CN113339091A - Brayton-kalina circulating energy storage power supply method and device - Google Patents

Brayton-kalina circulating energy storage power supply method and device Download PDF

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CN113339091A
CN113339091A CN202110804727.5A CN202110804727A CN113339091A CN 113339091 A CN113339091 A CN 113339091A CN 202110804727 A CN202110804727 A CN 202110804727A CN 113339091 A CN113339091 A CN 113339091A
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heat
temperature
energy storage
working medium
power supply
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CN113339091B (en
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王建强
沈佳杰
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Shanghai Institute of Applied Physics of CAS
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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
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/04—Using steam or condensate extracted or exhausted from steam engine plant for specific purposes other than heating
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • 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
    • Y02E60/14—Thermal energy storage
    • 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
    • Y02E70/00—Other energy conversion or management systems reducing GHG emissions
    • Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin
    • 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
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier

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Abstract

The invention provides a Brayton-kalina circulating energy storage power supply method which comprises an energy storage mode and a power supply mode. In the energy storage mode, the normal-temperature working medium is subjected to adiabatic compression by the compressor, and an isobaric heat release process is performed by the main heat storage system; the working medium discharges heat to the waste heat boiler, enters a turbine for adiabatic expansion to do work outwards, and then performs an isobaric heat absorption process through a cold accumulation system; the waste heat boiler and the steam turbine form an ammonia water circulation loop; the power mode is its reverse cycle. The invention also provides a corresponding energy storage and power supply device. The method utilizes the kalina cycle to recycle the low-temperature waste heat through the method and the device of the reversible heat pump and the Brayton cycle, further improves the energy storage efficiency, solves the problems of wind and light abandonment in photovoltaic power generation and wind power generation, solves the problem of large temperature difference between day and night in western areas while storing energy and supplying power, and provides cold air for companies or factories during the day and provides hot air for communities while supplying power at night.

Description

Brayton-kalina circulating energy storage power supply method and device
Technical Field
The invention relates to an energy storage method and a device thereof, in particular to a Brayton-kalina circulating energy storage power supply and heat supply method and a device thereof.
Background
The green energy represented by solar energy, wind energy and hydraulic potential energy has the advantages of environmental protection and inexhaustibility, however, the green energy is generally influenced by natural conditions such as weather, seasons and sunlight, and is difficult to provide stable energy output, so that the power matched with a power grid is difficult to output. Therefore, a certain energy storage technology is adopted, and the time is exchanged by the space, which is a better solution. Physical energy storage represented by fused salt energy storage has the characteristics of low cost, high efficiency, simple structure and the like. At present, heat is stored mainly in an electric heating mode or by electrically heating a heat-conducting medium. But has a disadvantage in that the conversion efficiency between heat storage and power generation is still not ideal.
The prior granted patent of the applicant (heat pump type energy storage power supply and heat supply method and device ZL201711402735.7) discloses a heat pump type energy storage power supply and heat supply method and device, wherein a Brayton cycle which is reversible mutually is used as an energy storage and power generation principle, energy is stored in a reverse Brayton cycle, and power is generated in a Brayton cycle. Wherein the energy is stored through the heat storage of molten salt and the cold storage of antifreeze; the cold accumulation medium reduces the temperature of the inlet gas of the compressor in the power generation mode, and the heat accumulation medium improves the temperature of the inlet gas of the turbine so as to achieve the purposes of energy storage and power generation. However, the actual energy storage efficiency of the energy storage system is about 40% -70%, and a large amount of low-temperature waste heat is discharged according to energy conservation.
Disclosure of Invention
The invention aims to provide a high-efficiency Brayton-Carlina circulating energy storage and power supply method and device, so as to overcome the defect of low efficiency of the traditional electric heating heat storage medium energy storage mode and solve the problems of wind and light abandon in photovoltaic power generation and wind power generation.
The principle that the Carnot cycle and the reverse Carnot cycle are mutually reversible in thermodynamics is considered, the heat of the low-temperature heat source is transferred to the high-temperature heat source through reverse Carnot cycle working to realize energy storage, and then the heat of the high-temperature heat source is transferred to the low-temperature heat source to do work to the outside to realize energy release and power generation. However, in reality, the physical processes of the carnot cycle and the reverse carnot cycle are difficult to realize, so the invention utilizes the reverse brayton cycle for energy storage and the positive brayton cycle for power generation, and because the reverse brayton cycle and the positive brayton cycle are mutually reversible under an ideal condition, the conversion efficiency of the power generation after theoretical energy storage is generally superior to the traditional modes of directly electrically heating or electrically heating a heat-conducting medium and the like. The energy storage mode has the characteristic of low cost, the cost of the molten salt is very low, the cost of the stainless steel container is also low, and the working medium can be air; the electric energy can be stored and simultaneously the heating air and the cold air can be supplied.
The invention utilizes the kalina circulating system to recycle the low-temperature waste heat. Kalina cyclic utilization aqueous ammonia solvent is as working medium, and the aqueous ammonia is because boiling point and concentration have a negative correlation, and aqueous ammonia concentration is higher, and the boiling point is lower, and the boiling point of pure ammonia is 33.34 degrees centigrade below, and along with the reduction of aqueous ammonia concentration, the boiling point will also improve, therefore the aqueous ammonia is as working medium, can match exhaust-heat boiler's temperature better through adjustment concentration. The ammonia water can be decomposed into rich ammonia steam and poor ammonia water solution after being heated, the rich ammonia steam has a lower boiling point, the steam turbine can have a lower outlet temperature, meanwhile, the poor ammonia water solution obtained through separation can be used for reheating the ammonia gas, and meanwhile, the boiling point is improved, so that the ammonia gas is easy to condense.
In order to achieve the above object, the present invention provides a brayton-kalina cycle type energy storage and power supply method, which comprises the following modes:
(1) an energy storage mode: after the working medium at normal temperature is subjected to adiabatic compression by a compressor, an isobaric heat release process is carried out through a main heat storage system; the working medium discharges heat to the waste heat boiler, enters a turbine for adiabatic expansion to do work outwards, then carries out an isobaric heat absorption process through a cold accumulation system, and is recycled or released to the outside;
(2) a power supply mode: the normal temperature working medium is subjected to isobaric heat release through a cold accumulation system, then is subjected to adiabatic compression through a compressor, is subjected to isobaric heat absorption through a main heat accumulation system, then enters a turbine for adiabatic expansion to apply work to the outside, and then is circulated or released to the outside after the heat is discharged to a waste heat boiler; the net output work is used to power the process;
for the energy storage mode and the power supply mode, the basic ammonia solution enters a waste heat boiler to absorb heat discharged from the working medium to the waste heat boiler, so that the basic ammonia solution is converted into an ammonia water gas-liquid mixture through isobaric heat absorption and enters a separator; the method comprises the steps of separating a gas-liquid two-phase mixture into ammonia-rich steam and an ammonia-poor solution by using a separator, wherein the ammonia-rich steam enters a steam turbine for adiabatic expansion to do work outwards, the ammonia-poor solution enters an ammonia circulating heat exchanger to preheat a basic ammonia solution before entering an evaporator, the ammonia-poor solution is throttled and depressurized by a throttle valve after being discharged, then is mixed with exhaust steam discharged from the steam turbine in a mixer to form a basic ammonia solution, enters a condenser for isobaric heat release, is boosted by a working medium pump, then enters the ammonia circulating heat exchanger to be preheated by the ammonia-poor solution, and then the basic ammonia solution returns to a waste heat boiler to absorb heat and repeats the process.
The working medium comprises air, argon, nitrogen, helium or carbon dioxide.
The working medium exchanges heat with the main heat storage system in the energy storage mode, so that the heat storage medium at the position of the low-temperature point in the main heat storage system exchanges heat with the low-temperature point of the heat storage medium
Figure BDA0003166071650000021
Raised to a high temperature point
Figure BDA0003166071650000022
And transferring to the position of a high-temperature point of the main heat storage system; and exchanges heat with the cold accumulation system, so that the heat accumulation medium at the position of the high-temperature point in the cold accumulation system is subjected to normal temperature T from the airairDown to its low temperature point T0And transferring to the position of the low-temperature point of the cold accumulation system; the working medium exchanges heat with the cold accumulation system in the power supply mode, so that the heat accumulation medium at the position of the low-temperature point in the cold accumulation system is subjected to heat exchange from the low-temperature point T of the heat accumulation medium0Is lifted and transferred to the position of a high-temperature point of the cold accumulation system; and exchanges heat with the main heat storage system to ensure that the heat storage medium at the position of the high-temperature point in the main heat storage system is heated from the high-temperature point
Figure BDA0003166071650000031
Lowered to the low temperature point
Figure BDA0003166071650000032
And transferred to the location of the low temperature point of the primary thermal storage system.
In the energy storage mode, before the working medium enters the compressor, the regenerative heat storage system performs isobaric heat absorption, so that the heat storage medium at the position of a high-temperature point in the regenerative heat storage system is enabled to be at the high-temperature point T1Down to the low temperature point Tair+ delta T and transferring to the position of the low temperature point of the regenerative heat storage system; in the power supply mode, after the working medium passes through the waste heat boiler, the regenerative thermal storage system performs isobaric heat release, so that the thermal storage medium at the position of a high-temperature point in the regenerative thermal storage system is enabled to be subjected to constant-pressure heat release from a low-temperature point T of the thermal storage mediumair+ Δ T rise to the high temperature point T1And transferring to the position of a high-temperature point of the regenerative heat storage system 7; and delta T is the heat exchange temperature difference.
On the other hand, the invention provides a Brayton-kalina circulating energy storage power supply device which is characterized in that the Brayton-kalina circulating energy storage power supply device is based on the Brayton-kalina circulating energy storage power supply method; corresponding to the energy storage mode, the system comprises an air inlet device, a compressor, a main heat exchanger, a waste heat boiler, a turbine, a cold accumulation heat exchanger and an air outlet device which are sequentially connected in series along the direction of a working medium, wherein the main heat exchanger is connected with a main heat accumulation system; corresponding to the power supply mode, the system comprises an air inlet device, a cold accumulation heat exchanger, a compressor, a main heat exchanger, a turbine, a waste heat boiler and an air outlet device which are sequentially connected in series along the direction of a working medium, wherein the cold accumulation heat exchanger is connected with a cold accumulation system; corresponding to energy storage mode and power supply mode, exhaust-heat boiler, separator, steam turbine, blender, condenser, working medium pump and ammonia circulation heat exchanger establish ties in proper order and form the return circuit along the trend of aqueous ammonia mixture medium, and the separator links to each other with the steam turbine through its rich ammonia steam outlet, and the poor ammonia solution export of separator with still be equipped with between the blender along the trend of aqueous ammonia mixture medium establish ties in proper order ammonia circulation heat exchanger and choke valve.
The main heat storage system is formed by connecting more than one heat storage module in series, and each heat storage module comprises at least two heat storage medium heat preservation containers which are communicated with each other and have different internal heat storage medium temperatures or at least one heat storage medium heat preservation container which is communicated with each other and has an inclined temperature layer with the internal heat storage medium having a temperature difference gradient; and the cold accumulation system comprises at least two cold accumulation medium heat preservation containers which are mutually communicated and have different internal cold accumulation medium temperatures or at least one cold accumulation medium heat preservation container which is mutually communicated and has an inclined temperature layer with the internal cold accumulation medium having a temperature difference gradient.
Corresponding to the energy storage mode, a regenerative heat exchanger is connected in series between the air inlet device and the compressor, and the regenerative heat exchanger is connected with a regenerative heat storage system; and corresponding to the power supply mode, a regenerative heat exchanger is connected in series between the waste heat boiler and the gas outlet device, and the regenerative heat exchanger is connected with a regenerative heat storage system.
The regenerative heat storage system comprises at least two heat storage medium heat preservation containers which are communicated with each other and have different internal heat storage medium temperatures or at least one heat storage medium heat preservation container which is communicated with each other and has an inclined temperature layer with the internal heat storage medium having a temperature difference gradient.
