WO1997031184A1 - Hydrogen fueled power plant with recuperation - Google Patents
Hydrogen fueled power plant with recuperation Download PDFInfo
- Publication number
- WO1997031184A1 WO1997031184A1 PCT/US1997/002814 US9702814W WO9731184A1 WO 1997031184 A1 WO1997031184 A1 WO 1997031184A1 US 9702814 W US9702814 W US 9702814W WO 9731184 A1 WO9731184 A1 WO 9731184A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- flow
- oxygen
- steam
- pressurized
- hydrogen
- Prior art date
Links
- 239000001257 hydrogen Substances 0.000 title claims abstract description 72
- 229910052739 hydrogen Inorganic materials 0.000 title claims abstract description 72
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 title claims abstract description 55
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 claims abstract description 108
- 239000001301 oxygen Substances 0.000 claims abstract description 108
- 229910052760 oxygen Inorganic materials 0.000 claims abstract description 108
- 238000002485 combustion reaction Methods 0.000 claims abstract description 40
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 15
- 238000000034 method Methods 0.000 claims description 25
- 238000001816 cooling Methods 0.000 claims description 24
- 239000000203 mixture Substances 0.000 claims description 19
- 238000010438 heat treatment Methods 0.000 claims description 4
- 239000000446 fuel Substances 0.000 abstract description 21
- 150000002431 hydrogen Chemical class 0.000 abstract description 19
- 150000002430 hydrocarbons Chemical class 0.000 abstract description 6
- 229930195733 hydrocarbon Natural products 0.000 abstract description 5
- 239000004215 Carbon black (E152) Substances 0.000 abstract description 3
- MYMOFIZGZYHOMD-UHFFFAOYSA-N Dioxygen Chemical compound O=O MYMOFIZGZYHOMD-UHFFFAOYSA-N 0.000 abstract description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 8
- 239000007789 gas Substances 0.000 description 6
- 239000007788 liquid Substances 0.000 description 5
- 239000012530 fluid Substances 0.000 description 4
- 229910052757 nitrogen Inorganic materials 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- 239000012809 cooling fluid Substances 0.000 description 2
- -1 gaseous oxygen Chemical compound 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 229910017464 nitrogen compound Inorganic materials 0.000 description 1
- 150000002830 nitrogen compounds Chemical class 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 230000003134 recirculating effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
-
- 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
- F02C6/003—Gas-turbine plants with heaters between turbine stages
-
- 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
- F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
- F02C3/20—Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products
- F02C3/22—Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products the fuel or oxidant being gaseous at standard temperature and pressure
-
- 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
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/005—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for the working fluid being steam, created by combustion of hydrogen with oxygen
Definitions
- the present invention relates to a method of burning hydrogen in a turbine power plant. More specifically, the present invention relates to a power plant in which hydrogen is burned in oxygen and in which exhaust heat is recovered by recuperation.
- a hydrocarbon fuel such as natural gas or distillate oil
- a hydrocarbon fuel such as natural gas or distillate oil
- the hot gas which is typically pressurized to about 1000-1500 kPa (150-200 psia)
- the hot gas transfers heat to feed water so as to generate steam, which is then expanded in a steam turbine to produce shaft power.
- the turbine drives a load, such as an electrical generator or compressor, so as to deliver useful shaft power.
- NOx oxides of nitrogen
- thermal NOx the conversion of atmospheric nitrogen in the combustion air to NOx
- organically bound nitrogen compounds such as HN 3 (ammonia) and HCN
- prompt NOx the reaction between atmospheric nitrogen and hydrocarbon fragments formed from the breakdown of hydrocarbons in the fuel
- Burning hydrogen fuel in pure oxygen would eliminate Nox entirely since there would be no hydrocarbons to create prompt and fuel bound NOx and no atmospheric nitrogen.
- Combustors for rocket engines have traditionally operated by combusting liquid hydrogen in liquid oxygen.
- power plant turbines must operate for extended periods of time without deterioration and must make as efficient use as possible of the energy available in the fuel.
