator 5028, described below) back to the common sump 5012. In still other embodiments, a subset of the fluids 140, 170, 216 may be drawn from the common reservoir 5012.

The power cycle 5000 may also include one or more work stations 5016 where the working fluid 138 is used to do work. In the illustrated embodiment, the work stations 5016 include one or more turbines. During use, the high-pressure working fluid 138 exits the first volume 108 of the generator 100 where it is directed into the inlet of at least one of the one or more the turbines 5016. The turbines 5016, in turn, receive the high-pressure working fluid 138, and output low-pressure working fluid 138 and torque. In other embodiments, different forms of work stations 5016 may be used such as heat exchangers, and the like.

The power cycle 5000 also includes a condenser 5024 positioned downstream of the work station 5016. During use, the condenser 5024 is configured to cool the working fluid 138 such that any steam remaining therein will condense into a liquid state.

The power cycle 5000 further includes a CO₂/H₂O separator 5028 positioned downstream of the condenser 5024. During use, the separator 5028 is configured to physically separate the CO₂ gas from the condensed H₂O of the working fluid 138. Once separated, the separator 5028 is configured to output the separated CO₂ gas via a first output 5032 and output the separated H₂O via a second output 5036 to be returned to the steam generator 100.

The power cycle 5000 further includes a biomass growth facility 5040. In the illustrated embodiment, the biomass growth facility 5040 receives the separated CO₂ gas from the separator 5028, compresses the gas using a compressor 5044, and then uses the compressed CO₂ gas to grow various forms of vegetation such as, but not limited to, algae, moss, wood, and the like.

FIGS. 2 and 3 illustrate another embodiment of the steam generator 1100. The steam generator 1100 is substantially similar to the steam generator 100 described above so only the differences between the two embodiments will be described in detail herein. As shown in FIG. 2, the illustrated steam generator 1100 is configured to burn both the first fuel 102 and a second fuel 154 during operation. Specifically, the generator 1100 is configured to burn “wet biomass 154” as the second fuel to supplement the combustion of the first fuel 102. In some embodiments, a wet biomass 154 may 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 combustor 110 and therefore retain most if not all of their natural moisture content. As a clean, renewable fuel stock, wet biomass 154 offers a high gross thermal combustion energy due to the presence of volatile hydrocarbons not present in dry biomass materials. The wet biomass 154 also contains a relatively high water content.

The steam generator 1100 includes a third injector 1500 configured to inject the second fuel 154 into the first volume 108 via the internal combustor 110. In the illustrated embodiment where the second fuel 154 is in a solid state, the third injector 1500 includes one or more biomass pressure chambers 1512 which can provide a metered, incremental supply of wet biomass 154 to the combustor 110 of the steam generator 100 under conditions which do not cause the temperature in the combustor 110 to significantly drop, and in amounts which can be cleanly combusted along with the first fuel 102. In some embodiments, the wet biomass 154 is stored in a reservoir 1504 at or near atmospheric pressure, and then undergoes a pressing or airlock process 1508 where a select amount of the biomass is transitioned into the biomass pressure chambers 1512 at or near the working pressure of the first volume 108. Once in the pressure chamber 1512, the wet biomass 154 may be injected into the internal combustor 110 as needed to support combustion overall.

During operation, the internal combustor 110 is configured so that the second fuel 154 is introduced into the first volume 108 in such a manner that the conditions at the point of ignition of the second fuel 154 (e.g., the ignition environment) are optimal for combustion within the volume 108. More specifically, the internal combustor 110 may include a series of nozzles, jets, baffles, orifices, manifolds, injectors, spreaders, and the like to direct the introduction of the second fuel 154, the oxygen-rich gas 186, the first fuel 102, and any supplemental substances with respect to each other and within the internal combustor 110.

In still other embodiments, the internal combustor 110 is configured to produce an oxygen-rich ignition environment for the second fuel 154. In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and between 80-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and between 82-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and between 84-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and between 86-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and between 88-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and between 90-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and between 92-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and between 94-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and between 95-100% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the internal combustor 110 is configured to produce an ignition environment that includes a mixture of the second fuel 154 and approximately 94% pure oxygen (e.g., ±1%, ±2%, ±3%, ±5%, ±10%).

During use, the wet biomass 154 is combusted under high oxygen, high-heat conditions within the internal combustor 110 to produce a second gas 1516 and a second amount of heat 1520. Specifically, the high water content in the wet biomass 154 is converted to steam while the hydrocarbons (including volatile hydrocarbons) of the wet biomass 154 are cleanly combusted to produce additional steam and CO₂.