The heat storage medium of the main heat storage system comprises a mixture of one or more of an organic heat carrier, a solution, a molten salt and a compressed gas, wherein the solution is a liquid mixture of one or more of inorganic salt or carbon-containing compound and water, the molten salt is a liquid molten substance at high temperature, the mixture of one or more of nitrate, potassium salt, chlorine salt and fluorine salt is a liquid mixture, and the organic heat carrier comprises one or more of mineral oil and synthetic heat conduction oil; and the cold accumulation medium of the cold accumulation system comprises a mixture of one or more of substances such as methanol, ethanol, glycol, glycerol, lubricating oil and the like and water.
The heat storage medium of the regenerative heat storage system comprises a mixture of one or more of an organic heat carrier, a solution, a molten salt and a compressed gas, wherein the solution is a liquid mixture of one or more of inorganic salts or carbon-containing compounds and water, the molten salt is a liquid molten substance of a mixture containing one or more of nitrates, potassium salts, chlorine salts and fluorine salts at a high temperature, and the organic heat carrier comprises one or more of mineral oil and synthetic heat conduction oil.
The Brayton-kalina circulating energy storage power supply method takes the Brayton cycle of a reversible energy storage mode and a power supply mode as the principle of energy storage and power generation, and stores energy reversely in the Brayton cycle and supplies power in the Brayton cycle; storing energy through molten salt heat storage and antifreeze liquid cold storage; the cold accumulation medium reduces the temperature of the inlet gas of the compressor in the power generation mode, and the heat accumulation medium improves the temperature of the inlet gas of the turbine so as to realize the purposes of energy storage and power generation; in addition, considering that the actual energy storage efficiency of the energy storage system only using the Brayton cycle is about 40% -70%, and a large amount of low-temperature waste heat is discharged according to energy conservation, the invention also utilizes the kalina cycle system to recycle the low-temperature waste heat, the kalina cycle utilizes the mixture of ammonia water as a working medium, and the ammonia water has negative correlation with the concentration due to the melting point, so the melting point of the ammonia water has negative feedback on the temperature, the heat absorption process can be closer to the efficient isothermal heat absorption process, and the low-temperature heat energy can be effectively recycled and used for generating electricity.
In addition, the Brayton-kalina circulating energy storage power supply method can also be provided with a regenerative heat storage system to recycle the waste heat of the waste gas at the outlet of the turbine in the Brayton cycle into the regenerative heat storage system, and in the reverse Brayton cycle, the part of waste heat is used for preheating the air entering the compressor, so that the waste heat in the power generation of the system is effectively utilized, on the other hand, the inlet temperature of the compressor is improved, the compression ratio can be effectively reduced, the difficulty in system design is reduced, and the cost of system components is reduced; meanwhile, the cold accumulation system is simplified, residual cold of turbine outlet waste gas in the reverse Brayton cycle is recovered in the cold accumulation system, the working temperature range of the Brayton cycle is wider, the influence caused by heat exchange temperature difference is reduced, and meanwhile the cold accumulation system can provide cheap cold air for communities or partial industrial facilities in summer.
Drawings
Fig. 1 is a schematic diagram of a refrigeration energy storage mode of a brayton-kalina cycle energy storage and power supply method according to a first embodiment of the invention.
Fig. 2 is a schematic diagram of a heating and power supplying mode of the brayton-kalina cycle type energy storage and power supplying method according to the first embodiment of the present invention.
Fig. 3 is a schematic structural diagram of a brayton-kalina cycle energy storage power supply apparatus according to a second embodiment of the invention in a refrigeration energy storage mode.
Fig. 4 is a schematic structural diagram of a brayton-kalina cycle energy storage power supply apparatus according to a second embodiment of the invention in a heating and power supply mode.
Fig. 5 is a schematic diagram of an energy storage residual cold recovery mode of a brayton-kalina cycle energy storage power supply method according to a third embodiment of the present invention.
Fig. 6 is a schematic diagram of a brayton-kalina cycle power supply regenerative mode of the brayton-kalina cycle energy storage power supply method according to the third embodiment of the present invention.
Fig. 7 is a schematic structural diagram of a brayton-kalina cycle energy storage and power supply apparatus according to a fourth embodiment of the invention in an energy storage residual cold recovery mode.
Fig. 8 is a schematic structural diagram of a brayton-kalina cycle energy storage power supply apparatus according to a fourth embodiment of the invention in a brayton-kalina cycle power supply regenerative mode.
Reference numerals:
1. an air intake device; 2. a regenerative heat exchanger; 3. a compressor; 4. a primary heat exchanger; 5. a turbine; 6. an air outlet device; 7. a regenerative thermal storage system; 8. a primary thermal storage system; 9. a regenerative media pump; 10. a heat storage medium pump; 11. a low temperature heat recovery tank; 12. a high temperature heat recovery tank; 13. a low temperature heat storage tank; 14. a high temperature heat storage tank; 15. a low temperature cold storage tank; 16. a cold storage tank at normal temperature; 17. a cold storage medium pump; 18. a cold storage heat exchanger; 19. a cold storage system; 20. an ammonia cycle regenerative system; 21. a waste heat boiler; 22. a separator; 23. a steam turbine; 24. an ammonia recycle heat exchanger; 25. a condenser; 26. a working medium pump; 27. a mixer; 28. a throttle valve.
Detailed Description
The preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
First embodiment Brayton-kalina circulating energy storage power supply method based on cold storage type Brayton
Fig. 1-2 are schematic diagrams of a brayton-kalina cycle energy storage and power supply method according to a first embodiment of the invention, the method including an energy storage mode and a power supply mode. In this embodiment, since the brayton-kalina cycle energy storage and power supply method is based on the cold storage type brayton, the energy storage mode is a refrigeration energy storage mode, and the power supply mode is a heating power supply mode.
Fig. 1 is a schematic diagram of a refrigeration energy storage mode of a brayton-kalina cycle energy storage power supply method. In the refrigeration energy storage mode, the air intake device 1 absorbs dry air (taking air as an example) from the outside as a working medium, the working medium is gas, the working medium at normal temperature enters the compressor 3 for adiabatic compression, the working medium is compressed into high-temperature high-pressure gas, the working medium enters the main heat exchanger 4 after coming out of the outlet of the compressor 3 to exchange heat with the main heat storage system 8 through the main heat exchanger 4, so that an isobaric heat release process is performed through the main heat storage system 8, that is, the main heat exchanger 4 transfers the heat of the high-temperature working medium at the outlet of the compressor to the main heat storage system 8, so that the temperature of the high-temperature working medium is reduced; meanwhile, the heat storage medium in the main heat storage system 8 is heated, so that the heat storage system completes heat storage and energy storage. At this time, since the isentropic efficiency of the compressor 3 and the turbine 5 is less than 1, the working medium needs to release a part of heat. The working medium discharges heat to the waste heat boiler 21, and the heat discharged by the working medium enters the waste heat boiler 21 to heat the basic ammonia solution, so that the basic ammonia solution absorbs heat in an isobaric manner to be changed into an ammonia water gas-liquid mixture and enters the separator 22. Subsequently, the gas-liquid two-phase mixture is separated into ammonia-rich vapor and ammonia-lean solution by the separator 22. Wherein the ammonia-rich steam enters the steam turbine 23 for adiabatic expansion to do work outwards; the poor ammonia solution enters the ammonia circulation heat exchanger 24 to preheat the basic ammonia solution before entering the waste heat boiler 21, the poor ammonia solution is throttled and depressurized by the throttle valve 28 after being discharged, then is mixed with the dead steam discharged from the steam turbine 23 in the mixer 27 to form the basic ammonia solution, enters the condenser 25 for isobaric heat release, is boosted by the working medium pump 26, then enters the ammonia circulation heat exchanger 24 to be preheated by the poor ammonia solution, and then the basic ammonia solution returns to the waste heat boiler 21 and repeats the processes, thus completing the circulation. After the working medium discharges heat to the waste heat boiler, the working medium is adiabatically expanded after entering the turbine 5 to do work outwards, the high-temperature and high-pressure working medium is expanded into the low-temperature and normal-pressure working medium according to a certain compression ratio, the low-temperature gas enters the cold accumulation heat exchanger 18 after coming out of the turbine outlet, and the low-temperature working medium passing through the turbine outlet is subjected to an isobaric heat absorption process through the cold accumulation system 19, namely, the heat of the cold accumulation medium in the cold accumulation system 19 is absorbed, so that the temperature of the low-temperature working medium is increased; meanwhile, the temperature of the cold accumulation medium is reduced, so that the cold accumulation system 19 finishes cold accumulation and energy storage. At this time, the working medium is circulated or released to the outside through the gas outlet means 6 as appropriate.
Fig. 2 is a schematic diagram of a heating and power supplying mode of the brayton-kalina cycle type energy storage and power supplying method according to the first embodiment of the present invention. For the heating power supply mode, as shown in fig. 2, it is just opposite to the refrigeration energy storage mode, the air intake device 1 absorbs dry air from the outside as the working medium, the working medium firstly enters the cold storage heat exchanger 18 of the antifreeze working medium to exchange heat with the cold storage system 19, so that the cold storage system 19 performs the isobaric heat release process, that is, the cold storage heat exchanger 18 absorbs the heat of the normal temperature working medium through the cold storage medium in the cold storage system 19, so that the temperature of the working medium is reduced; at the same time, the low-temperature cold storage medium in the cold storage system 19 is warmed up. Then, the working medium enters the compressor 3 for adiabatic compression, the working medium is compressed into high-temperature and high-pressure gas, the gas enters the main heat exchanger 4 after coming out of the outlet of the compressor 3 to exchange heat with the main heat storage system 8 through the main heat exchanger 4, and isobaric heat absorption is carried out through the main heat storage system 8, namely, the main heat exchanger 4 transfers the heat of the heat storage medium in the main heat storage system 8 to the working medium, so that the temperature of the working medium is increased; at the same time, the heat storage medium in the primary heat storage system 8 is cooled. Then, the working medium enters the turbine 5 for adiabatic expansion to do work outwards, the high-temperature and high-pressure working medium is expanded into the low-temperature and normal-pressure working medium, at the moment, the working medium is still much higher than the normal temperature, the discharged medium-temperature working medium enters the waste heat boiler 21 to heat the basic ammonia solution, so that the basic ammonia solution absorbs heat isobarically and is changed into an ammonia water gas-liquid mixture to enter the separator 22, the gas-liquid two-phase mixture is separated into ammonia-rich steam and ammonia-poor solution by the separator 22, the ammonia-rich steam enters the turbine 23 for adiabatic expansion to do work outwards, the ammonia-poor solution enters the ammonia circulation heat exchanger 24 to preheat the basic ammonia solution before entering the waste heat boiler 21, the ammonia-poor solution is throttled and depressurized by the throttle valve 28 after being completely heated, and then is mixed with the exhaust steam discharged from the turbine 23 into the basic ammonia solution in the mixer 27 to release heat isobarically and then enters the condenser 25, the pressure is increased by a working medium pump 26, then the ammonia enters an ammonia circulating heat exchanger 24 to be preheated by the lean ammonia solution, then the basic ammonia solution returns to the waste heat boiler 21, the process is repeated, and the circulation is completed. The working medium absorbed by the waste heat boiler circulates or is released to the outside through the air outlet device 6 according to the circumstances. In the process, net work is output to the outside, and the work is used for supplying power.
