WO2024258884A9 - Système de conversion d'énergie sans carbone pour fournir de la chaleur et de l'électricité de traitement à haute température - Google Patents

Système de conversion d'énergie sans carbone pour fournir de la chaleur et de l'électricité de traitement à haute température Download PDF

Info

Publication number
WO2024258884A9
WO2024258884A9 PCT/US2024/033464 US2024033464W WO2024258884A9 WO 2024258884 A9 WO2024258884 A9 WO 2024258884A9 US 2024033464 W US2024033464 W US 2024033464W WO 2024258884 A9 WO2024258884 A9 WO 2024258884A9
Authority
WO
WIPO (PCT)
Prior art keywords
working fluid
engine
heat exchanger
compressor
coupled
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2024/033464
Other languages
English (en)
Other versions
WO2024258884A3 (fr
WO2024258884A2 (fr
Inventor
Claudio Filippone
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO2024258884A2 publication Critical patent/WO2024258884A2/fr
Publication of WO2024258884A3 publication Critical patent/WO2024258884A3/fr
Publication of WO2024258884A9 publication Critical patent/WO2024258884A9/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants

Definitions

  • heat removal systems generally require complex piping networks to hydraulically couple the pressure vessel containing the nuclear core to heat exchangers configured inside or outside of the pressure vessel.
  • the coolant circulating between the nuclear core and the heat exchangers may be either actively circulated by electrically driven pumps and/or blowers, or passively circulated via gravity- driven natural circulation mechanisms.
  • the main difference between the thermal energy by the reactor during normal operations versus the thermal energy generated by decay heat is their power rating.
  • the decay heat power rating is approximately 6% of the nominal power the reactor supplied at the moment of shut down, and this percentage decreases exponentially as time elapses.
  • the power turbine is mechanically decoupled from the rotary turbomachinery forming the gas-turbine.
  • the power turbine is mechanically coupled with and drives an electric generator.
  • One of the methods for a turbo-propeller type of gas turbine to be converted into an aeroderivative gas turbine for electrical power generation includes removing the propeller and gearbox from the power turbine and mechanically coupling the power turbine to an electric generator.
  • Another method to convert a turbo-fan gas turbine to an aeroderivative gas turbine for the production of electricity includes removing the fan and replacing it with a low-pressure ratio compressor to supply compressed air to the high- pressure compressor, which provides high-pressure compressed air to the combustors.
  • the nozzle designed to generate thrust, is also eliminated and the outlet of the expander turbine is hydraulically coupled to a power turbine that is further coupled to an electric generator.
  • All typologies of gas turbines dedicated to the production of electricity represent combustion engines generally converting fossil fuels energy into mechanical or fluid-dynamic energy, defined as the energy represented by a fluid characterized by a certain temperature, pressure and mass flow rate. Burning a mixture formed by air and fossil-fuels generates high- temperature exhaust gases which expand through an expander turbine and convert the fluid dynamic energy of the exhaust gases into shaft work and electricity by i) mechanically coupling the power turbine shaft to an electric generator or ii) by fluid-dynamically coupling the high energy content exhaust gases to a mechanically decoupled power turbine that is further coupled to an electric generator unit.
  • combustion chambers designed to mix and ignite the mixture formed by the oxygen, contained in environmental air, with the fossil fuels supplied for the combustion (e.g., in gaseous, liquid, or particulate form), to generate high-temperature exhaust gases that expand through the expander turbomachinery and/or through the power turbine.
  • fossil fuels supplied for the combustion e.g., in gaseous, liquid, or particulate form
  • a smaller combustion chamber generally processes a smaller amount of air-fuel mixture and produces a proportional amount of power.
  • a larger combustion chamber generally processes a larger air-fuel mixture mass resulting in the expansion of a larger amount of exhaust gases.
  • Commercial combustion engines represented by aeroderivative, and gas turbines generally do not include a heat exchanger dedicated to transfer thermalenergy from a carbon -free heat source (e.g., not sourced in the combustion of air-fossil-fuels mixtures) to the fluid expanding in the expander or power turbine.
  • Various exemplary embodiments of the present disclosure may provide a thermal -to- electric power conversion system by retrofitting commercial engines formed by aeroderivative and gas-turbines coupled to electric generators by augmenting the energy content represented by the combustion of fossil fuels within gas-turbines’ and aeroderivative’ combustors, by-passing, or entirely replacing the combustors normally included in these engines to increase the working fluids energy content in these engines by means of heat exchangers disposed under various configurations, for example, within retrofitted engine casing, outside of the engine casing, hybrid configurations (partially within and partially outside of the engine casing), or utilizing configurations in which the thermal transfer between the heat source and the working fluid occurs within the heat source casing.
  • the thermal or heat source transferring thermal energy through the heat exchanger to one or multiple working fluids for conversion to electricity, torque, or as thermal supply to support process heat applications may be represented by carbon-free energy sources (e.g., a nuclear core, solar-thermal, high-temperature geothermal, and waste thermal energy).
  • carbon-free energy sources e.g., a nuclear core, solar-thermal, high-temperature geothermal, and waste thermal energy.
  • the heat exchanger may operate with at least one primary and one secondary side wherein thermal transfer media, represented by working fluids, circulates and exchanges thermal energy transfers between the working fluids and the materials forming the heat exchanger.
  • thermal transfer media represented by working fluids
  • one of the working fluids circulates in the primary side, the “primary working fluid” of the heat exchanger, without mixing with the working fluid circulating in the secondary side, the “secondary working fluid”.
  • the primary and secondary working fluids are suitable fluids thermally coupled on the primary side to the heat source, with the secondary fluid further thermally coupled to the components forming a power conversion system (e.g., engines represented by modified aeroderivative and gas-turbines components), or a process heat application.
  • the secondary working fluid heated by the primary fluid expands in the modified turbomachinery systems that includes aeroderivative or gas turbine components coupled to electric generators.
  • the secondary working fluid may be environmental air.
  • the primary working fluid and the air may not mix.
  • air, compressed by the engine compressor circulates through the heat source exchanger where thermal energy is transferred from the heat source to the air.
  • the heated compressed air, exiting the secondary side of the heat exchanger may flow through the engine combustor where a metered amount of fossil-fuel is mixed and ignited by temperature. The result is combustion of the metered amount of fossil fuel.
  • the combined mass of exhaust gases and mass of heated air make up the energy requirement for the engine expander or power turbine to operate at engine-design conditions to convert the combined thermal energy represented by the heated air and the combustion products developed by the combustor into an air-exhaust gases mixture with high energy content driven through static nozzles (e.g., turbomachinery stator) and expand through the components of the expander (e.g., turbomachinery rotor) or those forming the power turbine, thus generating shaft work and fluid dynamic energy.
  • static nozzles e.g., turbomachinery stator
  • expander e.g., turbomachinery rotor
  • those forming the power turbine thus generating shaft work and fluid dynamic energy.
  • the expander outlet drives a power turbine coupled to an electric generator
  • the combined thermal energy is indirectly converted into electricity as the energy content of the secondary working fluid is in part utilized to drive the compressor, with the remaining fluid dynamic energy dedicated to drive the power turbine, mechanically decoupled from the rotary components forming the compressor and expander turbine.
  • the heat exchanger thermally coupled via primary side to the heat source and secondary side to the working fluid circulating through the engine can be configured to transfer a substantial amount of the thermal energy from the carbon-free heat source to the air expanding at the outlet of the heat exchanger secondary circuit. In this configuration, there is no fossil-fuel burning.
  • the compressed heated air, compressed by the compressor driven by the expander flows directly into the stator and rotary components of the expander or power turbine turbomachinery for direct or indirect conversion of the secondary fluid energy content into electricity.
  • the present disclosure provides a system that transfers thermal energy from a carbon- free energy source to the compressed air normally generated by the compressor of commercial aeroderivative gas-turbine engines.
  • the system augments, bypasses or eliminates the fossil-fuel combustor normally included in these engines, heats the compressed air through a heat exchanger to increase the air energy content, expands the heated air through the expander and produces shaft work that drives the engine compressor and produces electricity when the expander is coupled to a generator.
  • the heat exchanger may be positioned within the inner spacing defined by the engine casing forming a pressure boundary normally surrounding the combustor(s) structures utilized by commercial engines (e.g., commercial gas-turbines and derivatives).
  • the body of the heat exchanger may be configured to occupy the volume formed by the inner spacing between the combustor and the engine casing to induce the compressed air or secondary working fluid to flow through the heat exchanger and exchange thermal energy with the primary working fluid circulating through the heat source prior to entering the combustor.
  • the heat exchanger may be positioned within a retrofitted extended engine casing.
