US20150000280A1 - Electricity generation device and method - Google Patents
Electricity generation device and method Download PDFInfo
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- US20150000280A1 US20150000280A1 US14/371,569 US201314371569A US2015000280A1 US 20150000280 A1 US20150000280 A1 US 20150000280A1 US 201314371569 A US201314371569 A US 201314371569A US 2015000280 A1 US2015000280 A1 US 2015000280A1
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- evaporator
- reheater
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- 230000005611 electricity Effects 0.000 title claims abstract description 25
- 238000000034 method Methods 0.000 title claims abstract description 24
- 239000012530 fluid Substances 0.000 claims abstract description 111
- 239000002918 waste heat Substances 0.000 claims abstract description 20
- 239000007788 liquid Substances 0.000 claims abstract description 15
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims abstract description 14
- 238000011084 recovery Methods 0.000 claims abstract description 9
- 229910052757 nitrogen Inorganic materials 0.000 claims abstract description 7
- 239000007789 gas Substances 0.000 claims description 22
- 238000003860 storage Methods 0.000 claims description 8
- 238000010438 heat treatment Methods 0.000 claims description 6
- 238000003303 reheating Methods 0.000 claims description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 4
- 238000004146 energy storage Methods 0.000 claims description 3
- 238000001704 evaporation Methods 0.000 claims description 3
- 239000003949 liquefied natural gas Substances 0.000 claims 1
- 239000003570 air Substances 0.000 description 12
- 230000008901 benefit Effects 0.000 description 7
- 238000009826 distribution Methods 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 241001672018 Cercomela melanura Species 0.000 description 1
- 238000004887 air purification Methods 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 238000012864 cross contamination Methods 0.000 description 1
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- 239000002803 fossil fuel Substances 0.000 description 1
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- 231100000719 pollutant Toxicity 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
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- 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
-
- 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
- F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
- F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
- F02C1/05—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly characterised by the type or source of heat, e.g. using nuclear or solar energy
-
- 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
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
-
- 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
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
- F01K25/103—Carbon dioxide
-
- 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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/02—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of multiple-expansion type
- F01K7/025—Consecutive expansion in a turbine or a positive displacement engine
-
- 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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
-
- 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
- F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
- F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
-
- 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
- F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
- F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
- F02C1/08—Semi-closed cycles
-
- 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
- F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/60—Application making use of surplus or waste energy
Definitions
- the present invention relates to electricity generation devices and methods that use a cryogenic fluid such as liquid nitrogen or liquid air and a source of low grade waste heat, and means of increasing the efficiency of energy recovery from such devices.
- a cryogenic fluid such as liquid nitrogen or liquid air and a source of low grade waste heat
- Electricity distribution networks are often supported by a fleet of diesel generators and open cycle gas turbines that provide electricity during periods of high demand and emergency events such as the unexpected failure of a power station.
- Such generating assets often referred to as peaking plant, burn fossil fuels at low efficiency and can be a significant source of atmospheric pollutants.
- the services provided by such peaking plant include, but are not limited to:
- the loss of power from the electricity distribution network can result in significant economic loss to some consumers, such as a data centre, or danger to personnel, for example in the event of a power failure at a hospital.
- Such applications often utilise diesel generators to provide standby electricity in the event of an interruption to the supply of electricity from the distribution network. Replacement of such diesel powered generators with a zero emissions device that uses a fuel from a sustainable source would be of benefit.
- the present inventors have realised that there is potential to generate electricity using the expansion of liquid air, liquid nitrogen or cryogen to drive a turbine to generate electricity.
- Such a device could provide a compact, reactive and environmentally clean solution to the problems of balancing network supply with demand.
- WO 2007/096656 discloses a cryogenic energy storage system which exploits the temperature and phase differential between low temperature liquid air, liquid nitrogen or cryogen, and ambient air, or waste heat, to store energy at periods of low demand and/or excess production, allowing this stored energy to be released later to generate electricity during periods of high demand and/or constrained output.
- the system comprises a means for liquefying air during periods of low electricity demand, a means for storing the liquid air produced and an expansion turbine for expanding the liquid air.
- the expansion turbine is connected to a generator to generate electricity when required to meet shortfalls between supply and demand.
- GB1100569.1 develops the power recovery element of WO 2007/096656 and discloses a device, the cryogenset, and method for the generation of zero emission electricity that uses a cryogenic fluid and a source of low grade waste heat, and can be used to provide load balancing and emergency support to an electricity distribution network, or back up power to a critical consumer such as a hospital or data centre.
- the invention of GB1100569.1 utilises a cryogenic fluid, such as liquid nitrogen or liquid air, and a source of low grade waste heat 140 to power a turbogenerator.
- the emissions from the device are either gaseous nitrogen or gaseous air and present no environmental concerns.
- the cryogenic fluid is manufactured in an industrial refrigeration or air separation plant 100 using power from the grid 150 or from a renewable source 160 and supplied by tanker or pipeline 110 to the cryogenset 130 preferably via a storage tank 120 .
- a major constraint on the efficiency of such systems and devices is the poor utilisation of the thermal energy released from the cryogenic fluid during heating to ambient temperature.
- the exhaust of the cryogenset is only a few degrees above the temperature of the cryogenic fluid, and therefore significantly below ambient temperature. Ideally, the exhaust from the process would be much closer to ambient temperature due to more effective recovery of work from the process.
