CN114658546B - Engineering application-oriented liquid air energy storage system and method - Google Patents
Engineering application-oriented liquid air energy storage system and method Download PDFInfo
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- CN114658546B CN114658546B CN202210280033.0A CN202210280033A CN114658546B CN 114658546 B CN114658546 B CN 114658546B CN 202210280033 A CN202210280033 A CN 202210280033A CN 114658546 B CN114658546 B CN 114658546B
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- 239000007788 liquid Substances 0.000 title claims abstract description 95
- 238000004146 energy storage Methods 0.000 title claims abstract description 40
- 238000000034 method Methods 0.000 title claims abstract description 24
- 238000011084 recovery Methods 0.000 claims abstract description 58
- 238000005057 refrigeration Methods 0.000 claims abstract description 45
- 238000001816 cooling Methods 0.000 claims abstract description 39
- 238000007906 compression Methods 0.000 claims abstract description 23
- 230000006835 compression Effects 0.000 claims abstract description 21
- 238000010438 heat treatment Methods 0.000 claims abstract description 13
- 238000010248 power generation Methods 0.000 claims abstract description 13
- 238000005496 tempering Methods 0.000 claims abstract description 11
- 230000005611 electricity Effects 0.000 claims description 29
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 21
- 239000012530 fluid Substances 0.000 claims description 20
- 238000009834 vaporization Methods 0.000 claims description 12
- 230000008016 vaporization Effects 0.000 claims description 12
- 239000011232 storage material Substances 0.000 claims description 10
- 239000002184 metal Substances 0.000 claims description 4
- 229910052573 porcelain Inorganic materials 0.000 claims description 4
- 238000005265 energy consumption Methods 0.000 claims description 3
- 239000013529 heat transfer fluid Substances 0.000 claims description 2
- 230000008569 process Effects 0.000 description 13
- 239000007789 gas Substances 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 4
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000000746 purification Methods 0.000 description 2
- 238000004064 recycling Methods 0.000 description 2
- 239000002918 waste heat Substances 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000005338 heat storage Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/08—Adaptations for driving, or combinations with, pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The application relates to a liquid air energy storage system and a method for engineering application, wherein the system comprises the following components: the air liquefaction subsystem comprises an air compressor unit, a refrigeration and cooling unit and a liquid air storage tank; the refrigeration and tempering unit cools the air output by the air compressor unit to be liquid and heats the liquid air to vaporize the liquid air; the power generation subsystem comprises a preheater and a turbine set, wherein the preheater is used for preheating vaporized air output from the refrigeration and cooling unit, and exhaust gas output by the turbine set provides a main heat source for the preheater; the low-temperature heat energy recovery unit is used for recovering heat energy of the later-stage compression of the air compressor unit and providing an auxiliary heat source for the preheater; the high-temperature heat energy recovery unit is used for recovering heat energy of the front-stage compression of the air compressor unit, and the recovered heat energy is used for further heating air pushing the turbine unit to do work so as to improve the work-doing capability of the turbine unit. The application realizes the efficient cascade utilization of the compression heat energy and the effective recovery of the liquid air cold energy, has high technical feasibility and is easy to realize engineering application.
Description
Technical Field
The application relates to the technical field of liquid air energy storage, in particular to a liquid air energy storage system and method for engineering application.
Background
The liquid air energy storage technology is a cryogenic energy storage technology which uses liquid air or liquid nitrogen as an energy storage medium. The redundant electric power of the electric network is used for driving air liquefaction circulation to manufacture liquid air and store the liquid air, and simultaneously stores high-temperature compression heat generated in the air compression process and improves the functional capacity of an air turbine when needed; when electricity is needed, the liquid air is pressurized by the liquid pump, and the low-temperature cold energy is recovered and stored to drive the air turbine to do work and generate electricity. The liquid air energy storage has the characteristics of large volume energy storage density, long service life of components, environmental friendliness, no limitation of geographical conditions and the like, and can be applied to large-scale and energy-type power systems. Whether the low-temperature vaporization cold energy of the recovered liquid air and the high-temperature compression heat energy of the compressed air can be stored and recovered efficiently is important to improving the overall performance of the liquid air energy storage system.
In the prior art, the problems of the liquid air energy storage system and the method are as follows: engineering application is difficult to realize due to the limitation of manufacturing process and cost; based on the domestic compressor manufacturing process level and system process, the outlet temperature of the compressor is difficult to keep uniform, and the recycling efficiency of compression heat recovery and liquid air vaporization cold energy recovery is low; the compression heat has the difference of high grade and low grade, and the problems of low recovery utilization rate and energy waste exist when the compression heat with different grades is uniformly utilized.