  • the extended casing seals the OEM engine casing and maintains the engine casing pressure boundary while increasing its internal volume to further accommodate internal space for conduits or channels, that do not interfere with the normal operations of the combustor.
  • a larger heat exchanger can be configured to channel the secondary fluid represented by compressed air through the heat exchanger to exchange thermal energy with the primary working fluid prior to the now heated compressed air flows through the combustor.
  • the engine casing may be configured with hydraulic ports positioned on the extended engine casing walls to enable the compressed air to exit the engine casing through piping hydraulically coupled to an external heat exchanger. In this configuration, the heat exchanger primary fluid circulating through the carbon-free heat source transfers thermal energy to the secondary working fluid outside of the engine casing where its energy content is increased prior to flowing back into the engine casing resulting in heated air flowing through the combustor.
  • the heat exchanger may replace the combustors and be positioned within the engine casing retrofitted with inlet and outlet ports hydraulically sealing the engine casing for the primary working fluid circulating through the heat source to circulate through the heat exchanger primary side inlet and outlet ports through the engine casing.
  • the heat exchanger may be formed by a printed circuit heat exchanger, for example, formed by diffusion bonded layers with axial channels for the secondary working fluid (e.g., air) to flow through, and radial channels for the primary working fluid to flow through.
  • the heat exchanger is shaped to fit the volume formed by the engine casing inner spacing between the engine casing internals and the engine shaft shroud providing mechanical support to the combustor.
  • the printed circuit heat exchanger may be equipped with axial and radial bellows to eliminate stress points induced by thermal fatigue as the heat exchanger body expands and contracts.
  • a power conversion system for converting thermal energy from a heat source to electricity is provided.
  • Another aspect of the invention may provide a system for the transfer of thermal energy to a process heat application represented, for example, by steel manufacturing.
  • the secondary fluid may be circulated through the metal materials to elevate their temperature prior to conducting various steel manufacturing processes.
  • FIG. 1 is a partial functional schematic cross-sectional side view, symmetrical with respect to the longitudinal axis, of an unmodified commercial gas turbine engine coupled to an electric generator, showing multistage compressor and multistage expander rotary and stationary turbomachinery coupled by a shaft, the main combustor and combustion chamber components included within the engine casing with internal flow pathways for the air to flow from the compressor inlet, mix with fossil fuel and ignite in the combustor, and the combustion product outlet the engine from the expander outlet after producing shaft work and electricity.
  • Fig. la is a partial functional schematic cross-sectional side view of a simplified engine shown in Fig. 1.
  • FIG. 2 is a partial functional schematic cross-sectional side view of a simplified engine shown in Fig. 1, with additional retrofitted components to enable extending the engine casing while maintaining the pressure boundary of the OEM engine casing, including a heat exchanger and internal conduits for the heat exchanger to transfer thermal energy from a carbon free heat source to the compressed working fluid compressed by the compressor and flow the heated working fluid through the combustor.
  • FIG. 3 is a partial functional schematic cross-sectional side view of a simplified engine shown in Fig. 1, with retrofitted engine casing components to enable the compressed working fluid from the compressor to circulate outside of the engine casing and return to the engine casing through retrofitted hydraulic ports after the working fluid has been heated by heat transfer with a carbon free heat source so that the heated working fluid is supplied to the combustor.
  • FIG. 4 is a partial functional schematic cross-sectional side view of a simplified engine shown in Fig. 1, with retrofitted engine casing components to enable the compressed working fluid from the compressor to circulate through a heat exchanger positioned within the retrofitted extended casing components, for the heated compressed working fluid to directly expand through a power turbine coupled to an electric generator.
  • FIG. 5 is a partial functional schematic cross-sectional side view of a simplified engine shown in Fig. 1, with retrofitted engine casing components to enable the compressed working fluid from the compressor to circulate through a bypass tube prior to entering the heat exchanger positioned within the retrofitted extended casing components, for the heated working fluid to directly expand through the expander.
  • Figs. 5a and 5b are cross sectional views of different sides of the heat exchanger shown in Fig.5.
  • Fig. 6 is a partial functional schematic cross-sectional side view of a simplified engine shown in Fig. 5 configured with a heat exchanger and showing the bypass tubing configured with hydraulic ports positioned with retrofitted extended casing components and internal conduits and passageways for compressed working fluid to flow within an inner space into the inlet of the secondary heat exchanger header.
  • FIG. 7 is a partial functional schematic cross-sectional side view of a simplified engine shown in Fig. 1 configured without a combustor and without a heat exchanger and showing hydraulic ports positioned with retrofitted extended casing components and internal conduits and passageways for compressed working fluid to flow within an inner space into the inlet of the secondary heat exchanger header through the hydraulic ports for direct expansion through the expander.
  • Fig. 8 is a partial perspective three-dimensional cross-sectional view of the engine of Fig. 6 retrofitted with extended casing showing the internal conduits, heat exchanger, bypass tubing, and thermally insulated piping thermally coupling the heat exchanger to a carbon-free heat source.
  • Fig. 8a is a schematic representation of the retrofitted engine casing shown in Fig. 8 including a heat exchanger.
  • Fig. 8b is a simplified schematic representation of the engine shown in Fig. 8.
  • Fig. 9 is a perspective view of a carbon-free heat source represented by a nuclear reactor coupled to the retrofitted engine shown in Fig. 8.
  • Fig. 10 is a cross-sectional schematic view of a gas-turbine engine coupled to electric generators with schematic representation of combustors positioned substantially parallel to the longitudinal axis and inner rotary shaft coupling the compressor to the expander turbomachinery and to the generators via mechanical couplers and a gear box.
  • Fig. 11 is a cross-sectional view of the engine shown in Fig. 10 retrofitted with a compact heat exchanger replacing the combustors with a compressed working fluid flowing though headers and channels in the longitudinal axial direction and a heat source working fluid flowing through headers and channels in the radial direction.
  • Fig. 12 is a schematic partial three-dimensional cross-sectional view of the compact or printed circuit heat exchanger shown in Fig. 11 showing the working fluid flow pathways and the heat source working fluid flow pathways.
  • Fig. 12a shows a simplified cross-sectional schematic view of the heat exchanger shown in Fig. 12.
  • Fig. 13 is a cross-sectional schematic view of the engine shown in Fig. 10 with the engine hood extended to house a heat exchanger retrofitted within the engine casing to enable the engine to operate with both the combustion gases of a combustor mixed with the heat source working fluid.
  • Fig. 13a is a cross sectional schematic view of the engine shown in Fig. 10 and Fig. 13 with the engine hood extended to house a chamber for the working fluid aiding the combustion of a combustor and mixed with the combustion gases, with the engine hood extended and equipped with hydraulic ports to hydraulically couple the chamber inside the engine hood to an external heat exchanger.
  • Fig. 14 shows a carbon-free engine coupled to an external heat exchanger thermally coupled to a carbon-free heat source configured to heat up a heat source working fluid and produce electricity through a full Brayton cycle with intercooler and recuperator heat exchangers.
  • Fig. 15 shows the carbon-free engine of Fig. 14, coupled to an external heat exchanger thermally coupled to a carbon-free heat source configured to heat up a heat source working fluid and produce electricity through a simple Brayton cycle.
  • Fig. 16 is a schematic representation of the carbon-free heat source of Fig. 15 coupled to an external heat exchanger through high temperature piping surrounded by low- temperature piping.
  • Fig. 17 is a schematic representation of the engine shown in Fig. 14 and Fig. 15 coupled to an external heat exchanger integrated within a carbon-free heat source configured to produce thermal power.
  • Fig. 18 is a schematic representation of the carbon free engine shown in Fig. 11 integrating a compact or printed circuit heat exchanger within the extended hood of the engine directly coupled to the heat source working fluid of a carbon-free heat source comprising a simple Brayton or Rankine cycle.
  • Fig. 19 is a schematic representation of the engine shown in Fig. 11, directly coupled to the heat source working fluid circulating in two carbon-free heat source unit, where one heat source unit produces electricity and heats up the heat source working fluid, while the other carbon-free heat source unit only heats up the heat source working fluid.
  • Fig. 20 is schematic representation of a carbon-free heat source configured as an electric power conversion system and as a thermal energy supply system coupled to a power utilization system.
  • Fig. 21 is a schematic representation of the carbon-free heat source of Fig. 20 coupled to an electric arc furnace to support a steelmaking processes.
  • Fig. 22 is a schematic representation of the carbon-free heat source of Fig. 20 and Fig. 21 further coupled to a steelmaking reheating chamber to support steelmaking processes.
  • Figs. 1 and la illustrate an unmodified, commercial or traditional, fossil-fueled turbine-generator power conversion system, also referred to as engine 100.
  • the engine 100 includes a casing 101 formed by an inlet 102 and an outlet for a working fluid 112 to flow through.
  • the casing 103 surrounds the axial compressor axial stator turbomachinery 113 and the compressor rotor turbomachinery 114.