- the inventors have discovered that further work can be extracted from the working fluid by the inclusion of additional power recovery cycles to the main open Rankine cycle described in GB1100569.1.
- the additional power recovery cycles combined with the main Rankine cycle exploit the temperature differences between ambient and the exhaust of the first Rankine cycle to extract more work from the working fluid.
- Several cycles can be included to progressively increase the final exhaust temperature to close to ambient.
- the efficiency of each additional cycle progressively reduces as the temperature difference between the hot and cold parts of the cycle reduces, thereby lowering the Carnot efficiency of each incremental additional cycle.
- one or two additional cycles would be applied as the cost—benefit of further cycles is marginal.
- a combined cycle gas turbine power station utilises an open Brayton cycle combined with a closed steam Rankine bottoming cycle.
- a cryogenset could be combined with a closed Rankine cycle utilizing a working fluid that condenses in the operating range between ambient and the temperature of the cryogen (see FIG. 2 ).
- an open or closed Brayton cycle could be used (see FIGS. 3 a and b ).
- the inlet air to the Brayton bottoming cycle may be first passed through an air purification unit to remove water and carbon dioxide.
- simplification of the design is achieved by combining the main working fluid and bottoming cycle working fluid at the inlet of the first or second expansion turbine.
- an energy generation device comprising:
- a storage tank for storing a cryogenic fluid
- a fluid pump for compressing cryogenic fluid taken from the storage tank to a high pressure
- an evaporator for evaporating the high pressure cryogenic fluid, to provide a high pressure gas
- a first expansion turbine for expanding the high pressure gas and extracting work from the high pressure gas
- a first reheater for reheating the gas exhausted from the first expansion turbine using ambient or waste heat
- the second expansion turbine has an exhaust outlet which is split into first and second paths such that the working fluid exhausted from the second expansion turbine is divided into first and second portions, wherein the first portion of working fluid is directed along the first path to ambient through a first exhaust, and the second portion of working fluid is directed along the second path to an inlet of the evaporator such that the second portion of working fluid exchanges thermal energy with the high pressure cryogenic fluid within the evaporator;
- a first compressor for compressing the second portion of working fluid after it has passed through the evaporator, wherein an exhaust outlet of the compressor is connected with an exhaust outlet of the first expansion turbine such that the second portion of working fluid and the gas exhausted from the first expansion turbine are combined and directed into the first reheater to be reheated using the ambient or waste heat.
- the present invention combines a Rankine cycle with a Brayton cycle.
- the compressor is generally driven by an electric motor or similar device.
- One or both of the expansion turbines could be used to drive a generator to produce electricity from the rotational energy produced by expansion turbines.
- the cryogenic fluid acts as the working fluid within the system.
- the working fluid in the two cycles is the same.
- the mass flow of fluid through the second turbine is inherently greater than that through the first turbine.
- the fluid pump compresses the cryogenic fluid to a high pressure of at least 50 bar and more typically over 100 bar.
- the electricity generation device may further comprise a superheater for heating the high pressure working fluid output from the evaporator to a high temperature using a source of heat from a co-located process.
- the co-located source of heat may be from the ambient environment, from the atmosphere, the ground, river, sea or lake water or from a source of waste heat such as a power station, or industrial plant such as steel works or a data centre, or similar source of low grade waste heat, e.g. cooling water from a power station.
- the superheater may be positioned in the system between the evaporator and the first expansion turbine.
- the combined flow of fluid that passes through the reheater is expanded to around ambient pressure in the second expansion turbine.
- the second expansion turbine comprises a low pressure turbine from which work is extracted.
- the divided exhaust of the second low pressure expansion turbine releases part of the flow to ambient through the first exhaust and the remainder is circulated to the evaporator where the low pressure working fluid exchanges thermal energy with the cryogenic high pressure working fluid.
- the resulting low pressure and low temperature gas is compressed in the compressor before merging with the exhaust of the first high pressure expansion turbine.
- the reheater reheats the working fluid exhausted from the first expansion turbine using a source of ambient or waste heat.
- the peak cycle temperature is driven by the available heating source. This can be from the ambient environment, from the atmosphere, the ground, river, sea or lake water or from a co-located process such as a power station, or industrial plant such as steel works or a data centre, or similar source of low grade waste heat.
- the device may further comprise a third expansion turbine and a second reheater positioned between the evaporator and the first expansion turbine, and a fourth expansion turbine and a third reheater positioned between the first reheater and the second expansion turbine.
- the heated cryogen working fluid is expanded through two high pressure stages and two low pressure stages and the pressure is progressively reduced in the four stages, with interstage re-heating between each expansion stage.
- a superheater may be positioned between the evaporator and the third expansion turbine.
- the device may further comprise a second compressor for compressing the second portion of working fluid after it has passed through the evaporator a first time and directing the second portion of working fluid back through the evaporator a second time before it is further compressed by the first compressor.
- the second portion of the working fluid is first cooled in the evaporator and then compressed by the second, low pressure compressor before returning for further cooling in the evaporator and compression in the first, high pressure compressor.
- the additional compressor reduces the compressor work, by utilising interstage cooling.
- the high pressure turbine stage, or stages may be mounted on the same power shaft as the compressor, or compressors. This arrangement has the advantage of both higher efficiency and reduced cost, through reduced drive losses.
