Classifications

• • 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
  • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
  • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
  • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
  • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02K—DYNAMO-ELECTRIC MACHINES
  • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
  • H02K7/18—Structural association of electric generators with mechanical driving motors, e.g. with turbines
  • H02K7/1807—Rotary generators
  • H02K7/1823—Rotary generators structurally associated with turbines or similar engines
• • 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
  • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
  • F01K23/18—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids characterised by adaptation for specific use
• • 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
  • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, 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
  • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
  • F02C3/04—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor
• • 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
  • F02C6/16—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads for storing compressed air
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
  • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
  • F25J1/0012—Primary atmospheric gases, e.g. air
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
  • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
  • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
  • F25J1/0035—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work
  • F25J1/0037—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work of a return stream
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
  • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
  • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
  • F25J1/004—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by flash gas recovery
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
  • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
  • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
  • F25J1/0045—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by vaporising a liquid return stream
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
  • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
  • F25J1/0201—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using only internal refrigeration means, i.e. without external refrigeration
  • F25J1/0202—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using only internal refrigeration means, i.e. without external refrigeration in a quasi-closed internal refrigeration loop
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
  • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
  • F25J1/0203—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a single-component refrigerant [SCR] fluid in a closed vapor compression cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
  • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
  • F25J1/0228—Coupling of the liquefaction unit to other units or processes, so-called integrated processes
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
  • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
  • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
  • F25J1/0244—Operation; Control and regulation; Instrumentation
  • F25J1/0245—Different modes, i.e. 'runs', of operation; Process control
  • F25J1/0251—Intermittent or alternating process, so-called batch process, e.g. "peak-shaving"
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
  • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
  • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
  • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
  • F25J1/0262—Details of the cold heat exchange system
  • F25J1/0264—Arrangement of heat exchanger cores in parallel with different functions, e.g. different cooling streams
• • 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
  • F05D2220/30—Application in turbines
  • F05D2220/31—Application in turbines in steam turbines
• • 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
  • F05D2220/30—Application in turbines
  • F05D2220/32—Application in turbines in gas turbines
• • 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
  • F05D2240/00—Components
  • F05D2240/35—Combustors or associated equipment
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J2205/00—Processes or apparatus using other separation and/or other processing means
  • F25J2205/24—Processes or apparatus using other separation and/or other processing means using regenerators, cold accumulators or reversible heat exchangers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J2210/00—Processes characterised by the type or other details of the feed stream
  • F25J2210/06—Splitting of the feed stream, e.g. for treating or cooling in different ways
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J2235/00—Processes or apparatus involving steps for increasing the pressure or for conveying of liquid process streams
  • F25J2235/02—Processes or apparatus involving steps for increasing the pressure or for conveying of liquid process streams using a pump in general or hydrostatic pressure increase
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J2240/00—Processes or apparatus involving steps for expanding of process streams
  • F25J2240/80—Hot exhaust gas turbine combustion engine
  • F25J2240/82—Hot exhaust gas turbine combustion engine with waste heat recovery, e.g. in a combined cycle, i.e. for generating steam used in a Rankine cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
  • F25J2240/00—Processes or apparatus involving steps for expanding of process streams
  • F25J2240/90—Hot gas waste turbine of an indirect heated gas for power generation
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
  • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids

Definitions

• the invention relates to a method according to the preamble of claim 1.
• the "main air compressor” may be decided or in addition to the here "main compressed air flow” air volume for the combustion unit and the
• Air compression system which includes the main air compressor, serve mainly to supply the combustion unit and the cold storage system. Under “the main compressed air flow, in the main air compressor on the first
• Compressed air level is compressed, "here is in any case to understand the sum of the proportions of compressed in the main air compressor air, which ultimately in the
• Combustion unit or be introduced into the cold storage system.
• the main air compressor may have one or more serially connected stages and be formed single or multi-stranded.
• Main air compressors and booster can have a common drive or driven by separate shafts.
• pressure level is used here in order to be able to ignore unavoidable and unintentional pressure differences, such as, for example, the natural pressure losses of the appliances flown through.
• a pressure level includes, for example, one
• Pressure level may be equal to, lower, or higher than the first pressure level. As a rule, it is at least 5 bar, preferably more than 8 bar higher than the first pressure level.
• the refrigeration, storage and recovery can be carried out in the invention by any suitable method.