Second embodiment brayton-kalina circulating energy storage power supply device based on cold storage type brayton
We define the following notation:
Figure BDA0003166071650000071
low temperature point of the main heat storage system, unit: k;
Figure BDA0003166071650000072
high temperature point of the main heat storage system, unit: k;
T0: cold storage system low temperature point, unit: k;
Tair: air normal temperature, unit: k; the high temperature point of the cold accumulation system is also Tair；
Figure BDA0003166071650000073
Inlet temperature of waste heat boiler in refrigeration energy storage mode, unit: k;
Figure BDA0003166071650000074
turbine inlet in refrigeration energy storage modeTemperature, unit: k;
Figure BDA0003166071650000075
outlet temperature of the compressor in the refrigeration energy storage mode, unit: k;
T0c1: outlet temperature of the turbine in the refrigeration energy storage mode, unit: k;
T1c1: inlet temperature of the compressor in the refrigeration energy storage mode, unit: k;
Figure BDA0003166071650000076
outlet temperature of the compressor in heating and power supply mode, unit: k;
Figure BDA0003166071650000077
inlet temperature of the turbine in heating and power mode, unit: k;
T0c2: inlet temperature of the compressor in heating and power mode, unit: k;
T1c2: outlet temperature of the turbine in heating and power mode, unit: k;
Tout1: outlet temperature in refrigeration energy storage mode, unit: k;
Tout2: outlet temperature in heating and power mode, unit: k;
Q2c1b: the power of the heat absorbed by the working gas from the cold accumulation system in the refrigeration energy storage mode is as follows: MW;
Q1c1: the power of the heat absorbed by the working gas from the main heat storage system in the refrigeration energy storage mode is as follows, unit: MW;
Q2c2b: the power of the heat absorbed by the working gas from the cold storage system in the heat supply and power supply mode is as follows: MW;
Q1c2: the power of the heat absorbed by the working gas from the main heat storage system in the heat supply and power supply mode is as follows, unit: MW;
Wc1: power of the compressor in the refrigeration energy storage mode, unit: MW;
Wt1: power of the turbine in the refrigeration energy storage mode, unit: MW;
Wc2: power of the compressor in heating and power supply mode, unit: MW;
Wt2: power of the turbine in the heating and power supply mode, unit: MW;
Figure BDA0003166071650000081
net input power in refrigeration energy storage mode, unit: MW;
Figure BDA0003166071650000082
net output power in power supply and heat supply mode, unit: MW;
ηcp: the polytropic efficiency of the compressor;
ηtp: the polytropic efficiency of the turbine;
ηs: heat storage efficiency in a refrigeration energy storage mode;
ηw: generating efficiency in a heating and power supply mode;
ηall: the comprehensive efficiency of energy storage of the system;
kappa: a working gas adiabatic index;
pi: the compression ratio of the compressor 3 and the turbine 5 in the refrigeration energy storage mode;
pi': the compression ratio of the compressor 3 and the turbine 5 in the heating and power supply mode;
p: compression ratio in a refrigeration energy storage mode;
p': compression ratio in the heating and power supply mode;
Wall: storage capacity, unit: J/K or MW & H;
c: specific heat capacity, unit: j/(kg. K);
m: total mass of molten salt, unit: kg or t;
v: total volume of molten salt, unit: m is3m；
M': the total mass of the antifreeze solution, unit: kg or t;
v': the total volume of the antifreeze solution, unit: m is3；
Wcold: the cold air power can be provided in the refrigeration energy storage mode;
Whot: the heating power can be provided in the heating power supply mode;
f: flow rate of working gas
According to the refrigeration heat storage mode and the heating power supply mode shown in fig. 1 and fig. 2, fig. 3 and fig. 4 show a brayton-kalina cycle type energy storage power supply device according to a second embodiment of the invention. In the present embodiment, the primary heat storage system 8 and the cold storage system 19 of the apparatus are both in the form of a double tank. Wherein, the main heat storage system 8 comprises a high-temperature container, namely a high-temperature heat storage tank 14 and a low-temperature container, namely a low-temperature heat storage tank 13, the two containers are both made of high-temperature-resistant and corrosion-resistant stainless steel materials with an additional heat insulation layer, and the temperature of the low-temperature container is maintained at
Figure BDA0003166071650000091
The temperature of the high-temperature container is maintained at
Figure BDA0003166071650000092
Molten salt or heat conducting oil is adopted as a heat storage medium in the container body; the cold accumulation system 19 is composed of a normal temperature tank, here a normal temperature cold accumulation tank 16 (i.e. an antifreeze tank), and a low temperature container, here a low temperature cold accumulation tank 15 (i.e. an antifreeze cold accumulation tank), wherein a heat insulation layer is additionally arranged on the low temperature container body, the heat insulation layer is not arranged outside the normal temperature tank, and the temperature of the low temperature container is maintained at T0The temperature of the normal temperature container is maintained at T1(in the present embodiment, T1At room temperature Tair) The cold storage medium in the container body is exemplified by an automobile antifreeze. The low temperature point of the main heat storage system 8 is thus
Figure BDA0003166071650000093
The high temperature point of the main heat storage system 8 is
Figure BDA0003166071650000094
The cold storage system 19 has a low temperature point of T0The high temperature point of the cold accumulation system 19 is air normal temperature Tair。
Generally, high-temperature molten salt has high corrosivity to metal, so the temperature of the molten salt is controlled to be 700 ℃ in the embodiment. Of course, the temperature of the molten salt can be controlled to be higher, but the requirement on materials is higher, and the cost is increased correspondingly.
As shown in fig. 3, corresponding to the refrigeration energy storage mode, the brayton-kalina cycle type energy storage power supply device includes an air inlet device 1, a compressor 3, a main heat exchanger 4 connected with a main heat storage system 8, a waste heat boiler 21, a turbine 5, a cold storage heat exchanger 18 connected with a cold storage system 19, and an air outlet device 6 which are connected in series in sequence along the direction of a working medium by pipelines; the waste heat boiler 21, the separator 22, the steam turbine 23, the mixer 27, the condenser 25, the working medium pump 26 and the ammonia circulating heat exchanger 24 are sequentially connected in series along the trend of the ammonia water mixture medium to form a loop, the separator 22 is connected with the steam turbine through an ammonia-rich steam outlet of the separator, the ammonia circulating heat exchanger 24 and the throttle valve 28 are further arranged between an ammonia-poor solution outlet of the separator 22 and the mixer 27 and are sequentially connected in series along the trend of the ammonia water mixture medium. The exhaust-heat boiler 21, the separator 22, the steam turbine 23, the mixer 27, the condenser 25, the working medium pump 26, the ammonia circulation heat exchanger 24 and the throttle valve 28 jointly form an ammonia circulation regenerative system 20. Thereby, a first arrangement is formed.
Therefore, corresponding to the refrigeration energy storage mode, the temperature at which the brayton-kalina cycle type energy storage power supply device absorbs a certain flow from the outside from the air inlet device 1 is T1The dry air as working medium is compressed adiabatically after entering the compressor 3, and the working medium is compressed into high-temperature and high-pressure gas for a given compression ratio P, wherein the compressor is not an ideal compressor, and the isentropic efficiency eta of the compressor is consideredcAnd polytropic efficiency ηcpIsentropic efficiency, also known as adiabatic efficiency, and polytropic efficiency can be scaled, with the parameters given being different depending on the equipment. The temperature of the gas after coming out of the compressor is increased to
Figure BDA0003166071650000101
(psi is the compression ratio intermediate parameter,
Figure BDA0003166071650000102
kappa is an adiabatic index, pi is a compression ratio of a refrigeration energy storage mode, namely compression ratios of the compressor 3 and the turbine 5 in the refrigeration energy storage mode), then the working medium enters the main fused salt gas heat exchanger 4, the main heat exchanger 4 transfers the heat of the high-temperature working medium at the outlet of the compressor 3 to the low-temperature fused salt in the low-temperature heat storage tank 13 of the main heat storage system 8, and the temperature of the high-temperature working medium is controlled by the low-temperature fused salt in the low-temperature heat storage tank 13 of the main heat storage system 8
Figure BDA0003166071650000103
Is reduced to
Figure BDA0003166071650000104
Low temperature molten salt on the other hand
Figure BDA0003166071650000105
Is heated to
Figure BDA0003166071650000106
Then enters the high-temperature heat storage tank 14 through the heat storage medium pump 10, that is, the working medium exchanges heat with the main heat storage system 8 through the main heat exchanger 4 in the refrigeration energy storage mode, so that the heat storage medium at the position of the low temperature point in the main heat storage system 8 is enabled to be at the low temperature point of the heat storage medium
Figure BDA0003166071650000107
Raised to a high temperature point
Figure BDA0003166071650000108
And transferred to the location of the high temperature point of the primary thermal storage system 8. Since the isentropic efficiency of the compressor turbine is less than 1, the working medium needs to release a portion of the heat. The working medium discharges heat to the waste heat boiler 21, and the heat discharged by the working medium enters the waste heat boiler 21 to heat the basic ammonia solution, so that the basic ammonia solution absorbs heat in an isobaric manner to be changed into an ammonia water gas-liquid mixture and enters the separator 22. Subsequently, the gas is separated by a separator 22The liquid-two phase mixture is separated into ammonia-rich vapor and ammonia-lean solution. Wherein the ammonia-rich steam enters the steam turbine 23 for adiabatic expansion to do work outwards; the poor ammonia solution enters the ammonia circulation heat exchanger 24 to preheat the basic ammonia solution before entering the waste heat boiler 21, the poor ammonia solution is throttled and depressurized by the throttle valve 28 after being discharged, then is mixed with the dead steam discharged from the steam turbine 23 in the mixer 27 to form the basic ammonia solution, enters the condenser 25 for isobaric heat release, is boosted by the working medium pump 26, then enters the ammonia circulation heat exchanger 24 to be preheated by the poor ammonia solution, and then the basic ammonia solution returns to the waste heat boiler 21 and repeats the processes, thus completing the circulation. The temperature of the working medium after heat absorption of the waste heat boiler is reduced to
Figure BDA0003166071650000109
The working medium with high temperature and high pressure is expanded into the working medium with low temperature and normal pressure according to a certain compression ratio after entering the turbine 5 for adiabatic expansion, wherein the turbine 5 is not an ideal turbine, and the isentropic efficiency eta of the turbine is consideredtAnd polytropic efficiency ηtpThe temperature of the gas coming out of the outlet of the turbine 5 being reduced to
Figure BDA00031660716500001010
Figure BDA00031660716500001011
Then the working medium enters a cold accumulation heat exchanger 18 of the working medium of the anti-freezing solution, the cold accumulation heat exchanger 18 absorbs the heat of the cold accumulation medium (i.e. the anti-freezing solution) in the cooling liquid pool where the high temperature point of the cold accumulation system 19 is located through the low temperature working medium at the outlet of the turbine 5, here, the cold accumulation medium in the normal temperature cold accumulation tank 16, so that the temperature of the low temperature working medium is from T0c1Is raised to T1c1On the other hand, the temperature of the cold storage medium is from its high temperature point (i.e. the air normal temperature T)air) Cooling to T0Then enters the area where the low temperature point of the cold accumulation system 19 is located, namely the low temperature cold accumulation tank 15, through the cold accumulation medium pump 17, that is, the working medium exchanges heat with the cold accumulation system 19 through the cold accumulation heat exchanger 18 in the refrigeration and energy storage mode, so that the cold accumulation medium at the position where the high temperature point of the cold accumulation system 19 is located is from the high temperature point (namely the air normal temperature T)air) Down to the low temperature point T0And transferred to the location of the low temperature point of the cold storage system 19. The discharged working medium is then optionally circulated or released to the outside via the gas outlet means 6.
Corresponding to the heat supply and power supply mode, as shown in fig. 4, the brayton-kalina cycle type energy storage and power supply device is just opposite to the refrigeration energy storage mode, and comprises an air inlet device 1, a cold storage heat exchanger 18, a compressor 3, a main heat exchanger 4, a turbine 5, a waste heat boiler 21 and an air outlet device 6 which are sequentially connected in series by pipelines along the trend of working media, wherein the cold storage heat exchanger 18 is connected with a cold storage system 19; the waste heat boiler 21, the separator 22, the steam turbine 23, the mixer 27, the condenser 25, the working medium pump 26 and the ammonia circulating heat exchanger 24 are sequentially connected in series along the trend of the ammonia water mixture medium to form a loop, the separator 22 is connected with the steam turbine 23 through an ammonia-rich steam outlet of the separator, the ammonia circulating heat exchanger 24 and the throttle valve 28 are further arranged between an ammonia-poor solution outlet of the separator 22 and the mixer 27 and are sequentially connected in series along the trend of the ammonia water mixture medium. Thereby, a second arrangement is formed.