  • the engine casing 103 merges into engine casing 123 which forms the base of the casing structures forming the combustor body 109a, which further merges with casing 104a which surrounds the expander stator turbomachinery 116 and expander rotor turbomachinery 117.
  • the compressor rotor 118a is mechanically coupled to the shaft 118, which is mechanically coupled to a gear box 118c, which is further mechanically coupled to the expander rotor 118b.
  • the compressor rotor 118a is mechanically coupled to the expander rotor 118b as the expander rotor 118b drives the compressor rotor 118a.
  • the compressor rotor 118a is directly coupled to the expander rotor 118b (no gear box 118c).
  • the compressor rotor 118a is mechanically decoupled from the expander rotor 119b as it may be driven by an electrical motor coupled through a mechanical coupler 121 as shown for the coupling of shaft 118 to motor-generator 120.
  • the engine casing 123 may be configured to flange extended combustor casing 103 through flange 103a pressure sealed through seals 124.
  • Combustor casing 103 (also referred to as bucket casing 103), is further coupled to the combustor bucket hood 122 (also referred as casing hood 122).
  • the combustor structure 109 is configured to enable compressed working fluid 112 to mix with fossil fuel spray 105s supplied by a fossil fuel supply system 105, where fossil fuel 105a is pressurized inside the combustion chamber 106 to ignite and increase the energy content of the resulting combustion gases and working fluid 112.
  • a fossil fuel supply system 105 where fossil fuel 105a is pressurized inside the combustion chamber 106 to ignite and increase the energy content of the resulting combustion gases and working fluid 112.
  • working fluid 112 is compressed by the compressor turbomachinery 114 and becomes compressed working fluid 112c.
  • This compressed working fluid flows through channels 119b formed within the combustor casing 104 with ducts and internal combustor structures so as to change the direction of the compressed working fluid 112c as shown in channel 109b until it enters the combustion chamber 108, formed by structures with patterned holes where working fluid 112c enters the combustion area 110, mixes with fossil fuel 105a and ignites.
  • the resulting exhaust gases 111 mixed with superheated working fluid 112sh flow within the nozzle conduit 109 to expand out of the nozzle outlet plane indicated by the letter “N” into the expander stator 116 and rotor 116 turbomachinery resulting in a conversion of thermal energy from the superheated working fluid 112sh and combustion gases.
  • exhaust gases 11 le and exhaust working fluid 112e exit the engine.
  • the expander rotor 118b drives the compressor rotor 118a producing additional torque to drive the generator 120 which produces electric power at its electric bus 125.
  • Fig. la shows a simplified configuration of engine 100, where the compressor rotor 118a is decoupled from the expander rotor 118b.
  • FIG. 2 illustrates a retrofitted power conversion system of engine 100 shown in Figs. 1 and la, also referred to as engine 200.
  • the internal conduits 109b for the compressed working fluid 112c to flow in are unchanged as part of the engine casing 123, while a series of passageways 109a and 103 c are retrofitted within the combustor casing 103 to direct the compressed working fluid 112c into an extended casing 201 flanged to the flanges 103b originally designed to couple the combustor casing 103 to the engine hood 112 of Figs. 1 and la.
  • an extended sealed volume housing the heat source heat exchanger 208 is provided.
  • the added casing 214 further provides an inlet and outlet hydraulic ports for a hot heat source working fluid 206h to flow through inlet 204 and flow out of the extended casing 214 through outlet 205.
  • hot heat source working fluid 206h flows through superheater 208, it transfers thermal energy to the compressed working fluid 112c without mixing. More specifically, hot heat source working fluid 206 flows through piping 215 with thermal insulation 207h into the superheater inlet header 209.
  • the superheater heat exchanger 208 is formed by a primary inlet header 209 and a primary outlet header 210 coupled to a primary thermodynamic loop where the heat source working fluid 206 circulates, and a secondary inlet header 21 land a secondary outlet header 212 where the compressed working fluid circulates.
  • Superheater heat exchanger 208 may be represented by a printed circuit heat exchanger with primary channels in the “y” direction coupled to the primary inlet and outlet headers 209 and 210 respectively, and secondary channels in the “x” direction coupled to the secondary inlet and outlet headers 211 and 212 respectively.
  • the compressed working fluid 112c is thermally coupled to the heat source working fluid 206, such that as both working fluids flow through the superheater 208, the hot heat source working fluid 206h cools down to cold heat source working fluid 206c and the compressed working fluid 112c becomes compressed hot working fluid 112h prior to mixing with fossil fuel 105a within the combustion chamber are 110.
  • the resulting combustion gases 111 and superheated working fluid 112sh flow with higher energy content through the nozzle structures 109 for conditioning both working fluids into the expander turbomachinery 117 generating torque at the expander rotor 115a.
  • This torque can be utilized by coupling expander rotor shaft 115a via mechanical coupler 121 to an electric generator, as shown in Fig. 1, or to the compressor rotor 115 via gear box 118c or to both compressor rotor and to an electric generator.
  • the resulting exhaust working fluid 112e and the exhaust combustion gases 11 le at the engine outlet denoted by the “OUT” plane are characterized by high temperature and higher pressure than that of the working fluid 112 at the engine inlet at the inlet plane denoted by “IN”.
  • these working fluids exhaust characteristics at the engine 200 outlet may be utilized to transport thermal energy and flow rate through a thermal utilization system 2003 shown in Fig. 20. [054] Fig.
  • FIG. 3 shows a partial functional schematic cross-sectional view of the engine 100 shown in Fig. 2 with simplified retrofitting modifications as the superheater heat exchanger 208 is disposed outside of engine 200 combustor casing 103.
  • the retrofitted combustor casing 103 is minimally modified, while the combustor header 302 is modified to include hydraulic inlet and outlet ports 304 and 303 respectively.
  • the combustor chamber 106 is surrounded by conduits that 301 to channel the compressed working fluid 112c. This working fluid is compressed by compressor turbo machinery 114 and exits the modified combustor header 302, to be superheated outside of the engine 300.
  • This working fluid then returns as hot working fluid 112h back into the modified combustor header 302 to mix with fossil fuel 105a resulting in combustion gases 111 and superheated working fluid 112sh.
  • the combustion gases 111 and superheated working fluid 112sh then flow through the nozzle structure 109 and expand through the expander turbomachinery to produce torque, and exhaust working fluid 112e and exhaust gases 11 le with a controlled energy content.
  • the energy content of these working fluid is proportional to the amount of thermal energy converted to torque at the expander rotary shaft 115a.
  • the flow paths developed inside the combustor casing 103 and the combustor header 302 for the compressed working fluid 112c enable this fluid to remain pressurized by the compressor turbomachinery 114 while circulating through external thermally insulated cold piping 306 and hot piping 305.
  • FIG. 4 is a partial functional schematic cross-sectional side view of a simplified engine shown in Figs.1-3 with a retrofitted engine casing 402 coupled to the combustor casing 103 by flange 103b on one end, and to the combustor header 202 on the other end by flange 203 sealed by seals 124.
  • Combustor engine casing 402 further extends the volume inside the combustor casing 103 to substantially entirely eliminate the combustion chamber 106, the fossil fuel system 105 and the fossil fuel 105a normally included in engine 100 in Fig. 1.
  • a larger superheater heat exchanger 401 may be fitted within the extended combined volume formed by coupling combustor casing 103 to combustor casing 402 and to combustor header 202.
  • engine 400 is carbon-free as the compressed working fluid 112c is superheated without combustion of fossil fuels.
  • hot heat source working fluid 206h flows at the inlet 204 of an inlet hydraulic port positioned on the combustor casing 402, through superheater heat exchanger 401 (e.g., a printed heat exchanger with channels as described for engine 200) thermally coupling the compressed working fluid 112c to an external carbon -free energy source.
  • superheater heat exchanger 401 e.g., a printed heat exchanger with channels as described for engine 200
  • the superheater heat exchanger 401 includes primary circuit and secondary circuit inlet and outlet headers 404, 405, 406 and 407 respectively, for the compressed working fluid 112c to be heated up by the hot heat source working fluid 206h.
  • the compressed working fluid 112c energy content has been increased to compressed hot working fluid 112h for this fluid to expand through the expander turbomachinery 117 as described for engines 100, 200 and 300.
  • the torque developed at the expander shaft 115a by the expansion of compressed hot working fluid 112h is converted into electricity by generator 403.
  • the generator 403 is thermally insulated from the hot exhaust working fluid 112e, and is cooled by a jacket 408, where an auxiliary coolant circulates.
  • the coolant may circulate through the jacket by piping 410 passing through a hollow mechanical support 409 mechanically coupling the generator 403 to the outlet engine casing 104.
  • the electrical connections 125 for generator 4o3 may also be routed through the hollow mechanical support 409.
  • FIG. 5 shows a partial functional schematic cross-sectional view of a simplified engine 500 with a similar functionality as that described in Fig. 4.
  • the combustor header 501 provides hydraulic access to a bypass piping 505 for the compressed working fluid 112c to flow directly into superheater heat exchanger header 509, while hot heat source working fluid 206h circulates into the modified combustor case 402 with less back pressure as inlet and outlet primary headers 204, 205, 507 and 508 may be further extended within the volume constrained by combustor casing 103 dimensions.
  • bypass pressure headers 511a and 511b create a compartment preventing compressed working fluid 112c to mix with hot and cold heat source working fluid 206h and 206c respectively.