• the cold storage system means for generating cold from compressed air (refrigeration) and the means
• CONFIRMATION COPY for generating a compressed air flow at the second pressure level
• Cold recovery are formed by separate apparatus; however, preferably at least partially the same apparatuses are used for refrigeration and recovery.
• the cold storage can be done in any known manner, for example in the form of a cold or cryogenic fluid or in the form of a solid cold storage, such as a regenerator.
• a storage fluid can be cooled only by the transfer of sensible heat or formed by liquefaction of a gas.
• combinations of all possibilities for refrigeration, storage and recovery are possible.
• cold storage system does not include systems which serve another main purpose and incidentally act as a cold storage, such as air separation plants, which are operated variable depending on the price of electricity and thereby buffer liquid products.
• the invention is therefore based on the object to reduce the expenditure on equipment for the combined system.
• Combustion air can be made smaller and more cost-effective or at best completely omitted.
• the first and second pressure levels are different.
• the "first pressure level” is between 4 and 10 bar, preferably between 4 and 8 bar and the “second pressure level” above 10 bar, preferably between 12 and 70 bar.
• This pressure difference is generated in particular by a first secondary compressor for the recompression of compressed in the main air compressor compressed air to the second pressure level.
• the first after-compressor is part of the "air compression system". In normal operation, all the air is introduced from the main air compressor in the first booster.
• the energy storage capacity of the system is increased by the use of at least one cold compressor, while in the known system, although a cold compressor is used, but this is only used in the loading mode.
• This cold compressor serves, in the second mode of operation, at least part of the first compressed air flow in the cold storage system to the second
• Pressure level (and in some embodiments beyond the second pressure level to a higher pressure level) are brought.
• warm gas compressor the heat of compression in one
• cold compressor is used for this purpose.
• a "cold compressor” is understood here to mean a gas compressor whose inlet temperature is below 240 K.
• the cold storage system of the invention may also comprise two or more cold compressors.
• the first compressed air flow can be formed only by a first part of the main compressed air flow generated in the main air compressor.
• the remainder - or a part of it - can directly (that is on the
• combustion turbine which is not coupled with an air compressor.
• a "combustion turbine” is understood here to mean a system in which, similar to a conventional gas turbine system, combustion exhaust gas in a turbine
• Expander is working to relax in order to generate electrical energy in a generator coupled to the turbine.
• gas turbine expander and gas turbine compressor for compressing the combustion air is a
• combustion turbine is not mechanically coupled to a compressor, but transfers the recovered mechanical energy completely or practically completely to a generator for generating electrical energy.
• Combustion turbine generated by work-performing expansion of the combustion gas mechanical energy is thus completely or substantially completely converted into electrical energy within the efficiency of the machine.
• Main air compressor for the cold storage system also completely the function of compression of the combustion air for the power plant.
• the cold storage system more precisely in the means for generating refrigeration from compressed air, at least in the first mode of operation (charging operation), cold is obtained by working expansion of air.
• the first partial flow At least a part (the “first partial flow") of the first compressed air flow is introduced into an air turbine. This drives a “second booster” for at least a part (the "second
• the second partial flow preferably comprises the first partial flow, that is to say the secondary compressor increases the inlet pressure of the air turbine and thus the cooling power generated there without additional energy being required from outside
• the cold storage system may have two turbine-booster combinations and additionally an externally driven booster; the latter can also be designed as a cycle compressor.
• An example of this is a cold storage system in which, in the first mode of operation, only a single compressor is running for air driven by an air turbine.
• the cold storage system of the invention may in particular be designed as a liquid air storage system according to claim 5.
• the "means for generating refrigeration from compressed air” are designed as air liquefiers, the "means for generating a
• the liquid air can be stored in the invention without pressure (ie under ambient pressure). Alternatively, it is stored at an elevated pressure, preferably in the range of 3 to 25 bar, for example 4, 6, 8 or 16 bar.
• the air evaporator may comprise an air turbine in which in the second mode of operation at least part of the (pseudo) vaporized air is released from a fourth pressure level to the second pressure level, the air turbine in particular to an electric generator or to a cold engine is mechanically coupled to increase the pressure of an air flow in the second mode of operation.
• the air turbine in particular to an electric generator or to a cold engine is mechanically coupled to increase the pressure of an air flow in the second mode of operation.
• Air turbines are used.