The temperature of the Brayton-kalina circulating energy storage power supply device which absorbs a certain flow from the outside by the air inlet device 1 is T1c2＝T1The working medium firstly enters the cold accumulation heat exchanger 18 for heat exchange, and the cold accumulation heat exchanger 18 absorbs the heat of the normal temperature working medium through the low temperature antifreeze solution in the low temperature cold accumulation tank 15 of the cold accumulation system 19, so that the temperature of the working medium is reduced from the normal temperature to T0c2On the other hand, the temperature in the low-temperature cold storage tank 15 of the cold storage system 19 is T0Is heated to a high temperature point (i.e., air normal temperature T)air) Enters the normal temperature cold accumulation tank 16 through the cold accumulation medium pump 17, that is, the working medium exchanges heat with the cold accumulation system 19 through the cold accumulation heat exchanger 18 in the heat supply and power supply mode, so that the heat accumulation medium at the position of the low temperature point in the cold accumulation system 19 is enabled to be from the low temperature point T of the heat accumulation medium0Raised to a high temperature point (i.e. normal temperature T of air)air) And transferred to the location of the high temperature point of the cold storage system 19. The working medium enters the compressor 3 for adiabatic compression after heat exchange and temperature reduction, and the working medium is compressed for a given compression ratio PThe gas is compressed into high-temperature and high-pressure gas, the compressor is not an ideal compressor, and the isentropic efficiency eta of the compressor is consideredcAnd polytropic efficiency ηcpThe temperature of the gas after exiting the outlet of the compressor 3 is increased to
Figure BDA0003166071650000111
The working medium then enters the main heat exchanger 4 which transfers the heat of the high temperature molten salt in the high temperature heat storage tank 14 of the main heat storage system 8 to the working medium at the outlet of the compressor 3, so that the working medium temperature is driven from
Figure BDA0003166071650000112
Is raised to
Figure BDA0003166071650000113
On the other hand at a temperature of
Figure BDA0003166071650000114
Is cooled to
Figure BDA0003166071650000115
Enters the low-temperature heat storage tank 13 through the heat storage medium pump 10, that is, the working medium exchanges heat with the main heat storage system 8 through the main heat exchanger 4 in the heat supply and power supply mode, so that the heat storage medium at the position of the high-temperature point in the main heat storage system 8 is enabled to be discharged from the high-temperature point
Figure BDA0003166071650000121
Lowered to the low temperature point
Figure BDA0003166071650000122
And transferred to the location of the low temperature point of the primary thermal storage system 8. The working medium enters the turbine 5 for adiabatic expansion after heat exchange and temperature rise, and the high-temperature and high-pressure working medium is expanded into a low-temperature and normal-pressure working medium according to a certain compression ratio, wherein the turbine 5 is not an ideal turbine, and the isentropic efficiency eta of the turbine is consideredtAnd polytropic efficiency ηtpThe temperature of the gas coming out of the outlet of the turbine 5 is reduced to
Figure BDA0003166071650000123
k is an adiabatic index, and pi' is a compression ratio of a heat supply and power supply mode), at this time, the working medium is still higher than the normal temperature, so that waste heat recovery can be performed through the ammonia circulation heat recovery system 20, the working medium discharges heat to the waste heat boiler 21, the heat discharged by the working medium enters the waste heat boiler 21 to heat the basic ammonia solution, and the basic ammonia solution is converted into an ammonia water gas-liquid mixture through isobaric heat absorption and enters the separator 22. Subsequently, the gas-liquid two-phase mixture is separated into ammonia-rich vapor and ammonia-lean solution by the separator 22. Wherein the ammonia-rich steam enters the steam turbine 23 for adiabatic expansion to do work outwards; the poor ammonia solution enters the ammonia circulation heat exchanger 24 to preheat the basic ammonia solution before entering the waste heat boiler 21, the poor ammonia solution is throttled and depressurized by the throttle valve 28 after being discharged, then is mixed with the dead steam discharged from the steam turbine 23 in the mixer 27 to form the basic ammonia solution, enters the condenser 25 for isobaric heat release, is boosted by the working medium pump 26, then enters the ammonia circulation heat exchanger 24 to be preheated by the poor ammonia solution, and then the basic ammonia solution returns to the waste heat boiler 21 and repeats the processes, thus completing the circulation. The working medium absorbed by the waste heat boiler circulates or is released to the outside through the air outlet device 6 according to the circumstances.
The main heat exchanger 4 of the invention is a heat exchanger of molten salt working medium, which reduces heat exchange temperature difference as much as possible to improve energy storage efficiency, generally speaking, the reasonable heat exchange temperature difference delta T is 15-30 degrees. For the refrigeration energy storage mode and the power supply and heating mode, see the following temperature relationship:
Figure BDA0003166071650000124
Figure BDA0003166071650000125
Figure BDA0003166071650000126
Figure BDA0003166071650000127
the cold storage heat exchanger 18 of the present invention should reduce the heat exchange temperature difference as much as possible to improve the energy storage efficiency, and generally speaking, the reasonable heat exchange temperature difference Δ T is 15 to 30 degrees. For the refrigeration energy storage mode and the power supply and heat supply mode, the temperature relationship is as follows,
T0c1＝T0-ΔT，
T1c1＝T1-ΔT，
T0c2＝T0+ΔT，
T1c2＝T1+ΔT。
the working medium compressor 3 of the invention is not an ideal compressor, and the isentropic efficiency eta of the compressor should be consideredcAnd polytropic efficiency ηcpAll be less than 1, to refrigeration energy storage mode and power supply heating mode, the exit temperature relation of working medium compressor 3 is:
Figure BDA0003166071650000131
Figure BDA0003166071650000132
the turbine 5 of the invention is not an ideal turbine, and the isentropic efficiency eta of the turbine is consideredtAnd polytropic efficiency ηtpAre both smaller than 1, and for the refrigeration energy storage mode and the power supply and heat supply mode, the inlet and outlet temperature relationship of the turbine 5 is as follows:
Figure BDA0003166071650000133
Figure BDA0003166071650000134
in the invention, the compression ratios of the working medium in the compressor 3 and the turbine 5 in the power supply and heating mode are determined by the isentropic efficiency of the compressor and the inlet and outlet temperature. The compression ratio intermediate parameters of the working medium in the compressor 3 and the turbine 5 are as follows:
Figure BDA0003166071650000135
the comprehensive energy storage efficiency of the system is determined by the refrigeration coefficient epsilon of the refrigeration energy storage cycle, the heat engine efficiency eta in the power supply and heating mode and the power generation efficiency eta' in the regenerative system.
In the invention, the pipeline of the working medium needs to be sealed and can bear the pressure of at least 30Bar and the high temperature of 600 ℃.
Third embodiment Brayton-kalina circulating energy storage power supply method based on regenerative Brayton
Fig. 5-6 are schematic diagrams of a brayton-kalina cycle energy storage and power supply method according to a third embodiment of the invention, the method includes an energy storage mode and a power supply mode. In this embodiment, since the brayton-kalina cycle energy storage power supply method is based on the regenerative brayton, the energy storage mode is an energy storage residual cold recovery mode, and the power supply mode is a brayton-kalina cycle power supply regenerative mode.
Fig. 5 is a schematic diagram illustrating an energy storage residual cold recovery mode of the brayton-kalina cycle energy storage power supply method according to the third embodiment of the invention. The energy storage residual cold recovery mode is basically the same as the refrigeration energy storage mode in the brayton-kalina cycle type energy storage power supply method according to the first embodiment of the invention, and the difference is only that: before the working medium enters the compressor 3, the working medium enters the regenerative heat exchanger 2, so that isobaric heat absorption is carried out through the regenerative heat storage system 7.
Specifically, the air intake device 1 absorbs dry air (taking air as an example) from the outside as a working medium, and the working medium at normal temperature enters the regenerative heat exchanger 2, so that isobaric heat absorption is performed by the regenerative heat storage system 7, and the temperature is raised by absorbing heat from the regenerative heat storage system 7; then the working medium enters a compressor 3 for adiabatic compression, and the working medium is compressed into high-temperature high-pressure gas; then the working medium enters the main heat exchanger 4 and absorbs the heat of the high-temperature and high-pressure gas through the main heat storage system 8 to perform isobaric heat release, so that the heat of the working medium is released into the main heat storage system 8, and meanwhile, the main heat storage system completes heat storage and energy storage. Since the isentropic efficiency of the compressor turbine is less than 1, the working medium needs to release a portion of the heat. The working medium discharges heat to the waste heat boiler 21, and the heat discharged by the working medium enters the waste heat boiler 21 to heat the basic ammonia solution, so that the basic ammonia solution absorbs heat in an isobaric manner to be changed into an ammonia water gas-liquid mixture and enters the separator 22. Subsequently, the gas-liquid two-phase mixture is separated into ammonia-rich vapor and ammonia-lean solution by the separator 22. Wherein the ammonia-rich steam enters the steam turbine 23 for adiabatic expansion to do work outwards; the poor ammonia solution enters the ammonia circulation heat exchanger 24 to preheat the basic ammonia solution before entering the waste heat boiler 21, the poor ammonia solution is throttled and depressurized by the throttle valve 28 after being discharged, then is mixed with the dead steam discharged from the steam turbine 23 in the mixer 27 to form the basic ammonia solution, enters the condenser 25 for isobaric heat release, is boosted by the working medium pump 26, then enters the ammonia circulation heat exchanger 24 to be preheated by the poor ammonia solution, and then the basic ammonia solution returns to the waste heat boiler 21 and repeats the processes, thus completing the circulation. After the heat is discharged to the waste heat boiler through the working medium, the working medium enters the turbine 5 to perform adiabatic expansion so as to do work to the outside, the working medium expands to be gas with low temperature and normal pressure, the temperature of the working medium is much lower than the normal temperature, then the working medium enters the cold accumulation heat exchanger 18 to perform an isobaric heat absorption process through the cold accumulation system 19, namely, the temperature is raised through absorbing heat from the cold accumulation system 19, and then the discharged working medium circulates or is released to the outside through the gas outlet device 6 according to the circumstances.
For the brayton-kalina cycle power supply regenerative mode, as shown in fig. 6, it is exactly opposite to the energy storage residual cold recovery mode, and the brayton-kalina cycle power supply regenerative mode is basically the same as the heat supply power supply mode in the brayton-kalina cycle energy storage power supply method according to the first embodiment of the present invention, and the difference is only that: after passing through the waste heat boiler 21, the working medium enters the regenerative heat exchanger 2, so that isobaric heat release is performed by the regenerative heat storage system 7.