- this object is accomplished in a method of generating rotating shaft power, comprising the steps of: (i) combusting a flow of pressurized hydrogen in a flow of pressurized oxygen in a combustor, thereby consuming at least a portion of the flow of pressurized oxygen and producing a flow of hot pressurized steam, (ii) expanding the flow of hot pressurized steam so as to produce a flow of at least partially expanded steam, at least a portion of the expansion being accomplished in a turbine, thereby producing shaft power, and (iii) transferring heat from the flow of at least partially expanded steam to at least one of the flows of pressurized hydrogen and pressurized oxygen prior to the combustion thereof.
- the flows of hydrogen and oxygen are pressurized above their critical pressures prior to the combustion thereof, and the step of transferring heat from the flow of expanded steam comprises transferring heat to both the flows of pressurized hydrogen and oxygen.
- Figure 1 is a schematic diagram of a first embodiment of the turbine power plant according to the current invention, in which all of the oxygen for combustion of the hydrogen fuel is supplied to the first combustor, after the oxygen has been passed through one or more cooling flow paths.
- Figure 2 is a schematic diagram of a second embodiment of the turbine power plant according to the current invention, in which only the oxygen necessary for stoichiometric combustion of the hydrogen fuel is supplied to each combustor.
- Figure 1 a schematic diagram of a first embodiment of the hydrogen fueled power plant of the current invention.
- the primary components of the power plant are an oxygen source 1, a hydrogen source 2, a recuperator 6, primary, secondary and tertiary combustora ⁇ , 10, and 12, respectively, and high, intermediate and low pressure power turbines 14, 16, and 1 8, respectively, each of which drives a load (not shown ) such as an electrical generator.
- the turbines are preferably of the conventional type and comprised of a plurality of alternating rows of stationary vanes and rotating blades.
- the stationary vanes are affixed to a cylinder and the rotating blades are affixed to a centrally disposed rotating shaft.
- the combustors may be of the conventional type used in gas turbines or may be of special design.
- the oxygen 30 from the oxygen source 1 is at a temperature of approximately 143°K (258°R ) or colder so that it is a cryogenic liquid.
- a b oost compressor 3 raises the pressure of the oxygen 30 above its supercritical pressure, which for oxygen in approximately 4970 kPa (720 psia) and, most preferably to about 34,500 kPa (5000 psia) .
- the pressurized oxygen 3 2 then flows through the recuperator 6, where it is heated, preferably to about 540°C (1000°F) . Since the oxygen 32 is preferably pressurized above its critical pressure, no change in state accompanies this heating so that the heated oxygen 34 discharged from the recuperator remains in essentially the liquid state. However, if sub-critical pressure oxygen, including gaseous oxygen, is supplied to the recuperator 6, the heated oxygen 34 will be in the gaseous state.
- the recuperator has heat transfer surfaces formed therein that allow heat to flow from low pressure steam 76, discussed further below, to the pressurized oxygen 32 without contact between the oxygen and the steam.
- the recuperator 6 may be of the shell and tube type, with the pressurized oxygen 32 flowing through finned tubes and the low pressure steam 76 flowing over the tubes. From the recuperator 6, the heated pressurized oxygen 34 is divided into three streams 38, 40 and 42.
- Oxygen stream 38 flows through a cooling flow path 24 formed in the high pressure turbine 14, where it is used to cool the turbine components so that they are not excessively heated by the hot pressurized steam/oxygen mixture 71 that flows through the high pressure turbine 14.
- the turbine components through which the cooling flow path 24 extends may include the rotating blades and stationary vanes.
- the blades and vanes have cooling fluid passages formed within them that allow heat transferred to the blades and vanes from the hot steam/oxygen mixture 71 to be subsequently transferred to the oxygen 38 flowing through the cooling path 24, thereby heating the oxygen 38 and cooling the blades and vanes.
- the further heated oxygen 39 which has now been preferably heated to approximately 650°C (1200°F) , is then discharged from the cooling flow path 24 and exits the turbine.