  • FIGs. 5a and 5b are cross sectional views of different sides of the heat exchanger shown in Fig.5. Accordingly, Fig 5a shows the inlet header 509 with channels 513 for compressed working fluid 112c to flow through. Fig 5b illustrates the channels 512 of header 508 of a superheater heat exchanger similar to that described in Fig. 4.
  • Fig. 6 is a partial functional schematic cross-sectional view of a simplified engine 600 with similar operating principles as described for engine 500 shown in Fig. 5.
  • the superheating heat exchanger 604 is not invasive into combustor casing 103 so as to minimize the modification to this component of engine 100 shown in Fig. 1 other than removing all of the original engine manufacturer equipment out of combustor casing 103 and replacing it with a modified nozzle supporting structure 109a.
  • Fig. 7 is a partial functional schematic cross-sectional view of the simplified engine shown in Fig.
  • This configuration is one of the least invasive as it enables recycling of most of the original manufacturer equipment forming the combustor casing, removing all of the combustor equipment inside the combustor casing 701 (e.g., fossil fuel system 105, combustion chamber) and fitting the ducting structure 702 inside the combustor casing 701 to enable the compressed working fluid 112c to exit the combustor casing structure through outlet 705 flowing toward the external superheating heat exchanger denoted by the arrow 706, and returning back for expansion through the expander turbomachinery 117 as denoted by arrow 707 as compressed hot working fluid 112h.
  • the combustor casing 701 e.g., fossil fuel system 105, combustion chamber
  • Fig. 8 is a partial perspective three-dimensional cross-sectional view of the engine 600 of Fig.6 retrofitted with extended casing showing the conduits internal to the modified combustor casing, a configuration of the superheating heat exchanger, bypass tubing, and thermally insulated piping thermally coupling the primary circuit of the superheater heat exchanger to a carbon-free heat source.
  • the compressed working fluid 112c makes a partial flow reversal at the last stage of rotary compressor turbomachinery at location 109b and flows inside an annular channel formed by the inner walls of combustor casing 103 and the modified nozzle structure 515a replacing the combustion chamber denoted by the dashed box prior to flange 103a.
  • the compressed working fluid 112c inlets the bypass tubing 112 at the hydraulic outlet connecting to one end of the bypass tubing 802 and pressurizes the internal volume formed by the inner walls of the combustor header or hood 202 so as to induce the compressed working fluid 112c to inlet the superheater heat exchanger 801 with working principle described in previous Figures.
  • the functions of bypass tube 802 are equivalent to those described for bypass tubes 401 in Fig.4, 506 in Fig. 5 and 604 in Fig.6.
  • Flange adapter 803 enables to align the superheater heat exchanger 801 with the rotary axis 119 of engine 800.
  • Fig. 8a is a schematic representation of the superheating heat exchanger 801 fitted inside the modified combustor casing shown in Fig. 8.
  • Fig. 8b is a simplified schematic representation of the engine shown in Fig. 8 with functioning principles described in previous Figures.
  • FIG. 9 is a perspective view of a carbon-free heat source 900 represented by a nuclear reactor coupled to the retrofitted engine shown in Fig. 8, wherein the carbon-free heat source 900 is fitted within a shipping container.
  • a series of hydraulic ports 901 enable thermal coupling of piping 411 and 412 of engine 800 to thermal source 900.
  • only one set of piping 411 and 412 are shown to simplify the illustration as the same type of piping is equipping each of the retrofitted combustors shown in this Figure (e.g., 5 times piping 411 and 412 coupling to ports 901).
  • FIG. 10 is a cross-sectional schematic view of a commercial aero-derivative gasturbine engine 1000, coupled to electric generators 120 and 403 with schematic representation of combustors positioned substantially parallel to the longitudinal axis and inner rotary shaft 119 coupling the compressor to the expander turbomachinery and to the generators 120 and 403 via mechanical couplers 121and a gear box 118c as described in previous Figures.
  • This configuration uses hood 1001 to seal the combustors disposed inside of the sealing hood 1001 and the combustor casing 103, the hydraulic coupler 1003 and extended piping 1004 coupled to the engine outlet 808 are provided to indicate a method for transporting the exhaust gases 11 le and exhaust working fluid 112e to a thermal power utilization system shown in Figs. 20, 21 and 22.
  • FIG. 11 is a cross-sectional view of the engine 1000 shown in Fig. 10 retrofitted with a compact heat exchanger 1104 replacing the combustors shown in Fig. 10 for the compressed working fluid 112c flowing though the secondary inlet header 1204 of the compact heat exchanger 1104 (also referred to as superheater 1104), through axial channels 1103 in the axial direction to minimize the formation of backpressure, while the hot heat source working fluid 206h flows through the inlet primary headers 1104a through heat transfer channels in the radial direction.
  • a flow straightener 1102 is positioned at the inlet 807 of engine 1100, 1003a denote the axial channels for the compressed working fluid 112c to flow through, 1103r denote radial channels for the hot heat source working fluid 206h to flow through without mixing with the working fluid 112.
  • the compact heat exchanger is fully comprised within the volume normally occupied by combustors’ equipment and, in this configuration, it is formed by at least 2 bodies 1104a and 1104b coupled by a flexible member 1109 to minimize thermal cycling fatigue.
  • Fig. 12 is a schematic partial three-dimensional cross-sectional view of the compact radial heat exchanger body 1104 shown in Fig. 11, further showing the compressed working fluid 112c flow pathways and the heat source working fluid 206h flow pathways within the channels inside the compact heat exchanger 1200.
  • 1201 denotes the first heat exchanger module (equivalent to 1104a in Fig. 11) and the second module 1202 (equivalent to 1104b in Fig.11)
  • 1203 is the outlet conduit for the heat source working fluid 112c (after thermal exchange with the compressed working fluid 112c).
  • 1204 denotes the compressed working fluid inlet header, while 1205 is the compressed working fluid outlet header.
  • 1206 denotes the compact heat exchanger inner diameter and 1207 denotes the outer diameter, while 1208 and 1209 indicate the heat source working fluid inlet and outlet headers respectively.
  • Fig. 12a shows a simplified cross-sectional schematic view of the heat exchanger shown in Fig. 12.
  • Fig. 13 is a cross-sectional schematic view of the engine 1000 shown in Fig. 10 with the engine hood extended to house a super heating heat exchanger 1302 (also referred as SH- HEX 1302), retrofitted within the engine 1300 casing to enable the engine 1300 to operate with both the combustion gases produced by combustor chamber 106, mixed with the compressed heat source working fluid 112c.
  • a super heating heat exchanger 1302 also referred as SH- HEX 1302
  • the SH-HEX 1302 is integrated within the hood of engine 1300
  • 810 and 809 denote the coupling flanges for the hot heat source working fluid 206h respectively.
  • 1303 denotes the inlet compressed working fluid channel
  • 1303a represents the internal channel structure nozzle side
  • 1303b denotes the internal channel structure on the compressor side
  • 1303 st denotes the compressed working fluid 112c channels structures and thermal insulation
  • 1304 is the external superheater heat exchanger, with 1304p as the primary side of the external superheater heat exchanger 1304 and 1304s as the secondary side of external superheater heat exchanger 1304.
  • Fig. 13a is a cross sectional schematic view of the engine 1000 shown in Fig. 10 and 1300 shown in Fig. 13, with the engine hood 1101 extended to house a chamber 1309 for the compressed working fluid 112c aiding the combustion of a combustor and mixed with the combustion gases, with the engine hood 1101 extended and equipped with hydraulic ports 1315 and 1316 to hydraulically couple the chamber 1309 inside the engine 1300 to an external heat exchanger 1304, wherein 1305c and 1305h indicated cold and hot conduits, 1306 is the external heat exchanger housing, 1307 and 1308 represent the cold compressed working fluid 112c inlet and outlet ports respectively, while 1309a and 1309b denote the hot collector and chamber respectively. 1310, 1311, 1312, 1314 represent the external hydraulic ports for the headers of the external heat exchanger, while 1315 and 1316 denote the engine casing outlet and inlet hydraulic ports respectively.
  • Fig. 14 shows a carbon-free engine 1441 coupled to an external heat exchanger 1306 thermally coupled to a carbon -free heat 1400 configured to heat up a heat source working fluid 206 and produce electricity through a full Brayton cycle with intercooler and recuperator heat exchangers 1407 and 1409 respectively.
  • the carbon-free power generation and conversion plant 1400 is shown.
  • Fig. 15 shows a power conversion system of the present disclosure.
  • the system may include a turbine-generator engine 1414 (also referred to as aero-derivative 1414, or engine 1414), a heat exchanger 1306 (also referred to as an external heat exchanger 1306 or E-HEX 1306), and a heat source 1500.
  • the heat source 1500 may be any suitable heat source, including, for example, a heat source obtained by a core with fission or fusion nuclear fuel, a heat source represented by a solar collector, or a heat source represented by industrial processes producing waste thermal energy.
  • the heat source may be referred to as a carbon- free heat source.
  • a fission nuclear reactor is used as an example heat source.
  • the principles and embodiments apply to any other suitable heat source.
  • the heat source 1500 is thermally coupled to the E-HEX 1306 and the E-HEX 1306 is thermally coupled to the engine 1414 for the production of electricity, the supply of process heat and the supply of pumping power for a working fluid to support process heat applications.
  • the engine 1414 is formed by turbine-generator components disposed within an engine body or an engine casing 103 (also referred to as casing 103).
  • the casing 103 may include an inlet 807.
  • a working fluid (also referred to as “WF”) 112 may flow through the compressor turbo machinery 114 and 113, and may be compressed by the compressor turbo machinery 114 and 113 into a compressed WF 112c inside the casing 103.