Specifically, the air intake device 1 absorbs dry air from the outside as a working medium, and the working medium first enters the cold storage heat exchanger 18 to release heat at equal pressure. The temperature is reduced by releasing heat from the cold accumulation system 19, and then the working medium enters the compressor 3 for adiabatic compression, so that the working medium is compressed into high-temperature high-pressure gas; then the working medium comes out from the outlet of the compressor 3 and enters the main heat exchanger 4 to absorb heat at equal pressure, the main heat exchanger 4 transfers the heat in the main heat storage system 8 to the working medium to continuously raise the temperature of the working medium, then the working medium enters the turbine 5 to perform adiabatic expansion, the high-temperature and high-pressure working medium is expanded into normal-pressure gas, then the working medium releases redundant heat and enters the regenerative heat exchanger 2 to release heat at equal pressure, the temperature of the working medium is reduced after the heat of the working medium is released into the regenerative heat storage system 7, and the working medium at the outlet of the regenerative heat storage system 7 is still higher than the normal temperature due to the existence of heat exchange temperature difference. Therefore, before the working medium enters the regenerative thermal storage system 7, the working medium enters the waste heat boiler 21 to heat the basic ammonia solution, so that the basic ammonia solution absorbs heat in an isobaric manner to be changed into an ammonia water gas-liquid mixture, the ammonia water gas-liquid mixture enters the separator 22, the gas-liquid two-phase mixture is separated into ammonia-rich steam and ammonia-poor solution by the separator 22, the ammonia-rich steam enters the turbine 23 to perform adiabatic expansion so as to do work outwards, the ammonia-poor solution enters the ammonia circulating heat exchanger 24 so as to be preheated before the basic ammonia solution enters the waste heat boiler 21, the ammonia-poor solution is throttled and depressurized by the throttle valve 28 after being completely heated, then is mixed with exhaust steam discharged from the turbine 23 in the mixer 27 to be the basic ammonia solution, enters the condenser 25 to release heat in an isobaric manner, is pressurized by the working medium pump 26, then enters the ammonia circulating heat exchanger 24 so as to be preheated by the ammonia-poor solution, and then the basic ammonia solution returns to the waste heat boiler 21 to repeat the above processes, thus completing the cycle. The working medium absorbed heat by the waste heat boiler 21 passes through the regenerative heat exchanger 2 and then circulates or is released to the outside through the gas outlet device 6 according to circumstances. In the process, net work is output to the outside, and the work is used for supplying power.
Fourth embodiment brayton-kalina circulating energy storage power supply device based on regenerative brayton
We define the following notation:
Figure BDA0003166071650000151
low temperature point of the main heat storage system, unit: k;
Figure BDA0003166071650000152
high temperature point of the main heat storage system, unit: k;
T0: low temperature point of cold storage system, unit: k; (ii) a
T1: high temperature point of the regenerative heat storage system, unit: k; (ii) a
Tair: air normal temperature, unit: k, also the high temperature point of the cold storage system 19;
Tair+ Δ T: the low temperature point of the regenerative heat storage system, unit: k;
Δ T: heat transfer temperature difference, unit: k;
Figure BDA0003166071650000153
exhaust-heat boiler inlet temperature under the energy storage waste cooling recovery mode, unit: k;
Figure BDA0003166071650000154
turbine inlet temperature in the energy storage waste cooling recovery mode, unit: k;
Figure BDA0003166071650000155
compressor outlet temperature in the energy storage residual cooling recovery mode, unit: k;
T0c1: turbine outlet temperature in the energy storage waste cooling recovery mode, unit: k;
T1c1: compressor inlet temperature in the energy storage waste heat recovery mode, unit: k;
Figure BDA0003166071650000156
brayton-kalina cycle power supply loopCompressor outlet temperature in hot mode, unit: k;
Figure BDA0003166071650000161
the inlet temperature of the turbine in the Brayton-kalina cycle power supply regenerative mode is as follows: k;
T0c2: inlet temperature of the compressor in the Brayton-kalina cycle power supply regenerative mode, unit: k;
T1c2: the outlet temperature of the turbine in the Brayton-kalina cycle power supply regenerative mode is as follows: k;
T1c2i: the inlet temperature of the regenerative heat storage system in the Brayton-kalina cycle power supply regenerative mode is as follows: k;
Tout1: outlet temperature in energy storage waste cooling recovery mode, unit: k;
Tout2: outlet temperature in brayton-kalina cycle power supply regenerative mode, unit: k;
Q2c1a: the power of the heat absorbed by the working medium from the regenerative heat storage system in the energy storage residual cold recovery mode is as follows, unit: MW;
Q2c1b: the power of the heat absorbed by the working medium from the cold accumulation system in the energy storage residual cold recovery mode is as follows, unit: MW;
Q1c1: the power of the heat absorbed by the working medium from the main heat storage system in the energy storage residual cold recovery mode is as follows, unit: MW;
Q2c2a: the power of the heat absorbed by the working medium from the regenerative heat storage system in the Brayton-kalina cycle power supply regenerative mode is as follows, unit: MW;
Q2c2b: the power of heat absorbed by the working medium from the cold accumulation system in a Brayton-kalina cycle power supply regenerative mode is as follows: MW;
Q1c2: the power of the heat absorbed by the working medium from the main heat storage system in the Brayton-kalina cycle power supply regenerative mode is as follows: MW;
Q1c2: brayton-kalinaThe power of heat release before the working medium enters the regenerative heat storage system in the circulating power supply regenerative mode is as follows: MW;
Wc1: power of the compressor in the energy storage residual cooling recovery mode, unit: MW;
Wt1: the power of the turbine in the energy storage residual cooling recovery mode, unit: MW;
Wc2: the power of the compressor in the Brayton-kalina cycle power supply regenerative mode is as follows: MW;
Wt2: the power of the turbine in the Brayton-kalina cycle power supply regenerative mode is as follows: MW;
Figure BDA0003166071650000162
net input power in energy storage residual cooling recovery mode, unit: MW;
Figure BDA0003166071650000163
net output power in power supply and heat supply mode, unit: MW;
ηcp: the polytropic efficiency of the compressor;
ηtp: the polytropic efficiency of the turbine;
ηs: heat storage efficiency in the energy storage waste cold recovery mode;
ηw: generating efficiency in a Brayton-kalina cycle power supply regenerative mode;
ηall: the comprehensive efficiency of energy storage of the system;
kappa: a working medium adiabatic index;
pi: the compression ratios of the compressor 3 and the turbine 5 in the energy storage residual cold recovery mode;
pi': the compression ratios of the compressor 3 and the turbine 5 in a Brayton-kalina cycle power supply regenerative mode;
p: compression ratio in energy storage residual cold recovery mode;
p': compression ratio in a Brayton-kalina cycle power supply regenerative mode;
Wall: storage capacity, unit: J/K or MW & H;
c: specific heat capacity, unit: j/(kg. K);
m: total mass of molten salt, unit: kg or t;
v: total volume of molten salt, unit: m is3；
M': the total mass of the antifreeze solution, unit: kg or t;
v': the total volume of the antifreeze solution, unit: m is3；
Wcold: the cold air power can be provided under the energy storage residual cold recovery mode;
Whot: the heating power can be provided in a Brayton-kalina cycle power supply regenerative mode;
f: the flow rate of the working medium.
Based on the energy storage residual cold recovery mode and the brayton-kalina cycle power supply regenerative mode shown in fig. 5 and 6, fig. 7 and 8 show a brayton-kalina cycle energy storage power supply device according to a fourth embodiment of the invention. In the present embodiment, the regenerative thermal storage system 7, the main thermal storage system 8, and the cold storage system 19 of the apparatus are each composed of one or more sets of thermal storage media (or cold storage media) in the form of two tanks. Wherein, the regenerative thermal storage system 7 is composed of a high temperature container, a high temperature regenerative tank 12 and a low temperature container, a low temperature regenerative tank 11, the two container bodies are externally provided with an insulating layer, and the temperature of the low temperature container is maintained at Tair+ Δ T, the high temperature vessel temperature is maintained at T1(ii) a The main heat storage system 8 comprises a high-temperature container, namely a high-temperature heat storage tank 14 and a low-temperature container, namely a low-temperature heat storage tank 13, wherein the high-temperature container and the low-temperature container are both made of high-temperature-resistant and corrosion-resistant stainless steel materials with an additional heat insulation layer, and the temperature of the low-temperature container is maintained at
Figure BDA0003166071650000171
The temperature of the high-temperature container is maintained at
Figure BDA0003166071650000172
The thermal storage system 19 is composed of a low-temperature vessel, here a low-temperature thermal storage tank 15, and a normal-temperature vessel, here a normal-temperature thermal storage tank 16The composition is that the low-temperature container body is externally provided with a heat-insulating layer, the outside of the normal-temperature container is not provided with the heat-insulating layer, and the temperature of the low-temperature container is maintained at T0The temperature of the normal temperature container is maintained at the normal temperature Tair(ii) a The container body adopts antifreeze as a cold accumulation medium. Generally, high-temperature molten salt has high corrosivity to metal, so the temperature of the molten salt is controlled to be 700 ℃ in the embodiment. Of course, the temperature of the molten salt can be controlled to be higher, but the requirement on materials is higher, and the cost is increased correspondingly. The low temperature point of the main heat storage system 8 is thus
Figure BDA0003166071650000181
The high temperature point of the main heat storage system 8 is
Figure BDA0003166071650000182
The high temperature point of the regenerative thermal storage system 7 is T1The low temperature point of the regenerative thermal storage system 7 is Tair+ Δ T; the cold storage system 19 has a low temperature point of T0The high temperature point of the cold accumulation system 19 is air normal temperature Tair。
As shown in fig. 7, corresponding to the energy storage residual cold recovery mode, the brayton-kalina cycle type energy storage and power supply apparatus and the brayton-kalina cycle type energy storage and power supply apparatus according to the second embodiment of the present invention are arranged in the substantially same manner corresponding to the refrigeration energy storage mode, and the difference is only that: a regenerative heat exchanger 2 is connected in series between the air inlet device 1 and the compressor 3, and the regenerative heat exchanger 2 is connected with a regenerative heat storage system 7.
The Brayton-kalina circulating energy storage power supply device absorbs a certain flow of normal temperature T from the outside from the air inlet device 1airIs used as a working medium which enters the recuperative heat exchanger 2 for isobaric heat absorption by absorbing heat Q from the recuperative heat storage system 72c1aThen raising the temperature to ensure that the temperature of the high-temperature working medium is changed from the normal temperature TairIs raised to T1c1On the other hand, the temperature T of the heat storage medium in the high-temperature heat recovery tank 12 is lower than1Down to TairAfter + delta T, the working medium enters the low-temperature heat recovery tank 11 through the heat recovery medium pump 9, that is, the working medium passes through the heat recovery under the energy storage residual cold recovery modeThe heat exchanger 2 exchanges heat with the regenerative heat storage system 7, so that the heat storage medium at the position of the high-temperature point in the regenerative heat storage system 7 is enabled to exchange heat from the high-temperature point T1Down to the low temperature point Tair+ Δ T and shifted to the location of the low temperature point of the regenerative thermal storage system 7. Then the working medium enters the compressor 3 for adiabatic compression, and the working medium is compressed into high-temperature and high-pressure gas for a given compression ratio P, wherein the compressor 3 is not an ideal compressor, and the isentropic efficiency eta is consideredcAnd polytropic efficiency ηcpThe temperature of the gas after exiting the outlet of the compressor 3 is increased to
Figure BDA0003166071650000183
(
Figure BDA00031660716500001810
Kappa is the adiabatic index, and kappa is the compression ratio of the compressor 3 and the turbine 5 in the energy storage waste heat recovery mode); then the working medium enters the main heat exchanger 4 to carry out isobaric heat release, and the heat-Q of the working medium is transferred1c1The temperature is reduced after being released into the main heat storage system 8, so that the temperature of the high-temperature working medium is increased
Figure BDA0003166071650000184
Is reduced to
Figure BDA0003166071650000185
On the other hand, the temperature of the molten salt in the low-temperature molten salt tank 13 is controlled by the temperature
Figure BDA0003166071650000186
Is raised to
Figure BDA0003166071650000187
Then enters a high-temperature molten salt tank 14 through a heat storage medium pump 10, that is, the working medium exchanges heat with the main heat storage system 8 through the main heat exchanger 4 in an energy storage residual cold recovery mode, so that the heat storage medium at the position of a high-temperature point in the main heat storage system 8 is enabled to be discharged from a low-temperature point of the heat storage medium
Figure BDA0003166071650000188
Raised to a high temperature point
Figure BDA0003166071650000189
And transferred to the location of the high temperature point of the primary thermal storage system 8. Since the isentropic efficiency of the compressor turbine is less than 1, the working medium needs to release a portion of the heat. The working medium discharges heat to the waste heat boiler 21, and the heat discharged by the working medium enters the waste heat boiler 21 to heat the basic ammonia solution, so that the basic ammonia solution absorbs heat in an isobaric manner to be changed into an ammonia water gas-liquid mixture and enters the separator 22. Subsequently, the gas-liquid two-phase mixture is separated into ammonia-rich vapor and ammonia-lean solution by the separator 22. Wherein the ammonia-rich steam enters the steam turbine 23 for adiabatic expansion to do work outwards; the poor ammonia solution enters the ammonia circulation heat exchanger 24 to preheat the basic ammonia solution before entering the waste heat boiler 21, the poor ammonia solution is throttled and depressurized by the throttle valve 28 after being discharged, then is mixed with the dead steam discharged from the steam turbine 23 in the mixer 27 to form the basic ammonia solution, enters the condenser 25 for isobaric heat release, is boosted by the working medium pump 26, then enters the ammonia circulation heat exchanger 24 to be preheated by the poor ammonia solution, and then the basic ammonia solution returns to the waste heat boiler 21 and repeats the processes, thus completing the circulation. The temperature of the working medium after heat absorption by the waste heat boiler 21 is reduced to
Figure BDA0003166071650000191
Then enters the turbine 5 for adiabatic expansion, the working medium expands into low-temperature normal-pressure gas, the turbine 5 is not an ideal turbine, and the isentropic efficiency eta is consideredtAnd polytropic efficiency ηtp. The temperature of the gas coming out of the outlet of the turbine 5 is reduced to
Figure BDA0003166071650000192
The working medium then enters the cold storage heat exchanger 18 for isobaric heat absorption by absorbing heat Q from the cold storage system 192c1bThen raising the temperature to make the working medium temperature from low temperature T0c1Is raised to TairΔ T, on the other hand, from the room temperature T, the cold storage medium in the room temperature cold storage tank 16airDown to T0Then enters the low-temperature cold accumulation tank 15 through the cold accumulation medium pump 17, that is, the working medium passes through the cold accumulation tank in the energy storage residual cold recovery modeThe heat exchanger 18 exchanges heat with the cold accumulation system 19, so that the cold accumulation medium at the position of the high-temperature point in the cold accumulation system 19 is cooled from the high-temperature point (namely the normal temperature T of the air)air) Down to the low temperature point T0And transferred to the location of the low temperature point of the cold storage system 19. Finally the working medium is heated to a temperature TairΔ T is discharged from the gas outlet means 6, and then the discharged working medium is circulated or released to the outside through the gas outlet means 6 as appropriate.