Disclosure of Invention
Aiming at the defects of the prior art, the application provides a liquid air energy storage system and a liquid air energy storage method for engineering application, which solve the technical problem of energy waste caused by low compression heat recovery utilization rate in the liquid air energy storage process.
The technical scheme adopted by the application is as follows:
the liquid air energy storage system for engineering application comprises an air liquefaction subsystem, a low-temperature heat energy recovery unit, a high-temperature heat energy recovery unit and a power generation subsystem;
the air liquefaction subsystem comprises an air compressor unit, a refrigeration and refrigeration unit and a liquid air storage tank; the air compressor unit is a multi-stage compression device with inter-stage cooling; the refrigerating and cooling unit is used for cooling compressed air output by the air compressor unit to be in a liquid state, the liquid air storage tank is used for storing the cooled liquid air, and the refrigerating and cooling unit is also used for recovering cold energy generated by vaporization of the liquid air so as to reduce air liquefaction energy consumption;
the power generation subsystem comprises a preheater and a turbine set, wherein the preheater is used for preheating vaporized air output from the refrigeration and cooling unit, the turbine set is a multi-stage turbine power generation device which takes air as working medium and carries out interstage heating, and exhaust gas output by the turbine set provides a main heat source for the preheater;
the low-temperature heat energy recovery unit is used for recovering low-grade heat energy compressed at the rear stage of the air compressor unit, and the recovered low-grade heat energy provides an auxiliary heat source for the preheater;
the high-temperature heat energy recovery unit is used for recovering high-grade heat energy compressed by a front stage of the air compressor unit, and the recovered high-grade heat energy is used for further heating air pushing the turbine unit to do work so as to improve the work-doing capability of the turbine unit.
The further technical scheme is as follows:
the refrigeration and tempering unit comprises a tempering module and a low-temperature expander;
the cold return module comprises a cold accumulator and a heat exchanger, wherein the cold accumulator recovers cold energy generated by vaporization of liquid air and uses the recovered cold energy for further cooling compressed air output by the air compressor unit;
when the cold energy of the cold accumulator is insufficient, compressed air output by the air compressor unit enters the low-temperature expansion machine and the heat exchanger in two ways respectively, and the air expanded and cooled to low temperature by the low-temperature expansion machine is used as cold source air to further cool the air flowing through the heat exchanger to be in a liquid state.
And a return pipeline is arranged between the cooling module and the air compressor unit and is used for conveying the cold source air after cooling release back to the air compressor unit for pressurization again to form circulation.
The low-temperature heat energy recovery unit comprises a cold water tank and a hot water tank;
the cold water tank, the final-stage cooler of the air compressor unit, the hot water tank and the preheater are connected in series to form a circulation loop.
The high-temperature heat energy recovery unit comprises a heat accumulator, a radiator, a first three-way valve and a second three-way valve;
the first three-way valve is respectively connected with a hot end outlet of a heat conduction fluid medium of the heat accumulator, inlets of heaters of all stages of the turbine unit and outlets of coolers of all stages of the air compressor unit;
the second three-way valve is respectively connected with a cold end outlet of a heat conduction fluid medium of the heat accumulator, an outlet of the radiator and inlets of coolers of all stages of the air compressor unit;
the outlets of the heaters of each stage of the turbine unit are respectively connected with the inlets of the radiators.
The heat conduction fluid medium adopted by the high-temperature heat energy recovery unit is heat conduction oil; the heat accumulator is filled with energy storage materials, and the energy storage materials adopt one of cobbles, porcelain balls and metal balls.
The low-temperature expander is in power connection with the air compressor unit, so that the air compressor unit recovers the output function of the low-temperature expander for pressurizing air.
And when the main heat source of the preheater is insufficient, the auxiliary heat source is utilized to supply heat, otherwise, the auxiliary heat source is not utilized to supply heat.
The low-temperature heat energy recovery unit and the high-temperature heat energy recovery unit are respectively used for supplying the recovered heat to external users.