- a device according to the present invention may be used as the power recovery component of a cryogenic energy storage system.
- the device of the present invention has an improved cost/benefit trade off relative to the cryogenset described in GB1100569.1. Calculations by the inventors have indicated that a 20% or more improvement in specific work can be achieved for a less than 4% increase in equipment cost. In the storage market, the significant reduction in operating costs resulting from the improved efficiency of the present invention will be favourable for the modest increase in capital cost.
- the present invention offers a number of significant advantages over the devices shown in FIGS. 2 , 3 a and 3 b .
- the advantages include:
- FIG. 1 shows the configuration of a cryogenset in relation to co-located sources of waste heat and the cryogen delivery options from a remote located air separation plant;
- FIG. 2 shows a cryogenset with a Rankine bottoming cycle
- FIG. 3 a shows a cryogenset with a closed Brayton bottoming cycle
- FIG. 3 b shows a cryogenset with an open Brayton bottoming cycle
- FIG. 4 shows a first embodiment of an electricity generation device and method of the present invention with two turbine stages
- FIG. 5 shows a temperature entropy diagram for the first embodiment of the invention shown in FIG. 4 ;
- FIG. 6 shows a second embodiment of an electricity generation device and method of the present invention with four turbine stages
- FIG. 7 shows a third embodiment of an electricity generation device and method of the present invention with four turbine stages and two compressor stages.
- a first embodiment of the present invention consists of a cryogenic tank 400 from which a cryogenic, or working, fluid is transferred to a high pressure pump 410 .
- the cryogenic fluid is compressed to a high pressure, of at least 50 bar and more typically over 100 bar.
- the high pressure fluid is then heated in a heat exchanger 420 , referred to as an evaporator, where thermal energy is transferred between the cryogenic working fluid from the tank and low pressure working fluid in a Brayton loop of the combined cycle.
- Further heat is optionally added from a co-located source of waste heat 480 , such as cooling water from a power station, in the superheater 430 .
- the resulting high pressure fluid which is now in the gaseous state if the pressure is below the critical pressure or in a liquid state if the temperature and pressure conditions are supercritical, is expanded through a first high pressure turbine 440 , from which work is extracted.
- the exhaust from the high pressure turbine is combined with the discharge from the Brayton cycle loop compressor 470 and reheated using ambient or waste heat 480 in the reheater 450 .
- the combined flow (Rankine loop and Brayton loop) is expanded to around ambient pressure in the low pressure turbine 460 from which work is extracted.
- the exhaust of the turbine is then divided, part of the flow is released to ambient through the exhaust 490 and the remainder is circulated to the evaporator 420 where the low pressure working fluid exchanges thermal energy with the cryogenic high pressure working fluid.
- the steady-state flow from the exhaust 490 is equal to the mass flow from the tank.
- the portion of the exhaust which is circulated to the evaporator 420 is a low pressure and low temperature gas which is compressed in the compressor 470 before merging with the exhaust of the high pressure turbine 440 .
- the working fluid in the Rankine loop and the Brayton loop are inherently the same.
- the cycle is represented on a temperatureentropy diagram in FIG. 5 , where the state numbers shown on the diagram of FIG. 5 correspond to the numbered positions shown in hexagons in FIG. 4 .
- a significantly improved performance is achieved by expanding the heated cryogen working fluid through two high pressure stages 441 and 442 and two low pressure stages 461 and 462 where the pressure is progressively reduced in four stages, with interstage re-heating between each expansion stage. In this way, the expansion process is closer to the ideal isothermal case.
- the complete process is as follows: the cryogenic working fluid is first transferred from a tank 400 to a high pressure pump 410 . The now high pressure fluid is then heated in an evaporator 420 where thermal energy is exchanged with a low pressure fluid in a Brayton loop.
- the high pressure warmed working fluid is then optionally further heated by waste heat or ambient heat in a superheater 430 .
- the high pressure and high temperature working fluid is then expanded in a high pressure turbine 441 , reheated in a re-heater 451 and expanded in a further high pressure turbine 442 .
- the working fluid then combines with the high pressure feed from the Brayton loop and is heated in a further re-heater 452 .
- the fluid is expanded in a low pressure turbine 461 , is then re-heated in a further re-heater 453 and finally expanded in a further low pressure turbine stage 462 .
- the exhaust of the final low pressure turbine is divided into a re-circulation flow and an exhaust flow 490 .
- the re-circulation flow is first cooled in the evaporator 420 and then compressed in a compressor 470 before combining with the main working fluid flow upstream of the reheater 452 .
- Typical temperatures, pressures and mass flows at various points around the cycle are shown in the following table (Table 1) and refer to the numbered positions shown in hexagons in FIG. 6 :
- table 1 refers to one example of the invention, operating at relatively low pressure (Stage 1 turbine inlet of 100 bar), in line with the operating pressures of readily available turbo-machinery. Analysis by the inventors has indicated better performance can be achieved at higher peak working fluid pressures should such equipment be available.
- an additional compressor stage is added to the system to reduce the compressor work, by utilising interstage cooling.
- the low pressure Brayton loop working fluid is cooled in the evaporator 420 and first compressed by the low pressure compressor 472 before returning for further cooling in the evaporator and compression in the high pressure compressor 471 .