And corresponds to a brayton-kalina cycle power supply heat recovery mode, as shown in fig. 8, which is just opposite to an energy storage residual cold recovery mode; the brayton-kalina cycle energy storage and power supply device is basically the same as the brayton-kalina cycle energy storage and power supply device according to the second embodiment of the invention in arrangement form corresponding to the heat supply and power supply mode, and the difference is only that: a regenerative heat exchanger 2 is connected in series between the waste heat boiler 21 and the air outlet device 6, and the regenerative heat exchanger 2 is connected with a regenerative heat storage system 7.
Therefore, corresponding to the brayton-kalina cycle power supply regenerative mode, the brayton-kalina cycle energy storage power supply device absorbs a certain flow of normal temperature T from the outside from the air inlet device 10c2＝TairAs a working medium, into the cold storage heat exchanger 18 for isobaric heat release by releasing heat Q from the cold storage system 192c2bThen raising the temperature to ensure that the temperature of the working medium is changed from the normal temperature TairReduced to low temperature T0c2On the other hand, the cold storage medium in the low-temperature cold storage tank 15 is cooled from the low temperature T0Is raised to TairAfter the temperature difference is-delta T, the cold storage medium enters the normal temperature cold storage tank 16 through the cold storage medium pump 17, and since the normal temperature cold storage tank 16 is not provided with a heat insulation layer and can exchange heat with the outside, the temperature of the cold storage medium in the normal temperature cold storage tank 16 can be maintained at room temperature, that is, the working medium exchanges heat with the cold storage system 19 through the cold storage heat exchanger 18 in the Brayton-kalina cycle power supply heat regeneration mode, so that the cold storage medium at the low temperature point in the cold storage system 19 is changed from the low temperature point T0Is raised to TairΔ T and transferred to the position of the high temperature point of the cold storage system 19, and then changed to the normal temperature T by heat exchange with the outsideair. The working medium is then heated to a temperature T0c2Entering the compressor 3 for adiabatic compression, compressing the working medium into high-temperature and high-pressure gas for a given compression ratio P', wherein the compressor 3 is not an ideal compressor and the isentropic efficiency eta is consideredpAnd polytropic efficiency ηcpThe temperature of the gas after exiting the outlet of the compressor 3 is increased to
Figure BDA0003166071650000201
Figure BDA0003166071650000202
(
Figure BDA0003166071650000203
Kappa is the adiabatic index, and pi' is the compression ratio of the Brayton-kalina cycle power supply regenerative mode); the working medium enters the main heat exchanger 4 for isobaric heat absorption by absorbing heat Q from the main heat storage system 81c2Raising the temperature to ensure that the high-temperature working medium is heated from the temperature
Figure BDA0003166071650000204
Is raised to
Figure BDA0003166071650000205
On the other hand, the temperature of the heat storage medium in the high-temperature heat storage tank 14 is changed from the temperature
Figure BDA0003166071650000206
Is reduced to
Figure BDA0003166071650000207
Then enters a low-temperature heat storage tank 13 through a heat storage medium pump 10, that is, the working medium exchanges heat with the main heat storage system 8 through the main heat exchanger 4 in a Brayton-kalina cycle power supply regenerative mode, so that the heat storage medium at the position of the high-temperature point in the main heat storage system 8 exchanges heat with the main heat storage system 8 from the high-temperature point
Figure BDA0003166071650000208
Lowered to the low temperature point
Figure BDA0003166071650000209
Turning overMove to the location of the low temperature point of the primary thermal storage system 8. Then the working medium enters the turbine 5 to perform adiabatic expansion and do work externally, the working medium expands into normal pressure gas, the turbine 5 is not a turbine, and the isentropic efficiency eta of the turbine 5 is consideredtAnd polytropic efficiency ηtp. The temperature of the gas coming out of the outlet of the turbine 5 is reduced to
Figure BDA00031660716500002010
Then the working medium releases energy Q to the outsideoutSo that the gas temperature is from T1c2Down to T1c2i＝T1+ Δ T, the working medium discharges heat to the exhaust-heat boiler 21, and the heat discharged from the working medium enters the exhaust-heat boiler 21 to heat the basic ammonia solution, so that the basic ammonia solution absorbs heat isobarically and becomes an ammonia water gas-liquid mixture, which enters the separator 22. Subsequently, the gas-liquid two-phase mixture is separated into ammonia-rich vapor and ammonia-lean solution by the separator 22. Wherein the ammonia-rich steam enters the steam turbine 23 for adiabatic expansion to do work outwards; the poor ammonia solution enters the ammonia circulation heat exchanger 24 to preheat the basic ammonia solution before entering the waste heat boiler 21, the poor ammonia solution is throttled and depressurized by the throttle valve 28 after being discharged, then is mixed with the dead steam discharged from the steam turbine 23 in the mixer 27 to form the basic ammonia solution, enters the condenser 25 for isobaric heat release, is boosted by the working medium pump 26, then enters the ammonia circulation heat exchanger 24 to be preheated by the poor ammonia solution, and then the basic ammonia solution returns to the waste heat boiler 21 and repeats the processes, thus completing the circulation. Then the working medium enters the regenerative heat exchanger 2 to release heat at equal pressure, and the working medium releases heat-Q to the regenerative heat storage system 72c2aAfter that, the temperature is raised so that the working medium temperature is raised from the temperature T1c2iDown to Tair+2 Δ T, on the other hand, from the temperature T of the heat storage medium in the low-temperature heat recovery tank 11air+ Δ T rise to T1Then enters a high-temperature heat recovery tank 12 through a heat recovery medium pump 9, that is, the working medium exchanges heat with the heat recovery and storage system 7 through the heat recovery heat exchanger 2 in a Brayton-Carlina cycle power supply heat recovery mode, so that the heat storage medium at the position of the high-temperature point in the heat recovery and storage system 7 is enabled to be at the low-temperature point T from the heat storage mediumair+ Δ T rise to the high temperature point T1And transferred to the high temperature of the regenerative heat storage system 7Where the point is located. Finally the working medium is heated to a temperature TairThe +2 Δ T is discharged from the gas outlet device 6 and supplied to the outside as a heating source. In the brayton-kalina cycle power supply regenerative mode, the turbine 5 applies work to the outside, the compressor 3 consumes the work, and net output work to the outside in the process, that is, the work is used for power supply.
The main heat exchanger 4 of the present invention should reduce the heat exchange temperature difference as much as possible to improve the energy storage efficiency, and generally speaking, the reasonable heat exchange temperature difference Δ T is 3-15 degrees. For the energy storage residual cold recovery mode and the Brayton-kalina cycle power supply regenerative mode, see the following temperature relationship,
Figure BDA0003166071650000211
Figure BDA0003166071650000212
Figure BDA0003166071650000213
Figure BDA0003166071650000214
the regenerative heat exchanger 2 of the invention should reduce the heat exchange temperature difference as much as possible to improve the energy storage efficiency, and generally speaking, the reasonable heat exchange temperature difference delta T is 3-15 degrees. For the energy storage residual cold recovery mode and the Brayton-kalina cycle power supply regenerative mode, the temperature relationship is as follows,
T1c1＝T1-ΔT，
T1c2i＝T1+ΔT，
Tin1＝Tair，
Tout2＝Tair+2ΔT。
the cold accumulation heat exchanger of the invention should reduce the heat exchange temperature difference as much as possible to improve the energy storage efficiency, generally speaking, the reasonable heat exchange temperature difference Delta T is 3-15 degrees. For the energy storage residual cold recovery mode and the Brayton-kalina cycle power supply regenerative mode, the temperature relationship is as follows,
T0c1＝T0-ΔT，
T0c2＝T0+ΔT，
Tin2＝Tair，
Tout1＝Tair-ΔT。
the working medium compressor 3 of the invention is not an ideal compressor, and the isentropic efficiency eta should be consideredcAnd polytropic efficiency ηcpAll be less than 1, for energy storage waste cold recovery mode and brayton-kalina circulation power supply backheat mode, the exit temperature relation of working medium compressor 3 is:
Figure BDA0003166071650000221
Figure BDA0003166071650000222
in the above formula, the first and second carbon atoms are,
Figure BDA0003166071650000223
Figure BDA0003166071650000224
the turbine 5 of the invention is not an ideal turbine, and the isentropic efficiency eta should be consideredtAnd polytropic efficiency ηtpAre all less than 1, and for the energy storage residual cold recovery mode and the Brayton-kalina cycle power supply regenerative mode, the inlet and outlet temperature relationship of the turbine 5 is as follows:
Figure BDA0003166071650000225
Figure BDA0003166071650000226
in the above equation, the compression ratio intermediate parameters ψ, ψ' are:
Figure BDA0003166071650000227
Figure BDA0003166071650000228
the compression ratios of the working medium in the compressor 3 and the turbine 5 in the Brayton-Carlina cycle power supply regenerative mode are determined by the isentropic efficiency of the compressor 3 and the inlet and outlet temperatures. The compression ratio intermediate parameters of the working medium in the compressor 3 and the turbine 5 are as follows:
Figure BDA0003166071650000229
the system energy storage comprehensive efficiency is determined by the refrigeration coefficient epsilon of the refrigeration energy storage cycle, the heat engine efficiency eta in the power supply and heating mode and the power generation efficiency eta ' and eta ' in the ammonia circulation regenerative system 20, wherein eta ' is ignored.
In the invention, the pipeline of the working medium needs to be sealed and can bear the pressure of at least 30Bar and the high temperature of 600 ℃.