• the liquid air is brought before its (pseudo) evaporation to a fourth pressure level, which is more than 42 bar, preferably more than 63 bar.
• a fourth pressure level which is more than 42 bar, preferably more than 63 bar.
• An upper limit for the fourth pressure level is formed by the operating parameters of the air turbine.
• the air turbine can also be designed as a hot turbine whose
• Inlet temperature is above the ambient temperature (hot gas expander). It is also possible to provide a plurality of such air turbines in the air evaporator, for example for each cold machine.
• cold machine is meant here a machine for increasing the pressure of an air stream whose inlet temperature is well below the ambient temperature, in particular below 240 K. This may be a cold compressor for gaseous air or a pump for liquid air.
• a liquid storage fluid is cooled in the cold storage system in the first mode and introduced into a cold tank and taken in the second mode liquid storage fluid from the cold tank and warmed. It makes sense to store the warmed liquid storage fluid in a second, warm tank. In this case, only sensible heat is transferred to or from the storage fluid, that is to say it undergoes no phase transition either during cooling or during heating.
• the cooling and heating of the storage fluid is between two
• the first, lower temperature level T1 can be in the range of 78 to 120 K, preferably 78 to 100 K, the second, higher temperature level T2 in the range of 130 to 200 K, preferably
• the "first compressed air flow” is not liquefied, but only cooled. This cold is not stored as cryogenic liquid air, but in a solid, the storage mass of the regenerator.
• the invention also relates to a device according to claim 11.
• the device according to the invention can be supplemented by device features which correspond to the features of the dependent method claims.
• FIG. 1 shows the basic principle of the invention with at least three - here five -
• Figure 2 shows a first embodiment of the invention, wherein the
• Vaporization system is formed
• Figures 13 to 17 show three alternative embodiments of a power plant for use in each of the preceding embodiments, and Figure 18 shows an alternative embodiment of an air evaporator.
• Air volumes for other purposes eg instrument air.
• first pressure level is in the embodiments at about 5 bar, the "second pressure level” at about 17 bar.
• the roughly schematically illustrated in the figure 1 combined system according to the invention comprises an air compression system 100, a cold storage system 200 and a power plant 300.
• the air compression system 100 comprises a main air compressor 2 and a first after-compressor 10, the cold storage system 200 means 201 for Generation of refrigeration from compressed air, means 202 for storing thereby produced cold and means 203 for generating a compressed air flow at a second, higher pressure level.
• the power plant 300 has a combustion unit and a
• Combustion turbine which is connected to an electric generator (not shown in detail in Figure 1).
• FIG. 1 shows three modes of operation:
• A a "first operating mode” (pure charging operation)
• a ' a modified "first mode" (charging mode combined with
• the first booster 10 In the first mode of operation A, the first booster 10, the power plant 300 and the means 203 for generating a compressed air flow are out of operation. It will
• Atmospheric air 99 is compressed in the main air compressor 2 to the first pressure level.
• the "main compressed air flow” 101 is completely introduced as a "first compressed air flow” in the means 201 for generating cold air from compressed air, wherein cold generated there is stored in the cold storage means 202.
• the first after-compressor 10 and the means 201 for producing refrigeration from compressed air are out of operation. It is exclusively the
• Cold storage 202 discharged. Atmospheric air 99 is compressed in the main air compressor 2 to the first pressure level.
• the "main compressed air flow” 101 is completely introduced as “first compressed air flow” into the means 203 for generating a compressed air flow by means of the cold stored in the cold storage 202.
• the generated thereby "third compressed air flow” 204 is located on the second
• the cold storage system 200 is completely out of service. (Of course, the cold stored in the cold storage 202 remains cold until natural losses are obtained, but the cold storage is neither charged nor deliberately discharged.) Only the power plant is operated, the main air compressor 2, but continues to run. The entire main compressed air stream 101 is recompressed as "second compressed air stream" 103 in the first after-compressor 10 to the second pressure level and used in the power plant 300 as combustion air 104. The air flow 104 is in this
• the means 203 for generating a compressed air flow are out of operation.
• the main compressed air stream 101 is split between the cold storage system 200 (first compressed air flow 102) and the power plant (second compressed air flow 103).
• first compressed air flow 102 first compressed air flow 102
• second compressed air flow 103 second compressed air flow 103
• any desired portion of the main compressed air flow 101 can be introduced into the cold storage system 200 as the first compressed air flow 102. For a long time will be
• the main compressed air stream 101 is also divided between the cold storage system 200 (first compressed air stream 102 - here after 203) and the power plant (second compressed air stream 103).