- the compressor work is reduced by this design but at the expense of the complexity of an additional compressor stage.
- the high pressure turbine stage 440 or stages 441 and 442 are mounted on the same power shaft as the compressor 470 or compressors 471 and 472 .
- the inventors have discovered the power delivered by the high pressure turbine stages almost exactly matches the compressor power requirement at the optimal operating conditions.
- This embodiment has the advantage of both higher efficiency and reduced cost, through reduced drive losses through the deletion of the electric motor connected to the compressor and reducing the power output and therefore size of the generator connected to the turbines.
- the generator output is reduced in this embodiment, the net output of the system remains the same as the previous embodiment as the parasitic electrical load of the compressor motor is removed through directly driving the compressor by the high pressure turbines.
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Abstract
The present invention relates to electricity generation devices and methods that use a cryogenic fluid such as liquid nitrogen or liquid air and a source of low grade waste heat, and means of increasing the efficiency of energy recovery from such devices by combining Rankine and Brayton cycles.
Description
- The present invention relates to electricity generation devices and methods that use a cryogenic fluid such as liquid nitrogen or liquid air and a source of low grade waste heat, and means of increasing the efficiency of energy recovery from such devices.
- Electricity distribution networks (or grids) are often supported by a fleet of diesel generators and open cycle gas turbines that provide electricity during periods of high demand and emergency events such as the unexpected failure of a power station. Such generating assets, often referred to as peaking plant, burn fossil fuels at low efficiency and can be a significant source of atmospheric pollutants. The services provided by such peaking plant, include, but are not limited to:
-
- balancing differences in supply and demand at different times of the day and at short notice;
- providing electricity required to power the auxiliary equipment required for restart of a generating asset in the event of total network failure (black-start support);
- network reinforcement where parts of the electricity distribution network have a shortfall in capacity during periods of high power demand;
- injecting power into the network to support the frequency of the grid when demand for electricity increases rapidly.
- In addition, the loss of power from the electricity distribution network can result in significant economic loss to some consumers, such as a data centre, or danger to personnel, for example in the event of a power failure at a hospital. Such applications often utilise diesel generators to provide standby electricity in the event of an interruption to the supply of electricity from the distribution network. Replacement of such diesel powered generators with a zero emissions device that uses a fuel from a sustainable source would be of benefit.
- There is a need for a device that can provide a similar service but that uses a fuel that produces low or preferably zero atmospheric pollution that originates from a sustainable source.
- The present inventors have realised that there is potential to generate electricity using the expansion of liquid air, liquid nitrogen or cryogen to drive a turbine to generate electricity. Such a device could provide a compact, reactive and environmentally clean solution to the problems of balancing network supply with demand.
- WO 2007/096656 discloses a cryogenic energy storage system which exploits the temperature and phase differential between low temperature liquid air, liquid nitrogen or cryogen, and ambient air, or waste heat, to store energy at periods of low demand and/or excess production, allowing this stored energy to be released later to generate electricity during periods of high demand and/or constrained output. The system comprises a means for liquefying air during periods of low electricity demand, a means for storing the liquid air produced and an expansion turbine for expanding the liquid air. The expansion turbine is connected to a generator to generate electricity when required to meet shortfalls between supply and demand.
- GB1100569.1 develops the power recovery element of WO 2007/096656 and discloses a device, the cryogenset, and method for the generation of zero emission electricity that uses a cryogenic fluid and a source of low grade waste heat, and can be used to provide load balancing and emergency support to an electricity distribution network, or back up power to a critical consumer such as a hospital or data centre. Referring to
FIG. 1 , the invention of GB1100569.1 utilises a cryogenic fluid, such as liquid nitrogen or liquid air, and a source of lowgrade waste heat 140 to power a turbogenerator. The emissions from the device are either gaseous nitrogen or gaseous air and present no environmental concerns. The cryogenic fluid is manufactured in an industrial refrigeration orair separation plant 100 using power from the grid 150 or from a renewable source 160 and supplied by tanker orpipeline 110 to thecryogenset 130 preferably via a storage tank 120. - A major constraint on the efficiency of such systems and devices is the poor utilisation of the thermal energy released from the cryogenic fluid during heating to ambient temperature. The exhaust of the cryogenset is only a few degrees above the temperature of the cryogenic fluid, and therefore significantly below ambient temperature. Ideally, the exhaust from the process would be much closer to ambient temperature due to more effective recovery of work from the process.
- The inventors have discovered that further work can be extracted from the working fluid by the inclusion of additional power recovery cycles to the main open Rankine cycle described in GB1100569.1. The additional power recovery cycles combined with the main Rankine cycle exploit the temperature differences between ambient and the exhaust of the first Rankine cycle to extract more work from the working fluid. Several cycles can be included to progressively increase the final exhaust temperature to close to ambient. However, the efficiency of each additional cycle progressively reduces as the temperature difference between the hot and cold parts of the cycle reduces, thereby lowering the Carnot efficiency of each incremental additional cycle. In practice, one or two additional cycles would be applied as the cost—benefit of further cycles is marginal.