During operation of the steam generator 1100 of FIGS. 2 and 3 operate in a similar fashion to the steam generator 100 discussed above. As such, only the differences will be described in detail herein. In concert with the operation of the first injector 112 and the second injector 116, the third injector 1500 injects the second fuel 154 into the internal combustor 110 of the first volume 108. The size, shape, and layout of the internal combustor 110, in turn, causes the second fuel 154, the first fuel 102, and the oxygen-rich gas 186 to mix and produce the desired ignition environment therein (e.g., an oxygen-rich, high-pressure, and high-temperature conditions). The second fuel 154 then ignites and continues to combust within the internal combustor 110 as all three injectors 112, 116, 1500 continue to operate.

As discussed above, the combustion of the second fuel 154, in turn, generates the second gas 1516 and heat 1520. 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 for the second fuel 154 results in a second gas 1516 that primarily contains large volumes of CO₂ and steam.

As combustion of the second fuel 154 continues, the heated second gasses 1516 may exit the internal combustor 110 via the channels 123 formed in the barrier 122 and enter the rest of the first volume 108 to combine with the first gasses 114, the first steam flow 130, and the second steam flow 236 to form the combined working fluid 138.

Furthermore, while combustion of the first fuel 102 continues, the first fluid 140 is pumped through the first heat transfer element 132 where it absorbs the thermal energy of the first volume 108 and begins to warm. After flowing through the first heat transfer element 132, the first fluid 140 flows into the first volume 108 via the one or more apertures 156 of the first steam source 126 to produce the first steam flow 130. The first steam flow 130 then mixes with the first gasses 114 contained within the first volume 108.

Still further, while combustion of the first fuel 102 continues, the third fluid 216 is pumped through the third heat transfer element 212 where it exchanges thermal energy with the first volume 108 and begins to warm. After flowing through the third heat transfer element 212, the third fluid 216 flows into the first volume 108 via the one or more apertures 228 of the second steam source 232 to form the second steam flow 236. The second steam flow 236 then mixes with the first gasses 114 and the first steam flow 130 contained within the first volume 108 to form a combined working fluid 138.

As the generator 1100 continues to operate, the above elements generally produce a set of operating condition within the first volume 108 during steady-state operation. For example, in some embodiments the steady-state temperature in the first volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may be between 3700 degrees Fahrenheit and 43000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the steady-state temperature in the first volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may be between 500 PSI and 1000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the steady-state pressure within the first volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 may 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 volume 108 can 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%).

Finally, the combined working fluid 138 contained within the first volume 108 at the above identified conditions may then flow out of the first volume 108 via the discharge port 136 to do work (discussed below). In some embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 700 to 1300 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 700 to 1000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 700 to 900 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 800 to 1200 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 900 to 1100 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at approximately 1000 degrees Fahrenheit (e.g., ±1%, ±2%, ±3%, ±5%, ±10%).

In some embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 700 to 2000 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 800 to 1900 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 900 to 1700 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 800 to 1500 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 1000 to 1600 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 1100 to 1500 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 1200 to 1400 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at between approximately 900 to 1100 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%). In still other embodiments, the working fluid 138 can flow out of the first volume 108 through the discharge port 136 at approximately 1300 PSI (e.g., ±1%, ±2%, ±3%, ±5%, ±10%).

In some embodiments, the ratio of how much of the first fuel 102 is burned relative to the second fuel 154 may be adjustable. For example, in some embodiments the generator 1100 may be operable in a first condition where the ratio of first fuel 102 to second fuel 154 is reduced (e.g., less volume of the first fuel 102 is burned per unit of the second fuel 154). In such embodiments, the first condition may be used in instances where the generator 1100 requires a reduced thermal input. Such conditions may include operating in a steady-state condition, under reduced load, or in hotter environmental conditions. In still other embodiments, the generator 1100 may be operable in a second condition where the ratio of the first fuel 102 to second fuel 154 may be increased (e.g., a greater volume of the first fuel 102 is burned per unit of the second fuel 154). In such embodiments, the second condition may be used in instances where the generator 1100 requires a larger thermal input such as during start up, under increased load, or subject to colder environmental conditions. In still other embodiments, the generator 1100 may be operable in a third condition where only the first fuel 102 is burned and the second fuel 154 is shutoff. In still other embodiments, the generator 1100 may be operable in a fourth condition where only the second fuel 154 is burned and the first fuel 102 is shutoff.

FIG. 5 illustrates another embodiment of a power cycle 6000. The power cycle 6000 is substantially similar to the power cycle 5000 discussed above. As such, only the differences will be described in detail herein. The power cycle 6000 includes the steam generator 1100 incorporated therein. The steam generator 1100, in turn, is in communication with a first fuel source 6004, an oxygen-rich gas or oxidizer source 6008, and a second fuel source 6008.