• the cold storage 202 is discharged at the same time and the power plant 300 charged with additional combustion air 104, which (except for the re-compression 10) comes directly to the main air compressor 2.
• any desired portion of the main compressed air flow 101 can be introduced into the cold storage system 200 as the first compressed air flow 102.
• 50 to 100% are introduced into the cold storage system. Values outside of this numeric range are usually only briefly during the transition to normal operation C or pure
• Unloading operation B reached.
• Apparatus groups are formed. Preferably, however, one, several or all apparatus parts of the means 201 for generating cold from compressed air are simultaneously
• Component of the means 203 for generating a compressed air stream are then used both in the first and in the second mode of operation. This further reduces the expenditure on equipment.
• FIG. 2 shows a first embodiment of the invention, in which the
• Cold storage system 200 as air liquefaction and evaporation system
• the air compression system 100 has a filter 1, a pre-cooler 3 and an aftercooler 98 for the after-compressor 10.
• Main air compressor 2 and after-compressor 10 are each formed single-stranded.
• the main air compressor 2 has three to four stages, the after-compressor 10 one to three stages.
• a cleaning device 4 is installed, which in particular removes water and carbon dioxide, before this air flow enters the cold part of the cold storage system 200.
• Embodiment designed as it is common in air liquefaction technology and in cryogenic air separation plants.
• the "means for generating cold from compressed air” are designed as Heilvermillioner 201, the “means for storing thereby generated cold” as a liquid air tank 202 and the "means for generating a
• air liquefier 201 and air evaporator 203 are completely separate.
• the main compressed air stream 101 is supplied here completely as the first compressed air stream 102 through the cleaning device 4 and via line 102a to the air liquefier 201.
• a first part 210 (which can simultaneously form the "first partial flow” and the "second partial flow” in the sense of the claims) is recompressed in a second after-compressor 5a with aftercooler 5b to a pressure of 6 to 10 bar, in one
• Secondary heat exchanger 26 cooled and relaxed in a first air turbine 5 to just above atmospheric pressure.
• the first air turbine 5 is mechanically coupled to the second after-compressor 5a.
• the working expanded air is warmed in the cold part of a main heat exchanger 21 and further in the secondary heat exchanger 26 to about ambient temperature and finally blown off via line 211 into the atmosphere or used for drying purposes.
• the remainder 212 of the cleaned first compressed air flow 102a is further compressed in an externally driven by an electric motor cycle compressor 11 with aftercooler 1 1 b and in a third booster 12a with aftercooler 12b to an even higher third pressure level of 30 to 60 and finally to a first part in a second air turbine 12, which drives the third boost compressor 12a,
• Embodiment is under pressure (second pressure level). Flash gas 213 from the separator 23 is warmed in the main heat exchanger 21 to approximately ambient temperature and returned to the inlet of the Kreisiaufverêtrs 1. A small portion of the supercooled liquid air is further expanded in a second throttle valve 25 to about atmospheric pressure, warmed in the subcooler 24 and mixed with the exhaust gas of the first air turbine 5.
• the power plant 300 and the air evaporator 203 the power plant receives its combustion air exclusively from the air evaporator.
• the main compressed air stream 101 is here completely supplied as the first compressed air flow 102 through the cleaning device 4 and via line 102a the air evaporator 203 and provides the heat for the evaporation and heating of the stored liquid air and also forms itself a part of the combustion air.
• a first part of the purified first compressed air stream 102a is cooled in a further secondary heat exchanger 29 and a further main heat exchanger 28, without being liquefied, in a first cold compressor 31 to the second
• Ambient temperature warmed and fed into the combustion air line 204 A second part is cooled in the main heat exchanger 28 to an intermediate temperature (in the example 150 K) and brought to the second pressure level in a second cold compressor 32 and fed into the combustion air line 204.
• an intermediate temperature in the example 150 K
• Liquid air is removed from the liquid air tank 202, brought in a pump 27 to the second pressure level and the evaporation and heating in
• the power plant contains a combustion turbine, which is a combustion chamber
• Combustion unit 42 an expander 44 for combustion gas 303 and a generator 43 for generating electrical energy, but no compressor for combustion air. Rather, all the mechanical energy in that
• Expander 44 obtained is transmitted via a mechanical coupling to the generator 43.