  • the compressed WF 112c circulates in a pressurized state within an engine hood 1101 (also referred to as “engine hood 1101”).
  • the engine hood 1101 includes a hydraulic outlet port 1316 and a hydraulic inlet port 1315, and is coupled to the engine casing 103 through sealing flanges 103a.
  • the compressed WF 112c at the outlet of the compressor turbo-machinery flow straightener and conditioners 113 flows out of the hydraulic port 1315 through a WF cold piping 1305c, into the E-HEX 1306 through an inlet port 1307, which forms a part of the E-HEX secondary header 1304s.
  • HS-WF heat source Working Fluid
  • the HS-WF 206 may be any suitable fluid in gaseous, liquid or supercritical form, including, for example helium, water, liquid metals, molten salts, sCCE (supercritical carbon dioxide).
  • cold HS-WF 206c Prior to relatively cold HS-WF 206c circulating back from an E-HEX outlet port 1312, through cold HS-WF piping 411, into a heat source Pressure Vessel 1501, cold HS-WF 206c may be further cooled down through a cooler heat exchanger (also referred to as “C-HEX”) 1401, wherein the HS-WF 206 transfers thermal energy to a Coolant Working Fluid (also referred to as “CWF”) 1402, which may be represented by air, water or any suitable fluid in gaseous, liquid or supercricitcal form.
  • a gas e.g.
  • a turbo-machinery 1503 may be represented by a fan-, recirculator- or a compressor-driven by a motor 1503.
  • the turbo-machinery 1504 may be represented by a pump impeller driven by the motor 1503.
  • HS-WF 206 is compressed and circulates within a Heat Source Heat Exchanger (also referred to as “HS-HEX”) 1410, it increases its energy content and flows through the outlet of HS-HEX disposed within the pressure vessel 1501 as a high-temperature HS-WF 206ht, prior to expanding in an expander turbo-machinery 1411.
  • HS-HEX Heat Source Heat Exchanger
  • the HS-HEX 1410 may be thermally coupled to any heat source, including the heat source represented by a nuclear core, in which fission or fusion nuclear fuel generates thermal energy.
  • the heat source represented by a nuclear core, in which fission or fusion nuclear fuel generates thermal energy.
  • the high-temperature HS-WF 206ht expands through a turbo-machinery 1411, its energy content decreases proportionally to the amount of thermal energy converted to electricity through an electric generator 1412. For example, when there is no conversion of electricity through the electric generator 1412, the high-temperature HS-WF 206ht may not change its energy content.
  • motor 1503 When the electromagnetic rotary machines referred to as motor 1503, generator 1412 and generator 120 are formed by induction rotors or permanent magnets rotors, these machines can switch from motors to generators depending on whether the electromagnetic rotor is providing torque to turbomachinery, also referred to as motoring, or the turbomachinery supplies torque to the electromagnetic rotor, also referred to as generating.
  • turbomachinery also referred to as motoring
  • generating also referred to as generating
  • the hot HS-WF 206h discharged by the turbo machinery 1411, circulates through the HS-WF hot piping 412 through a hydraulic port 901 coupled to an Outer Shell Pressure Vessel 1502. As a result, the hot HS-WF 206h flows into an E-HEX inlet port 1314, which is a part of an E-HEX primary header 1304p. As a result of thermal transfer from the hot HS- WF 206h to the compressed cold WF 112c, HS-WF 206h energy content is further decreased and becomes cold HS-WF 206c. In this configuration, the compressed WF 112c circulating back into the pressure vessel 1501, represents the Ultimate Heat Sink of the Heat Source 1410.
  • Hot WF 112h circulates through hot piping 1305h into the modified engine hood 1101 through the inlet port 1316.
  • Hot piping 1305h and portions of ducting inside the engine hood 1101 are thermally insulated. Thermal insulation is also utilized to thermally insulate the cold WF 112c from the hot WF 112h through thermally insulated structural components 1303st inside engine hood 1101.
  • compressed hot WF 112h flows inside the engine hot WF 112h collector 1309a, it is fluid-dynamically conditioned through internal channel structures 1303a and nozzle conduit 109 in order for hot WF 112h to flow at optimal thermodynamic and fluid dynamic conditions out of nozzle plan N.
  • a hot WF chamber 1309 and its internal conduits thermally insulated from the engine compressor rotor 118a, engine shaft 118 and compressed WF inlet conduit 109b may be configured to form the nozzle supporting structures to condition hot WF 112h for expansion through one or multiple turbo-machinery expander rotary components 117.
  • hot WF 112h flows out of secondary E-HEX header 1304s through hydraulic port 1308, it flows through hot WF piping 1305h into hydraulic port 1316 of modified engine hood 1101, and pressurizes casing 103 sealed by hood 1101 through sealing flanges 103a coupling the engine casing 103 to the engine hoot 1101.
  • casing 103 a series of internal conduits physically separate and thermally insulate the cold WF 112c from the hot WF 112h through the internal insulated channel 1303b on the compressor side, and flow conditioning pathway 1303a combined with the nozzle structure 109 to further condition hot WF 112h prior to expansion through expander rotary turbomachinery 117.
  • hot WF 112h exits the nozzle plane N and is further conditioned by stationary multistage or single stage turbo machinery 116 and expands through multistage or single stage rotor 117.
  • hot WF 112h expands, its energy content is reduced proportionally to the amount of thermal energy converted into mechanical energy at the shaft 118.
  • exhaust WF 112e temperature is similar to the temperature of WF 112h.
  • rotor turbo-machinery 117 transfers mechanical energy to shaft 118 a portion of this energy is employed by the compressor rotor 118a for the compressor to compress WF 112, the remaining energy may be converted into electricity by generator 120, for distribution by power cable and three-phase AC or DC electrical buses 125, and/or to compress exhaust WF 112e into process heat tubing 1004 coupled to the engine outlet 808 through hydraulic coupler 1003 to transport exhaust WF 112e at a controlled temperature, based on the amount of WF 112h converted to electricity via generator 120, to support process heat applications as, for example, shown in Figures 20-22.
  • the carbon-free heat source energy of the present invention is configured to convert thermal energy represented by the HS-WF 206ht into electricity directly via electric generator 1503, indirectly via generator 120 and into exhaust WF 112e at a desired working pressure and temperature.
  • WF 112e can be intubated, through piping via hydraulic coupler 1003 to process heat piping 1004, and transported to support process heat applications as it will be described in Figures 22, 23 and 24.
  • Fig. 17 is a schematic representation of the engine 1414 shown in Fig. 14 and Fig. 15 coupled to an external heat exchanger 1702 integrated within a carbon-free heat source 1700 configured to produce thermal power.
  • Fig. 18 is a schematic representation of the carbon free engine 1100 shown in Fig. 11 integrating a compact or printed circuit heat exchanger 1200 also denoted as 1801 in this Figure, within the extended hood 1101 of the engine 1100 directly coupled to the heat source working fluid 206 of a carbon-free heat source 1800 comprising a simple Brayton or Rankine cycle.
  • Fig. 19 is a schematic representation of the engine 1100 shown in Fig. 11, directly coupled to the heat source working fluid 206 circulating in two carbon-free heat source units, where heat source unit 1400 produces electricity and heats up the heat source working fluid 206, while the other carbon-free heat source unit 1900 only heats up the heat source working fluid 206.
  • Fig. 20 shows a system for electric and thermal power conversion and power utilization according to an embodiment of the present disclosure.
  • the system may also be referred to as a thermal and electric power conversion and utilization system 2000S, which may include a thermal energy source 2000 (also referred to as heat source 2000 or HS 2000), a first power conversion system 2001 (also referred to as PCS 2001), a second power conversion system 2002 (also referred to as PCS 2002), and a thermal and electric power utilization system 2003.
  • the heat source 2000 may be any suitable heat source, including, for example, a heat source obtained by a core with fission or fusion nuclear fuel, a heat source represented by a solar collector, or a heat source represented by industrial processes producing waste thermal energy.
  • the heat source 2000 may be referred to as a carbon-free heat source 2000.
  • a fission nuclear reactor as also described in Figs. 9 and 14-19, is used as an example heat source, and an electric arc furnace and a long steel product re-heating station (shown in Fig. 22) are used as an example of thermal and electric power utilization system.
  • the principles and embodiments apply to any suitable heat source where thermal energy may be utilized for conversion to electricity and to support any suitable high- and low-temperature industrial process, in which the utilization of process heat (e.g., electric and high-temperature process heat for hydrogen production) may be implemented.
  • the carbon-free heat source 2000 may be formed by an intermediate heat exchanger 2007 (also referred to as I-HEX 2007), thermally coupled to a heat source heat exchanger 2004 (also referred to as source heat exchanger 2004 or Source-HEX 2004), where the I-HEX 2007 and the Source-HEX 2004 may be disposed within a modular container 2039 to reduce the balance of plant outside of container 2039 and to ease transport.
  • I-HEX 2007 and Source-HEX 2004 are thermally coupled through heat transfer media 2005 and heat transfer media C2006.
  • the Source-HEX 2004 may be disposed within the source pressure vessel 2046.
  • the heat transfer media 2006 and the I-HEX 2007 may be disposed within a pressure vessel 2008.
  • Pressure vessels 2046 and 2008 may be flanged together through a flange 2047 or be merged into a single pressure vessel should the selected heat transfer media 2005 and 2006 be the same or compatible.
  • Heat transfer media 2005 and 2006 may be represented by any suitable gaseous, liquid or supercritical fluids utilizing convective and conductive heat transfer mechanisms, as well as by solid materials utilizing thermal radiative and conductivity heat transfer mechanisms.
  • the Source-HEX 2004 may be configured to generate thermal energy through thermal coupling of the heat transfer media 2005 with any typology of fission or fusion fuels.