- oxygen streams 40 and 42 flow through cooling flow paths 26 and 28 formed in the intermediate and low pressure turbines 16 and 18, respectively.
- the cooling flow paths 24, 26 and 28 are of the closed loop type so that all of the oxygen 38, 40 and 42 that enters the cooling flow paths is discharged from the turbines 14, 16 and 18.
- a certain amount of the oxygen 38, 40 and 42 can be bled from the cooling flow paths 24, 26, and 28 into the steam/oxygen mixtures 71-76 flowing through the turbines.
- the pressurized oxygen 34 is used as the cooling fluid for the turbine components
- the turbine could also be cooled by the pressurized hydrogen 54, either exclusively, or in combination with the oxygen by employing separate oxygen and hydrogen cooling flow paths through selected turbine components.
- such cooling may be accomplished by recirculating steam from the recuperator, as discussed hereinafter.
- the hydrogen 50 from the hydrogen source 1 is at a temperature of 17°K (30°R) or less so that it is also a cryogenic liquid.
- a boost compressor 4 raises the pressure of the hydrogen 50 above the supercritical pressure, which for hydrogen in approximately 1280 kPa (185 psia) and, most preferably to about 34,500 kPa (5000 psia) .
- the pressurized hydrogen 52 then flows through the recuperator 6 in which it is heated, preferably to about 540 ⁇ C (1000°F) , in a manner similar to the pressurized oxygen 32.
- the hydrogen 32 is preferably pressurized above its critical pressure, no change in state accompanies this heating so that the heated hydrogen 54 discharged from the recuperator remains in essentially the liquid state. However, if sub-critical pressure hydrogen, including gaseous hydrogen, is supplied to the recuperator 6, the heated hydrogen 54 will be in the gaseous state.
- the recuperator has heat transfer surfaces formed therein that allow heat to flow from the low pressure steam 76 to the pressurized hydrogen 52 without contact between the hydrogen and the steam.
- the heated pressurized hydrogen 54 is divided into three streams 56, 58 and 60, which are directed to the primary, secondary and tertiary combustors 8, 10, and 12, respectively.
- the pressure of the steam/oxygen mixtures 73-76 flowing through the intermediate and low pressure turbines 16 and 18, respectively, is less than that flowing through the high pressure turbine 14. Therefore, in the preferred embodiment of the invention, the hydrogen streams 58 and 60 are partially expanded in small power turbines 20 and 22, respectively, prior to their introduction into the secondary and tertiary combustors 10 and 12. This allows a portion of the energy expended to compress the hydrogen 52 to be recovered as useful work.
- sufficient hydrogen 56 is combusted in the primary combustor 8 to heat the high pressure steam/oxygen mixture 71 to approximately 1650°C (3000°F) .
- the high pressure steam/oxygen mixture 71 is partially expanded to an intermediate pressure in the high pressure turbine 14 so as to produce useful shaft power.
- the temperature of the steam/oxygen mixture 72 is reduced, preferably to about 810°C (1500°F) .
- the intermediate pressure steam/oxygen mixture 72 discharged from the high pressure turbine 14 is then reheated in the secondary combustor 10, in which the second portion 59 of the hydrogen fuel is combusted with a portion of the oxygen in the steam/oxygen mixture 72. Since not all of the remaining oxygen is consumed in the second combustor 10, the combustion may again be characterized as oxygen rich/fuel lean.
- the combustion in the secondary combustor 10 preferably raising the temperature of the intermediate pressure steam/oxygen mixture back to approximately 1650°C (3000 ⁇ F) .
- the reheated intermediate steam/oxygen mixture 73 from the secondary combustor 10 is then further expanded to a low pressure in the intermediate pressure turbine 16, thereby producing additional shaft power. In so doing, its temperature is again reduced, preferably to about 810°C (1500°F) .
- the low pressure steam/oxygen mixture 74 discharged from the intermediate pressure turbine 16 is then reheated in the tertiary combustor 12, in which the third portion 57 of the hydrogen fuel is combusted with the remaining portion of the oxygen in the steam/oxygen mixture 74, preferably raising the temperature of the low pressure steam/oxygen mixture back to approximately 1650°C (3000°F) .