- The approach is well known, and the so called ‘topping’ or ‘bottoming’ cycle is often applied to power generation devices. For example, a combined cycle gas turbine power station utilises an open Brayton cycle combined with a closed steam Rankine bottoming cycle. A cryogenset could be combined with a closed Rankine cycle utilizing a working fluid that condenses in the operating range between ambient and the temperature of the cryogen (see
FIG. 2 ). Alternatively, an open or closed Brayton cycle could be used (seeFIGS. 3 a and b). - In most cases, different working fluids are used for the main and bottoming cycle, such as air and steam in the case mentioned above. The inventors have noticed that in the case of the cryogenset, a single working fluid can be used for both the main working fluid and bottoming cycle working fluid if an open Brayton cycle (such as that shown in
FIG. 3 b) is used as the bottoming cycle. This has the advantage of simplifying the design and reducing cost, an essential feature in the target market of reserve power. In the cycle ofFIG. 3 b, the inlet air to the Brayton bottoming cycle may be first passed through an air purification unit to remove water and carbon dioxide. Referring toFIG. 4 , simplification of the design is achieved by combining the main working fluid and bottoming cycle working fluid at the inlet of the first or second expansion turbine. - Accordingly, the present invention provides an energy generation device comprising:
- a storage tank for storing a cryogenic fluid,
- a fluid pump for compressing cryogenic fluid taken from the storage tank to a high pressure,
- an evaporator for evaporating the high pressure cryogenic fluid, to provide a high pressure gas,
- a first expansion turbine for expanding the high pressure gas and extracting work from the high pressure gas;
- a first reheater for reheating the gas exhausted from the first expansion turbine using ambient or waste heat;
- a second expansion turbine for expanding the working fluid exhausted from the first reheater and extracting work from the working fluid exhausted from the first reheater; wherein
- the second expansion turbine has an exhaust outlet which is split into first and second paths such that the working fluid exhausted from the second expansion turbine is divided into first and second portions, wherein the first portion of working fluid is directed along the first path to ambient through a first exhaust, and the second portion of working fluid is directed along the second path to an inlet of the evaporator such that the second portion of working fluid exchanges thermal energy with the high pressure cryogenic fluid within the evaporator; and
- a first compressor for compressing the second portion of working fluid after it has passed through the evaporator, wherein an exhaust outlet of the compressor is connected with an exhaust outlet of the first expansion turbine such that the second portion of working fluid and the gas exhausted from the first expansion turbine are combined and directed into the first reheater to be reheated using the ambient or waste heat.
- Consequently, the present invention combines a Rankine cycle with a Brayton cycle.
- The compressor is generally driven by an electric motor or similar device. One or both of the expansion turbines could be used to drive a generator to produce electricity from the rotational energy produced by expansion turbines.
- The cryogenic fluid acts as the working fluid within the system.
- With the arrangement of the present invention, the working fluid in the two cycles is the same. In addition, the mass flow of fluid through the second turbine is inherently greater than that through the first turbine.
- The fluid pump compresses the cryogenic fluid to a high pressure of at least 50 bar and more typically over 100 bar.
- The electricity generation device may further comprise a superheater for heating the high pressure working fluid output from the evaporator to a high temperature using a source of heat from a co-located process. The co-located source of heat may be from the ambient environment, from the atmosphere, the ground, river, sea or lake water or from a source of waste heat such as a power station, or industrial plant such as steel works or a data centre, or similar source of low grade waste heat, e.g. cooling water from a power station. The superheater may be positioned in the system between the evaporator and the first expansion turbine.
- The combined flow of fluid that passes through the reheater is expanded to around ambient pressure in the second expansion turbine. The second expansion turbine comprises a low pressure turbine from which work is extracted.
- The divided exhaust of the second low pressure expansion turbine releases part of the flow to ambient through the first exhaust and the remainder is circulated to the evaporator where the low pressure working fluid exchanges thermal energy with the cryogenic high pressure working fluid. The resulting low pressure and low temperature gas is compressed in the compressor before merging with the exhaust of the first high pressure expansion turbine.
- The reheater reheats the working fluid exhausted from the first expansion turbine using a source of ambient or waste heat. The peak cycle temperature is driven by the available heating source. This can be from the ambient environment, from the atmosphere, the ground, river, sea or lake water or from a co-located process such as a power station, or industrial plant such as steel works or a data centre, or similar source of low grade waste heat.
- The device may further comprise a third expansion turbine and a second reheater positioned between the evaporator and the first expansion turbine, and a fourth expansion turbine and a third reheater positioned between the first reheater and the second expansion turbine. In this case, the heated cryogen working fluid is expanded through two high pressure stages and two low pressure stages and the pressure is progressively reduced in the four stages, with interstage re-heating between each expansion stage. In this case, a superheater may be positioned between the evaporator and the third expansion turbine.
- The device may further comprise a second compressor for compressing the second portion of working fluid after it has passed through the evaporator a first time and directing the second portion of working fluid back through the evaporator a second time before it is further compressed by the first compressor. In this arrangement, the second portion of the working fluid is first cooled in the evaporator and then compressed by the second, low pressure compressor before returning for further cooling in the evaporator and compression in the first, high pressure compressor. The additional compressor reduces the compressor work, by utilising interstage cooling.
- The high pressure turbine stage, or stages, may be mounted on the same power shaft as the compressor, or compressors. This arrangement has the advantage of both higher efficiency and reduced cost, through reduced drive losses.
- A device according to the present invention may be used as the power recovery component of a cryogenic energy storage system.