  • the I-HEX 2007 is thermally coupled to the process heat exchanger 2030 (also referred to as P- HEX 2030), which may be disposed within a modular container 2041, which houses the PCS 2002.
  • HS-WF 206 may be any suitable working fluid as those utilized as heat transfer media 2005 and 2006.
  • HS-WF 206 thermally couples the thermal energy source 2000, PCS 2001, PCS 2002 and the power utilization system 2003.
  • a high energy thermodynamic state e.g., high-temperature, high-pressure and high massflowrate
  • HS-WF 206 when HS-WF 206 is at a low energy thermodynamic state, it is represented by solid arrows.
  • HS-WF 206 may circulate through containers 2039 that houses the source heat exchanger 2004, container 2040, housing PCS 2001, and container 2041 that houses PCS 2002, by operation of pump 2011 of PCS 2001.
  • pump 2011 For configurations in which HS-WF 206 is a gaseous working fluid, pump 2011 may be configured as a compressor 2011.
  • the flow rate of high energy content HS-WF circulating out of I-HEX 2007 may be controlled by a three-way valve 1901 actuated by a control system (not shown in Fig. 20).
  • valve 1901 may be actuated to enable partial flow or shutoff the PH-WF circulation within PCS 2002.
  • a substantial amount (e.g., substantially all) of the energy content represented by PH-WF may be converted into electricity by turbinegenerator 2013.
  • the electric and thermal power system operators determine the amount of thermal energy from Source-HEX 2004 that may be converted to electricity by PCS 2001, versus the amount of thermal energy transferred to the PCS 2002 and to the PH-WF 2016.
  • the turbinegenerator 2013, housed within container 2040, is part of a Rankine or Brayton thermodynamic cycle.
  • the power conversion components forming the PCS 2001 support the operations of a Brayton cycle.
  • the power conversion components forming the PCS 2001 support the operations of a Rankine cycle. Accordingly, when the PCS 2001 operates as a Brayton cycle, the turbomachinery of the turbine-generator assembly 2013 may be represented by axial or centrifugal turbines, the pressure tank 2012 may be utilized to support HS-WF 206 inventory control operations, for example, through actuation of valves to reduce or increase the inventory of gaseous HS-WF 206 (pressure tank 2012 valves are not shown in Fig. 20). To complete the thermodynamic closed-loop forming the PCS 2001, the cooler heat exchanger 2009 may reset the HS-WF 206 minimum Brayton cycle temperature and pressure.
  • the cooler heat exchanger 2009 may be represented by a radiator, through which HS-WH 206 circulates on one side of the cooler heat exchanger, with fluids representing the Ultimate Heat Sink, for example, environmental air or water, circulated on the other side of the cooler heat exchanger 2009, further aided by active fans or pumps.
  • the HS-WF 206 is represented by a working fluid in a liquid form or a two-phase fluid (e.g., water-steam)
  • the turbine-generator 2013 may be represented by a traditional vapor-powered turbine driving an electric generator
  • the cooler heat exchanger 2009 and the HS-WF 206 reservoir 2010 become part of the Rankine cycle condenser
  • the pressure tank 2012 may be represented by a pressurizer.
  • the thermal -hydraulic couplings between containers 2039, 2040, and 2041 are not shown in Fig. 20. These hydraulic couplings may be represented by hydraulic ports 901 as shown, for example, in Fig. 9.
  • the compressor-recirculator turbomachinery 114 can be driven by shaft 118a as shown in Figs. 5-7, and 11, 13, 13a, 17- 19 when the generator 120 is disconnected from mechanical coupler 121.
  • the compressor-recirculator turbomachinery 114 is driven by an electric motor with multiple electric energy source, as represented by the PCS 2001 and the PCS 2002, where electric power is controlled and distributed across the electric and thermal conversion system 2000S through the power supply 1710 which may be coupled to the power grid or system 2000S microgrid, for example, represented by electrical connections 2042.
  • PH-WF 2016 As PH-WF 2016 is compressed by compressor turbomachinery 114, it flows through the one circuit of the P-HEX 2030 (e.g. heat exchanger secondary circuit), without mixing with the HS-WF 206 circulating on the other circuit of this heat exchanger (e.g., heat exchanger primary circuit).
  • the HS-WF 206 circulating on the other circuit of this heat exchanger (e.g., heat exchanger primary circuit).
  • substantially all of the inventory, or a part of the inventory, of hot PH-WF 2016h flows through inlet 2037 of power utilization system 2003.
  • vent valve 2023 of PCS 2002 Assuming vent valve 2023 of PCS 2002 is set to the closed position, all of the inventory of the hot PH-WF 2016h, flows out of outlet 2043 interfacing the PCS 2002 with the arc furnace piping 2052, into the furnace 2032.
  • actuated valve 2023a When actuated valve 2023a is open, hot PH-WF 2016h flows inside furnace 2032 through inlet 2037 as a result of compressor turbomachinery 114.
  • PH-WF 2016h transfers its thermal energy to the materials to be melted into liquid steel to support industrial steelmaking operations. These materials are transformed from solids at environmental temperature to liquid through very high temperature induced by electric arcs.
  • a high temperature area 2028 is formed.
  • substantially all of the solid materials inside the furnace may change their thermodynamic state from solid to liquid, which may need substantial energy.
  • the total electric consumption at the electrodes 2036 is reduced proportionally to the amount of energy transferred from the thermal energy source 2000, to the power utilization system 2003 via PH-WF 2016h.
  • the hot PH-WF 2016h flows inside the furnace 2032, heats up the solid materials to be melted into liquid steel, and continues to flow out of the furnace 2032 through outlet 2038 and return PH-WF piping 2017.
  • PH-WF 2016h flows through return piping 2017, it flows through a filtering system 2029 configured to trap contaminants from the materials to be melted inside the furnace.
  • Filtered PH-WF 2016f flows through heat exchanger 2033 disposed within or thermal-hydraulically coupled to return flow piping 2017, to cool down prior to entering inlet 2045 of the PCS 2002.
  • Part of the thermal energy transferred by PH-WF 2016f is converted into electricity by turbine-generator 2021 (e.g., based on a Rankine or Brayton power cycle), while a portion of this energy is rejected to the environment through condenser heat exchanger 2022, (for Rankine configurations), or radiator heat exchanger 2022 (for Brayton configurations), thermally rejecting heat via fan 2018.
  • the fan 2018 may be disposed at PCS 2002 outlet 2019, where environmental cooling fluids (e.g. water or air) flow through PCS 2002 inlet 2020.
  • the electrodes 2036 are lifted and electrically disconnected via electric bus 2035, and the liquid steel gate 2048 is opened for a duration of time proportional to the amount of liquid steel 2050 to be processed while emptying the furnace.
  • the actuated PH-WF valve 2023a is closed, while the actuated vent valve 2023 is opened.
  • the hot PH-WF 2016h transfers its energy to heat exchanger 2024 of the PCS 2022.
  • the carbon-free thermal energy source 2000, the PCS 2001, and PCS 2002 may be configured to produce electricity to be distributed to the power grid or system 2000s microgrid to support steel re-heating as shown in Fig. 22, via electric buses 1710, and power conditioner 2035.
  • a controlled flow of PH-WF 2016h is provided through manifold 2053 for thermal hydraulic coupling with hot PH-WF hot piping 2027 as, for example, shown in Fig. 22.
  • Fig. 21 shows a simplified configuration with schematic and top view representations of the system for electric and thermal power conversion and power utilization 2000s shown in Fig. 20.
  • Fig. 21 further shows multiple thermal and electrical energy sources and power conversion systems according to another embodiment of the present disclosure.
  • the system shown in Fig. 21 may also be referred to as a thermal and electric power conversion and utilization system 2100.
  • Fig. 21 shows a top view of building 2101, housing multiple thermal energy sources configured as, for example, heat sources 900, 1700 and 1400, described in Figs. 9, 14 and 17 respectively, a power conversion system 2002, described in Fig. 20, an underground Independent Spent Fuel Storage Installation (ISFSI) 2012, as defined by the U.S.
  • ISFSI underground Independent Spent Fuel Storage Installation
  • an electric power transformer 2035 to condition the electricity produced by the power conversion system 2002 and supply it to the electric and thermal power utilization system 2003, a thermally insulated piping system 2027 for a working fluid 2016h at high temperature to flow directly from the thermal sources 900, 1700 and 2100, or indirectly through the process heat exchanger 2030 (also referred to as P-HEX 2030) of power conversion system 2002 shown in Fig. 20, a power utilization system 2003 represented by a furnace 2032, and a thermally insulated flow return piping system 2017 thermal-hydraulically coupled to the furnace 2032 for the working fluid 2016h with a lower energy content to return to the power conversion system 2002.
  • the thermal and electric power conversion and utilization system 2100 results in a small footprint inclusive of the steel manufacturing plant represented by the furnace 2032 and steelmaking equipment, for example, shown in Fig. 22, with building 2101 altogether within the power generation and steelmaking plant comprised within the plant security fence 2104.
  • the building 2101 shown in Fig. 21 is configured to house three thermal power sources and one ISFSI. As this is a prefabricated design for the building, extending it to accommodate additional thermal energy sources, for example, to satisfy increased steel production capabilities may be done at low cost.
  • the operations and functions of the thermal energy sources 900, 1400 and 1700, as well as those of the power conversion system 2002 and power utilization system 2003 are described in greater detail in Fig. 20.
  • the steel slab is found as relatively low temperature steel slab 22061t when it enters the reheating chamber 2200, and its temperature increases as it moves through the reheating chamber 2200 to exit the reheating chamber as a relatively high temperature steel slab 2206ht.
  • the reheating chamber 2200 is pressurized by the PH-WF 2016, flexible seals 2207 minimize the loss of PH-WF 2016 at the reheating chamber processed steel inlet 2210 and outlet 2211.
  • the PH-WF 2016 is collected by the PH-WH 2016 collector 2204 at the PH-WF 2016 working fluid outlet of the reheating chamber 2200.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