Results of the experiment
Two examples are listed below to describe the operation mode of the brayton-kalina cycle type energy storage and power supply apparatus based on cold storage brayton according to the second embodiment of the present invention, and the operation mode of the brayton-kalina cycle type energy storage and power supply apparatus based on regenerative brayton according to the second embodiment of the present invention.
According to the second embodiment of the present invention, for the refrigeration energy storage mode, the temperature of the low temperature cold storage tank 15 may be fixed, for a given compression ratio 22, the air intake device sucks in a dry working medium (assuming a normal temperature of 20 ℃) from the outside as a working medium, then the working medium is adiabatically compressed by the compressor to do work for 4.42MW, 482 ℃ higher than an ideal outlet temperature may be calculated according to the isentropic efficiency and the compression ratio of the compressor, the working medium exchanges heat with the low temperature heat storage tank 13 of the main heat storage system 8 after coming out of the compressor, heats the molten salt in the low temperature heat storage tank 3 at a low temperature of 166 ℃ to the temperature of 467 ℃ molten salt, and the temperature of the working medium is reduced to 181 ℃ after isobaric heat release for-2.88 MW. The working medium enters the turbine 5 to do work outside by-2.42 MW after exchanging heat with the main heat storage system 8, the outlet temperature of the turbine 5 is-72 ℃ at the moment, the working medium is discharged from the turbine and exchanges heat with the normal-temperature heat storage tank 16, the antifreeze in the normal-temperature heat storage tank 16 with the high temperature of 20 ℃ is cooled to the antifreeze temperature of-57 ℃, the working medium absorbs heat by the isobaric pressure of 0.88MW and then is heated to 5 ℃, the temperature of the working medium is lower than the ambient temperature of 15 ℃ at the moment and is supplied as cold air, and the cold air power is 0.14 MW.
Therefore, in the refrigeration energy storage mode, when the input power is 2MW, the fused salt stores heat by 2.88MW, the antifreeze stores cold by 0.88MW, and the cold air is released by 0.14 MW.
For the power supply and heating mode, the compression ratio of 7.11 different from that of the refrigeration cycle is used to enable the whole cycle to be self-consistent, after the working medium comes out of the cold accumulation heat exchanger 18, the temperature is-42 ℃ according to the temperature difference of 15 ℃ of the heat exchanger, heat is released to be-0.74 MW, then the working medium is subjected to adiabatic compression work application of 1.85 by the compressor 3 and reaches the outlet temperature of 151 ℃, the working medium comes out of the compressor 3 and exchanges heat with the main heat storage system 8, the molten salt in the high-temperature heat storage tank 14 with the high temperature of 467 ℃ is cooled to the temperature of the molten salt with the low temperature of 166 ℃, and the temperature of the working medium is raised to 452 ℃ after isobaric heat release. After the working medium exchanges heat for 2.88MW through the main heat exchanger 4, the working medium enters the turbine 5 to do work for-2.83 MW outside through adiabatic expansion, the outlet temperature is 156 ℃, after the working medium comes out from the turbine, the temperature of the working medium is 136 ℃ higher than the ambient temperature, the waste heat power is 1.3MW, and if the power generation efficiency of the regenerative system is about 22% at the moment. The power can be recovered to 0.286 MW. Therefore, in the power supply and heating mode, the power supply is 0.98MW, the waste heat recovery is 0.26MW, and the total power generation is about 1.266 MW. The comprehensive energy storage efficiency is 63.3%.
According to the fourth embodiment of the invention, in the energy storage residual cold recovery mode, the brayton-kalina cycle type energy storage power supply device absorbs dry air with a flow rate of 256.28Kg/s at a normal temperature of 20 ℃ from the outside from the air inlet device 1 as a working medium, the working medium enters the regenerative heat exchanger 2 to perform isobaric heat absorption, the temperature is raised after absorbing 37.69MW of heat from the regenerative heat storage system 7, so that the temperature of the high-temperature working medium is raised from the normal temperature of 20 ℃ to 167 ℃, and on the other hand, the heat storage medium in the high-temperature regenerative tank 12 is lowered from the temperature of 170 to 23 and then enters the low-temperature regenerative tank 11 through the regenerative medium pump 9; then the working medium enters the compressor 3 for adiabatic compression, and for a given compression ratio of 18.3, the working medium is compressed into high-temperature and high-pressure gas, wherein the compressor 3 is not an ideal compressor, the isentropic efficiency of 0.9 is considered, and the temperature of the gas after coming out of the outlet of the compressor 3 is increased to be
Figure BDA0003166071650000241
Degree; then the working medium enters the main heat exchanger 4 to perform isobaric heat release, the temperature of the working medium is reduced after 158.2MW of heat of the working medium is released into the main heat storage system 8, so that the temperature of the high-temperature working medium is reduced from 799.9 ℃ to 183 ℃, and on the other hand, the temperature of the molten salt in the low-temperature heat storage tank 13 is increased from 180 ℃ to 196.9 ℃ and then the molten salt enters the high-temperature heat storage tank 14 through the heat storage medium pump 10; then the working medium enters the turbine 5 for adiabatic expansion, the working medium is expanded into low-temperature normal-pressure gas, the turbine 5 is not a turbine, and the isentropic efficiency is considered to be 0.95. The temperature of the gas is reduced to-61.4 ℃ after the gas comes out from the outlet of the turbine 5, then the working medium enters the cold accumulation heat exchanger 18 to perform isobaric heat absorption, the temperature is raised after the heat is absorbed by 20.1MW from the cold accumulation system 19, so that the temperature of the working medium is raised from-61.4 ℃ to 17 ℃, and on the other hand, the temperature of the cold accumulation medium in the normal-temperature cold accumulation tank 16 is reduced from 20 ℃ to-58.4 ℃ at normal temperature and then enters the low-temperature cold accumulation tank 15 through the cold accumulation medium pump 17; finally, the working medium is discharged from the air outlet device 6 at the temperature of 17 ℃ and is used as a cold air source to be supplied to the outside.
And for the Brayton-kalina cycle power supply regenerative mode, the Brayton-kalina cycle energy storage power supply device absorbs a certain flow from the outside from the air inlet device 1 at the normal temperature of 20 DEGThe dry air is used as working medium, the working medium enters the cold accumulation heat exchanger 18 to perform isobaric heat release, the temperature of the working medium is reduced from the normal temperature of 20 ℃ to the low temperature of 55.4 ℃ by releasing heat from the cold accumulation system 19 with the power of-19.3 MW and then is increased, on the other hand, the cold accumulation medium in the low-temperature cold accumulation tank 15 is increased from the low temperature of-58.4 ℃ to the temperature of 17 ℃ and then enters the normal-temperature cold accumulation tank 16 through the cold accumulation medium pump 17, and then the working medium enters the cold accumulation tank 16 at the temperature T0c2The gas enters the compressor 3 for adiabatic compression, and the working medium is compressed into high-temperature and high-pressure gas for a given compression ratio of 10.57, wherein the compressor 3 is not an ideal compressor, the isentropic efficiency of 0.9 is considered, and the temperature of the gas is increased to 177 ℃ after the gas comes out from the outlet of the compressor 3; the working medium enters the main heat exchanger 4 to absorb heat at equal pressure, the temperature is increased by absorbing 158.2MW of heat from the main heat storage system 8, so that the temperature of the high-temperature working medium is increased from 177 ℃ to 793.9 ℃, and on the other hand, the heat storage medium in the high-temperature heat storage tank 14 is reduced from 797.9 to 180 ℃ and then enters the low-temperature heat storage tank 13 through the heat storage medium pump 10; then the working medium enters the turbine 5 to perform adiabatic expansion and do work outwards, the working medium expands into normal pressure gas, the turbine 5 is not a turbine, and the isentropic efficiency is considered to be 0.95. The temperature of the gas after exiting from the outlet of the turbine 5 is reduced to 297 ℃; then the working medium releases energy Q to the outsideoutThe gas temperature is reduced from 297 ℃ to 173 ℃, then the working medium enters the regenerative heat exchanger 2 to perform isobaric heat release, the working medium releases 37.7MW of heat to the regenerative heat storage system 7 and then increases the temperature, so that the temperature of the working medium is reduced from 177 ℃ to 26 ℃, and on the other hand, the heat storage medium in the low-temperature heat recovery tank 11 is increased from 23 ℃ to 170 ℃ and then enters the high-temperature heat recovery tank 12 through the regenerative medium pump 9; finally, the working medium is discharged from the air outlet device 6 at the temperature of 26 ℃ and is used as a heating source to be supplied to the outside. The released heat of 37.7MW enters kalina for recycling, and the generating efficiency of the ammonia circulating regenerative system 20 is about 18%. The electric power can be recovered to 6.8 MW.
Therefore, under the energy storage residual cold recovery mode, when the input power is 100MW, the fused salt stores heat for 158MW, consumes the regenerative heat for 37.7MW, stores cold for 20.1MW, and releases cold air for 0.77 MW. Under brayton-kalina circulation power supply backheat mode, power supply is 68MW, consumes thermal storage 158MW, consumes cold-storage 19.3MW, backheat energy storage 37.7MW, and the release heat is 31.8MW, release heating installation 1.54 MW. The electric power is recovered to 6.8 MW. The energy storage efficiency is 74.8%, and the kalina cycle is stated to improve the energy storage efficiency.
In the above embodiments, the working medium is air, and may be replaced by any gas that does not change phase at the working temperature, such as carbon dioxide. Generally, monatomic gases, such as argon, nitrogen or helium, contribute to system operating efficiency due to their higher adiabatic index. However, due to the cost problem, the monatomic gas should be recycled to reduce the cost, and air is used as the diatomic gas and is a zero-cost working medium which is very easy to obtain.
In the above embodiments, the regenerative thermal storage system 7 uses a thermal storage medium in the form of a double tank, however, in other embodiments, the regenerative thermal storage system 7 may also use a single tank or a multi-tank form. That is to say, the regenerative thermal storage system 7 includes at least two thermal storage medium thermal insulation containers which are communicated with each other and have different internal thermal storage medium temperatures or at least one thermal storage medium thermal insulation container which is communicated with each other and has an inclined temperature layer with a temperature difference gradient in the internal thermal storage medium, so that the regenerative thermal storage system 7 stores or releases heat through the flow of the thermal storage medium between the thermal storage medium thermal insulation containers having different temperatures or the movement of the inclined temperature layer of the thermal storage medium in the container in the regenerative thermal storage mode of energy storage waste cold recovery or brayton-kalina cycle power supply. The heat regenerative and storage system 7 mainly functions to recycle the high-temperature gas at the outlet of the turbine 5, recycle the waste heat and then feed the waste heat into the compressor 3 to improve the efficiency and reduce the compression ratio. The heat storage medium of the main heat storage system 8 can be heat storage medium or heat conduction oil, the working temperature range of the heat conduction oil is more advantageous within 400 ℃, the working temperature of the heat conduction oil is relatively higher than that of water or antifreeze, and the heat conduction oil has good fluidity, so the heat storage medium is selected as the heat storage medium of the heat recovery heat storage system 7. Besides, water or antifreeze can also be used for the regenerative thermal storage system 7. The heat storage medium of the regenerative heat storage system 7 can also be other organic heat carriers, such as one or more liquid mixtures of mineral oil and synthetic heat transfer oil; or may be a solution, i.e. a liquid mixture of one or more of an inorganic salt or a carbon-containing compound with water; still alternatively, it may be a molten salt or a compressed gas.