An energy storage method of the liquid air energy storage system facing engineering application comprises the following steps:
in the electricity consumption low-valley period, the air compressor unit compresses the external air to high pressure, and the high-pressure air is cooled to low-temperature liquid air through the refrigeration and cooling unit and stored in the liquid air storage tank; meanwhile, the high-grade heat energy compressed by the front stage of the air compressor unit is recovered by the high-temperature heat energy recovery unit, and the low-grade heat energy compressed by the rear stage of the air compressor unit is recovered by the low-temperature heat energy recovery unit;
in the electricity consumption peak period, liquid air is pumped out by a liquid air storage tank, flows through a refrigeration and refrigeration unit for vaporization, cold energy is stored in the refrigeration and refrigeration unit, the vaporized air is initially heated in a preheater, and then is heated and expanded to do work through a turbine unit interstage to drive a generator to generate electricity;
the heat source for interstage heating of the turbine unit in the electricity consumption peak period is from the high-grade heat energy recovered by the high-temperature heat energy recovery unit in the electricity consumption low-temperature period through the heat-conducting fluid medium; the cold source for interstage cooling of the air compressor unit in the electricity low-valley period is from a heat-conducting fluid medium after heat is released from the inside of the high-temperature heat energy recovery unit;
the main heat source of the preheater in the electricity consumption peak period comes from exhaust gas discharged by the turbine set for acting, and the auxiliary heat source comes from low-grade heat energy recovered by the low-temperature heat energy recovery unit; when the main heat source is insufficient, the auxiliary heat source is started.
The beneficial effects of the application are as follows:
aiming at the problem that the compression and outlet temperatures are difficult to maintain uniformly and accurately, the application stores and utilizes the compression heat in steps, thereby obviously improving the recycling rate of energy.
The application realizes the efficient cascade utilization of compression heat and the effective recovery of liquid air cold energy, greatly improves the thermodynamic performance and economic benefit of the system, and has the theoretical cyclic electricity storage efficiency of more than 50 percent.
The system adopts the process equipment with stable design, wherein main equipment such as a compressor, a turbine expander, a high-pressure heat exchanger, a regenerator, a heat accumulator and the like can be manufactured in China, the difficult problem of neck clamping is avoided in theory, and the technical feasibility is high.
The refrigeration and cooling unit and the high-temperature heat energy recovery unit have high integration level, small manufacturing difficulty and small cold dissipation.
Drawings
Fig. 1 is a schematic diagram of a system structure according to an embodiment of the present application.
Fig. 2 is a schematic structural diagram of a regenerator in a back cooling module according to an embodiment of the present application.
In the figure: 100. an air compressor unit; 101. A filter; 102. A centrifugal air compressor unit; 103. a first cooler; 104. A second cooler; 105. a precooler; 106. a purifier; 107. an air reversing tee joint; 108. A centrifugal booster unit; 109. A third cooler; 110. A fourth cooler; 200. A refrigerating and cooling unit; 201. A back cooling module; 202. A low temperature expander; 300. a liquid air storage tank; 400. a liquid-air pump; 500. A preheater; 600. A turbine unit; 601. A first heater; 602. A first turbine; 603. A second heater; 604. A second turbine; 605. A third heater; 606. A third turbine; 700. A low-temperature heat recovery unit; 701. A cold water tank; 702. A hot water tank; 800. A high-temperature heat recovery unit; 801. A heat accumulator; 802. A first three-way valve; 803. A heat sink; 804. A second three-way valve; 1021. A first centrifugal air compressor; 1022. a second centrifugal air compressor; 1023. a third centrifugal air compressor; 1081. A first centrifugal supercharger; 1082. a second centrifugal supercharger; 1083. Third centrifugal pressurization; 1084. A fourth centrifugal supercharger; 1085. a fifth centrifugal supercharger; 2011. a housing.
Description of the embodiments
The following describes specific embodiments of the present application with reference to the drawings.
As shown in fig. 1, the present application provides a liquid air energy storage system for engineering applications, which includes an air liquefaction subsystem, a low-temperature heat energy recovery unit 700, a high-temperature heat energy recovery unit 800 and a power generation subsystem;
an air liquefaction subsystem including an air compressor train 100, a refrigeration chiller 200, and a liquid air storage tank 300; air compressor package 100 is a multi-stage compression device with inter-stage cooling; the refrigeration and tempering unit 200 is used for cooling the compressed air output by the air compressor unit 100 to a liquid state, the liquid air storage tank 300 is used for storing the cooled liquid air, and the refrigeration and tempering unit 200 is also used for recovering cold energy generated by vaporization of the liquid air so as to reduce air liquefaction energy consumption;
the power generation subsystem comprises a preheater 500 and a turbine set 600, wherein the preheater 500 is used for preheating vaporized air output from the refrigeration and refrigeration unit 200, the turbine set 600 is a multi-stage turbine power generation device which takes air as a working medium and is provided with interstage heating, and the exhaust gas output by the turbine set 600 provides a main heat source for the preheater 500;
the low-temperature heat energy recovery unit 700 is used for recovering low-grade heat energy compressed by the rear stage of the air compressor unit 100, and the recovered low-grade heat energy provides an auxiliary heat source for the preheater 500;
the high-temperature heat energy recovery unit 800 is used for recovering high-grade heat energy compressed by the front stage of the air compressor unit 100, and the recovered high-grade heat energy is used for further heating air pushing the turbine unit 600 to do work so as to improve the working capacity of the turbine unit 600.