In some embodiments, the second fuel source 6008 may include a reservoir or tank 1504 in which wet biomass 154 may be collected and stored. In such embodiments, the biomass 154 within the reservoir 1504 may be procured from the biomass growth facility 6040 incorporated into the power cycle 6000. As such, the current power cycle 6000 is configured such that the second fuel source 6008 may be at least partially self-sufficient as the CO₂ contained within the working fluid 138 of the steam generator 1100 may subsequently be used, via the biomass growth facility 5040, to grow the very biomass burned by the steam generator 1100. Stated differently, the carbon-dioxide fed blooms of algae can be harvested, partially dehydrated and re-fed to the system as wet biomass 154.

The power cycle 6000 may also include a fluid (e.g., water) access point 7024 to add or remove fluid from the circuit during operation. In instances where the generator 1100 and power cycle 6000 are consuming more fluid than the generator 1100 producing via combustion, the power cycle 6000 may draw water into the system via the access point 7024. In contrast, in instances where the generator 1100 is producing more fluid via combustion than the generator 1100 and cycle 6000 are consuming, any excess water may be extracted via the access point 7024 and used. Specifically, the large volume of moisture contained within the wet biomass 154 increases the volume of steam produced by the generator 1100 during combustion, as such, excess water may be produced.

As shown in FIG. 5, the power cycle 6000 is additionally coupled to an energy distribution network 7000. The distribution network 7000 includes a pump 7004 driven by the turbine 5016, a water chiller 7008, and one or more point loads 7012. In the illustrated embodiment, the pump 7004, water chiller 7008, and point loads 7012 are all interconnected via a network of pipes 7020.

During use, the power cycle 6000 powers the turbine 5016 as discussed above which, in turn, drives the pump 7004. The pump 7004 then pumps a second working fluid 7016 through the distribution network 7020. In some embodiments, the second working fluid 7016 includes a liquid (e.g., water) that is pumped through the network 7020 under pressure. In other embodiments, the second working fluid 7016 includes a gas (e.g., air) that is compressed by the pump 7004 and circulated through the network under pressure. The second working fluid 7016 conveys both kinetic and thermal energy along the network 7020 during operation.

As shown in FIG. 5, the water chiller 7008 is in fluid communication with network 7020 and positioned immediately downstream of the pump 7004. During use, the water chiller 7008 receives thermal energy from the steam generator 1100 and utilizes the heat to cool the working fluid 7016 using an absorption refrigeration process. In some embodiments, the water chiller 7008 receives the thermal energy in the form of heat removed from the working fluid 138 by the condenser 5024. However, in other embodiments, different forms of conveying thermal energy from the generator 1100 to the water chiller 7008 may be used.

As shown in FIG. 5, the point loads 7012 of the network 7000 are positioned remotely from the generator 1100. During use, the point loads 7012 receive the second working fluid 7016 via the network 7020 and use the fluid 7016 to conduct work. For example, the illustrated point loads 7012 include heat exchangers 7030 to exchange thermal energy with the fluid 7016 for cooling. In other examples, the point loads 7012 include turbines or paddle wheels for driving local generators 7034. Together, the cooling and local power generating capabilities of the point loads 7012 make them well suited for use in data centers where high cooling and electrical requirements are needed.

As stated above, a combustion steam generator 1100 presents an attractive source of energy for data centers. As a first reason, the steam generator 1100 is a principally mechanical/thermomechanical system. As such, the steam generator is by design, immune from electro-magnetic pulses, hacking over data networks, and other species of electronic attack. As a second reason, the power output by the steam generator 1100 can be moved from a point of generation to a point of use as either hot steam or pressurized water. In this way, the energy contained cold water pressurized by a pump or turbine driven by steam generator 100 can be communicated, via piping, to the point of use to power one or more apparatus for power generation. Unlike electrical transmission lines, pipes containing pressurized water are not vulnerable to emp or other electronic attack. In certain embodiments, the steam output by internal combustion steam generator 100 drives a steam powered turbine which creates a supply of pressurized cold water provided to a water-driven motor at a point of use. In some embodiments, the water-driven motor can be a double acting positive displacement pump, which is cycled by a pressure differential between a supply of high-pressure cold water, and a low-pressure return. The aforementioned water-driven motor can generate AC or DC power at the point of use. Additionally, the pressurized cold water can be used as a coolant for highly exothermic applications, such as data centers.

Various features and aspects of the disclosure are set forth in the following claims.