- the oxygen is preferably depleted by the combustion in the tertiary combustor 12
- this combustion may be characterized as stoichiometric and the fluid discharged b y the tertiary combustor is essentially pure steam.
- the reheated low pressure steam 75 from the tertiary combustor 12 is then further expanded in the low pressure turbine 18, where its temperature is again reduced, preferably to about 810°C (1500°F) .
- the low pressure turbine 18 produces yet more shaft power.
- the pressure of the expanded steam 76 discharged from the low pressure turbine 18 is at sub- atmospheric pressure, for example, about 7 kPa (1 psia) .
- the total pressure drop experienced by the fluid from the primary combustor 8 to the recuperator 6 is approximately evenly divided among the high, intermediate and low pressure turbines 14, 16 and 18, respectively, so that the expansion ratio in each turbine is the cube root of 3.
- the combustion in the tertiary combustor 12 consumes all of the remaining oxygen, it may be desirable in some circumstance to employ lean combustion in the tertiary combustor 12 as well, so that the fluid discharged from the tertiary combustor will contain some excess oxygen.
- the embodiment shown in Figure 1 employs three turbines 24, 16 and 18, a greater or lesser number of turbines could also be utilized in order to optimize thermodynamic efficiency and cost.
- the steam 76 discharged from low pressure turbine 18 is directed to the recuperator 6, where its temperature is further reduced by transferring heat to the incoming flows of cryogenic oxygen and hydrogen 32 and 52, respectively.
- the temperature of the steam 77 discharged from the recuperator 6 will be a function of the temperature and mass flow rate of the incoming steam 76 as well as the inlet and outlet temperatures and flow rates of the oxygen and hydrogen.
- the steam 77 will be sufficiently cooled in the recuperator 6 so that it is condensed.
- the condensate 77 is then discharged for use as process water or discharged to the environment.
- the recuperator 6 may only partially cool the steam 76, in which case the partially cooled expanded steam discharged from the recuperator will then be directed to a condenser (not shown) .
- rotating shaft power is efficiently produced without the generation of NOx.
- the only emission from the power plant is pure water, which can be safely discharged to the environment after, at most, a slight cooling.
- FIG. 2 shows a second embodiment of the current invention.
- oxygen 132 and hydrogen 152 are supplied by oxygen and hydrogen sources 101 and 102, respectively.
- the oxygen 132 and hydrogen 152 are pressurized above their critical pressures but are not cryogenic -- e.g., ambient temperature and approximately 20,500 kPa (3000 psia).
- the oxygen 132 and hydrogen 152 are heated in a recuperator 106 by the transfer of heat from the low pressure steam 176, as before.
- the oxygen 134 and hydrogen 154 are preferably heated to approximately 260-540°C (500-1000°F) .
- the heated oxygen 134 and heated hydrogen 154 are each divided into three streams.
- the first portion 144 of the oxygen and the first portion of the hydrogen 160 are combusted in a primary combustor 108.
- the combustion is carried out essentially stoichiometrically so that essentially all of the oxygen 144 is consumed in combusting all of the hydrogen 160.
- the primary combustor 108 discharges a flow of high pressure supercritical essentially pure steam 171 -- i.e., steam at a pressure greater than the supercritical pressure of steam, which is approximately 21,840 kPa (3168 psia) .
- the temperature is prevented from becoming excessive by the introduction of flows of supercritical steam 181 and 188 into the primary combustor 108, as discussed below, that moderate the combustion temperature. Consequently, the high pressure supercritical steam 17 1 discharged from the primary combustor 108 is comprised of the steam formed by the combustion of the oxygen 144 and hydrogen 160, as well as the injection of steam 181 and 188.
- the supercritical steam 171 discharged by the primary combustor 108 is at a pressure and temperature of approximately 20,500 kPa (3000 psia) and 1650°C (3000°F) , respectively.