In one embodiment, air compressor package 100 includes a filter 101, a centrifugal air compressor package 102, a first cooler 103, a second cooler 104, a precooler 105, a purifier 106, an air reversing tee 107, a centrifugal booster package 108, a third cooler 109, and a fourth cooler 110; the devices are sequentially arranged along the air flow direction, and the connection relation of the devices along the air side is as follows:
the input end of the filter 101 is used for being connected with the outside air, and the output end of the filter 101 is connected with the input end of the centrifugal air compressor unit 102;
the centrifugal air compressor unit 102 is preferably of a three-stage compression design, and comprises a first centrifugal air compressor 1021, a second centrifugal air compressor 1022 and a third centrifugal air compressor 1023 shown in fig. 1, and can also be of a first stage, a second stage or a fourth stage;
the input end of the first cooler 103 is connected with the output end of the second centrifugal air compressor 1022, and the output end of the first cooler 103 is connected with the input end of the third centrifugal air compressor 1023;
the input end of the second cooler 104 is connected with the output end of the centrifugal air compressor unit 102, and the output end of the second cooler 104 is connected with the input end of the precooler 105;
the output end of the precooler 105 is connected with the input end of the purifier 106, the output end of the purifier 106 is connected with the first inlet end of the air reversing tee 107, and the output end of the air reversing tee 107 is connected with the input end of the centrifugal booster unit 108;
the centrifugal boost unit 108 is preferably of a five stage compression design, including a first centrifugal booster 1081, a second centrifugal booster 1082, a third centrifugal booster 1083, a fourth centrifugal booster 1084, and a fifth centrifugal booster 1085, as shown in fig. 1; other levels such as three-level, four-level and the like can be adopted;
an input end of the third cooler 109 is connected to an output end of the third centrifugal booster 1083, and an output end of the third cooler 109 is connected to an input end of the fourth centrifugal booster 1084;
the input end of the fourth cooler 110 is connected with the output end of the centrifugal booster unit 108, the output end of the fourth cooler 110 is connected with the input end of the refrigeration and tempering unit 200, and the reflux gas output end of the refrigeration and tempering unit 200 is connected with the second inlet end of the air reversing tee 107;
a centrifugal air compressor unit 102 that pressurizes raw air to a prescribed pressure for purification, and a centrifugal booster unit 108 that pressurizes raw air and return air returned from the refrigeration and return unit 200 to a high-pressure supercritical state.
In one embodiment, the refrigeration chiller unit 200 includes a chiller module 201 and a low temperature expander 202;
the recooling module 201 includes a regenerator and a heat exchanger, the regenerator recovers cold energy generated by vaporization of liquid air and uses the recovered cold energy to further cool compressed air output from the air compressor unit 100;
when the cold energy of the regenerator is insufficient, the compressed air output by the air compressor unit 100 is split into two streams and enters the low-temperature expander 202 and the heat exchanger, and the air expanded and cooled to the low temperature by the low-temperature expander 202 is used as cold source air to further cool the air flowing through the heat exchanger to be in a liquid state.
A return line is provided between the cooling module 201 and the air compressor package 100 for returning the cold source air (and the "return air") to the air compressor package 100 for re-pressurization to form a cycle.
As shown in fig. 2, the regenerator operation of the recooling module 201 includes a cool-charging process and a cool-releasing process:
the cold charging process occurs in the electricity consumption peak period, at this time, liquid air flows in from the bottom of the shell 2011 of the regenerator, evaporates into high-pressure gas in the regenerator and flows out from the top, and the vaporization cold energy of the liquid air is transferred to the cold storage material in the shell 2011 of the regenerator for storage;
the cold releasing process occurs in the electricity consumption valley period, and at this time, the external air is compressed and cooled, flows in from the top of the regenerator, absorbs the low-temperature cold energy stored in the regenerator, and finally flows out from the bottom of the shell 2011 to form liquid air and is stored in the liquid air storage tank.