Divers modes de réalisation donnés à titre d'exemple d'un système d'alimentation pour convertir l'énergie thermique issue d'une source de chaleur en électricité sont décrits. Dans un mode de réalisation donné à titre d'exemple, le système de conversion d'énergie comprend un moteur à turbine basé sur des moteurs à turbine à gaz à combustible fossile ou à gaz lourd couplés à des générateurs électriques, équipé d'un échangeur de chaleur couplé thermiquement à une source de chaleur sans carbone pour convertir l'énergie thermique provenant de la source de chaleur sans carbone en air s'écoulant à travers le compresseur de moteur et s'étendant à travers la turbomachine d'un détendeur couplé à un arbre mécanique entraînant le compresseur de moteur et un générateur électrique.
PCT/US2024/033464 2023-06-11 2024-06-11 Système de conversion d'énergie sans carbone pour fournir de la chaleur et de l'électricité de traitement à haute température Ceased WO2024258884A2 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US202363472341P 2023-06-11 2023-06-11
US63/472,341 2023-06-11
US202463623336P 2024-01-21 2024-01-21
US63/623,336 2024-01-21
US202463639697P 2024-04-28 2024-04-28
US63/639,697 2024-04-28

Publications (3)

Publication Number Publication Date
WO2024258884A2 WO2024258884A2 (fr) 2024-12-19
WO2024258884A3 WO2024258884A3 (fr) 2025-01-16
WO2024258884A9 true WO2024258884A9 (fr) 2025-03-13