- the high pressure supercritical steam 171 is partially expanded to an intermediate pressure in the high pressure turbine 114 so as to produce useful shaft power. In so doing, the temperature of the steam is reduced, preferably to about 810°C (1500°F) .
- the intermediate pressure steam 172 discharged from the high pressure turbine 114 is then reheated in the secondary combustor 110, in which the second portion 159 of the hydrogen fuel is combusted with the second portion 136 of the oxygen.
- the combustion in the secondary combustor 110 is preferably carried out under essentially stoichiometric conditions so that essentially pure intermediate pressure steam 173 is produced.
- the combustion in the secondary combustor 110 preferably raises the temperature of the intermediate pressure steam 173 back to approximately 1650°C (3000°F) .
- the reheated intermediate pressure steam 173 from the secondary combustor 110 is then further expanded to a low pressure in the intermediate pressure turbine 116, thereby producing additional shaft power. In so doing, its temperature is again reduced, preferably to about 810°C (1500°F) .
- the low pressure steam 174 discharged from the intermediate pressure turbine 116 is then reheated in the tertiary combustor 112, in which the third portion 157 of the hydrogen fuel is combusted with the third portion 135 of the oxygen.
- the combustion in the tertiary combustor 112 is preferably carried out under essentially stoichiometric conditions so that essentially pure low pressure steam 175 is produced.
- the combustion in the tertiary combustor 112 preferably raises the temperature of the low pressure steam 175 back to approximately 1650°C (3000°F) .
- the reheated low pressure steam 175 from the tertiary combustor 112 is then further expanded in the low pressure turbine 18, where its temperature is again reduced, preferably to about 810°C (1500°F) .
- the low pressure turbine 118 produces yet more shaft power.
- the pressure of the expanded steam 176 discharged from the low pressure turbine 118 is at sub- atmospheric pressure as before, with the total pressure drop experienced by the fluid being approximately evenly divided among the high, intermediate and low pressure turbines 114, 116 and 118, respectively.
- the steam 176 discharged from the low pressure turbine 118 is directed to the recuperator 106, where its temperature is further reduced by transferring heat to the incoming flows of oxygen 132 and hydrogen 152, respectively, as before, but also to pressurized water 179, as discussed below.
- the cooled steam 177 is then directed to a condenser 198.
- the condensate from the condenser 198 is divided into two steams 178 and 199.
- the stream 199 is discharged for other uses or to the environment .
- the condensate stream 178 is pressurized by a pump 200 to a pressure greater than its critical pressure, and preferably to approximately 20,500 kPa (3000 psia) .
- the pressurized water 179 could be injected directly into the primary combustor 108 in order to control the combustion temperature, the pressurized water 179 preferably first flows through the recuperator 1 0 6 where its temperature is raised by the transfer of heat from the expanded steam 176. Within the recuperator 106, the water 179 is divided into two streams 180 and 181.
- the first stream 180 is discharged from the recuperator 6 as a flow of supercritical steam after having flowed through only a portion of the heat transfer apparatus. Preferably its temperature is raised to approximately 260°C (500°F) .
- the steam 180 discharged from the recuperator 106 is then divided into three streams 1 82, 184 and 186, each of which flows through one of the cooling flow paths 124, 126 and 128 formed in the components of the high, intermediate and low pressure turbines 114, 116 and 118, as previously discussed. In each of the cooling flow paths, heat is transferred to the steam, preferably raising its temperature to approximately 540°C (1000°F) .
- the second stream of supercritical steam 181 from the recuperator 106 is discharged after having flowed through the entirety of the heat transfer apparatus so that its temperature is raised beyond that of the steam 180, and preferably to approximately the same temperature as the steam flows 183, 185 and 187 discharged from the turbine cooling flow paths 124, 126 and 128 -- i.e., to approximately 540°C (1000 ⁇ F) .
- the second flow of heated supercritical steam is directed directly to the primary combustor 108.
- the recuperator 106 is located downstream of the low pressure turbine 118, the recuperator could also be advantageously located upstream of the low pressure turbine.
- the low pressure turbine 118 may be of the condensing type, and the low pressure combustor may be eliminated.