Specifically, the energy storage material filled in the regenerator of the back cooling module 201 may be cobblestone, porcelain ball, metal ball, etc., and the air may be in direct contact with the regenerator material or may be indirectly transferred to store high-grade cold.
Specifically, the preferred structure of the back cooling module 201 includes a cold box, in which components such as a regenerator, a heat exchanger, a pipe, and a valve are integrated, and the low temperature expander 202 is located outside the cold box.
The cooling liquefaction of compressed air by the refrigeration chiller 200 has two modes of operation:
1) There is a back-cooled air liquefaction cycle: the cold energy is absorbed in the cold accumulator to cool and liquefy. The method comprises the following steps: the air output by the centrifugal booster unit 108 enters the back cooling module 201, is liquefied after cold energy is absorbed by the cold accumulator, and then enters the liquid air storage tank 300.
2) No back cooling air liquefaction circulation: failure to obtain sufficient cold energy from the regenerator requires the cryogenic expander 202 to liquefy, such as by means of an expander when no cold energy can be recovered from the regenerator during initial start-up. The method comprises the following steps:
when the cold energy of the cold accumulator is insufficient, air entering the cold return module 201 is divided into two parts, one part passes through the low-temperature expansion machine 202, the other part enters the heat exchanger, one part passing through the heat exchanger is cooled by being used as a cold source after being expanded, cooled and liquefied by the low-temperature expansion machine 202, the cooled liquid air enters the liquid air storage tank 300 for storage, the cold source returns to the second inlet end of the air reversing tee 107 after being released for cooling, and enters the centrifugal booster unit 108 again from the output end of the air reversing tee 107 for pressurization to form circulation.
The low-temperature cold energy is produced by expansion in the low-temperature expander 202, most of the cold energy is finally stored in the form of liquid air, and is recycled by the regenerator of the back-cooling module 201 in the power generation process, and a small part of the cold energy can be dissipated due to equipment cold loss.
Specifically, the low temperature expander 202 is in power connection with the air compressor package 100 to form a booster turbine expander, such that the air compressor package 100 recovers the output of the low temperature expander 202 for use in booster air.
In one embodiment, the turbine unit 600 includes a first heater 601, a first turbine 602, a second heater 603, a second turbine 604, a third heater 605, and a third turbine 606, where the above devices are sequentially arranged along the working air flow direction, i.e., the devices are sequentially connected in the order listed above along the working medium side.
Wherein the output of the third turbine 606 is coupled to the heat source medium input of the preheater 500 for providing a primary heat source for the preheater 500.
Specifically, the cold medium input end of the preheater 500 is connected to the preheated liquid air output end of the refrigeration and tempering unit 200, and the preheated liquid air input end of the refrigeration and tempering unit 200 is connected to the output end of the liquid air storage tank 300 through the liquid air pump 400.
In one embodiment, the low-temperature heat recovery unit 700 includes a cold water tank 701 and a hot water tank 702; the cold water tank 701, the final stage cooler of the air compressor package 100, the hot water tank 702, and the preheater 500 are connected in series in a circulation loop.
The low-temperature heat recovery unit 700 adopts a "double-tank" model including a cold water tank 701 and a hot water tank 702, and uses water as a heat storage medium, and the low-temperature heat recovery unit 700 can realize the waste heat utilization for providing a heating service to a user.
The low-temperature heat recovery unit 700 is used as an auxiliary heat source of the preheater 500 when necessary, and provides for preheating the liquid air in the system through the preheater 500. The dashed lines between cold water tank 701, preheater 500 and hot water tank 702 in fig. 1 indicate that an auxiliary heat source supply circuit is formed between the three when the main heat source provided by turbine unit 600 of preheater 500 is insufficient to meet the preheating requirement; when the main heat source provided by the turbine unit 600 is sufficient, the low-temperature heat recovery unit 700 is not required to provide a heat source for the preheater 500. It can be understood by those skilled in the art that the corresponding connecting pipelines are all provided with valve devices, and the automatic switching of the heat source can be realized through the cutting-off of the valves.