Family

ID=93852864

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2024/033464 Ceased WO2024258884A2 (fr) 2023-06-11 2024-06-11 Système de conversion d'énergie sans carbone pour fournir de la chaleur et de l'électricité de traitement à haute température

Country Status (1)

Country Link
WO (1) WO2024258884A2 (fr)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5967461A (en) * 1997-07-02 1999-10-19 Mcdonnell Douglas Corp. High efficiency environmental control systems and methods
US6827104B2 (en) * 2001-10-24 2004-12-07 Mcfarland Rory S. Seal and valve systems and methods for use in expanders and compressors of energy conversion systems
AU2016211197A1 (en) * 2015-01-30 2017-09-21 Claudio Filippone Waste heat recovery and conversion
CA3074015A1 (fr) * 2017-08-31 2019-03-07 Claudio Filippone Systeme de conversion d'energie pour generateurs d'energie nucleaire et procedes associes
EP3660294B1 (fr) * 2018-11-30 2024-07-31 Rolls-Royce plc Moteur de turbine à gaz
US11506124B2 (en) * 2020-03-27 2022-11-22 Raytheon Technologies Corporation Supercritical CO2 cycle for gas turbine engines having supplemental cooling
IT202000006727A1 (it) * 2020-03-31 2021-10-01 Nuovo Pignone Tecnologie Srl Turboespantore-generatore integrato a tenuta

Also Published As

Publication number Publication date
WO2024258884A3 (fr) 2025-01-16
WO2024258884A2 (fr) 2024-12-19

Similar Documents

Publication Publication Date Title
CN114174660B (zh) 能量转换设备和系统
EP3623602B1 (fr) Cycle d'expansion hybride à refroidissement intermédiaire et turbo-générateur
Ma et al. Dynamic simulation and analysis of transient characteristics of a thermal-to-electrical conversion system based on supercritical CO2 Brayton cycle in hypersonic vehicles
US11749417B2 (en) Power conversion system for nuclear power generators
El-Genk et al. Noble-gas binary mixtures for closed-Brayton-cycle space reactor power systems
US20160290214A1 (en) Heat pipe cooled turbine casing system for clearance management
US20230392545A1 (en) Power conversion system including engine and heat exchanger
Andreades et al. Reheat-air brayton combined cycle power conversion design and performance under nominal ambient conditions
WO2012045034A2 (fr) Systèmes de moteur d'avion et procédés de fonctionnement associés
EP3850221B1 (fr) Module de compresseur
EP1057986A1 (fr) Moteur thermique
US3956899A (en) Gas turbine plant where a circulating medium is indirectly heated
WO2024258884A9 (fr) Système de conversion d'énergie sans carbone pour fournir de la chaleur et de l'électricité de traitement à haute température
CA2789172A1 (fr) Installation de production d'energie a partir d'un reacteur nucleaire rapide a gaz
JP6712672B1 (ja) 超臨界ｃｏ２ガスを用いた発電装置及び発電システム
EP3864257B1 (fr) Module de turbine
Wright et al. Operational Results of a Closed Brayton Cycle Test‐Loop
Qin et al. Load-following operation of supercritical CO2 power cycles under turbine speed control with different shaft configurations
Keller et al. Industrial closed-cycle gas turbines for conventional and nuclear fuel
Saadon et al. Modelling and thermal analysis of organic rankine cycle with superheater and preheater
EP4176163B1 (fr) Système de récupération de chaleur perdue en tant que système de secours pour une machine pour la production d'énergie
US12221924B2 (en) Combined gas turbine engine and fuel cell
Li et al. " Supercritical carbon dioxide turbine design and arrangement optimization", Front
Angelino et al. Medium temperature 100 kW ORC engine for total energy systems
Kostin et al. Development of a design for the GT-MHR energy conversion unit

Legal Events

Date Code Title Description
NENP Non-entry into the national phase

Ref country code: DE