- The device of the present invention has an improved cost/benefit trade off relative to the cryogenset described in GB1100569.1. Calculations by the inventors have indicated that a 20% or more improvement in specific work can be achieved for a less than 4% increase in equipment cost. In the storage market, the significant reduction in operating costs resulting from the improved efficiency of the present invention will be favourable for the modest increase in capital cost.
- The present invention offers a number of significant advantages over the devices shown in
FIGS. 2 , 3 a and 3 b. The advantages include: - 1. Reduced part count and therefore cost. The present inventors have calculated that the cost increase of the present invention relative to the single cycle cryogenset of GB 1100569.1 is less than 4%, for a 20% improvement in efficiency. The designs shown in
FIGS. 2 , 3 a and 3 b would be likely to incur cost increases of 20 to 40% for similar efficacy improvements. - 2. Simplified fluid handling. The closed Rankine and Brayton cycles require separate fluid loops which lead to an associated complexity in preventing cross contamination of the fluids. The system of the present invention does not suffer from such complexity.
- Embodiments of the present invention will now be described with reference to the figures in which:
-
FIG. 1 shows the configuration of a cryogenset in relation to co-located sources of waste heat and the cryogen delivery options from a remote located air separation plant; -
FIG. 2 shows a cryogenset with a Rankine bottoming cycle; -
FIG. 3 a shows a cryogenset with a closed Brayton bottoming cycle; -
FIG. 3 b shows a cryogenset with an open Brayton bottoming cycle; -
FIG. 4 shows a first embodiment of an electricity generation device and method of the present invention with two turbine stages; -
FIG. 5 shows a temperature entropy diagram for the first embodiment of the invention shown inFIG. 4 ; -
FIG. 6 shows a second embodiment of an electricity generation device and method of the present invention with four turbine stages; and -
FIG. 7 shows a third embodiment of an electricity generation device and method of the present invention with four turbine stages and two compressor stages. - A first embodiment of the present invention, shown in
FIG. 4 , consists of acryogenic tank 400 from which a cryogenic, or working, fluid is transferred to ahigh pressure pump 410. The cryogenic fluid is compressed to a high pressure, of at least 50 bar and more typically over 100 bar. The high pressure fluid is then heated in aheat exchanger 420, referred to as an evaporator, where thermal energy is transferred between the cryogenic working fluid from the tank and low pressure working fluid in a Brayton loop of the combined cycle. Further heat is optionally added from a co-located source ofwaste heat 480, such as cooling water from a power station, in thesuperheater 430. The resulting high pressure fluid, which is now in the gaseous state if the pressure is below the critical pressure or in a liquid state if the temperature and pressure conditions are supercritical, is expanded through a firsthigh pressure turbine 440, from which work is extracted. The exhaust from the high pressure turbine is combined with the discharge from the Braytoncycle loop compressor 470 and reheated using ambient orwaste heat 480 in thereheater 450. The combined flow (Rankine loop and Brayton loop) is expanded to around ambient pressure in thelow pressure turbine 460 from which work is extracted. The exhaust of the turbine is then divided, part of the flow is released to ambient through theexhaust 490 and the remainder is circulated to theevaporator 420 where the low pressure working fluid exchanges thermal energy with the cryogenic high pressure working fluid. The steady-state flow from theexhaust 490 is equal to the mass flow from the tank. The portion of the exhaust which is circulated to theevaporator 420 is a low pressure and low temperature gas which is compressed in thecompressor 470 before merging with the exhaust of thehigh pressure turbine 440. The working fluid in the Rankine loop and the Brayton loop are inherently the same. - The cycle is represented on a temperatureentropy diagram in
FIG. 5 , where the state numbers shown on the diagram ofFIG. 5 correspond to the numbered positions shown in hexagons inFIG. 4 . - In a second, preferred embodiment of the invention, shown in
FIG. 6 , two additional turbine stages are added to the process to improve the work recovery from the working fluid. The inventors have found a significantly improved performance is achieved by expanding the heated cryogen working fluid through two high pressure stages 441 and 442 and two low pressure stages 461 and 462 where the pressure is progressively reduced in four stages, with interstage re-heating between each expansion stage. In this way, the expansion process is closer to the ideal isothermal case. The complete process is as follows: the cryogenic working fluid is first transferred from atank 400 to ahigh pressure pump 410. The now high pressure fluid is then heated in anevaporator 420 where thermal energy is exchanged with a low pressure fluid in a Brayton loop. The high pressure warmed working fluid is then optionally further heated by waste heat or ambient heat in asuperheater 430. The high pressure and high temperature working fluid is then expanded in ahigh pressure turbine 441, reheated in a re-heater 451 and expanded in a furtherhigh pressure turbine 442. The working fluid then combines with the high pressure feed from the Brayton loop and is heated in afurther re-heater 452. The fluid is expanded in alow pressure turbine 461, is then re-heated in afurther re-heater 453 and finally expanded in a further lowpressure turbine stage 462. The exhaust of the final low pressure turbine is divided into a re-circulation flow and anexhaust flow 490. The re-circulation flow is first cooled in theevaporator 420 and then compressed in acompressor 470 before combining with the main working fluid flow upstream of thereheater 452. Typical temperatures, pressures and mass flows at various points around the cycle are shown in the following table (Table 1) and refer to the numbered positions shown in hexagons inFIG. 6 : -
Process Temperatures, Pressure Temperature Mass Flow Pressures and Flows Bar abs ° C. Kg/s 1 Storage Tank 5.0 −197 30 2 Evaporator Inlet 102 −193 30 3 Super-Heater Inlet 101.5 −57 30 4 Stage 1 Turbine Inlet 100 20 30 5 Stage 1 Turbine Outlet 31.6 −54 30 6 Stage 2 Turbine Inlet31.6 20 30 7 Stage 2Turbine Outlet 10 −53.9 30 8 Stage 3Turbine Inlet 10 20 93.83 9 Stage 3 Turbine Outlet3.32 −51.26 93.83 10 Stage 4 Turbine Inlet3.32 20 93.83 11 Stage 4 Turbine Outlet1.1 −51.37 93.83 12 Compressor Inlet 1 −186 63.83 13 Compressor Outlet 10 −96.03 63.83 - It is noted that the conditions shown in table 1 refer to one example of the invention, operating at relatively low pressure (Stage 1 turbine inlet of 100 bar), in line with the operating pressures of readily available turbo-machinery. Analysis by the inventors has indicated better performance can be achieved at higher peak working fluid pressures should such equipment be available.