• the combustion air 204 is in a heater 41 against relaxed
• Combustion gas 304 warmed up and enters a combustion chamber (combustion unit) 42, in which a fuel (fuel) 302 is burned, which is formed in particular by natural gas.
• the hot combustion gas 303 is depressurized in the combustion turbine to approximately atmospheric pressure. Its waste heat is used in the heater 41; a steam generation is not provided.
• the cold storage system 200 is out of operation, the liquid air tank 202 its
• the combustion air for the power plant 300 comes here exclusively via the line 104 from the air compression system 100. There, the entire main pressure stream 101 is recompressed in the first booster 10 to the second pressure level.
• Recirculation Compressors 1 can work in the same or different ways
• the two secondary compressors 5a and 12a are driven by air turbines (ie indirectly by the main air compressor 2 and its drive), so do not require any additional energy import.
• Circulation compressor 11 more energy must be plugged from the outside.
• Plate heat exchanger blocks realized.
• the two pairs can each be realized by an integrated main heat exchanger, which combines both functions in itself.
• FIGS. 3 to 5 three further embodiments of an air evaporator are shown, each of which can replace the air evaporator in FIG. Figure 3 shows an embodiment of the air evaporator that does not require an external power supply that goes beyond the main air compressor.
• the cold machines 27, 31, 32 are each driven by an air turbine 27t, 31t and 32t.
• the liquid air is brought in the pump 27 to a fourth pressure level, which is significantly higher than the second pressure level and in this and the following embodiments at 65 bar.
• the air generated particularly high pressure is distributed after heating in the main heat exchanger 28 on the three parallel turbines 27t, 31t, 32t and there expanded to the second pressure level work.
• the work-relaxing air becomes again
• Air evaporator of Figures 2 and 3 possible by, for example, only one or two of the cold machines 27, 31 and 32 of Figure 2 are equipped with turbine drive according to Figure 3.
• the liquid air in the pump is also brought to the above-mentioned fourth pressure level.
• the air generated particularly high pressure is released after heating in the main heat exchanger 28 to approximately ambient temperature in the turbine 204 to the second pressure level work.
• the working expanded air is warmed in the main heat exchanger 28 and finally fed into the combustion air line 204.
• the air turbine 204 is coupled in Figure 4 to a generator which provides additional electrical energy in the second mode of operation (discharge operation).
• the cold machines 27, 31 and 32 consume energy analogous to Figure 2.
• Figure 5 largely corresponds to Figure 4, but the air is on the fourth
• the air turbine 240 thus has a lower inlet temperature (and also a lower outlet temperature) than in FIG.
• a system can be used as a cold storage system, in which air liquefaction and evaporation of air is carried out at least partially in the same apparatus.
• a system is, for example, in the earlier patent application EP 12004833.5 and the corresponding thereto
• the "means 201 for generating refrigeration from compressed air” have an air turbine 13t and an after-compressor 13a with aftercooler 13b.
• the "means 203 for generating a compressed air flow at the second pressure level” include an externally driven booster 31.
• a warm heat exchanger 21 and a cold heat exchanger 26 are part of both “means” 201, 203.
• the cold storage 202 is in contrast to the figures 2 to 5 not formed as a liquid air tank, but as a pair of
• Liquid tanks 73/74 for storing a liquid storage fluid at two different temperature levels T1 and T2 with T2> T1.
• first mode of operation storage fluid is cooled from the warm tank 73 to about T1 and introduced into the cold tank 74.
• the storage fluid used in the example is liquid propane, T1 is approximately 90 K, T2 is approximately 150 K.
• the (sensible) cold required for this is generated in the air turbine 13t.
• the first Compressed-air stream 102 is first recompressed in the after-compressor 13a with aftercooler 13b from the second to the third pressure level, then cooled in the warm heat exchanger 21 to a temperature of for example 155 K and expanded in the air turbine 13t to approximately atmospheric pressure.
• the air enters at a temperature of about 85 K in the cold heat exchanger 26 and is heated there and further in the warm heat exchanger 21 to about ambient temperature.
• Main compressed air stream 101 sent as the first compressed air stream 102 through the cleaning device 4 and enters as a purified first compressed air flow 102a in the
• Heat exchanger 21 warmed and finally introduced as a "third compressed air flow" in the combustion air line 204.