In an embodiment, the high-temperature heat recovery unit 800 includes a heat accumulator 801, a radiator 803, a first three-way valve 802, and a second three-way valve 804;
the first three-way valve 802 is respectively connected with a hot end outlet of the heat conduction fluid medium of the heat accumulator 801, inlets of the heaters of all stages of the turbine unit 600 and outlets of the coolers of all stages of the air compressor unit 100;
the second three-way valve 804 is respectively connected with a cold end outlet of the heat conduction fluid medium of the heat accumulator 801, an outlet of the radiator 803 and inlets of coolers of each stage of the air compressor unit 100;
the heater outlets of each stage of the turbine unit 600 are respectively connected to inlets of the radiator 803.
The heat accumulator 801 is filled with energy storage materials, and the energy storage materials adopt one or more of cobbles, porcelain balls and metal balls. The heat transfer fluid medium used in the high-temperature heat recovery unit 800 is preferably heat transfer oil.
The operation of the heat accumulator 801 includes a heat accumulation process and a heat release process:
the heat release process occurs in the electricity consumption peak period, high-temperature heat conduction oil flows out from a hot end outlet of a heat conduction fluid medium of the heat accumulator 801, flows into each stage of heater (a third heater 605, a second heater 603 and a first heater 601) of the turbine unit 600 through a first three-way valve 802 respectively, flows out from each stage of heater of the turbine unit 600, flows back to a cold end of the heat conduction fluid medium of the heat accumulator 801 after heat dissipation and temperature reduction through a radiator 803, and heats up after absorbing heat energy stored by an energy storage material in the process of flowing from the cold end to the hot end in the heat accumulator 801, and flows out from a hot end outlet of the heat conduction fluid medium of the heat accumulator 801 to form circulation;
the heat accumulation process occurs in the electricity consumption valley period, normal-temperature heat conduction oil flows out from a cold end outlet of a heat conduction fluid medium of the heat accumulator 801, flows into each stage of coolers (a third cooler 109, a second cooler 104 and a first cooler 103) of the air compressor unit 100 through a second three-way valve 804 respectively, flows out from each stage of coolers of the air compressor unit 100, returns to a hot end of the heat conduction fluid medium of the heat accumulator 801 through a first three-way valve 802, releases heat energy to an energy storage material in the process of flowing from the hot end to the cold end in the heat accumulator 801, then cools down, and flows out from the cold end outlet of the heat conduction fluid medium of the heat accumulator 801 to form circulation.
Specifically, the high-temperature heat recovery unit 800 may also be used to supply the recovered heat to an external user for waste heat utilization.
It will be appreciated by those skilled in the art that in the liquid air energy storage system for engineering application of the present application, the necessary valve devices are disposed on the connecting lines between the devices, and automatic control can be achieved through the valves.
The application also provides an energy storage method of the liquid air energy storage system facing the engineering application, which comprises the following steps:
during the electricity consumption low-valley period, the air compressor unit 100 compresses the external air to a high pressure, and the high-pressure air is cooled to low-temperature liquid air through the refrigerating and cooling unit 200 and stored in the liquid air storage tank 300; meanwhile, the high-grade heat energy of the front-stage compression of the air compressor unit 100 is recovered by the high-temperature heat energy recovery unit 800, and the low-grade heat energy of the rear-stage compression of the air compressor unit 100 is recovered by the low-temperature heat energy recovery unit 700;
in the electricity consumption peak period, liquid air is pumped out by the liquid air storage tank 300, flows through the refrigeration and refrigeration unit 200 for vaporization, cold energy is stored in the refrigeration and refrigeration unit 200, the vaporized air is initially heated in the preheater 500, and then is heated and expanded to work through the interstage of the turbine unit 600 to drive the generator to generate electricity;
wherein:
the heat source for interstage heating of the turbine unit 600 in the electricity consumption peak period comes from the high-grade heat energy recovered by the high-temperature heat energy recovery unit 800 in the electricity consumption low-temperature period through the heat-conducting fluid medium; the cold source for interstage cooling of the electric low-valley period air compressor unit 100 comes from the heat-conducting fluid medium after heat release inside the high-temperature heat recovery unit 800;
the main heat source of the preheater 500 in the electricity consumption peak period comes from the exhaust gas discharged by the turbine set 600 for doing work, and the auxiliary heat source comes from the low-grade heat energy recovered by the low-temperature heat energy recovery unit 700; when the main heat source is insufficient, the auxiliary heat source is started.