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- 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
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP53036397A JP2001515556A (en) | 1996-02-26 | 1997-02-25 | Hydrogen fuel power plant using heat transfer heat exchanger |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US60662896A | 1996-02-26 | 1996-02-26 | |
US08/606,628 | 1996-02-26 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997031184A1 true WO1997031184A1 (en) | 1997-08-28 |
Family
ID=24428772
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1997/002814 WO1997031184A1 (en) | 1996-02-26 | 1997-02-25 | Hydrogen fueled power plant with recuperation |
Country Status (4)
Country | Link |
---|---|
JP (1) | JP2001515556A (en) |
KR (1) | KR19990087240A (en) |
CA (1) | CA2247197A1 (en) |
WO (1) | WO1997031184A1 (en) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1998012421A1 (en) * | 1996-09-19 | 1998-03-26 | Siemens Westinghouse Power Corporation | Closed loop steam cooled steam turbine |
WO1998017897A1 (en) * | 1996-10-21 | 1998-04-30 | Siemens Westinghouse Power Corporation | Hydrogen fueled power plant |
DE19808119A1 (en) * | 1996-09-30 | 1999-09-02 | Mitsubishi Heavy Ind Ltd | Low temperature hydrogen combustion turbine |
WO2010104547A3 (en) * | 2009-03-09 | 2010-11-04 | Clean Energy Systems, Inc. | Method and system for enhancing power output of renewable thermal cycle power plants |
GB2504568A (en) * | 2012-07-31 | 2014-02-05 | James Corbishley | Venturi heat exchanger for power plant condenser |
EP2295766A3 (en) * | 2009-08-06 | 2014-05-21 | General Electric Company | Combined-cycle steam turbine having novel steam cooling flow configuration |
WO2015118282A1 (en) | 2014-02-04 | 2015-08-13 | James Corbishley | Apparatus and method of energy recovery for use in a power generating system |
SE2100028A1 (en) * | 2021-03-01 | 2022-02-23 | Procope Maarten | Utilization of hydrogen and oxygen for explosion engines and heating of buildings etc. |
EP4083501A1 (en) * | 2021-04-30 | 2022-11-02 | Siemens Energy Global GmbH & Co. KG | Combustion device for combustion of hydrogen and method for carrying out the combustion |
EP4134528A1 (en) * | 2021-07-28 | 2023-02-15 | Pratt & Whitney Canada Corp. | Aircraft engine with hydrogen fuel system |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2016079828A (en) * | 2014-10-10 | 2016-05-16 | 川崎重工業株式会社 | Turbine blade cooling structure and gas turbine engine |
GB202215721D0 (en) * | 2022-10-24 | 2022-12-07 | Rolls Royce Plc | Gas turbine engine fuel system |
Citations (2)
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FR1000608A (en) * | 1946-03-11 | 1952-02-14 | Rateau Soc | High power gas turbine engine unit with good efficiency at fractional loads |
US4148185A (en) * | 1977-08-15 | 1979-04-10 | Westinghouse Electric Corp. | Double reheat hydrogen/oxygen combustion turbine system |
-
1997
- 1997-02-25 WO PCT/US1997/002814 patent/WO1997031184A1/en not_active Application Discontinuation
- 1997-02-25 CA CA002247197A patent/CA2247197A1/en not_active Abandoned
- 1997-02-25 KR KR1019980706641A patent/KR19990087240A/en not_active Application Discontinuation
- 1997-02-25 JP JP53036397A patent/JP2001515556A/en active Pending
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
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FR1000608A (en) * | 1946-03-11 | 1952-02-14 | Rateau Soc | High power gas turbine engine unit with good efficiency at fractional loads |
US4148185A (en) * | 1977-08-15 | 1979-04-10 | Westinghouse Electric Corp. | Double reheat hydrogen/oxygen combustion turbine system |
Non-Patent Citations (2)
Title |