• a small part 206 may optionally take a detour via a regeneration gas heater 6 and the cleaning device 4, where it is used as a regeneration gas.
• storage fluid is conveyed from the cold tank 74 to the cold heat exchanger 26 by means of the pump 71, where it is warmed from approximately T1 to approximately T2 and finally introduced into the warm tank 73.
• the "third compressed air flow” forms the entire combustion air for the power plant 300 in the operating case B.
• the system of Figure 6 may also be in the modified first and second
• Operation A 'and B' of Figure 1 are driven.
• the cold storage system 200 is out of order and the liquid level in the tanks 73, 74 remains constant.
• the combustion air for the power plant 300 comes here exclusively via the line 104 from the air compression system 100. There, the entire main pressure stream 101 is recompressed in the first booster 10 to the second pressure level.
• FIG. 7 shows a combined system which differs only slightly from that of FIG. Only the pure charging mode (A) is shown here.
• the first after-compressor 10 is used to produce the first compressed air stream 102.
• the cold storage is virtually charged by the booster.
• FIG. 8 likewise differs only in the charging mode (A) from FIGS. 6 and 7, specifically in that both the main air compressor 2 and the first one
• After-compressor 10 are used to generate the first compressed air stream 102.
• the refrigeration cycle of both compressors 2, 10 is operated.
• the turbines have equal inlet and outlet temperatures.
• FIG. 9 differs from FIG. 8 in that the two turbine / compressor combinations 12, 13 are also connected in parallel on the compressor side.
• Figure 10 largely corresponds to Figure 6.
• the cold storage 200 is designed as a regenerator cold storage.
• the storage mass of the regenerator 28 is cooled in the first mode (A) and reheated in the second mode (B). Refrigeration and generation of the third compressed air flow work analogously to FIG. 6. Normal operation does not differ from FIG. 6 (C).
• FIG. 10 Analogous to the compressor configuration in FIGS. 7, 8 and 9, the embodiment of FIG. 10 can also be modified in that in the first embodiment Operating mode, only the first compressor 10 or both the main air compressor and the secondary compressor 2, the "first compressed air flow" generate in the first embodiment Operating mode, only the first compressor 10 or both the main air compressor and the secondary compressor 2, the "first compressed air flow" generate in the first embodiment Operating mode, only the first compressor 10 or both the main air compressor and the secondary compressor 2, the "first compressed air flow" generate in the
• Heat exchanger 26 While the liquid is pumped from one container 73/74 in the other 74/73, the vapor or the gas from the gas space above the liquid from the receiver container 74/73 in the
• Source container 73/74 passed.
• the gas space of the two containers 73/74 can be
• a non-condensable gas such as nitrogen
• FIG. 10 has outer container 120, a heat insulation 121 and an inner container 122 which is filled with a porous mass 123 which has a high heat capacity. In all embodiments shown so far, one of the alternatives
• Embodiments of the power plant 300 are used, as shown in Figures 13 to 18.
• HSRG heat recovery steam generator - sometimes also referred to as a waste heat boiler
• the source of this further heat can be arbitrary, for example, residual heat from another process, heat from one
• Heat storage or a solar system This can be at the same
• FIG. 15 shows three variants of a system with two combustion turbines 44a, 44b, which are both coupled to the generator 43.
• the recuperator 41 is used simultaneously for the heating of regeneration gas 206 for the cleaning device 4.
• On the left is shown a variant with a combined heat exchanger 41, on the right another, in which only two-stream high-temperature heat exchangers 41, 41a and 41b are used.
• Figure 18 shows a variant of the invention in the second mode of operation, which may be applied to the systems of Figures 2 to 5.
• the liquid air is brought in the pump 27 to a fourth pressure level of 40 to 200 bar, heated in the heater 41 by indirect heat exchange with combustion gas to a temperature of for example 600 ° C and by means of a work-performing relaxation in a hot air turbine 1800 to the second Pressure level of the combustion process brought, whereby additional electrical energy is generated.

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• 2014
  • 2014-03-21 US US14/770,836 patent/US9608498B2/en not_active Expired - Fee Related
  • 2014-03-21 WO PCT/EP2014/000776 patent/WO2014146796A1/de active Application Filing
  • 2014-03-21 CN CN201480016703.1A patent/CN105074141B/zh not_active Expired - Fee Related
  • 2014-03-21 EP EP14716236.6A patent/EP2976511A1/de not_active Withdrawn

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