In one embodiment, during the off-peak period, the external air is purified by the filter 101 to enter the centrifugal air compressor unit 102 with inter-stage cooling, pressurized to a purification pressure of about 0.9MPa, pre-cooled by the pre-cooler 105 to the purifier 106 to remove impurities such as water and carbon dioxide; then the air is boosted to a high pressure of about 8MPa by the centrifugal booster unit 108 with inter-stage cooling, is cooled to low-temperature liquid air (when the cold energy of the cold accumulator is insufficient, the low-temperature expansion agent is started for cooling) by the cold accumulator through the refrigeration and refrigeration unit 200, and the liquid air is output from the refrigeration and refrigeration unit 200 and stored in the liquid air storage tank 300;
in one embodiment, during peak electricity consumption, liquid air is pumped from the liquid air storage tank 300 by the liquid air pump 400, flows to the regenerator of the refrigeration and refrigeration unit 200, is vaporized in the regenerator, and leaves cold energy in the regenerator, and the vaporized air is initially heated to about 85 ℃ by the high-temperature air of the turbine in the preheater 500 (which can be adjusted according to practical conditions).
In one embodiment, the compression heat recovered from the outlet air (about 113 ℃) of the fourth cooler 110 by the low-temperature heat recovery unit 700 is stored in the form of hot water, which can be used as city heating output on the one hand, and can also preheat gasified air when the heat source required in the preheater is insufficient on the other hand.
In an embodiment, the heat-conducting fluid medium adopted by the high-temperature heat energy recovery unit 800 is heat-conducting oil, and the heat-conducting oil recovers high-grade heat energy generated in the compression process of the air compressor unit 100 and is stored in the heat accumulator 801 in the electricity consumption low-valley period, and when the electricity consumption peak period needs to reheat air, the high-temperature heat-conducting oil leads out heat from the heat accumulator 801.
In order to further illustrate the technical effects of the application, simulation calculation is performed on the system shown in fig. 1, and in the whole system, the power consumption is about 14.36MW for 8 hours in the charging process, namely the electricity consumption low-valley period; the power generation process is to generate 9.19MW in the power peak period for 5 hours. The design cycle power storage efficiency of the system can be calculated to be 51%.
Those of ordinary skill in the art will appreciate that: the foregoing description is only a preferred embodiment of the present application, and the present application is not limited thereto, but it is to be understood that modifications and equivalents of some of the technical features described in the foregoing embodiments may be made by those skilled in the art, although the present application has been described in detail with reference to the foregoing embodiments. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the protection scope of the present application.
Claims (10)
1. The liquid air energy storage system for engineering application is characterized by comprising an air liquefaction subsystem, a low-temperature heat energy recovery unit (700), a high-temperature heat energy recovery unit (800) and a power generation subsystem;
the air liquefaction subsystem comprises an air compressor unit (100), a refrigeration and refrigeration unit (200) and a liquid air storage tank (300); the air compressor unit (100) is a multi-stage compression device with inter-stage cooling; the refrigerating and cooling unit (200) is used for cooling compressed air output by the air compressor unit (100) to be in a liquid state, the liquid air storage tank (300) is used for storing the cooled liquid air, and the refrigerating and cooling unit (200) is also used for recovering cold energy generated by vaporization of the liquid air so as to reduce air liquefaction energy consumption;
the power generation subsystem comprises a preheater (500) and a turbine set (600), wherein the preheater (500) is used for preheating vaporized air output from the refrigeration and refrigeration unit (200), the turbine set (600) is a multi-stage turbine power generation device which takes air as a working medium and is provided with interstage heating, and the exhaust gas output by the turbine set (600) provides a main heat source for the preheater (500);
the low-temperature heat energy recovery unit (700) is used for recovering low-grade heat energy of the post-stage compression of the air compressor unit (100), and the recovered low-grade heat energy provides an auxiliary heat source for the preheater (500);
the high-temperature heat energy recovery unit (800) is used for recovering high-grade heat energy compressed by the front stage of the air compressor unit (100), and the recovered high-grade heat energy is used for further heating air pushing the turbine unit (600) to do work so as to improve the working capacity of the turbine unit (600).
2. The liquid air energy storage system for engineering applications of claim 1, wherein the refrigeration and tempering unit (200) comprises a tempering module (201) and a cryogenic expander (202);
the cold return module (201) comprises a cold accumulator and a heat exchanger, wherein the cold accumulator recovers cold energy generated by vaporization of liquid air and uses the recovered cold energy for further cooling compressed air output by the air compressor unit (100);
when the cold energy of the cold accumulator is insufficient, compressed air output by the air compressor unit (100) respectively enters the low-temperature expander (202) and the heat exchanger in two streams, and the air expanded and cooled to low temperature by the low-temperature expander (202) is used as cold source air to further cool the air flowing through the heat exchanger to be in a liquid state.