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NAJJAR Y S H: "HYDROGEN FUELED AND COOLED GAS TURBINE ENGINE", INTERNATIONAL JOURNAL OF HYDROGEN ENERGY, vol. 15, no. 11, 1 January 1990 (1990-01-01), pages 827 - 832, XP000174546 * |
Y. TSUJIKAWA ET AL.: "Characteristic of hydrogen-fueled gas turbine cycle with intercooler, hydrogen turbine and hydrogen heater", INTERNATIONAL JOURNAL OF HYDROGEN ENERGY, vol. 10, no. 10, 1985, OXFORD (GB), pages 677 - 683, XP002032262 * |
Cited By (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5953900A (en) * | 1996-09-19 | 1999-09-21 | Siemens Westinghouse Power Corporation | Closed loop steam cooled steam turbine |
WO1998012421A1 (en) * | 1996-09-19 | 1998-03-26 | Siemens Westinghouse Power Corporation | Closed loop steam cooled steam turbine |
DE19808119A1 (en) * | 1996-09-30 | 1999-09-02 | Mitsubishi Heavy Ind Ltd | Low temperature hydrogen combustion turbine |
US6098398A (en) * | 1996-09-30 | 2000-08-08 | Mitsubishi Heavy Industries, Ltd. | Low temperature hydrogen combustion turbine |
DE19808119C2 (en) * | 1996-09-30 | 2002-06-27 | Mitsubishi Heavy Ind Ltd | Hydrogen combustion turbine plant |
WO1998017897A1 (en) * | 1996-10-21 | 1998-04-30 | Siemens Westinghouse Power Corporation | Hydrogen fueled power plant |
US5775091A (en) * | 1996-10-21 | 1998-07-07 | Westinghouse Electric Corporation | Hydrogen fueled power plant |
US8631658B2 (en) | 2008-03-07 | 2014-01-21 | Clean Energy Systems, Inc. | Method and system for enhancing power output of renewable thermal cycle power plants |
EP2406468A4 (en) * | 2009-03-09 | 2014-08-27 | Clean Energy Systems Inc | Method and system for enhancing power output of renewable thermal cycle power plants |
WO2010104547A3 (en) * | 2009-03-09 | 2010-11-04 | Clean Energy Systems, Inc. | Method and system for enhancing power output of renewable thermal cycle power plants |
EP2406468A2 (en) * | 2009-03-09 | 2012-01-18 | Clean Energy Systems, Inc. | Method and system for enhancing power output of renewable thermal cycle power plants |
EP2295766A3 (en) * | 2009-08-06 | 2014-05-21 | General Electric Company | Combined-cycle steam turbine having novel steam cooling flow configuration |
GB2504568A (en) * | 2012-07-31 | 2014-02-05 | James Corbishley | Venturi heat exchanger for power plant condenser |
GB2504568B (en) * | 2012-07-31 | 2014-06-11 | James Corbishley | A method of condensing and energy recovery using the Venturi effect, and a method of energy storage using that method in a hydrogen oxygen combusting turbine |
WO2015118282A1 (en) | 2014-02-04 | 2015-08-13 | James Corbishley | Apparatus and method of energy recovery for use in a power generating system |
US10233783B2 (en) | 2014-02-04 | 2019-03-19 | James CORBISHLEY | Apparatus and method of energy recovery for use in a power generating system using the Venturi effect |
SE2100028A1 (en) * | 2021-03-01 | 2022-02-23 | Procope Maarten | Utilization of hydrogen and oxygen for explosion engines and heating of buildings etc. |
EP4083501A1 (en) * | 2021-04-30 | 2022-11-02 | Siemens Energy Global GmbH & Co. KG | Combustion device for combustion of hydrogen and method for carrying out the combustion |
WO2022228766A1 (en) | 2021-04-30 | 2022-11-03 | Siemens Energy Global GmbH & Co. KG | Combustion device for combusting hydrogen and method for carrying out the combustion |
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Also Published As
Publication number | Publication date |
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KR19990087240A (en) | 1999-12-15 |
JP2001515556A (en) | 2001-09-18 |
CA2247197A1 (en) | 1997-08-28 |
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