- In another embodiment shown in
FIG. 7 , an additional compressor stage is added to the system to reduce the compressor work, by utilising interstage cooling. The low pressure Brayton loop working fluid is cooled in theevaporator 420 and first compressed by thelow pressure compressor 472 before returning for further cooling in the evaporator and compression in thehigh pressure compressor 471. The compressor work is reduced by this design but at the expense of the complexity of an additional compressor stage. - In a further embodiment, which is not shown in the figures, the high
pressure turbine stage 440 orstages compressor 470 orcompressors
Claims (20)
1. An energy generation device comprising:
a storage tank for storing a cryogenic fluid,
a fluid pump for compressing cryogenic fluid taken from the storage tank to a high pressure,
an evaporator for evaporating the high pressure cryogenic fluid, to provide a high pressure gas,
a first expansion turbine for expanding the high pressure gas and extracting work from the high pressure gas;
a first reheater for reheating gas exhausted from the first expansion turbine using ambient or waste heat;
a second expansion turbine for expanding working fluid exhausted from the first reheater and extracting work from the working fluid exhausted from the first reheater; wherein
the second expansion turbine has an exhaust outlet which is split into first and second paths such that the working fluid exhausted from the second expansion turbine is divided into first and second portions, wherein the first portion of working fluid is directed along the first path to ambient through a first exhaust, and the second portion of working fluid is directed along the second path to an inlet of the evaporator such that the second portion of working fluid exchanges thermal energy with the high pressure cryogenic fluid within the evaporator; and
a first compressor for compressing the second portion of working fluid after it has passed through the evaporator, wherein an exhaust outlet of the compressor is connected with an exhaust outlet of the first expansion turbine such that the second portion of working fluid and the gas exhausted from the first expansion turbine are combined and directed into the first reheater to be reheated using the ambient or waste heat.
2. The device of claim 1 wherein at least one of the first and second expansion turbines is used to drive a generator to produce electricity.
3. The device of claim 1 wherein the fluid pump provides for compressing the cryogenic fluid to a pressure of at least 50 bar.
4. The device of claim 1 , further comprising a superheater for heating high pressure working fluid output from the evaporator to a high temperature using a source of heat from a co-located process.
5. The device of claim 4 , wherein the co-located source of heat is at least one of the ambient environment, the atmosphere, the ground, river, sea or lake water, and waste heat from a power station or industrial plant.
6. The device of claim 1 , wherein the first expansion turbine is mounted on a same power shaft as the first compressor.
7. The device of claim 1 , further comprising:
a third expansion turbine and a second reheater positioned between the evaporator and the first expansion turbine, and
a fourth expansion turbine and a third reheater positioned between the first reheater and the second expansion turbine.
8. The device of claim 7 wherein the first and third expansion turbines are mounted on a same power shaft as the first compressor.
9. The device of claim 1 , further comprising a second compressor for compressing the second portion of the working fluid after it has passed through the evaporator a first time and directing the second portion of the working fluid back through the evaporator a second time before the second portion of the working fluid is compressed by the first compressor.
10. The device of claim 9 further comprising:
a third expansion turbine and a second reheater positioned between the evaporator and the first expansion turbine, and
a fourth expansion turbine and a third reheater positioned between the first reheater and the second expansion turbine,
wherein the first and third expansion turbines are mounted on a same power shaft as the first and second compressors.
11. A cryogenic energy storage system having a power recovery component comprising the device of claim 1 .
12. A method of generating energy comprising:
storing a cryogenic fluid in a storage tank;
extracting the cryogenic fluid from the storage tank and compressing the cryogenic fluid to a high pressure using a fluid pump;
evaporating the high pressure cryogenic fluid in an evaporator to provide a high pressure gas;
expanding the high pressure gas using a first expansion turbine and extracting work from the high pressure gas;
reheating gas exhausted from the first expansion turbine using a first reheater and ambient or waste heat;
expanding working fluid exhausted from the first reheater and extracting work from the working fluid exhausted from the first reheater using a second expansion turbine; wherein
the second expansion turbine has an exhaust outlet which is split into first and second paths such that the working fluid exhausted from the second expansion turbine is divided into first and second portions, wherein
the first portion of working fluid is directed along the first path to ambient through a first exhaust, and the second portion of working fluid is directed along the second path to an inlet of the evaporator such that the second portion of working fluid exchanges thermal energy with the high pressure cryogenic fluid within the evaporator; and
using a first compressor to compress the second portion of working fluid after it has passed through the evaporator, wherein an exhaust outlet of the compressor is connected with an exhaust outlet of the first expansion turbine such that the second portion of working fluid and the gas exhausted from the first expansion turbine are combined and directed into the first reheater to be reheated using the ambient or waste heat.