3. The liquid air energy storage system for engineering applications according to claim 2, wherein a return line is arranged between the cooling module (201) and the air compressor unit (100) for delivering the cooled cold source air back to the air compressor unit (100) for pressurization again to form a cycle.
4. The liquid air energy storage system for engineering applications according to claim 1, wherein the low temperature heat energy recovery unit (700) comprises a cold water tank (701) and a hot water tank (702);
the cold water tank (701), the final stage cooler of the air compressor unit (100), the hot water tank (702) and the preheater (500) are connected in series to form a circulation loop.
5. The liquid air energy storage system for engineering applications according to claim 1, wherein the high temperature heat energy recovery unit (800) comprises a regenerator (801), a radiator (803), a first three-way valve (802) and a second three-way valve (804);
the first three-way valve (802) is respectively connected with a hot end outlet of a heat conduction fluid medium of the heat accumulator (801), inlets of heaters of all stages of the turbine unit (600) and outlets of coolers of all stages of the air compressor unit (100);
the second three-way valve (804) is respectively connected with a cold end outlet of a heat conduction fluid medium of the heat accumulator (801), an outlet of the radiator (803) and inlets of coolers of all stages of the air compressor unit (100);
the outlets of the heaters of each stage of the turbine unit (600) are respectively connected with the inlets of the radiators (803).
6. The liquid air energy storage system for engineering applications according to claim 5, wherein the heat transfer fluid medium used by the high temperature heat recovery unit (800) is heat transfer oil; the heat accumulator (801) is filled with energy storage materials, and the energy storage materials adopt one of cobbles, porcelain balls and metal balls.
7. The liquid air energy storage system for engineering applications of claim 2, wherein the cryogenic expander (202) is in dynamic connection with the air compressor package (100) such that the air compressor package (100) recovers the output of the cryogenic expander (202) for use in pressurizing air.
8. The liquid air energy storage system for engineering applications of claim 1, wherein the primary heat source of the preheater (500) is utilized to provide heat when insufficient, and wherein the secondary heat source is not utilized to provide heat otherwise.
9. The liquid air energy storage system for engineering applications according to claim 1, wherein the low temperature heat energy recovery unit (700) and the high temperature heat energy recovery unit (800) are also used for supplying the recovered heat to external users, respectively.
10. A method of storing liquid air energy for engineering applications according to any one of claims 1 to 9, comprising:
during the electricity consumption valley period, the air compressor unit (100) compresses the external air to high pressure, the high-pressure air is cooled to low-temperature liquid air through the refrigeration and back-cooling unit (200), and the low-temperature liquid air is stored in the liquid air storage tank (300); meanwhile, the high-temperature heat energy recovery unit (800) recovers high-grade heat energy compressed by the front stage of the air compressor unit (100), and the low-grade heat energy compressed by the rear stage of the air compressor unit (100) is recovered by the low-temperature heat energy recovery unit (700);
in the electricity consumption peak period, liquid air is pumped out by a liquid air storage tank (300), flows through a refrigeration and refrigeration unit (200) for vaporization, cold energy is stored in the refrigeration and refrigeration unit (200), the vaporized air is initially heated in a preheater (500), and then is subjected to interstage heating and expansion work through a turbine unit (600) to drive a generator for power generation;
the heat source of the inter-stage heating of the turbine unit (600) in the electricity consumption peak period is from the high-grade heat energy recovered by the heat conduction fluid medium through the high-temperature heat energy recovery unit (800) in the electricity consumption low-temperature period; the cold source of the inter-stage cooling of the air compressor unit (100) in the electricity-using valley period comes from the heat-conducting fluid medium after heat release in the high-temperature heat energy recovery unit (800);
the main heat source of the preheater (500) in the electricity consumption peak period comes from exhaust gas discharged by the turbine set (600) for doing work, and the auxiliary heat source comes from low-grade heat energy recovered by the low-temperature heat energy recovery unit (700); when the main heat source is insufficient, the auxiliary heat source is started.
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| AU2017416627A1 (en) * | 2017-06-01 | 2020-01-23 | Institute Of Engineering Thermophysics, Chinese Academy Of Sciences | Staged cold energy storage type supercritical compressed air energy storage system and method |
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