In the above embodiments, the main heat storage system 8 employs one or more sets of heat storage media in the form of two tanks and the heat storage media is molten salt, however, in other embodiments, the main heat storage system 8 may also take the form of a single tank or a plurality of tanks. That is to say, the main thermal storage system 8 is formed by connecting more than one thermal storage modules in series, each thermal storage module comprises at least two thermal storage medium thermal insulation containers which are mutually communicated and have different internal thermal storage medium temperatures or at least one thermal storage medium thermal insulation container which is mutually communicated and has an inclined temperature layer with a temperature difference gradient in the internal thermal storage medium, so that the main thermal storage system 8 stores or releases heat through the flow of the thermal storage medium between the thermal storage medium thermal insulation containers with different temperatures or the movement of the inclined temperature layer of the thermal storage medium in the container in the energy storage residual cold recovery mode or the brayton-kalina cycle power supply regenerative mode. The single tank is difficult to form effective large temperature difference, and the double-tank heat storage is relatively beneficial to improving the efficiency and capacity of energy storage. On the other hand, the heat storage medium of the main heat storage system 8 may be a molten salt, which is a liquid molten substance containing a mixture of one or more salts such as nitrate, potassium salt, chlorine salt, fluorine salt, etc. at a high temperature, such as nitrate, chlorine salt, fluorine salt, wherein nitrate has a low cost and a wide working temperature, and can work at 150 ℃ to 600 ℃, and relatively speaking, nitrate is a good heat storage medium; chlorine and fluorine salts generally operate above 400 ℃. On the other hand, the heat conducting oil can also be used. For lower heat storage temperature, heat conduction oil can be adopted, for example, the boiling point of alkylbenzene type heat conduction oil is 170-180 ℃, the boiling point of alkyl naphthalene type heat conduction oil is 240-280 ℃, the boiling point of alkyl biphenyl type heat conduction oil is over 330 ℃, the use temperature of biphenyl and biphenyl ether low-melting mixture type heat conduction oil can reach 400 ℃, and the use temperature of alkyl biphenyl ether type heat conduction oil is not more than 330 ℃ at most. Of course the thermal storage medium may also be a solution, i.e. a liquid mixture of one or more of an inorganic salt or a carbon-containing compound and water. In addition, the heat storage medium can also adopt compressed gas, namely high-temperature and high-pressure gas is directly sealed in a metal sealing tank, and a heat insulation layer is additionally arranged.
In the above-described embodiments, the cold storage system also employs the cold storage medium in the form of a double tank, however, in other embodiments, the cold storage system 19 may also employ a multi-tank form, but it is difficult to provide a single-tank form because it is necessary to include a medium container with or without an insulating layer. That is, the cold accumulation system comprises at least two cold accumulation medium heat preservation containers which are mutually communicated and have different internal cold accumulation medium temperatures or at least two cold accumulation medium heat preservation containers which are mutually communicated and have inclined temperature layers with temperature difference gradients, so that when the cold accumulation system is in a refrigeration energy storage mode or supplies heat and power, cold accumulation or cold release is carried out through the flowing of the cold accumulation medium between the cold accumulation medium heat preservation containers with different temperatures or the movement of the inclined temperature layers of the cold accumulation medium in the containers. The cold accumulation system mainly serves as a low-temperature heat source of the whole system. The cold storage medium of the cold storage system 19 may be an antifreeze (a mixed liquid containing one or more of water, ethylene glycol, glycerin, methanol, and ethanol), or any mixed liquid containing one or more of methanol, ethanol, ethylene glycol, glycerol, and lubricating oil and water. The antifreeze has a low melting point, and is therefore suitable for cold storage to obtain a low temperature point T0In fact, the antifreeze can also be replaced by other media, such as water or heat transfer oil, or even heat storage bricks. The melting point temperature of water is lower than that of molten salt, the water can be used as a low-temperature heat source, the cost of the water is lower, and the requirement on the purity of the water is not high, so that even natural precipitation with zero cost can be used. Although the antifreeze has certain cost, the energy storage efficiency of the whole system can be effectively improved, so that the antifreeze is used as a cold storage medium. The cold storage medium may also be a liquid mixture solution comprising water or carbon-containing compounds.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention, and various modifications may be made to the above-described embodiment of the present invention. All simple and equivalent changes and modifications made according to the claims and the content of the specification of the present application fall within the scope of the claims of the present patent application. The invention has not been described in detail in order to avoid obscuring the invention.

Claims (10)

1. A Brayton-kalina circulating energy storage power supply method is characterized by comprising the following modes:
(1) an energy storage mode: after the working medium at normal temperature is subjected to adiabatic compression by a compressor, an isobaric heat release process is carried out through a main heat storage system; the working medium discharges heat to the waste heat boiler, enters a turbine for adiabatic expansion to do work outwards, then carries out an isobaric heat absorption process through a cold accumulation system, and is recycled or released to the outside;
(2) a power supply mode: the normal temperature working medium is subjected to isobaric heat release through a cold accumulation system, then is subjected to adiabatic compression through a compressor, is subjected to isobaric heat absorption through a main heat accumulation system, then enters a turbine for adiabatic expansion to apply work to the outside, and then is circulated or released to the outside after the heat is discharged to a waste heat boiler; the net output work is used to power the process;
for the energy storage mode and the power supply mode, the basic ammonia solution enters a waste heat boiler to absorb heat discharged from the working medium to the waste heat boiler, so that the basic ammonia solution is converted into an ammonia water gas-liquid mixture through isobaric heat absorption and enters a separator; the method comprises the steps of separating a gas-liquid two-phase mixture into ammonia-rich steam and an ammonia-poor solution by using a separator, wherein the ammonia-rich steam enters a steam turbine for adiabatic expansion to do work outwards, the ammonia-poor solution enters an ammonia circulating heat exchanger to preheat a basic ammonia solution before entering an evaporator, the ammonia-poor solution is throttled and depressurized by a throttle valve after being discharged, then is mixed with exhaust steam discharged from the steam turbine in a mixer to form a basic ammonia solution, enters a condenser for isobaric heat release, is boosted by a working medium pump, then enters the ammonia circulating heat exchanger to be preheated by the ammonia-poor solution, and then the basic ammonia solution returns to a waste heat boiler to absorb heat and repeats the process.
2. The brayton-kalina cycle energy storage and power supply method of claim 1, wherein the working medium comprises air, argon, nitrogen, helium or carbon dioxide.
3. The brayton-kalina cycle type energy storage and power supply method according to claim 1, wherein the working medium exchanges heat with the main heat storage system in the energy storage mode, so that the heat storage medium at the position of the low temperature point in the main heat storage system is separated from the low temperature point of the heat storage medium
Figure FDA0003166071640000011
Raised to a high temperature point
Figure FDA0003166071640000012
And transferring to the position of a high-temperature point of the main heat storage system; and exchanges heat with the cold accumulation system, so that the heat accumulation medium at the position of the high-temperature point in the cold accumulation system is subjected to normal temperature T from the airairDown to its low temperature point T0And transferring to the position of the low-temperature point of the cold accumulation system;
the working medium exchanges heat with the cold accumulation system in the power supply mode, so that the heat accumulation medium at the position of the low-temperature point in the cold accumulation system is subjected to heat exchange from the low-temperature point T of the heat accumulation medium0Is lifted and transferred to the position of a high-temperature point of the cold accumulation system; and exchanges heat with the main heat storage system to ensure that the heat storage medium at the position of the high-temperature point in the main heat storage system is heated from the high-temperature point
Figure FDA0003166071640000013
Lowered to the low temperature point
Figure FDA0003166071640000014
And transferred to the location of the low temperature point of the primary thermal storage system.
4. The brayton-kalina cycle type energy storage and power supply method according to claim 3, wherein in the energy storage mode, before the working medium enters the compressor, the regenerative thermal storage system performs isobaric heat absorption, so that the thermal storage medium at the high temperature point in the regenerative thermal storage system is from the high temperature point T of the regenerative thermal storage system1Down to the low temperature point Tair+ Δ T and transfer to regenerative thermal storage systemThe location of the low temperature point;
in the power supply mode, after the working medium passes through the waste heat boiler, the regenerative thermal storage system performs isobaric heat release, so that the thermal storage medium at the position of a high-temperature point in the regenerative thermal storage system is enabled to be subjected to constant-pressure heat release from a low-temperature point T of the thermal storage mediumair+ Δ T rise to the high temperature point T1And transferring to the position of a high-temperature point of the regenerative heat storage system 7; and delta T is the heat exchange temperature difference.
5. A Brayton-kalina cycle energy storage power supply device, characterized in that it is based on the Brayton-kalina cycle energy storage power supply method of one of claims 1 to 4;
corresponding to the energy storage mode, the system comprises an air inlet device, a compressor, a main heat exchanger, a waste heat boiler, a turbine, a cold accumulation heat exchanger and an air outlet device which are sequentially connected in series along the direction of a working medium, wherein the main heat exchanger is connected with a main heat accumulation system;
corresponding to the power supply mode, the system comprises an air inlet device, a cold accumulation heat exchanger, a compressor, a main heat exchanger, a turbine, a waste heat boiler and an air outlet device which are sequentially connected in series along the direction of a working medium, wherein the cold accumulation heat exchanger is connected with a cold accumulation system;
corresponding to energy storage mode and power supply mode, exhaust-heat boiler, separator, steam turbine, blender, condenser, working medium pump and ammonia circulation heat exchanger establish ties in proper order and form the return circuit along the trend of aqueous ammonia mixture medium, and the separator links to each other with the steam turbine through its rich ammonia steam outlet, the poor ammonia solution export of separator with still be equipped with between the blender along the trend of aqueous ammonia mixture medium establish ties in proper order ammonia circulation heat exchanger and choke valve.
6. The brayton-kalina cycle type energy storage and power supply device according to claim 5, wherein the main heat storage system is formed by connecting more than one heat storage modules in series, each heat storage module comprises at least two heat storage medium heat preservation containers which are communicated with each other and have different internal heat storage medium temperatures or at least one heat storage medium heat preservation container which is communicated with each other and has an inclined temperature layer with a temperature difference gradient of the internal heat storage medium;
and the cold accumulation system comprises at least two cold accumulation medium heat preservation containers which are mutually communicated and have different internal cold accumulation medium temperatures or at least two cold accumulation medium heat preservation containers which are mutually communicated and have temperature difference gradient of the internal cold accumulation medium and are provided with temperature gradient layers.
7. The brayton-kalina cycle type energy storage and power supply device according to claim 5, wherein a regenerative heat exchanger is connected in series between the air inlet device and the compressor corresponding to the energy storage mode, and the regenerative heat exchanger is connected to a regenerative heat storage system;
and corresponding to the power supply mode, a regenerative heat exchanger is connected in series between the waste heat boiler and the gas outlet device, and the regenerative heat exchanger is connected with a regenerative heat storage system.
8. The brayton-kalina cycle type energy storage and power supply device according to claim 7, wherein the regenerative thermal storage system comprises at least two thermal storage medium thermal containers which are communicated with each other and have different internal thermal storage medium temperatures or at least one thermal storage medium thermal container which is communicated with each other and has an inclined temperature layer with a temperature difference gradient for the internal thermal storage medium.
9. The brayton-kalina cycle type energy storage and power supply device according to claim 6, wherein the heat storage medium of the main heat storage system comprises a mixture of one or more of an organic heat carrier, a solution, a molten salt and a compressed gas, the solution is a liquid mixture of one or more of inorganic salts or carbon-containing compounds and water, the molten salt is a liquid molten substance at a high temperature containing a mixture of one or more of nitrates, potassium salts, chlorides and fluorine salts, and the organic heat carrier comprises a liquid mixture of one or more of mineral oil and synthetic thermal oil;
and the cold accumulation medium of the cold accumulation system comprises a mixture of one or more of methanol, ethanol, glycol, glycerol and lubricating oil and water.
10. The brayton-kalina cycle type energy storage and power supply device according to claim 8, wherein the heat storage medium of the regenerative heat storage system comprises a mixture of one or more of an organic heat carrier, a solution, a molten salt and a compressed gas, the solution is a liquid mixture of one or more of inorganic salts or carbon-containing compounds and water, the molten salt is a liquid molten substance at a high temperature containing a mixture of one or more of nitrates, potassium salts, chlorides and fluorides, and the organic heat carrier comprises a liquid mixture of one or more of mineral oil and synthetic thermal oil.
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