13. The method of claim 12 further comprising using at least one of the first and second expansion turbines to drive a generator and produce electricity.
14. The method of claim 12 , further comprising using a superheater and a source of heat from a co-located process to heat high pressure working fluid output from the evaporator to a high temperature.
15. The method of claim 12 , further comprising:
expanding the high pressure gas using a third expansion turbine;
reheating gas exhausted from the third expansion turbine using a second reheater; and
expanding the working fluid exhausted from the first reheater using a fourth expansion turbine; and
reheating the gas exhausted from the fourth expansion turbine using a third reheater.
16. The method of any of claim 12 , further comprising using a second compressor to compress the second portion of working fluid after it has passed through the evaporator a first time and directing the second portion of working fluid back through the evaporator a second time before it is compressed by the first compressor.
17. The method of claim 12 , wherein the cryogenic fluid comprises at least one of liquid nitrogen, liquid air and liquid natural gas.
18. The device or method of claim 15 further comprising using a second compressor to compress the second portion of working fluid after it has passed through the evaporator a first time and directing the second portion of working fluid back through the evaporator a second time before it is compressed by the first compressor.
19. The device of claim 4 further comprising:
a third expansion turbine and a second reheater positioned between the evaporator and the first expansion turbine, and
a fourth expansion turbine and a third reheater positioned between the first reheater and the second expansion turbine
20. The device of claim 4 further comprising a second compressor for compressing the second portion of the working fluid after it has passed through the evaporator a first time and directing the second portion of the working fluid back through the evaporator a second time before the second portion of the working fluid is compressed by the first compressor.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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GB1200548.4 | 2012-01-13 | ||
GB1200548.4A GB2498382A (en) | 2012-01-13 | 2012-01-13 | Electricity generation using a cryogenic fluid |
PCT/GB2013/050037 WO2013104904A1 (en) | 2012-01-13 | 2013-01-10 | Electricity generation device and method |
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US20150000280A1 true US20150000280A1 (en) | 2015-01-01 |
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US14/371,569 Abandoned US20150000280A1 (en) | 2012-01-13 | 2013-01-10 | Electricity generation device and method |
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US (1) | US20150000280A1 (en) |
EP (1) | EP2802756B1 (en) |
JP (1) | JP5982499B2 (en) |
KR (1) | KR101705657B1 (en) |
CN (1) | CN104169542A (en) |
ES (1) | ES2762458T3 (en) |
GB (1) | GB2498382A (en) |
PL (1) | PL2802756T3 (en) |
PT (1) | PT2802756T (en) |
SG (1) | SG11201403770PA (en) |
WO (1) | WO2013104904A1 (en) |
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WO2020014238A1 (en) * | 2018-07-11 | 2020-01-16 | Resolute Waste Energy Solutions | Nested loop supercritical co2 waste heat recovery system |
US11187114B2 (en) * | 2016-09-09 | 2021-11-30 | Eric Dupont | Mechanical system for generating mechanical energy from liquid nitrogen, and corresponding method |
US11287182B2 (en) * | 2017-11-27 | 2022-03-29 | Siemens Energy Global GmbH & Co. KG | Method for power generation during the regasification of a fluid by supercritical expansion |
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CN103527274A (en) * | 2013-10-23 | 2014-01-22 | 肖波 | Cold energy liquid air (liquid nitrogen) engine system |
CN104806882B (en) * | 2015-04-09 | 2018-01-16 | 华南理工大学 | A kind of temperature, pressure balancer being applied in natural gas expansion process and its application |
EP3133268B1 (en) * | 2015-08-21 | 2020-09-30 | Ansaldo Energia IP UK Limited | Method for operating a power plant |
KR102127960B1 (en) * | 2018-10-31 | 2020-07-09 | 고등기술연구원연구조합 | System and Method for Liquid Air Evaporation with Industrial Plant |
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Also Published As
Publication number | Publication date |
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GB201200548D0 (en) | 2012-02-29 |
SG11201403770PA (en) | 2014-07-30 |
JP2015504132A (en) | 2015-02-05 |
ES2762458T3 (en) | 2020-05-25 |
PT2802756T (en) | 2019-12-13 |
EP2802756A1 (en) | 2014-11-19 |
KR101705657B1 (en) | 2017-02-10 |
PL2802756T3 (en) | 2020-03-31 |
EP2802756B1 (en) | 2019-10-09 |
CN104169542A (en) | 2014-11-26 |
GB2498382A (en) | 2013-07-17 |
JP5982499B2 (en) | 2016-08-31 |
KR20140134269A (en) | 2014-11-21 |
WO2013104904A1 (en) | 2013-07-18 |
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